Exhaust plenum systems and methods for ventilation system

Abstract

To provide exhaust plenum systems and methods for a ventilation system.SOLUTION: Described herein is a ventilation system for a building that includes an air source heat pump and an exhaust plenum system. The air source heat pump may include a compressor, a condenser, a reversing valve, and an evaporator. The exhaust plenum system is configured to mix a building infrastructure exhaust airflow with an ambient airflow to provide an exhaust-ambient airflow mixture to the air source heat pump. The use of the exhaust-ambient airflow mixture improves the efficiency of the air source heat pump.SELECTED DRAWING: Figure 7

Description

[Technical Field]

[0001] (CROSS-REFERENCE TO RELATED APPLICATIONS) This application claims priority to U.S. Patent Application No. 18 / 762,157, filed July 2, 2024, which claims priority to U.S. Provisional Patent Application No. 63 / 660,233, filed June 14, 2024, the entire contents of each of which are incorporated herein by reference. [Background technology]

[0002] As electrification and carbon neutral initiatives encourage the use of clean energy (e.g., electricity generated by the sun, wind, water, etc.) for heating and cooling needs as an alternative to the use of fossil fuels, the need for energy efficiency solutions is increasing for systems currently being implemented and that will be implemented in the future. Thermodynamic heating and cooling systems are utilized to condition clean, comfortable air for both commercial and residential buildings, and current processes have been understood for quite some time.

[0003] 1 and 16 (Pressure-Enthalpy Refrigeration Cycle of a Conventional Thermodynamic Cooling System at 95°F Ambient Airflow Temperature), which respectively show a conventional thermodynamic cooling (e.g., air conditioning or refrigeration) system and its associated pressure-enthalpy (PH) refrigeration cycle. In some embodiments, a conventional thermodynamic cooling ventilation system 100 comprises a compression unit 102, a condensing unit 104, an evaporative unit 106, and a metering device 108 (e.g., an expansion valve) in fluid communication for the purpose of circulating a fluid (e.g., a refrigerant) that removes heat from an operating environment. When the heat pump functions as a conventional thermodynamic cooling and ventilation system 100, reversing valves 110, disposed between the compression unit 102 and the condensing unit 104 and between the compression unit 102 and the evaporating unit 106, are configured so that fluid exiting a compressor outlet 112 of the compression unit 102 is directed to the condensing unit 104 (e.g., via the reversing valve 110), and fluid exiting the evaporating unit 106 is directed to a compressor inlet 114 of the compression unit 102 (e.g., via the reversing valve 110). More specifically, when a (e.g., refrigerant) fluid is in a liquid state, the (e.g., refrigerant) fluid absorbs heat and transitions from the liquid state to a gaseous or vapor state. When a (e.g., refrigerant) fluid is in a gas / vapor state, the (e.g., refrigerant) fluid releases heat as it transitions from the gaseous state to the liquid state.

[0004] For a cooling operation, a (e.g., refrigerant) fluid enters the compression unit 102 (e.g., via the compressor inlet 114) as a low-pressure saturated gas / vapor (point C). The compression unit 102 compresses the (e.g., refrigerant) fluid such that it comprises high-pressure saturated gas / vapor upon exiting the compression unit (e.g., via the compressor outlet 112) (point D). The high-pressure saturated gas / vapor travels through the reversing valve 110 and enters the condensing unit 104 (point E).

[0005] In the condensing unit 104, the high-pressure saturated gas / vapor condenses, transitioning from a high-pressure saturated gas / vapor to a high-pressure mixture having a liquid portion and a gas / vapor portion, and then to a saturated high-pressure liquid. The condensation process (point E to point F) releases heat to the (e.g., external or outdoor) environment 116. The saturated high-pressure condensed liquid exiting the condensing unit 104 (point F) then proceeds to a metering device 108 (e.g., an expansion valve) (point G).

[0006] A metering device 108 (e.g., an expansion valve) restricts fluid flow, reducing the pressure and transitioning the saturated, high-pressure condensed liquid to a low-pressure mixture having a liquid portion and a gas / vapor portion (Point A). The low-pressure mixture having a liquid portion and a gas / vapor portion enters the evaporation unit 106 (Point A). The evaporation unit 106 (Point A) transitions the low-pressure mixture having a liquid portion and a gas / vapor portion to a low-pressure saturated gas / vapor (Point B). The transition (Point A to Point B) absorbs heat from the (e.g., interior or indoor) environment 118. The heated, low-pressure saturated gas / vapor proceeds to the compressor inlet 114 (Point C) of the compression unit 102, and the refrigeration cycle repeats.

[0007] Pressure, temperature, and enthalpy values ​​for a typical refrigeration cycle are shown in Table I. More specifically, with reference to Table I and Figure B, between points A and B, the low-temperature, low-pressure fluid (e.g., a mixture of liquid and gas / vapor) from the metering device 108 enters the evaporation unit 106, causing an increase in enthalpy, which cools the (e.g., interior or indoor) environment 118. Between points B and C, the low-temperature, low-pressure fluid (e.g., gas / vapor) becomes saturated gas / vapor as it proceeds to the compression unit 102, causing a slight increase in temperature and enthalpy. [Table 1]

[0008] Between points C and D, the low-temperature, low-pressure fluid (e.g., saturated gas / vapor) enters the compression unit 102, where the fluid is compressed to provide a high-temperature, high-pressure fluid (e.g., saturated gas / vapor). Between points D and E, the high-temperature, high-pressure fluid (e.g., saturated gas / vapor) proceeds to the condensing unit 104, causing a slight decrease in enthalpy. Between points E and F, the high-temperature, high-pressure fluid (e.g., saturated gas / vapor) transitions to a high-temperature, high-pressure fluid (e.g., saturated liquid), resulting in a more significant decrease in enthalpy. Heat from the condensing unit 104 is exchanged into the (e.g., external or outdoor) environment 116.

[0009] Between points F and G, the temperature and enthalpy of the high temperature, high pressure fluid (e.g., saturated liquid) decreases slightly as the saturated liquid enters a metering device (e.g., expansion valve) 40. Between points G and A, the high temperature, high pressure fluid (e.g., saturated liquid) transitions to a low temperature, low pressure fluid (e.g., liquid and gas / vapor mixture) with nearly the same enthalpy. The cycle repeats at this point.

[0010] 2 and 17 (Pressure-Enthalpy Refrigeration Cycle of a Conventional Thermodynamic Heating and Ventilation System at 0°F Ambient Airflow Temperature), a conventional thermodynamic heating and ventilation system and its associated pressure-enthalpy (PH) refrigeration cycle are shown, respectively. In some embodiments, the conventional thermodynamic heating and ventilation system 200 also comprises a compression unit 102, a condensing unit 104, an evaporative unit 106, and a metering device 108 (e.g., an expansion valve) in fluid communication for the purpose of circulating a heat-adding (e.g., refrigerant) fluid within the operating environment. Advantageously, when the heat pump functions as a conventional thermodynamic heating and ventilation system 200, the reversing valves 110, which are positioned between the compression unit 102 and the condensing unit 104 and between the compression unit 102 and the evaporating unit 106, are configured so that fluid exiting the compression equipment outlet 112 of the compression unit 102 is directed to the condensing unit 104 (e.g., via the reversing valve 110), and fluid exiting the evaporating unit 106 is directed to the compressor inlet 114 of the compression unit 102 (e.g., via the reversing valve 110).

[0011] For a heating operation, a (e.g., refrigerant) fluid enters the compression unit 102 (e.g., via compressor inlet 114) as a low-pressure, low-temperature saturated gas / vapor. The compression unit 102 compresses the (e.g., refrigerant) fluid, transitioning the fluid from a low-pressure, low-temperature saturated gas / vapor to a high-pressure, high-temperature (e.g., superheated) saturated gas / vapor. Condensation of the (e.g., refrigerant) fluid releases heat to the interior or indoor environment 118. More specifically, the incoming (e.g., refrigerant) fluid transitions from a high-pressure, high-temperature saturated gas / vapor to a saturated liquid.

[0012] The (e.g., refrigerant) fluid then proceeds to a metering device 108 (e.g., an expansion valve). The metering device 108 restricts the flow of the (e.g., refrigerant) fluid, reducing its pressure and temperature. The low-temperature, low-pressure fluid (e.g., saturated liquid) then enters the evaporation unit 106, which absorbs heat from the (e.g., external or outdoor) environment 116, changing the fluid from a low-temperature, low-pressure liquid to a low-temperature, low-pressure gas / vapor. The (e.g., refrigerant) fluid then proceeds to the compressor inlet 114 of the compression unit 102, and the heating cycle repeats.

[0013] Pressure, temperature, and enthalpy values ​​for a typical heating cycle are shown in Table II. More specifically, with reference to Table II and Figure 17, between points A and B, the low-temperature, low-pressure fluid (e.g., a mixture of liquid and gas / vapor) from metering device 108 (at point G) enters evaporation unit 106, causing an increase in enthalpy, which draws heat from the (e.g., external or outdoor) environment 116. Between points B and C, the low-temperature, low-pressure mixture of liquid and gas / vapor becomes a low-temperature, low-pressure saturated gas / vapor as it proceeds through reversing valve 110 to compression unit 102, causing a slight increase in temperature and enthalpy. [Table 2]

[0014] Between points C and D, the low-temperature, low-pressure fluid (e.g., saturated gas / vapor) enters the compression unit 102, where it is compressed to provide a high-temperature, high-pressure (e.g., superheated) fluid (e.g., saturated gas / vapor). Between points D and E, the high-temperature, high-pressure fluid (e.g., saturated gas / vapor) proceeds through the reversing valve 110 to the condensing unit 104, causing a slight decrease in enthalpy. Between points E and F, the high-temperature, high-pressure fluid (e.g., saturated gas / vapor) transitions to a high-temperature, high-pressure fluid (e.g., saturated liquid), resulting in a more significant decrease in enthalpy. Heat from the condensing unit 104 is exchanged into the (e.g., interior or indoor) environment 118.

[0015] Between points F and G, the temperature and enthalpy of the high temperature, high pressure fluid (e.g., saturated liquid) decreases slightly as the saturated liquid enters the metering device 108 (e.g., expansion valve). Between points G and A, the high temperature, high pressure fluid (e.g., saturated liquid) transitions to a low temperature, low pressure fluid (e.g., a mixture of liquid and gas / vapor) with nearly the same enthalpy. The cycle repeats at this point.

[0016] Problematically, during heating operation, a larger pressure and temperature change (i.e., delta) exists between the high pressure side of the refrigeration cycle and the low pressure side of the refrigeration cycle. In fact, the suction temperature proximate the compressor inlet 114 of the compression unit 102 becomes more of a limiting factor as the ambient temperature in the (e.g., exterior or outdoor) environment 116 decreases further (e.g., to temperatures below zero), affecting the ability of the conventional thermodynamic heating and ventilation system 200 to operate effectively. [Table 3]

[0017] Referring to Table III, which illustrates an example at 0 degrees ambient for heating mode, the condenser capacity of a conventional thermodynamic heating and ventilation system is 186,100 BTUH and the coefficient of performance (COP) efficiency is 1.78. COP is a dimensionless value that measures the electrical efficiency of a heating and cooling system.

[0018] In current thermodynamic cooling systems, when high-pressure saturated gas / vapor condenses in the condensing unit 104 (from point E to point F), the process emits heat to the (e.g., external or outdoor) environment 116. In current thermodynamic heating systems, when low-pressure, low-temperature liquid evaporates in the evaporating unit 106, the process absorbs heat from (thereby emitting cooling) the (e.g., external or outdoor) environment 116.

