Protocols & Procedures (WIP)

Explore measurement guides developed by CUNY BPL for agency use, for evaluating pre- and post-retrofit conditions of common retrofits under DEM’s energy efficiency programs. Learn more about this guide and see how to get started. Explore our content sitemap and see how everything connects.

All Plants

Plants are centralized systems that work together to maintain occupant comfort and provide essential functions in a facility such as air, water, and electricity distribution. Plants comprise various systems and components that serve different functions. More The operation and efficiency of the systems and their components determine the energy consumption and environmental impact of the plant. Monitoring building systems and components can provide a better understanding of how energy is used and where improvements can be made to reduce consumption, GHG emissions, and operational costs to meet efficiency and environmental goals. Read more about each plant below. Less

Cooling

Air-cooled Chilled Water Plant
General Overview An air-cooled chilled water plant consists of an air-cooled chiller system and a chilled water loop system operating together to meet the cooling demand in a facility. The air-cooled chiller produces chilled water through the basic refrigeration cycle. The primary chilled water pump circulates the chilled water between the chiller and the chilled water loop. In some cases, a secondary chilled water pump distributes the chilled water produced by the chiller to air handling units (AHUs) in the building. Figure 1. Air-cooled chilled water plant (click on image to enlarge). Systems Air-cooled Chiller An air-cooled chiller provides chilled water to the chilled water loop system and components. Learn More Figure 2. Air-cooled chiller (click on image to enlarge). Chilled Water Loop A chilled water loop system consists of a closed loop distribution system that supplies chilled water to the building and includes components (see Figure 3). Learn More Figure 3. Chilled water loop (click on image to enlarge). Evaluation of Energy Consumption The primary energy consumption of an air-cooled chilled water plant is the sum of the energy consumed by its individual components. The thermal energy rejected from the building to the outdoors can also be measured to assess the plant’s overall performance, typically expressed in kilowatts of power consumed per ton of cooling provided (kW/ton). Table 1 summarizes the system component measurements and values required to quantify the annual energy consumption and operating characteristics of an air-cooled chilled water plant. Table 1. Key values and components to measure to evaluate energy consumption. Plant Quantification Values to be Quantified Energy Consuming Component Air-cooled chilled water plant electricity usage (kWh) Average hourly chiller kWh Average hourly pump motor kWh Condenser fan motor Compressor motor Chilled water pump motors Cooling load on building/Heat rejected to the outdoors Average hourly thermal load of chiller evaporator (Btu/h) Further Reading ASHRAE (2020). 2020 ASHRAE Handbook: HVAC Systems and Equipment. Atlanta, GA: ASHRAE. Gordon, J.M.; Ng, K.C. (2000). Cool thermodynamics: The engineering and physics of predictive, diagnostic and optimization methods for cooling systems. Cambridge International Science Publishing; pp. 159-177. Wei, J.; Reddy, T.A. (2003). “Reevaluation of the Gordon-Ng Performance Models for Water-Cooled Chillers.” ASHRAE Transactions, Vol. 109, Part 2. Atlanta, GA: American Society of Heating, Refrigerating and Air Conditioning Engineers.

An air-cooled chilled water plant consists of an air-cooled chiller system and a chilled water loop system operating to meet the cooling demand in a …


Water-cooled Chilled Water Plant
General Overview A water-cooled chilled water plant consists of a water-cooled chiller system, a condenser water loop system and a chilled water loop system operating together to meet cooling demand in a facility. If a waterside economizer is implemented in the facility, the chilled water plant includes a waterside economizer system as well. Figure 1. Water-cooled chilled water plant (click on image to enlarge). Systems Water-cooled Chiller A water-cooled chiller produces chilled water using the basic refrigeration cycle, which is then distributed through the chilled water loop to the facility. The primary systems and components of a water-cooled chiller are shown in Figure 2. Learn More Figure 2. Water-cooled chiller (click on image to enlarge). Chilled Water Loop A chilled water loop consists of a closed loop distribution system that supplies chilled water to the building. Components of a chilled water loop are shown in Figure 3. Learn More Figure 3. Chilled water loop (click on image to enlarge). Condenser Water Loop A condenser water loop consists of an open loop distribution system that circulates condenser water from a chiller condenser to a cooling tower, where the condenser water is cooled and returned to the chiller condenser. Components of a condenser water loop are shown in Figure 4. Learn More Figure 4. Condenser water loop (click on image to enlarge). Waterside Economizer System Waterside economizers may use an external plate-and-frame heat exchanger between the condenser and chilled water loop, or the chiller itself may be set up to perform the function of a waterside heat exchanger. When the outdoor temperatures are favorable, heat from the chilled water loop may be rejected directly to the condenser water loop through a heat exchanger without running the chiller compressor motor. Components of a waterside economizer system are shown in Figure 5. Learn More Figure 5. Waterside economizer system (click on image to enlarge). Evaluation of Energy Consumption The primary energy consumption of a water-cooled chilled water plant is the total energy used by its individual components. The thermal energy rejected from the building to the outdoors can also be measured to assess the plant’s overall performance, typically expressed in kilowatts of power consumed per ton of cooling provided (kW/ton). Table 1 summarizes the system component measurements and values needed to quantify the annual energy consumption and operating characteristics of the water-cooled chilled water plant. Table 1. Key values and components to measure to evaluate energy consumption. Plant Quantification Values to be Quantified Energy Consuming Component Water-cooled chilled water plant electricity usage (kWh) Average hourly chiller (kWh) Average hourly pump motors (kWh) Average hourly cooling tower fan motors (kWh) Chiller compressor motor Chilled water pump motors Condenser water pump motors Heat exchanger pump motor (if present) Cooling tower fan motors Cooling load on building/Heat rejected to the outdoors Average hourly thermal load on chiller evaporator (Btu/h) Coefficient of Performance (COP) Electricity input Cooling load output Further Reading ASHRAE (2019). “ASHRAE Handbook: HVAC Applications,” Chapter 43. SUPERVISORY CONTROL STRATEGIES AND OPTIMIZATION. I-P Edition. ASHRAE (2019). “ASHRAE Handbook: HVAC Applications,” Chapter 48. DESIGN AND APPLICATION OF CONTROLS. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 38. COMPRESSORS. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 40. COOLING TOWERS. I-P Edition. Consulting Specifying Engineer (2021). “Understanding chilled water plant performance”. Consulting - Specifying Engineer | Understanding chilled water plant performance (csemag.com). Taylor, S (2012). “Optimizing Design & Control of Chilled Water Plants Part 5: Optimized Control Sequences”. ASHRAE Journal, Vol. 54, No 6. American Society of Heating, Refrigerating and Air Conditioning Engineers; pp: 56-74. Taylor, S (2014). “How to Design & Control Waterside Economizers.” ASHRAE Journal, Vol. 56, No 6. American Society of Heating, Refrigerating and Air Conditioning Engineers; pp: 30-36.

Consists of a water-cooled chiller system, a condenser water loop system, and a chilled water loop system operating together to meet cooling demand in a …


Heating

Hot-water Heating Plant
General Overview The hot water heating (HWH) plant uses input energy (e.g., fuel, electricity, or biomass) to generate hot water, which is distributed throughout a facility for space heating. An HWH boiler may also produce hot water for other demands, such as domestic hot water or process heat. A hot water heating plant typically consists of a hot water heating boiler, a feedwater system, and a hot water heating loop. Figure 1. Hot water heating plant (click on image to enlarge). Systems Hot Water Heating Boiler The HWH boiler system is the largest energy-consuming component of the hot water heating plant. Hot water is primarily generated through heat transfer from combustion gases in the combustion chamber to the water. The heated water is then distributed throughout the facility to meet space heating or domestic hot water demands. The main components of an HWH boiler system include the burner, combustion chamber, heat exchanger, and draft fan, as shown in Figure 2. Learn More Figure 2. Hot water heating boiler system (click on image to enlarge). Hot Water Loop The hot water loop system encompasses the distribution system responsible for moving hot water throughout the building. Components of a typical hot water loop system are primary-only or primary-secondary pumps, piping network and piping insulation and are shown in Figure 3. Learn More Figure 3. Hot water loop system (click on image to enlarge). Feedwater System The feedwater system provides treated make-up water and returned hot water from the hot water loop. Feedwater requires proper treatment to remove pollutants and preserve the efficiency of the boiler. Figure 4 shows the components for the feedwater system. Learn More Figure 4. Feedwater system and chemical treatment for make-up water (click on image to enlarge). Evaluation of Energy Conumption The total energy consumption of an HWH plant is the sum of the energy used by its individual components. This includes the fuel consumed by the boiler to meet the heating load and the electricity required to operate the burner fan motor, primary and secondary pumps, and feedwater pump. Table 1 summarizes the system component measurements and values needed to quantify the annual energy consumption and operating characteristics of the HWH plant. Table 1. Key values and components to measure to evaluate energy consumption. Plant Quantification Values to be Quantified Energy Consuming Component Hot water heating plant fuel consumption (Btu) Average hourly fuel consumption (Btuh) Boiler Hot water heating plant electricity consumption (kWh) Average hourly burner fan motor (kWh) Average hourly primary HWH pump motor (kWh) Average hourly secondary HWH pump motor (kWh) Average hourly feedwater pump (kWh) Total operating time for the pump motors Outdoor air temperature (F) Heat load delivered Average hourly heat rejected from the hot water loop (Btu/h) Terminal Units Heat recovered Average hourly heat delivered to the make-up water (Btu/h) Heat exchanger (if present) Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 32. BOILERS. I-P Edition.

Produces and distributes hot water in a facility. Terminal units are used to reject heat from the hot water and provide heating to one or more spaces.


Steam Plant
General Overview A low-pressure steam plant uses input energy (e.g., fuel, gas, or biomass) to generate steam in a boiler, which is then distributed throughout a facility or group of facilities for heating. Low pressure steam plants are generally operated at 15 psig or less (steam temperature below ~250 F). Low pressure steam can be used directly as a heating medium and distributed to the terminal equipment, or it can be used indirectly by being piped to heat exchangers to heat water to use at terminal equipment and/or domestic hot water (DHW) systems. A low pressure steam plant and associated systems are shown in Figure 1. A steam plant consists of a steam boiler, steam distribution system, condensate recovery system, blowdown system and economizer. Figure 1. Steam plant diagram (click on image to enlarge). Systems Steam Boiler A steam boiler system is the largest energy-consuming system in the steam plant. A steam boiler generates steam by transferring heat from the combustion gases in the combustion chamber to the water. The steam produced is then transported out to the facility to meet the heating loads. Learn More Figure 2. Steam Boiler System (click on image to enlarge). -- Steam Distribution System A low-pressure steam distribution system supplies the steam to the facility or facilities. Steam distribution systems are generally closed-loop, where the steam condensate is returned to the steam boiler to be re-heated (see Condensate Recovery System below). The steam distribution system contains various valves and steam traps to regulate heating and manage condensate throughout a building. Learn More Figure 3. Steam Distribution System (click on image to enlarge). Condensate Recovery System A condensate recovery system complements the steam distribution system to maintain the efficiency of the steam plant. The condensate usually returns to the boiler, minimizing the feedwater and fuel supply to the boiler. Learn More Figure 4. Condensate Recovery System (click on image to enlarge). Feedwater System The feedwater system provides fresh or, at times, treated water to the steam boiler system and allows for removal of water that contains pollutants (i.e., unwanted minerals and/or sediment). This increases the longevity of the system equipment, at a cost of the energy required to heat the feedwater, which is colder than the recirculated condensate. Feedwater systems may include a heat exchanger – commonly called an economizer – which recovers heat from the boiler fuel gases and uses it to pre-heat the feedwater. Learn More Figure 5. Feedwater System (click on image to enlarge). Blowdown System The blowdown system removes suspended solids and sludge from the boiler water to maintain the operation and efficiency of steam plant components. An integrated blowdown system minimizes unnecessary blowdown by monitoring water quality and allows heat recovery from the blowdown water to preheat feedwater, generate service hot water, or support other applications. Figure 6. Blowdown System (click on image to enlarge). Evaluation of Energy Consumption The total energy consumption of a steam plant is the sum of the energy used by its individual components. This includes the fuel consumed by the boiler to meet the building’s heating load and the electricity required to operate the burner fan motor, condensate pump, and feedwater pump. Table 1 summarizes the system component measurements and values needed to quantify the annual energy consumption and operating characteristics of the steam plant. Table 1. Key values and components to measure to evaluate energy consumption. Plant Quantification Values to be Quantified Energy Consuming Component Steam boiler plant fuel consumption (Btu) Average hourly fuel consumption (Btu/h) Boiler Steam plant electricity consumption (kWh) Average hourly burner fan motor (kWh) Total operating hours of burner fan motor Average hourly condensate pump motor kWh Average hourly feedwater pump motor (kWh) Total operating time for pump motors Burner fan motor Condensate pump motor Feedwater pump motor Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 11. STEAM SYSTEMS. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 32. BOILERS. I-P Edition. ASHRAE (2019). “ASHRAE Handbook: HVAC Applications,” Chapter 50, Section 2.5. WATER TREATEMENT: DEPOSITION, CORROSION, AND BIOLOGICAL CONTROL. I-P Edition. Spirax Sarco (2022). “Learn More About Steam” Steam Insights. https://www.spiraxsarco.com/learn-about-steam.

Produces and distributes steam throughout the facility for space heating. Terminal units transfer heat to the spaces, while condensate recovery systems …


Air Handling

Air Handling Plant
General Overview The air handling plant (AHP) uses input energy (e.g., electricity, heated water, or chilled water) to condition the air and maintain required indoor environmental conditions such as temperature, humidity, and fresh air supply. The AHP may consist of various types of air handling units (AHUs) at the system level, including rooftop units, fan coil units, and constant-speed units, which will be discussed in the system-level descriptions. For a more detailed overview of various system configurations for this plant, please refer to the ASHRAE HVAC Systems and Equipment Handbook (2020), Section 4 – Air Handling and Distribution. Figure 1. Air Handling Plant (click on image to enlarge). Systems The systems and components that make up the air handling plant are listed and described further in Table 1 below. It should be noted that for a given AHP, there may be a mix of air handling systems installed (e.g., constant-speed, constant-volume, variable air volume) and configurations (e.g., split heat pump, rooftop unit). Constant-speed, Constant-volume (CSCV) AHU A CSCV air handling system provides heating, cooling, and ventilation air to a space in a facility. The AHU is built out of various sections on-site. The volume of outside air in the AHU can be modulated from 0% (outside air damper fully closed) to a typical ventilation rate (minimum outside air damper position) and in some cases can provide 100% outside air (economizer mode). Learn More Figure 2. CSCV Air Handling Unit Systems and Components (click on image to enlarge). Dual-speed, Constant-Volume (DSCV) AHU A DSCV system is similar to a CSCV system, except the fan motors in the AHU have a high and low speed setting. This configuration allows the AHU to operate at a slower speed during setbacks at unoccupied times, such as night or weekends. Variable-air Volume (VAV) AHU A VAV system consists of a main AHU and multiple VAV boxes that serve different zones. The AHU has fan motors that are equipped with variable frequency drives (VFDs) that allow the fan speed (and associated air volume) to modulate as the building demand changes. VAV boxes are installed in the supply air ductwork in the zones served and are generally installed with a heating coil, also known as a reheat coil. This enables the system to adjust the supply air temperature to prevent over-cooling a space. The VAV system allows for space temperature and ventilation air control in each zone. VAV boxes are usually set with a minimum damper position associated with the minimum required ventilation airflow needed for the zone. Learn More Figure 3. VAV Air Handling Plant Systems and Components (click on image to enlarge). Air-to-air Energy Recovery Air-to-air heat exchangers transfer energy between two airstreams that must be at different temperatures for sensible heat transfer and different moisture contents for latent heat transfer. Learn More Dedicated Outdoor Air System (DOAS) A DOAS system is designed to heat, cool, humidify, dehumidify, and filter ventilation air independent of the space heating and cooling needs of a facility. A DOAS can generally provide limited space heating and cooling, but only as a byproduct of the required volumes of ventilation air provided to a space or zone. Fan Coil Unit (FCU) An FCU is a smaller, factory-assembled device that circulates and conditions air. Split Heat Pump (HP) An HP is a split system that provides heating or cooling and is comprised of an indoor unit with a fan and evaporator coil and an outdoor unit with a fan and condenser coil. Fuel-Fired Furnace A fuel-burning device that heats air for space conditioning. Rooftop Unit (RTU) A roof-mounted packaged system that provides heating, cooling, and ventilation while supplying air directly to a space below or into a set of ducts. Induction Unit (non-fan powered) A system that uses a fast-moving primary air stream (usually created by a set of nozzles) to induce air from the space to be drawn through the unit and mixed with the primary air stream. The primary air stream is generated by a separate system such as a CSCV AHU or a DOAS. Evaluation of Energy Consumption The energy consumption of an air handling plant (AHP) is the total energy used by each air handling unit (AHU) system, including electricity for the supply and return fans and the energy required to heat or cool the air. Heating and cooling energy may come from a central heating or cooling plant or be generated directly at the AHU, such as natural gas for heating or electricity for compressor-based cooling. Table 1 summarizes the system component measurements and values needed to quantify the annual energy consumption of an AHP. Table 1. Key values and components to measure to evaluate energy consumption. System(s) Values to Quantify Energy Consuming Component Constant-speed, constant-volume AHU Dual-speed, constant-volume AHU Variable air volume AHU Dedicated outside air system Fan coil unit Average hourly fan motor kWh Average Btu/h at coils Fan motors Heating coil Cooling coil Heat pump Average hourly heat pump kWh (includes supply and condenser fan motors and compressor motors) Fan motors Compressor Fuel fired furnace Average hourly furnace fuel consumption Average hourly burner kWh (includes supply fan motors) Burner Fan motors Rooftop Unit Average hourly fuel consumption: average hourly rooftop unit kWh (includes supply and condenser fan motors and compressor motors) Burner Fan motors Compressor Induction Unit Average Btu/h at coils Heating coil Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 1. HVAC SYSTEM ANALYSIS AND SELECTION. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 4. AIR HANDLING AND DISTRIBUTION. I-P Edition. ASHRAE (2019). “ANSI/ASHRAE/IES Standard 90.1-2019 – Energy Standard for Buildings Except Low-Rise Residential Buildings”. ASHRAE. Taylor, S (2014). “Return Fans in VAV Systems”. ASHRAE Journal, Vol. 56; pp. 54-58.

This plant conditions and distributes air in a facility to meet required indoor environmental conditions. This plant works in conjunction with heating and …


Lighting

Lighting Plant
General Overview A lighting plant consists of the electrical distribution system and one or more light fixture systems. The electrical distribution system provides power to the light fixture system, which provides the actual illumination to indoor spaces, emergency evacuation routes, and outdoor areas. The electrical distribution system receives electricity from the power grid, which then is distributed through switchgear and panelboards. A lighting plant and associated systems are shown in Figure 1. Measurements may be taken at the electrical distribution or light fixture system levels. Figure 1. Lighting Plant. Keep in mind that a lighting plant will have several electrical panelboards (click on image to enlarge). Systems Electrical Distribution System The electrical distribution system is comprised of main and secondary switchgear and panelboards. The switchgear distributes electricity to the panelboards, and the panelboards provide electricity to the light fixture systems. Panelboards typically serve light fixture systems in multiple spaces across a facility and are generally broken down by floor or smaller spaces on a floor. Sometimes multiple electric panelboards are required to provide power to a single space such as a warehouse, gymnasium, or garage. Components of an electrical distribution system are shown in Figure 2. Learn More Figure 2. Electrical distribution system (click on image to enlarge). note Panelboards can have mixed loads or be dedicated just to lighting. Mixed panelboards serve the light fixture systems and other electrical loads such as receptacles, office equipment, or miscellaneous plug loads. Dedicated panelboards exclusively serve light fixture systems including interior, exterior, and emergency lighting. Light Fixture System The light fixture system is comprised of luminaires, lamps, and controls. Controls can be manual or automatic. All lighting systems have some form of manual controls, such as wall switches within a space or electrical disconnects (circuit breakers) at the panelboard. Some lighting systems have automatic controls, which may include a control panel and sensors. Components of a light fixture system are shown in Figure 3. Learn More Figure 3: Two Dedicated Lighting Panelboards with Automatic Controls, each panelboard is considered a system (click on image to enlarge). Evaluation of Energy Consumption To quantify the energy consumption of the lighting plant, the components of all lighting systems should be measured. Some facilities may have a combination of the aforementioned systems and a level of engineering judgement will be necessary to determine how much of what to measure. Table 1. Key values and components to measure to evaluate energy consumption. Plant Quantification Values to be Quantified Energy Consuming Component Lighting plant electricity usage (kWh) Average hourly kWh served by the electrical distribution system Light fixtures and automatic controls (if applicable). Further Reading Richman, EE. (2016). “Measurement and Verification of Energy Savings and Performance from Advanced Lighting Control.” Richland, WA: Pacific Northwest National Laboratory.

Consists of the electrical distribution system and light fixture systems to provide illumination to the interior and exterior of the facility.


All Systems

Systems are interconnected groups of equipment within a facility that support the operation of the building’s plant. These systems fulfill essential functions such as supplying conditioned air, electricity, and hot and cold water, ensuring the building operates efficiently and meets occupant needs. More Certain systems can be measured to determine their energy usage, which helps in estimating their annual energy consumption. By monitoring these systems, inefficiencies can be identified more easily, performance can be optimized, and energy use can be managed effectively to meet sustainability goals. Other systems consist of multiple components that collectively support system operations. To accurately assess the energy consumption of such systems, all components within them should be measured. Read more about each system below. Less

Cooling

Air-cooled Chiller
General Overview An air-cooled chiller consists of an evaporator, a compressor, condenser fans, and an expansion valve. The system produces chilled water through the basic refrigeration cycle. Components Each of the various components associated with an air-cooled chiller are listed below (see Figure 1). Air-cooled chillers may be customized with a variety of high-performance components, such as variable frequency drives (VFD) on condenser fans and compressors, high efficiency compressor designs, thermostatic or electronic expansion valves, condenser coils with enhanced heat transfer characteristics, optimized condenser fan design and system airflow characteristics, and digital direct control systems that optimize the energy efficiency of the chiller. Figure 1. Air-cooled chiller (click on image to enlarge). Evaporator The evaporator transfers heat from the chilled water to the refrigerant. Compressor The compressor increases the temperature and pressure of the refrigerant; a chiller may have one or more compressors. Air-cooled chillers typically have screw, scroll, and reciprocating compressors. Reciprocating compressors are among the most widely used types in this type of chiller. They consist of a cylinder and a piston that move in a reciprocating motion to compress the refrigerant. Screw compressors generate high pressure for small amounts of refrigerant vapor by compressing it between a pair of meshing screws. Scroll compressors use two interleaved scrolls that rotate simultaneously to compress refrigerant vapor within a chamber. Learn More Condenser Fan Condenser fans of an air-cooled chiller cool down the refrigerant by forcing airflow over the condenser coils using outdoor air. Constant-speed, Constant-volume Condenser Fan A constant-speed, constant-volume (CSCV) fan uses a power-driven rotating impeller to circulate air at a single speed. Learn More Variable-speed, Variable-volume Condenser Fan A variable-speed, variable-volume (VSVV) fan uses a power-driven rotating impeller to circulate air. Air flow rates fluctuate as required by the plant and system it serves. Learn More Expansion Valve The expansion valve reduces the pressure in the refrigerant, allowing it to collect heat in the evaporator. Evaluation of Energy Consumption The primary energy consumption of an air-cooled chiller is the electricity used for the compressor motor and condenser fan motors. The thermal energy rejected by the chiller to the outdoors can also be measured to evaluate the overall performance of the chiller. These two values can be expressed as kilowatts of power consumed per ton of cooling provided (kW/ton). Table 1 provides a summary of the components measurements and values needed to quantify the annual energy consumption and operating characteristics of an air-cooled chiller. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements Air-cooled chiller electricity usage (kWh) Average hourly chiller kWh Annual operating time for the chiller Condenser fan motor Compressor motor and its controls Hourly measurements of true RMS Annual operating hours Hourly measurement of outdoor air temperature Cooling load on building/Heat rejected to the outdoors Average hourly chilled water flow rate (GPM) Chilled water pump Hourly measurement of chilled water flow rate Average hourly chilled water temperature difference across evaporator (F) Evaporator Hourly temperature of chilled water entering and leaving the chiller evaporator Measurement Locations The measurement locations for an air-cooled chiller and chilled water pumps are shown in Figure 2. Figure 2. Air cooled chiller measurement locations (click on image to enlarge). Further Reading ASHRAE (2020). 2020 ASHRAE Handbook: HVAC Systems and Equipment. Atlanta, GA: ASHRAE. Gordon, J.M.; Ng, K.C. (2000). Cool thermodynamics: The engineering and physics of predictive, diagnostic and optimization methods for cooling systems. Cambridge International Science Publishing; pp. 159-177. Wei, J.; Reddy, T.A. (2003). “Reevaluation of the Gordon-Ng Performance Models for Water-Cooled Chillers.” ASHRAE Transactions, Vol. 109, Part 2. Atlanta, GA: American Society of Heating, Refrigerating and Air Conditioning Engineers.

Produces chilled liquid and works in conjunction with an AHU to provide cooling. The condenser rejects heat absorbed by the refrigerant directly to the …


Chilled Water Loop
Header for marker 1 Lorem ipsum dolor sit amet, consectetur adipiscing elit, sed do eiusmod tempor incididunt ut labore et dolore magna aliqua. Porttitor lacus luctus accumsan tortor posuere. Semper risus in hendrerit gravida rutrum. Porttitor rhoncus dolor purus non enim. Suspendisse ultrices gravida dictum fusce ut placerat orci nulla. Leo vel fringilla est ullamcorper. Integer malesuada nunc vel risus commodo viverra maecenas. In ante metus dictum at tempor commodo ullamcorper a. Dui id ornare arcu odio ut sem nulla pharetra. Nullam eget felis eget nunc lobortis mattis aliquam. Consectetur adipiscing elit pellentesque habitant morbi tristique senectus. Check this page for reference. Header for marker 2 Lorem ipsum dolor sit amet, consectetur adipiscing elit, sed do eiusmod tempor incididunt ut labore et dolore magna aliqua. Porttitor lacus luctus accumsan tortor posuere. Semper risus in hendrerit gravida rutrum. Porttitor rhoncus dolor purus non enim. Suspendisse ultrices gravida dictum fusce ut placerat orci nulla. Leo vel fringilla est ullamcorper. Integer malesuada nunc vel risus commodo viverra maecenas. In ante metus dictum at tempor commodo ullamcorper a. Dui id ornare arcu odio ut sem nulla pharetra. Nullam eget felis eget nunc lobortis mattis aliquam. Consectetur adipiscing elit pellentesque habitant morbi tristique senectus. Check this page for reference. .imageMap__container { width: 100%; display: grid; grid-template-columns: repeat(11, 1fr); grid-template-rows: repeat(11, 1fr); position: relative; margin-top: 5rem; overflow: hidden; } .imageMap__container img { width: 100%; height: auto; grid-column: 1/-1; grid-row: 1/-1; pointer-events: none; overflow: hidden; } .markers { background: #52a85a; border-width: 4px; border-style: solid; border-radius: 50%; border-color: #fff; width: 18px; height: 18px; box-sizing: border-box; align-self: center; justify-self: center; animation: ownpulse 3s cubic-bezier(.19,1,.22,1) infinite both; position: relative; outline: 3px solid #52a85a; &:hover { cursor: pointer; } } .markers:hover { background: #19232a; outline-color: #19232a; } .markers:focus-within .marker__card, .markers:focus .marker__card { display: block; } .marker__card { background-color: #19232a; color: white; padding: 1.5em; border-radius: 8px; display: none; min-height: 100px; position: absolute; width: 350px; height: 250px; overflow: scroll; z-index: 100; -webkit-box-shadow: 0.8px 0.6px 2.2px rgba(0, 0, 0, 0.02), 2px 1.5px 5.3px rgba(0, 0, 0, 0.028), 3.8px 2.9px 10px rgba(0, 0, 0, 0.035), 6.7px 5.1px 17.9px rgba(0, 0, 0, 0.042), 12.5px 9.6px 33.4px rgba(0, 0, 0, 0.05), 30px 23px 80px rgba(0, 0, 0, 0.07); box-shadow: 0.8px 0.6px 2.2px rgba(0, 0, 0, 0.02), 2px 1.5px 5.3px rgba(0, 0, 0, 0.028), 3.8px 2.9px 10px rgba(0, 0, 0, 0.035), 6.7px 5.1px 17.9px rgba(0, 0, 0, 0.042), 12.5px 9.6px 33.4px rgba(0, 0, 0, 0.05), 30px 23px 80px rgba(0, 0, 0, 0.07); min-width: 220px; animation: fadeInUp; animation-duration: .5s; animation-fill-mode: both; cursor: default; } .left-marker { left: 20px; } .right-marker { left: -360px; } .bottom-marker { top: -250px; } .marker__card__title { color: inherit; margin-top: 0; margin-bottom: 1rem; &:hover { cursor: text; } } .marker__card__content { &:hover { cursor: text; } } #img-container:hover { transform: scale(1.75); -webkit-box-shadow: 0.8px 0.6px 2.2px rgba(0, 0, 0, 0.02), 2px 1.5px 5.3px rgba(0, 0, 0, 0.028), 3.8px 2.9px 10px rgba(0, 0, 0, 0.035), 6.7px 5.1px 17.9px rgba(0, 0, 0, 0.042), 12.5px 9.6px 33.4px rgba(0, 0, 0, 0.05), 30px 23px 80px rgba(0, 0, 0, 0.07); box-shadow: 0.8px 0.6px 2.2px rgba(0, 0, 0, 0.02), 2px 1.5px 5.3px rgba(0, 0, 0, 0.028), 3.8px 2.9px 10px rgba(0, 0, 0, 0.035), 6.7px 5.1px 17.9px rgba(0, 0, 0, 0.042), 12.5px 9.6px 33.4px rgba(0, 0, 0, 0.05), 30px 23px 80px rgba(0, 0, 0, 0.07); z-index: 5; } #img-container:hover .marker__card { font-size: 13px; } @keyframes ownpulse { 0% { -webkit-box-shadow: 0 0 0 0 #fff; box-shadow: 0 0 0 0 #fff; } 50% { -webkit-box-shadow: 0 0 0 40px rgba(92,112,214,0); box-shadow: 0 0 0 40px rgba(92,112,214,0); } 0% { -webkit-box-shadow: 0 0 0 0 #fff; box-shadow: 0 0 0 0 #fff; } 50% { -webkit-box-shadow: 0 0 0 40px rgba(92,112,214,0); box-shadow: 0 0 0 40px rgba(92,112,214,0); } } @keyframes zoomIn { 0% { opacity: 0; transform: scale3d(.3,.3,.3); -webkit-transform: scale3d(.3,.3,.3); } 50% { opacity: 1; } } @keyframes fadeInUp { 0% { opacity: 0; transform: scale3d(.3,.3,.3) translate3d(0,100%,0); -webkit-transform: scale3d(.3,.3,.3); -webkit-transform: translate3d(0,100%,0); } 100% { opacity: 1; -webkit-transform: none; transform: none; } 0% { opacity: 0; -webkit-transform: translate3d(0,100%,0); transform: scale3d(.3,.3,.3) translate3d(0,100%,0); } 100% { opacity: 1; -webkit-transform: none; transform: none; } } -- General Overview A chilled water (CHW) loop consists of two main components: pumps and motors, and a piping network. The pumps circulate chilled water from the chiller’s evaporator through the piping network to terminal units, such as water-to-air heat exchangers in air handling units or radiant equipment like chilled beams, before returning it to the chiller. A CHW loop can be designed as either a primary-flow system or a primary-secondary system. Primary Flow A primary-flow chilled water system consists of CHW pumps that circulate chilled water from the air-conditioned zone to the chillers. Primary pumps are usually headered to allow for the minimum flow through the chiller and there are usually multiple pumps to allow for staging and redundancy; however, a chiller dedicated pumping design can also be found in some facilities. Primary-flow systems can be either constant-primary-flow or variable-primary-flow. A constant-primary-flow system usually has a staged cooling system and constant speed CHW pumps. A variable-primary-flow system has primary CHW pumps with variable speed drives that regulate the flow of the system based on the cooling load of the building. Primary-secondary Flow A primary-secondary chilled water system consists of a primary CHW loop with primary pumps as well as a secondary CHW loop with secondary pumps to distribute the cooling load to the building. The components of a primary-secondary flow system are shown in Figure 1. The following designs can be found in a primary-secondary flow system: A constant-primary variable-secondary flow system uses constant-speed pumps to maintain flow through the primary loop, while separate pumps in the secondary loop distribute flow and cooling load to the facility. This configuration typically includes a two-way valve that regulates flow between the primary and secondary loops. A variable-primary variable-secondary flow system has variable frequency drives (VFDs) installed on primary and secondary pump motors controlled by the differential pressure in the piping network. Components The main components associated with the CHW loop are primary pumps for primary-flow systems and primary and secondary pumps for primary-secondary flow systems. Figure 1. Chilled water loop components (click on image to enlarge). Primary CHW Pump and Motor A primary CHW pump and motor circulates chilled water from the evaporator section of the chiller to the building in a primary-only system or to the secondary pump and motor through the piping network. A primary CHW pump and motor can operate at constant speed or variable speed based on the design of the chilled water plant. Constant-speed, Constant-volume Pump A constant-speed, constant-volume pump and motor operates at a single speed to circulate liquid (e.g., water, water, and glycol solution) through a piping network where the flow rate through the pump does not vary more than 5%. Learn More Variable-speed, Variable-volume Pump A variable-speed, variable-volume pump and motor circulate liquid (e.g., water or water and glycol solution) through a piping network where the flow rate fluctuates as required by the plant and systems they serve. Learn More Secondary CHW Pump and Motor A secondary CHW pump and motor circulates chilled water from the primary piping network to the building. A secondary CHW pump and motor are found in primary-secondary flow systems and can be at constant-speed or can be equipped with variable frequency drives that are controlled by the differential pressure in the secondary piping network. Constant-speed, Constant-volume Pump A constant-speed, constant-volume (CSCV) pump and motor operates at a single speed to circulate liquid (e.g., water, water, and glycol solution) through a piping network where the flow rate through the pump does not vary more than 5%. Learn More Variable-speed, Variable-volume Pump A variable-speed, variable-volume (VSVV) pump and motor circulate liquid (e.g., water or water and glycol solution) through a piping network where the flow rate fluctuates as required by the plant and systems they serve. Learn More Primary CHW Piping Network The primary CHW piping network is connected to the evaporator section of the chiller and extends through the building to deliver chilled water to that facility in a primary-flow system. In a primary-secondary system, the primary piping network is dedicated to circulating chilled water through the evaporator of the chiller. Secondary CHW Piping Network The secondary CHW piping network is connected to the primary piping network to deliver chilled water to the facility. Evaluation of Energy Consumption The primary energy consumption in a CHW loop is the electricity used to run the pump motors. The heat loss across the piping network contributes to the overall energy consumption for the entire CHW loop system. Table 1 provides a summary of system component measurements and values needed to quantify the annual energy consumption and operating characteristics of a CHW loop. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements Primary CHW loop pump electricity usage (kWh) - constant-speed system Average hourly primary CHW pump motor kWh Total operating time for the pumps Constant-speed pump motor Spot measurements of true RMS power Hourly measurement of motor runtime Primary CHW loop pump electricity usage (kWh) - variable-speed system Average hourly primary CHW pump motor kWh Total operating time for the pumps Variable-speed pump motor Hourly measurement of motor runtime Hourly measurement of outdoor air temperature Secondary CHW loop pump electricity usage (kWh) - variable-speed system (if present) Average hourly primary CHW pump motor kWh Total operating time for the pumps Variable-speed pump motor Hourly measurement of motor runtime Hourly measurement of outdoor air temperature Flow (GPM) Average hourly chilled water flow (GPM) through a pump Average hourly loop pressure differential Hourly measurement of water flow rate Hourly measurement of supply and return water temperature Measurement Locations The measurement locations for a primary-flow and a primary-secondary flow are shown in Figure 2. Figure 2. Chilled water loop measurement locations (click on image to enlarge). Further Reading ASHRAE (2019). “ASHRAE Handbook: HVAC Applications,” Chapter 43. SUPERVISORY CONTROL STRATEGIES AND OPTIMIZATION. I-P Edition. Taylor, S (2012). “Optimizing Design & Control of Chilled Water Plants Part 5: Optimized Control Sequences”. ASHRAE Journal, Vol. 54, No 6. American Society of Heating, Refrigerating and Air Conditioning Engineers; pp: 56-74.

Connected to the evaporator side of a chiller, this system moves chilled water or other liquid in the facility to provide cooling with the help of pumps …


Condenser Water Loop
General Overview A condenser water (CW) loop consists of a CW pump and motor, an evaporative cooling tower with a fan and motor, and a CW piping network. The CW loop system is designed to reject the heat given off by the condenser side of the chiller. A CW loop can have the following configurations: Variable-speed Fans and Constant-flow System A variable-speed constant-flow CW loop consists of variable-speed cooling tower fans and constant-speed CW pumps. Variable-speed Fans and Variable-flow System A variable-speed variable-flow CW loop consists of variable-speed CW pumps and a cooling tower with variable-speed fans. Constant-speed Fans and Constant-flow System A constant-speed constant-flow CW loop consists of constant-speed cooling tower fans and constant-speed CW pumps. Components The main components associated with the condenser water loop are shown in Figure 1. Figure 1. Condenser water loop components (click on image to enlarge). Condenser Water Pump and Motor A condenser water pump and motor circulates condenser water from the condenser section of the chiller to the cooling tower. A condenser water loop pump and motor can be constant speed or equipped with variable frequency drives (VFDs). tip Taylor (2012) provides scenarios that limit the cost effectiveness of VFDs on condenser loop pumps. Constant-speed, Constant-volume Pump A constant-speed condenser water pump provides a fixed flow to the cooling tower and chiller, independent of cooling tower heat rejection capacity or building cooling load. Learn More Variable-speed, Variable-volume Pump A variable-speed condenser water pump and motor modulates the flow to the cooling tower and chiller based on the heat rejection capacity of the cooling tower and the minimum flow rate required through the condenser section of the chiller. Learn More Evaporative Cooling Tower An evaporative cooling tower rejects heat from the condenser section of the chiller, using forced airflow and the latent heat of evaporation to provide the cooling effect on the condenser water. A cooling tower may have one or more sections (called cells). Each cell typically has one fan and motor. The cooling tower fan and motor may operate at a constant or variable speed. Constant-speed, Constant-volume Cooling Tower Fan The overall cooling capacity of the condenser water loop in a cooling tower with multiple cells and constant speed fans and motors is controlled by staging (turning on) the cells. Learn More Variable-speed, Variable-volume Cooling Tower Fan Cooling towers with variable speed fans and motors generally operate the fans at the lowest speed possible and stage fans based on the overall CW heat rejection needed to satisfy the specific sequence of operation of the chilled water plant. Learn More Figure 2. Evaporative Cooling Tower (click on image to enlarge). Evaluation of Energy Consumption The primary energy consumption of a condenser water loop is the electricity used for the pump motors and the cooling tower fans. Table 1 provides a summary of system component measurements and value calculations needed to quantify the annual energy consumption and operating characteristics of a CW loop. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Value to be Quantified Energy Consuming Components Measurements Variable-flow CW loop electricity usage (kWh) Average hourly pump motor kWh Total operating time for the pump Variable-speed pump motor Hourly measurement of true RMS power Hourly measurement of outdoor air temperature Variable-speed cooling tower electricity usage (kWh) Average hourly fan motor kWh Total operating time for the fan Variable-speed cooling tower fan motors Hourly measurement of true RMS power Hourly measurement of outdoor air temperature Hourly measurement of relative humidity Constant-flow CW loop electricity usage (kWh) Average hourly pump motor kWh Total operating time for the pump Constant-speed pump motor Spot measurements of true RMS power Hourly measurement of motor runtime Constant-speed cooling tower electricity usage (kWh) Average hourly fan motor kWh Total operating time for the fan Constant-speed cooling tower fan motors Spot measurements of true RMS power Hourly measurement of outdoor air temperature Hourly measurement of relative humidity Heat rejected to the outdoors Average hourly Btu rejected from the condenser water loop Hourly measurement of condenser water flow rate Hourly measurement of condenser suppy and return water temperature Measurement Locations The measurements for the condenser water loop are schematically shown in Figure 3, include: Figure 3. Condenser water loop measurement locations (click on image to enlarge). Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 40. COOLING TOWERS. I-P Edition. Taylor, S (2012). “Optimizing Design & Control of Chilled Water Plants Part 5: Optimized Control Sequences”. ASHRAE Journal, Vol. 54, No 6. American Society of Heating, Refrigerating and Air Conditioning Engineers; pp: 56-74.

