US20220397312A1 - Counter-current flow in both ac and hp modes for part load optimization - Google Patents
Counter-current flow in both ac and hp modes for part load optimization Download PDFInfo
- Publication number
- US20220397312A1 US20220397312A1 US17/342,657 US202117342657A US2022397312A1 US 20220397312 A1 US20220397312 A1 US 20220397312A1 US 202117342657 A US202117342657 A US 202117342657A US 2022397312 A1 US2022397312 A1 US 2022397312A1
- Authority
- US
- United States
- Prior art keywords
- refrigerant
- heat exchanger
- mode
- outdoor heat
- current flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000005457 optimization Methods 0.000 title description 5
- 239000003507 refrigerant Substances 0.000 claims abstract description 217
- 238000004378 air conditioning Methods 0.000 claims description 65
- 238000010438 heat treatment Methods 0.000 claims description 28
- 238000001816 cooling Methods 0.000 claims description 24
- 238000000034 method Methods 0.000 claims description 13
- 238000009423 ventilation Methods 0.000 claims description 4
- 238000005057 refrigeration Methods 0.000 claims 2
- DDMOUSALMHHKOS-UHFFFAOYSA-N 1,2-dichloro-1,1,2,2-tetrafluoroethane Chemical compound FC(F)(Cl)C(F)(F)Cl DDMOUSALMHHKOS-UHFFFAOYSA-N 0.000 description 13
- 230000001932 seasonal effect Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 5
- 238000004422 calculation algorithm Methods 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 2
- 230000003287 optical effect Effects 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000002860 competitive effect Effects 0.000 description 1
- 238000004590 computer program Methods 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 230000002085 persistent effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 238000013515 script Methods 0.000 description 1
- 239000004065 semiconductor Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/06—Several compression cycles arranged in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
Definitions
- HVAC heating, ventilation, and air conditioning
- Thermodynamic vapor-compression systems are used to regulate environmental conditions within an enclosed space.
- such systems have a circulation fan that pulls air from the enclosed space through ducts and pushes the air back into the enclosed space through additional ducts after conditioning the air (e.g., heating or cooling).
- a refrigerant may flow in a circuit between two heat exchangers, typically coils.
- One heat exchanger may be “inside” the structure (the “indoor heat exchanger” or “indoor coil”) and the other heat exchanger may be outside the structure (the “outdoor heat exchanger” or “outdoor coil”).
- the refrigerant may absorb heat as it passes through the outdoor heat exchanger and release heat as it passes through the indoor heat exchanger.
- the refrigerant may absorb heat as it passes through the indoor heat exchanger and release heat as it passes through the outdoor heat exchanger.
- Heat pumps can reverse the direction of refrigerant flow, to change between heating and air conditioning.
- a reversing valve typically controls the direction of refrigerant flow.
- State-of-the-art HVAC rooftop systems utilize two thermodynamic circuits, each thermodynamic circuit has a dedicated outdoor coil and shares an indoor coil with the other thermodynamic circuit. These state-of-the-art systems are designed for highest efficiency in either the cooling, air-conditioning (AC), mode or heating, heat pump (HP), mode.
- the state-of-the-art HVAC systems do not accommodate a configuration where the highest level of efficiency is reached in part-load for both air-conditioning and heat pump modes. Part load working conditions may be the most important for regulations and impact rooftop efficiency.
- An exemplary HVAC system operable in a cooling (AC) mode and a heat pump (HP) mode, the HVAC system including an indoor heat exchanger having a first refrigerant passage extending in a first direction and a second refrigerant passage extending in a second direction opposite from the first direction, a first refrigerant circuit comprising a first compressor, a first expansion valve, a first outdoor heat exchanger, the first refrigerant passage, and a first reversing valve operable to control a direction of first refrigerant in the first refrigerant circuit, and a second refrigerant circuit comprising a second compressor, a second expansion valve, a second outdoor heat exchanger, the second refrigerant passage, and a second reversing valve operable to control a direction of second refrigerant in the second refrigerant circuit.
- AC cooling
- HP heat pump
- the first refrigerant circuit is AC mode optimized whereby the first outdoor heat exchanger and the first refrigerant passage are counter-current flow in the AC mode and co-current flow in the HP mode
- the second refrigerant circuit is HP mode optimized whereby the second outdoor heat exchanger and the second refrigerant passage are counter-current flow in the HP mode and co-current flow in the AC mode.