[0019] This heat / cooling exhaust, a by-product of the thermodynamic process, is not yet utilized, and the carbon dioxide footprint of the system that utilizes this exhaust is reduced, costs are decreased, and system efficiency is increased. Additionally, exhaust from other building infrastructure systems can also be utilized to further increase the efficiency and electrical performance of the building ventilation system. Summary of the Invention [Means for solving the problem]

[0020] In one aspect, a ventilation system having an exhaust plenum system for improved heating and cooling of a building is provided. The ventilation system includes an air-source heat pump (ASHP) and an exhaust plenum system. The ASHP includes an ASHP coil and a source / sink fan. The exhaust plenum system includes an exhaust plenum system open grate, and the exhaust plenum system is configured to collect building infrastructure exhaust airflow and direct the building infrastructure exhaust airflow to the exhaust plenum system open grate. During operation, the building infrastructure exhaust airflow is combined with an ambient airflow to create an exhaust-ambient airflow mixture. The exhaust-ambient airflow mixture is directed through the source / sink fan to pass around the ASHP coil, and the ASHP is operable to extract an additional amount of energy from the exhaust-ambient airflow mixture compared to the amount of energy extracted from the ambient airflow mixture alone.

[0021] In another aspect, a method for improved heating and cooling of a building using an exhaust plenum system is provided. The method includes directing an exhaust flow, including a building infrastructure exhaust airflow, into an exhaust plenum system toward an air-source heat pump (ASHP). The exhaust plenum system may include an exhaust plenum system open grate and be positioned adjacent to the ASHP. During operation, the exhaust flow may be mixed with an ambient airflow entering the exhaust plenum system through the exhaust plenum system open grate to create an exhaust-ambient airflow mixture. The exhaust-ambient airflow mixture may pass around an ASHP coil of the ASHP. The ASHP extracts an additional amount of energy from the exhaust-ambient airflow mixture compared to the amount of energy extracted from the ambient airflow mixture alone.

[0022] In a further aspect, a ventilation system for a building includes an air-source heat pump including a compressor, a condenser, a reversing valve, and an evaporator, and an exhaust plenum system configured to mix a building infrastructure exhaust airflow with an ambient airflow and provide the exhaust-ambient airflow mixture to either the evaporator or the condenser of the air-source heat pump. The exhaust-ambient airflow mixture includes an additional amount of energy to be extracted by the evaporator or condenser from the exhaust-ambient airflow mixture compared to the amount of energy extracted from the ambient airflow mixture alone, thereby improving the efficiency of the air-source heat pump.

[0023] In yet another aspect, a method for ventilating a building is provided that includes admitting an airflow into an air-source heat pump via a source / sink fan, passing the airflow over an evaporator or condenser using the source / sink fan, collecting energy from the evaporation or condensation of the airflow, converting the airflow to a building infrastructure exhaust airflow, exhausting the building infrastructure exhaust airflow from the evaporator or condenser, admitting the building infrastructure exhaust airflow into an exhaust plenum, passing the building infrastructure exhaust airflow through the exhaust plenum, exiting the building infrastructure exhaust airflow from the exhaust plenum, mixing the building infrastructure exhaust airflow with an ambient airflow, thereby creating an exhaust-ambient airflow mixture, and directing the exhaust-ambient airflow mixture over the evaporator or condenser to restart the cycle of converting the airflow to a building infrastructure exhaust airflow. The present invention provides, for example, the following items. (Item 1) A ventilation system (300) having an exhaust plenum system for improved heating and cooling of a building, comprising: An air source heat pump (ASHP), comprising: ASHP coil and Source / Think Fan ASHP, which has The exhaust plenum system includes an open grille and an exhaust plenum, the exhaust plenum is configured to collect building infrastructure exhaust airflow, including air and / or waste heat from industrial processes, from multiple sources within the building and direct the building infrastructure exhaust airflow to the exhaust plenum system open grate; the directed building infrastructure exhaust airflow exits the exhaust plenum system open grate into an outdoor environment and combines with ambient airflow outside the exhaust plenum system to create an exhaust-ambient airflow mixture; the source / sink fan is operable to direct the exhaust-ambient airflow mixture past and around the ASHP coil; an exhaust plenum system, wherein the ASHP coil is operable to extract an additional amount of energy from the exhaust-ambient airflow mixture compared to the amount of energy extracted from the ambient airflow mixture alone; A ventilation system comprising: (Item 2) The ventilation system of the preceding item, wherein the exhaust plenum system is made of a durable material. (Item 3) 10. The ventilation system of claim 9, wherein the exhaust plenum system comprises a heating coil configured to inject heat into the building infrastructure exhaust airflow. (Item 4) 10. The ventilation system of claim 1, wherein the heating coil uses hot water, steam, or electricity to generate heat. (Item 5) The ventilation system of any one of the preceding items, wherein the waste heat is heat from a boiler, data center server, computer equipment, air compressor, steam system, dryer exhaust, oven, stove, cooking appliance, home appliance, generator, or turbine. (Item 6) 1. A method for improved heating and cooling of a building using an exhaust plenum system in conjunction with a ventilation system, comprising: directing building infrastructure exhaust airflow, including air and / or waste heat from industrial processes, from multiple sources within the building into an exhaust plenum toward an air source heat pump (ASHP); the exhaust plenum system includes an exhaust plenum system open grate that allows the building infrastructure exhaust airflow to exit the exhaust plenum into an outdoor environment, the exhaust plenum system open grate being positioned adjacent to the ASHP; mixing the building infrastructure exhaust airflow with an ambient airflow in the outdoor environment outside the exhaust plenum system to create an exhaust-ambient airflow mixture; passing the exhaust air-ambient airflow mixture around an ASHP coil of the ASHP; extracting an additional amount of energy from the exhaust-ambient airflow mixture via the ASHP coil compared to the amount of energy extracted from the ambient airflow mixture alone; A method comprising: (Item 7) 10. The method of claim 1, further comprising: venting the exhaust-ambient airflow mixture to the outside through a top of a source / sink fan. (Item 8) 10. The method of claim 1, further comprising injecting heat into the building infrastructure exhaust airflow using a heating coil. (Item 9) 10. The method of claim 1, wherein the heating coil utilizes hot water, steam, or electricity to generate the heat. (Item 10) 1. A ventilation system for a building, comprising: an air source heat pump including a compressor, a condenser, a reversing valve, and an evaporator; 1. An exhaust plenum system comprising: collecting a building infrastructure exhaust airflow, including air and / or waste heat from industrial processes, from a plurality of sources within the building; directing said building infrastructure exhaust airflow through an exhaust plenum system open grate; mixing the building infrastructure exhaust airflow with an ambient airflow in an outdoor environment outside the exhaust plenum system and providing an exhaust air-ambient airflow mixture to either the evaporator or the condenser of the air-source heat pump, the exhaust air-ambient airflow mixture providing an additional amount of energy to be extracted by the evaporator or the condenser from the exhaust air-ambient airflow mixture compared to the amount of energy extracted from the ambient airflow mixture alone, improving efficiency of the air-source heat pump; an exhaust plenum system configured to A ventilation system comprising: (Item 11) The ventilation system of any one of the preceding items further comprises ductwork coupled at a first end to a building infrastructure system that generates a building infrastructure exhaust airflow and coupled at a second end to the exhaust plenum system. (Item 12) 10. The ventilation system of claim 1, wherein the exhaust plenum system comprises galvanized steel or aluminum. (Item 13) 10. The ventilation system of claim 1, wherein the building infrastructure exhaust airflow includes air passed over a water vapor piping system, an electrical panel, an appliance, a room with a window, or a vehicle parking structure. (Item 14) The exhaust plenum system is an exhaust plenum system open grate for allowing ambient airflow to mix with said building infrastructure exhaust airflow and providing said exhaust-ambient airflow mixture; 10. The ventilation system according to claim 9, further comprising: (Item 15) The exhaust plenum system is a plurality of duct connections, one or more of the plurality of duct connections equipped with a damper or louver operable to regulate the building infrastructure exhaust airflow and prevent backflow of the building infrastructure exhaust airflow when the ventilation system is not operating; 10. The ventilation system according to claim 9, further comprising: (Item 16) 10. The ventilation system of claim 9, wherein the exhaust plenum system comprises an exhaust plenum system open grate formed from passages adjacent to the air source heat pump. (Item 17) 1. A method for ventilating a building, comprising: admitting an airflow into the air source heat pump via a source / sink fan; passing the airflow over an evaporator or a condenser using the source / sink fan; collecting energy from the evaporation or condensation of said air stream; converting said airflow into a building infrastructure exhaust airflow from multiple sources within said building, said airflow including air and / or waste heat from industrial processes; Discharging the building infrastructure exhaust air stream from the evaporator or the condenser; collecting the building infrastructure exhaust airflow in an exhaust plenum of an exhaust plenum system; passing the building infrastructure exhaust airflow through the exhaust plenum; exiting the building infrastructure exhaust airflow from the exhaust plenum through an exhaust plenum system open grate of the exhaust plenum system; exhausting the building infrastructure exhaust air stream from the building; mixing the building infrastructure exhaust airflow with an ambient airflow in an outdoor environment outside the exhaust plenum system, thereby creating an exhaust-ambient airflow mixture; directing said exhaust air-ambient airflow mixture across said evaporator or said condenser to restart the cycle of converting said airflow from said evaporation or condensation into building infrastructure exhaust airflow; A method comprising: (Item 18) 10. The method of claim 9, wherein the exhaust air-ambient air flow mixture provides an additional amount of energy for extraction by the evaporator or the condenser from the exhaust air-ambient air flow mixture compared to the amount of energy extracted from the ambient air flow mixture alone, improving the efficiency of the air-source heat pump. (Item 19) 10. The method of claim 1, wherein the exhaust air-ambient air flow mixture is recycled once by the air source heat pump. (Summary) Described herein is a ventilation system for a building that includes an air-source heat pump and an exhaust plenum system. The air-source heat pump may include a compressor, a condenser, a reversing valve, and an evaporator. The exhaust plenum system is configured to mix a building infrastructure exhaust airflow with an ambient airflow and provide the exhaust-ambient airflow mixture to the air-source heat pump. The use of the exhaust-ambient airflow mixture improves the efficiency of the air-source heat pump. [Brief explanation of the drawings]

[0024] [Figure 1] FIG. 1 illustrates a conventional thermodynamic cooling system.

[0025] [Figure 2] FIG. 2 illustrates a conventional thermodynamic heating and ventilation system.

[0026] [Figure 3] FIG. 3 illustrates a functional block diagram of a thermodynamic heating and ventilation system equipped with an exhaust plenum system, according to an embodiment.

[0027] [Figure 4] FIG. 4 illustrates an exemplary method for an exemplary ventilation system.

[0028] [Figure 5] FIG. 5 illustrates an exemplary method for an exemplary ventilation system.

[0029] [Figure 6A] FIG. 6A illustrates a top-down view of an example air-source heat pump with an exhaust plenum system, according to an embodiment of the disclosed subject matter.

[0030] [Figure 6B] FIG. 6B illustrates a side view of an example of an air-source heat pump with an exhaust plenum system, according to an embodiment of the disclosed subject matter.

[0031] [Figure 6C] FIG. 6C illustrates another side view of an example air-source heat pump with an exhaust plenum system, according to an embodiment of the disclosed subject matter.