Connects to the condenser side of a water-cooled chiller and uses pumps to transfer water or other liquid to cooling tower fans which reject heat to the …


Water-cooled Chiller
General Overview The water-cooled chiller system produces chilled water through the basic refrigeration cycle and consists of an evaporator, a compressor, a condenser, and an expansion valve. The system can be constant-speed or variable-speed. Constant-speed System A constant-speed water-cooled chiller has a compressor motor that runs at a constant speed based on the total capacity of the chiller and adjusts the refrigerant flow with modulating vanes in the compressor when partial capacity of the chiller is needed. Variable-speed System A variable-speed water-cooled chiller has a variable frequency drive on the compressor motor and can reduce the speed of the compressor during partial load conditions. Components The four main components of every chiller are an evaporator, a compressor and motor, a condenser, and an expansion valve. The components are shown in Figure 1. Figure 1. Water-cooled chiller components (click on image to enlarge). Evaporator The evaporator transfers heat from the chilled water loop to the refrigerant through a heat exchanger. Compressor The compressor increases the temperature and pressure of the refrigerant between the evaporator and condenser sections of a chiller. A chiller may have one or more compressors. Water-cooled chillers typically have centrifugal compressors. Centrifugal compressors are dynamic compressors, which increase refrigerant vapor pressure by converting the velocity pressure from the rotating impellers to static pressure in the discharged vapor. They can be driven with a constant-speed motor or a motor with a variable frequency drive (VFD). A centrifugal compressor with a constant-speed motor uses variable guide vanes to change the speed of the gas as it enters the compressor, which changes the centrifugal force and the lift. “Lift” in a chiller system refers to the difference between the condenser water temperature leaving the chiller and the chilled water temperature leaving the chiller. A centrifugal compressor with a VFD on the motor varies the speed of the impeller to control the lift. Condenser The condenser rejects heat from the refrigerant to the condenser water loop through a heat exchanger. Expansion Valve The expansion valve depressurizes the warm refrigerant between the condenser and evaporator to reduce the temperature of the refrigerant. Then, the cold refrigerant is delivered to the evaporator to pick up more heat from the chilled water loop. Evaluation of Energy Consumption The primary energy consumption in a water-cooled chiller is the electricity used by the compressor motor and its controls. Thermal energy rejected by the chiller to the outdoors can be measured to evaluate the overall performance of the chiller, which can be expressed as kilowatts of power consumption per ton of cooling provided (kW/ton). Table 1 provides a summary of system component measurements and values needed to quantify the annual energy consumption and operating characteristics of a water-cooled chiller. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Component to be Measured Measurements Constant-speed water-cooled chiller power draw Average hourly chiller kWh and annual operating time for the chiller Constant-speed compressor motor and controls Spot measurements of true RMS power of the constant-speed compressor motor and controls Compressor motor runtime Variable-speed water-cooled chiller power draw Hourly chiller kWh and annual operating time for the chiller Variable-speed compressor motor and its controls Spot measurements of true RMS power of the constant-speed compressor motor and controls Compressor motor runtime Hourly measurement of outdoor air temperature Cooling load on building/Heat rejected to the outdoors Hourly chilled water temperature difference across evaporator (F) Evaporator Hourly temperature of chilled water entering and leaving the chiller evaporator Hourly condenser water temperature difference across condenser (F) Condenser Hourly temperature of chilled water entering and leaving the chiller condenser. Hourly chilled water flow rate (GPM) Chilled water pump Hourly measurement of chilled water flow rate Hourly condenser water flow rate (GPM) Condenser water pump Hourly measurement of condenser water flow rate Measurement Locations The measurement locations for a water-cooled chiller are schematically shown in Figure 2. Figure 2. Water-cooled chiller measurement locations (click on image to enlarge). Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 38. COMPRESSORS. I-P Edition. Consulting Specifying Engineer (2021). “Understanding chilled water plant performance”. Consulting - Specifying Engineer | Understanding chilled water plant performance (csemag.com).

Produces chilled liquid and works in conjunction with an AHU to provide cooling. The condenser side rejects heat to the outdoor air using cooling towers.


Waterside Economizer
General Overview A waterside economizer is used to fully or partially cool the chilled water without mechanical heat transfer when outdoor air temperatures are cold enough to meet the building’s cooling demand. Typical waterside economizer systems have an external heat exchanger; however, the chiller itself may occassionally be set up to perform the function of a waterside heat exchanger. Components The components associated with a waterside economizer are heat exchanger, piping, and valves. These components are shown in Figure 1. Figure 1. Waterside economizer system components (click on image to enlarge). External Heat Exchanger Typical heat exchangers installed in waterside economizers systems are plate and frame heat exchangers. They can be configured as integrated and non-integrated economizers. The non-integrated configuration consists of a plate-and-frame heat exchanger (PFHX) in parallel with chillers and requires the heat exchanger to supply the entire cooling load. An integrated configuration, the PFHX are arranged in series, allowing the chiller to utilize pre-cooled chilled water and minimizing the energy required by chillers. Learn More Piping, fittings, and valves Piping can have different arrangements to allow the desirable operation of the waterside economizer. Evaluation of Energy Consumption The primary effect of waterside economizer is the savings in electricity usage at plant level to meet the cooling load of the building. For more information about the energy consumption of the overall water-cooled chilled water plant, see the Water-Cooled Chilled Water Plant. The cooling energy savings are equivalent to the heat rejected through the waterside economizer. Table 1 provides a summary of the components to measure to arrive at values needed to quantify the heat rejected from the chilled water to condenser water by free cooling. Table 1. Key values and measurements to evaluate heat transfer. System Quantification Values to be Quantified Energy Consuming Components Measurements Waterside economizer heat rejection load Hourly Btu/h transferred, differential of temperature for chilled water loop. Heat exchanger of waterside economizer Hourly flow rate of the supply stream (GPM) Temperature of supply stream entering and leaving the heat exchange (F)  Measurement Locations The measurement locations for the waterside economizer are schematically shown in Figure 2: Figure 2. Waterside economizer measurement locations (click on image to enlarge). Further Reading ASHRAE (2019). “ASHRAE Handbook: HVAC Applications,” Chapter 48. DESIGN AND APPLICATION OF CONTROLS. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 40. COOLING TOWERS. I-P Edition. Taylor, S (2014). “How to Design & Control Waterside Economizers,” ASHRAE Journal, Vol. 56, No 6. American Society of Heating, Refrigerating and Air Conditioning Engineers; pp: 30-36. Trane Engineers Newsletter (2016). “Waterside Economizers - Keep the ‘Free’ In Free-Cooling.” Trane, 2016. https://www.trane.com/content/dam/Trane/Commercial/global/products-systems/education-training/engineers-newsletters/waterside-design/ADM-APN058-EN_06012016.pdf.

Used to cool or partially cool the chilled water without mechanical heat transfer when outdoor air temperatures are cold enough to meet the building’s …


Heating

Boiler
General Overview A boiler system provides hot water or steam to distribute the heating load within a facility. Heat is transferred from the combustion chamber to the water until it reaches the set point temperature for hot water, the boiling point for steam, or beyond the boiling point for superheated steam. Components The main components of a boiler system are burner, combustion chamber, heat exchanger, and draft fan. These components are shown in Figure 1. Figure 1. Boiler System (click on image to enlarge). Combustion Chamber The combustion chamber is where the fuel is burned. It houses the burners and is designed to support extremely high temperatures. Heat Exchanger The heat exchanger in boiler systems facilitates heat transfer from the fuel combustion chamber to the water without direct contact. Non-condensing boilers typically have a single heat exchanger chamber, while condensing boilers include a secondary heat exchanger to increase the heat transfer area and improve efficiency. To operate in condensing mode, the return water temperature must be at or below 140°F. Learn More Burner The primary function of the burner is to deliver fuel and air, mix them in the correct proportions, provide an ignition source, and ensure efficient combustion. Burners can be designed for a single fuel or configured to operate on multiple fuels. Burner controls play a crucial role in the overall efficiency of the boiler system. Depending on the system, the firing rate may be constant, variable in discrete stages, or fully variable. Draft Fan (Burner Fan Motor) Mechanical draft boilers usually have a draft fan that creates the required pressure difference. It is driven by a motor to provide oxygen to the combustion chamber for adequate combustion. Learn More Evaluation of Energy Consumption The boiler is one of the largest energy-consuming systems in a heating plant. Its key energy-consuming components include the burner and, if present, the draft fan. The primary energy source is typically liquid fuel or natural gas, though electricity may also be used to power the draft fan. The primary energy consumption of a boiler system is the fuel that is used to drive the combustion reaction to heat the water. Table 1 provides a summary of measurements needed to quantify the annual consumption and operating characteristics of a boiler. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements Boiler energy consumption Average hourly fuel consumption (Btu/h) Burner Hourly fuel consumption by the boiler Hours of operation of the motors Hourly measurement of outside air temperature Burner fan electricity usage (kWh) Average hourly burner fan motor kWh Pump Motor Runtime Burner fan motor Spot measurements of true RMS power of the burner fan motor Hours of operation of the motors Measurement Locations The measurement locations for a boiler system are shown in Figure 2. Figure 2. Boiler measurement locations (click on image to enlarge). Further Reading ASHRAE (2014). “ASHRAE Guideline 14-2014 – Measurement of Energy, Demand, and Water Savings.” Annex A. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 11. STEAM SYSTEMS. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 21. FANS. I-P Edition.

Produces hot water or steam with the use of fuel oil or natural gas.


Feedwater System
General Overview The feedwater system usually receives condensate recovered from the condensate recovery system and make-up water (treated fresh water). It maintains water levels in the boiler, extending its lifespan. Feedwater systems supply fresh water to hot water or steam boilers to make up for losses from boiler blowdown, steam traps, hot water use, or other losses. The feedwater system receives inputs of make-up water and, in steam systems, condensate from the condensate recovery system. Components The main components of a boiler feedwater system are one or more feed pumps, and a receiver tank. Feedwater systems may include an economizer, and larger systems also may have a deaerator tank. These components are shown in Figure 1. Figure 1. Feedwater system and components (click on image to enlarge). Pumps and Motors The feedwater pumps and motors inject the feedwater stored in the feedwater tank into the boiler. The pumps and motors are driven by a feedwater controller that monitors the water level of the boiler and the water contaminant levels. When the controller receives the signal, it turns on the pumps and feedwater flows into the boiler. Constant-speed, Constant-volume Pump A constant-speed, constant-volume pump and motor operates at a single speed to circulate liquid. Learn More Variable-speed, Variable-volume Pump A variable-speed, variable-volume pump and motor circulate liquid (e.g., water or water and glycol solution) through a piping network where the flow rate fluctuates as required by the plant and systems they serve. Learn More Piping Network The piping network for a feedwater system can serve one or multiple boilers for a hot water or steam plant where each boiler has its own feedwater valve. The feedwater valve opens and closes based on the boiler controller signal. Feedwater Tank The feedwater tank is a chamber that receives make-up water and condensate recovered from the condensate recovery system. The make-up water is treated to remove contaminants and its temperature is increased prior to being discharged into the feedwater tank. Economizer An economizer–or flue gas heat recovery unit–is a heat exchanger installed on the stack of a boiler to recover heat from combustion gases discharged through the stack that would otherwise be wasted. Evaluation of Energy Consumption The primary energy consumption in a feedwater system is the electricity used to run the pump motors. Table 1 provides a summary of system component measurements and values needed to quantify the annual energy consumption and operating characteristics of the feedwater system. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements Feedwater pump electricity consumption (kWh) Average Hourly pump motor (kW) Total operating time for the pump Pump motor Hourly true RMS power draw to the pump motor Total operating hours The primary function of the economizer is to reduce fuel consumption by recovering heat from the flue stack to preheat the feedwater before it enters the boiler. This heat recovery improves efficiency and can be reflected in the overall energy consumption of the low-pressure steam plant. For more information see the steam plant. Measurement Locations The measurement locations for a feedwater water system are shown in Figure 2. Figure 2. Feedwater system measurement locations (click on image to enlarge). Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 32. Boilers. I-P Edition.

Used in hot water heating and steam plants, the feedwater system maintains a sufficient water level in a boiler with make-up water and condensate water.


Hot Water Loop
General Overview A hot water heating (HWH) loop system circulates hot water produced by a hydronic boiler to terminal units, such as heating coils in air handling units or radiant equipment, before returning it to the boiler. This circulation is managed through a piping network using either primary-only or primary-secondary pumps. Primary-flow System A primary-flow HWH loop system consists of pumps that circulate hot water from the designated zone to the boilers. The components are shown in Figure 1. Primary pumps are usually headered to allow for the minimum flow through the boiler, usually with multiple pumps to allow for staging and redundancy; however, a boiler-dedicated pumping design can also be found in some facilities. Primary-flow systems can be either constant-primary-flow or variable-primary-flow. A constant-primary-flow system usually has a staged heating system and constant speed HWH loop pumps. A variable-primary-flow system has primary HWH loop pumps with variable speed drives that regulate the flow of the system based on the heating load of the building. The heating system may be staged or constant. Primary-secondary Flow System In a system with primary-secondary pumps, the primary pumps circulate the hot water to a low loss header, while the secondary pumps circulate the hot water to the zones in the facility. The components of a primary-secondary flow system are shown in Figure 2. The following arrangements can be found in a primary-secondary flow system: A constant-primary variable-secondary flow system has constant speed pumps that drive the flow through the primary loop and variable-speed pumps of a separate secondary loop that distribute the heating load to the terminal units. The secondary pumps are controlled by the heat load demand in the terminal units. A variable-primary variable-secondary flow system has variable-speed pumps on both the primary and secondary loops. They are controlled by the firing rate in the boiler and the heat load demand in the terminal units. Components The main components associated with the HWH loop system are primary pumps for primary-flow systems, primary and secondary pumps for primary-secondary flow systems, piping network, and terminal units. Figure 1. Hot Water Loop Components (click on image to enlarge). Primary HWH Loop Pump and Motor A primary HWH loop pump and motor circulate water from the boiler to the building in a primary-only system or to the secondary pump and motor in a primary-secondary system through the piping network. A primary HWH loop pump and motor can operate at constant speed or variable speed based on the design of the hot water plant. Constant-speed, Constant-volume Pump A constant-speed, constant-volume pump and motor operates at a single speed to circulate liquid. Learn More Variable-speed, Variable-volume Pump A variable-speed, variable-volume pump and motor circulate liquid (e.g., water or water and glycol solution) through a piping network where the flow rate fluctuates as required by the plant and systems they serve. Learn More Secondary HWH Loop Pump and Motor A secondary HWH loop pump and motor circulates water from the primary piping network to the building. A secondary HWH loop pump and motor are found in primary-secondary flow systems and can be at constant-speed or can be equipped with variable frequency drives that are controlled by the differential pressure in the secondary piping network. Constant-speed, Constant-volume Pump A constant-speed, constant-volume (CSCV) pump and motor operates at a single speed to circulate liquid (e.g., water, water, and glycol solution) through a piping network where the flow rate through the pump does not vary more than 5%. Learn More Variable-speed, Variable-volume Pump A variable-speed, variable-volume (VSVV) pump and motor circulate liquid (e.g., water or water and glycol solution) through a piping network where the flow rate fluctuates as required by the plant and systems they serve. Learn More Primary HWH Loop Piping Network The primary HWH loop piping network is connected to the boiler and extends through the building to deliver hot water to that facility in a primary-flow system. In a primary-secondary system, the primary piping network is dedicated to circulating water through the boiler. The piping should be covered with insulation that minimizes heat losses with the environment. Secondary HWH Loop Piping Network The secondary HWH piping network is connected to the primary piping network to deliver hot water to the facility. The piping should be covered with insulation that minimizes heat losses into the environment. Terminal Units Terminal units provide heating to an end-user, where the heat source can be either steam or hot water. Typical terminal units for heating are fan-coil units, unit heaters, radiators, and convectors. The amount of hot water supplied to the terminal units is generally adjusted with a modulating valve controlled by a temperature sensor, which is typically not part of the HWH loop. Fan-coil Units A fan coil unit is a smaller, factory-assembled device that is used to circulate and condition air for cooling or heating. Unit Heaters A unit heater is a standalone device containing a fan that blows over a small heat exchanger to provide heat to a space. Radiators Radiators are a common terminal unit to distribute heat to space. By routing hot water through the radiator, the heat is transferred to the piping where it relies on radiation as well as free convection to warm a space. Convectors Convectors are similar to radiators in how energy is received, but rely almost exclusively on convection to distribute heat to a space. This leads to a cooler temperature to the touch, as well as a smaller terminal unit. Evaluation of Energy Consumption The primary energy consumption in a HWH loop is the electricity used to run the pump motors. The heat loss across the piping network contributes to the overall energy consumption for the entire HWH plant–in particular, the boiler system. Table 1 provides a summary of system component measurements and values needed to quantify the annual energy consumption and operating characteristics of a HWH loop system. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Component to be Measured Measurements Primary HWH loop pump electricity usage (kWh) - constant-speed system Average hourly primary HWH pump motors kWh Total operating time of the pump motors Constant-speed pump motor Spot measurements of true RMS power hourly measurement of motor runtime Primary HWH loop pump electricity usage (kWh) - variable-speed system Average hourly primary HWH pump motor kWh Total operating time for the pumps Outdoor air temperature as a proxy for heating load Variable-speed pump motor Hourly measurement of true RMS power hourly measurement of outdoor air temperature Secondary HWH loop pump electricity usage (kWh) - variable-speed system (if present) Average hourly primary HWH pump motor kWh Total operating time for the pumps Outdoor air temperature as a proxy for heating load Variable-speed pump motor Hourly measurement of true RMS power hourly measurement of outdoor air temperature Primary HWH loop water flow – constant speed system Average hourly water flow (GPM) through a pump Hourly measurement of water flow rate Terminal units – heating load delivered Average hourly Btu rejected from the hot water loop Hourly measurement of water flow rate Hourly measurement of supply and return water temperature Measurement Locations The measurement locations for a primary-flow and primary-secondary flow hot water loop system are shown in Figure 3. Figure 2. Hot water loop measurement locations (click on image to enlarge). Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 13. Hydronic Heating and Cooling. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 44. Centrifugal Pumps. I-P Edition.

Circulates hot water produced by a boiler to terminal units in the facility and then back to the boiler using with the help of hot water pumps and a piping …


Steam Condensate Recovery
General Overview The steam condensate recovery system collects condensate from the steam distribution system through steam traps and recovers waste heat. Before returning to the boiler, the condensate typically passes through a deaerator to remove unwanted oxygen. Since condensate is purified water at high temperatures, its reuse helps reduce fuel consumption and lowers water treatment costs for make-up water. Components Condensate recovery systems are typically equipped with pumps, pipe networks, and a heat exchanger. Condensate is passed into a receiver tank. The components of a condensate recovery system are shown in Figure 1. Figure 1. Condensate recovery system diagram (click on image to enlarge). Condensate Pumps Condensate pumps are responsible for moving condensate from the receiver tank(s) back to the boiler system. In some cases, the receiver tank, pump, and float controls are packaged together. An appropriately-sized pump is crucial to avoiding condensate buildup, which could create problems with terminal units. Learn More Pipe Networks The pipe network of a condensate recovery system transports flash steam and condensate. Designs should consider differential of pressure between different lines. It is usually covered with insulation material to minimize heat losses into the environment. Evaluation of Energy Consumption The primary purpose of the condensate recovery system on the steam plant is to minimize heat losses and manage condensate that could otherwise be damaging to the steam plant. Generally, the energy related to the condensate system is not quantified; instead, the energy consumption of the overall low-pressure steam plant is quantified. For more information, see Steam Plant. Table 1. Key values, components and measurements to evaluate energy consumption. Plant Quantification Values to be Quantified Energy Consuming Component Steam boiler plant fuel consumption (Btu) Average hourly fuel consumption (Btu/h) Boiler Steam plant electricity consumption (kWh) Average hourly burner fan motor (kWh) Total operating hours of burner fan motor Average hourly condensate pump motor kWh Average hourly feedwater pump motor (kWh) Total operating time for pump motors Burner fan motor Condensate pump motor Feedwater pump motor Further Reading ASHRAE (2014). “ASHRAE Guideline 14-2014 – Measurement of Energy, Demand, and Water Savings.” Annex A. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 11. STEAM SYSTEMS. I-P Edition. U.S. Department of Energy. (2014). “A Sourcebook for Industry – Energy,” https://www.energy.gov/sites/prod/files/2014/05/f15/steamsourcebook.pdf

The steam condensate recovery system is responsible for collecting condensate from the steam distribution system through steam traps.


Steam Distribution
General Overview A steam distribution system is responsible for distributing the steam produced by a steam boiler system as well as handling any condensate generated in the process. Common configurations for steam distribution systems include one-pipe and two-pipe systems. The main focus here is on two-pipe systems, as they are common in larger facilities. In a two-pipe system, the condensate is handled by a dedicated return line and is kept separate from any steam. The condensate return line can be treated as its own system and is discussed in a separate protocol and procedure document. Components Figure 1. Steam distribution system diagram (click on image to enlarge). Steam Heater and Piping Network A steam heater acts as a heat reservoir for the distribution loops throughout the building. This reservoir allows for the boilers to run at a constant rate while the heating load of the building fluctuates. The steam piping network is equipped with valves, fittings, and connections to properly maintain the pressure differential in the system. It is covered with piping insulation that minimizes heat losses within the environment. Terminal Units Terminal units provide heating to an end-user, where the heat source can be either steam or hot water. Typical terminal units for heating are fan-coil units, unit heaters, radiators, and convectors. The amount of steam supplied to the terminal units is generally adjusted with a modulating valve controlled by a temperature sensor, which is not typically part of the steam distribution system. Fan-coil units A fan coil unit is a smaller, factory-assembled device that is used to circulate and condition air for cooling or heating. Unit heaters A unit heater is a standalone device containing a fan that blows over a small heat exchanger containing steam or some other heating source to provide heat to a space. Radiators Radiators are a common terminal unit used to distribute heat to a space. When routing steam through a radiator, the heat transfers to the piping, where it relies on radiation as well as free convection to warm a space. Convectors Convectors are similar to radiators in how energy is received, but rely almost exclusively on convection to distribute heat to a space. This leads to a cooler temperature to the touch, as well as a smaller terminal unit. Heat Exchanger Steam distribution systems sometimes include steam-to-water heat exchangers that transfer heat to a heating hot water loop or a domestic hot water system. Converters and heated storage tanks can also be classified as steam-to-water heat exchangers. Steam Traps Steam traps separate the condensate water from the steam distribution system, ensuring proper distribution and system efficiency. Steam traps can be mechanical or thermostatic. Mechanical traps rely on the density difference between condensate and steam. Common mechanical traps include the float traps and bucket traps, which both rely on the buoyancy effect. Thermostatic traps rely on the temperature difference between the condensate and steam. Common thermostatic traps include bellows or bimetallic elements, which open and close a discharge port in response to temperature. Vacuum Pump If present, a vacuum pump is located after the steam traps and reduces pressure in the piping network. This increases the rate at which the piping network and terminal units fill with steam and may allow the boiler to operate at a lower temperature, as placing the system under a vacuum lowers the boiling point of water. Learn More Evaluation of Energy Consumption The steam distribution system distributes heat energy, with losses to the non-conditioned environment along the way, but does not inherently consume energy. The exceptions are systems with a vacuum pump, which consumes electricity. Generally, the energy related to the steam distribution system is not quantified; instead the energy consumption of the overall low pressure steam plant is quantified. For more information see Steam Plant. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements Vacuum pump electricity usage (kWh) - if present Average hourly pump motor (kWh) Total operating time for the pumps Pump Motor Spot measurements of true RMS power Hours of operation of the pump motor Hourly measurement of outdoor air temperature Further Reading ASHRAE (2014). “ASHRAE Guideline 14-2014 – Measurement of Energy, Demand, and Water Savings.” Annex A. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 11. STEAM SYSTEMS. I-P Edition.

Responsible for distributing the steam produced by a steam boiler system as well as handling any condensate generated in the process.


Air Handling

Air-to-air Energy Recovery
General Overview An air-to-air energy recovery (AAER) system consists of a heat exchanger component, air ducts, and any associated device for its operation. AAER systems extract sensible (and sometimes latent) energy from a previously conditioned “outgoing” airstream and use that energy to pre-condition a separate “incoming” air stream. Typically, the outgoing airstream is drawn from occupied spaces in a building, and the incoming air is from the outdoors. The two airstreams must be at different temperatures for sensible heat transfer and different moisture contents for latent transfer. For a more detailed description of the system, refer to the ASHRAE HVAC Systems and Equipment Handbook (2020), Chapter 26. Components Figure 1 shows the main components associated with a fixed plate heat exchanger including the heat exchanger, air ducts and fan and motors. In a AAER with a rotary wheel heat exchanger there is also a motor used to power the rotary wheel. Figure 1. Air-to-air heat recovery system with fixed plate each exchanger (click on image to enlarge). Heat Exchangers The heat exchanger transfers energy between the two airstreams. The most common air-to-air heat exchangers as defined by ASHRAE are listed below. The energy transfer effectiveness in a heat exchanger relies on its configuration, the material properties of the energy exchange surface, and a design that maximizes the contact of the airstream with the heat exchange surface. Rotary Air-to-air Energy Exchanger A rotary wheel exchanger consists of a belt driven wheel that is built up by a matrix of foils. The wheel rotates and moves through both the incoming and outgoing air streams, effectively transferring heat between them. The pressure drop and efficiency of the exchanger depends on the wheel diameter and density of corrugation. Most rotary wheel exchangers transfer both sensible heat and latent energy. Figure 3 shows an example of a rotary wheel heat exchanger. Learn More Figure 3. Rotary air-to-air energy exchangers (click on image to enlarge). Fixed Plate Heat Exchanger A fixed plate heat exchanger functions by providing neighboring channels, separated by plates, for airstreams to pass through and transfer energy. The channel separation determines both the pressure drop and efficiency of the heat exchanger. Many fixed plate heat exchangers only transfer sensible heat, but they can be designed to transfer latent energy (i.e., moisture) as well, depending on the material used. Coil Energy Recovery (Runaround) Loop Coil energy recovery loops, also known as runaround loops, make use of a heat exchanging coil that connects the incoming and outgoing exhaust air streams. The loop contains a heat transfer fluid (i.e., water, glycol) and a pump to move the liquid between both streams. Coil energy recovery loops transfer sensible heat only. Heat Pipe Heat Exchanger Heat pipe heat exchangers operate by using a working fluid that changes phases to transfer heat. As shown in Figure 5, one side of the heat pipe is placed in the exhaust stream and the other is placed in the supply stream, causing one side of the pipe to undergo evaporation and the other side to undergo condensation, effectively transferring heat. Heat pipe heat exchangers transfer sensible heat only. note See Chapter 26 of the ASHRAE Handbook on Heating, Ventilating, and Air-Conditioning Systems and Equipment for discussion of these and other heat exchangers. Air Duct Ducts transport air to and from served zones, heat recovery units and air handling units. Duct systems often include dampers and turning vanes to control flow volume and reduce pressure losses, which can directly impact system efficiency. Rotary Air-to-Air Energy Exchanger Motor Most heat exchangers are passive devices and rely on the fan and motor components in other systems to move air through them. In the case of a rotary air-to-air energy exchanger, the heat exchange medium is rotated through the airstreams, where the exchanger medium picks up or releases heat and possibly moisture. A small constant or variable speed motor is needed to rotate the heat exchanger. Evaluation of Energy Consumption The primary effect of air-to-air energy recovery is to reduce fuel and/or electricity consumption by capturing waste heat. A heat exchanger will increase the static pressure in the air streams which requires additional fan motor energy. In a rotary wheel configuration, the motor that drives the wheel should be considered when estimating the energy impact. The impact of the AAER on both temperature and humidity must be considered to gain a full picture of its energy impact. Table 1 provides a summary of the components to measure to arrive at values needed to quantify the annual energy consumption of a heat recovery system. Table 1. Key values and measurements to evaluate heat transfer. System Quantification Values to be Quantified Energy Saving Component Measurements Heat Recovered Average hourly Btu recovered Heat Exchanger Average hourly incoming (outdoor) airflow (CFM) Average hourly incoming air stream temperatures on each side of heat exchanger Average hourly humidity on each side of heat exchanger Heat recovery system electricity consumption (kWh) (if applicable) Average hourly fan motor (and rotary wheel motor if applicable) kWh Fan motor (and rotary wheel motor if applicable) Hourly measurement of true RMS power Measurement Locations The measurement locations for a heat recovery system are shown in Figure 7. Figure 7. Air-to-air recovery measurement locations (click on image to enlarge). Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 1. HVAC SYSTEM ANALYSIS AND SELECTION. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 26. AIR-TO-AIR ENERGY RECOVERY EQUIPMENT. I-P Edition. CenterPoint Energy (2022). “Runaround Loops.” Energy Recovery Systems. https://www.centerpointenergy.com/en-us/Services/Pages/Runaround-loops-MN.aspx?sa=MN&au=bus Heatex (2022). “Heat Exchanger Basics.” https://www.heatex.com/knowledge/heat-exchanger-basics. National Renewable Energy Laboratory (2003). “Laboratories for the 21st Century: Best Practices” https://www.nrel.gov/docs/fy04osti/34349.pdf Paulina Kanaś (2019).” The influence of geometrical parameters on heat and mass transfer processes in rotary heat exchangers.” SN Applied Sciences.

Uses heat exchangers to transfer heat from the outgoing air stream (return air) to the incoming air stream (outdoor air).


Constant-speed, Constant-volume Air Handling Unit
General Overview A constant-speed, constant-volume (CSCV) air handling unit provides conditioning to mixed air (a combination of outdoor and return air), discharges the conditioned air into zones, returns air from the zones, and exhausts air to the outdoors. The CSCV system has a constant volumetric airflow rate. The discharge air is conditioned by heating or cooling heat exchangers that are supplied from the heating and cooling loop systems (e.g., steam loop, hot water heating loop, chilled water loop). For a more detailed description of the system, refer to the ASHRAE HVAC Systems and Equipment Handbook (2020), Section 4. Components The major components of a CSCV system include fans and motors, heat exchanger coils, and dampers. Figure 1 illustrates the components of the CSCV system. In general, mixed air is conditioned by heating or cooling coils that receive energy from the heating or cooling loops, with mechanical valves regulating the energy introduced to the coils. Supply and return fans circulate air to and from the served zones, while dampers control airflow. Figure 1. Constant-volume, Constant-speed AHU components (click on image to enlarge). Fan and Motor The fan motors provide pressure in the system to move air through the duct work. Typically, fans are placed on the return and supply side of the unit to maintain proper airflow. The air is either blown or pulled through filters and heat exchanger coils, depending on the configuration. In a CSCV system, the motors operate in an on/off manner. Learn More Heat Exchanger (Heating/Cooling Coils) The heat exchanger includes a set of heating and cooling coils that provide heating or cooling to the air before it is discharged from the AHU. Mechanical valves regulate the amount of energy introduced from the loop to the heat exchangers, which control the energy supplied to the discharge air. Learn More Dampers Dampers are generally interlocked and are controlled to supply appropriate quantities of fresh air to the AHU and exhaust air to the outdoors. The dampers can also be set to maintain desired building pressures. Evaluation of Energy Consumption The primary energy consumption of a CSCV is the electricity that is used to run the fan and motor and the energy transferred to the air for heating and cooling. Table 1 provides a summary of measurements needed to quantify the annual consumption and operating characteristics of the CSCV pump and motor. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements Air handling unit electricity usage (kWh) Average hourly fan motor (kWh) Fan motors Spot measurements of true RMS power Heating/cooling load on building (Btu/h) Average hourly thermal load of heating/cooling coils (Btuh) Heating/cooling coils System air measurement Air flow rate measurement Measurement Locations The measurement locations for a CSCV AHU are shown in Figure 2. Figure 2. CSCV AHU measurement locations (click on image to enlarge). Further Reading ASHRAE (2014). “ASHRAE Guideline 14-2014 – Measurement of Energy, Demand, and Water Savings.” Annex A. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 1. HVAC SYSTEM ANALYSIS AND SELECTION. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 4. AIR HANDLING AND DISTRIBUTION. I-P Edition.

Provides conditioned air to one or more spaces. The supply and return fans operate at constant-speed.


Variable-speed, Variable-volume Air Handling Unit
General Overview A variable-speed, variable-volume (VSVV) air handling system conditions mixed air (a combination of outdoor and return air), discharges the conditioned air into zones, returns air from the zones, and exhausts air to the outdoors. The served zones are typically equipped with variable-air volume boxes (VAV), which allow for zone-specific control of supply airflow. The overall airflow of the air handling unit (AHU) is modulated using variable-frequency drives (VFDs) on the supply and return fan motors based on how much air the VAV boxes require. For a more detailed description of the system, refer to the ASHRAE HVAC Systems and Equipment Handbook (2020), Section 4. Components The major components of a VSVV system are the fans and motors, motor VFDs, heat exchanger coils, dampers, and VAV boxes. The components associated with the VSVV are shown in Figure 1. In general, the mixed air is conditioned by heating or cooling coils that use the output of the heating or cooling loops, using mechanical valves to regulate the amount of energy introduced to the coils. Supply and return fans with VFDs and dampers control airflows inside the main AHU. Dampers in the VAV boxes control zone airflows. Occasionally, a VAV box is equipped with a supply fan. Figure 1. Variable-speed, Variable-volume Components (click on image to enlarge). AHU Fan Motors and Variable-frequency Drives The fan motors with VFDs provide pressure in the system to move air through the duct work. Typically, fans are placed on the return and supply side of the unit to maintain proper airflow. The air is blown through filters and heat exchanger coils to be conditioned. Fan speeds are varied based on the need for conditioned or ventilation air in the zones served. Learn More Heat Exchanger (Heating/Cooling Coils) The heat exchanger includes a set of heating and cooling coils, which provide heating or cooling to the air before it is discharged from the AHU. Mechanical valves regulate the amount of energy introduced from the loop to the heat exchangers that control the energy supplied to the discharge air. Learn More Dampers Dampers are generally interlocked and are controlled to supply appropriate quantities of fresh air to the AHU and exhaust air to the outdoors. The dampers can also be set to maintain desired building pressures. Variable-air Volume (VAV) Box A device that includes a damper to control zone specific airflow, a VAV box is sometimes equipped with a fan based on the overall system design. VAV boxes are typically equipped with reheat coils to prevent over-cooling of zones with low cooling loads and high ventilation air requirements. Evaluation of Energy Consumption The energy consumption of a VSVV air handling system is electricity for the fan motors and VFD, thermal energy for heating or cooling across the VSVV AHU heat exchanger, and the electricity or thermal energy used at the VAV reheat boxes. Table 1 provides a summary of the components and operating characteristics of a variable speed system. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements AHU power consumption Hourly fan motor kWh Fan motors and associated VFDs Hourly true RMS energy Outdoor air temperature (if VFD is temperature dependent) AHU heating/cooling load on building Hourly thermal load of heating/cooling coils (Btuh) Heating/cooling coils Airflow rate and temperature difference across the heating/cooling coil VAV box consumption (if applicable) Hourly reheat kWh Electric reheat coil (if present) Hourly true RMS energy VAV box consumption (if applicable) Hourly thermal load reheat coils (Btuh) Hot water or steam reheat coil Airflow rate and temperature difference across the heating/cooling coil VAV box consumption (if applicable) Hourly fan motor kWh Fan motor (if present) Hourly true RMS energy Measurement Locations The measurement locations for a VSVV air handling system are schematically shown in Figure 2. Figure 2. VSVV AHU measurement locations (click on image to enlarge). Further Reading ASHRAE (2014). “ASHRAE Guideline 14-2014 – Measurement of Energy, Demand, and Water Savings.” Annex A. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 1. HVAC SYSTEM ANALYSIS AND SELECTION. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 4. AIR HANDLING AND DISTRIBUTION. I-P Edition. Li, Y. (2015). “Variable Frequency Drive Applications in HVAC Systems”, in M. Chomat (ed.), New Applications of Electric Drives, IntechOpen, London. 10.5772/61782.

Provides conditioned air to one or more spaces. The supply and return fans operate at variable speeds.


Lighting

Lighting Fixture
General Overview A lighting fixture system produces light to illuminate a specific area or areas. Current is received from the electrical distribution system. The group of fixtures that comprise a lighting system can be configured in many ways with different lamp types. A building can have one or more lighting fixture systems. The main components of an individual lighting fixture are lamps, ballasts, and controls. Components Figure 1 shows the main components associated with a lighting fixture system. Figure 1. Lighting Fixture System, fixtures are of a single type in this room (click on image to enlarge). Figure 2: Lighting fixture system of the building consists of many different types of fixtures (i.e., fixtures that consume different amounts of energy) (click on image to enlarge). Lamps Lamps refer to the enclosure of a lighting source. The most common types of lamps are incandescent, fluorescent, high intensity discharge (HID), induction, and LED. Many types of lamps can be used within a facility. All lamps convert electrical energy to light, with some energy converted to heat as well. The efficiency of the lamp in minimizing losses to heat is the biggest determining factor in the energy efficiency of the lighting fixture system. In addition to electrical efficiency, different lamps produce different color spectrums, which are better suited to different applications. For example, an office typically requires white light with a “cool” tone. However, warehouse lighting may be more yellow or orange without impacting its function. Ballast A ballast is an electrical device that regulates the voltage and current supplied to a lamp. While incandescent lamps do not require ballasts, all other lamp types need them to ensure stable operation. Ballasts come in various types, each designed for specific lamps, and some fixture systems have ballasts integrated into the lamp component. The regulation of voltage and current results in some energy loss as heat, and ballast efficiency varies depending on how well these losses are minimized. Housing The fixture housing is the physical receptacle that houses the lamp and ballast. The housing may include shutters or diffusers that direct and disperse the light. Some housing is designed to disperse the heat generated by the lamp and ballast more effectively, which increases the life of the fixture. Controls Controls regulate the operation of the light fixtures, such as when they are turned on and off, and their brightness. Controls can be manual or automatic. Manual controls are wall switches within a space and circuit breakers at the electrical panelboard and switchgear. Automatic controls use sensors and/or timers to determine when and how to regulate the fixture operation. The two most common sensors used in lighting controls are motion sensors, which approximate when a space is occupied or vacant, and daylight sensors, which determine when natural sources are providing enough light for the fixtures to be turned off or dimmed. Some automatic controls have their own control panel that is wired directly to the circuits at the lighting panelboards or the ballasts of individual fixtures. Evaluation of Energy Consumption Electricity is the energy source for all modern lighting systems. Table 1 provides a summary of system component measurements and values needed to quantify the hourly energy consumption and operating characteristics of a lighting fixture system. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements Lighting fixture system electricity usage (kWh) Average hourly panelboard or switchgear (kWh) Total operating time for the light fixtures Light fixtures and automatic controls (if applicable). Hourly measurement of electricity supplied to the light fixture system from the panelboard or switchgear Total operating hours of the light fixtures Illuminance delivered Lumens Light fixtures Lumens incident on surfaces that require illumination (workstations, walkways, shelving, etc.) Light quality Color rendering index Lamps Color rendering index measurement (speciality equipment) Measurement Locations Electrical measurements of lighting fixtures must be taken at the electrical distribution components. Further details can be found in the Electrical Distribution page. An auditor can develop a sampling plan and use a light on/off logger to measure the schedule of a single fixture. The single light fixture should be representative of the other fixtures in the room to assume the same schedule for all fixtures. Then, a direct power draw measurement at the electrical panelboard that serves the fixture is needed. The power draw data and the schedule data obtained from the light on/off logger allows an auditor to estimate energy consumption. Figure 3. Lighting fixture measurement locations (click on image to enlarge). Figure 4: Electrical measurement necessary to estimate energy. Measurement is taken at the electrical panelboard that serves the lighting fixtures (click on image to enlarge). Calculation Methodology Further Reading California Energy Commission (June 2015). 2016 Building Energy Efficiency Standard for Residential and Nonresidential Buildings, Title 24, Part 6, Chapter 6: Residential Compliance Manual, CA: California.

A lighting fixture system uses ballasts to regulate electricity to the lamps, which produce light to illuminate areas in the facility.


Electrical Distribution

Electrical Distribution
General Overview An electrical distribution system is made up of switchgear and panelboards connected by wires. Switchgear is used to disaggregate the power coming from the utility grid to serve various aggregate loads in a facility, such as lights, motors, receptacle circuits, or miscellaneous equipment. A panelboard is used as the final disconnect and protection point for individual circuits in a space. A lighting panelboard is connected to the light fixture system in one or more spaces, typically on a single floor of a facility, or the outdoor light fixture system. Panelboards may either be dedicated to the lighting system or “mixed”, serving both lighting loads and other circuits. Components Figure 1 shows the main components associated with the electrical distribution system: switchgear and panelboard. Figure 1. Diagram of an electrial distribution system (click on image to enlarge). Switchgear Switchgear is an assembly that contains circuit breakers, fuses, and other accessories to interrupt current flow and protect electrical equipment and occupants. The electricity delivered by a utility company is passed through a step-down transformer and then to a switchgear as the first layer of protection in a facility. Then, electricity is distributed among other assemblies, such as a secondary switchgear or panelboards. The configuration of primary and secondary switchgears is dependent on the facility. Not all facilities have secondary switchgear. Dedicated Panelboard A dedicated electrical panelboard supplies electricity only to the light fixture system. Figure 2 shows a dedicated panelboard without a panel cover to show how the electrical wiring is distributed. The electricity from the primary or secondary switchgear enters from the top (or bottom) of the panelboard, and then splits across all of the branch circuits. Figure 2. Dedicated panelboard system (click on image to enlarge). Figure 3 is an example of a schedule of circuits on a dedicated panelboard. The schedule typically describes the type of load (e.g., lights) and the space that is served by the breaker. There is no standard naming convention for circuits. Figure 3. Example of a dedicated panelboard schedule (click on image to enlarge). Mixed Panelboard A Mixed electrical panelboard supplies electricity to the lighting fixture system and other loads (typically receptacle circuits). Mixed panelboards typically exist in small or older facilities. The electricity from the primary or secondary switchgear enters from the top or bottom of the panelboard and then splits across all of the branch circuits. The interior of a mixed panelboard looks similar to Figure 2, but the panel schedule highlights a collection of different loads as shown in Figure 4. Figure 4: Example of a mixed panelboard schedule (click on image to enlarge).1 Evaluation of Energy Consumption The electrical distribution system does not consume electricity, but it can be a useful point by which to measure the electrical energy associated with the Lighting Plant. Table 1. Key values, components and measurements to evaluate energy consumption. System Quantification Values to be Quantified Energy Consuming Component Measurements Lighting fixture system electricity consumption (kWh) Average hourly panelboard or switchgear kWh Total operating time for the light fixtures Light fixtures and automatic controls (if applicable). Average hourly electricity supplied to the light fixture system from the switchgear or panelboard Total operating hours of the light fixtures Measurement Locations Figures 5 and 6 show typical measurement locations in an electrical distribution system. Figure 5: Three-phase power measurement using a Dent EliteProXC Power Logger to capture to total power draw of all fixtures served by the panelboard (click on image to enlarge). Figure 6: Current measurement using current transformers and a data logger to collect measurement data. In this figure, measurements are taken at the circuit breaker level to capture specific fixtures. Voltage and power factor measurements are taken with a power meter (click on image to enlarge). Measurement locations in the electrical distribution system are at the conductors in the panelboard or switchgear. To measure a lighting plant, the best practice is to capture as much of the lighting plant in a single measurement as possible. Measuring at switchgear may be appropriate if all lighting panelboards are dedicated and connected to it, but only the distribution line that supplies electricity to lighting should be measured. Alternatively, a sample of panelboards and/or circuits can be measured, but a sampling plan must be considered. For more information on sampling, please refer to Bonneville Power Administration’s guide on sampling. Calculation Methodology Further Reading Consulting-Specifying Engineer (20). “Back to Basics: Switchgear, Transformers and UPSs.”. https://www.csemag.com/articles/back-to-basics-switchgear-transformers-and-upss/; accessed May 24, 2022. Bonneville Power Administration (July 2018). “Sampling for M&V: Reference Guide.” EE Richman (February 2016). PNNL-SA-25222. “Measurement and Verification of Energy Savings and Performance from Advantage Lighting Controls” Richland, WA: Pacific Northwest National Laboratory. Footnotes Blue represents lighting fixtures, red represents others electrical loads. ↩︎

This system regulates the amount of electricity supplied to different areas of the facility. This is the primary measurement location of lighting fixture …


All Components

Components are the individual parts that constitute a system within a facility and serve as the primary energy-consuming equipment. Tracking these components enables detailed monitoring and maintenance, helping to identify issues such as equipment malfunctions or inefficiencies. More By understanding the performance of each component, building operators can optimize energy usage, reduce waste, and lower the overall costs associated with operating the plant and its systems. Read more about each component below. Less

Heat Exchangers

Air-to-air Heat Exchanger
General Overview Air-to-air heat exchangers transfer energy between two airstreams that must be at different temperatures for sensible heat transfer and different moisture contents for latent heat transfer. In a building, an air-to-air heat exchanger can be used to recover latent or sensible heat during the cooling or heating season. Recovering energy from the exhaust stream lessens the energy load on the air handling plant. Typical air-to-air heat exchangers include fixed plate heat exchangers and rotary wheel heat exchangers, with the former typically only recovering sensible heat. Table 1. Plants and systems applicable to air-to-air heat exchanger. Plant System Component Controlling Variable Air Handling Plant AHU with Heat Recovery Unit Fixed plate heat exchanger Outdoor air temperature (F) Air Handling Plant AHU with Heat Recovery Unit Rotary wheel heat exchanger Outdoor air temperature (F) Air Handling Plant A dedicated outdoor air system (DOAS) Fixed plate or rotary wheel heat exchanger Outdoor air temperature (F) -- Table 2. Key values and measurements to evaluate heat transfer. Component Quantification Values to be Quantified Measurement  Energy recovered by the heat exchanger Hourly Btu/h transferred to the outdoor air entering the system Hourly air flow rate (CFM) of incoming air Hourly air temperature (F) of incoming air on both sides of the heat exchanger  Hourly relative humidity of the incoming air on both sides of the heat exchanger (only for latent heat recovery systems) Heat recovery system electricity consumption (if applicable) Average hourly motor kWh (for rotary wheel heat exchangers) Hourly true RMS power of the motor that drives the rotary fan (kW) -- Measurement Strategy The measurement strategy for an air-to-air heat exchanger is to measure the heat transfer (Btu/h) from airstream to airstream within the heat exchanger, as well as any energy consuming components associated with the heat exchanger, such as the energy wheel motor. Figure 1 shows the measurement locations in a fixed plate heat exchanger. Figure 1. Fixed-plate heat exchanger measurement locations (click on image to enlarge). Figure 2 shows the measurement locations in a rotary wheel heat exchanger. Figure 2. Rotary wheel heat exchanger measurement locations (click on image to enlarge). What to Measure Measurements needed to quantify the annual energy consumption and operating characteristics of an air-to-air heat exchanger: True RMS Power Measurement Use this technique to measure power draw (true RMS power) at one-hour intervals using a data logger. Outdoor Air Temperature Measurement Use this technique to measure outdoor air temperature (OAT) at one-hour intervals with a data logger. System Air Temperature Measurement Use this technique to measure the air temperature of various air streams in an air handling unit at one-hour intervals with data loggers. Relative Humidity Measurement Use this technique to measure relative humidity (RH %) of various air streams in an air handling unit at one-hour intervals with data loggers. Table 3. Measurement equipment. Equipment Description Measurement (Units) DENT ELITEproXC Portable Power Data Logger (EXCUNC) DENT 16” RoCoil Flexible Rope Current Transformers (CT-R16-A4-U) Provides a measurement of true RMS power from voltage and current inputs and records long-term power (kW) and energy (kWh) measurements. Requires ELOG19 software and a USB connection cable for programming and downloading data files. True RMS Power (kW) Onset HOBO MX1101 logger Measures and records temperature and relative humidity. Using bluetooth technology you can transmit your data wirelessly to your mobile device using the HOBOconnect app. Stores 84,000 measurements. System Air Temperature (F) Relative Humidity (%) Onset HOBO Temperature/Relative Humidity Weatherproof Data Logger (MX2301) Records outdoor air temperature and relative humidity using internal sensors. Requires HOBOware software and a USB connection cable for programming and downloading data files. Outdoor Air Temperature (F) Relative Humidity (%) Hot Wire Anemometer (Blue) (TSI 9545) Simultaneously measures and logs data for several ventilation parameters using a single probe with multiple sensors. It measures velocity, temperature, and relative humidity, and calculates flow, wet bulb, and dew point temperature. System Air Temperature (F) Relative Humidity (%) -- Energy Consumption Quantification The general methodology for quantifying the energy impact of an air-to-air heat exchanger is to determine the temperature differential on the supply side of the heat exchanger and the supply airflow. If latent energy is also transferred, this is determined by the humidity differential across the heat exchanger. The supply flow rate can be measured or assumed, depending on available resources. These energy transfer values can be regressed against a controlling variable (such as outdoor air temperature) to develop a regression model. Depending on the variability of operations, daily or weekly models may be developed to better characterize the component. How to Quantify The following downloadable file(s) can be used to calculate energy consumption based on the measurements taken for this component: Air to Air Heat Transfer Calculator Uses measured air flow rate, fan power and runtime, and temperature to calculate total annual heat transfer and energy savings for an ERV. For more details about the methodology behind the calculator above see the Air-to-air Heat Exchanger Heat Transfer calculation. Further Reading ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 1. HVAC SYSTEM ANALYSIS AND SELECTION. I-P Edition. ASHRAE (2020). “ASHRAE Handbook: HVAC Systems and Equipment,” Chapter 26. AIR-TO-AIR ENERGY RECOVERY EQUIPMENT. I-P Edition. CenterPoint Energy (2022). “Runaround Loops.” Energy Recovery Systems. https://www.centerpointenergy.com/en-us/Services/Pages/Runaround-loops-MN.aspx?sa=MN&au=bus Heatex (2022). “Heat Exchanger Basics.” https://www.heatex.com/knowledge/heat-exchanger-basics.

The rotary wheel achieves heat transfer using temperature difference between two airstreams without direct contact of these airstreams.


Liquid-to-liquid Heat Exchanger
General Overview A liquid-to-liquid heat exchanger transfers heat between two liquids using a temperature difference without direct contact between them. In a building, this type of heat exchanger can be installed in condensate cooling, vent condensing, boiler blowdown, and waterside economizer (free cooling), and in refrigeration applications such as evaporators and condensers. Typical liquid-to-liquid heat exchangers are plate-and-frame heat exchangers and tube heat exchangers. Table 1 shows the plant and system configurations that may contain a liquid-to-liquid heat exchanger. Table 1. Plants and systems containing liquid-to-liquid heat exchangers. Plant System Component Controlling Variable Water-cooled Chilled Water Plant Waterside Economizer Liquid-to-liquid heat exchanger Outdoor air temperature (F) Steam Plant Blowdown Tank Heat recovery system Liquid-to-liquid heat exchanger Blowdown water temperature (F) Service Hot Water Plant Service Hot Water Tank Liquid-to-liquid heat exchanger Schedule and occupancy Evaluation of Heat Transfer In a liquid-to-liquid heat exchanger, heat is transferred from a liquid with excess heat (waste heat stream) to a liquid where the recovered heat benefits the process (supply stream). This is the principal energy phenomenon that reduces the overall energy usage of the entire plant or system where the heat exchanger is installed. A pump and motor may be required to circulate the liquids in the waste heat and supply streams. Table 2 provides a summary of measurements needed to quantify the annual energy transfer and operating characteristics of a liquid-to-liquid heat exchanger. Table 2. Key values and measurements to evaluate heat transfer. Component Quantification Values to be Quantified Measurement  Heat transferred by the heat exchanger to the supply stream Average hourly Btu/h transferred Average hourly flow rate of the supply stream (GPM) Temperature of supply stream entering and leaving the heat exchange (F)  Heat recovery system electricity consumption (if applicable), non-weather dependent system Average hourly pump motor kWh (if needed) Operating schedule Hourly true RMS power (kWh) Heat recovery system electricity consumption (if applicable), weather dependent system Average hourly pump motor kWh (if needed) Average hourly outdoor air temperature (OAT) Hourly true RMS power (kW) Outdoor air temperature (F) Measurement Strategy The measurement strategy for a liquid-to-liquid heat exchanger involves measuring the supply stream flow through the heat exchanger and the temperatures at the supply stream inlet and outlet. If a pump is used in the system, the flow rate can be measured at the supply stream pump. Measurement locations are generically represented in Figure 1. Figure 1. Liquid-to-liquid heat exchanger measurement locations (click on image to enlarge). Measurement Equipment Table 3 provides the equipment required to carry out the measurements of this component. Table 3. Measurement equipment. Equipment Description Measurement (Units) Ultrasonic Flow Meter DXNP (DXNP-ABS-NN) Designed for systems engineers to quickly troubleshoot problems and verify performance during system commissioning and diagnostics. Allows measurement of flows throughout the plumbing infrastructure without intrusion. Water Flow Rate (GPM) DENT ELITEproXC Portable Power Data Logger (EXCUNC) DENT 16” RoCoil Flexible Rope Current Transformers (CT-R16-A4-U) Provides a measurement of true RMS power from voltage and current inputs and records long-term power (kW) and energy (kWh) measurements. Requires ELOG19 software and a USB connection cable for programming and downloading data files. True RMS Power (kW) 4-Channel Analog Data Logger (UX120-006M) Thermocouple Sensor (TC6-T) An analog logger that supports up to four external sensors allowing you to measure temperature, current, voltage, air flow, pressure and more in one single logger. HOBOware Pro or HOBOware free software is required for logger operation. Pipe Surface Water Temperature Calculation Methodology The general methodology for quantifying the useful energy supplied by a liquid-to-liquid heat exchanger is determined by the temperature differential and flow rate of the supply stream. These values are multiplied by the heat capacity and density of the liquid (e.g., water, water-glycol mix) to find the energy flow rate. The energy flow rate can be regressed against a controlling variable (such as outdoor air, pump runtime or flow rate) to develop a regression model. Depending on operational variability, daily or weekly models may be developed to better characterize the component. Click the button below to go to the calculators for this component. Further Reading Apogee Interactive (2022). “Free Cooling.” Commercial Library. https://c03.apogee.net/mvc/home/hes/land/el?utilityname=union-power&spc=cel&id=1094; accessed February 4, 2021. ASHRAE (2019). ASHRAE Handbook: HVAC Applications. Chapter 48. DESIGN AND APPLICATION OF CONTROLS. I-P Edition. ASHRAE (2020). ASHRAE Handbook: HVAC Systems and Equipment. Chapter 40. COOLING TOWERS. I-P Edition. Carrier (2016). “How to Model a Waterside Economizer Application.” Carrier Engineering Newsletter, Vol. 4, Issue 1. Gordon, J.M.; Ng, K.C. (2001). “Cool Thermodynamics: The Engineering and Physics of Predictive, Diagnostic and Optimization Methods for Cooling Systems,” Cambridge: Cambridge International Science Pub; pp. 159-177. Trane (2008). “’Free’ Cooling Using Water Economizers.” Engineers Newsletter, Vol. 37-3. Also available at https://www.trane.com/Commercial/Uploads/PDF/11598/ News-%20Free%20Cooling%20using%20Water%20Economizers.pdf; accessed February 4, 2021. Trane (2010). CDS-PRM001-EN. TRACE 700 User’s Manual-Building Energy and Economic Analysis, Version 6.2; pp. 43-49. Also available at https://tranecds.custhelp.com/ci/fattach/get/55941/0/filename/FreeCooling%5B1%5D.pdf; accessed June 17, 2022. Taylor, S (2014). “How to Design & Control Waterside Economizers,” ASHRAE Journal, Vol. 56, No 6. American Society of Heating, Refrigerating and Air Conditioning Engineers; pp. 30-36. Trane (2016). “Waterside Economizers - Keeping the ‘Free’ In Free-Cooling.” Engineers Newsletter, Vol. 45-2. Also available at https://www.trane.com/content/dam/Trane/Commercial/global/products-systems/education-training/engineers-newsletters/waterside-design/ADM-APN058-EN_06012016.pdf; accessed February 4, 2021.

The fixed plate achieves heat transfer using temperature difference between two liquids without direct contact of these liquids.


Pump and Motor

Constant-speed, Constant-volume Pump and Motor
General Overview A constant-speed, constant-volume (CSCV) pump and motor operates at a single speed to circulate liquid (e.g., water, water, and glycol solution) through a piping network where the flow rate through the pump does not vary more than 5%. Centrifugal pumps are the most common type of pumps used. Table 1 shows the plant and system configurations that may contain a CSCV pump and motor that operate based on a regular schedule (e.g., same time of day, same days of week). Table 1. Plants and systems applicable to CSCV pumps and motors. Plant System Component Air-cooled chilled water plant Chilled water loop Primary chilled water pump Water-cooled chilled water plant Condenser water loop Condenser water pump Water-cooled chilled water plant Chilled water loop Primary chilled water pump Water-cooled chilled water plant Chilled water loop Secondary chilled water pump Water-cooled chilled water plant Waterside economizer Waterside economizer pump (if present) Hot water plant Hot water boiler Makeup water pump Hot water plant Hot water loop Building loop pump Steam plant Steam boiler Makeup water pump Steam plant Feedwater tank Feedwater pump Service water plant Service hot water loop Service hot water Recirculation pump Evaluation of Energy Consumption The primary energy source for a CSCV pump is the electricity used to run the pump motor. Table 2 provides a summary of measurements needed to quantify the annual energy consumption and operating characteristics of the CSCV pump and motor. Table 2. Key values and measurements to evaluate energy consumption. Component Quantification Values to be Quantified Measurement  Electricity usage of a CSCV pump motor Average hourly power input to the pump motor Average hourly operating time for the pump motor True RMS power of pump motor that drives the pump (kW) Pump motor runtime Measurement Strategy The measurement strategy for a CSCV pump and motor involves conducting a one-time measurement of the power draw and long-term measurements of the operational schedule of the motor. The approach assumes that the power draw stays constant throughout the measurement period. Because the motor runs at constant-speed and is under a constant load, it is either operating at full power (when on) or it is drawing no power (when off). A motor on/off data logger is used to record the operating schedule. The true RMS power is measured at the main feed to the constant-speed motor. Measurement locations are generically represented in Figure 1. Figure 1. CSCV pump and motor measurement locations (click on image to enlarge). Measurement Equipment Table 3 provides the equipment required to carry out the measurements of this component. Table 3. Measurement equipment. Equipment Description Measurement (Units) Onset HOBO Motor On/Off Data Logger (UX90-004) Records when a motor is on and off, as well as runtime. Requires HOBOware software and a USB connection cable for programming and downloading data files. Motor Runtime (minutes) Fluke 345 Power Quality Clamp Meter Multi-purpose electrical measurement tool used to take true RMS power readings over a short period of time. True RMS Power (kW) Calculation Methodology Click the button below to go to the calculators for this component. Pump Motor Energy Consumption Calculation Estimate the annual energy consumption of variable speed and constant speed pump motors. Further Reading Evans , P. (2017, Sept 26). How a Chiller, Cooling Tower and Air Handling Unit work together. Retrieved from The Engineering Mindset.com: https://theengineeringmindset.com/chiller-cooling-tower-air-handling-unit-work-together/ Evans, P. (2023, Jan 6). How Do Centrifugal Pumps Work. Retrieved from The Engineering Mindset.com: https://theengineeringmindset.com/how-do-centrifugal-pumps-work/

Operates at a single speed to circulate liquid (water or glycol solution) through a piping network.


Variable-speed, Variable-volume Pump and Motor
General Overview A variable-speed, variable-volume (VSVV) pump and motor circulate liquid (e.g., water or water and glycol solution) through a piping network where the flow rate fluctuates as required by the plant and systems they serve. Outdoor air temperature (OAT) is the independent variable that drives the pump speed since heating and cooling loads are generally affected by OAT. The pump motor is equipped with a variable frequency drive (VFD) that may be integrated in the pump and motor package or installed separately. Centrifugal pumps are the most common type of pumps used in buildings. Table 1 shows the plant and system configurations that may contain a VSVV pump and motor and the controlling variable. Table 1. Plants and systems containing variable-speed, variable-volume pumps Plant System Component Controlling Variable Air-cooled chilled water plant Chilled water loop Primary chilled water pump Outdoor air temperature (F) Water-cooled chilled water plant Condenser water loop Condenser water pump Outdoor air temperature (F) Water-cooled chilled water plant Chilled water loop Primary chilled water pump Outdoor air temperature (F) Water-cooled chilled water plant Chilled water loop Secondary chilled water pump Outdoor air temperature (F) Water-cooled chilled water plant Waterside economizer Waterside economizer pump (if present) Outdoor air temperature (F) Hot water plant Hot water boiler Makeup water pump Outdoor air tempearature (F) Hot water plant Hot water loop Building Loop Pump Outdoor air temperature (F) Steam plant Steam Boiler Makeup water pump Outdoor air temperature (F) Steam plant Feedwater Tank Feedwater pump Outdoor air temperature (F) Service water plant Service hot water loop Service hot water; recirculation pump Occupancy schedule: time of day, day of week. Evaluation of Energy Consumption The primary energy source of a VSVV pump is the electricity used to run the pump motor. Table 2 provides a summary of measurements needed to quantify the annual energy consumption and operating characteristics of the VSVV pump and motor. Table 2. Key values and measurements to evaluate energy consumption.1 Component Quantification Values to be Quantified Measurement Electricity input to a variable-speed, variable-volume pump motor Hourly power input to a VSVV pump motor at known speeds (e.g. 30%, 50%, 75%, 100%) Average hourly outdoor air temperature (OAT) Hourly true RMS power of pump motor that drives the pump (kW) Outdoor air temperature (F) Measurement Strategy The measurement strategy for a variable-speed, variable-volume pump and motor involves measuring power draw of the pump motor at various known speeds, developing a mathematical relationship between the power and speed, and then collecting hourly OAT. Measurement locations are generically represented in Figure 1. Figure 1. Variable-speed, Variable-volume pump and motor measurement locations (click on image to enlarge). Measurement Equipment Table 3 provides the equipment required to carry out the measurements of this component. Table 3. Measurement equipment. Equipment Description Measurement (Units) DENT ELITEproXC Portable Power Data Logger (EXCUNC) DENT 16” RoCoil Flexible Rope Current Transformers (CT-R16-A4-U) Provides a measurement of true RMS power from voltage and current inputs and records long-term power (kW) and energy (kWh) measurements. Requires ELOG19 software and a USB connection cable for programming and downloading data files. True RMS Power (kW) Onset HOBO Temperature/Relative Humidity Weatherproof Data Logger (MX2301) Records outdoor air temperature and relative humidity using internal sensors. Requires HOBOware software and a USB connection cable for programming and downloading data files. Outdoor Air Temperature (F) Calculation Methodology The general methodology for quantifying the energy consumption of a variable-speed, variable-volume (VSVV) pump motor is based on the true RMS power of the three-phase power supply, measured either at the motor’s main power panel or at the three-phase input to the VFD. These values are regressed against outdoor air temperature to develop a temperature-dependent regression model. Depending on operational variability, daily or weekly models may be created to better characterize the system. This model is then applied to climate normal year data to estimate the typical energy use of the VSVV pump. Click the button below to go to the calculators for this component. Pump Motor Energy Consumption Calculation Estimate the annual energy consumption of variable speed and constant speed pump motors. Further Reading ​​Chaurette, J. (2003). In PUMP SYSTEM ANALYSIS AND CENTRIFUGAL PUMP SIZING (5th ed.). Retrieved November 2019, from https://www.pumpfundamentals.com/download/book/chapter4.pdf Satterfield, Z. (2010). Fundamentals of Hydraulics: Pressure. Tech Brief, 9(4), pp. 1-4. Retrieved November 21, 2019, from https://www.nesc.wvu.edu/files/d/5c5a9fd1-0f8b-48c5-9063-b55d12651b91/fund-of-hydr-pressure.pdf Taylor, S. T. (2002, February). Primary-only vs. primary-secondary variable flow systems. ASHRAE Journal, 25-29 Trane. (2002). Variable-Primary-Flow Systems Revisited. Trane Engineers Newsletter, 31(4). Retrieved November 2019, from https://www.trane.com/content/dam/Trane/Commercial/global/products-systems/education-training/engineers-newsletters/waterside-design/adm_apn005_en.pdf Footnotes Option 1: Measure hourly true RMS power of pump and motor and measure hourly OAT; Option 2: Measure hourly pump and motor speed and hourly OAT ↩︎

Operates at different speeds with a variable frequency drive to circulate liquid (water or glycol solution) through a piping network.


Fan and Motor

Constant-speed, Constant-volume Fan and Motor
General Overview A constant-speed, constant-volume (CSCV) fan uses a power-driven rotating impeller to circulate air at a single speed. Fans can be either axial or centrifugal. Table 1 shows the plant and system configurations that may contain a CSCV fan and motor and the most common respective controlling variables. Table 1. Plants and systems containing constant-speed, constant-volume fans. Plant System Component Controlling Variable Air-cooled Chilled Water Plant Air-cooled Chiller Condenser Fan Outdoor air temperature (F) Water-cooled Chilled Water Plant Cooling Tower Cooling Tower Fan Wet-bulb temperature (F) Air Handling Unit AHUs AHU Supply Fan Motor schedule and/or Outdoor air temperature (F) Air Handling Unit AHUs AHU Return Fan Motor schedule and/or Outdoor air temperature (F) Hot Water Heating Domestic Hot Water Steam Boiler Burner fan Motor schedule and/or Outdoor air temperature (F) Evaluation of Energy Consumption The primary energy source for a CSCV fan is the electricity used to run the fan motor. Table 2 provides a summary of measurements needed to quantify the annual energy consumption and operating characteristics of the CSCV fan and motor. Table 2. Key values and measurements to evaluate energy consumption. Component Quantification Values to be Quantified Measurement Electricity usage of CSCV fan motor (kWh) Average hourly true RMS power of the motor True RMS power of motor that drives the fan (kW) Controlling variable, non-weather dependent Yearly operating schedule Fan motor runtime (hours) Controlling variable, weather dependent Average hourly outdoor air temperature (OAT) Outdoor air temperature (F) Measurement Strategy The measurement strategy for a CSCV fan and motor involves a one-time measurement of true RMS power and long-term monitoring of the motor’s operational schedule. This approach assumes that true RMS power remains constant throughout the measurement period. Since the motor runs at a constant speed and is assumed to be under a constant load, it either operates at full power when on or draws no power when off. A motor on/off data logger records the operating schedule. True RMS power is measured at the main feed to the constant-speed motor. Measurement locations are generically represented in Figure 1. If the fans are in a modular configuration (assuming they all run at the same speed), then only one fan needs to be measured, provided substantiating documentation from the building automation system (BAS) shows that all cells are operating equally at the same time. If fans are further staged, all fans should be measured. In some cases, the motor’s operational schedule is related to the facility’s heating or cooling load. OAT can serve as a proxy variable for this load and can be measured onsite or obtained from a nearby weather station. Figure 1. CSCV fan measurement locations (click on image to enlarge). Measurement Equipment Table 3 provides the equipment required to carry out the measurements of this component. Table 3. Measurement equipment. Equipment Description Measurement (Units) Onset HOBO Temperature/Relative Humidity Weatherproof Data Logger (MX2301) Records outdoor air temperature and relative humidity using internal sensors. Requires HOBOware software and a USB connection cable for programming and downloading data files. Outdoor Air Temperature (F) Relative Humidity (%) Onset HOBO Motor On/Off Data Logger (UX90-004) Records when a motor is on and off, as well as runtime. Requires HOBOware software and a USB connection cable for programming and downloading data files. Motor Runtime (minutes) Fluke 345 Power Quality Clamp Meter Multi-purpose electrical measurement tool used to take true RMS power readings over a short period of time. True RMS Power (kW) Onset HOBO 4-Channel Analog Data Logger (UX120-006M) Used in conjunction with the CTV series of sensors. Records measurements from up to four CTV sensors. Requires HOBOware software and a USB connection cable for programming and downloading data files. Electrical Current (Amps) Calculation Methodology The general methodology for quantifying the energy consumption of a CSCV fan motor involves measuring the true RMS power of the motor. The estimated annual energy consumption of a CSCV fan is estimated using the simulated yearly schedule of the fan. Many CSCV fans run on a set daily or weekly schedule. However, the yearly schedule may depend on outdoor air temperature (OAT). If so, operating hours can be regressed against OAT to develop a regression model. Depending on operational variability, daily or weekly models may be created to better characterize the component. This model is then applied to climate normal year data to estimate the typical annual operating schedule, which is used alongside true RMS power to calculate the estimated annual electricity consumption. Click the button below to go to the calculators for this component. Fan Motor Energy Consumption Calculation Estimate the annual energy consumption of variable speed and constant speed fan motors. Further Reading Boyd, BK.; McMordie Stoughton, KL.; Lewis, T. (2017). “Cooling Tower (Evaporative Cooling System) Measurement and Verification Protocol.” Golden, CO: National Renewable Energy Laboratory. https://www.nrel.gov/docs/fy18osti/70219.pdf. Crowther, H.; Furlong, J. (2004). “Optimizing Chillers and Towers.” ASHRAE Journal, Vol. 46, No. 7, July 2004; pp. 34-40. Morrison, F. (2014). “Saving Energy with Cooling Towers.” ASHRAE Journal, Vol. 56, No. 2, February 2014; pp. 34-40. Tom, S. (July 2017). Cat. No. 11-808-616-01. “CHILLED WATER SYSTEM OPTIMIZER.” Farmington, Connecticut: Carrier Corporation.

This type of fan circulates air at a single speed and can be either axial or centrifugal.


Variable-speed, Variable-volume Fan and Motor
General Overview A variable speed fan and motor uses a power-driven rotating impeller to circulate air. Air flow rates fluctuate as required by the plant and system it serves. Outdoor air temperature (OAT) is the independent variable that drives the fan speed. The heating and cooling loads are affected by OAT. Axial and centrifugal fans with a variable speed drive are the most common type of variable speed fans used in buildings. Table 1 shows the plant and system configurations that may contain variable-speed fans and motors and the most common respective controlling variables. Table 1. Plants and systems containing variable-speed fans. Plant System Component Controlling Variable Air-cooled Chilled Water Plant Air-cooled Chiller Condenser Fan Outdoor air temperature (F) Water-cooled Chilled Water Plant Cooling Tower Cooling Tower Fan Wet-bulb temperature (F) AHU AHUs AHU Supply Fan Outdoor air temperature (F) Air Handling Plant AHUs AHU Return Fan Outdoor air temperature (F) Hot Water Heating; Domestic Hot Water; Steam Boiler Burner fan Outdoor air temperature (F) Evaluation of Energy Consumption The primary energy source for a variable-speed fan is the electricity used to run the fan motor. Table 2 provides a summary of measurements needed to quantify the annual energy consumption and operating characteristics of the variable-speed fan and motor. Table 2. Key values and measurements to evaluate energy consumption. Component Quantification Values to be Quantified Measurement Electricity usage of VSVV fan motor (kWh) Power input to the motor at known speeds (e.g., 30%, 50%, 75%, 100%) True RMS power of motor that drives the fan (kW) Controlling variable, non-weather dependent1 Yearly operating schedule Fan motor runtime (h) Controlling variable, weather dependent2 Average hourly outdoor air temperature (OAT) Outdoor air temperature (OAT) Measurement Strategy The measurement strategy for a variable-speed fan and its motor involves measuring power draw of the fan motor at various known speeds, developing a mathematical relationship between the power and speed, and then collecting average hourly motor speed and associated controlling variable (OAT, Wet-bulb temperature). Measurement locations are generically represented in Figure 1. Figure 1. VSVV fan measurement locations (click on image to enlarge). Measurement Equipment Table 3 provides the equipment required to carry out the measurements of this component. Table 3. Measurement equipment. Equipment Description Measurement (Units) DENT ELITEproXC Portable Power Data Logger (EXCUNC) DENT 16” RoCoil Flexible Rope Current Transformers (CT-R16-A4-U) Provides a measurement of true RMS power from voltage and current inputs and records long-term power (kW) and energy (kWh) measurements. Requires ELOG19 software and a USB connection cable for programming and downloading data files. True RMS Power (kW) Onset HOBO Temperature/Relative Humidity Weatherproof Data Logger (MX2301) Records outdoor air temperature and relative humidity using internal sensors. Requires HOBOware software and a USB connection cable for programming and downloading data files. Outdoor Air Temperature (OAT) Relative Humidity (%) Calculation Methodology The general methodology for quantifying the energy consumption of a variable-speed fan and motor is based on the true RMS power of the three-phase power supply, measured either at the motor’s main electrical panel or at the three-phase input to the VFD. To develop a temperature-dependent regression model, these values are regressed against a controlling variable, such as outdoor air temperature (OAT) or wet-bulb temperature. Depending on operational variability, daily or weekly models may be created to better characterize the component. This model is then used with climate normal year data to estimate the typical energy use of the variable-speed fan. Click the button below to go to the calculators for this component. Fan Motor Energy Consumption Calculation Estimate the annual energy consumption of variable speed and constant speed fan motors. Further Reading Boyd, BK.; McMordie Stoughton, KL.; Lewis, T. (2017). “Cooling Tower (Evaporative Cooling System) Measurement and Verification Protocol.” Golden, CO: National Renewable Energy Laboratory. https://www.nrel.gov/docs/fy18osti/70219.pdf. Crowther, H.; Furlong, J. (2004). “Optimizing Chillers and Towers.” ASHRAE Journal, Vol. 46, No. 7; pp. 34-40. Morrison, F. (2014). “Saving Energy with Cooling Towers.” ASHRAE Journal, Vol. 56, No. 2; pp. 34-40. Tom, S. (July 2017). “CHILLED WATER SYSTEM OPTIMIZER.” Cat. No. 11-808-616-01. Farmington, Connecticut: Carrier Corporation. Footnotes This variable should be measured to quantify the electricity usage of the VSVV fan if the operation is weather dependent. ↩︎ This variable should be measured to quantify the electricity usage of the VSVV fan if the operation is not weather dependent ↩︎

This type of fan uses a variable frequency drive (VFD) to regulate its speed to conserve energy.


Compressor and Motor

Constant-speed Compressor and Motor
General Overview A compressor is one of the main components of a chiller. A constant-speed compressor operates at a constant speed to raise the vapor pressure of the refrigerant and power the refrigeration cycle of the chiller. Table 1. Plants and systems containing liquid-to-liquid heat exchangers. Plant System Component Air-cooled Chilled Water Plant Air-cooled Chiller Chiller Compressor Water-cooled Chilled Water Plant Water-cooled Chiller Chilled Compressor Evaluation of Energy Transfer The primary energy source for a constant-speed compressor is the electricity used to run the compressor motor. Table 2 provides a summary of measurements needed to quantify the annual power consumption and operating characteristics of the constant-speed compressor and motor. Table 2. Key values and measurements to evaluate energy consumption. Component Quantification Values to be Quantified Measurement Electricity usage of a constant-speed compressor motor Average hourly power input to the compressor motor Average hourly operating time for the compressor motor True RMS power of compressor motor that drives the compressor (kW) Outdoor air temperature (F) Measurement Strategy Figure 1. Constant-speed compressor and motor measurement locations (click on image to enlarge). The measurement strategy for a constant-speed compressor and motor involves a one-time measurement of power draw and long-term monitoring of the motor’s operational schedule. The approach assumes that the power draw stays constant throughout the measurement period. Because the motor runs at constant speed and is under a constant load, it is either operating at full power (when on) or it is drawing no power (when off). A motor on/off data logger is used to record the operating schedule. The true RMS power is measured at main feed to the constant-speed motor. Measurement locations are generically represented in Figure 1. Measurement Equipment Table 3. Measurement equipment. Equipment Description Measurement (Units) DENT ELITEproXC Portable Power Data Logger (EXCUNC) DENT 16” RoCoil Flexible Rope Current Transformers (CT-R16-A4-U) Provides a measurement of true RMS power from voltage and current inputs and records long-term power (kW) and energy (kWh) measurements. Requires ELOG19 software and a USB connection cable for programming and downloading data files. True RMS Power (kW) Onset HOBO Temperature/Relative Humidity Weatherproof Data Logger (MX2301) Records outdoor air temperature and relative humidity using internal sensors. Requires HOBOware software and a USB connection cable for programming and downloading data files. Outdoor Air Temperature (F) Relative Humidity (%) Calculation Methodology The general methodology for quantifying the electricity consumption of a constant-speed compressor and motor involves measuring their electrical energy use. Depending on operational variability, daily or weekly models incorporating cooling load or a proxy (such as outdoor air temperature) may be developed to better characterize consumption. The typical energy use of a constant-speed compressor is estimated using its simulated yearly schedule. A more detailed explanation of the calculation methodology is provided below. Click the button below to go to the calculators for this component. Pump Motor Energy Consumption Calculation Estimate the annual energy consumption of variable speed and constant speed pump motors. Further Reading ASHRAE. (2020). HVAC Systems and Equipment. Atlanta, GA: ASHRAE.

This equipment is typically used in a chiller system to increase the temperature and pressure of refrigerant.