[0032] [Figure 6D] FIG. 6D illustrates a side view of an example of an air-source heat pump with an exhaust plenum system, according to an embodiment of the disclosed subject matter.

[0033] [Figure 7] FIG. 7 illustrates an example of a packaged direct expansion air source heat pump equipped with an exhaust plenum system, according to an embodiment.

[0034] [Figure 8A] FIG. 8A illustrates a pressure-enthalpy refrigeration cycle chart of a thermodynamic heating ventilation system equipped with an exhaust plenum system as disclosed herein at 0° F. ambient airflow temperature.

[0035] [Figure 8B]FIG. 8B illustrates a table of exemplary performance values ​​for an exemplary thermodynamic heating and ventilation system equipped with an exhaust plenum system having a pressure-enthalpy refrigeration cycle as shown in the exemplary chart of FIG. 8A.

[0036] [Figure 8C] FIG. 8C illustrates a table displaying the condenser capacity and efficiency of an exemplary thermodynamic heating and ventilation system equipped with an exhaust plenum system having a pressure-enthalpy refrigeration cycle as shown in the exemplary chart of FIG. 8A.

[0037] [Figure 8D] FIG. 8D illustrates a table displaying the heating capacities of a standard air-source heat pump and an air-source heat pump with an exhaust plenum system having a pressure-enthalpy refrigeration cycle as shown in the example chart of FIG. 8A.

[0038] [Figure 9] FIG. 9 illustrates a table displaying exhaust-ambient airflow mixture temperatures according to an embodiment of the disclosed subject matter.

[0039] [Figure 10A] FIG. 10A illustrates a graph displaying an exemplary comparison of heating capacity of a standard air-source heat pump versus an exemplary air-source heat pump with an exhaust plenum system as described herein as a function of temperature.

[0040] [Figure 10B] FIG. 10B illustrates a table displaying an exemplary comparison of cooling capacity of the standard air-source heat pump of FIG. 10A versus an exemplary air-source heat pump with an exhaust plenum system.

[0041] [Figure 11A] FIG. 11A illustrates a graph displaying exemplary cooling capacities of a standard air-source heat pump and an exemplary air-source heat pump with an exhaust plenum system as a function of temperature as described herein.

[0042] [Figure 11B] FIG. 11B illustrates a table depicting example heating capacities of an example air-source heat pump with an exhaust plenum system provided by several different ventilation system modules.

[0043] [Figure 11C] FIG. 11C illustrates a chart depicting the cooling capacity of an air-source heat pump with an exhaust plenum system provided by several different ventilation system modules.

[0044] [Figure 12A] FIG. 12A illustrates a graph displaying the total monthly output of a standard air-source heat pump and an exemplary air-source heat pump with an exhaust plenum system for a 50,000 CFM laboratory example in accordance with the disclosed subject matter.

[0045] [Figure 12B] FIG. 12B illustrates a table displaying the heating output, cooling output, and total output of an exemplary air-source heat pump with a standard air-source heat pump and exhaust plenum system for the 50,000 CFM laboratory example of FIG. 12A.

[0046] [Figure 12C] FIG. 12C illustrates a table displaying the maximum monthly output of a standard air-source heat pump and an exemplary air-source heat pump with an exhaust plenum system for the 50,000 CFM laboratory example of FIG. 12A.

[0047] [Figure 12D] FIG. 12D illustrates a table displaying the number of air source heat pump modules required for a standard air source heat pump and an air source heat pump with an exhaust plenum system in conjunction with the information presented in the examples of FIGS. 12A-12C.

[0048] [Figure 13A]FIG. 13A illustrates a graph displaying the total monthly output of a standard air source heat pump and an air source heat pump with an exhaust plenum system for a high rise residential building, according to one embodiment.

[0049] [Figure 13B] FIG. 13B illustrates a table of heating and cooling output values ​​of a standard air-source heat pump for a high-rise residential building.

[0050] [Figure 13C] FIG. 13C illustrates a table of heating and cooling outputs of an air-source heat pump with an exhaust plenum system for the high-rise residential building of FIG. 13B in accordance with an embodiment of the disclosed subject matter.

[0051] [Figure 13D] FIG. 13D illustrates a table comparing the heat and cooling output of the standard air-source heat pump of FIG. 13B and the exemplary air-source heat pump with an exhaust plenum system of FIG. 13C, as well as the efficiency improvement provided by the exemplary air-source heat pump with an exhaust plenum system implemented in accordance with the disclosed subject matter.

[0052] [Figure 14] FIG. 14 illustrates an example of a mini-split air source heat pump condensing unit with an exhaust plenum system, according to an embodiment of the disclosed subject matter.

[0053] [Figure 15] FIG. 15 illustrates an example of a residential air source heat pump condensing unit with an exhaust plenum system, according to an embodiment of the disclosed subject matter.

[0054] [Figure 16] FIG. 16 illustrates an example of a pressure-enthalpy refrigeration cycle for a conventional thermodynamic cooling system at a 95° F. ambient airflow temperature.

[0055] [Figure 17]FIG. 17 illustrates an example of a pressure-enthalpy refrigeration cycle for a conventional thermodynamic heating and ventilation system at 0° F. ambient airflow temperature. DETAILED DESCRIPTION OF THE INVENTION

[0056] Detailed Description Described herein are methods for utilizing exhaust air from thermodynamic heating and cooling systems for improved efficiency of the thermodynamic heating and cooling systems. In some embodiments, the methods include drawing building infrastructure exhaust airflow from various portions of a building into an exhaust plenum system and passing the building infrastructure exhaust airflow and ambient airflow over the coils of a heat pump or cooling device, thereby mixing the building infrastructure exhaust airflow with the ambient airflow and creating an exhaust-ambient airflow mixture that increases the efficiency and capacity of the machine.

[0057] In some embodiments, mixing the building infrastructure exhaust airflow with the ambient airflow increases the temperature of the exhaust-ambient airflow mixture. In some embodiments, mixing the exhaust air with the ambient airflow decreases the temperature of the exhaust-ambient airflow mixture.

[0058] Described herein are ventilation systems and methods for utilizing building infrastructure exhaust airflow within thermodynamic heating and cooling systems for improved efficiency through the use of an exhaust plenum system. The building infrastructure exhaust airflow is reused within an air-source heat pump system via the exhaust plenum system, which allows the building infrastructure exhaust airflow to be combined with ambient airflow, thereby creating an exhaust-ambient airflow mixture to be used by the air-source heat pump, as opposed to using only ambient airflow. The amount of exhaust-ambient airflow mixture input to the air-source heat pump is calculated based on the required BTUs of the thermodynamic system. The exhaust plenum system removes air from the conditioned space, improving indoor air quality, moisture control, temperature control, odor control, combustion by-product control, and balancing building pressure. The ventilation systems and methods can be utilized in either commercial or residential settings.

[0059] Described herein is a ventilation system for a building including an air-source heat pump including a compressor, a condenser, a reversing valve, and an evaporator, and an exhaust plenum system configured to mix a building infrastructure exhaust airflow with an ambient airflow and provide the exhaust air-ambient airflow mixture to the air-source heat pump, wherein use of the exhaust air-ambient airflow mixture improves the efficiency of the air-source heat pump.

[0060] In another example, a ventilation system is described herein that utilizes the exhaust air of a thermodynamic heating and cooling system for improved efficiency. In the exemplary ventilation system, an exhaust plenum system increases the efficiency of the thermodynamic system by utilizing energy (measured in BTUs) from the building infrastructure exhaust airflow. By using a mixture of ambient airflow and building infrastructure exhaust airflow, the thermodynamic system can achieve higher productivity by extracting heat from the exhaust-ambient airflow mixture for heating purposes or rejecting heat from the exhaust-ambient airflow mixture for cooling purposes.

[0061] In some embodiments, the thermodynamic system is an air-source heat pump. In some embodiments, the air-source heat pump is configured to operate in two modes: one to produce chilled water and one to produce hot water. This eliminates the need for both a chiller and a boiler. In some embodiments, the air-source heat pump is sized to ensure that the airflow requirements for the air-source heat pump exceed the amount of building infrastructure exhaust airflow being removed. When an air-source heat pump (ASHP) is sized for full load (i.e., the capacity of the ASHP to meet the maximum expected heating or cooling load under typical operating conditions), the air-source heat pump requires more ambient airflow than the building infrastructure exhaust airflow from the building. In some embodiments, the air-source heat pump requires 6 to 7 times more ambient airflow than the building infrastructure exhaust airflow. During the ventilation system design phase, heating and cooling ambient airflow conditions (up to 70°F and 72°F, respectively) can be established, and a determination can be made as to whether the amount of building infrastructure exhaust airflow being discharged from the air-source heat pump exceeds the building's needs. In some embodiments, the ambient airflow temperature, supply airflow (e.g., conditioned (heated or cooled) air delivered to the habitable environment), and building infrastructure exhaust airflow are individually monitored to ensure that the building infrastructure exhaust airflow is consistently discharged at the proper flow rate. For example, if the ambient airflow temperature is 52-55°F and the supply air handling unit can be used economically without requiring any hot or cold water, the source / sink fan of the air-source heat pump would still be allowed to properly discharge the building infrastructure exhaust airflow. In some embodiments, the compressor in the air-source heat pump would be disabled, but the source / sink fan on the air-source heat pump would still be allowed to run.

[0062] Another way to achieve adequate consistent airflow is to allow a minimum number of source / sink fans to operate. In some embodiments, the air-source heat pump's controller tracks the number of source / sink fans operating and the fan speed of each source / sink fan. In some embodiments, the air-source heat pump controller monitors these two aspects and ensures that the minimum airflow is met. In some embodiments, the minimum airflow is reset for occupied and unoccupied modes (i.e., when the building is occupied or unoccupied).

[0063] An exhaust plenum system recovers energy exhausted from the building infrastructure as a result of the functioning of the air-source heat pump. The exhaust method can be through any fluid medium, with air or water being the most common. Areas of a building that may provide building infrastructure exhaust airflow include bathrooms, kitchens, laboratories, garages, laundry rooms, storage areas, workshops, or other areas where pollutants and moisture accumulate. In some embodiments, the exhaust plenum system comprises one or more plenums and / or ducts.

[0064] For example, one or more in-line exhaust fans may be in series with the exhaust plenum system. In some embodiments, if an in-line exhaust fan in series with the exhaust plenum system is present, the exhaust plenum system is equipped with a bypass damper to allow the building infrastructure exhaust airflow to exit the plenum side to the exterior when the air-source heat pump is not operating. The one or more exhaust air handlers may include an energy wheel, etc.

[0065] The exhaust plenum system may also be operable to recover waste building infrastructure energy using other processes, such as utilizing fluid media to generate heat or chilled water. Some examples include through process heat, boiler flue gases, data centers, compressed air systems, steam systems, laundry facilities, kitchen appliances, and power generation equipment.

[0066] For example, waste heat from an industrial process can be reused to preheat the ambient airflow entering an air-source heat pump. Or, with respect to boiler flue gas, heat from the boiler can be captured using an economizer to preheat the airflow or coils via the building infrastructure exhaust airflow and injected into the exhaust plenum system. In a data center example, heat generated by servers and related computer equipment can be recovered. In other examples, waste heat from air compressors in a compressed air system can be reused and / or condensate from a steam system can be recovered. In a laundry facility example, heat from dryer exhaust and hot water from the washing process can be recovered and reused. Meanwhile, with respect to kitchen equipment, heat from ovens, stoves, other cooking appliances, and home appliances, for example, can be captured and potentially reused. In a further example, power generation equipment produces heat from generators and turbines that can be recovered. The foregoing are intended as examples, and other examples are also envisioned for recycling building energy.