All Measurements

Measurements refer to the data collected from plants, systems, and components to monitor energy use, heat transfer, performance, and efficiency. These measurements provide a clear view of how energy is utilized by each piece of equipment. More Regularly taking measurements enables trend analysis, helps identify inefficiencies, and supports informed decision-making to enhance energy efficiency and achieve environmental targets. Read more about each measurement below. Less

Temperature and Humidity

Outdoor Air Temperature
Understanding Outdoor Air Temperature (OAT) Measurements This technique uses weatherproof data loggers to take long-term measurements of the outside air temperature (OAT) (F) at one-hour intervals. This technique can be used to characterize the cooling or heating load for any temperature-dependent system such as chillers, boilers, variable-speed air handling units, and ventilation systems. Accurate measurements can only be taken when data loggers are properly installed. Measurements should be taken at one-hour intervals to provide insight into the temperature values that are driving the control mechanisms of the building equipment. Pair OAT with other information about the specific system’s operating conditions in order to calculate annual energy consumption. For more information about how this data is used to estimate annual energy consumption, please refer to the calculation methodology of the type of equipment that relies on OAT. The duration of the long-term measurement should be a minimum of six weeks with data being collected at one-hour intervals. Measurements should be taken when the system of interest is operating under normal conditions. Type of Measurement Direct Measurement Equipment to Use The measurement equipment needed for this procedure is a temperature logger (or a combined temperature and humidity data logger). Refer to the Fell Catalog to identify weatherproof data loggers that measure outside air temperature. The contents of this guide are largely based off of the Onset Hobo MX2301 logger, which can be found and borrowed through FELL. If the logger is installed outdoors, avoid locations with too much sunlight because the logger will measure higher temperatures. Data loggers can be installed inside the ductwork of an air handling unit (AHU) or ventilation system so long as the airstream entering the unit is outside air. The logger must be placed as close as possible to the location where the outside air stream is entering the ductwork. The temperature data measured by the logger should be collected as hourly average values–not instantaneously. With this method, the logger will detect temperature fluctuations across the hour and store the average value of those fluctuations, rather than the measured temperature value at a single point in time (which does not account for those changes). Please note that loggers require setup with a computer or phone using the manufacturer’s proprietary software prior to installation and measurement logging, and that older loggers require the use of a cable to connect to a computer. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement Steps 1. Prepare for Data Acquisition Use the manufacturer’s software to set up and launch the logger(s). Refer to the equipment’s user manual for detailed instructions on how to set up the logger. Logging interval: 1-hour Date and time to start logging Date and time to stop logging Values to measure: Temperature (OF), Relative Humidity (%) if necessary Sampling interval: 1-second Figure 1. How to configure the MX2301 logger on HOBOConnect. (Click to Start Video) 2. Install Equipment Confirm that the outside air dampers are open and that there is outside air intake in the duct (if installing the logger directly in an AHU). Place the logger in the outside air duct or outdoors, staying away from direct sunlight. Confirm that the logger is recording, and that the sensor is accurately identifying the outside air temperature. If the logger has a screen, check the temperature value displayed there. If the logger does not have a screen, use the software to connect to the logger and check the temperature it detects Do not move the logger after it has been installed. Figure 2. How to install MX2301 MX1101 UX100 temperature loggers. (Click to Start Video) 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment and use a laptop or phone with the manufacturer’s proprietary software installed to do the following: Do not remove the logger or sensors. If you remove the logger, you may need to start over with the setup and installation process. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with the proprietary software or Microsoft Excel after exporting the dataset as a .csv file. Determine whether the measured results align with the expected OAT values based on observed weather trends or known outside air damper schedules. Figure 3. How to check data of bluetooth loggers using HOBOConnect. (Click to Start Video) 4. Retrieve Measurement Equipment and Download All Final Data After verifying that the logger is collecting data, do the following: Allow the logger to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the logger. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the logger via Bluetooth. Use the proprietary software to stop the logger and end data collection. Download all data from the logger and save the file in the.csv file format for analysis. Figure 4. How to extract data from the logger and convert to csv on HOBOConnect. (Click to Start Video) Troubleshooting Our Measurement Equipment Problem 1: Logger is measuring unexpected values Solution: If the ambient temperature reading is higher or lower than expected, adjust the placement of the logger. Problem 2: Logger screen is blank Solution: The logger might have an energy saving feature that conserves battery life by turning off the screen. Try pressing one of the logger buttons or connecting to it with your phone or laptop.​ If the screen remains blank, try replacing the battery. If it remains blank, reach out to our equipment specialist for a replacement.

Use this technique to measure outdoor air temperature (OAT) at one-hour intervals with a data logger.


Pipe Surface Water Temperature
Understanding Pipe Surface Water Temperature Measurements This technique uses a 4-channel analog logger with a thermocouple sensor to record long-term water temperature (°F) measurements at one-hour intervals. It measures fluid temperature from the surface of a pipe rather than directly in the water stream. The collected data can be used to determine the cooling load and heat rejected by a cooling plant, the heat load delivered by a heating plant, and the heat recovered by an economizer. For more details on how collected data is used for calculations, refer to the calculation methodology of the system being measured. Measurements should be taken at one-hour intervals rather than as instantaneous values. When recording hourly measurements, the logger captures multiple temperature readings throughout the hour and stores the average value. Since temperature can fluctuate within an hour, an instantaneous reading may not accurately reflect these variations. The duration of the long-term measurement should be a minimum of six weeks. Measurements should be taken when the system of interest is operating under normal conditions. Type of measurement Proxy Measurement Equipment to Use The measurement equipment needed for this procedure is a 4-channel analog logger that is compatible with thermocouple sensors. Thermocouple sensors are specially designed to measure very high temperatures, such as as those within the flue stack of a boiler, and very low temperatures, such as those on the surface of water pipes for a chiller system. Different thermocouple sensors are used to measure hot or cold pipes. Refer to the FELL catalog to identify the correct loggers and sensors for your project. The contents of this guide are largely based off the Onset HOBO UX120-14M logger and the TC6-T sensor, which can be found and borrowed through FELL. For sensors installed at a pipe surface, the sensor must be secured with thermal tape and the pipe surface should be cleaned prior to installation. Please note that loggers require setup with a computer or phone using the manufacturer’s proprietary software prior to installation and measurement logging, and that older loggers require the use of a cable to connect to a computer. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement steps 1. Prepare for Data Acquisition Use the manufacturer’s software to set up and launch the logger(s). Refer to the equipment’s user manual for detailed instructions on how to set up the logger. Logging interval: 1-hour4 Date and time to start logging Date and time to stop logging Value(s) to measure: Temperature (oF) Activate input channels on the logger Type of thermocouple sensor (K-type or T-type) Sampling interval: 1-second Figure 1. How to configure 4-channel analog logger with CT on HOBOware. (Click to Start Video) 2. Install Equipment Connect the sensors to the data logger. Place the data logger near the pipes. Avoid adhering the logger to the pipe itself. Clean the surface of the pipe where the sensor will be placed, removing any dust. Place the sensor on the clean surface and apply thermal tape to fully cover the sensor. Figure 2. How to install the 4-channel analog logger with CT onsite. (Click to Start Video) 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment and use a laptop or phone with the manufacturer’s proprietary software installed to do the following: Do not remove the logger or sensors. If you remove the logger, you may need to start over with the setup and installation process. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with proprietary software or Microsoft Excel after exporting the dataset as a .csv file. Determine whether measured results align with the expected operation of the system or component. Figure 3. How to check data of loggers using HOBOware. (Click to Start Video) 4. Retrieve Measurement Equipment and Download All Final Data After verifying that the logger is collecting data, do the following: Allow the logger to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the logger. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the logger via Bluetooth. Use the proprietary software to stop the logger and end data collection. Download all data from the logger and save the file in the.csv file format for analysis. Figure 4. How to extract data from the logger using HOBOware. (Click to Start Video) Troubleshooting Our Measurement Equipment Problem: the logger is measuring unexpected values Solution: Verify that the logger is calibrated. Re-calibrate the equipment if necessary. Clean the surface of the pipe with a damp cloth to wipe off any dirt and grime. Ensure the sensor is covered with thermal tape to prevent measurement of the ambient air around the pipe.

Use this technique to measure the temperature of water inside a piping system at one-hour intervals with a data logger.


Relative Humidity
Understanding Relative Humidity Measurements This technique uses data loggers to take long-term measurements of relative humidity (% RH) at one-hour intervals. This technique can be used to characterize the performance of heat/energy recovery ventilators. Data is used for calculations such as regression models to estimate the heat and energy recovered by an air-to-air heat/energy recovery system. For a more detailed description of how relative humidity data is used in calculations, please refer to the Air-to-Air Energy Recovery System and calculation methodology of the system being measured. Relative humidity measurements should be taken at one-hour intervals and paired with the temperature of the system if both variables are required to characterize performance. Measurements should be taken at one-hour average intervals; do not use instantaneous values. When taking one-hour measurements, the logger detects humidity several times every hour and stores the average value. Sometimes humidity can fluctuate over a one-hour period, and the instantaneous value will not indicate that change. The duration of the long-term measurement should be a minimum of six weeks. Measurements should be when the system of interest is operating under normal conditions. Type of Measurement Direct Measurement Equipment to Use The measurement equipment required for this procedure is a humidity data logger. Most loggers available at FELL can simultaneously measure temperature and humidity. If both variables are needed, relative humidity and temperature should be recorded at the same time. The same data loggers can be used to measure humidity when monitoring outdoor air temperature or system air temperature. Refer to the FELL catalog to identify temperature/humidity data loggers. The contents of this guide are largely based off the Onset HOBO MX2301 logger, which can be found and borrowed through FELL. The data loggers should be installed in the ductwork with the air stream. The relative humidity data measured by the logger should be collected as hourly average values; not as instantaneous values. When operating under this method, the logger detects humidity fluctuations across the hour and stores the average value of those fluctuations, rather than the measured relative humidity value at an instantaneous point in time (which does not account for those changes). Please note that loggers require setup with a computer or phone using the manufacturer’s proprietary software prior to installation and measurement logging, and that older loggers require the use of a cable to connect to a computer. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement Steps 1. Prepare for Data Acquisition Use the manufacturer’s software to set up and launch the logger(s). Refer to the equipment’s user manual for detailed instructions on how to set up the logger. Logging interval: 1-hour Date and time to start logging Date and time to stop logging Value(s) to measure: Relative Humidity (%), Temperature (F) if necessary Sampling interval: 1-second Figure 1. How to configure the MX2301 logger on HOBOConnect. (Click to Start Video) 2. Install Equipment To accurately measure relative humidity of outside air, use a weatherproof data logger only. Place the logger inside of the air duct as close as possible to the outside air damper. Alternatively, install the logger on the roof or somewhere with little foot traffic but away from direct sunlight. To measure relative humidity of the air streams inside of an AHU, place the loggers inside of the ductwork. AHUs typically have panels that open to reach inside of ductwork. There are up to four air streams inside an AHU: outside air, return air, mixed air, and supply/discharge air. A separate data logger should be used for each air stream. Confirm that the logger is recording, and that the sensor is accurately identifying the airstream’s temperature. If the logger has a screen, check that the temperature value is displayed on the logger screen. If the logger does not have a screen, use the software to connect to the logger and check the temperature it detects. Do not place the loggers near heating or cooling coils. Mixed air relative humidity is particularly challenging to measure, as some mixed air chambers make it difficult to position a data logger for accurate readings. The measurement uncertainty introduced is unknown, and CUNY BPL recommends experimenting with different logger placements within the air chamber to improve accuracy. Figure 2. How to install the MX2301 MX1101 UX100 temperature loggers. (Click to Start Video) 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment and use a laptop or phone with the manufacturer’s proprietary software installed to do the following: Do not remove the logger or sensors. If you remove the logger, you may need to start over with the setup and installation process. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with the proprietary software or Microsoft Excel after exporting the dataset as a .csv file. Determine whether the measured results align with the expected operation of the system or component. Figure 3. How to check data of bluetooth loggers using HOBOConnect. (Click to Start Video) 4. Retrieve Measurement Equipment and Download All Final Data After verifying the logger is collecting data, do the following: Allow the logger to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the logger. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the logger via Bluetooth. Download all data from the logger and save the file in the .csv format for analysis. Figure 4. How to extract data from the logger and convert to csv on HOBOConnect. (Click to Start Video) Troubleshooting Our Measurement Equipment Air handling units come in all sizes, and there is no single method for properly installing all relative humidity loggers. Installing at the mixing plenum/chamber is the most challenging because you are trying to measure the mixed air temperature, which is the combination of return air and outside air. Problem: the logger is measuring unexpected values Solution: Verify that the logger is calibrated. Re-calibrate the equipment if necessary. Adjust the placement of the logger and ensure that the logger is installed correctly and that there is no interference from heating and cooling coils.

Use this technique to measure relative humidity (RH %) of various air streams in an air handling unit at one-hour intervals with data loggers.


System Air Temperature
Understanding System Air Temperature Measurements This technique uses data loggers to take long-term measurements of air temperature (F) at one-hour intervals. This technique can be used to characterize air handling unit (AHU) performance; supply/discharge air, return air, exhaust air, and mixed air temperatures are measured with this technique. Each air stream requires a different logger for data collection. This data is used to estimate the thermal loads of the system during the heating and cooling seasons. For a more detailed description of how to characterize an AHU, please refer to the protocols and procedures Air Handling Plant. Measurements should be taken at one-hour average intervals; not instantaneously. When taking one-hour measurements, the logger detects the temperature several times over every hour and stores the average value. Sometimes temperature can fluctuate over a one-hour period, but the instantaneous temperature value will not indicate that change. The duration of the long-term measurement should be a minimum of six weeks. Measurements should be taken when the system is operating under normal conditions. Although AHUs typically operate year-round, the heating and cooling seasons affect their schedules. To calculate the annual energy consumption of a unit, six weeks of measurements should be taken for each season. To calculate only the heating or cooling season energy consumption, six weeks of measurements for that season should be taken. Type of Measurement Direct Measurement Equipment to Use The measurement equipment needed for this procedure is a temperature logger (or a combined temperature and humidity data logger). Refer to the FELL catalog to identify temperature/humidity data loggers. The contents of this guide are largely based off the Onset HOBO MX1101 logger, which can be found and borrowed through FELL. The data loggers should be installed in the ductwork with the air stream. Users should avoid placing the loggers near heat exchangers, such as the heating or cooling coils within the air handling unit, because the logger will detect the temperature of air around those components instead of the true air temperature. The temperature data measured by the logger should be collected as hourly average values; not instantaneously. Operating under this method, the logger detects temperature fluctuations across the hour and stores the average value of those fluctuations rather than the measured temperature value at an instantaneous point in time (which does not account for those changes). Please note that loggers require setup with a computer or phone using the manufacturer’s proprietary software prior to installation and measurement logging, and that older loggers require the use of a cable to connect to a computer. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement steps 1. Preparation for data acquisition Use the manufacturer’s software to set up and launch the logger(s). Refer to the equipment’s user manual for detailed instructions on how to set up the logger. Logging interval: 1-hour Date and time to start logging Date and time to stop logging Value(s) to measure: Temperature (F), Relative Humidity (%) if necessary Sampling interval: 1-second Figure 1. How to configure the MX1101 logger on HOBOConnect. (Click to Start Video) 2. Installation of equipment To measure temperature of the air streams inside of an AHU, place the loggers inside of the ductwork. (Mixed air temperature is the most difficult data to collect because some mixed air chambers make it difficult to install a data logger to accurately capture mixed air. The measurement uncertainty introduced is unknown and CUNY BPL suggests experimenting with different logger placements within the air chamber. Do not place the loggers near the heating and cooling coils.) Confirm that the logger is recording, and that the sensor is accurately identifying the airstream’s temperature. If the logger has a screen, ensure that the temperature value is displayed on the logger screen. If the logger does not have a screen, use the software to connect to the logger and check the temperature it detects. Do not move the logger after it has been installed. Figure 2. How to install the MX2301 MX1101 UX100 temperature loggers. (Click to Start Video) 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment and use a laptop or phone with the manufacturer’s proprietary software installed to do the following: Do not remove the logger or sensors. If you remove the logger, you may need to start over with the setup and installation process. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with the proprietary software or Microsoft Excel after exporting the dataset as a .csv file. Determine whether the measured results align with the expected operation of the system or component based on observed equipment schedules. Figure 3. How to check data of bluetooth loggers using HOBOConnect. (Click to Start Video) 4. Retrieve Measurement Equipment and Download All Final Data After verifying that the logger is collecting data, do the following: Allow the logger to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the logger. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the logger via Bluetooth. Use the proprietary software to stop the logger and end data collection. Download all data from the logger and save the file in the.csv file format for analysis. Figure 4. How to extract data from the logger and convert to csv on HOBOConnect. (Click to Start Video) Troubleshooting Our Measurement Equipment Air handling units come in all sizes, and there is no single method for properly installing all temperature loggers. Installing at the mixing plenum/chamber is the most challenging because you are trying to measure the mixed air temperature, which is the combination of return air and outside air. Problem 1: the logger is measuring unexpected values. Solution Verify that the logger is calibrated. Re-calibrate the equipment if necessary. Problem 2: The temperature reading is higher than expected Solution: Adjust the placement of the logger, ensuring that the logger is installed correctly and that there is no interference from heating and cooling coils.

Use this technique to measure the air temperature of various air streams in an air handling unit at one-hour intervals with data loggers.


Electrical

Electrical Current
Understanding Electrical Current Measurements This technique uses a data logger and current transformers to take long-term measurements of electrical current (Amps) at one-hour intervals. This data provides insight on the operating schedule of the system or component and can be used to calculate energy consumption of the target equipment at the power panel or electrical panelboard. A system or component that is running (i.e., consuming energy) will have high current draw. A system or component that is not running (i.e., has no energy consumption) will have low or no current draw. Data loggers and current sensors use instantaneous measurements of current over the course of an hour to calculate the average amperage. As such, current data should be recorded as hourly average values, not instantaneous. When taking one-hour measurements, the logger detects current over the course of every hour and store that value. Occassionally, current can fluctuate over a one-hour period (motors turn off or change speed), but the instantaneous current value will not indicate that change. The duration of the long-term measurement and when to measure is dependent on the system and the operation of the building. The best practice is a minimum of six weeks with data being collected at one-hour intervals; longer measurement periods are encouraged for deeper analysis of the equipment. Measurements should be taken when the system or component is operating under normal conditions. Type of Measurement Direct and Proxy This methodology is a direct measurement of current; however, it is also considered a proxy measurement of power and energy, as well as operational hours of the system or component. Measurement Equipment to Use The measurement equipment needed for this procedure is an energy data logger with capacity to measure AC current over time and record measurement data in its internal storage. Refer to the FELL catalog to identify data loggers that measure current draw by an electricity-powered system. The contents of this guide are largely based off of the Onset HOBO 4-channel analog logger (UX120-006M) and the Onset Split-Core AC Current Transformer (CTV-x), which can be found and borrowed through FELL. Current transformers are sensors that detect the magnetic field induced by an electrical current through a wire. As the current increases or decreases, the magnetic field strength changes, and the current transformers detect this change. The data logger calculates current through the wire based on the signal from the transformers and record the AC current value in its internal storage. A data logger can have multiple current transformers connected to it, allowing a user to measure multiple wires with a single logger. It is important to know how many wires will be measured and the current rating of those wires, so the appropriate current transformers are used. Please note that loggers require setup with a computer or phone using the manufacturer’s proprietary software prior to installation and measurement logging, and that older loggers require the use of a cable to connect to a computer. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement Steps 1. Prepare for Data Acquisition Use the manufacturer’s software to set up and launch the logger(s). Refer to the equipment’s user manual for detailed setup instructions. Before proceeding, identify the current rating(s) of the wires to be measured to ensure the selection of a properly sized current transformer for this measurement approach. For further guidance on selecting the appropriate current transformer for the target system or component, consult the equipment’s instruction manual. Logging interval: 1-hour Date and time to start logging Date and time to stop logging Sampling interval: 1-second Value to measure: AC current (Amps) Activate input channels of the logger Select the current rating of transformers being used An example of how to setup the Onset HOBO 4-channel analog logger (UX120-006M) is shown in the video below Figure 1. How to configure the 4-channel analog logger with CT on HOBOware (Click to Start Video). 2. Install Equipment Confirm that the equipment is operational. Connect the sensors to the data logger. Determine whether the distribution system supplies electricity to other loads unrelated to the project to avoid measuring unintended energy consumption. Identify the wiring configuration of the distribution system. This will determine how to set up the logger and sensors. Based on the wiring configuration and instructions from the equipment’s user manual, install the sensor and logger to measure the current draw by the system. The current transformers are clamps that open and surround the wire, see Figure 2. Clamp the sensors around the electrical wires. Make sure they are facing the right direction, or the current may be recorded with negative values. Adhere the data logger to the panelboard. Some loggers have magnets that allow for placement on the panelboard itself, while others do not. Figure 2. How to install the 4-channel analog logger with CT onsite (Click to Start Video). 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment and use a laptop or a phone with the manufacturer’s proprietary software installed to do the following: Do not remove the logger or sensors. If you remove the logger, you may need to start over with the setup and installation process. If necessary, connect the logger to the laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with the proprietary software or Microsoft Excel after exporting the dataset as a .csv file. Determine whether the results align with the expected operation of the system or component based on observed operational patterns or known equipment schedules. Figure 3. How to check data of logger using HOBOware. (Click to Start Video) 4. Retrieve Measurement Equipment and Download Data After verifying that the logger is collecting data, do the following: Allow the logger to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the logger from the panel. If necessary, connect the logger to the laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Use the proprietary software to stop the logger and end data collection. Download all data from the logger and save the file in the .csv file format for analysis. Figure 4. How to extract data from the logger using HOBOware. (Click to Start Video) Troubleshooting Our Measurement Equipment Problem 1: Unexpected Negative Readings Solution: Confirm that all current transformers (CTs) are facing the correct direction. Problem 2: Unexpected Low Values Solution: Confirm that the current rating for the electrical distribution system is within the range of the current rating for the CTs. Problem 3: CTs Do Not Fit in Panelboard Casing Solution: If it is safe to do so, trace the wires outside the panelboard and install the sensors there. If this is unsafe or not possible to do, consider seeking the help of a certified electrician.

Use this technique to measure electrical current (Amps) at one-hour intervals with a data logger.


Electrical Spot Measurement
Understanding Electrical Spot Measurements This technique uses a handheld power meter to take one-time measurements of true RMS power draw (kW) at an electrical distribution system, such as a panelboard, power panel, or switchgear. One-time measurements provide a snapshot of power draw, voltage, current, and power factor for a system or component, such as lighting fixtures, chillers, and fan or pump motors. This technique is commonly used for loads with a constant power draw, including constant-speed fans, pumps, and certain lighting fixture systems. If power draw changes over time, CUNY BPL recommends using a data logger to take direct measurements of electrical energy consumption (kWh). Power meters use instantaneous measurements of current and voltage to calculate the instantaneous power draw. As the meter remains connected to the distribution system, it calculates the average power draw, which is displayed on the meter’s screen. Manufacturers of power meters and data loggers use different calculation methodologies to calculate the power draw. In order to compare power draw data obtained from different loggers and meters, refer to the user manual to understand the calculation methodology used by the equipment. It is advised to take a minimum of three measurements 1-2 minutes apart while the system or component is in operation. The average of the three measurements (true RMS power, voltage, current and power factor) should be calculated, as averaging the values helps to reduce the measurement uncertainty. Electrical distribution systems can have different configurations, such as three-phase delta, three-phase wye, single-phase, and split phase on a delta configuration. It is important to first identify the configuration of the system before taking any measurements. The configuration of the system will determine the connections to make with the measurement equipment. Refer to the Measurement Steps section for more details on the different configurations. Type of Measurement Proxy This is a proxy measurement of electrical energy consumption of a system or component. Energy consumption is calculated with true RMS power draw and the runtime (operating schedule) of the system or component. Measurement Equipment to Use The measurement equipment needed for this procedure is a handheld power meter with a current transformer and voltage cables. Refer to the FELL catalog to identify data loggers that measure power and energy draw by an electricity-powered system. The contents of this guide are largely based off the Fluke 345 PQ Clamp Meter and the Extech PQ2071, both of which can be found and borrowed through FELL. A power meter typically measures AC voltage, current, and power factor, and can display all values simultaneously. Please note that some power meters can log data for a short amount of time or take a screen shot of the measurements while the meter is connected to the load. Taking a picture with a phone is another option for saving measurement data. While some power meters can measure true three-phase power by measuring each phase, other meters with fewer wire connections can only estimate three-phase power. The Fluke 345 PQ Clamp Meter is an example of a meter that only estimates three-phase power. The Extech PQ20711 is an example of a meter that can measure three phases without estimation. Both meters should only be used on a balanced load, meaning the currents and voltages on each phase are equal. If the load is not balanced, three-phase power cannot be accurately measured with a handheld meter and a data logger with the capacity to measure three phases at the same time (such as the Dent EliteProXC2) should be used instead. Measurement Steps 1. Prepare for Data Acquisition The following sections discusses the most common wire configurations found in a distribution system and assume a handheld power meter is being used, for details on how to install data loggers refer to the True RMS Energy guide. Values to measure: True RMS power (kW) Voltage (V) Current (Amps) Power Factor 2. Install Equipment Confirm that the equipment is operational. Identify whether the distribution system supplies electricity to other loads that are not relevant to the project (to avoid measuring unwanted loads). Identify the wiring configuration of the distribution system. This will determine how to set up the logger and sensors. Based on the wiring configuration and instructions from the equipment’s user manual, install the sensor and logger to measure the current, voltage, and power factor to the system. An example of how to connect the Fluke 345 PQ Clamp Meter is shown below Figure 1. How to install the fluke 345 PQ clamp meter. (Click to Start Video) Some power meters offered through FELL can measure three-phase power with different calculation methods. Carefully read the user manual of the power meter to identify the calculations used to estimate three-phase power. Single-phase Wire Configurations A single-phase electrical distribution system typically consists of a hot wire and a neutral wire. The hot wire provides current to the load, while the neutral wire returns the current to the supply in order to complete the circuit. To measure the power draw of a single-phase system, measure the voltage across the hot wire and neutral wire, and measure the current of the hot wire. Figures 2 and 3 are examples of how measurement equipment offered by the FELL are connected on a single-phase system. Figure 2. Single-phase power measurement connections for the Fluke 345 Power Quality Clamp Meter. Image courtesy of Fluke Corporation. Figure 3. Single-phase, three wire or split-phase connections for the Extech Instruments Clamp meter, model PQ2071. Image courtesy of Extech Instruments. Three-phase Wire Configurations For a three-phase distribution system, there are two common wire configurations: the three wire (delta) and four wire (wye). Both wire configurations require slightly different connections of the voltage leads. Manufacturers of power meters have specific instructions for making connections for a given wire configuration. Refer to the power meter’s user manual for detailed instructions. Figures 3, 4, and 5 are examples of how some of the meters offered by the FELL are connected to three-phase systems. Figure 4. Three-phase power measurement using the Fluke 345 Power Quality Clamp Meter. Image courtesy of Fluke Corporation. For the connection illustrated in Figure 3, this power meter can only measure line-to-line voltage of two phases and the current of the third phase to estimate True RMS power. Figure 5. Three-phase, three wire (delta) power measurement connections using the Extech Instruments Clamp meter, model PQ2071. Figure 6: Three-phase, four wire (wye) power measurement connections using the Extech Instruments Clamp meter, model PQ2071. Troubleshooting Our Measurement Equipment Problem 1: It can be difficult or confusing to know how to connect a power meter to a panelboard because panelboards can have many different colored wires. Older panelboards might not have clear or accurate labeling at the circuit breakers, making it challenging to make proper connections. Solution: In cases where it is unclear how the power is distributed, do not touch the panel or install any sensors without first having someone from the facility identify the power distribution. Problem 2: The panelboard is too small, and connections cannot be made within the space constraints. Solution: Connect the sensors at the panelboard’s input or measure at the switchgear. Problem 3: A voltage connection cannot be made because the alligator clips are too large or contact cannot be made with the metal lugs in the panelboard. Solution: Voltage connection can be difficult if you are not using the correct attachments. Voltage cables can have alligator clips or leads to accommodate for space constraints. In a case where connection cannot be made, use different size voltage leads or investigate alternative attachments for the panelboard’s configuration. Problem 4: Unexpected Negative Values Solution: At times, measurements will return as negative values because of how the voltage cables are connected. Connect voltage cables in different ways until you obtain positive values. Make sure the connections are correct for accurate power measurements. If you are not sure about the connections, consult a certified electrician.

Use this technique to take one-time measurements of different electrical properties such as voltage, current, power draw, and power factor with a handheld …


True RMS Power
Understanding Hourly True RMS Power Measurements This technique uses a data logger to take long-term measurements of the electrical energy (kWh) and power draw (kW) of a system or component at one-hour intervals. Measurements are taken at the electrical distribution system (specifically at a panelboard, power panel, or switchgear) that serves the system or component. Measurement data is used to estimate the annual energy consumption of the system or component. Data loggers and power meters use instantaneous measurements of current and voltage to calculate the instantaneous power draw. Over time, the logger or meter calculates the average power draw. Manufacturers of measurement equipment use different calculations for power draw. In order to compare data obtained from different measurement equipment, it is important to understand the calculation used by the equipment. The manufacturer’s user manual or technical specifications discuss these features in detail. The duration of the long-term measurement and when to measure is dependent on the system and the operation of the building. Best practice is to collect the data for a minimum of six weeks at one-hour intervals; longer measurement periods are encouraged for deeper analysis of the equipment. Measurements should be taken when the system or component is operating under normal conditions. Type of Measurement Electrical energy measurements are direct measurements of energy, and the obtained data can be used to calculate the annual energy consumption of the system or component. This methodology can also be used as a proxy measurement of operational hours of the system or component. Daily or weekly models can be developed to better characterize the equipment. Measurement Equipment The measurement equipment needed for this procedure is an energy data logger that has the capacity to measure AC voltage and current. The sensors used to measure AC current are known as current transformers. This is because they operate like the transformers used by utility companies to step-up and step-down voltage. Alternating current in the conductor (the wire that is being measured) induces a voltage on the current transformer, which then produces a current signal that the data logger detects and records. However, unlike utility transformers, the measurement equipment only transforms a tiny portion of the current flowing through the wire that is being measured. AC voltage is measured with voltage leads (usually alligator clips). tip If you are NYC agency personnel and you require measurement tools, data loggers, meters or sensors, we offer equipment lending through the Field Equipment Lending Library. This measurement technique makes use of the following equipment available in the Field Equipment Lending Library: Enegry Data Logger Equipment Provides a measurement of true RMS power from voltage and current inputs and records long-term power (kW) and energy (kWh) measurements. Requires ELOG19 software and a USB connection cable for programming and downloading data files. Borrow Equipment note Please note that loggers will require setup with a computer or phone using the manufacturer’s proprietary software prior to installation and measurement logging and that older loggers will require the use of a cable to connect to a computer. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement Steps 1. Prepare for Data Acquisition The following sections assume a data logger is being used. For details on measurement with a power meter, refer to the One-time true RMS power guide. Use the manufacturer’s software to set up and launch the logger(s). Refer to the equipment’s user manual for detailed instructions on how to set up the logger. Logging interval: 1-hour Date and time to start logging Date and time to stop logging Values to measure: Power (kW), Energy (kWh) An example of how to set up the Dent EliteProXC power data logger is shown in the video below. Figure 1. How to configure the Dent EliteProXC Power Meter on ELOG software. (Click to Start Video) 2. Install Equipment Confirm that the equipment is operational. Determine whether the distribution system supplies electricity to any unrelated loads to avoid measuring unintended energy consumption. Identify the wiring configuration of the distribution system. This will determine how to set up the logger and sensors. Clamp the sensors around the electrical wires. Make sure they are facing the right direction, or the current may be recorded with negative values. Based on the wiring configuration and instructions from the equipment’s user manual, install the sensor and logger to measure the power and energy to the system. This section illustrates the most common wire configurations for a panelboard and how the Dent EliteProXC data logger is connected. Figure 2. How to install the Dent EliteProXC Power Meter. (Click to Start Video) 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment and use a laptop or a phone with the manufacturer’s proprietary software installed to do the following: warning Do not remove the logger or sensors. If you remove the logger, you may need to start over with the setup and installation process. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with the proprietary software or Microsoft Excel after exporting the dataset as a .csv file. Determine whether the results align with the expected operation of the system or component based on observed operational patterns or known equipment schedules. Figure 3. How to check data on the power meter using ELOG19. (Click to Start Video) 4. Retrieve Measurement Equipment and Download Data After verifying that the logger is collecting data, do the following: Allow the logger to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the logger from the panel. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Use the proprietary software to stop the logger and end data collection. Download all data from the logger and save the file in the .csv file format for analysis. Figure 4. How to extract data from the power meter and convert to .csv on ELOG software. (Click to Start Video) 5. Process and Analyze Measured Data Use the collected measurement data in the corresponding calculator file based on the type of component you are measuring: Heat Exchangers Air-to-air Heat Exchanger Component The rotary wheel achieves heat transfer using temperature difference between two airstreams without direct contact of these airstreams. Fan and Motor Constant-speed, Constant-volume Fan and Motor Component This type of fan circulates air at a single speed and can be either axial or centrifugal. Variable-speed, Variable-volume Fan and Motor Component This type of fan uses a variable frequency drive (VFD) to regulate its speed to conserve energy. Pump and Motor Variable-speed, Variable-volume Pump and Motor Component Operates at different speeds with a variable frequency drive to circulate liquid (water or glycol solution) through a piping network. Compressor and Motor Constant-speed Compressor and Motor Component This equipment is typically used in a chiller system to increase the temperature and pressure of refrigerant. Electrical Distribution Electrical Distribution System This system regulates the amount of electricity supplied to different areas of the facility. This is the primary measurement location of lighting fixture systems. Troubleshooting Unexpected Negative Readings Confirm that all current transformers (CTs) are facing the correct direction. Unexpected Low Values Confirm that the current rating for the electrical distribution system is within the range of the current rating for the CTs. CTs Do Not Fit in Panelboard Casing If it is safe to do so, trace the wires outside the panel board and install the sensors there. If this is unsafe or not possible to do, consider following an alternative approach of measuring current to the system with either instantaneous true power or nameplate data as a proxy for total power draw and energy consumption.

Use this technique to measure power draw (true RMS power) at one-hour intervals using a data logger.


Runtime

Lighting Fixture Runtime
Understanding Lighting Fixture Runtime Measurements This technique uses data loggers to take long-term measurements of the runtime duration for a lamp or lighting fixture. This technique can be used on lighting systems with any schedule and located in any space type. Accurate measurements can only be taken when data loggers are properly installed. The equipment’s on/off status is detected based on the light level that is generated when the lights are on. Measurements should be taken at one-hour intervals,​ and will provide insight on the hours of operation of the lamp(s)​. ​Lighting runtime measurements should be paired with t​he wattage and number of fixtures​ ​to calculate total power draw (kW)​ and energy consumption (kWh)​ of the lighting system. For more information about how ​this data is used to estimate the ​annual energy ​consumption, ​please refer to the Lighting Plant Calculation Methodology.​ Please note that this approach is recommended as a secondary or supplementary method in the case where ​direct electrical measurements cannot be taken. ​​In cases where measuring all fixtures associated with a retrofit is not possible, sampling should be used. ​Sampling is the process of measuring a ​subset of ​fixture​s​ that represent the entire population. For example, in an office​ space​ there might be ceiling fixtures, wall mounted fixtures, and desk lamps​, but ​​​a light logger ​can ​only ​be used to measure ​a single fixture ​at a time​. Rather than measuring all fixtures in the office, one light logger ​may be used ​per fixture type​. In this example, ​one logger ​may be used ​to measure the runtime of a ceiling fixture, another logger for a wall mounted fixture, and ​final ​logger for a desk lamp. The collected runtime data will be used to estimate the annual energy consumption​. Therefore, ​it is important to ​sample​​ ​the fixtures​s​ that operate​ ​under normal conditions so that ​they can ​​​reasonably represent all fixtures of the same type. If runtime of an entire room or space​ is more important than ​that of a specific ​fixture type, ​a​​ ​single light logger can be calibrated to a light fixture that is used during normal ​space ​operations. The runtime data will be representative of the hours of operation of the space and all fixtures within that space. To calculate the annual energy consumption​, the ​total power draw (kW) of all fixtures in the space must be identified. The duration of the long-term measurement should be a minimum of six weeks, and data should be collected at one-hour intervals. Measurements should be taken when the fixtures are operating under normal conditions. Type of Measurement Proxy Measurement Equipment to Use The measurement equipment needed for this procedure is a lighting on/off data logger. Some data loggers may have an additional occupancy sensor that detects the motion of people, but this is not necessary for this measurement technique. Refer to the FELL catalog to identify data loggers to measure lighting runtime. The contents of this guide are largely based off of the Onset HOBO UX90-002 Light on/off logger which can be found and borrowed through FELL. When a lighting system turns on, it emits photons. The lighting on/off sensor operates by using a photosensor to detect the light level and records the length of time for which the light is detected. The runtime period is considered complete once the light turns off, the light level decreases, and the sensor no longer detects the emitted photons. The logger records the amount of time that the light was detected (i.e., the lights were on) and documents this in its internal storage for each hour interval. Loggers require calibration prior to each use. To do this, the lights should be on, and the logger should be placed in a location that is unshaded, but also not too close to other light sources (such as sunlight or other fixtures), because the logger may detect those and collect unwanted data. Please ​note ​​that loggers ​require setup with a computer or phone ​using ​​the manufacturer’s proprietary software prior to installation and measurement logging​ and that older loggers will require the use of a cable to connect to a computer​.​ Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement Steps 1. Prepare for Data Acquisition Use the manufacturer’s software to ​set up ​​and launch ​the logger​(s)​. Refer to the ​equipment’s ​user manual for detailed instructions on how to ​set up​ the logger. Logging interval: 1-hour Date and time to start logging< Date and time to stop logging Value to measure: ​R​untime (minutes) Figure 1. How to configure the light on/off data logger on HOBOware. (Click to Start Video) 2. Install Equipment Confirm that the fixture is operational and turn the light fixture on.​ Place the data logger near the light fixture​ in a non-hazardous location. ​While the light is on, c​alibrate the data logger to the fixture (refer to the ​data logger’s ​user manual for instructions​ and requirements for calibration​)​.​ ​​​Visually confirm that the logger is recording, and that the sensor is accurately identifying whether or not the lights are on. Figure 2. How to calibrate and install the light on/off logger. (Click to Start Video) 3. Verify Data is Being Collected Wait ​24-48 hours to verify data collection. Return to the location of the measured equipment ​​and use ​​a laptop or phone with the manufacturer’s ​proprietary​ software installed to do the following: Do not remove the logger or sensors. If you remove the logger, you may need to start over with the setup and installation process. ​​​​If necessary, connect the logger to the laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. ​​​Analyze the data with a ​​plot graph​. This can be done with the proprietary software or Microsoft Excel after exporting the dataset as a .csv file. Determine whether ​the ​measured results align with ​the ​expected operation of the fixtures or space​ based on observed operational patterns or known equipment schedules. Figure 3. How to check data of runtime loggers using HOBOware. (Click to Start Video) 4. Retrieve Measurement Equipment and Download All Final Data After verifying ​that ​the logger is collecting data​,​ do the following: Allow the logger to collect data for the remainder of the measurement period​.​​ ​​After the measurement period ​has concluded, ​remove the logger​. If necessary, connect the logger to the laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Download all data from the logger and ​save the file in the​​ .​csv format for analysis​. Figure 4. How to extract data from the logger and convert to .csv file on HOBOware. (Click to Start Video) Troubleshooting Our Measurement Equipment Problem 1: Light logger continues to detect light despite the fixture being turned off Solution: The light logger may be detecting another light source, such as the sun or another fixture. Calibrate the logger again with the same fixture. If the problem persists, try calibrating with a different fixture. If the problem continues, reach out to our equipment specialist for a replacement logger. Problem 2: The logger screen is blank Solution: The logger might have an energy saving feature that conserves battery life by turning off the screen. Try pressing one of the logger buttons or connecting to it with your phone or laptop.​ If the screen remains blank, try replacing the battery. If it remains blank, reach out to our equipment specialist for a replacement.

Use this technique to measure the hours of operation of a light fixture or lamp with a data logger.


Motor Runtime
Understanding Motor Runtime Measurements This technique uses data loggers to take long-term measurements of the runtime duration for a constant or dual-speed motor. This technique can be used on motors with any end-use, including both air and water distribution. Accurate measurements can only be taken when data loggers are properly placed on the motor enclosure. The equipment’s on/off status is detected based on the AC magnetic field that is generated when the motors are running. Measurements provide insight into the hours of operation of the motor. They should be taken at one-hour intervals. Motor runtime measurements should be paired with the spot measurement of true RMS power draw (kW) to calculate the energy consumption of the equipment. The duration of the long-term measurement should be a minimum of six weeks and data should be collected at one-hour intervals. Measurements should be taken when the system or component is operating under normal conditions. Type of Measurement Direct This is a direct measurement of motor runtime and determines the operating schedule of the motor. Measurement Equipment to Use The measurement equipment needed for this procedure is a motor on/off data logger. Refer to the FELL catalog to identify data loggers that measure motor runtime. The contents of this guide are largely based off of the UX90-004 Onset HOBO Motor runtime logger, which can be found and borrowed through NYC Energy Tools. When a motor turns on, it generates a magnetic field. The motor on/off sensor operates by detecting the field and recording the length of time for which it is detected. The runtime period is considered complete once the motor turns off, the magnetic field weakens, and the sensor no longer detects the field. The logger records the amount of time the field was detected for (i.e., the motor was running) and documents the duration in its internal storage for each hour interval. A separate data logger should be used for each motor if more than one is measured. Please note that loggers require setup with a computer or phone using the manufacturer’s proprietary software prior to installation and measurement logging, and that older loggers require the use of a cable to connect to a computer. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement Steps 1. Prepare for Data Acquisition Use the manufacturer’s software to set up and launch the logger(s). Refer to the equipment’s user manual for detailed instructions on how to set up the logger. Logging interval: 1-hour Date and time to start logging Date and time to stop logging Value to measure: Runtime (minutes) An example of how to setup the UX90-004 Onset HOBO Motor runtime logger is shown in the video below. Figure 1. How to configure the motor on/off data logger on HOBOware. (Click to Start Video) 2. Install Equipment Confirm that the motor is operational. Place the data logger on the motor casing in a non-hazardous location. When the motor is running, calibrate the data logger (refer to the data logger’s user manual for instructions and requirements for calibration). Visually confirm that the logger is recording, and that the sensor is accurately identifying whether the motor is running. Figure 2. How to calibrate and install the motor on/off data logger on a motor. (Click to Start Video) 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment and use a laptop or phone with the manufacturer’s proprietary software installed to do the following: Do not remove the logger. If you remove the logger, you may need to start over with the setup and installation process. If necessary, connect the logger to the laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with the proprietary software or Microsoft Excel after exporting the dataset as a csv file. Determine whether the results align with the expected operation of the system or component based on observed operational patterns or known equipment schedules. Figure 3. How to check data of runtime loggers using HOBOware. (Click to Start Video) 4. Retrieve Measurement Equipment and Download All Final Data After verifying that the logger is collecting data, do the following: Allow the logger to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the logger from the motor. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Use the proprietary software to stop the logger and end data collection. Download all data from the logger and save the file in the .csv format for analysis. Figure 4. How to extract data from the logger and convert to .csv file on HOBOware. (Click to Start Video) Troubleshooting Our Measurement Equipment Problem 1: Detecting the Signal from Another Motor Solution: If the logger detects a signal from a nearby motor instead of the motor of interest, wait until the nearby motor turns off before calibrating the logger. This prevents interference from the electromagnetic field generated by the larger motor. Problem 2: Unexpected Readings Solution: Confirm with building staff that the motor has been operating as expected. Verify that the logger is calibrated and re-calibrate the equipment if necessary. Ensure that the logger is installed correctly (i.e., placed directly on the motor housing, and not on the base of the motor).

Use this technique to measure the hours of operation of a pump, fan or compressor motor with a data logger.


Flow and Pressure

Water Flow Rate
Understanding Water Flow Rate Measurements This technique uses a flow meter to measure the flow rate of a fluid within a pipe. The technique is typically used on water loop systems to measure the flow through heating and cooling plants, but it can also be used to measure the flow rate of other fluids (e.g., glycol). Measurement data is used to calculate how much heat is added or removed by the heating or cooling plant, energy/heat recovered by a liquid-to-liquid heat recovery system, and heating energy for domestic hot water. This measurement technique is preferred over the pump curve method because it measures flow rate directly and removes the need for additional calculations. The pump curve method requires the differential pressure between the discharge and suction of all pumps for a water loop system and the technical specifications of all pumps. However, a major challenge with this technique is that measurements must be taken on a straight pipe; the flow meter should not be installed near elbows or T-shaped pipes. Additionally, piping systems are typically covered with thick layers of insulation to minimize heat losses. To install the flow meter, the insulation must be cut and removed (Figure 2). CUNY BPL recommends conducting a site survey to examine the piping system in the facility and determine whether taking a direct flow measurement is possible. Measurements should be taken at one-hour intervals; not instantaneously. When taking one-hour measurements, the flow meter detects the flow several times every hour and stores the average value. Sometimes flow can fluctuate over a one-hour period, and the instantaneous flow value will not indicate that change. The duration of the long-term measurement and when to measure is dependent on the system and the operation of the building. For water loop systems that operate year-round and are driven by outside air temperature (F), one full year of measurement (12 consecutive months, 52 consecutive weeks, or 365 consecutive days) is required for the baseline and one full year for the reporting period. For water loop systems that operate during a particular season, the full season must be measured for the baseline and reporting periods. For water loop systems that are not driven by OAT, it is recommended to measure flow rate for a minimum of six weeks. Measurements should be taken when the system or component is operating under normal conditions. Type of Measurement Direct Measurement Equipment to Use The measurement equipment needed for this procedure is an ultrasonic flow meter. Flow meters work by emitting ultrasonic sounds from the transducers to the pipe surface and into the fluid. Transducers operate in sets of two, and both transducers act as transmitters and receivers of ultrasonic sound. The time it takes for sound to travel from one transducer to the other is called transit time. Flow rate is calculated by the meter using the transit time. This is the commonly used method to measure water or other liquids in a pipe. Refer to the NYC Energy Tools catalog to identify the correct flow meters for your project. The sensors of the ultrasonic flow meters available are clamp-on so there is no need to drill into the piping. By default, some flow meters are set to measure the properties of water. If glycol or other liquids will be measured, refer to the user manual and change the settings of the meter to measure the fluid in the system. The contents of this guide are largely based off the DXN Portable Ultrasonic Measurement System, which can be found and borrowed through the NYC Energy Tools field equipment library. Certain fluids contain moving particles, such as bubbles or solid material. To accurately measure the flow rate of these fluids, some flow meters measure the transit time using the doppler effect. The moving particles in the fluid cause the ultrasonic sound to shift in frequency (Hz), and the shift in frequency is directly related to the speed of the moving particles. Transducers used in this scenario are known as doppler transducers. To ensure proper installation and avoid signal interference or data loss, manufacturers such as Instruments Direct Inc. recommend installing the flow meter on a straight section of pipe, positioned at least 10 to 15 times the pipe’s external diameter away from an elbow. Please note that certain flow meters offered at the FELL require setup with a computer or phone using the manufacturer’s proprietary software prior to installation. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement Steps 1. Prepare for Data Acquisition Identify the location where the flow meter will be installed. Refer to the equipment’s user manual for detailed instructions on how to set up the meter(s). Logging interval: 1-hour (for variable speed pumps) Date and time to start logging Date and time to stop logging Value to measure: Water flow rate (GPM) Confirm if properties of fluid matches with the fluid to be measured Figure 1. Piping covered with insulation for a cooling plant. This is the location where the ultrasonic flow meter will be installed. 2. Install Equipment Confirm that the equipment is operational. Some piping systems have a layer of insulation to minimize heat loss. There are scenarios in which the insulation must be cut to install the transducers of the flow meter. Consult with personnel who work in the facility to determine if this is appropriate. See Figure 4 for reference. If installing the flow meter is not possible, consider using the pump curve method to determine flow rate of the fluid. Refer to the user manual of the measurement equipment to determine how to install the transducers. Figure 2. Insulation is being removed and the piping is exposed. Figure 3. Insulation is fully removed for a section of the piping. Figure 4. The transducers of the ultrasonic flow meter are being installed on the exposed piping. The ultrasonic flow meter in use is the DXN Portable Ultrasonic Measurement System. 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment to do the following: Do not remove the logger. If you remove it, you may need to start over with the setup and installation process. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with the software or Microsoft Excel after exporting the dataset as a .csv file. Please note that the format file may vary based on the measurement equipment. Determine whether measured results align with the expected operation of the system or component. Figure 5. Retrieve data screen on the DXN Portable Ultrasonic Measurement System. For this meter, a USB storage device is connected to the back of the meter. 4. Retrieve Measurement Equipment and Download All Final Data After verifying the meter is collecting data do the following: Allow the meter to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the meter. If necessary, connect the meter to a laptop or phone via USB cable. Otherwise, use the software to connect with the logger via Bluetooth. If applicable, use the proprietary software to stop the meter and end data collection. Download all data from the meter and convert to csv file format for analysis. Figure 6. Final data table in .csv format. Data was extracted from the DXN Portable Ultrasonic Measurement System and exported for analysis. Troubleshooting Our Measurement Equipment Problem 1: Presence of Turbulence Turbulence occurs when a fluid flows across an obstacle or a sharp corner. It can also occur if the fluid flows at a high speed due to drag forces between the fluid and the piping. The flow meter cannot accurately measure fluid flow if turbulence is present. Solution: Install the flow meter away from elbow pipes, as the sharp corner will cause turbulence. A rule of thumb is to place the meter on straight piping at least 10 to 15 pipe diameters away from the elbow. Problem 2: Data Accuracy and Measurement Interferences Solution: Depending on the type of flow measurement (i.e., transit time or doppler), the transducers must be installed in a specific position on the pipe. refer to the user manual for details. For transit time measurements, the transducers must be a certain distance from each other as determined by the size of the pipe. For doppler measurements, the placement of the transducers depends on how much solid material is in the fluid. Remove any insulation from the pipe and wipe it with a rag to clean the surface. Couplant is a type of grease that must be applied to the sensor of the transducer. The couplant allows sound to travel faster and is necessary for the flow meter to detect a stronger signal. Without couplant, the sound waves generated by the meter will travel through the air at a slower speed, causing the meter to detect a weaker signal. For more information, refer to the user manual and the resources section of this guide.

Use this technique to measure water flow rate in a piping system with an ultrasonic flow meter with logging capabilities.


Water Pressure and Pump Curve
Understanding Water Pressure and Pump Curve Measurements This technique uses water pressure measurements to infer the water flow rate (in GPM) for a pump. This is called the pump curve method because it uses the pump curve, pressure data, and technical specifications of a pump to determine the water flow rate, as illustrated in Figure 1. A water loop system can have multiple pumps, and the water flow rate for each pump must first be determined and then summed to obtain the total flow rate of the water loop. Measurement data is used to calculate how much heat is added or removed by the heating or cooling plant. Data is also used to calculate energy/heat recovered with a liquid-to-liquid heat recovery system. Water pressure measurements are taken at the inlet (suction) and outlet (discharge) sides of a pump. To measure water pressure, CUNY BPL recommends using a programmable data logger with pressure transducers installed on the access ports of the piping network. This is preferred over a pressure gauge reading because the pressure gauge introduces greater measurement error. This technique should be used only if direct measurement of water flow rate with a flow meter is not possible. To properly use this technique, you need the pump impeller size, model number, and pump curve, as well as the information on the pump motor nameplate, such as the horsepower and efficiency (for each pump in the water loop)–in addition to the pressure measurements. Without this information, this technique cannot be executed. Depending on how the piping network is designed in the facility, a combination of a direct measurement of water flow rate and this measurement technique can be used. Measurements should be taken at one-hour intervals; do not use instantaneous values. For water loop systems that operate year-round and are driven by outside air temperature (OAT), one full year of measurement (12 consecutive months, 52 consecutive weeks, or 365 consecutive days) is required for the baseline and one full year for the reporting period. For water loop systems that operate during a particular season, the full season must be measured for the baseline and reporting periods. For water loop systems that are not driven by OAT, it is recommended to measure flow rate for a minimum of six weeks. Measurements should be taken when the system or component is operating under normal conditions. Figure 1 illustrates a typical pump curve with the flow rate (in GPM) marked on the horizontal axis and total head (in meters) marked on the vertical axis. Flow rate was determined by applying the pump impeller size and the total feet of head to the pump curve. Type of Measurement Proxy Figure 1. A typical pump curve marked with the determined flow rate on the bottom axis. Total head is calculated by taking the difference between discharge and suction pressure and multiplying it by a constant. Design FT, design GPM, pump RPM, and pump horsepower are all obtained from the nameplate on the pump or from the technical specifications for that pump model. \begin{equation*} \Delta P = Discharge \hspace{2mm} Pressure - Suction \hspace{2mm} Pressure\end{equation*} \begin{equation*} Total \hspace{2mm} Head = \Delta P * 2.31 Pressure\end{equation*} Where, $\Delta P =$ differential pressure across the pump, psi $Discharge \hspace{2mm} Pressure =$ water pressure leaving the pump, psi $Suction \hspace{2mm} Pressure =$ water pressure entering the pump, psi $Total \hspace{2mm} Head =$ operating pressure of the pump converted from psi, feet $2.31 =$ constant equivalent to one pound of pressure per in $^2$ of water (at 60 degrees F), feet/psi Measurement Equipment to Use The measurement equipment needed for this procedure is a data logger with pressure transducers. The contents of this guide are largely based off of Onset HOBO UX120-006M data logger and the Ashcroft Pressure Transducer, which can be found and borrowed through the FELL. The Ashcroft Pressure Transducer measures voltage between 0V and 5V. The pressure transducer connects to the UX120-006M data logger which then converts the voltage signal to pressure in PSI units. Please refer to our video instructions for details on how to configure the UX120-006M to detect voltage and convert to pressure. CUNY BPL recommends using this equipment, rather than the on-site pressure gauge, to determine the pump flow to reduce measurement error. One pressure transducer should be used for each side of the pump. Heating and cooling plants can have different pump configurations, such as primary-only and primary-secondary pumps. Additionally, pumps can operate at constant speed or variable speed. It is important to identify the pump configuration and number of pumps for the plant so enough data loggers and transducers are borrowed from the FELL. Please note that loggers require setup with a computer or phone using the manufacturer’s proprietary software prior to installation and measurement logging, and that older loggers require the use of a cable to connect to a computer. Refer to the measurement equipment’s user manual for a detailed description of setup requirements. Measurement Steps 1. Prepare for Data Acquisition Identify the temperature (hot or cold) of the pipes that will be measured. Use the manufacturer’s software to set up the logger. Refer to the user manual for detailed instructions on how to set up the logger. Logging interval: 1-hour Date and time to start logging Date and time to stop logging Values to measure: voltage (V) or pressure (psi)1 Activate input channels on the logger Type of sensor Sampling interval: 1-second Figure 2. How to setup 4-channel analog logger with CT to measure water pressure and pump curve. (Click to Start Video) 2. Install at the Site Confirm that the equipment is operational. Locate the pressure gauges that are installed on the suction and discharge sides of the pump, (Figure 3). Connect the transducers to the data logger. Place the data logger near the pipes, avoiding placing the logger on the pipe itself. Confirm that the pressure gauge has a stop-valve to prevent water from flowing. If there is no stop valve on the piping system, consider using the direct water flow measurement. Remove the stop-valve and replace it with a T-shaped valve to stop the flow of water, as shown in Figure 3. Connect the transducer to the T-shaped valve. To avoid leaks, wrap Teflon tape around the installed equipment. Figure 3 illustrates a pressure gauge installed on an access port to the return chilled water line of a water-cooled chilled water plant. Notice the stop valve handle to the bottom right of the pressure gauge. This is used to stop the flow of water. Will Update the below video once correct video is found -- Figure 3. How to install the 4-channel analog logger with CT onsite. (Click to Start Video) -- 3. Verify Data is Being Collected Wait 24-48 hours to verify data collection. Return to the location of the measured equipment and use a laptop or a phone with manufacturer’s propriety software installed to do the following: Do not remove the logger or sensors. If you remove the logger, you may need to start over with the setup and installation process. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to connect with the data logger via Bluetooth. Analyze the data with a plot graph. This can be done with proprietary software or Microsoft Excel after exporting the dataset as a .csv file. Determine whether the results align with the expected operation of the system or component based on observed operational patterns or known equipment schedules. Figure 4. How to check the data of loggers using HOBOware. (Click to Start Video) 4. Retrieve Measurement Equipment and Download All Final Data After verifying the logger is collecting data, do the following: Allow the logger to collect data for the remainder of the measurement period. After the measurement period has concluded, remove the transducers and data logger. If necessary, connect the logger to a laptop or phone via USB cable. Otherwise, use the software to Stop the logger and end data collection. Download all data from the logger and save the file in the .csv file format for analysis. Figure 5. How to extract the data from the logger using HOBOware. (Click to Start Video) Troubleshooting Our Measurement Equipment Problem: the logger is measuring unexpected values Solution: Verify that the logger is calibrated. Re-calibrate the equipment if necessary. Footnotes This is dependent on the measurement capability of the chosen logger. ↩︎

Use this technique to measure the pressure differential across pumps at one-hour intervals with data loggers. Data can be used to infer the water flow rate …


All Calculations

Calculations use measurement data to determine key energy-related metrics, such as total energy consumption, heat transfer, and efficiency rates. They can also be used to assess environmental impacts, including greenhouse gas emissions. More Overall, calculations help interpret the data, enabling more informed decisions for energy management and sustainability goals. Each page includes downloadable, spreadsheet-based calculators along with detailed instructions for using them to estimate the annual energy consumption of systems or components. Read more about each calculation below. Less

Energy Consumption

Cooling Tower Fans Energy Consumption
Introduction This methodology applies to evaporative cooling towers and the ECM is the installation of VFDs on the fan motors. In the pre-retrofit condition, a single- or two-speed fan in each cooling tower cell is run at a constant speed. There are several operating modes for a cooling tower based upon how much variation is possible with the fan speeds. Cells are turned on or off depending on how much cooling is needed in the building. With two-speed fans, operational optimization occurs by staging each cell to turn on sequentially at low speed until all cells are on, and then begin turning the fans to full speed as the load increases. With single-speed fans, each cell is turned on as the load increases. In a retrofit with VFDs, the fans in all cells are run simultaneously and their speed is modulated based on the cooling load. As fan power is the cube of the fan speed, energy can be saved by running the fans at lower speeds. The speed modulation is controlled in three possible modes: Maintaining a constant condenser water entering temperature Maintaining a constant approach temperature Minimizing overall system power consumption This methodology only covers the measurement of energy consumption with respect to maintaining a constant condenser water entering temperature. Regardless of the operating sequence of the cells or the speed of the fans, there is usually a minimum water flow per cell and minimum flow per chiller that must be maintained. This guide assumes that the pre- and post-retrofit flow rates through the cooling tower do not change, as would be expected if a VFD was installed on the condenser water pump at the same time as the VFDs on the fans. Calculators Table 1. Cooling tower (CT) fans energy calculators. Calculator (Downloadable Files) Description Required Data To Use This Calculator Constant Speed CT Fan Energy Using Motor Runtime Data.xlsx Uses motor runtime data in seconds per hour from the cooling tower fan motor. Spot measurements of true RMS power is also required. Hourly motor runtime (seconds) One-time true RMS power (kW) Hourly Outdoor air temperature (F) Hourly Relative humidity (%) Constant One or Two Speed CT Fan Energy Using kW Data.xlsx Uses measured hourly kW data to estimate annual energy consumption for a constant-speed one- or two-speed cooling tower fan motor. Hourly true RMS power (kW) Hourly Outdoor air temperature (F) Hourly Relative Humidity (%) Constant One or Two Speed CT Fan Energy Using Electrical Current Data.xlsx Uses electric current data as a proxy for power to estimate the annual energy consumption of the cooling tower fans. Spot measurements of voltage and power factor are required. Hourly current (Amps) One-time true RMS power (kW) at different fan speeds Hourly Outdoor air temperature (F) Hourly Relative humidity (%) Variable Speed CT Fan Energy Using kW Data.xlsx Uses measured hourly kW data to calculate annual energy for a VS cooling tower fan Hourly true RMS power (kW) Hourly Outdoor air temperature (F) Hourly Relative humidity (%) Cooling Tower (CT) Fan Calculations Constant Speed CT Fan Energy Using Motor Runtime Data This calculation is for a cooling tower with constant-speed fans. Measured input data include spot measurements for true power and motor operational time per hour, as measured by motor on/off loggers on each fan in the tower. Convert seconds on per hour to average energy per hour (Worksheet: “Step 2. Energy Calcs”). Repeat for all fans and then sum to get a total for the cooling tower. Note that since the data loggers cannot be perfectly synced, the time stamp for the dataset for each fan will be different. The workbook time-aligns the datasets. \begin{equation} \overline{E}_{f}(t) = \frac{On_f(t)*P_f}{3600} \end{equation} \begin{equation} \overline{E}(t) = \sum_{f=1}^{F} \overline{E}_{f}(t) \end{equation} Where, $\overline{E}_{f}(t) =$ Average hourly fan motor energy on for each fan, f, kWh $t =$ Time index $On_{f}(t) =$ Measured time that motor is on for each fan, f, seconds $P_{f} =$ One-time power measurement for each fan, f, kW $\overline{E}(t) =$ Total average energy of all fan motors, kWh $F =$ Total number of fans Wet-bulb temperature is calculated from the measured dry-bulb temperature and measured relative humidity with the following empirical equation (Worksheet: “Step 3 Wetbulb Calcs”)1. \begin{equation} T_{wb} = T_{db}tan^{-1}[0.151977(RH+8.313659)^{1/2}] \end{equation} \begin{equation*} +tan^{-1}(T_{db}+RH) \end{equation*} \begin{equation*} -tan^{-1}(RH-1.676331)+0.00391838(RH)^{3/2} \end{equation*} \begin{equation*} *tan^{-1}(0.023101*RH) - 4.686035 \end{equation*} Where, $T_{wb} =$ Wet-bulb temperature, C $T_{db} =$ Dry-bulb temperature, C $RH =$ Relative Humidity, % To model the total fan energy at different wet-bulb temperatures, a second-order polynomial regression model is fitted, with total fan energy as a function of wet-bulb temperature (Worksheet: “Step 4 Regression”). \begin{equation} E(T_{wb}) = a*T_{wb}^{2} + b*T_{wb} + c \end{equation} Where, $E(T_{wb}) =$ Average hourly fan energy, kWh $a,b,c =$ Regression Coefficients Calculate operating hours (Worksheet: “Step 5 Daily Op Hrs”). \begin{equation} On(t) = \begin{cases} 1 & \text{if } \overline{E}(t) 0\\ 0 & \text{if } \overline{E}(t) = 0 \end{cases} \end{equation} \begin{equation} \overline{On}_{d,h} = \begin{cases} 1 & \text{if } \overline{E}(n) 0 \text{ for any } n \in N(d,h) \\ 0 & 0 \end{cases} \end{equation} Where, $On(t) =$ Cooling tower fans are on, binary $\overline{On}_{d,h} =$ Cooling tower is on for a given day of the week, d, and hour of the day, h, binary $N(d,h) =$ Total number of measured data points that fall on day of week, d, and hour of the day, h $n \in N(d,h) =$ Index for the subset of measured data points that fall on day of week, d, and hour of the day, h Calculate energy used for full year for each fan (Worksheet: “Step 6 Results”). \begin{equation} E = \sum_{t=1}^{8760} \overline{On}_{d,h}(t) * CoolingSeason(t) * E(T_{wb}(t)) \end{equation} Where, $E =$ Annual energy, kWh $CoolingSeason(t) =$ Does the given hour, t, fall within the cooling season, binary Constant One or Two Speed CT Fan Energy Using kW Data This calculation is for a cooling tower with constant-speed fans. Measured input data is average hourly power draw (in kW) as measured by a DENT power logger for each fan in the cooling tower. Total energy for each hour (Worksheet: “Step 2 Energy Calcs”). Since the measured power value (kW) is the average for an hour, it is equivalent to the energy for the hour (kWh). \begin{equation} \bar{E}(t) = \sum_{f = 1}^F \bar{E}_{f}(t) \end{equation} Where, $\bar{E}_{f}(t) =$ average hourly fan motor energy on for each fan, f, kWh $\bar{E} =$ total average energy of all fan motors, kWh $F =$ total number of fans in the cooling tower $t =$ time index The remainder of the workbook is the same as the motor runtime data workbook, and therefore uses Equations 3 through 7 to calculate the total annual energy. Constant One- or Two-Speed CT Fan Energy Using Electrical Current Data This calculation is for a cooling tower with constant-speed fans. Measured input data include hourly average current (in Amps) as directly measured by current transformers, and spot measurements for true power for each fan in the cooling tower. Total energy for each hour (Worksheet: “Step 2 Energy Calcs”). Since the measured current (Amps) is the average for an hour, Equation 10 yields the average energy per hour (kWh) assuming voltage is constant. \begin{equation} \overline{E}_{f}(t) = \frac{i_{f}(t) * P_{f}}{I_{f}} \end{equation} \begin{equation} \overline{E}(t) = \sum_{f=1}^{F} \overline{E}_{f}(t) \end{equation} Where, $\overline{E}_{f}(t) =$ Average hourly fan motor energy on for each fan, f, kWh $i_{f}(t) =$ Average hourly current for each fan, f, Amps $t =$ Time index $P_{f} =$ One-time power measurement for each fan, f, kW $I_{f} =$ One-time current measurement for each fan, f, Amps $\overline{E} =$ Total average energy of all fan motors, kWh $F =$ Total number of fans in the cooling tower The remainder of the workbook is the same as the motor runtime data workbook, and therefore uses Equations 3 through 7 to calculate the total annual energy. Variable Speed CT Fan Energy Using kW Data This calculation is for a cooling tower with variable-speed fans. Measured input data is average hourly power draw (in kW) as measured by a DENT data-logging power logger for one fan in the cooling tower. It is assumed that all the remaining fans are run at the same speed. Total energy for each hour (Worksheet: “Step 2 Energy Calcs”). Since the measured power value (kW) is the average for an hour, it is equivalent to the energy for the hour (kWh). \begin{equation} \overline{E}(t) = \overline{E}_{1}(t) * F \end{equation} Where, $\overline{E}_{1}(t) =$ Average hourly fan motor energy for the measured fan, kWh $\overline{E} =$ Total average energy of all fan motors, kWh $F =$ Total number of fans in the cooling tower $t =$ Time index The remainder of the workbook is the same as the motor runtime data workbook, and therefore uses Equations 3 through 7 to calculate the total annual energy. Further Reading For more information on the different types of fans found in AHU systems, please read “Application of Fans in Commercial HVAC Equipment” from the Carrier Corporation: https://www.utcccs-cdn.com/hvac/docs/1001/Public/0F/04-581070-01.pdf For more information on the different types of motors that can be used in an AHU retrofit, please read Chapter 7 (starts on page 91) of the Premium Efficiency Motor Selection and Application Guide from the U.S. Department of Energy: https://www.energy.gov/sites/prod/files/2014/04/f15/amo_motors_handbook_web.pdf#page=91 For general information on Option A M&V guides, please read section 4.2 (starts on page 23) of “M&V Guidelines: Measurement and Verification for Performance-based Contracts Version 4.0” from the U.S. Department of Energy: https://www.energy.gov/sites/prod/files/2016/01/f28/mv_guide_4_0.pdf#page=23 Footnotes Stull, R., “Wet-Bulb Temperature from Relative Humidity and Air Temperature”, J. of the American Meteorological Society, Nov 2011, pp. 2267-2269 ↩︎

Estimate the annual energy consumption of single-speed or variable-speed cooling tower fans for evaporative cooling towers.


Fan Motor Energy Consumption
Introduction This methodology applies to fan motors that operate at constant or variable speed. Fan motors exist in many building systems including air handling units, energy recovery ventilation units, condensers in an air-cooled chiller, and many others. The calculators provided in this section use equations that estimate the annual energy consumption of a fan motor regardless of the system of which it is part. The exception to this is cooling tower fans, which have their own methodology here The type of data that is measured from the fan motor will determine the calculator to use. Calculators Table 1. Fan motor energy calculators Calculator (Downloadable Files) Description Required Data To Use This Calculator Constant Speed Fan Energy Using Motor Runtime Data.xlsx Uses motor runtime (in seconds) and true RMS power (kW) data to estimate annual energy consumption of a CSCV single-speed fan motor. This calculator can work with data from two fans, e.g., if you measured a supply and return fan in an AHU use this calculator to estimate the total annual energy consumption of the AHU. Data from both fans must be in the same format. Hourly motor runtime (seconds) One-time true RMS power (kW) Constant One- or Two- Speed Fan Energy Using kW Data.xlsx Uses measured hourly kW data to estimate annual energy consumption for a constant-speed one- or two-speed fan motor. Hourly true RMS power (kW) Constant One- or Two- Speed Fan Energy Using Electrical Current Data.xlsx Uses hourly current data (in amperes) and true RMS power (kW) data to estimate annual energy consumption of a CSCV two-speed fan motor. This calculator can work with data from two fans (e.g., if you measured a supply and return fan in an AHU, use this calculator to estimate the total annual energy consumption of the AHU). Data from both fans must be in the same format. Hourly current (amperes) One-time true RMS power (kW) Constant One- or Two- Speed Fan Energy Using Motor Speed Data.xlsx Uses hourly motor speed data obtained from the VFD or BMS and spot measurement data of kW to estimate the annual energy consumption of a constant-speed one- or two-speed fan motor. Hourly motor speed (RPM) One-time measurement of true RMS power (kW) Variable Speed Fan Energy Using kW Data.xlsx Uses hourly true RMS power to calculate hourly energy consumption then estimate the annual energy consumption of a VSVV fan motor. This calculator can work with data from two fans (e.g., if you measured a supply and return fan in an AHU, use this calculator to estimate the total annual energy consumption of the AHU). Data from both fans must be in the same format. Hourly true RMS power (kW) Hourly outside air temperature (F) Fan Motor Calculations Constant Speed Fan Energy Using Motor Runtime Data This calculation tool is for a constant speed, constant volume system. Measured input data include spot measurements for true power and motor operational time per hour, as measured by motor on/off loggers for the supply and return fans in the Fan Motor. Convert the fan runtime from seconds per hour to a percentage of the hour the fan is operating (Worksheet: “Step 2. Percent Runtime Calc”) for both supply and return fans. \begin{equation} \%FanOn_{f}(t_{f}) = \frac{On_{f}(t_{f})}{3600} \end{equation} Where, $\hspace{5mm} \%FanOn_{f}(t_{f}) =$ Percent of an hour that the motor is on for either supply or return fan, f, % $\hspace{5mm} On_{f}(t_{f}) =$ Measured time that motor is on for either supply or return fan, f, in seconds $\hspace{5mm} t_{f} =$ Index for each measured data point for either supply or return fan, f Average % hour motor is on for each hour, h, of each day of the week, d (Worksheet: “Step 3. Daily Avg Runtime Calcs”). \begin{equation} \overline{\%FanOn}_{d,h,f} = \frac{\sum_{n_{f}}^{N_{f}(d,h)} \%FanOn_{f}(N_{f})}{N_{f}(d,h)} \end{equation} Where, $\overline{\%FanOn}_{d,h,f} =$ Average % time motor is on per hour for given day of week, d, and hour of day, h, for either supply of return fan, f, % $N_{f}(d,h) =$ Total number of measured data points that fall on day of week, d, and hour of day, h, for either supply or return fan, f $n_{f} \in t_{f}(d,h) =$ Index for the subset of measured data points that fall on day of week, d, and hour of the day, h, for either supply or return fan Find average hours per day fan is on (Worksheet: “Step 4. Results”). \begin{equation} \overline{HrsOn}_{d,f} = \sum_{h=0}^{23} \overline{\%FanOn}_{d,h,f} \end{equation} Where, $\overline{HrsOn}_{d,f} =$ Average hours per day for given day of week, d, for either supply or return fan, f, hours Calculate energy used for the simulation period that users input for each fan (Worksheet: “Step 4. Results”). \begin{equation} E_{f} = \sum_{d=1}^{7} \overline{HrsOn}_{d,f} * operating \hspace{2mm} weeks \hspace{2mm} per \hspace{2mm} year * P_{f} \end{equation} Where, $E_{f} =$ Annual energy for either supply or return fan, f, kWh $P_{f} =$ Measured power for either supply or return fan, f, kW Total energy used by Fan Motor (Worksheet: “Step 4. Results”). \begin{equation} E = E_{supply} + E_{return} \end{equation} Where, $E =$ Total energy usage for the Fan Motor, kWh Constant One or Two Speed Fan Energy Using kW Data This calculation tool is for a constant speed or two-speed, constant-volume system. Measured input data is average hourly power draw (in kW) as measured by a data logging power meter for the supply and return fans in the AHU. Average equivalent % hour motor is on full speed for each hour, h, of each day of the week, d, (Worksheet: “Step 3. Avg Day of Week Calcs”). \begin{equation} \bar{P}_{d,h,f} = \frac{\sum_{n_f = 1}^{N_f(d,h)} P_f(t_f)}{N_f(d,h)} \end{equation} Where, $\bar{P}_{d,h,f} =$ average motor power for given day of week, d, and hour of day, h, for either suply or return fan, f, kW $P_f(t_f) =$ measured motor power for either supply or return fan, f, kW $t_f =$ index for measured data points for either supply or return fan, f, datasets $N_f(d,h) =$ total number of measured data points that fall on day of week, d, and hour of day, h, for either supply or return fan, f $n_f \in t_f(d,h) =$ index for subset of measured data points that fall on day of week, d, and hour of day, h, for either supply or return fan, f Calculate energy used for the simulation period that users input for each fan (Worksheet: “Step 4. Results”). \begin{equation} E_f = \sum_{d = 1}^7 \sum_{h = 1}^24 \bar{P}_{d,h,f} * [\textit{operating weeks per year}] \end{equation} Where, $E_f =$ annual energy for either supply or return fan, f, kWh $\bar{P}_{d,h,f} =$ average motor power for given day of week, d, and hour of day, h, for either supply or return fan, f, kW Total energy used by the AHU (Worksheet: “Step 4. Results”). \begin{equation} E = E_{supply} + E_{return} \end{equation} Where, $E =$ total energy usage for AHU, kWh Constant One- or Two-Speed Fan Energy Using Electrical Current Data This calculation tool is for VFD-controlled fans that are operated at two speeds, as well as for a constant speed, constant volume system. Measured input data include hourly average current (in Amps), as directly measured by current transformers, and spot measurements for true power at both high and low speed operation for the supply and return fans in the Fan Motor. If the tool is used for a constant speed, constant volume system, then set the low speed input data to zeroes and enter the all the input data for high speed. Convert seconds fan is on per hour to percent fan is on per hour (Worksheet: “Step 2. Percent Runtime Calcs”) for supply and return fans. \begin{equation} \%FanOn_{high,f}(t_{f}) = \begin{cases} 100\% & \text{if } i_{high,f} * (1+\varepsilon) \begin{equation} \%FanOn_{low,f}(t_{f}) = \begin{cases} 100\% & \text{if } i_{f}(t_{f}) Where, $\%FanOn_{high,f}(i) =$ Percent of an hour that motor is running at high speed for either supply or return fan, f, % $\%FanOn_{low,f}(i) =$ Percent of an hour that motor is running at low speed for either supply or return fan, f, % $i_{f}(t_{f}) =$ Measured current for either supply or return fans, f, Amps $t_{f} =$ Index for each measured data point for either supply or return fans, f, datasets $i_{high,f} =$ One-time measured current at high speed setpoint for either supply or return fan, f, Amps $i_{low,f} =$ One-time measured current at the low speed setpoint for either supply or return fan, f, Amps $\varepsilon =$ Error tolerance to classify current as representing high speed or low speed operation Average % hour motor is on for each hour of each day of the week (Workseet: “Step 3 Daily Avg Runtime Calcs”). \begin{equation} \overline{\%FanOn}_{s,d,h,f} = \frac{\sum_{n_f=1}^{N_{f}(d,h)} \%FanOn_{s,f}(n)}{N_{f}(d,h)} \end{equation} Where, $\overline{\%FanOn}_{s,d,h,f} =$ Average % time motor is at either low speed or high speed setpoint, s, per hour for given day of wekk, d, and hour of the day, h, for either supple of return fan, % $N_{f}(d,h) =$ Total number of measured data points that fall on day of week, d, and hour of day, h, for either supply or return fan, f $n_{f} \in i_{f}(d,h) =$ Index for subset of measured data points that fall on day of week, d, and hour of day, h, for either supply or return fan, f Find average hours per day fan is on (Worksheet: “Step 4. Results”). \begin{equation} \overline{HrsOn}_{s,d,f} = \sum_{h=0}^{23} \overline{\%FanOn}_{s,d,h,f} \end{equation} Where, $\overline{HrsOn}_{s,d,f} =$ Average hours per day for given day of week, d, for either supply or return fan, f, hours Calculate energy used for full year for each fan (Worksheet: “Step 4. Results”). \begin{equation} E_{f} = \sum_{d=1}^{7} (\overline{HrsOn}_{low,d,f} * P_{low,f} + \overline{HrsOn}_{high,d,f} * P_{high,f}) * 52 [weeks \hspace{2mm} per \hspace{2mm} year] \end{equation} Where, $E_{f} =$ Annual energy for either supply or return fan, f, kWh $P_{s,f} =$ Measured power for either the low speed or high speed setpoint, s, and for either supply or return fan, f, kW Total energy used by Fan Motor (Worksheet: “Step 4. Results”). \begin{equation} E = E_{supply} + E_{return} \end{equation} Where, $E =$ Total energy usage for the Fan Motor, kWh Constant One- or Two-Speed Fan Energy Using Motor Speed Data This calculation tool is for VFD-controlled fans that are operated at two speeds. Measured input data include hourly average motor speed (in RPM) as downloaded from a BAS or a VFD, and spot measurements for true power at both high and low speeds for supply and return fans in the AHU. Convert the fan runtime from seconds per hour to a percentage of the hour the fan is operating (Worksheet: “Step 2. Percent Runtime Calc”) for both supply and return fans. \begin{equation} \%FanOn_{high,f}(t_{f}) = \begin{cases} 100\% & \text{if } S_{high,f} * (1+\varepsilon) \begin{equation} \%FanOn_{low,f}(t_{f}) = \begin{cases} 100\% & \text{if } S_{f}(t_{f}) Where, $\%FanOn_{high,f}(i) =$ percent of an hour that motor is running at high speed for either supply or return fan, f, % $\%FanOn_{low,f}(i) =$ percent of an hour that motor is running at low speed for either supply or return fan, f, % $S_f(t_f) =$ measured speed from VFD for either supply or return fan, f, rpm $t_f =$ index for each measured data point for either supply or return fan, f, datasets $S_{high,f} =$ high speed setpoint for either supply or return fan, f, rpm $S_{low,f} =$ low speed setpoint for either supply or return fan, f, rpm $\varepsilon =$ error tolerance to classify current as representing high-speed or low-speed operation The remaining calculations for this workbook are Equations (12), (13), (14) and (15), as described in the section for the “Two-speed VFD-controlled Fans OR Constant Speed, Constant Volume Fans Using a Current Transformer” workbook. Variable Speed Fan Energy Using kW Data This calculation tool is for VFD-controlled fans that are operated at different speeds proportional to the heating/cooling load. Because the heating/cooling load of a facility is mainly affected by outdoor air temperature (OAT), this data must be collected as well. Measured input data include average hourly power draw (kW) and average hourly OAT. Perform second-order polynomial regression analysis of true RMS power as a function of OAT. (Worksheet: “Step 3. Regression”) for supply and return fans. \begin{equation} P_{f}(OAT) = a*OAT^{2} + b*OAT + c \end{equation} Where, $P_{f} =$ Average hourly true RMS Power for either supply or return fan, f, kW $a,b,c =$ Regression coefficients $OAT_{f} =$ Outdoor air temperature for either supply or return fan, f Determine if the supply and return motors are on or off at each measurement interval based on the input true RMS power values (Worksheets: “Step 4. Schedule Calcs”). \begin{equation} On_{f}(t_{f}) = \begin{cases} 1 & \text{if } P_{f}(t_{f}) 0\\ 0 & otherwise \end{cases} \end{equation} Where, $P_{f}(t_{f}) =$ Measured power $On_{f}(t_{f}) =$ Motor is on at time, $t_{f}$ for either supply or return fan, f, binary Average hourly % motor is on for each hour of each day of the week, for supply and return fan motors (Worksheet: “Step 5. Daily Avg Schedule Calc”). \begin{equation} \overline{\%FanOn}_{d,h,f} = \frac{\sum_{n_{f}=1}^{N_{f}(d,h)} On_{f}(t_{f})}{N_{f}(d,h)} \end{equation} Where, $\overline{\%FanOn}_{d,h,f} =$ Average % time motor is on per hour for given day of week, d, and hour of day, h, for either supply or return fan, f, % $N_{f}(d,h) =$ Total number of measured data points that fall on day of week, d, and hour od day, h, for either supply or return fan, f $n_{f} \in t_{f}(d,h) =$ Index for subset of measured data points that fall on day of week, d, and hour of day, h, for either supply or return fan, f Calculated energy (kWh) every hour based on normalized annual OAT for the supply and return fan motors (Worksheet: “Step 6. Energy Calcs,” column F & G). \begin{equation} E_{f} = \sum_{t=1}^{8760} P_{f}(OAT'(t))*\overline{\%FanOn}_{d,h,f}(t) \end{equation} Where, $E_{f} =$ Annual energy usage for either supply or return fan, f, kWh $OAT'(t) =$ Climate normal outdoor air temperature from National Weather Service at station closest to site, F Total energy used by Fan Motor (Worksheet: “Step 7. Results”). \begin{equation} E = E_{supply} + E_{return} \end{equation} Where, $E =$ Total energy usage for the Fan Motor, kWh

Estimate the annual energy consumption of variable speed and constant speed fan motors.