[0067] In some examples, exhaust plenum systems utilize heating coils to inject heat into the exhaust stream as a complement to the thermodynamic process of an air-source heat pump. In some embodiments, these heating coils may utilize hot water, steam, electricity, or other forms or combinations of heat generating sources.

[0068] The exhaust plenum system may be fabricated from a number of different materials. The exhaust plenum system may include durable materials such as galvanized steel or aluminum, plastic, and / or other materials.

[0069] In some embodiments, the exhaust plenum system is located and sized to accommodate the specific heat pump or chiller requirements of the ventilation system for a particular type of building (e.g., brick exterior, glass exterior, etc.) and building use or specific application (e.g., data center, office building, etc.).

[0070] The exhaust plenum system may be configured with one or more duct connections, depending on the specific application. For example, the duct connections may be configured with dampers or louvers to regulate airflow and prevent backflow of air when the thermodynamic system is not operating. Additionally or alternatively, the exhaust plenum system may be equipped with a filter upstream in the duct connection to help filter any items not intended to enter the air-source heat pump.

[0071] In some embodiments, the exhaust plenum system may be configured with access points, such as removable panels or access doors, to facilitate inspection, cleaning, and maintenance of the ducts, duct connections, and associated components.

[0072] The exhaust plenum system may be configured to isolate rooftop equipment from the building structure, thereby preventing the transmission of vibrations and noise caused by the operation of the equipment. Vibration prevention helps minimize disturbance to building occupants and reduces the risk of structural damage. Vibration and noise transmission may be prevented through the use of vibration isolation elements made of vibration-damping materials, such as rubber, neoprene, spring isolators, etc.

[0073] In some embodiments, the exhaust plenum system is equipped with a heat tracing system or snow melting system to effectively manage and prevent snow or ice accumulation. The heat tracing system may, for example, include electric heaters or be fed from the building hot water supply system with coils strategically positioned within the exhaust plenum system. Of course, the exhaust plenum system may also be equipped with drains to ensure proper drainage.

[0074] 3 illustrates a functional block diagram of a thermodynamic heating and ventilation system equipped with an exhaust plenum system, according to an embodiment. Thermodynamic heating and ventilation system 300 with an exhaust plenum system may include, for example, thermodynamic heating and ventilation system 326 and exhaust plenum system 322.

[0075] Thermodynamic heating and ventilation system 326 may include a compression unit 302, a compressor outlet 304, a compressor inlet 306, a condensing unit 308, a metering device 310, an evaporative unit 312, and a reversing valve 314, similar to the embodiments of Figures 1 and 2.

[0076] In some embodiments, the thermodynamic heating and ventilation system 326 is an air-source heat pump. In other embodiments, the thermodynamic heating and ventilation system may be a ground-source heat pump, a water-source heat pump, a hybrid heat pump, a solar-assisted heat pump, or any other type of system capable of generating heat.

[0077] The exhaust plenum system is operable to collect building infrastructure exhaust airflow 320, possibly obtained from building infrastructure systems within the indoor environment 318, and mix the building infrastructure exhaust airflow 320 with ambient airflow from the outdoor environment 316 to form an exhaust-ambient airflow mixture 324.

[0078] In some embodiments, the evaporative unit 312 includes one or more evaporative unit source / sink fans and an evaporative unit coil (both not shown in the examples). The one or more evaporative unit source / sink fans blow the exhaust air-ambient airflow mixture 324 over the evaporative unit coil. In some embodiments, after the exhaust air-ambient airflow mixture 324 has passed over the evaporative unit coil of the evaporative unit 312, it may be discarded from the evaporative unit 312 in a thermodynamic heating ventilation system 326 and recycled for addition to the building infrastructure exhaust airflow 320.

[0079] In some embodiments, the thermodynamic heating and ventilation system 300 with exhaust plenum system includes sensors that regulate the temperature of the indoor environment 318. The temperature of the indoor environment 318 is regulated through the use of a thermostat, which is at least one example of a regulation sensor.

[0080] FIG. 4 illustrates an exemplary method for an exemplary ventilation system to recycle exhaust airflow discharged by the ventilation system.

[0081] Process 400 is an exemplary method for reclaiming an exhaust airflow, in which an ambient airflow enters an air-source heat pump via a source / sink fan in block 402. The airflow is drawn or directed by the source / sink fan over either an evaporator or a condenser in block 404. The ASHP is operable to harvest energy from the airflow by either the process of evaporation or condensation over the respective evaporator or condenser in block 406.

[0082] After block 406, based on the ventilation system control settings, the airflow is exhausted from either the evaporator or the condenser as a building infrastructure exhaust airflow (block 408). Depending on the ventilation system control settings, the building infrastructure exhaust airflow may be directed in at least one of two directions. For example, baffles in the ventilation system ductwork may direct the building infrastructure exhaust airflow either out of the building (block 414) or into an exhaust plenum at block 410. At block 414, the building infrastructure exhaust airflow from the source / sink fans enters an outdoor environment, such as 316 in FIG. 3 .

[0083] Once the building infrastructure exhaust airflow is directed into the exhaust plenum at block 410, it eventually exits the exhaust plenum, mixes with the ambient airflow, and is directed into an airflow that is blown over the evaporator or condenser, thus restarting the cycle of process 400 at block 404.

[0084] FIG. 5 illustrates an exemplary method for an exemplary ventilation system.

[0085] At block 502, the process 500 includes an exhaust plenum system configured to direct an exhaust flow, including a building infrastructure exhaust airflow, toward an air-source heat pump (ASHP). As shown in another example, the exhaust plenum system may include an exhaust plenum system open grate, which may be positioned adjacent to the ASHP. The exhaust plenum open grate may be on one or more sides of the ASHP. The one or more sides of the ASHP may include the top and / or bottom of the ASHP.

[0086] The exhaust plenum open grate allows the exhaust flow, including the building infrastructure exhaust airflow, to mix with the ambient airflow entering the exhaust plenum system through the exhaust plenum system open grate, creating an exhaust-ambient airflow mixture (block 504).

[0087] In block 506 of process 500, the ventilation system is configured to apply an exhaust air-ambient airflow mixture around the ASHP coil of the ASHP.

[0088] Due to the increased energy provided by the exhaust airflow, in block 508, the ASHP is able to extract an additional amount of energy from the exhaust airflow-ambient airflow mixture compared to the amount of energy extracted from the ambient airflow mixture alone.

[0089] The additional energy, as described below, allows the ASHP to operate more efficiently, meet the building's heating and cooling needs more effectively, and reduce energy costs.

[0090] 6A illustrates a top-down view of an example of an air-source heat pump with an exhaust plenum system, in accordance with an embodiment of the disclosed subject matter. The air-source heat pump with exhaust plenum system 600 includes an exhaust plenum 601 and an air-source heat pump module bank 603.

[0091] In one embodiment, an air-source heat pump module bank 603 may include several individual air-source heat pump modules 602 and several air-source heat pump module source / sink fans 604. The exhaust plenum 601 may include an exhaust plenum passage 607 having an exhaust plenum open grate 606.

[0092] The exhaust plenum 601 may be positioned adjacent to the air-source heat pump module bank 603, for example, with the air-source heat pump module source / sink fan 604 being the highest part of the air-source heat pump 600 with the exhaust plenum system. In other embodiments, the exhaust plenum 601 is positioned adjacent to the center of the air-source heat pump module bank 603.

[0093] An air-source heat pump 600 with an exhaust plenum system may include several air-source heat pump modules 602, depending on the application. In the example of Figure 6A, the air-source heat pump 600 with an exhaust plenum system utilizes fourteen air-source heat pump modules 602. Of course, more or less than fourteen air-source heat pump modules 602 may be used. Additionally, each air-source heat pump module 602 may include an air-source heat pump module source / sink fan 604.

[0094] In some embodiments, air-source heat pump with exhaust plenum system 600 includes an exhaust plenum open grate 606 that forms an exhaust plenum passageway 607. In some embodiments, exhaust plenum open grate 606 is configured to allow building infrastructure exhaust airflow to mix with ambient airflow to form an exhaust-ambient airflow mixture. Depending on control settings for air-source heat pump with exhaust plenum system 600, the exhaust-ambient airflow mixture may be configured to be applied to an evaporative unit coil or a condensing unit coil. Alternatively, the exhaust-ambient airflow mixture may be configured to be exhausted to an outdoor environment by air-source heat pump module source / sink fan 604.

[0095] 6B illustrates a side view of an example of an air-source heat pump with an exhaust plenum system, according to an embodiment of the disclosed subject matter. As shown in the side view of FIG. 6B, the air-source heat pump with exhaust plenum system 600 includes an air-source heat pump module bank 603 including air-source heat pump modules 602, an exhaust plenum 601, and an air-source heat pump frame 608.

[0096] In some embodiments, the exhaust plenum 601 and the air-source heat pump module bank 603 are separated vertically by an air-source heat pump frame 608 (shown in FIG. 6B).

[0097] In some embodiments, the air source heat pump module bank 603 is positioned above the exhaust plenum 601 through the use of an air source heat pump frame 608 .

[0098] 6C illustrates another side view of an example air-source heat pump with an exhaust plenum system, according to an embodiment of the disclosed subject matter. As mentioned above, the air-source heat pump module 602 includes an air-source heat pump module source / sink fan 604, an evaporative unit 609, an evaporative unit coil 610, a condensing unit 611, and a condensing unit coil 613.

[0099] In some embodiments, the condensing unit 611 includes more coils than the evaporating unit 609. In other embodiments, the condensing unit 611 includes the same amount of coils as the evaporating unit 609. In yet other embodiments, the condensing unit 611 may include fewer coils than the evaporating unit 609.

[0100] The number of coils for either the evaporating unit 609 or the condensing unit 611 may be related to the capacity of the ASHP, etc.

[0101] 6D illustrates a side view of an example of an air-source heat pump with an exhaust plenum system, according to an embodiment of the disclosed subject matter. In this example view, the air-source heat pump with exhaust plenum system 600 is shown in a configuration where the exhaust plenum 601 is below and adjacent to the air-source heat pump module 602. In this example, an air-source heat pump frame 608 supports the air-source heat pump module 602. The exhaust plenum system duct connection 612 may be configured to direct building infrastructure exhaust airflow toward the air-source heat pump module source / sink fan 604.

[0102] The foregoing description of Figures 6A-6D provides a description of an example configuration of a ventilation system having an exhaust plenum system configured to employ advantageous features described herein.

[0103] FIG. 7 illustrates an example of a packaged direct expansion air source heat pump equipped with an exhaust plenum system in accordance with the disclosed subject matter.

[0104] Packaged direct expansion (DX) air-source heat pumps are decentralized ASHPs suitable for providing air conditioning (ie, cooling and heating) to, for example, apartment buildings, small offices, and the like.

[0105] The exhaust plenum system and packaged DX air-source heat pump 700 of FIG. 6 may include, for example, an air-source heat pump 718 and an exhaust plenum 704 .

[0106] In this example, the air-source heat pump 718 may include an exhaust blower 702, a return air damper 706, a condensing unit coil 714, an energy wheel 720, an exhaust fan 716, a compressor cabinet 722, and the air-source heat pump 718. The exhaust plenum 704 is configured to direct the building infrastructure exhaust airflow 708 toward the condensing unit coil 714.

[0107] When an exhaust plenum system is placed in series with an air-source heat pump 718 utilizing an energy wheel, it can still use the air being discharged to raise or lower the temperature entering the air-source heat pump, as the air leaving the energy wheel 720 may be at a lower temperature in the cooling system or a higher temperature in the heating system than the ambient airflow 712. Using the discharged air reduces the amount of work the compressor needs to do because the air-source heat pump 718 operates at a lower pressure. Figure 7 is an example of an exhaust plenum system tied to a packaged DX air-source heat pump unit.

[0108] In operation, exhaust air is drawn from the building via exhaust blower 702, energy is recovered through energy wheel 720, and the exhaust air supplemented with the recovered energy is exhausted from the unit ducted to exhaust plenum 704 as building infrastructure exhaust airflow 708. Building infrastructure exhaust airflow 708 leaves exhaust plenum 704 and mixes with outdoor ambient airflow 712, allowing for better operating points for refrigeration systems at lower pressures, for example.

[0109] For example, the air leaving the wheel is expected to be below the ambient air temperature it is designed for cooling and above the ambient air temperature it is designed for heating. See Typical Performance When an Energy Wheel is Used below. In Table IV below, the abbreviation DB is the "dry bulb" temperature and represents the air temperature without considering evaporation or relative humidity, while the abbreviation WB is the "wet bulb" temperature and considers the cooling effect due to moisture and evaporation. [Table 4]

[0110] In one example, exhaust plenum 704 is configured to be in series with the duct connection of an air-source heat pump 718 utilizing an energy wheel 720. In some embodiments, exhaust plenum 704 uses building infrastructure exhaust airflow 708 being exhausted by exhaust fan 716 to increase or decrease the temperature entering condensing unit coil 714, since the building infrastructure exhaust airflow 708 in the exhaust stream leaving the energy wheel has a lower temperature in a cooling design, or a higher temperature in a heating design, than the ambient airflow 712. Thus, the amount of work that the compression unit needs to do is reduced because the operating pressure of the unit is reduced.

[0111] In a more detailed operational example, building infrastructure exhaust airflow 708 is removed from the building infrastructure, for example, from kitchens, washer-dryers, hot water heaters, servers and IT equipment, or boiler exhaust, and energy is recovered through an energy wheel, and the building infrastructure exhaust airflow 708 from the units is ducted to an exhaust plenum 704. The building infrastructure exhaust airflow 708 mixes with ambient airflow 712 to form an exhaust-ambient airflow mixture 710, allowing for a better operating point for the refrigeration system at a lower pressure.

[0112] In some embodiments, during certain periods of the year, the building infrastructure exhaust airflow is diverted to prevent mixing with the ambient airflow when the temperature is not favorable.

[0113] FIG. 8A illustrates a pressure-enthalpy refrigeration cycle chart for a conventional thermodynamic heating and ventilation system equipped with an exhaust plenum system at 0° F. ambient airflow temperature. The pressure-enthalpy chart 800 with an exhaust plenum is similar to FIG. 17, described in the Background section of this application. Line AB in both charts is the evaporation line at a value of either pounds per square inch absolute (PSIA) or temperature (at a temperature below zero degrees F.). However, in FIG. 17, the PSIA for the standard system represented by FIG. 17 is 40 or −21 degrees F. Meanwhile, in contrast to FIG. 17, the evaporation line for a system with an exhaust plenum system as described herein is shown in chart 800 of FIG. 8A at a PSIA of 45 or −16 degrees F.

[0114] In the example described with reference to Figure 3, during heating operation as shown in pressure-enthalpy chart 800 with an exhaust plenum, the performance of the thermodynamic heating and ventilation system may be improved (i.e., increased) due to the exhaust-ambient airflow mixture having an elevated exhaust-ambient airflow mixture temperature passing through the evaporative unit coil compared to only the ambient airflow having a lower temperature. This is due, for example, to reduced suction temperature, which is increased using the exhaust plenum system. Suction temperature refers to the temperature of the refrigerant vapor as it leaves the evaporator coil and enters the compressor.

[0115] In pressure-enthalpy chart 800 with exhaust plenum, between points A and C, for example, the exhaust-ambient airflow mixture has a higher exhaust-ambient airflow mixture temperature compared to a typical thermodynamic heating and ventilation system (e.g., −16 degrees F vs. −21 degrees F), and when the exhaust-ambient airflow mixture is used in thermodynamic heating and ventilation system 300 with exhaust plenum system of FIG. 3 , the thermodynamic heating and ventilation system with exhaust plenum system has a higher ambient airflow temperature and operates at a higher evaporating pressure, which increases the efficiency and capacity of the thermodynamic heating and ventilation system with exhaust plenum system compared to the thermodynamic heating and ventilation system without the exemplary exhaust plenum system described in the previous examples.

[0116] Figure 8B illustrates a table of typical performance values ​​for a thermodynamic heating and ventilation system equipped with an exhaust plenum system such as that shown in the exemplary chart of Figure 8 A. The typical system performance table 802 shows each of the individual values ​​at points A-G on the pressure-enthalpy chart 800 with the exhaust plenum shown in Figure 8A.

[0117] 8C illustrates a table displaying the condenser capacity and efficiency of a thermodynamic heating and ventilation system equipped with an exhaust plenum system, according to an embodiment. The condenser capacity and efficiency table 804 shows that the thermodynamic heating and ventilation system with an exhaust plenum system has a 6.82% greater condensing unit capacity and a 5.62% greater coefficient of performance (COP). The COP may be used to quantify how effectively an ASHP transfers heat relative to the power it consumes.

[0118] FIG. 8D illustrates a table displaying the heating capacity of a standard air-source heat pump and an air-source heat pump with an exhaust plenum system, according to some embodiments of the disclosed subject matter. In the comparison table 806, due to the exhaust air-ambient airflow mixture temperature (i.e., mixed air temperature (MAT)) entering the exemplary air-source heat pump with an exhaust plenum system as described with reference to the previous examples, the efficiency and capacity of the unit is increased as opposed to only the ambient airflow entering the standard air-source heat pump. In this example, the examples relate to ambient airflow at 0°F, 10°F, 20°F, and 30°F, as shown in the first column. In some embodiments, the ambient airflow is below 0°F. Alternatively, the ambient airflow can be any temperature between 10°F and 30°F. In other alternatives, the ambient airflow is above 30°F.

[0119] The second and third columns show information relevant to a standard air-source heat pump. The second column displays the corresponding thousands of BTU per hour (MBH) for each ambient airflow temperature. MBH quantifies the rate of energy transfer in heating and cooling systems and is used to represent heating or cooling capacity. The third column displays the coefficient of performance (COP) for each ambient airflow temperature. COP is a dimensionless value that measures the electrical efficiency of the heating and cooling system. In this example, COP is calculated by dividing the heating output by the electrical energy input.

[0120] The fourth and fifth columns show information related to air-source heat pumps with exhaust plenum systems. The fourth column displays MBH per ambient airflow temperature. The fifth column displays COP per ambient airflow temperature.

[0121] In an embodiment where the ambient airflow is 0°F, the air source heat pump with the exhaust plenum system produces about 8.21% more MBH and about 5.61% higher COP than the standard air source heat pump.

[0122] In an embodiment where the ambient airflow is 10°F, the air source heat pump with the exhaust plenum system produces about 6.87% more MBH and about 3.74% higher COP than the standard air source heat pump.

[0123] In an embodiment where the ambient airflow is 20°F, the air source heat pump with the exhaust plenum system produces about 5.57% more MBH and about 4.22% higher COP than the standard air source heat pump.

[0124] In an embodiment where the ambient airflow is 30°F, the air source heat pump with the exhaust plenum system produces about 3.94% more MBH and about 2.26% higher COP than the standard air source heat pump.

[0125] FIG. 9 illustrates a table displaying exhaust-ambient airflow mixture temperatures according to an embodiment of the disclosed subject matter.

[0126] Temperature table 900 shows the mixed air temperature (MAT) entering an air-source heat pump with an exhaust plenum system at various ambient airflows (i.e., outside air temperatures (OAT)). Building loads and airflows vary based on building type and geographic location, which directly impacts equipment sizing and performance.

[0127] In this example, the exhaust plenum system is applied to a single 30-ton air-source heat pump requiring an airflow of 24,000 cubic feet per minute (CFM). The building infrastructure exhaust airflow entering the exhaust plenum system may be set to, for example, 2,000 CFM with a building infrastructure exhaust airflow temperature of 72°F.

[0128] The exhaust plenum system may be applied to a 1-ton air-source heat pump (i.e., the capacity of the air-source heat pump is 12,000 BTU, and 12,000 BTU equals 1 ton). While the example of FIG. 9 is 1 ton, it is envisioned that the exhaust plenum system as described herein may be applied to air-source heat pumps of several thousand tonnes. For example, a residential building may be equipped with an air-source heat pump requiring 50 CFM of airflow, while a large laboratory building may require an air-source heat pump capable of handling over 100,000 CFM.

[0129] In some examples as contemplated herein, the exhaust airflow entering the exhaust plenum system may be configured to handle a building infrastructure exhaust airflow of between approximately 500 and 24,000 CFM. However, in some embodiments, the building infrastructure exhaust airflow entering the exhaust plenum system is less than approximately 500 CFM. In other embodiments, the building infrastructure exhaust airflow entering the exhaust plenum system is greater than approximately 24,000 CFM.

[0130] The temperature of the building infrastructure exhaust airflow may indicate the amount of energy that may be extracted from the building infrastructure exhaust airflow. In some embodiments, the building infrastructure exhaust airflow temperature is between about 65°F and 78°F. In other embodiments, the building infrastructure exhaust airflow temperature is below 65°F, etc. In yet other embodiments, the building infrastructure exhaust airflow temperature is above 78°F, etc.

[0131] FIG. 10A illustrates a graph displaying the heating capacity of a standard air source heat pump and an air source heat pump with an exhaust plenum system as a function of temperature.

[0132] In graph 1000, the dashed line represents an air-source heat pump with an exhaust plenum system and the solid line represents a standard air-source heat pump. As shown in the graph, as the temperature decreases, the difference in capacity between the air-source heat pump with an exhaust plenum system and the standard air-source heat pump increases, and the efficiency of the air-source heat pump with an exhaust plenum system increases as the temperature decreases compared to the standard air-source heat pump.

[0133] FIG. 10B illustrates a table displaying the cooling capacities of a standard air-source heat pump and an air-source heat pump with an exhaust plenum system according to four embodiments. In chart 1002, the performance of a standard air-source heat pump (i.e., without the use of the exemplary exhaust plenum system) and the performance of an air-source heat pump with an exhaust plenum system are shown. Due to the MAT entering the air-source heat pump with an exhaust plenum system, the efficiency and capacity of the unit are increased, as opposed to only ambient air flow entering a standard air-source heat pump. In this example, the four embodiments relate to ambient air flow at 80°F, 85°F, 90°F, and 95°F, as shown in the first column. In some embodiments, the ambient air flow is below 80°F. In some embodiments, the ambient air flow is any temperature between 80°F and 95°F. In some embodiments, the ambient air flow is above 95°F.

[0134] The second and third columns show information relevant to a standard air-source heat pump. The second column displays thousands of BTU per hour (MBH) for each ambient airflow temperature. The third column displays the COP for each ambient airflow temperature. In this example, the COP is calculated by dividing the cooling output by the electrical energy input.