Lighting Plant and Systems Energy Consumption
Introduction These calculation tools developed by CUNY BPL are used to calculate annual energy consumption, but do not estimate savings. All calculation tools start by using input data (lighting runtime, AC current, etc.) to calculate hourly energy (kWh). Then data is averaged by hour of day and day of the week to get an approximation of how light fixtures operate during any hour of the week. Weekends and weekdays are extrapolated and summed to obtain a full-year estimate. To calculate savings, use the calculation tools with pre- and post-retrofit data and compare the energy consumption results. The calculation tools will extrapolate data to a full year regardless of how much input data is used, but a minimum of six (6) weeks of data at one-hour intervals is required to adhere to Measurement and Verification standards. If the total fixture inventory for the project is known, data can be used by the calculation tools to determine how much of the lighting load was directly measured, but this data is not necessary for the calculation tools to work. This is useful for someone who only measured a sample of fixtures as part of a sampling plan and wants to compare the annual estimates to the total lighting load. All lighting calculation tools generate an average hourly energy schedule using the input data. The schedule can be used to determine the interactive heating and cooling effects associated with the lighting retrofit, but it requires separate analysis. The first three methodologies are used when measuring electricity with data loggers and power meters to determine the annual energy consumption estimate of an electrical distribution system. The last methodology is used when measuring lighting runtime (operating schedule) to determine the annual energy consumption estimate of a lighting fixture system. Calculators Table 1. Lighting energy calculators Calculator (Downloadable Files) Description Required Data To Use This Calculator Lighting True RMS Power Output from Electric Panelboard.xlsx Uses the runtime and power of the panelboard to calculate the annual anergy consumption of a lighting electrical distribution system. Hourly lighting runtime Expected fixture wattage Fixture counts True RMS Power (total power draw) (kW) Lighting Electrical Current Output from Electric Panelboard.xlsx Uses voltage measurements alongside power, circuit amperage and current from the electrical panelboard to measure the total energy output from the system. Circuit voltage (V) Power factor (kW) Hourly current (amps) Lighting Electrical Current from Circuit Breakers.xlsx Uses voltage measurements alongside power, circuit amperage and current from circuit breakers to measure the total energy output from the system. Circuit voltage (V) Power factor (kW) Hourly current (amps) Lighting Inventory and Operating Schedule.xlsx Uses the panel energy use to calculate the operating schedule of the system. Lighting Panel Total Energy Use (kW) Lighting Energy Consumption Lighting True RMS Power Output from Electric Panelboard The following equations are used to calculate the annual energy consumption of a lighting electrical distribution system where energy in kilowatt hours (kWh) is measured at the output end of an electrical panelboard or switchgear. It is assumed that data is collected for six (6) weeks at one-hour intervals with a data-logging power meter that has the capacity to measure three-phase power. Find hourly average energy use for each hour of each day of the week (Worksheet: “Step 2. Avg Energy Calcs,” column J.) \begin{equation} \overline{kWh}_{d,h} = \frac{\sum_{1}^{N_{f}(d,h)} kWh_{n}}{N_{f}(d,h)} \end{equation} Where, $\overline{kWh}_{d,h} =$ Average energy of each hour for each day of the week (in kWh) $kWh_{n} =$ Measured hourly energy kWh from the data-logging power logger (in kWh) $N_{f}(d,h) =$ Total number of measuremed data points that fall on day of week, d, and hour the day, h Find total daily energy consumption (Worksheet: “Step 3. Results,” column C, “Step 3. Hourly Results.") \begin{equation} \overline{kWh}_{d} = \sum_{h = 0}^{23} \overline{kWh}_{d,h,n} \end{equation} Where, $\overline{kWh}_{d} =$ Sum of energy consumption for each day of the week (in kWh) $\overline{kWh}_{d,h} =$ Average energy of each h hour for each day of the week (in kWh) $h =$ Hour of the day where 0 is 12:00 a.m. and 23 is 11:00 p.m. Calculate the average energy consumption for weekdays (Worksheet: “Step 3. Results,” cell D3.) \begin{equation} \overline{kWh}_{Wd} = \frac{\sum_{d = 2}^{6} \overline{kWh}_{w,d}}{5} \end{equation} Where, $\overline{kWh}_{Wd} =$ Average energy consumption for weekdays (in kWH) $\overline{kWh}_{w,d} =$ Average energy of each n weekday (in kWh) $d =$ day of week: (2 = Monday, 3 = Tuesday, ... 6 = Friday) Calculate the average energy consumption for weekend days (Worksheet: “Step 3. Results,” cell D6.) \begin{equation} \overline{kWh}_{WEd} = \frac{\overline{kWh}_{we,1} + \overline{kWh}_{we,7}}{2} \end{equation} Where, $\overline{kWh}_{WEd} =$ Average energy consumption for each day of the week (in kWh) $\overline{kWh}_{we,d} =$ Average energy of each n weekend day (in kWh) $d =$ Day of week: (7 = Saturday, 1 = Sunday) Calculate the annual weekday energy consumption (Worksheet: “Step 3. Results,” cell E3.) \begin{equation} \overline{kWh}_{WdYr} = \overline{kWh}_{Wd} * (261 \hspace{2mm} weekdays \hspace{2mm} per \hspace{2mm} year - X) \end{equation} Where, $\overline{kWh}_{WdYr} =$ Annual weekday energy consumption (in kWh) $\overline{kWh}_{Wd} =$ Average weekday energy consumption (in kWh) $X =$ Number of weekdays that are adjusted to use weekend day average energy consumption Calculate the total weekend day energy consumption (Worksheet: “Step 3. Results,” cell E6.) \begin{equation} \overline{kWh}_{WEdYr} = \overline{kWh}_{WEd} * (104 \hspace{2mm} weekend \hspace{2mm} days \hspace{2mm} per \hspace{2mm} year + X) \end{equation} Where, $\overline{kWh}_{WEdYr} =$ Annual weekend day energy consumption (in kWh) $\overline{kWh}_{Wd} =$ Average weekday day energy consumption (in kWh) $X =$ Number of weekdays that are adjusted to use weekend day average energy consumption Calculate total annual estimate energy consumption (Worksheet: “Step 3. Results,” cell F3.) \begin{equation} \overline{kWh}_{anm} = \overline{kWh}_{WdYr} + \overline{kWh}_{WEdYr} \end{equation} Where, $\overline{kWh}_{ann} =$ Annual energy consumption (in kWh) $\overline{kWh}_{WdYr} =$ Annual weekday energy consumption (in kWh) $\overline{kWh}_{WEdYr} =$ Annual weekend day energy consumption (in kWh) If more than one electric panel or switchgear was measured, sum the annual energy consumption of all panels to find the total energy consumption of the electrical distribution system. \begin{equation} \overline{kWh} = \overline{kWh}_{{n}_{1}} + \overline{kWh}_{{n}_{2}} + ... \end{equation} Where, $\overline{kWh} =$ Total energy consumption for the electrical distribution system (in kWh) $\overline{kWh}_{n} =$ Total energy consumption for each panel or switchgear(in kWh) $n =$ Number of panels or switchgear measured Lighting Electrical Current Output from Electric Panelboard Lighting fixtures generally require single-phase power to operate, but electrical distribution systems are commonly three-phase. This methodology only applies to a three-phase, four-wire system (wye configuration). Additionally, the panelboard load must be balanced (all three electrical lines, or phases, must have the same current and line-to-neutral voltage). For an unbalanced load where voltage and current are not equal across the three lines, energy should be measured directly with a data-logging power logger capable of measuring a three-phase system. See section A.1. To estimate the energy consumption of the panelboard, including all fixtures served by it, current should be measured for all three electrical lines of the three-phase system. Current data should be at one-hour intervals and data should consist of an average sample of measurements1 for each one-hour interval. Power factor, line-to-line voltage, and true RMS power can be obtained from spot measurements with a handheld power meter. CUNY BPL recommends taking multiple spot measurements of those variables and averaging them (measure power factor at least three times at five-minute intervals and calculate the average–see Equation (9)). The average of the spot measurements helps reduce measurement uncertainty and should be used as inputs to the calculation tools. Equation (9) should be applied to power factor, voltage, and true RMS power. \begin{equation} \overline{PF} = \frac{PF_{t1} + PF_{t2} + PF_{t3} + PF_{tx}}{x} \end{equation} Where, $\overline{PF} =$ Average of measured power factor $PF =$ Spot measurement of power factor at the panelboard $t1 =$ First measurement $t2 =$ Second measurement, at least five minutes after the first measurement $t3 =$ Third measurement, at least five minutes after the second measurement $x =$ Number of spot measurements taken, at least five minutes apart \begin{equation} {V}_{avg,LL} = \frac{V_{t1}+V_{t2}+V_{t3}+V_{tx}}{x} \end{equation} Where, $V_{avg,LL} =$ Average line-to-line voltage $V_{t1} =$ First measurement of voltage $V_{t2} =$ Second measurement of voltage, at least five minutes after the first measurement $V_{t3} =$ Third measurement of voltage, at least five minutes after the second measurement $x =$ Number of spot measurements taken, at least five minutes apart Find the average current of the electrical distribution system for each hour interval. Current of all three phases is measured every hour. In this step, the average current of the panelboard is calculated for each hour interval. \begin{equation} I_{h,avg} = \frac{I_{1}+I_{2}+I_{3}}{3} \end{equation} Where, $I_{h,avg} =$ Average current for each hour interval (in Amps) $I_{1} =$ Hourly average current of line 1 (in Amps) $I_{2} =$ Hourly average current of line 1 (in Amps) $I_{3} =$ Hourly average current of line 3 (in Amps) Equation 11 calculates the three-phase power of the panelboard if line-to-line voltage is measured. If line-to-neutral voltage is measured (from hot wire to ground) the square root of 3 should be replaced with 3 and the line-to-neutral voltage should be used. Calculate three-phase power for each hour interval using the results from Equations (8), (9), and (10) (average current for each hour interval, average voltage, and average power factor). (Worksheet: “Step 2. Power Calcs,” column E, G, I.) \begin{equation} \overline{kW}_{h,3P} = \frac{\sqrt{3} * I_{h,avg} * V_{LL,avg} * PF}{1000} \end{equation} Where, $\overline{kW}_{h,3P} =$ Hourly three-phase power draw of the panelboard (in kW) $I_{h,avg} =$ Average current for each hour interval (in Amps) $V_{LL,avg} =$ Measured average line-to-line voltage (in V) $PF =$ Measured average power factor \begin{equation} \overline{kW}_{h,3P} = \sum_{n=1}^{3} \overline{kW}_{h,n} \end{equation} Where, $\overline{kW}_{h,3P} =$ Hourly three-phase power draw of the panelboard (in kW) $\overline{kW}_{h,n} =$ Hourly single-phase power for electrical line n (in kW) -- Calculate average energy consumption for each hour of the week (Worksheet: “Step 3. Avg Energy Calcs,” column C.) This equation helps to reduce the amount of data points to a week by taking the average of each hour for a given day of the week. In this step, the hourly power draw (kW) gets converted to hourly energy consumption (kWh) because data is in one-hour intervals. kWh = kW ∗ h, where h = 1. \begin{equation} \overline{kWh}_{d,h} = \frac{\sum_{1}^{N_{f}(d,h)} kW_{h,3P}}{N_{f}(d,h)} \end{equation} Where, $\overline{kWh}_{d,h} =$ Average energy consumption for each hour of each day of the week (in kW) $\overline{kW}_{h,3P} =$ Hourly three-phase power draw of the panelboard (in kW) $N_{f}(d,h) =$ Total number of data points that fall on day of week, d, and hour of the day, h Calculate total hourly energy consumption for a given day of the week (Worksheet: “Step 4. Results,” column C.) \begin{equation} \overline{kWh}_{d,w} = \frac{\sum_{h=0}^{23} \overline{kWh}_{d,h}}{h} \end{equation} Where, $\overline{kWh}_{d,w} =$ Average hourly energy consumption for a given day of the week of the three-phase panelboard (in kWh) $\overline{kWh}_{d,h} =$ Average energy consumption for each hour of each day of the week (in kWh) $h =$ Hour of the day where 0 is 12:00 a.m. and 23 is 11:00 p.m. Calculate the average energy consumption for weekdays (Worksheet: “Step 4. Results,” cell D3.) \begin{equation} \overline{kWh}_{Wd} = \frac{\sum_{d=2}^{6} \overline{kWh}_{w,d}}{5} \end{equation} Where, $\overline{kWh}_{Wd} =$ Average energy consumption for weekdays (in kWh) $\overline{kWh}_{wd,n} =$ Average hourly energy consumption of each n weekday (in kWh) $d =$ Day of week (2 = Monday, 3 = Tuesday, ..., 6 = Friday) $24 =$ Constant, hours per day $5 =$ Constant, weekdays per week Calculate the average energy consumption for weekend days (Worksheet: “Step 4. Results,” cell D6.) \begin{equation} \overline{kWh}_{WEd} = \frac{\overline{kWh}_{we,1} + \overline{kWh}_{we,7}}{2} \end{equation} Where, $\overline{kWh}_{WEd} =$ Average energy consumption for a weekend day (in kWh) $\overline{kWh}_{we,n} =$ Average energy consumption of each n weekend day (in kWh) $n =$ Day of week (7 = Saturday, 1 = Sunday) $2 =$ Constant, weekends per week Calculate the total annual weekday energy consumption (Worksheet: “Step 4. Results,” cell E3.) \begin{equation} \overline{kWh}_{WdYr} = \overline{kWh}_{Wd} * (261-X) \end{equation} Where, $\overline{kWh}_{WdYr} =$ Estimated annual weekday energy consumption (in kWh) $\overline{kWh}_{Wd} =$ Average energy consumption for weekdays (in kWh) $X =$ Number of weekdays that are considered holidays and adjusted to weekend day average energy consumption $261 =$ Constant, number of weekdays per year Calculate the total annual weekend day energy consumption (Worksheet: “Step 4. Results,” cell E6.) \begin{equation} \overline{kWh}_{WEdYr} = \overline{kWh} * (104+X) \end{equation} Where, $\overline{kWh}_{WEdYr} =$ Annual weekend day energy consumption (in kWh) $\overline{kWh}_{WEd} =$ Average weekend day energy consumption (in kWh) $X =$ Number of weekdays that are considered holidays and adjusted to weekend day average energy consumption $104 =$ Constant, number of weekend days per year Calculate total annual energy consumption of the panelboard \begin{equation} \overline{kWh}_{ann} = \overline{kWh}_{WdYr} + \overline{kWh}_{WEdYr} \end{equation} Where, $\overline{kWh}_{ann} =$ Estimated annual energy consumption of the panelboard (in kWh) $\overline{kWh}_{WdYr} =$ Estimated annual weekday energy consumption (in kWh) $\overline{kWh}_{WEdYr} =$ Estimated annual weekend day energy consumption (in kWh) If more than one panelboard was measured, sum the annual energy consumption of all panels to find the total energy consumption of all measured panelboards. \begin{equation} \overline{kWh} = \overline{kWh}_{{n}_{1}} + \overline{kWh}_{{n}_{1}} + ... \end{equation} Where, $\overline{kWh} =$ Total energy consumption of all measured panelboards (in kWh) $\overline{kWh}_{n} =$ Total energy consumption for each panelboard (in kWh) $n =$ Number of panelboards measured Lighting Electrical Current from Circuit Breakers Lighting fixtures generally require single-phase power to operate, but electrical distribution systems are commonly three-phase. When measuring individual circuits of a panelboard, it is essential to know which phase the circuit is connected to. A proper line-to-neutral connection is required to accurately measure the circuit’s voltage. This calculation tool requires the phase of the circuit to be specified in order to calculate annual energy consumption. If multiple circuits are measured and are connected to the same phase, then only the voltage of that phase is necessary Additionally, the user should ensure that the panelboard is balanced (i.e., all three electrical lines, or phases, must have the same current and line-to-line voltage). If the panelboard is not balanced, then it must be specified in the calculation tool (see worksheet ‘Step 1.1 Circuit Raw Data’). The following equations are used to calculate the annual energy consumption of a lighting electrical distribution system where AC current is measured at the output of circuit breakers in an electrical panelboard. AC current should be measured using a data logger with current transformers (e.g., Onset HOBO 4-channel analog logger and the Onset CTV-x current transformer sensors) for one or more circuit breakers; a group of circuits can be measured with a single transformer. Current data should be at one-hour intervals and data should be averaged with a sample of measurements1 for each one-hour interval. Obtain voltage from spot measurements (i.e., measured one time) with a power meter at the circuit breakers. It is assumed that multiple spot measurements are taken and averaged (e.g., measure line-to-neutral voltage for a circuit breaker three times at five-minute intervals and calculate the average) see Equation (20). The average value should be used with these equations to reduce measurement uncertainty. In this scenario, the line-to-neutral voltage is measured for a single circuit. If measuring multiple circuits, be sure to take multiple spot measurements of line-to-neutral voltage for all circuits. \begin{equation} V_{LN,avg} = \frac{V_{t1,n} + V_{t2,n} + V_{t3,n} + V_{tx,n}}{x} \end{equation} Where, $n =$ The electrical line that was measured of the three-phase system $V_{avg,n} =$ Average line-to-neutral voltage of a circuit in electrical line n $V_{t1,n} =$ First measurement of voltage for electrical line n $V_{t2,n} =$ Second measurement of voltage for electrical line n, at least five minutes after the first measurement $V_{t2,n} =$ Third measurement of voltage for electrial line n, at least five minutes after the second measurement $x =$ Number of spot measurements taken, at least five minutes apart For each circuit or group of circuits measured, calculate average power for each hour interval (Worksheet: “Step 2. Power Calcs.”). Power is calculated using line-to-neutral voltage and current of the circuit. \begin{equation} \overline{kW}_{h,n} = \frac{I_{n} * V_{LN,avg}}{1000} \end{equation} Where, $\overline{kW}_{h,n} =$ Average hourly power for a circuit n (in kW) $I_{n} =$ Measured average houry current for a circuit (in Amps) $V_{I,N,avg} =$ Measured average line-to-neutral voltage for a circuit (in V) Calculate average energy use for each hour of each day of the week (Worksheet: “Step 3. Avg Energy Calcs, column C, D, E, F.”). In this step, the hourly power draw (kW) gets converted to hourly energy consumption (kWh) because data is in one-hour intervals. kWh = kw * h, where h = 1. \begin{equation} \overline{kWh}_{d,h,c} = \frac{\sum_{1}^{N_{f}(d,h)} kW_{h}}{N_{f}(d,h)} \end{equation} Where, $\overline{kWh}_{d,h,c} =$ Average energy of each hour for each day of the week for each circuit (in kWh) $kW_{h} =$ Total power at each hour of each day of each week (in kW) $N_{f} =$ Total number of measured data points that fall on day of week, d, and hour of the day, h Calculate the sum of average hourly energy of all circuits (Worksheet: “Step 3. Avg Energy Calc” column G.) \begin{equation} \overline{kWh}_{d,h,n} = \sum_{c=1}^{4} \overline{kWh}_{d,h,c} \end{equation} Where, $\overline{kWh}_{d,h} =$ Total average energy for all circuits of each hour for each day of the week (in kWh) $\overline{kWh}_{d,h,c} =$ Total average energy for each hour for each day of the week for each circuit (in kWh) $c =$ Circuit that was measured Calculate total daily energy consumption for a given day of the wekk (Worksheet: “Step 4. Results,” column C.) \begin{equation} \overline{kWh}_{d,w} = \sum_{n=0}^{23} \overline{kWh}_{d,h} \end{equation} Where, $\overline{kWh}_{d,w} =$ Total average energy for each day of the week (in kWh) $\overline{kWh}_{d,h} =$ Total average energy of each h hour for each day of the week (in kWh) $h =$ Hour of the day where 0 is 12:00 a.m. and 23 is 11:00 p.m. Calculate the average energy consumption for weekdays in a week for all circuits (Worksheet: “Step 4. Results,” cell D3.) \begin{equation} \overline{kWh}_{WdCT} = \frac{\sum_{n=2}^{6} \overline{kWh}_{d,w}}{5} \end{equation} Where, $\overline{kWh}_{WdCt} =$ Average energy on a weekday (in kWh) $\overline{kWh}_{d,w} =$ Average hourly energy for each n weekday of the week (in kWh) $n =$ Day of week (2 = Monday, 3 = Tuesday, ..., 6 = Friday) $24 =$ Hours per day Calculate the average energy consumption for weekend days in a week for all circuits (Worksheet: “Step 4. Results,” cell D6.) \begin{equation} \overline{kWh}_{WEdCT} = \frac{\overline{kWh}_{1,w} + \overline{kWh}_{7,w}}{2} \end{equation} Where, $\overline{kWh}_{WEdCT} =$ Average energy on a weekend day (in kWh) $\overline{kWh}_{d,w} =$ Average hourly energy of each circuit for each n weekend day (in kWh) $n =$ Day of week (7 = Saturday, 1 = Sunday) $24 =$ Hours per day Calculate the total annual weekday energy consumption (Worksheet: “Step 4. Results,” cell E3.) \begin{equation} \overline{kWh}_{WdYr} = \overline{kWh}_{Wd} * (261 \hspace{2mm} weekdays \hspace{2mm} per \hspace{2mm} year - X) \end{equation} Where, $\overline{kWh}_{WdYr} =$ Annual weekday energy consumption (in kWh) $\overline{kWh}_{Wd} =$ Average weekly weekday energy consumption (in kWh) $X =$ Number of weekdays that are considered holidays and adjusted to weekend day average energy consumption Calculate the total annual weekend day energy consumption (Worksheet: “Step 4. Results,” cell E6.) \begin{equation} \overline{kWh}_{WEdYr} = \overline{hWh}_{WEd} * (104 \hspace{2mm} weekend \hspace{2mm} days \hspace{2mm} per \hspace{2mm} year + X) \end{equation} Where, $\overline{kWh}_{WEdYr} =$ Annual weekend day energy consumption (in kWh) $\overline{kWh}_{WEd} =$ Average weekly weekend day energy consumption $X =$ Number of weekdays that are considered holidays and adjusted to weekend day average energy consumption Calculate total annual estimated energy consumption. \begin{equation} \overline{kWh}_{ann} = \overline{kWh}_{WdYr} + \overline{kWh}_{WEDYr} \end{equation} Where, $\overline{kWh}_{ann} =$ Annual energy consumption (in kWh) $\overline{kWh}_{WdYr} =$ Annual weekday energy consumption (in kWh) $\overline{kWh}_{WEdYr} =$ Annual weekend day energy consumption (in kWh) Equation (26) is the annual energy consumption of the measured circuits for a panelboard. If additional circuits were measured for the same panelboard with a different data logger, be sure to consolidate the results (annual energy consumption) to obtain the total panelboard annual energy consumption. Additionally, if multiple panelboards were measured, be sure to sum up the annual consumption of all panelboards to obtain the total system energy consumption. Lighting Inventory and Operating Schedule The following equations are used to calculate the annual energy consumption of a lighting fixture system. This methodology does not require electrical measurements; only lighting runtime (operating schedule) of the fixtures. Runtime data is collected with a light logger that detects when a light source turns on and off. If multiple fixture types operate with the same schedule, the same runtime data can be used for calculations. This calculation tool can be used for different fixture types within a single space (e.g., an office space with five different types of fixtures). The number of fixtures of each type must be known as well as the respective power draw (refer to the manufacturer specifications of the lamps and ballasts). Calculate power draw of the fixture type. \begin{equation} kW_{fix1} = \frac{N * W_{fix1}}{1000} \end{equation} Where, $kW_{fix1} =$ Total power draw of single fixture type 1 (in kW) $W_{fix1} =$ Wattage of fixture type 1 (in W) $N =$ Number of fixtures of that type with the same operating schedule Convert fixture runtime measurements from seconds per hour to percent per hour (Worksheet: “Step 2. Percent Runtime Calcs”). \begin{equation} \%_{int} = \frac{t_{int}}{3600} \end{equation} Where, $\%_{int} =$ Percent per hour the fixtures are on $t_{int} =$ Measured number of seconds the fixtures are on in each hour interval (in seconds) $3600 =$ Constant, number of seconds in one hour Find the hourly average percentage for each day of the week the fixtures are on (Worksheet: “Step 3. Daily Avg Runtime Calcs”). \begin{equation} \%_{hourly} = \frac{\sum_{1}^{n} \%_{int,n}}{n} \end{equation} Where, $\%_{hourly} =$ Hourly average percentage the fixtures are on $\%_{int} =$ Percent per hour the fixtures are on $n =$ Number of data points that have the same hour of day and day of week Sum of runtime percentages for a given day of the week to determing the operating hours for that day (Worksheet: “Step 4. Results”). \begin{equation} \%_{daily} = \sum_{h=0}^{23} \%_{hourly,h} \end{equation} Where, $\%_{daily} =$ Daily average hours the fixtures are on $\%_{hourly} =$ Hourly average percentage fixtures are on $h =$ Hour of the day where 0 is 12:00 a.m. and 23 is 11:00 p.m. Convert the percentage to hours in order to determine hours per day fixtures are on in space being measured (Worksheet: “Step 4. Results”). \begin{equation} T_{daily} = \frac{\%_{daily}}{100} \end{equation} Where, $T_{daily} =$ Number of hours the fixtures are on for a given day (in hours) $\%_{daily} =$ Daily average hours in percent per day the fixtures are on Calculate the average energy use per weekday (Worksheet: “Step 4. Results”). \begin{equation} \overline{kWh}_{Wd,fix1} = \frac{\sum_{d=2}^{6} T_{Wd,fix1,d}}{5} * kW_{fix1} \end{equation} Where, $\overline{kWh}_{Wd,fix1} =$ Average energy consumption during weekdays for fixture type 1 (in kWh) $kW_{fix1} =$ Total power draw of single fixture type 1 (in kW) $T_{Wd,fix1,d} =$ Number of hours the fixtures are on for a given d weekday (in hours) $d =$ Day of week (2 = Monday, 3 = Tuesday, ..., 6 = Friday) Calculate the average energy use per weekend day (Worksheet: “Step 4. Results”). \begin{equation} \overline{kWh}_{WEd,fix1} = \frac{T_{We,fix1,1} + T_{We,fix1,7}}{2} * kW_{fix1} \end{equation} Where, $\overline{kWh}_{WEd,fix1} =$ Average consumption during weekend days for fixture type 1 (in kWh) $kW_{fix1} =$ Total power draw of single fixture type 1 (in kW) $T_{We,fix1,d} =$ Number of hours the fixtures are on for a given d weekend days (in hours) $d =$ Day of week (7 = Saturday, 1 = Sunday) Calculate the annual weekday energy consumption for the fixture type (Worksheet: “Step 4. Results”). \begin{equation} \overline{kWh}_{WdYr,fix1} = \overline{kWh}_{Wd,fix1} * (261 \hspace{2mm} weekdays \hspace{2mm} per \hspace{2mm} year - X) \end{equation} Where, $\overline{kWh}_{WdYr,fix1} =$ Annual weekday energy consumption of fixture type 1 (in kWh) $\overline{kWh}_{Wd,fix1} =$ Average energy consumption during weekdays for fixture type 1 (in kWh) $X =$ Number of weekdays that are adjusted to use weekend day average energy consumption Calculate the annual weekend energy consumption for the fixture type (Worksheet: “Step 4. Results”). \begin{equation} \overline{kWh}_{WEd,Yr,fix1} = \overline{kWh}_{WEd,fix1} * (104 \hspace{2mm} weekend \hspace{2mm} days \hspace{2mm} per \hspace{2mm} year + X) \end{equation} Where, $\overline{kWh}_{WEdYr,fix1} =$ Annual weekend day energy consumption of fixture type 1 (in kWh) $\overline{kWh}_{WEd,fix1} =$ Average energy consumption during weekend days for fixture type 1 (in kWh) $X =$ Number of weekdays that are adjusted to use weekend average energy consumption Calculate total annual estimated energy consumption for the fixture type (Worksheet: “Step 4. Results”). \begin{equation} \overline{kWh}_{ann,fix1} = \overline{kWh}_{WdYr,fix1} + \overline{kWh}_{WEdYr,fix1} \end{equation} Where, $\overline{kWh}_{ann,fix1} =$ Annual estimated energy consumption of fixture type 1 (in kWh) $\overline{kWh}_{WdYr,fix1} =$ Annual weekday energy consumption of fixture type 1 (in kWh) $\overline{kWh}_{WEdYr,fix1} =$ Annual weekend day energy consumption of fixture type 1 (in kWh) If multiple fixture types were measured find the sum of the annual estimated energy consumption for all fixture types (Worksheet: “Step 4. Results”). \begin{equation} \overline{kWh}_{ann} = \sum_{i=1}^{n} \overline{kWh}_{ann,{fix_{n}}} \end{equation} Where, $\overline{kWh}_{ann} =$ Total annual energy of all measured fixture types (in kWh) $\overline{kWh}_{ann,fix1} =$ Annual estimated energy consumption of each measured fixture type (in kWh) $n =$ Number of fixture types measured Hourly Results Worksheet Measurement data that is input into the calculation tools is used to generate an hourly energy consumption schedule for each hour in each day of the week. The schedule exists in the “Hourly Results” worksheet that is included in all four calculation tools. This data is useful to estimate the heating and cooling effects. CUNY BPL calculation tools do not calculate heating or cooling interactive effects. Further Reading For general information on Option A M&V guides, please read section 4.2 (starts on page 23) of “M&V Guidelines: Measurement and Verification for Performance-Based Contracts Version 4.0” from the U.S. Department of Energy: https://www.energy.gov/sites/prod/files/2016/01/f28/mv_guide_4_0.pdf#page=23 Richman, EE. (October 2012) “Standard Measurement and Verification Plan for Lighting Retrofit Projects for Buildings and Building Sites.” Richland, WA: Pacific Northwest National Laboratory. Richman, EE. (February 2016) “Measurement and Verification of Energy Savings and Performance from Advanced Lighting Controls.” Richland, WA: Pacific Northwest National Laboratory. Footnotes We recommend taking a sample of measurements and finding the average. The average value will be used to calculate annual energy consumption. As an example, the Onset HOBO 4-channel analog logger can measure a sample of current data at a predefined interval known as the sampling interval. If the logging interval is set to one-hour and the sampling interval is set to one-second, the logger will measure current every second for one hour then determine the average. The average will be stored in the logger as the one-hour interval measurement. This process will continue every hour for the duration of the measurement period. ↩︎

Estimate the annual energy consumption of a lighting plant.


Pump Motor Energy Consumption
Introduction This methodology applies to pump motors that operate at constant or variable speed. Pump motors are used to move water throughout the building for heating or cooling. The calculators provided in this section use equations that estimate the annual energy consumption of a pump motor, regardless of the system of which it is part. The type of data that is measured from the pump motor will determine the calculator to use. For more information on the type of data to collect, refer to table 1 in the next section. Calculators Table 1. Pump motor energy calculators Calculator (Downloadable Files) Description Required Data To Use This Calculator Constant Speed Pump Energy Using Motor Runtime Data.xlsx Uses motor runtime (in seconds) and true RMS power (kW) data to estimate annual energy consumption of a CSCV pump motor. Hourly motor runtime (seconds) One-time true RMS power (kW) Constant One or Two Speed Pump Energy Using kW Data.xlsx Uses hourly electrical current data and spot measurement data of kW to estimate the annual energy consumption for a constant speed one- or two-speed pump motor. Hourly true RMS power (kW) Constant One- or Two-Speed Pump Energy Using Electrical Current Data.xlsx Uses measured hourly kW data to estimate annual energy consumption for a constant speed one- or two-speed pump motor. Hourly electrical current (Amps) One-time measurement of true RMS power (kW) Variable Speed Pump Energy Using kW Data.xlsx Uses hourly true RMS power to calculate hourly energy consumption then estimate the annual energy consumption of a VSVV pump motor Hourly true RMS power (kW) Hourly outside air temperature (F) Variable Speed Pump Energy Using Motor Speed Data.xlsx Uses hourly motor speed data obtained from the VFD or BMS and spot measurements of kW to estimate the annual energy consumption of a variable-speed pump motor. Hourly motor speed (RPM) One-time measurement of true RMS power (kW) Pump Motor Calculations Constant Speed Pump Energy Using Motor Runtime Data This calculation tool is for a constant speed, constant volume system. Measured input data include spot measurements for true power and motor operational time per hour, as measured by motor on/off loggers. Convert seconds on per hour to percent on per hour (Worksheet: “Step 2. Percent Runtime Calcs”). \begin{equation} \%On(t) = \frac{On(t)}{3600} \end{equation} Where, $\%On(t) =$ Percent of an hour that the pump motor is on, % $On(t) =$ Measured time that pump motor is on, seconds $t =$ Index for each measured data point Average % hour motor is on for each hour of each day of the week (Worksheet: “Step 3. Daily Avg Runtime Calcs”). \begin{equation} \overline{\%On}_{d,h} = \frac{\sum_{n=1}^{N(d,h)} \%On(n)}{N(d,h)} \end{equation} Where, $\overline{\%On}_{d,h} =$ Average % time motor is on per hour for given day of week, d, and hour of the day, h, % $N(d,h) =$ Total number of measured data points that fall on day of week, d, and hour of the day, h $n \in t(d,h) =$ Index for the subset of measured data points that fall on day of week, d, and hour of the day, h Find the average hours per day pump is on (Worksheet: “Step 4. Results”). \begin{equation} \overline{HrsOn}_{d} = \sum_{h=1}^{24} \overline{\%On}_{d,h} \end{equation} Where, $\overline{HrsOn}_{d} =$ Average hours per day for given day of week, d, hours Calculate energy used for full year (Worksheet: “Step 4. Results”). \begin{equation} WeeksPumpOn = (DayOfYear(PumpOperationEndDate) \end{equation} \begin{equation*} - DayOfYear(PumpOperationStartDate)) * \frac{WeeksPerDay}{DaysPer Year}\end{equation*} \begin{equation} E = WeeksPumpOn * P\sum_{d=1}^{7} \overline{HrsOn}_{d} \end{equation} Where, $E =$ Annual pump energy, kWh $DayOfYear =$ Function to convert a date to the n^{th} day of the year $PumpOperationEndDate =$ Cooling season end date, mm/dd/yyyy $PumpOperationStartDate =$ Cooling season start date, mm/dd/yyyy $WeeksPumpOn =$ Pump operating time, weeks $WeeksPerYear =$ 52 $DaysPerYear =$ 365.24 $P =$ Measured pump power, kW Constant One- or Two-Speed Pump Energy Using kW Data This calculation tool is for a constant speed, constant volume pump. Measured input data is average hourly power draw (in kW) as measured by a DENT power logger. Average % hour motor is on for each hour of each day of the week (Worksheet: “Step 3. Avg Day of Week Calcs”). \begin{equation} \bar{P}_{d,h} = \frac{\sum_{n=1}^{N(d,h)} P(t)}{N(d,h)} \end{equation} Where, $\bar{P}_{d,h} =$ average motor power for given day of week, d, and hour of day, h, kW $P(t) =$ measured motor power, kW $t =$ index for measured data points $N(h,d) =$ total number of measured data points that fall on day of week, d, and hour of the day, h $n \in t(d,h) =$ index for subset of measured data points that fall on day of week, d, and hour of the day, h Calculate energy used for full year (Worksheet: “Step 4. Results”). WeeksPumpOn is from Equation 5. \begin{equation} E = WeeksPumpOn * \sum_{d = 1}^7 \sum_{h = 1}^{24} \bar{P}_{d,h} \end{equation} Where, $E =$ annual pump energy, kWh $WeeksPumpOn =$ Pump operating time, weeks Constant One- or Two-Speed Pump Energy Using Electrical Current Data This calculation tool is for a constant speed, constant volume pump. Measured input data include hourly average current (in Amps) as directly measured by current sensors, and spot measurements for true power. Convert average hourly current to percent on per hour (Worksheet: “Step 2. Percent Runtime Calcs”). \begin{equation} \%On(t) = \begin{cases} \frac{I(t)}{I_{max}} & \text{if } I(t) Where, $\%On(t) =$ percent of an hour that the pump motor is on, % $I(t) =$ measured time that pump motor is on, seconds $t =$ index for each measured data point $I_{max} =$ current measured at the maximum constnat speed, Amps Equations 3 to 5 are used to calculate the annual pump energy. Variable Speed Pump Energy Using kW Data This calculation tool is for VFD-controlled pumps that are operated at speeds proportional to the heating/cooling load as represented by proxy with OAT. Measured input data include average hourly power draw (kW) as measured by a DENT data logging power logger, and the average hourly OAT as measured by a temperature/RH logger. Fit a second-order polynomial regression model of true RMS power as a function OAT. (Worksheet: “Step 3. Regression”). \begin{equation} P(OAT) = a * OAT^{2} + b * OAT + c \end{equation} Where, $P =$ Average hourly true RMS power $a,b,c =$ Regression coefficients $OAT =$ Outdoor air temperature, F Average % hour motor is on for each hour of each day of the week (Worksheets: “Step 4. Schedule Calcs” and “Step 5. Daily Ave Schedule Calc”). \begin{equation} On(t) = \begin{cases} 1 & \text{if } P(t) 0\\ 0 & otherwise \end{cases} \end{equation} \begin{equation} \overline{\%On}_{d,h} = \frac{\sum_{n=1}^{N(d,h)} On(t)}{N(d,h)} \end{equation} Where, $P(t) =$ Measures power, kW $On(t)=$ Motor is on at time, t, binary $\overline{\%On}_{d,h} =$ Average % time motor is on per hour for given day of week, d, and hour of the day, h, % $N(d,h) =$ Total number of measured data points that fall on day of week, d, and hour of the day, h $n \in t(d,h) =$ Index for subset of measured data points that fall on day of week, d, and hour of the day, h Total annual pump energy (Worksheets: “Step 6. Energy Calcs” and “Step 7. Results”). \begin{equation} E = WeeksPumpOn * \sum_{t=1}^{8760} P(OAT'(t)) * \overline{\%On}_{d,h}(t) \end{equation} Where, $E =$ Annual energy usage, kWh $OAT'(t) =$ Hourly climate normal outside air temperature from National Weather Service at station closest to site, F $WeeksPumpOn =$ Pump operating times, weeks Variable Speed Pump Energy Using Motor Speed Data This calculation tool is for VFD-controlled pumps using hourly average motor speed (in RPM) as downloaded from a BAS or VFD, and spot measurements for true power. Convert the speed data from the BAS or VFD to power (Worksheet: “Step 2. Aggregate Data”) \begin{equation} P(t) = P_{max}(\frac{\omega(t)}{\omega_{max}})^{2.5} \end{equation} Where, $P(t) =$ average hourly true RMS power, kW $P_{max} =$ full speed true RMS power, kW $\omega_{max} =$ maximum motor speed, rpm $\omega(t) =$ motor speed, rpm This equation represents the pump affinity law, where theoretically the exponent is 3. To represent motor losses, the Consortium for Energy Efficiency recommends using a value of 2.5.1 Equations 9 to 12 are used to calculate the annual pump energy. Further Reading For more information on the different types of fans found in AHU systems, please read “Application of Fans in Commercial HVAC Equipment” from the Carrier Corporation: https://www.utcccs-cdn.com/hvac/docs/1001/Public/0F/04-581070-01.pdf For more information of the different types of motors that can be used in an AHU retrofit, please read Chapter 7 (starts on page 91) of the Premium Efficiency Motor Selection and Application Guide from the U.S. Department of Energy: https://www.energy.gov/sites/prod/files/2014/04/f15/amo_motors_handbook_web.pdf#page=91 For general information on Option A M&V guides, please read section 4.2 (starts on page 23) of “M&V Guidelines: Measurement and Verification for Performance-Based Contracts Version 4.0” from the U.S. Department of Energy: https://www.energy.gov/sites/prod/files/2016/01/f28/mv_guide_4_0.pdf#page=23 Footnotes Consortium for Energy Efficiency. Motor Efficiency, Selection, and Management: A Guidebook for Industrial Efficiency Programs (May 2011) ↩︎

Estimate the annual energy consumption of variable speed and constant speed pump motors.