[0135] The fourth and fifth columns show information related to air-source heat pumps with exhaust plenum systems. The fourth column displays MBH per ambient airflow temperature. The fifth column displays COP per ambient airflow temperature.

[0136] In an embodiment where the ambient airflow is 80°F, the air source heat pump with the exhaust plenum system produces 4.04% less MBH and a 3.90% higher COP than the standard air source heat pump.

[0137] In an embodiment where the ambient airflow is 85°F, the air source heat pump with the exhaust plenum system produces 2.58% more MBH and a 4.12% higher COP than the standard air source heat pump.

[0138] In an embodiment where the ambient airflow is 90°F, the air source heat pump with the exhaust plenum system produces 9.16% more MBH and a 5.77% higher COP than the standard air source heat pump.

[0139] In an embodiment where the ambient airflow is 95°F, the air source heat pump with the exhaust plenum system produces 17.31% more MBH and a 6.2% higher COP than the standard air source heat pump.

[0140] 11A illustrates a graph displaying the cooling capacity of a standard air-source heat pump and an air-source heat pump with an exhaust plenum system as a function of temperature. In graph 1102, the dashed line represents the air-source heat pump with an exhaust plenum system, and the solid line represents the standard air-source heat pump. As shown in graph 1102, as temperature increases, the difference in capacity between the air-source heat pump with an exhaust plenum system and the standard air-source heat pump increases, and the efficiency of the air-source heat pump with an exhaust plenum system increases as temperature increases compared to the standard air-source heat pump.

[0141] 11B illustrates a table depicting the heating capacity of an air-source heat pump with an exhaust plenum system according to 11 embodiments. In these examples, the air-source heat pump with an exhaust plenum system is used in connection with a laboratory setting year-round, as shown in chart 1104.

[0142] Column 1 of chart 1104 shows the number of air-source heat pump modules (shown in FIGS. 6B and 6C) in the laboratory, ranging from 6 to 16. In some embodiments, the number of air-source heat pump modules in the laboratory is less than 6. In some embodiments, the number of air-source heat pump modules in the laboratory is greater than 16.

[0143] Column 2 shows the total ambient airflow required by the source / sink fans, measured in CFM. This is calculated by multiplying the required airflow of the air-source heat pump with exhaust plenum system (which is 24,000 CFM in each embodiment) by the number of air-source heat pump modules in a given embodiment. For example, for an air-source heat pump with exhaust plenum system with 10 air-source heat pump modules, the total required airflow is 240,000 CFM.

[0144] Column 3 shows the laboratory building infrastructure exhaust airflow, measured in CFM. The laboratory building infrastructure exhaust airflow is used in an exhaust plenum system. In some embodiments, the laboratory space requires an ambient airflow of 1.5 to 2 CFM per square foot. This requirement is based on the air changes per hour and the load of the laboratory space.

[0145] The CFM of supply airflow and building infrastructure exhaust airflow are calculated using the following equations: [ka] In this equation, SQ represents the square footage of the building (ft 2 Units), A Arepresents the desired amount of ambient airflow (CFM / ft 2 Units), A S represents the supply airflow (in CFM) of the intake or air conditioning that provides air to an indoor environment such as indoor environment 318, and A E represents the building infrastructure exhaust airflow (in CFM).

[0146] In this embodiment, if the laboratory building comprises 25,000 square feet and the laboratory space requires an ambient airflow of 2 CFM per square foot, the laboratory building requires a supply airflow and building infrastructure exhaust airflow of 50,000 CFM.

[0147] Column 4 shows the ambient airflow temperature, measured in °F. In this embodiment, for each number of air-source heat pump modules, the ambient airflow temperature is 0°F. This is to ensure standardization between and facilitate comparison of the number of air-source heat pump modules. In some embodiments, the ambient airflow temperature is less than 0°F. In some embodiments, the ambient airflow temperature is greater than 0°F.

[0148] Column 5 shows the building infrastructure exhaust airflow temperature, measured in °F. In this embodiment, for each air-source heat pump module, the building infrastructure exhaust airflow temperature is 70°F. This is to ensure standardization between and facilitate comparison of the number of air-source heat pump modules. In some embodiments, the building infrastructure exhaust airflow temperature is less than 70°F. In some embodiments, the building infrastructure exhaust airflow temperature is greater than 70°F.

[0149] Column 6 shows the exhaust air-ambient airflow mixture temperature, measured in degrees Fahrenheit. In some embodiments, the exhaust air-ambient airflow mixture temperature is greater than 24.3°F. In some embodiments, the exhaust air-ambient airflow mixture temperature is any number between 24.3°F and 9.1°F. In some embodiments, the exhaust air-ambient airflow mixture temperature is less than 9.1°F.

[0150] Column 7 shows the single air source heat pump module capacity, measured in MBH. The single air source heat pump module capacity is calculated by the manufacturer and provided to the user. In some embodiments, the single air source heat pump module capacity is less than 265.40 MBH. In some embodiments, the single air source heat pump module capacity is any number between 265.40 MBH and 217.06 MBH. In some embodiments, the single air source heat pump module capacity is greater than 217.06 MBH.

[0151] Column 8 shows the total capacity, measured in MBH. The total capacity is calculated by multiplying the number of air source heat pump modules by the capacity of a single air source heat pump module. In some embodiments, the total capacity is less than 1592.40 MBH. In some embodiments, the total capacity is between 1592.40 MBH and 3472.96 MBH. In some embodiments, the total capacity is greater than 3472.96 MBH.

[0152] The approximate load on a supply air handling unit distributing conditioned air throughout a building (e.g., workplace, office, gym, residence, laboratory, data center, or any space requiring conditioned air) to be met by an air-source heat pump with an exhaust plenum system is calculated using the following equation: [ka]

[0153] In this equation, A S represents the supply air flow (in CFM), and A E represents the building infrastructure exhaust airflow (in CFM), K represents the density-specific heat product coefficient (unitless), T1 represents the design temperature (in °F), T2 represents the ambient airflow (in °F), and L represents the load (in MBH).

[0154] In some embodiments, the density-specific heat product coefficient K is between 1.08 and 1.12, depending on the air conditions. The density-specific heat product K is calculated using the following equation: [ka] In a working example, 0.0745 lbs. mass / ft. 3 For an air density (AIRDEN) of 100 psi, an isobaric specific heat of air (CPAIR) of 0.2444 BTU / (pounds mass × °F), and a convective heat transfer coefficient (CONVFC) of 60 min / hr, the density-specific heat product (K) is equal to 1.0925 BTU / (hours × cfm × F).

[0155] In one embodiment, with a sum of 50,000 CFM supply airflow and building infrastructure exhaust airflow, a density-specific heat product coefficient of 1.114, a design temperature of 55°F, and an ambient airflow temperature of 0°F, the calculated load on the supply air handling unit is 3,063.5 MBH (3,063,500 BTU / hr). The design temperature is the specific outdoor temperature condition that the ventilation system is designed to handle. There are various design temperatures, such as a cooling season design temperature, a heating season design temperature, and an indoor design temperature. Of course, there may be other design temperatures for specific applications, such as data centers, enclosed stadiums, etc.

[0156] In some embodiments, at 3,063.5 MBH with an ambient airflow temperature of 0° F., sixteen 30-ton air-source heat pump modules are required to heat the ambient airflow temperature to 70° F. using a standard air-source heat pump. In some embodiments, if the building infrastructure exhaust airflow, typically emitted from a building at 70° F. to 72° F., is mixed with the 0° F. ambient airflow, the number of air-source heat pump modules can be reduced to 14.

[0157] For every 25,000 CFM of supply airflow and building infrastructure exhaust airflow removed from the air source heat pump, one air source heat pump module can be removed.

[0158] 11C illustrates a chart depicting the cooling capacity of an air-source heat pump with an exhaust plenum system according to an embodiment of 11. In these examples, the air-source heat pump with an exhaust plenum system is used in connection with a laboratory setting year-round.

[0159] In chart 1106, column 1 shows the number of air-source heat pump modules (shown in FIGS. 6B and 6C) in the laboratory, ranging from 6 to 16. In some embodiments, the number of air-source heat pump modules in the laboratory is less than 6. In some embodiments, the number of air-source heat pump modules in the laboratory is greater than 16.

[0160] Column 2 shows the total ambient airflow required by the source / sink fans, measured in CFM. This is calculated by multiplying the required airflow of the air-source heat pump with exhaust plenum system (which is 24,000 CFM in each embodiment) by the number of air-source heat pump modules in a given embodiment. For example, for an air-source heat pump with exhaust plenum system with 10 modules, the total required airflow is 240,000 CFM.

[0161] Column 3 shows the laboratory building infrastructure exhaust airflow, measured in CFM. The laboratory building infrastructure exhaust airflow is used in an exhaust plenum system. In some embodiments, the laboratory space requires an ambient airflow of 1.5 to 2 CFM per square foot. This requirement is based on the air changes per hour and the load of the laboratory space.

[0162] The CFM of supply airflow and building infrastructure exhaust airflow are calculated using the following equations: [ka] In this equation, SQ represents the square footage of the building (ft 2 Units), A Arepresents the desired amount of ambient airflow (CFM / ft 2 Units), A S represents the supply air flow (in CFM), and A E represents the building infrastructure exhaust airflow (in CFM).

[0163] In this embodiment, if the laboratory building comprises 25,000 square feet and the laboratory space requires an ambient airflow of 2 CFM per square foot, the laboratory building requires a supply airflow and building infrastructure exhaust airflow of 50,000 CFM.

[0164] Column 4 shows the ambient airflow temperature, measured in °F. In this embodiment, for each number of air-source heat pump modules, the ambient airflow temperature is 95°F. This is to ensure standardization between and facilitate comparison of the number of air-source heat pump modules. In some embodiments, the ambient airflow temperature is less than 95°F. In some embodiments, the ambient airflow temperature is greater than 95°F.

[0165] Column 5 shows the building infrastructure exhaust airflow temperature, measured in °F. In this embodiment, for each air-source heat pump module, the building infrastructure exhaust airflow temperature is 72°F. This is to ensure standardization between and facilitate comparison of the number of air-source heat pump modules. In this embodiment, in some embodiments, the building infrastructure exhaust airflow temperature is less than 72°F. In some embodiments, the building infrastructure exhaust airflow temperature is greater than 72°F.

[0166] Column 6 indicates the exhaust air-ambient airflow mixture temperature, measured in degrees Fahrenheit. In some embodiments, the exhaust air-ambient airflow mixture temperature is greater than 92.0°F. In some embodiments, the exhaust air-ambient airflow mixture temperature is any number between 92.0°F and 87.0°F. In some embodiments, the exhaust air-ambient airflow mixture temperature is less than 87.0°F.

[0167] Column 7 shows the single air source heat pump module capacity, measured in tons of refrigeration. The single air source heat pump module capacity is calculated by the manufacturer and provided to the user. In some embodiments, the single air source heat pump module capacity is less than 25.98 tons. In some embodiments, the single air source heat pump module capacity is any number between 26.82 tons and 25.98 tons. In some embodiments, the single air source heat pump module capacity is greater than 26.82 tons.

[0168] Column 8 shows the total capacity, measured in tons of refrigeration. The total capacity is calculated by multiplying the number of air source heat pump modules by the capacity of a single air source heat pump module. In some embodiments, the total capacity is less than 160.94 tons. In some embodiments, the total capacity is between 160.94 tons and 415.68 tons. In some embodiments, the total capacity is greater than 415.68 tons.

[0169] The approximate load on the supply air handling unit to be satisfied by the air source heat pump is calculated using the following equation: [ka]

[0170] In this equation, A S represents the supply air flow (in CFM), and A E represents the building infrastructure exhaust airflow (in CFM), HFAC represents the enthalpy coefficient (unitless), (DB / WB)1 represents the ratio of the dry bulb (DB) temperature to the first wet bulb (WB) temperature, (DB / WB)2 represents the ratio of the DB temperature to the second WB temperature, and L represents the load (in thousands of BTU per hour (MBH)).

[0171] The enthalpy coefficient is calculated using the following equation: [ka] In one embodiment, 0.0745 lbs. mass / ft. 3 For an air density (AIRDEN), CPAIR, and a convective heat transfer coefficient (CONVFC) at 60 min / hr, the enthalpy coefficient (HFAC) is 4.47 (lbs mass x min / (hr x ft 3 ) The HFAC helps determine the total load on the ventilation system.

[0172] In one example, to cool the ambient airflow from 91 DB / 73 WB to 52 DB / 51.8 WB, with a supply airflow and building infrastructure exhaust airflow sum of 50,000 CFM and an enthalpy coefficient of 4.5, the air source heat pump cools the ambient airflow from 36.6 BTU / lb to 21.3 BTU / lb, the load is approximately 287 cooling tons or 3,442.5 MBH (3,442,500 BTU / hr).

[0173] At a load of approximately 287 cooling tons, approximately twelve 30-ton air-source heat pump modules are required to cool the ambient airflow temperature to 72° F. using a standard air-source heat pump. In some embodiments, if the air-source heat pump receives the exhaust air-ambient airflow mixture through an exhaust plenum system, eleven 30-ton air-source heat pump modules are required.

[0174] 12A illustrates a graph displaying the total monthly output of a standard air-source heat pump and an air-source heat pump with an exhaust plenum system for a 50,000 CFM laboratory, according to one embodiment. In the monthly electricity usage graph 1202, the standard air-source heat pump and the air-source heat pump with an exhaust plenum system are running for 12 hours per day. The dashed line represents the exhaust plenum system, and the solid line represents the standard air-source heat pump. As shown in the graph, the exhaust plenum system produces fewer kWh per month than the standard air-source heat pump.

[0175] 12B illustrates a table displaying the heating output, cooling output, and total output of a standard air-source heat pump and an air-source heat pump with an exhaust plenum system for a 50,000 CFM laboratory in accordance with the disclosed subject matter. As shown throughout the electricity usage chart 1204, the air-source heat pump with an exhaust plenum system is 21.19% more efficient than the standard air-source heat pump for heating operations. The air-source heat pump with an exhaust plenum system is 3.86% more efficient than the standard air-source heat pump for cooling operations. The air-source heat pump with an exhaust plenum system is overall 12.5% ​​more efficient than the standard air-source heat pump.

[0176] FIG. 12C illustrates a table displaying the monthly maximum output (i.e., monthly kWh) of a standard air-source heat pump and an air-source heat pump with an exhaust plenum system for a 50,000 CFM laboratory, according to one embodiment. As shown in the electricity demand comparison chart 1206, in January, the air-source heat pump with an exhaust plenum system is 8.1% more efficient than the standard air-source heat pump. In February, the air-source heat pump with an exhaust plenum system is 11.7% more efficient than the standard air-source heat pump. In March, the air-source heat pump with an exhaust plenum system is 14.7% more efficient than the standard air-source heat pump. In April, the air-source heat pump with an exhaust plenum system is 6.7% more efficient than the standard air-source heat pump. In May, the air-source heat pump with an exhaust plenum system is 4.8% more efficient than the standard air-source heat pump. In June, an air-source heat pump with an exhaust plenum system is 2.8% more efficient than a standard air-source heat pump. In July, an air-source heat pump with an exhaust plenum system is 3.6% more efficient than a standard air-source heat pump. In August, an air-source heat pump with an exhaust plenum system is 2.8% more efficient than a standard air-source heat pump. In September, an air-source heat pump with an exhaust plenum system is 3.2% more efficient than a standard air-source heat pump. In October, an air-source heat pump with an exhaust plenum system is 2.5% more efficient than a standard air-source heat pump. In November, an air-source heat pump with an exhaust plenum system is 14.4% more efficient than a standard air-source heat pump. In December, an air-source heat pump with an exhaust plenum system is 14.5% more efficient than a standard air-source heat pump.

[0177] As can be seen in the electrical demand comparison chart 1206, during what is typically the heating season, an air source heat pump with an exhaust plenum system is more efficient than when used during the cooling season.

[0178] 11B-12C, illustrates a table displaying the number of air source heat pump modules required for a standard air source heat pump and an air source heat pump with an exhaust plenum system. In the example shown in module comparison chart 1208, a standard air source heat pump requires 16 air source heat pump modules, while an air source heat pump with an exhaust plenum system requires only 14 air source heat pump modules.

[0179] FIG. 13A illustrates a graph displaying the total monthly output of a standard air source heat pump and an air source heat pump with an exhaust plenum system for a high rise residential building, according to one embodiment.

[0180] In the example shown in graph 1302, an exemplary high-rise residential building comprising 100,000 square feet and 10 floors is generated in energy modeling software to determine approximate building loads and airflow requirements. In this embodiment, weather data was based on hourly average temperatures at Boston Logan Airport.

[0181] The minimum ventilation requirement for the building is determined to be 10,000 CFM ambient airflow, and a building infrastructure exhaust airflow of 10,000 CFM is generated to balance the building. Additional ventilation and building infrastructure exhaust airflow are required during certain periods of the day, and calculations based on the restroom and kitchen spaces result in a maximum ventilation requirement of 17,500 CFM during certain periods.

[0182] The monthly output value represents the kWh required inside the building to heat and cool the building to 70°F from the monthly average temperature of the ambient airflow.

[0183] The dashed line represents the exhaust plenum system and the solid line represents the standard air source heat pump. As shown in the graph, the exhaust plenum system produces fewer kWh per month than the standard air source heat pump.

[0184] FIG. 13B illustrates a table of heating and cooling outputs of a standard air-source heat pump for a high-rise residential building, according to one embodiment.

[0185] In the monthly baseline table 1304, the monthly output values ​​represent the kWh required inside the building to heat and cool the building from the hourly average temperature of the ambient airflow to 70°F and 72°F, respectively.

[0186] In some embodiments, the thermal kWh output is less than 548.94 kWh. In some embodiments, the thermal kWh output is between 548.94 kWh and 37,674.09 kWh. In some embodiments, the thermal kWh output is greater than 37,674.09 kWh. In some embodiments, the total annual thermal output is 130,033.43 kWh.

[0187] In some embodiments, the cooling kWh output is less than 153.24 kWh. In some embodiments, the cooling kWh output is between 153.24 kWh and 43,301.17 kWh. In some embodiments, the cooling kWh output is greater than 43,301.17 kWh. In some embodiments, the total annual cooling output is 132,606.12 kWh.

[0188] FIG. 13C illustrates a table of heating and cooling outputs of an air-source heat pump with an exhaust plenum system for the high-rise residential building of FIG. 13B, according to an embodiment of the disclosed subject matter.

[0189] In the example shown in monthly table 1306 for a system with an exhaust plenum system, the thermal kWh output is less than 537.92 kWh. In some embodiments, the thermal kWh output is between 537.92 kWh and 33,511.16 kWh. In some embodiments, the thermal kWh output is greater than 33,511.16 kWh. In some embodiments, the total annual thermal output is 114,086.22 kWh.

[0190] In some embodiments, the cooling kWh output is less than 157.15 kWh. In some embodiments, the cooling kWh output is between 157.15 kWh and 34,659.84 kWh. In some embodiments, the cooling kWh output is greater than 34,659.84 kWh. In some embodiments, the total annual cooling output is 131,181.81 kWh.

[0191] In comparison to the monthly baseline table 1304 of FIG. 13B , which illustrates a table of heating and cooling outputs in kWh of a standard air-source heat pump for the same exemplary high-rise residential building, the air-source heat pump with an exhaust plenum system, in some embodiments, uses 11.05% less energy to produce heat than the standard air-source heat pump in January. In some embodiments, in February, the air-source heat pump with an exhaust plenum system uses 12.32% less energy to produce heat than the standard air-source heat pump. In some embodiments, in March, the air-source heat pump with an exhaust plenum system uses 14.33% less energy to produce heat than the standard air-source heat pump. In some embodiments, in April, the air-source heat pump with an exhaust plenum system uses 15.61% less energy to produce heat than the standard air-source heat pump. In some embodiments, in May, the air-source heat pump with an exhaust plenum system uses 10.15% less energy to produce heat than the standard air-source heat pump. In some embodiments, in June, an air-source heat pump with an exhaust plenum system uses 6.77% less energy to produce heat than a standard air-source heat pump. In some embodiments, in July, an air-source heat pump with an exhaust plenum system uses 2.01% less energy to produce heat than a standard air-source heat pump. In some embodiments, in August, an air-source heat pump with an exhaust plenum system uses 2.56% less energy to produce heat than a standard air-source heat pump. In some embodiments, in September, an air-source heat pump with an exhaust plenum system uses 5.51% less energy to produce heat than a standard air-source heat pump. In some embodiments, in October, an air-source heat pump with an exhaust plenum system uses 13.41% less energy to produce heat than a standard air-source heat pump. In some embodiments, in November, an air-source heat pump with an exhaust plenum system uses 13.50% less energy to produce heat than a standard air-source heat pump.In some embodiments, in December, an air source heat pump with an exhaust plenum system uses 12.83% less energy to produce heat than a standard air source heat pump.

[0192] In some embodiments, in March, an air-source heat pump with an exhaust plenum system uses 0.51% less energy to produce cooling than a standard air-source heat pump. In some embodiments, in April, an air-source heat pump with an exhaust plenum system uses 3.43% less energy to produce cooling than a standard air-source heat pump. In some embodiments, in May, an air-source heat pump with an exhaust plenum system uses 0.31% less energy to produce cooling than a standard air-source heat pump. In some embodiments, in June, an air-source heat pump with an exhaust plenum system uses 1.17% less energy to produce cooling than a standard air-source heat pump. In some embodiments, in July, an air-source heat pump with an exhaust plenum system uses 1.65% less energy to produce cooling than a standard air-source heat pump. In some embodiments, in August, an air-source heat pump with an exhaust plenum system uses 1.01% less energy to produce cooling than a standard air-source heat pump. In some embodiments, in September, an air-source heat pump with an exhaust plenum system uses 0.00012% less energy to produce cooling than a standard air-source heat pump. In some embodiments, in October, an air-source heat pump with an exhaust plenum system uses 0.00094% less energy to produce cooling than a standard air-source heat pump. In some embodiments, in November, an air-source heat pump with an exhaust plenum system uses 2.55% less energy to produce cooling than a standard air-source heat pump.