Heat Transfer

Air-to-air Heat Exchanger Heat Transfer
Introduction This calculation methodology is based on the 2020 ASHRAE Handbook – Systems and Equipment, Chapter 26. This methodology assumes that the air handling unit (AHU) uses a variable speed supply fan, and that the energy recovery component is a rotary wheel. The corresponding calculator is used to estimate a full year of sensible and latent heat transfer in an energy recovery ventilation (ERV) system: Air to Air Heat Transfer Calculator Uses measured air flow rate, fan power and runtime, and temperature to calculate total annual heat transfer and energy savings for an ERV. This methodology works with hourly data only and each measurement is taken at the start of the hour for a minimum duration of six weeks. If the ERV system is used during both the heating and cooling seasons, then six weeks of data per season is needed. Data is used to calculate heat transfer for the measurement period first, then is extrapolated to a full year. Measured data is obtained via the following measurement techniques: True RMS Power Measurement Use this technique to measure power draw (true RMS power) at one-hour intervals using a data logger. Outdoor Air Temperature Measurement Use this technique to measure outdoor air temperature (OAT) at one-hour intervals with a data logger. System Air Temperature Measurement Use this technique to measure the air temperature of various air streams in an air handling unit at one-hour intervals with data loggers. Relative Humidity Measurement Use this technique to measure relative humidity (RH %) of various air streams in an air handling unit at one-hour intervals with data loggers. Measurement points are shown in Figure 2 and the variables to measure are listed in Table 2. Figure 2. ERV system with measurement points. Section A.1 describes how to calculate the sensible and latent heat transfer for the duration of the measurement period. If six weeks of data is collected, then heat transfer will be calculated for each hour interval for those six weeks. Sensible and latent effectiveness are a measure of the performance of the ERV system. Effectiveness is the actual heat transfer divided by the maximum possible heat transfer by the heat exchanger. These values are calculated in section A.1 for each hour interval and are used in section A.2 to estimate the full-year heat transfer. To calculate latent heat transfer and effectiveness, first the humidity ratio $(lb_m/lb_m)$ must be calculated. Table 1 summarizes the equations used to determine humidity ratio for a given relative humidity value. The calculator selects the appropriate equation based on the measured hourly relative humidity and then uses the measured hourly temperature to run the calculation (CUNY BPL BRT, 2022, pp. 22). The equations in Table 1 result in a humidity ratio with units of grains of water per pound of dry air (grains/lb). The calculator performs an additional calculation to convert the units of grain/lb to $lb_m/lb_m$. Table 1. Humidity ratio equations for various relative humidity values based on dry-bulb temperature.1 Relative Humidity (%) Humidity Ratio Equation $10$ $W = 0.0000361T^3 - 0.0020357T^2 + 0.1276984T - 0.5452381$ $20$ $W = 0.0000750T^3 - 0.0044762T^2 + 0.2739286T - 1.1180952$ $30$ $W = 0.0001126T^3 - 0.0066310T^2 + 0.4050469T - 1.9071429$ $40$ $W = 0.0001530T^3 - 0.0091548T^2 + 0.5507684T - 2.6595238$ $50$ $W = 0.0001970T^3 - 0.0121548T^2 + 0.7163745T - 3.6595238$ $60$ $W = 0.0002407T^3 - 0.0151310T^2 + 0.8841486T - 4.7119048$ $70$ $W = 0.0002826T^3 - 0.0176905T^2 + 1.0265043T - 5.3857143$ $80$ $W = 0.0003303T^3 - 0.0211429T^2 + 1.2117316T - 6.6047619$ $90$ $W = 0.0003785T^3 - 0.0245833T^2 + 1.3932179T - 7.7880952$ $100$ $W = 0.0004270T^3 - 0.0280000T^2 + 1.5725361T - 8.9380952$ Where, $T =$ hourly measured air temperature of the respective air stream (F) $W_g =$ humidity ratio (grains/lb) To estimate heat transfer for a full year, simple linear regression (used to assess the relationship between two variables) is performed in Microsoft Excel using the LINEST function. These calculation steps are described in more detail in Section A.2. Section A.3 describes how to calculate the electrical energy consumption of the supply and return fan motors using hourly power draw data. The hourly data is used to develop an average hourly schedule of both fan motors for all seven days of the week as a proxy of the occupancy schedule of the facility. This occupancy schedule is used in Section A.2 to conduct the simple linear regressions. Air-to-air Heat Exchanger Calculations A.1: Heat Transfer for the Measurement Period The following methodology is used to calculate the sensible and latent heat transferred by the ERV system during the measurement period only. Sensible and latent effectiveness are also calculated in this process. All data used in section A.1 should rely on data being measured with either data loggers or BMS historical trends. Measured data used in this section is summarized in Table 3. Table 3. Hourly measured data required to calculate heat transfer. Hourly Measured Values $$T_1, T_2, T_3, T_4$$ Temperatures (F) $$RH_1, RH_2, RH_3$$ Relative Humidity (%) $$Q_2, Q_3$$ Air flow rate (ft$^3$/min) $$P_1, P_2$$ Fan motor Power (kW) Calculate the mass flow rate of supply air leaving the ERV for each hour interval. \begin{equation} \dot{m_2} = Q_2/v \end{equation} Where, $\dot{m_2} =$ hourly mass flow rate of supply air leaving the ERV (lb$_m$/min) $Q_2 =$ hourly air flow rate of supply air leaving the ERV (ft$^3$/min) $v =$ specific volume of air, 12.49 (ft$^3$/lb) Calculate the mass flow rate of return air entering the ERV for each hour interval. \begin{equation} \dot{m_3} = Q_3/v \end{equation} Where, $\dot{m_3} =$ hourly mass flow rate of return air entering the ERV (lb$_m$/min) $Q_3 =$ hourly air flow rate of return air entering the ERV (ft$^3$/min) $v =$ specific volume of air, 12.49 (ft$^3$/lb) Calculate the humidity ratio for outside air entering the ERV ($W_1$), supply air leaving the ERV ($W_2$) and return air entering the ERV ($W_3$) for each hour interval. In this step, the measured hourly temperature and relative humidity data of the respective air stream is used with the equations in Table 1 to determine the humidity ratio for that hour. In this same step, the units are converted from grains/lb to lb$_m$/lb$_m$. \begin{equation} W_n = 0.000142857 * W_g \end{equation} Where, $W_n =$ humidity ratio of a given air stream (lb$_m$/lb$_m$) $0.000142857 =$ constant value, (lb$_m$/lb$_m$) $W_g =$ humidity ratio calculated from Table 1 Calculate sensible heat transferred by the ERV for each hour interval. \begin{equation} q_s = \dot{m}_2c(T_1 - T_2) \end{equation} Where, $q_s =$ sensible heat transferred by the ERV each hour (Btu/h) $c =$ specific heat of air at normal atmospheric pressure, 0.243 (Btu/lb F) $\dot{m}_2 =$ hourly mass flow rate of supply air leaving the ERV (lb$_m$/min) $T_1 =$ hourly temperature of outside air entering the ERV (F) $T_2 =$ hourly temperature of supply aire leaving the ERV (F) Calculate latent heat transferred by the ERV for each hour interval. \begin{equation} q_L = \dot{m}_2h(W_1 - W_2) \end{equation} Where, $q_L =$ latent heat transferred by the ERV each hour (Btu/h) $h =$ latent heat of vaporization, 970.1 (Btu/lb) $\dot{m}_2 =$ hourly mass flow rate of supply air leaving the ERV (lb$_m$/min) $W_1 =$ hourly humidity ratio of outside air entering the ERV (lb$_m$/lb$_m$) $W_2 =$ hourly humidity ratio of supply air leaving the ERV (lb$_m$/lb$_m$) Heat transfer should be calculated only when the energy/heat recovery mode is on. This can be determined by checking the temperature difference across the recovery system in both the supply-air side and the return-air side. Another condition is that the supply fan motor must be running for heat transfer to occur. Sometimes the ERV is off and the supply fan motor is on. In this scenario, we cannot assume heat transfer occurs. \begin{equation} \text{If} \hspace{2mm} \begin{cases} T_1 - T_2 1 & \text{heat transfer during cooling season}\\ T_1 - T_2 Where, $T_1 =$ measured hourly temperature of outside air entering the ERV (F) $T_2 =$ measured hourly temperature of supply air leaving the ERV (F) \begin{equation} \text{If} \hspace{2mm} \begin{cases} T_3 - T_4 1 & \text{heat transfer during cooling season}\\ T_3 - T_4 Where, $T_3 =$ measured hourly temperature of return air entering the ERV (F) $T_4 =$ measured hourly temperature of exhaust air leaving the ERV (F) \begin{equation} \text{If} \hspace{2mm} \begin{cases} Q_2 0 & \text{heat transfer occurs}\\ Q_2 Where, $Q_2 =$ air flow rate of supply air leaving the ERV (ft$^3$/min) \begin{equation} \text{If} \hspace{2mm} \begin{cases} Q_3 0 & \text{heat transfer occurs}\\ Q_3 Where, $Q_3 =$ air flow rate of return air entering the ERV (ft$^3$/min) Sensible and Latent Heat Effectiveness Sensible and latent heat effectiveness has the same conditions as heat transfer where effectiveness should be calculated only when the energy/heat recovery mode is on and the supply fan motor must be running. Calculate the latent effectiveness for each hour interval. \begin{equation} \varepsilon_L = \frac{\dot{m}_2h(W_1 - W_2)}{\dot{m}_{min}h(W_1 - W_3)} \end{equation} Where, $\varepsilon_L =$ hourly latent effectiveness of the ERV $h =$ latent heat of vaporization, 970.1 (Btu/lb) $\dot{m}_2 =$ hourly mass flow rate of supply air leaving the ERV (lb$_m$/min) $\dot{m}_{min} =$ minimum hourly mass flow rate value (lb$_m$/min) $W_1 =$ hourly humidity ratio of outisde air entering the ERV (lb$_m$/lb$_m$) $W_2 =$ hourly humidity ratio of supply air leaving the ERV (lb$_m$/lb$_m$) $W_3 =$ hourly humidity ratio of return air entering the ERV (lb$_m$/lb$_m$) Calculate the sensible effectiveness for each hour interval. \begin{equation} \varepsilon_s = \frac{\dot{m}_2c(T_1 - T_2)}{\dot{m}_{min}c(T_1 - T_3)} \end{equation} Where, $\varepsilon_s =$ hourly sensible effectiveness of the ERV $c =$ specific heat of air at normal atmospheric pressure, 0.243 (Btu/lb F) $\dot{m}_2 =$ hourly mass flow rate of supply air leaving the ERV (lb$_m$/min) $\dot{m}_{min} =$ minimum hourly mass flow rate value (lb$_m$/min) $T_1 =$ hourly temperature of outisde air entering the ERV (F) $T_2 =$ hourly temperature of supply air leaving the ERV (F) $T_3 =$ hourly temperature of return air entering the ERV (F) A.2: Heat Transfer for the Full Year To estimate the full year heat transfer, the occupancy patterns and schedule defined in the measurement period are extrapolated to the entire year. Supply air flow (Q2), return air flow (Q3), and sensible and latent effectiveness are calculated by performing a regression analysis with the variables listed in Table 4. Regression analysis plots data on a graph and generates a line that traces the distribution of data. The line has a formula associated with it and the formula is used to project the dependent variable for the full year. To accomplish this, the Microsoft Excel function LINEST is used with the values in Table 4. Table 4. List of dependent and independent variables used in the regression analysis. Independent Variable Dependent Variable Regression 1 $P_2$ $Q_2$ Regression 2 $P_3$ $Q_3$ Regression 3 $Q_2$ $\varepsilon_s$ Regression 4 $Q_2$ $\varepsilon_L$ Regressions 1 and 2 There is a cubic relationship between fan motor draw and air flow rate. The equation that describes the relationship between these variables is: \begin{equation} y = ax^3 + bx^2 + cx + d \end{equation} Where, $y =$ dependent variable at each hour for a full year, the value being projects ($Q_2$ and $Q_3$) $x =$ independent variable at each hour for a full year, the suply fan motor energy consumption $a,b,c,d =$ cubic relationship coefficients With this formula, the air flow rate Q2 and Q3 can be projected for the full year by plugging in values for x, the supply fan motor power draw. This data is the measured power draw of the supply and return fan motors. Regressions 3 and 4 These steps yield an assessment of the relationship between the measured air flow rate of supply air leaving the ERV system (Q2) and the sensible and latent heat effectiveness that was calculated in section A.1. The relationship between air flow rate and effectiveness is linear, and the equation that describes the relationship is: \begin{equation} y = mx + b \end{equation} Where, $y =$ dependent variable at each hour for a full year, the value being projects (sensible and latent effectiveness) $m =$ slope of the line, generated by Excel $x =$ independent variable at each hour for a full year, the air flow rate of air leaving the ERV system ($Q_2$) $b =$ y-intercept of the line generated by Excel The values of $Q_2$ that were calculated in the previous section are then plugged into Equation (11) to project sensible and latent heat transfer effectiveness for the full year: \begin{equation} \varepsilon_s = m(Q_2) + b \end{equation} \begin{equation} \varepsilon_L = m(Q_2) + b \end{equation} Where, $\varepsilon_s =$ projected sensible effectiveness $\varepsilon_L =$ projected latent effectiveness $Q_2 =$ projected air flow rate of supply air leaving the ERV (ft$^3$/min) After projecting the airflows and effectiveness rates to a full year, the next step is to calculate the hourly mass flow rates and humidity ratios for a full year. Calculate the mass flow rate of supply air leaving the ERV for each hour interval for the entire year. \begin{equation} \dot{m}_2 = Q_2/v \end{equation} Where, $\dot{m}_2 =$ hourly mass flow rate of supply air leaving the ERV (lb$_m$/min) $Q_2 =$ projected hourly air flow rate of supply are leaving the ERV (ft$^3$/min) $v =$ specific volume of air, 12.49 (ft$^3$/lb) After projecting the airflows and effectiveness rates to a full year, the next step is to calculate the hourly mass flow rates and humidity ratios for a full year. \begin{equation} \dot{m}_3 = Q_3/v \end{equation} Where, $\dot{m}_3 =$ hourly mass flow rate of return air entering the ERV (lb$_m$/min) $Q_3 =$ projected hourly air flow rate of return air entering the ERV (ft$^3$/min) $v =$ specific volume of air, 12.49 (ft$^3$/lb) Calculate the humidity ratio for outside air entering the ERV (W1). In this step, the hourly climate normal year (CNY) outside air temperature (OAT) and relative humidity data is used with the equations in Table 1 to determine the humidity ratio for that hour. In this same step, the units are converted from grains/lb to lb$_m$/lb$_m$. \begin{equation} W_n = 0.000142857 * W_g \end{equation} Where, $W_n =$ humidity ratio of a given air stream (lb$_m$/lb$_m$) $0.000142857 =$ constant value, (lb$_m$/lb$_m$) $W_g =$ humidity ratio calculated from Table 1 Estimate the hourly humidity ratio of supply air leaving the ERV for the full year. In this equation, it is assumed that the latent heat of vaporization is constant. \begin{equation} W_2 = \frac{\dot{m}_2W_1 - \varepsilon_L\dot{m}_{min}(W_1-W_3)}{\dot{m}_2} \end{equation} Where, $W_2 =$ hourly humidity ratio of supply air leaving the ERV (lb$_m$/lb$_m$) $W_1 =$ hourly humidity ratio of outside air entering the ERV (lb$_m$/lb$_m$) $W_3 =$ hourly humidity ratio of return air entering the ERV (lb$_m$/lb$_m$) $\varepsilon_L =$ projected hourly latent effectiveness of the ERV $\dot{m}_{min} =$ minimum mass flow rate value (lb$_m$/min) $\dot{m}_2 =$ hourly mass flow rate data of supply air leaving the ERV (lb$_m$/min) Estimate the temperature of supply air leaving the ERV for the full year. In this equation, it is assumed that specific heat of air is constant. \begin{equation} T_2 = \frac{\dot{m}_2T_1 - \varepsilon_s\dot{m}_{min}(T_1-T_3)}{\dot{m}_2} \end{equation} Where, $T_2 =$ hourly temperature of supply air leaving the ERV (F) $T_1 =$ hourly temperature of outside air entering the ERV (F) $T_3 =$ hourly temperature of return air entering the ERV (F) $\varepsilon_s =$ projected hourly sensible effectiveness of the ERV $\dot{m}_{min} =$ minimum mass flow rate value (lb$_m$/min) $\dot{m}_2 =$ hourly mass flow rate data of supply air leaving the ERV (lb$_m$/min) CUNY BPL assumes that T3 and W3 are constant values, reasoning that occupants will want the same indoor air temperature, regardless of the season. It is up to the heating and cooling plants to maintain that setpoint temperature. The next step is to calculate sensible and latent heat transfer. Calculate sensible heat transferred by the ERV for each hour interval for the full year. \begin{equation} q_s = \dot{m}_2c(T_1 - T_2) \end{equation} Where, $q_2 =$ sensible heat transferred by the ERV each hour (Btu/h) $c =$ specific heat of air at normal atmospheric pressure, 0.243 (Btu/lb F) $\dot{m}_2 =$ hourly mass flow rate of supply air leaving the ERV (lb$_m$/min) $T_1 =$ hourly temperature of outside air entering the ERV (F) $T_2 =$ hourly temperature of supply air leaving the ERV (F) Calculate latent heat transferred by the ERV for each hour interval for the full year. \begin{equation} q_L = \dot{m}_2h(W_1 - W_2) \end{equation} Where, $q_2 =$ latent heat transferred by the ERV each hour (Btu/h) $h =$ latent heat of vaporization, 970.1 (Btu/lb) $\dot{m}_2 =$ hourly mass flow rate of supply air leaving the ERV (lb$_m$/min) $W_1 =$ hourly humidity ratio of outside air entering the ERV (lb$_m$/lb$_m$) $W_2 =$ hourly humidity ratio of supply air leaving the ERV (lb$_m$/lb$_m$) Heat transfer should be calculated only when the energy/heat recovery mode is on. This can be determined by checking the temperature difference across the recovery system in both the supply air side and the return air side, and air flow rate across the heat exchanger. Air flow happens when the supply fan motor and exhaust fan motor are on. Sometimes the ERV rotary wheel is off and air flow bypasses the rotary wheel when the supply fan motor is on. In this scenario, we cannot assume heat transfer occurs. \begin{equation} \text{If} \hspace{2mm} \begin{cases} T_1 - T_2 1 & \text{heat transfer during cooling season}\\ T_1 - T_2 Where, $T_1 =$ measured hourly temperature of outside air entering the ERV (F) $T_2 =$ measured hourly temperature of supply air leaving the ERV (F) \begin{equation} \text{If} \hspace{2mm} \begin{cases} T_3 - T_4 1 & \text{heat transfer during cooling season}\\ T_3 - T_4 Where, $T_3 =$ measured hourly temperature of return air entering the ERV (F) $T_4 =$ measured hourly temperature of exhaust air leaving the ERV (F) \begin{equation} \text{If} \hspace{2mm} \begin{cases} Q_2 0 & \text{heat transfer occurs}\\ Q_2 Where, $Q_2 =$ air flow rate of supply air leaving the ERV (ft$^3$/min) \begin{equation} \text{If} \hspace{2mm} \begin{cases} Q_3 0 & \text{heat transfer occurs}\\ Q_3 Where, $Q_3 =$ air flow rate of return air entering the ERV (ft$^3$/min) A.3: Annual Supply Fan Energy Consumption This calculation methodology assumes the power draw of the supply and exhaust fan motors is measured using a power logger at one-hour intervals over a minimum of six weeks. The power logger measures all three phases of the panelboard to capture accurate data. The process begins by calculating three-phase power using the provided formulas. The dataset is then condensed into an hourly schedule for all seven days of the week to determine when heat transfer occurs. Finally, this schedule is extrapolated to represent a full year, resulting in an estimate of the annual energy consumption of the fan motors. Calculate the hourly three-phase power draw of the motor by summing the single-phase power of each electrical line for each hour interval. \begin{equation} \overline{kW}_{h,3P} = \sum_{n=1}^3 \overline{kW}_{h,n} \end{equation} Where, $\overline{kW}_{h,3P} =$ hourly three-phase power draw of the motor (kW) $\overline{kW}_{h,n} =$ hourly single-phase power for electrical line n (kW) Calculate average energy consumption for each hour of the week. This step generates an hourly schedule for a week, and this schedule is used to calculate the full year heat transfer. In this step, the hourly power draw (kW) gets converted to hourly energy consumption (kWh) because data is in one-hour intervals2. \begin{equation} \overline{kWh}_{d,h} = \frac{\sum_1^{N_f(d,h)} \overline{kW}_{h,3P}}{N_f(d,h)} \end{equation} Where, $\overline{kWh}_{d,h} =$ average energy consumption for each hour of each day of the week (kWh) $\overline{kW}_{h,3P} =$ hourly three-phase power draw of the motor (kW) $N_f(d,h) =$ total number of data points that fall on day of week, d, and hour of the day, h Calculate average daily energy consumption for a given day of the week. \begin{equation} \overline{kWh}_{d,w} = \sum_{n=0}^{23} \overline{kWh}_{d,h} \end{equation} Where, $\overline{kWh}_{d,w} =$ average daily energy consumption for a given day of the week of the motor $\overline{kWh}_{d,h} =$ average energy consumption for each hour of each day of the week (kWh) $n =$ hour of the day where 0 is 12:00 a.m. and 23 is 11:00 p.m. Calculate the average energy consumption per day for weekdays. \begin{equation} \overline{kWh}_{Wd} = \frac{\sum_{n=2}^6 \overline{kWh}_{wd,n}}{5} \end{equation} Where, $\overline{kWh}_{Wd} =$ average energy consumption for weekdays (kWh) $\overline{kWh}_{wd,n} =$ average energy consumption of each $n$ weekday (kWh) $n =$ day of week: 2 = Monday, 3 = Tuesday, ..., 6 = Friday $5 =$ constant, weekdays per week Calculate the average energy consumption per day for weekend days. \begin{equation} \overline{kWh}_{Wed} = \frac{\sum_{n=1}^7 \overline{kWh}_{we,n}}{2} \end{equation} Where, $\overline{kWh}_{WEd} =$ average energy consumption for a weekend day (kWh) $\overline{kWh}_{we,n} =$ average energy consumption of each $n$ weekend day (kWh) $n =$ day of week: 7 = Saturday, 1 = Sunday $2 =$ constant, weekend days per week Calculate the annual weekday energy consumption (Worksheet: “Step 4. Results,” cell E3). \begin{equation} \overline{kWh}_{WdYr} = \overline{kWh}_{Wd} * (261 - X) \end{equation} Where, $\overline{kWh}_{WdYr} =$ estimated annual weekday energy consumption $\overline{kWh}_{Wd} =$ average weekday energy consumption (kWh) $X =$ number weekdays that are adjusted to a weekend day (holidays) $261 =$ constant, number of weekdays per year Calculate the total weekend energy consumption (Worksheet: “Step 4. Results,” cell E6). \begin{equation} \overline{kWh}_{WEdYr} = \overline{kWh}_{WEd} * (104 + X) \end{equation} Where, $\overline{kWh}_{WEdYr} =$ estimated annual weekend day energy consumption $\overline{kWh}_{WEd} =$ average weekend day energy consumption (kWh) $X =$ number of weekdays that are adjusted to a weekend day (holidays) $104 =$ constant, number of weekends per year Calculate the total annual energy consumption of the motor. \begin{equation} \overline{kWh}_{ann} = \overline{kWh}_{WdYr} + \overline{kWh}_{WEdYr} \end{equation} Where, $\overline{kWh}_{ann} =$ estimated annual energy consumption of the motor (kWh) $\overline{kWh}_{WdYr} =$ estimated annual weekday energy consumption (kWh) $\overline{kWh}_{WEdYr} =$ estimated annual weekend day energy consumption Calculate the total annual energy consumption of the supply and exhaust fan motors. \begin{equation} \overline{kWh}_{T,ann} = \overline{kWh}_{supply} + \overline{kWh}_{exhaust} \end{equation} Where, $\overline{kWh}_{T,ann} =$ estimated annual energy consumption of the fan motors (kWh) $\overline{kWh}_{supply} =$ esimated annual energy consumption of the supply fan motor (kWh) $\overline{kWh}_{exhaust} =$ estimated annual energy consumption of the exhaust fan motor (kWh) Further Reading For general information on Option A M&V guides, please read section 4.2 (starts on page 23) of “M&V Guidelines: Measurement and Verification for Performance-Based Contracts Version 4.0” from the U.S. Department of Energy: https://www.energy.gov/sites/prod/files/2016/01/f28/mv_guide_4_0.pdf#page=23 ASHRAE (2020) “2020 ASHRAE Handbook-HVAC Systems and Equipment” Chapter 26. CUNY Building Performance Lab (May 2020). “Quantification of Energy Savings from Implementing Building Re-tuning Recommendations.” (pp. 21–22). New York, NY: Department of Citywide Administrative Services. Footnotes CUNY Building Performance Lab. (n.d.). Quantification of Energy Savings from Implementing BuildingRe-tuning Recommendations (pp. 21–22) [Review of Quantification of Energy Savings from Implementing Building Re-tuning Recommendations]. DCAS. ↩︎ $kWh = kW * h$, where $h = 1$ ↩︎

For a rotary wheel heat exchanger, the equations and calculator in this page estimate the annual sensible and latent heat transfer across the rotary wheel …


Liquid-to-liquid Heat Exchanger Heat Transfer
Introduction This calculation methodology is loosely based on the 2020 ASHRAE Handbook – Systems and Equipment, Chapter 26 for air-to-air heat exchangers. Part of the methodology described in Chapter 26 is applicable in liquid-to-liquid heat transfer systems, specifically about sensible heat. There is no latent heat transfer in liquid-to-liquid heat exchangers (no moisture control) only sensible heat transfer which can be measured by monitoring the liquid’s temperature. If the temperature of the liquids in the system changes as they flow through the heat exchanger, heat transfer is happening. This methodology is applicable for systems that have liquid-to-liquid heat exchangers such as waterside economizers, blowdown heat recovery, and condensate cooling systems. Although this calculator can be used to evaluate energy transfer by any fluids (e.g., refrigerants), water is the only fluid to be evaluated in this methodology. Figure 1 shows an example of a plate and frame heat exchanger with the required measurement points. Figure 1. A plate and frame liquid-to-liquid heat exchanger with measurement points. This methodology works with hourly data only and each measurement is taken at the start of the hour. If the system operates seasonally, measurements should be taken for the duration of the season at one-hour intervals. If the system is not weather dependent, then a minimum of six (6) weeks of hourly data is required for this methodology to work. Calculator Table 1. Liquid-to-liquid heat transfer calculator Calculator (Downloadable File) Description Required Data To Use This Calculator Liquid-to-liquid Heat-transfer Calculator.xlsx Uses the flow rate and temperature of two fluids in the system to calculate the heat transfer. Fluid Flow Rate (GPM) Fluid Temperature (F) Heat-transfer Calculation The following equations are used to calculate the sensible heat transferred by the heat exchanger for a full year. All data used in this section should be measured with data loggers. A list of data that is required is summarized in Table 1. Table 2. Hourly measured data to calculate heat transfer. Hourly Measured Values $$T_1, T_2, T_3, T_4$$ Fluid Temperatures (F) $$Q_1$$ Fluid 1: Water flow rate (GPM) Calculate the mass flow rate of fluid 1 leaving the heat exchanger for each hour interval. \begin{equation} \dot{m_1} = Q_1 * 0.13368 * d \end{equation} Where, $\dot{m_1} =$ hourly mass flow rate of fluid 1 leaving the heat exchanger ($lb_m$/min) $Q_1 =$ hourly flow rate of fluid 1 leaving the heat exchanger (GPM) $d =$ density of water, 62 $(lb/ft^3)$ $0.13368 =$ unit conversion, GPM to $(ft^3/min)$ Heat transfer should be calculated only when the heat exchanger is operating. This can be determined by checking the temperature difference across the recovery system in both the supply side and waste heat stream side. Another condition is that water flow should exist across the heat exchanger. \begin{equation} \text{If} \hspace{2mm} \begin{cases} T_1 - T_2 1 & \text{if heat transfer occurs}\\ T_1 - T_2 Where, $T_1 =$ meausured hourly temperature of fluid 1 entering the heat exchanger (F) $T_2 =$ meausured hourly temperature of fluid 1 leaving the heat exchanger (F) \begin{equation} \text{If} \hspace{2mm} \begin{cases} T_3 - T_4 1 & \text{if heat transfer occurs}\\ T_3 - T_4 Where, $T_3 =$ meausured hourly temperature of fluid 1 entering the heat exchanger (F) $T_4 =$ meausured hourly temperature of fluid 1 leaving the heat exchanger (F) \begin{equation} \text{If} \hspace{2mm} \begin{cases} Q_1 0 & \text{if heat transfer occurs}\\ Q_1 Where, $Q_1 =$ hourly flow rate of fluid 1 leaving the heat exchanger (GPM) Calculate the sensive heat transferred by the heat exchanger for each hour interval. \begin{equation} q_s = \dot{m_1}c(T_1 - T_2) \end{equation} Where, $q_s =$ sensible heat transferred by the heat exchanger every hour (Btu/h) $c =$ specific heat of water at normal atmospheric pressure (Btu/lb F), 1 (Btu/lb F) $\dot{m_1} =$ hourly mass flow rate of fluid 1 leaving the heat exchanger ($lb_m$\min) $T_1 =$ hourly fluid 1 entering the heat exchanger temperature (F) $T_2 =$ hourly fluid 1 leaving the heat exchanger temperature (F) Calculate the total heat transfer by the heat exchanger for a whole year. \begin{equation} Q_s = \sum_{t=0}^{8760} q_s \end{equation} Where, $Q_s =$ total sensible heat transfer for a whole year (Btu/h) $q_s =$ sensible heat transferred by the heat exchanger every hour (Btu/h) $t =$ hours Further Reading For general information on Option A M&V guides, please read section 4.2 (starts on page 23) of “M&V Guidelines: Measurement and Verification for Performance-Based Contracts Version 4.0” from the U.S. Department of Energy: https://www.energy.gov/sites/prod/files/2016/01/f28/mv_guide_4_0.pdf#page=23 ASHRAE (2020) “2020 ASHRAE Handbook-HVAC Systems and Equipment”

For a fixed plate heat exchanger, the equations used in this methodology and calculator estimate the annual sensible heat transfer.


All Sequence of Operations

Sequence of Operations (SOO) are feedback loops that employ a combination of sensors, controllers, and actuators to impact a process and maintain a desired state. More For example, a thermostat provides a signal to a controller, and the controller sends a signal to the furnace. When the temperature falls below a certain setpoint, the controller sends a signal to the furnace to fire up and to turn on the air handler to provide heated air to the conditioned space. Once the temperature reaches the desired set point, the controller sends a signal to reduce the fan speed and/or to turn off the furnace. Less

Temperature Resets

Chilled Water Supply Temperature Reset
General Overview On cooler days during the cooling season, the chilled water supply temperature (CHWST) can be increased (i.e., reset) in a central cooling plant based on the reduced cooling load. The sequence of operation (SOO) uses outdoor air temperature (OAT), chilled water return temperature, or the average cooling coil valve positions of the AHUs served by the chiller as a proxy for the cooling load. CHWST reset saves energy by optimizing the central cooling plant energy consumption and by minimizing AHU reheat calls. The goal of CHWST reset is to use less energy during times of lower cooling demand. When OAT is lower, the rate of cooling energy supplied to the zones is moderated. If the AHU supply air temperature is simultaneously reset, the chilled water temperature that is supplied to the AHU cooling coils may also be moderated. Besides making the heat transfer throughout the system more efficient, the likelihood of VAV box reheat calls during the cooling season is reduced. note NYC Energy Conservation Code (Section C403.4.4) and ASHRAE 90.1 (Section 6.5.4.4 – Chilled- and Hot-Water Temperature Reset Controls) requires CHWST reset in new or replaced central cooling plants greater than 300,000 Btu/hr. The code calls for CHWST reset based on input from three possible variables: OAT, cooling coil valve position, or chilled water return temperature. Basic Control Logic SOOs are feedback loops that employ a combination of sensors, controllers, and actuators to impact a process and maintain a desired state. For example, a thermostat provides a signal to a controller, and the controller sends a signal to the furnace. When the temperature falls below a certain setpoint, the controller sends a signal to the furnace to fire up and to turn on the air handler to provide heated air to the conditioned space. Once the temperature reaches the desired set point, the controller sends a signal to reduce the fan speed and/or to turn off the furnace. Figure 1 presents a schematic of the general principle of the CHWST reset control feedback loop. When the facility needs cooling, but the OAT is not extremely high, the building automation system (BAS) raises the CHWST temperature setpoint. The CHWST temperature sensor provides the feedback signal; based on the measured error, the BMS coordinates the central chilled water plant components (e.g., cooling tower, condenser and chilled water pumps, chiller compressor) to moderate the CHWST to meet the new setpoint. Figure 1. Fundamental CHWST reset control logic. Algorithm for the Sequence of Operation The general CHWST reset algorithm is described in the ASHRAE handbook, “2019 ASHRAE HVAC – Applications.”1 The algorithm is implemented differently depending on the input control variable: OAT, cooling coil valve position, or chilled water return temperature. Outdoor Air Temperature Reset The general algorithm employed when OAT is the input variable is depicted in Figure 2. The proportional control during moderate temperatures (in this case between 60°F and 80°F) is set by the commissioning agent and generally aligns with the supply air temperature reset for the AHUs served by the central cooling plant. The upper bound of 54°F ensures sufficient dehumidification at moderate OAT and cooling loads. The lower bound of 44°F also ensures dehumidification at higher cooling loads and may reflect the lowest water temperature achievable by the chilled water plant. Figure 2. Chilled water supply temperature reset algorithm. Cooling Coil Valve Position CHWST setpoint can also be modulated in proportion to the to the average position of the cooling coil valves or a Trim and Response control to step up and step down the CHWST setpoint.2 The number of chilled water valves greater than 90% open, (i.e., the number of “requests”) determines the size of the increment to be made to CHWST setpoint. One request might lead to a 1°F setpoint increase, while three requests might lead to a 3°F change. No requests lead to a Trim action, whereupon the setpoint is decreased by a fixed increment. The Trim and Response control algorithm allows for a rapid increase in CHWST and a gradual reduction, which avoids unstable cycling of the chiller system. Cooling coil valve position is the preferred input control variable (over OAT) for variable speed pumping systems (both primary and primary-secondary). «««< HEAD As discussed by Taylor (2012), using cooling coil valve position as the input allows for integrated control of the CHWST reset SOO with the differential pressure reset SOO, while also minimizing the risk of insufficient dehumidification by the cooling coils.2 As discussed by Taylor (2013), using cooling coil valve position as the input allows for integrated control of the CHWST reset SOO with the differential pressure reset SOO, while also minimizing the risk of insufficient dehumidification by the cooling coils.2 main Figure 3 shows how the algorithm works when the number of cooling coil valves is used as the input variable. The more cooling coil valves that are greater than 90% open, the lower the ChWST setpoint becomes. Figure 3. Chilled water supply temperature reset algorithm. Chilled Water Return Temperature Chilled water return temperature (CHWRT) is the third possible input variable. The temperature differential (∆t) between the CHWRT and the CHWST is maintained to at least 25% of the design ∆t of the system. The use of ∆t as a control input might be found in primary-secondary chilled loop systems with constant speed primary pumps, where “low ∆t syndrome” is to be avoided (see Taylor 2002 for a detailed discussion on low ∆t).3 «««< HEAD Energy Savings ======= Key Values Needed to Assess Energy Consumption main The energy savings from CHWST reset comes from reducing the amount of electrical energy that is needed to run the central cooling plant to meet the CHWST setpoint. Figure 4 shows modeled chiller performance curves for CHWST reset.4 Note that the multiple curves represent different cooling loads; below 80°F, the curves drop (i.e., show increased efficiency). Figure 4. Chiller performance for a chilled water reset schedule below 80°F. Figure 5 presents a hypothetical comparison of the performance curves with and without CHWST reset. The key period to measure the savings is when the reset comes into play, in this case when OAT < 80°F. The total annual chiller energy saved is then the number of hours at each OAT multiplied by the difference in power consumption at those OAT values. While Figure 5 represents the compressor energy saved, there will be an increase in chilled water pump energy consumption to increase flows to meet the same cooling coil loads. Figure 5. Hypothetical difference in chiller performance with and without chilled water temperature reset. note A CHWST reset SOO alters the electrical energy consumption of all the motorized components in a central chilled water plant. Due to the highly interactive effects between the indoor loads, CHW loop, condenser water loop, chiller, indoor loads, and outdoor conditions, the energy calculations for a CHWST reset must be done on an hourly basis. «««< HEAD Evaluation of Energy Consumption The energy consumption of a water-cooled chilled water plant is the sum of the electrical energy of all systems associated with the plant. Key values that need to be quantified to estimate annual energy consumption are shown in Table 1. Key Values Needed to Assess Energy Consumption The energy consumption of a water-cooled chilled water plant is the sum of the electrical energy of all systems associated with the plant. main Table 1. Energy-consuming components associated with the CHWST reset SOO. System Quantification Values to be Quantified Energy Consuming Component Chilled water loop Hourly average pump motor (kWh) Average hourly pump flow (GPM) Primary CHW loop pump motor Chilled water loop Hourly average pump motor (kWh) Average hourly pump flow (GPM) Secondary CHW loop pump motor (if present) Water-cooled chiller Average hourly chiller (kWh) Average hourly Btu/h delivered to the chilled water loop Average hourly Btu/h rejected to the condenser water loop Compressor motor Condenser water loop Average hourly cooling tower fan motor (kWh) Cooling tower fan motor Condenser water loop Hourly average pump motor (kWh) Average hourly pump flow (GPM) Condenser loop pump motor Waterside economizer Average hourly Btu/h delivered to the chilled water loop Average hourly Btu/h rejected by the chilled water loop Cooling Heat Exchanger Waterside economizer Average hourly pump motor (kWh) Pump motor (if present) Components to Measure and Measurement Locations A CHWST reset SOO has potential interactivity with the entire water-cooled chilled water plant. One key assumption when analyzing CHWST reset is that the cooling loads and operating hours are not changing between the pre- and post-retrofit periods. The measurement boundary includes the entire cooling plant, Figure 6 shows a representation of where to collect data in a water-cooled chilled water plant. Refer to the chilled water loop, water-cooled chiller, condenser water loop, and waterside economizer system descriptions for more details on the specific measurement points for those systems. Figure 6. Measurement points in a cooling plant to assess energy consumption when implementing chilled water supply temperature reset. Interaction of CHWST Reset with other SOOs Supply Air Temperature Reset – Since the coil water is warmer with CHWST reset, there is an increased risk of high humidity in the zones due to the reduced capacity of coils to remove moisture from the supply air. «««< HEAD Chilled Water Pumping Differential Pressure Reset – Since differential pressure reset slows down the CHW flow and hence the heat transfer rate to the AHUs, it must be coordinated with CHWST reset. If the CHWST setpoint is raised and the flow is lowered simultaneously, it is possible that not enough heat will be removed from the building. Taylor (2012) explains that for primary variable and secondary variable chilled water loops, the two SOOs should be sequenced as shown in Figure 7: CHWST setpoint should first be increased to lower the cooling capacity; then, when the setpoint cannot be raised anymore, the differential pressure setpoint should start to be decreased. If the chilled water loop has constant speed pumps, then the sequence should be flipped: first increase the differential pressure (to reduce flow), then modulate the CHWST setpoint by staging the chillers or reducing capacity with vane guides.2 Chilled Water Pumping Differential Pressure Reset – Since differential pressure reset slows down the CHW flow and hence the heat transfer rate to the AHUs, it must be coordinated with CHWST reset. If the CHWST setpoint is raised and the flow is lowered simultaneously, it is possible that not enough heat will be removed from the building. Taylor (2013) explains that for primary variable and secondary variable chilled water loops, the two SOOs should be sequenced as shown in Figure 7: CHWST setpoint should first be increased to lower the cooling capacity; then, when the setpoint cannot be raised anymore, the differential pressure setpoint should start to be decreased. If the chilled water loop has constant speed pumps, then the sequence should be flipped: first increase the differential pressure (to reduce flow), then modulate the CHWST setpoint by staging the chillers or reducing capacity with vane guides.2 main Figure 7. Coordination of CHWST reset with differential pressure reset. Waterside Economizing – CHWST reset impacts both full- and partial-load waterside economizing. During full-load economizing, the chiller compressor is turned off. CHWST reset still has the effect of reducing the cooling demand for the cooling towers. In addition, it extends the hours that full-load economizing is suitable. During partial-load economizing, the two SOOs work synergistically to lower the overall cooling load to the compressor and cooling tower. Nighttime Zone Temperature Setback – Using cooling coil position or CHWRT as the input variable to CHWST reset ensures that the reset is closely coordinated with nighttime zone temperature setback. The setback suddenly changes the cooling load; cooling coil position or CHWRT would then immediately inform the algorithm to reset the CHWST setpoint. Note that using OAT as an input signal might result in a response lag. CHWST Reset SOO Calculation Methodology The annual energy consumption of a water-cooled chilled water plant with a CHWST reset SOO is the sum of the energy for each component system for each hour of the year. The model used must consider the hourly cooling loads and facility operations, outdoor conditions, operating parameters of the systems in the plant, and operation of associated AHU plant. note Due to the highly interactive nature of the water-cooled chilled water plant, a detailed plant model or whole facility energy model is needed to estimate annual consumption, based on the actual operational parameters and measured energy consumption of the various systems and components. Further Reading «««< HEAD Advisor Business Energy. (2019, October 7). Energy management and information systems. Retrieved from E Source: https://esource.bizenergyadvisor.com/article/energy-management-and-information-systems ASHRAE. (2019). ASHRAE Handbook Online: HVAC Applications (I-P ed.). ASHRAE. Retrieved from https://www.ashrae.org ASHRAE. (2019). Energy Standard for Buildings Except Low-Rise Residential Buildings. Atlanta, GA: ASHRAE. ASHRAE. (2019). Standard 90.1-2019: Energy standard for buildings except low-rise residential buildings. ASHRAE. Jiang, W., Winiarski, D., Katipamula, S., & Armstrong, P. (2007). Cost-Effective Integration of Efficient Low-Lift Base Load Cooling Equipment. Pacific Northwest National Laboratory. New York City Department of Buildings. (2020). New York City Energy Conservation Code (NYCECC). Retrieved 2021, from Section C403.4.4: https://up.codes/viewer/new_york_city/nyc-energy-conservation-code-2020/chapter/C4/commercial-energy-efficiency#C403.4.4 Taylor, S. (2002). Degrading Chilled Water Plant Delta-T: Causes and Mitigation. ASHRAE Transactions, 108. Taylor, S. (2012). Optimizing Design & Control of Chilled Water Plants. ASHRAE Journal, 56-74. Footnotes ASHRAE (2018). ASHRAE Guideline 36-2018, High Performance Sequences of Operation for HVAC Systems. Atlanta, GA: ASHRAE. ASHRAE (2019). ANSI/ASHRAE/IES Standard 90.1-2019, Energy Standard for Buildings Except Low-Rise Residential Buildings. Atlanta, GA: ASHRAE. ASHRAE (2020). ASHRAE Handbook: HVAC Systems and Equipment. Atlanta, GA: ASHRAE. Cai, J.; Kurtulus, O.; Braun, J.E. (2016). “Experimental Performance Investigation of Cooling or Heating Coil Valves and Their Impact on Temperature Controls.” International Refrigeration and Air Conditioning Conference, West Lafayette, IN. http://docs.lib.purdue.edu/iracc/1800 Fisher Controls (2005). “Control Valve Handbook.” https://www.emerson.com/documents/automation/control-valve-handbook-en-3661206.pdf. Davis, G. (2016, August 15). HVAC codes and standards: cooling and energy efficiency. Consulting-Specifying Engineer. https://www.csemag.com/articles/hvac-codes-and-standards-cooling-and-energy-efficiency/ PNNL (2012). “Large Commercial Buildings: Re-tuning for Efficiency - Air Handling Units: Pre-Re-Tuning and Trending and Re-Tuning.” PNNL-SA-85063. https://buildingretuning.pnnl.gov/documents/chapters/ch5_air_handling.pdf Trane (2016). “Multiple-zone VAV systems - Finding the Right Balance for VAV Energy Savings.” Trane Engineers Newsletter, Vol. 45-3. Fisher Controls (2017). “Dead Band Plus Hysteresis Estimation with ValveLink Diagnostics.” http://www.documentation.emersonprocess.com/groups/public/documents/bulletins/d103549x012.pdf Footnotes main ASHRAE. (2019). ASHRAE Handbook Online: HVAC Applications (I-P ed.). ASHRAE. Retrieved from https://www.ashrae.org ↩︎ Taylor, S. (2012). Optimizing Design & Control of Chilled Water Plants. ASHRAE Journal, 56-74. ↩︎ Taylor, S. (2002). Degrading Chilled Water Plant Delta-T: Causes and Mitigation. ASHRAE Transactions, 108. ↩︎ Jiang, W., Winiarski, D., Katipamula, S., & Armstrong, P. (2007). Cost-Effective Integration of Efficient Low-Lift Base Load Cooling Equipment. Pacific Northwest National Laboratory. ======= ↩︎