[0193] In some embodiments, in January, the air source heat pump with an exhaust plenum system utilizes 11.05% less total energy than the standard air source heat pump in January. In some embodiments, in February, the air source heat pump with an exhaust plenum system utilizes 12.32% less total energy than the standard air source heat pump. In some embodiments, in March, the air source heat pump with an exhaust plenum system produces a total of 14,324.96 kWh and the standard air source heat pump produces a total of 16,562.84, therefore, the air source heat pump with an exhaust plenum system utilizes 13.51% less total energy than the standard air source heat pump. In some embodiments, in April, the air source heat pump with exhaust plenum system produces a total of 7,515.44 kWh and the standard air source heat pump produces a total of 8610.08 kWh, so the air source heat pump with exhaust plenum system utilizes 12.71% less total energy than the standard air source heat pump. In some embodiments, in May, the air source heat pump with exhaust plenum system produces a total of 12,303.30 kWh and the standard air source heat pump produces a total of 12,633.72 kWh, so the air source heat pump with exhaust plenum system utilizes 2.62% less total energy than the standard air source heat pump. In some embodiments, in June, the air source heat pump with the exhaust plenum system produces a total of 23,677.21 kWh and the standard air source heat pump produces a total of 24,045.04 kWh, so the air source heat pump with the exhaust plenum system utilizes 1.53% less total energy than the standard air source heat pump. In some embodiments, in July, the air source heat pump with the exhaust plenum system produces a total of 43,123.08 kWh and the standard air source heat pump produces a total of 43,850.11 kWh, so the air source heat pump with the exhaust plenum system utilizes 1.66% less total energy than the standard air source heat pump.In some embodiments, in August, the air source heat pump with exhaust plenum system produces a total of 35,558.64 kWh and the standard air source heat pump produces a total of 35,936.70 kWh, so the air source heat pump with exhaust plenum system utilizes 1.05% less total energy than the standard air source heat pump. In some embodiments, in September, the air source heat pump with exhaust plenum system produces a total of 17,207.41 kWh and the standard air source heat pump produces a total of 17,316.03 kWh, so the air source heat pump with exhaust plenum system utilizes 0.63% less total energy than the standard air source heat pump. In some embodiments, in October, the air-source heat pump with exhaust plenum system produces a total of 7,394.37 kWh and the standard air-source heat pump produces a total of 7,976.12 kWh, so the air-source heat pump with exhaust plenum system utilizes 7.29% less total energy than the standard air-source heat pump. In some embodiments, in November, the air-source heat pump with exhaust plenum system produces a total of 10,776.35 kWh and the standard air-source heat pump produces a total of 12,429.72 kWh, so the air-source heat pump with exhaust plenum system utilizes 13.30% less total energy than the standard air-source heat pump. In some embodiments, in December, the air-source heat pump with exhaust plenum system utilizes 12.83% less energy to produce heat than the standard air-source heat pump.

[0194] FIG. 13D illustrates a table comparing the heat and cooling output of, and the efficiency improvement between, a standard air-source heat pump and an air-source heat pump with an exhaust plenum system, according to one embodiment.

[0195] In some embodiments, as shown, the total thermal output for the standard air-source heat pump is 130,033 kWh and the total thermal output for the exhaust plenum system is 114,086 kWh; therefore, the air-source heat pump with the exhaust plenum system is 12.26% more efficient than the standard air-source heat pump in this scenario.

[0196] In some embodiments, as shown, the total cooling output for the standard air-source heat pump is 132,606 kWh and the total cooling output for the air-source heat pump with an exhaust plenum system is 131,182 kWh; therefore, the air-source heat pump with an exhaust plenum system is 1.07% more efficient than the standard air-source heat pump in this scenario.

[0197] In some embodiments, as shown, the total output for the standard air-source heat pump is 262,639 kWh and the total output for the air-source heat pump with exhaust plenum system is 245,268 kWh; therefore, the air-source heat pump with exhaust plenum system is 6.61% more efficient than the standard air-source heat pump in this scenario.

[0198] FIG. 14 illustrates an example of a mini-split air source heat pump condensing unit with an exhaust plenum system, while FIG. 15 illustrates an example of a residential air source heat pump condensing unit with an exhaust plenum system, according to an embodiment of the disclosed subject matter.

[0199] The mini-split unit 1400 with an exhaust plenum system includes a condensing unit 1402 and an exhaust duct connection 1404 , and the dwelling unit 1500 with an exhaust plenum system includes an exhaust plenum connection 1504 and a condensing unit 1502 .

[0200] The disclosed exhaust plenum system can be applied to single-family homes or dwellings. Specifically, newer homes are often built with an emphasis on energy efficiency, which includes making homes more airtight to prevent heat loss and reduce energy consumption. However, building more airtight homes can also lead to a lack of natural ventilation, potentially causing indoor air quality problems such as stuffy air and increased levels of pollutants.

[0201] To address this, modern construction codes and practices often include requirements for mechanical ventilation systems. These systems require that fresh outdoor air be introduced into the home to balance the house and remove pollutants / moisture from kitchens and bathrooms, as well as the removal of exhaust air.

[0202] Exhaust air being removed from the house is directed to the exhaust plenum system via exhaust duct connection 1404 in a mini-split air source heat pump condensing unit implementation or exhaust duct connection 1504 in a residential air source heat pump implementation, and the techniques described herein can be used to increase the efficiency of the residential condensing unit and / or mini-split unit.

[0203] Although the example routines described above depict a particular sequence of operations, the sequence may be modified without departing from the scope of the present disclosure. For example, some of the depicted operations may be performed in parallel or in a different sequence without substantially affecting the functionality of the routine. In other examples, different components of an example device or system implementing the routine may perform functions substantially simultaneously or in a particular sequence.

Claims

1. A ventilation system (300) having an exhaust plenum system for improved heating and cooling of a building, comprising:

1. An air source heat pump (ASHP), comprising: An ASHP coil, Source / ThinkFan and an ASHP comprising: An exhaust plenum system comprising an open grille and an exhaust plenum, the exhaust plenum is configured to collect building infrastructure exhaust airflow, including air and / or waste heat from industrial processes, from multiple sources within the building and direct the building infrastructure exhaust airflow to the exhaust plenum system open grate; the directed building infrastructure exhaust airflow exits the exhaust plenum system open grate into an outdoor environment and combines with ambient airflow outside the exhaust plenum system to create an exhaust-ambient airflow mixture; the source / sink fan is operable to direct the exhaust-ambient airflow mixture past around the ASHP coil; an exhaust plenum system, wherein the ASHP coil is operable to extract an additional amount of energy from the exhaust-ambient airflow mixture compared to the amount of energy extracted from the ambient airflow mixture alone; A ventilation system comprising:

2. 10. The ventilation system of claim 1, wherein the exhaust plenum system is made of a durable material.

3. 10. The ventilation system of claim 1, wherein the exhaust plenum system comprises a heating coil configured to inject heat into the building infrastructure exhaust airflow.

4. 4. The ventilation system of claim 3, wherein the heating coil utilizes hot water, steam, or electricity to generate heat.

5. 10. The ventilation system of claim 1, wherein the waste heat is heat from a boiler, a data center server, computer equipment, an air compressor, a steam system, a dryer exhaust, an oven, a stove, a cooking appliance, an appliance, a generator, or a turbine.

6. 1. A method for improved heating and cooling of a building using an exhaust plenum system in conjunction with a ventilation system, comprising: directing building infrastructure exhaust airflow, including air and / or waste heat from industrial processes, from multiple sources within the building into an exhaust plenum towards an air source heat pump (ASHP); the exhaust plenum system includes an exhaust plenum system open grate that allows the building infrastructure exhaust airflow to exit the exhaust plenum into an outdoor environment, the exhaust plenum system open grate being positioned adjacent to the ASHP; mixing the building infrastructure exhaust airflow with an ambient airflow in the outdoor environment outside the exhaust plenum system to create an exhaust-ambient airflow mixture; passing the exhaust-ambient air flow mixture around an ASHP coil of the ASHP; extracting an additional amount of energy from the exhaust-ambient airflow mixture as compared to the amount of energy extracted from the ambient airflow mixture alone via the ASHP coil; A method comprising:

7. The method of claim 6, further comprising: exiting the exhaust-ambient airflow mixture outwardly through a top of a source / sink fan.

8. The method of claim 6 , further comprising injecting heat into the building infrastructure exhaust airflow using a heating coil.

9. 9. The method of claim 8, wherein the heating coil utilizes hot water, steam, or electricity to generate the heat.

10. 1. A ventilation system for a building, comprising: an air source heat pump including a compressor, a condenser, a reversing valve, and an evaporator; 1. An exhaust plenum system comprising: collecting building infrastructure exhaust airflows, including air and / or waste heat from industrial processes, from a plurality of sources within the building; directing the building infrastructure exhaust airflow through an exhaust plenum system open grate; mixing the building infrastructure exhaust airflow with an ambient airflow in an outdoor environment outside the exhaust plenum system and providing an exhaust air-ambient airflow mixture to either the evaporator or the condenser of the air-source heat pump, the exhaust air-ambient airflow mixture providing an additional amount of energy to be extracted by the evaporator or the condenser from the exhaust air-ambient airflow mixture compared to the amount of energy extracted from the ambient airflow mixture alone, improving efficiency of the air-source heat pump; an exhaust plenum system configured to A ventilation system comprising:

11. 11. The ventilation system of claim 10, further comprising ductwork coupled at a first end to a building infrastructure system that creates a building infrastructure exhaust airflow and coupled at a second end to the exhaust plenum system.

12. The ventilation system of claim 10 , wherein the exhaust plenum system comprises galvanized steel or aluminum.

13. 11. The ventilation system of claim 10, wherein the building infrastructure exhaust airflow comprises air passed over a water vapor piping system, an electrical panel, an appliance, a room with a window, or a vehicle parking structure.

14. the exhaust plenum system an exhaust plenum system open grate for allowing ambient airflow to mix with said building infrastructure exhaust airflow and providing said exhaust-ambient airflow mixture; The ventilation system of claim 10, comprising:

15. the exhaust plenum system a plurality of duct connections, one or more of the plurality of duct connections equipped with a damper or louver operable to regulate the building infrastructure exhaust airflow and prevent backflow of the building infrastructure exhaust airflow when the ventilation system is not operating; The ventilation system of claim 10, comprising:

16. The ventilation system of claim 10 , wherein the exhaust plenum system comprises an open grate formed from passages adjacent the air source heat pump.

17. 1. A method for ventilating a building, comprising: admitting an airflow into the air source heat pump via a source / sink fan; passing the airflow over an evaporator or a condenser using the source / sink fan; collecting energy from evaporation or condensation of said air stream; converting the air flow into a building infrastructure exhaust air flow from multiple sources within the building, the air flow including air and / or waste heat from industrial processes; Discharging the building infrastructure exhaust air stream from the evaporator or the condenser; collecting the building infrastructure exhaust airflow in an exhaust plenum of an exhaust plenum system; passing the building infrastructure exhaust airflow through the exhaust plenum; exiting the building infrastructure exhaust airflow from the exhaust plenum through an exhaust plenum system open grate of the exhaust plenum system; exhausting the building infrastructure exhaust air stream from the building; mixing the building infrastructure exhaust airflow with an ambient airflow in an outdoor environment outside the exhaust plenum system, thereby creating an exhaust-ambient airflow mixture; directing the exhaust air-ambient airflow mixture across the evaporator or the condenser to restart the cycle of converting the airflow from the evaporation or condensation into a building infrastructure exhaust airflow; A method comprising:

18. 18. The method of claim 17, wherein the exhaust air-ambient air flow mixture provides an additional amount of energy for extraction by the evaporator or the condenser from the exhaust air-ambient air flow mixture compared to the amount of energy extracted from the ambient air flow mixture alone, improving efficiency of the air-source heat pump.

19. 18. The method of claim 17, wherein the exhaust air-ambient airflow mixture is recycled once by the air source heat pump.

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