On cooler days during the cooling season, the chilled water supply temperature can be increased in a central cooling plant based on the reduced cooling …


Supply Air Temperature Reset
General Overview On warmer days during the heating season, the supply air temperature to the zones from the AHU plant can be lowered (i.e., reset) to meet the more moderate heating demands. During cooling season, the temperature can be reset upwards during periods of moderate cooling demands. The goal of Supply Air Temperature Reset (SATR) is to use less energy to meet heating and cooling demand. When Outdoor air temperature (OAT) is moderate, the rate of heating or cooling energy supplied to the zones is moderated. Besides increasing the efficiency of the heat transfer throughout the system, there is also a reduction in the likelihood of reheat calls at variable air volume (VAV) boxes during the cooling season. In addition, the SOO modulates temperature swings in the zones, thereby improving occupant comfort. note The NYC Energy Conservation Code (Section C403.6.5) requires supply air temperature reset for all multi-zone AHUs: Multiple-zone HVAC systems shall include controls that automatically reset the supply-air temperature in response to representative building loads, or to outdoor air temperature. The controls shall be configured to reset the supply air temperature not less than 25 percent of the difference between the design supply-air temperature and the design room air temperature. note According to ASHRAE 36-2018 (“High Performance Sequences of Operation for HVAC Systems”), single-zone air handling units (AHUs) should also have a SATR. Basic Control Logic SOOs are feedback loops that employ a combination of sensors, controllers, and actuators to impact a process and maintain a desired state. For example, a thermostat provides a signal to a controller, and the controller sends a signal to the furnace. When the temperature falls below a certain setpoint, the controller sends a signal to the furnace to fire up and to turn on the air handler to provide heated air to the conditioned space. Once the temperature reaches the desired set point, the controller sends a signal to reduce the fan speed and/or to turn off the furnace. Figure 1 presents a schematic of the general principle of the supply air temperature reset (SATR) control feedback loop. If the outdoor air temperature (OAT) is moderate, and by proxy the heating, or cooling, load is not at peak condition, then the building automation system (BAS) lowers, or raises, the supply air temperature setpoint; the supply air temperature sensor provides the feedback signal. Based on the measured error, the BAS controls the supply fan and heating (or cooling) coil valve position to moderate the supply air temperature. Figure 1. Fundamental SATR control logic. Algorithm for the Sequence of Operation The algorithm is implemented differently for single-zone AHUs vs. multi-zone AHUs, and for constant volume vs. variable volume AHUs. Single-Zone AHUs Figure 2 shows the supply temperature reset algorithm for a single-zone AHU, which can be described as follows (from left to right): Figure 2. Supply air temperature reset for single-zone AHUs (ASHRAE 36-2018, Figure 5.18.4.5-3). For a high heating loop signal (peak load), the supply air temperature (SAT) setpoint (SATsp) is at its maximum. As the heating load is reduced, the SATsp is reset to a lower value. The reset for the cooling loop signal shows two curves: the dotted line (labeled SATsp) is for economizer control and the dashed line (labeled SATsp-C) is for the cooling coil valve control. The two controls use the same SAT sensor. For economizing, if the measured SAT is greater than the minimum SATsp, then the outdoor air dampers will remain open. However, the measured SAT might be below the SATsp-C value at the same time, which means the cooling coil valve remains closed. The combination of the open outdoor air damper and closed cooling coil valve is the control that is needed for economizing. As the cooling loop signal increases (indicating a higher cooling load), the SATsp-C decreases. At some point, the measured SAT exceeds the setpoint, and the cooling coil valve begins to open. For constant speed systems , the SATsp is met by changing only the heating/cooling coil valve position. For variable speed systems, the setpoint is met by changing both the heating/cooling coil valve position and the supply air flow rate. As shown in Figure 3, the control for fan speed is a function of heating/cooling loop signal, as well as OAT. The three overlapping curves for cooling show that, as OAT increases, fan speed slows down. Since warmer air holds more moisture, this logic prevents introducing too much moisture to the zones in cooling mode. Figure 3. Supply fan speed setpoint (ASHRAE 36-2018, Figure 5.18.4.5-2). Figure 4 (which is an overlay of Figures 4 and 5) shows how fan speed is coordinated with the SATsp. Following the diagram from left to right, the highest heating demand is met by maximizing the SATsp and the fan speed. Then, as the demand is reduced, the fan speed is decreased until it reaches its minimum, at which point the SATsp is gradually decreased. After the deadband, at certain breakpoints either the fan speed is increasing while SATsp is constant, or SATsp is decreasing while fan speed is constant. Figure 4. Coordination of SATR and fan speed for variable speed systems (ASHRAE 36-2018, Figure 5.18.4.5-1). Multi-Zone VAV AHUs Figure 5 shows the heating season reset curve for multi-zone AHUs. The key difference between the single-zone (Figure 2) and multi-zone curves is that the slope of the curve can vary with the number of zone requests. When there are many requests from the VAV boxes, the SATR will change quickly to meet the demand. As the number of zone requests decreases, the SATR change will be less dramatic; this is known as Trim and Response control. Figure 5. Supply air temperature reset diagram for multi-zone AHUs (ASHRAE 36-2018, Figure 5.18.4.5-3). The supply fan speed in a multi-zone VAV AHU is set to meet static discharge pressure setpoints. Conventional control uses a constant pressure setpoint; in advanced HVAC control, the pressure is reset with the number of zone cooling SAT request according to Trim and Response logic. This is further described in the Static Pressure Reset Sequence of Operation. Data to Represent the Heating and Cooling Signal The last item to consider on the above diagrams is the actual measured data that represents the heating and cooling loop signal on the x-axis. The engineering literature (Trane 2016,1 PNNL 2012,2 Davis 20163) lists the following options: Outdoor air temperature – The most implemented loop signal is OAT, due to the reliability of temperature sensors and the ease of commissioning the algorithm. High indoor humidity during cooling season, however, is a risk of using OAT. When the supply temperature setpoint is modulated, the cooling coil will be modulated, which may result in insufficient dehumidification. Using wet-bulb temperature as the loop signal would avoid this issue, but humidity sensors are not generally reliable. Zone temperature demand – Zone temperature demand is the difference between measured zone temperature and zone temperature setpoint. If the trend of zone demand is moderate (i.e., not varying dramatically) the BAS will modulate the supply temperature setpoint. For a multi-zone AHU, a weighted average of the zone demands may be used. The commissioning agent might lower the weight for a “problem” zone that keeps calling for cooling/heating; or, they might raise the weight based on the size, use or location (e.g., interior vs. perimeter) of a zone. Zone VAV box damper position – This loop signal is used less frequently. If the damper is nearly closed, the demand is low, and vice versa. Again, for a multi-zone AHU, a weighted average across the zones may be used. Return air temperature – If the return air temperature is too high (or too low, for heating), then the zone cooling demand is high and the setpoint should be raised (or lowered, for heating). Number of zone reheat calls – For a multi-zone AHU during cooling season, the supply air temperature setpoint can be raised if many zones are calling for reheat. Combination of the above – PNNL (2012) recommends using zone demand first (zone temperature, damper position, or reheat calls), followed by return air temperature, then OAT. The measurement section of this guide discusses the measurement of these data points. Evaluation of Energy Consumption The avoided energy from SATR comes from reducing the amount of thermal energy needed by the heating and cooling coils to condition mixed air, and by reducing the electrical power needed to run the AHU fans. The total energy in the mixed air is the latent heat carried by the air’s moisture and the sensible heat as measured by the dry-bulb temperature. During cooling season, the cooling coils remove latent heat (through dehumidification) along with sensible heat. During heating season, it is assumed that only sensible heat is added by the heating coils and changes in latent heat are ignored. Changes to sensible heat are proportional to the product of air flow rate and temperature change. However, changes to latent heat are proportional to the product of air flow rate and water content change, which itself is a function of change in humidity and change in temperature. SATR reduces these temperature changes. As was shown in Figure 2, the SATsp is modulated with demand. In the absence of SATR (i.e., the pre-retrofit condition) the curve would appear as a three-part step curve: 1) a heating season setpoint; 2) a deadband setpoint; and 3) a cooling season setpoint. The difference in the curves, and therefore the energy savings, is greatest at moderate demand, which is where facilities operate most during the year. The change in fan energy from SATR depends on whether the AHU is a constant volume or variable volume system. For a constant volume system, the fan operation is the same with and without the SOO. For variable volume systems with a single-zone (as seen with Figure 4), fan speed is coordinated with SATsp. Without SATR, the fan speed curve would have three parts: 1) a negatively sloped curve for heating loop signals; 2) a deadband minimum speed to meet ventilation requirements; and 3) a positively sloped curve for cooling loop signals. tip If you superimpose this curve over the fan speed curve in Figure 4, you will see that the fan may run at higher speeds at higher demand and at lower speeds at lower demand. Therefore, it is not possible to predict a priori if fan energy will be increase or decrease. Table 1. Energy-consuming components associated with the SATR SOO. System Values to be Quantified Energy Consuming Component AHU Hourly average fan motor (kWh) Hourly average OAT (F) Hourly average relative humidity (%) Supply air fan and motor AHU Average hourly air flow (cfm) Temperature difference between Mixed Air and Discharge Air (F) Heating heat exchanger AHU Average hourly air flow (cfm) Temperature difference between Mixed Air and Discharge Air (F) Cooling heat exchanger Components to Measure and Measurement Locations The measurement locations for a SATR SOO are shown in Figure 6. Figure 6. SATR SOO measurement points. The SATR SOO measurement boundary includes the mixed air, discharge air, heat exchangers, power supply for the supply fan motor, and the supply fan and motor. Interaction of SATR with other SOOs The supply air temperature reset SOO has potential interactivity with other SOOs listed below. Cumulatively, these may also interact with the overall heating plant and water- or air-cooled chilled water plant. Economizing and Direct Control Ventilation (DCV) – These two SOOs both control the outdoor air damper, which in turn impacts the temperature and relative humidity of the mixed air. The mixed air is then conditioned to meet the SATsp. While SATR operates independently of the outside air damper position, economizing and DCV will impact the amount of energy used to condition the air. Therefore, economizing and DCV should be applied consistently between pre- and post-retrofit conditions to properly evaluate the impact of SATR. Static Pressure Reset – SATR and static pressure reset have a complicated interaction. Both SOOs seek to modulate when demand is moderate. As the SATsp is modulated, the zones may call for greater air flow, which means higher pressure is generated, contrary to the goal of the static pressure reset algorithm. Taylor (2016) points out that the two algorithms operate on different time scales, and therefore concerns that they work against each other are misplaced.1 SAT is reset gradually through the day, while static pressure resets may happen frequently within an hour. Nevertheless, static pressure reset should be applied consistently between pre- and post-retrofit conditions. SATR SOO Calculation Methodology One underlying assumption regarding this SOO is that the heating and cooling loads for the zones being served do not change during the pre- and post-retrofit periods and are correlated to OAT and hours of operation. The hourly electrical energy and thermal energy associated with heating or cooling the air is summed by OAT and coincident operating hours, and a regression model is developed. This is used with climate normal year data to develop an estimate of annual fan and motor electrical energy consumption and annual heating and cooling consumption. Further Reading ASHRAE (2018). High Performance Sequences of Operation for HVAC Systems. Atlanta, GA: ASHRAE. Footnotes Trane (2016). Multiple-zone VAV systems - Finding the Right Balance for VAV Energy Savings. Trane Engineers Newsletter, 45(3). ↩︎ Pacific Northwest National Laboratory (2012). Large Commercial Buildings: Re-tuning for Efficiency - Air Handling Units: Pre-Re-Tuning and Trending and Re-Tuning. Retrieved January 2021, from https://buildingretuning.pnnl.gov/documents/chapters/ch5_air_handling.pdf ↩︎ Davis, G. (2016, August 15). HVAC codes and standards: cooling and energy efficiency. Retrieved January 15, 2021, from Consulting-Specifying Engineer: https://www.csemag.com/articles/hvac-codes-and-standards-cooling-and-energy-efficiency/ ↩︎

On warmer days during the heating season, the supply air temperature to the zones from the AHU plant can be lowered to meet the more moderate heating …


Pressure Resets

Static Pressure Reset in an AHU
General Overview Static pressure reset in an air handling unit (AHU) slows down the fan in a multi-zone AHU that supplies air to variable air volume (VAV) terminal units. The main goal is to minimize the supply fan speed to provide just enough pressure to the boxes such that the damper for the terminal unit with the highest heating or cooling demand is 100% open. The goal of static pressure reset is to use less electrical energy to meet cooling and heating loads, by lowering the AHU fan speed. When loads are moderate, and if the AHU is operated with constant static pressure, the VAV boxes will close their dampers to reduce air flow to the zones. Although zone air flows and temperatures are properly maintained, the AHU supply fan is working harder than necessary. If the fan speed is modulated, then the VAV box dampers can be opened to maintain the flow to meet the load. The zone with the greatest demand will be opened nearly 100%. note ASHRAE Standard 90.1-2019 and the NYC Energy Conservation Code (Section C403.6.8) requires static pressure reset for all multi-zone AHUs: For systems with direct digital control of individual zones reporting to the central control panel, the static pressure setpoint shall be reset based on the zone requiring the most pressure. In such case, the setpoint is reset lower until one zone damper is nearly wide open. The direct digital controls shall be capable of monitoring zone damper positions or shall have an alternative method of indicating the need for static pressure that is configured to provide all of the following: Automatic detection of any zone that excessively drives the reset logic. Generation of an alarm to the system operational location. Allowance for an operator to readily remove one or more zones from the reset algorithm. The code applies to all mechanical systems that serve multiple zones, which are required to be VAV. Basic Control Logic SOOs are essentially feedback loops that employ a combination of sensors, controllers, and actuators to impact a process and maintain a desired state. For example, a thermostat provides a signal to a controller, and the controller sends a signal to the furnace. When the temperature falls below a certain setpoint, the controller sends a signal to the furnace to fire up and to turn on the air handler to provide heated air to the conditioned space. Once the temperature reaches the desired setpoint, the controller sends a signal to reduce the fan speed and/or to turn off the furnace. Figure 1 presents a schematic of the general principle of the static pressure reset control feedback loop. For a multi-zone AHU, the static pressure of the supply air is maintained at a level such that at least one VAV box damper position is set at 100%. The pressure reset value is determined by the number of requests that are received by the building automation system (BAS). Figure 1. Fundamental static pressure reset control logic. tip ASHRAE Guideline 36 (“High-Performance Sequences of Operation for HVAC Systems”) includes a detailed algorithm based on VAV flow and damper position that can be used to determine the number of requests sent from each VAV to the BAS. Algorithm for the Sequence of Operation The reset algorithm is known as Trim and Response (T&R), where Trim indicates a decrement and Response indicates an increment. The BAS will receive VAV “requests” and adjust the pressure setpoint. This section will first define a VAV request, and then present details of the T&R algorithm. Figure 2 presents a diagram of the algorithm used to calculate requests for an individual VAV box. During a single data sample, there can be multiple requests per box, which reflects the relative urgency to reset the static pressure. Figure 2. Algorithm to calculate static pressure reset requests (Placeholder graphic, ASHRAE 36-2018, Section 5.6.8.2). The BAS calculates a weighted sum of the total number of requests from all VAV boxes that are served by the AHU. Individual boxes may be weighted more depending on the size, the use, or the location of the zone. During commissioning, a box may be weighted less if it is found to be repeatedly calling for resets. Figure 3 presents a diagram of the T&R algorithm, with the variables defined in Table 1. Table 1. Trim and Request variables (ASHRAE 36-2018, Table 5.1.14.3). Variable Definition SP0 Initial setpoint SP1 Reset setpoint SPmin Minimum setpoint SPmax Maximum setpoint I Number of ignored requests R Number of requests from zones SPtrim Trim amount SPres Respond amount The condition R>I (left side of the diagram) ensure that the pressure reset only happens when the number of requests is great enough. Note the difference in the Respond and Trim equations. For Respond, the incremental increase, SPres, is multiplied by (R-I), which allows the system to raise the static pressure quickly. Conversely, for Trim, only a gradual decrement by SPtrim is possible per time step. Note also that the setpoint is bound within the range SPmin and SPmax. Typically, the time step is set to two minutes. Figure 3. Trim and Response logic for static pressure reset. Finally, the upper right quadrant of Figure 3 shows the control loop for adjusting fan speed and VAV damper position, which is sampled more frequently than for the pressure setpoint reset. note ASHRAE 36-2018 describes the general logic, though different controls manufacturers may apply additional logic. For example, Johnson Controls (2018) implements different rules in their control logic between cooling and heating seasons. In summer, supply air temperature is fixed and static pressure is reset; in winter, static pressure is fixed and supply air temperature varies. This control scheme also turns on Trim and Response only if zones are occupied. Evaluation of Energy Consumption The avoided energy from implementing static pressure reset comes mostly from reducing the electrical power to run the AHU fans. Static pressure reset generally has minimal impact on heating and cooling energy; while pressure is decreased by reducing airflow, the amount of heating and cooling energy delivered to the space should be approximately the same. Heating and cooling reductions may occur when dramatic differences in pre- and post-retrofit space temperatures can be demonstrated. In some cases, there is overheating or underheating in some zones, which this SOO may resolve. If this SOO is being implemented as part of a complete AHU replacement, heating and cooling energy reductions may also be seen. Table 2 provides a summary of the components to be measured to arrive at the values needed to quantify the annual energy consumption and operating characteristics of an AHU with a pressure reset SOO. Table 2. Energy-consuming components associated with the static pressure reset SOO. System Quantification Values to be Quantified Energy Consuming Component AHU Hourly average fan motor (kWh) Fan and Motor AHU Average hourly air flow (cfm) Temperature difference between Mixed Air and Discharge Air Cooling Coil Components to Measure and Measurement Locations The measurement locations for a static pressure reset SOO are shown in Figure 4. Figure 4. Static pressure reset SOO measurement points. Interaction of Static Pressure Reset with other SOOs The pressure reset SOO has potential interactivity with other SOOs listed below. Cumulatively, these may also interact with the overall heating plant and water- or air-cooled chilled water plant. Economizing and Demand Controlled Ventilation (DCV) – Static pressure reset only operates when a zone is occupied, and therefore interacts with DCV. If a zone is unoccupied, DCV will call for the damper to close to the minimum airflow needed for ventilation. If more zones are unoccupied, airflow demands drop and the pressure should reset downward due to occupancy rather than lower space conditioning demands. Supply Air Temperature Reset – There is a clear interaction between supply air temperature reset and static pressure reset. If supply air temperature is lowered, then the flow – and thereby the pressure –must increase to supply the same amount of energy to a zone, and vice versa. Trane (2016) points out that these two SOOs must be finely tuned during commissioning to avoid instability.1 Seidl (2008) states that the T&R logic of these two resets are likely to be driven by different zones, and therefore a single zone is unlikely to cause instability.2 Zone Temperature Reset – BASs limit the range that occupants can reset zone temperatures to keep setpoint near design conditions. If a zone were to be reset too far from design conditions, it might become a so-called “rogue zone” (i.e., where boxes are always wide open) that then dominates the static pressure reset algorithm. Static Pressure Reset SOO Calculation Methodology One underlying assumption regarding this SOO is that the heating and cooling loads for the zones being served do not change during the pre- and post-retrofit periods and are correlated to outdoor air temperature and hours of operation. The hourly electrical energy is summed by OAT and coincident operating hours, and a regression model is developed. This is used with climate normal year data to develop an estimate of annual fan and motor electrical energy consumption. Further Reading ​​​ASHRAE. (2018). High Performance Sequences of Operation for HVAC Systems. Atlanta, GA: ASHRAE. ASHRAE. (2019). Standard 90.1-2019: Energy standard for buildings except low-rise residential buildings. ASHRAE. ​Johnson Controls. (n.d.). Air handling unit reset application note: Sequence of operation – Winter mode. Retrieved 2021, from https://docs.johnsoncontrols.com/bas/r/Metasys/en-US/Air-Handling-Unit-Reset-Application-Note/AHU-Reset-Control-System ​New York City Department of Buildings. (2020). New York City Energy Conservation Code (NYCECC). Retrieved 2021, from Section C403.6.8.: Chapter C4 Commercial Energy Efficiency: Commercial Energy Efficiency, New York City Energy Code 2020 | UpCodes Footnotes ​Trane. (2016). Multiple-zone VAV systems - Finding the Right Balance for VAV Energy Savings. Trane Engineers Newsletter, 45(3), 1-7. ↩︎ ​Seidl, R. (2008). Using Demand Based Reset Strategies. National Conference on Building Commissioning. ↩︎

Slows down the fan in a multi-zone AHU that supplies air to variable air volume terminal units.


Economizing

Waterside Economizing
General Overview When outdoor weather is relatively mild and there is still a need for cooling in a facility, waterside economizing in a central cooling plant can be implemented through a heat exchanger and a specific sequence of operation (SOO). Waterside-economizing in a water-cooled chilled water plant reduces chiller energy consumption when outdoor air temperature (OAT) and humidity conditions are suitable. While waterside economizers are implemented in a variety of ways this guidance is specifically for indirect economizing by an auxiliary heat exchanger as a system retrofit. Direct economizing by the interconnection of water circuits between the chilled water loop and condenser water loop has proven to be problematic given the debris and contaminants that can be introduced into an open cooling tower. Waterside economizers provide a cost-effective and energy-saving opportunity for a facility using a water-cooled chiller connected to an open cooling tower system and a liquid-to-liquid heat exchanger. When OAT is cold enough to use the cooling tower to chill the condenser water return temperature below the chilled water supply temperature setpoint, the chiller compressor can be turned off to achieve free cooling. Typically, the waterside economizer is turned on if the wet bulb temperature is below 45°F and the dry bulb is below 55°F. Under these conditions, a chilled water setpoint of around 55°F is achievable. note The NYC Energy Conservation Code (NYCEEC) requires waterside economizing for new water-cooled chilled water systems larger than 720,000 Btu/h. The code states that the economizer should be integrated with the chiller, which means that the economizer meets 100% of the cooling load (i.e., the chiller compressor is off) when it is cold enough or to work simultaneously with the chiller to share the load under more moderate conditions, generally when dry bulb temperature is less than 55°F and wet bulb temperature is less than 45°F. Waterside economizers can be installed in a chilled water plant with variable or constant speed pumping, though variable speed pumping provides greater savings. While airside economizers on the air handling units (AHUs) are preferred over waterside chilled water economizers due to their higher efficiency, there are certain conditions when waterside economizers are suitable. A multi-story office building that, for architectural reasons, does not allow for outdoor air intake for the AHUs is a candidate for waterside economizing. Buildings with a winter cooling load, such as a data center or museum, are also candidates for waterside economizers. Facilities where concerns about pollutants and humidity are introduced through the outdoor air intake of an airside economizer, such as a laboratory or educational building, are other applications. Basic Control Logic SOOs are essentially feedback loops that employ a combination of sensors, controllers, and actuators to impact a process and maintain a desired state. For example, a thermostat in a room sends a signal when the temperature falls below a certain setpoint, and the boiler system controls a pump to circulate hot water to the radiator to increase the temperature in the space. If the water temperature in the boiler is below a certain setpoint, the controls initiate the firing sequence for the boiler, and it continues to run until the boiler high temperature setpoint is reached. Figure 1 presents a schematic of the general principle of the waterside economizing control feedback loop. If the OAT is within the economizing range (when the dry bulb temperature is less than 55°F and the wet bulb temperature is less than 45°F), the economizer algorithm is turned on to alter the operation of the central cooling plant. The feedback loop with the chilled water supply temperature operates as normal to ensure the central cooling plant meets the cooling load. However, within the central cooling plant, a three-way valve directs the chilled water loop to bypass the chiller and go through a heat exchanger with the condenser water loop. This redirection essentially removes the refrigeration cycle from the heat transfer process. While the compressor is turned off to save energy, the cooling tower fans, condenser and chilled water pumps are still on. Above the economizing temperature threshold, the three-way valve may partially direct the chilled water through the heat exchanger with the rest continuing to the chiller. In this case, the chiller compressor continues to run to share the load with the economizer. Figure 1. Basic waterside economizing control logic. Algorithm for the Sequence of Operation This section describes the control algorithm to determine when economizing is turned on and off, and whether the economizing mode is full-load or partial-load. Changes in the operation of the components of the central cooling plant are shown in the flowchart in Figure 2. Figure 2. Flow chart of waterside economizers. When outdoor dry bulb and wet bulb temperatures are low enough to enable waterside economizers, the optimum control sequence of the SOO is described below. Site-specific conditions may require varying this control strategy. The chilled water supply temperature (CHWST) setpoint is modulated as limits allow while meeting the cooling demand. The chilled water (CHW) flow rate is adjusted to match the desired CHWST setpoint. With known parameters, such as the current CHW flow rate, wet bulb temperature, and the design conditions of the heat exchanger (HX) and the cooling tower, the CHW temperature leaving the HX can be predicted (PHXLWT in the diagram). According to Taylor (2014), the waterside economizer should be disabled when it cannot provide at least a 1°F reduction between the entering and exiting CHW.1 Chillers are disabled when the economizer can supply the entire cooling load; conversely, if the cooling demand is not met by the current chilled water supply, chillers are turned on. As many tower cells as possible should be enabled while making sure the tower flow is within the minimum limits. Condenser water should be maintained at a minimum flow rate that can match the CHW flow at the desired supply temperature setpoint. Meanwhile, the reduced condenser water flow must be compatible with the tower limits through controlling pump speed, staging pumps, and modulating the HX valves. The condenser water supply temperature (CWST) (entering the HX) equals the HXLWT (leaving the HX) minus the HX approach temperature. The condenser water return temperature (leaving the HX) depends on the cooling load supplied by the HX. In other words, the cooling tower speed and approach are modulated to provide the desired condenser water temperature that can cool the chilled water entering the HX to meet the cooling demand at current wet bulb temperature. Evaluation of Energy Consumption Waterside economizers alter the electrical energy consumption of all the motorized components in a central cooling plant. Due to the highly interactive effects between the indoor loads, the CHW loop, condenser water loop, chiller, indoor loads, and outdoor conditions, the energy calculations for a waterside economizer must be done on an hourly basis. The energy consumption of a water-cooled chilled water plant is the sum of the electrical energy associated with all the systems associated with the plant. Key values that need to be quantified to estimate annual energy consumption are shown in Table 1. Table 1. Energy-consuming components associated with waterside economizer SOO. System Quantification Values to be Quantified Energy Consuming Component Chilled water loop electricity usage (kWh) Average hourly pump motor (kWh) Hours of operation of the pumps Pump motor Water-cooled chiller compressor electricity usage (kWh) Average hourly chiller compressor motor (kWh) Hours of operation of the compressor Compressor motor Cooling load on building / Heat rejected to the outdoors (Btu/h) Average hourly thermal load on chiller evaporator (Btu/h) Evaporator Water-cooled chiller condenser heat transfer (Btu/h) Average hourly Btu/h rejected to the condenser water loop Condenser Condenser water loop fan electricity usage (kWh) Average hourly fan motor (kWh) Total operating time for the fans Cooling tower fan motor Condenser water loop pump electricity usage (kWh) Average hourly pump motor (kWh) Total operating time for the pumps Pump motor Waterside economizer heat transfer (Btu/h) Average hourly Btu/h delivered to the chilled water loop Average hourly Btu/h rejected to the chilled water loop Waterside economizer pump electricity usage (kWh) (if present) Average hourly pump motor (kWh) Total operating time for the pumps Pump motor (if present) Components to Measure and Measurement Locations Refer to the chilled water loop, water-cooled chiller, condenser water loop, and waterside economizer system descriptions for specific components to measure. The measurement boundary and locations for a waterside economizer SOO is highlighted in Figure 3. Figure 3. Waterside economizer measurement points. Interaction of Waterside Economize with other SOOs A waterside economizer has potential interactivity with the entire water-cooled chilled water plant. One key assumption when analyzing a waterside economizer is that the cooling loads and operating hours are not changing between the pre- and post-retrofit periods. Condenser Water Supply Temperature Reset – CWST reset leads to an increase in the amount of time the cooling tower can lower return condenser water temperatures below the CWST setpoint. Waterside economizers inherently incorporate CWST reset. Hence, when evaluating the energy savings from waterside economizing, it is important to document whether an SOO for CWST reset was present pre-retrofit. Waterside Economizer SOO Calculation Methodology The annual energy consumption of a water-cooled chilled water plant with a waterside economizer is the sum of the energy for each component system for each hour of the year. The model used must consider the hourly cooling loads and facility operations, outdoor conditions, operating parameters of the systems in the plant, and operations of associated AHU plants. Due to the highly interactive nature of the water-cooled chilled water plant, a detailed plant model or whole facility energy model is needed to estimate annual consumption, based on the actual operational parameters and measured energy consumption of the various systems and components. Footnotes ​​​Taylor, S. (2014). How to design & control waterside economizers. ASHRAE Journal, 56, 30-36. ↩︎

When outdoor weather is relatively mild and there is still a need for cooling in a facility, waterside economizing in a central cooling plant can be …


Airside Economizing
General Overview Airside economizing saves energy by using outdoor air to cool a facility instead of the chilled water plant, or direct expansion cooling in an air handling unit (AHU), when the outdoor air temperature (OAT) meets certain criteria, as described in the NYC Energy Conservation Code (Table C403.5.3.3). Basic Control Logic Sequences of operation (SOOs) are essentially feedback loops that employ a combination of sensors, controllers, and actuators to impact a process and maintain a desired state. For example, a thermostat provides a signal to a controller, and the controller sends a signal to the furnace. When the temperature falls below a certain setpoint, the controller sends a signal to the furnace to fire up and to turn on the air handler to provide heated air to the conditioned space. Once the temperature reaches the desired setpoint, the controller sends a signal to reduce the fan speed and/or to turn off the furnace. Figure 1 presents a schematic of the general principle of the economizing control feedback loop. If OAT is within the economizing range, the outdoor air damper (OAD) position is opened 100%. The control signals to the AHU are adjusted to consider that the OAD is 100% open while still meeting the zone temperature setpoints. Figure 1. Fundamental airside economizing control logic. The goal of economizing is to use less energy to meet the cooling load. The AHU draws in outdoor air when the outdoor air temperature and humidity are in a range to allow it to cool interior spaces. Optimizing the amount of outdoor air reduces the amount of energy needed to condition the space. note ASHRAE Standard 90.1-2019 and NYC code requires that outdoor air be introduced when conditions are warranted. This SOO is suitable for all AHUs with variable OAD position control, including constant air volume, two-speed air volume, and variable volume AHUs. Control strategies may be based on dry bulb temperature or enthalpy. Algorithm for the Sequence of Operation Economizing is generally implemented using three methods: 1. Dry Bulb Temperature The OAD position opens when the dry bulb temperature is within a suitable range. In NYC, the maximum temperature at which the energy code allows for economizing is 65oF. As OAT approaches the discharge air temperature (DAT), the damper position is modulated, and the cooling coil is turned off (modulated economizer mode). At the higher end of this range, the OAD position is 100% and the cooling coil is modulated to provide sufficient cooling and dehumidification (integrated economizer mode). Dry bulb is the simplest economizer control method. 2. Dry Bulb Temperature Difference The OAD position opens when the dry bulb temperature of the return air is higher than the dry bulb temperature of the outdoor air. As OAT approaches DAT, the damper position is modulated, and the cooling coil is turned off (modulated economizer mode). At the higher end of this range, the OAD position is 100% and the cooling coil is modulated to provide sufficient cooling and dehumidification (integrated economizer mode). 3. Enthalpy There are two methods of enthalpy economizing: Single Enthalpy – This control method takes humidity into account by measuring the enthalpy of air instead of dry bulb temperature; economizing is used only below 28 Btu/lb. When humidity is high, reducing the outdoor air fraction lowers the cooling coil demand, as less moisture needs to be removed by condensing it on the coil. Dual Enthalpy – Dual enthalpy control turns off economizing when outdoor air enthalpy is greater than return air enthalpy. Evaluation of Energy Consumption Economizing only affects the cooling energy consumption needed to condition the outdoor air and is not used during heating season. The total energy embodied in the outdoor air entering the system is equal to the latent heat carried by the moisture in the air plus the sensible heat as measured by the dry bulb temperature. The cooling coils remove latent heat through dehumidification. When the dry bulb temperature or enthalpy is in the economizing range, the OAD opens and the cooling coil valve is modulated or turned off. Therefore, to evaluate the benefit of economizing, it is only necessary to calculate the change in energy removed from outdoor air when conditions warrant economizing. The AHU also consumes electrical energy to drive the supply and return fans. The on/off scheduling of the fan motors, speed modulation through VFDs (if present), and the system pressure will impact the energy consumption. Economizing only modulates the volume of outdoor air introduced to the AHU. Unless the fan motor is changed or a VFD is installed as a part of the retrofit, it is assumed that fan speed and power do not change between the pre- and post-retrofit conditions. Table 1 provides a summary of the components to be measured to arrive at the values needed to quantify the annual energy consumption and operating characteristics of an AHU with an airside economizing SOO. Table 1. Energy consuming components associated with the airside economizing SOO. System Quantification Values to be Quantified Energy Consuming Component AHU Average hourly air flow (cfm) Fan Motor AHU Temperature and relative humidity (RH) of return air Outdoor air Mixed air Discharge air Cooling Coil Components to Measure and Measurement Locations The measurement locations for the airside economizing SOO are shown in Figure 2. Figure 2. Airside economizing SOO measurement points. Interaction of Airside Economizing with other SOOs Airside economizing can interact with demand-controlled ventilation, in that the airside economizing will inherently over ventilate a space but is doing so with no chilled water. Airside Economizing SOO Calculation Methodology One underlying assumption regarding this SOO is that the heating and cooling loads for the zones being served do not change during the pre- and post-retrofit periods and are correlated to OAT and hours of operation. The sensible and latent energy associated with cooling the air is summed by OAT and coincident operating hours, and a regression model is developed. This is used with climate normal year data to develop an estimate of annual cooling consumption. Further Reading ASHRAE (2018). High Performance Sequences of Operation for HVAC Systems. Atlanta, GA: ASHRAE.

Uses outdoor air to cool a facility instead of the chilled water plant, or direct expansion cooling in an air handling unit, when the outdoor air …


Ventilation

Search Results: 0 Plants related to ""

Please enter another search term.

Search Results: 0 Systems related to ""

Please enter another search term.

Search Results: 0 Components related to ""

Please enter another search term.

Search Results: 0 Calculation related to ""

Please enter another search term.

Search Results: 0 Measurements related to ""

Please enter another search term.

Search Results: 0 Sequences of Operations related to ""

Please enter another search term.