- An exemplary method includes operating an HVAC system in a cooling mode or a heating mode, the HVAC system including an indoor heat exchanger having a first refrigerant passage extending in a first direction and a second refrigerant passage extending in a second direction opposite from the first direction, wherein fresh air flows generally in the second direction across the indoor heat exchanger, a first refrigerant circuit comprising a first refrigerant, a first compressor, a first outdoor heat exchanger, and the first refrigerant passage, and a second refrigerant circuit comprising a second refrigerant, a second compressor, a second outdoor heat exchanger, and the second refrigerant passage.
- the first refrigerant circuit is AC optimized whereby, in the AC mode, the first refrigerant is in counter-current flow in the first outdoor heat exchanger and the indoor heat exchanger
- the second refrigerant circuit is HP optimized whereby, in the HP mode, the second refrigerant is in counter-current flow in the second outdoor heat exchanger and the indoor heat exchanger.
- An exemplary heating and/or cooling method includes operating the HVAC system in an AC mode part load, an AC mode full load, a HP mode part load, or a HP mode full load, the HVAC system including an indoor heat exchanger having a first refrigerant passage extending in a first direction and a second refrigerant passage extending in a second direction opposite from the first direction, wherein fresh air flows generally in the second direction across the indoor heat exchanger, a first refrigerant circuit comprising a first refrigerant, a first compressor, a first outdoor heat exchanger, and the first refrigerant passage, and a second refrigerant circuit comprising a second refrigerant, a second compressor, a second outdoor heat exchanger, and the second refrigerant passage.
- Operating in the AC mode part load includes operating only the first refrigerant circuit and directing the first refrigerant in a direction from the first compressor through the first outdoor heat exchanger and then the first refrigerant passage, wherein the first refrigerant is in counter-current flow through the first outdoor heat exchanger and the first refrigerant passage.
- Operating in the AC mode full load includes directing the first refrigerant in a direction from the first compressor through the first outdoor heat exchanger and then the first refrigerant passage, where the first refrigerant is in counter-current flow through the first outdoor heat exchanger and the first refrigerant passage, and directing the second refrigerant in a direction from the second compressor through the second outdoor heat exchanger and then the second refrigerant passage, where the second refrigerant is in co-current flow in the second outdoor heat exchanger and in the second refrigerant passage.
- Operating in the HP mode part load includes operating only the second refrigerant circuit and directing the second refrigerant in a direction from the second compressor through the second refrigerant passage and then the second outdoor heat exchanger, wherein the second refrigerant is in counter-current flow in the second outdoor heat exchanger and in the second refrigerant passage.
- Operating in the HP mode full load includes directing the second refrigerant in a direction from the second compressor through the second refrigerant passage and then the second outdoor heat exchanger, where the second refrigerant is in counter-current flow in the second outdoor heat exchanger and in the second refrigerant passage, and directing the first refrigerant in a direction from the first compressor through the first refrigerant passage and then the first outdoor heat exchanger, where the first refrigerant is in co-current flow in the first outdoor heat exchanger and in the first refrigerant passage.
- FIG. 1 is a block diagram of an exemplary HVAC system that implements counter-current flow in both cooling and heating modes for part load optimization;
- FIG. 2 schematically illustrates a portion of an exemplary indoor heat exchanger implementing first and second refrigerant passages
- FIG. 3 is a block diagram of an exemplary HVAC system operating in cooling mode part load
- FIG. 4 is a block diagram of an exemplary HVAC system operating in cooling mode full load
- FIG. 5 is a block diagram of an exemplary HVAC system operating in heating mode part load.
- FIG. 6 is a block diagram of an exemplary HVAC system operating in heating mode full load.
- FIG. 1 is a schematic illustration of an exemplary HVAC system 100 .
- HVAC system 100 is a vapor-compression system comprising a first refrigerant circuit 102 that can implement a thermodynamic heat recovery process in the cooling (AC) mode and the heating (HP) mode and a second refrigerant circuit 202 that can implement a thermodynamic heat recovery process in the cooling mode and the heating mode.
- HVAC system 100 may be implemented for example as a rooftop unit.
- One of the first refrigerant circuit and the second refrigerant circuit is optimized for the cooling mode and the other refrigerant circuit is optimized for the heating mode.
- the full load performance of system 100 is a compromise between an AC designed unit and a HP designed unit and the highest level of efficiency will be reached in part load. Part load working conditions are the most important for eco-design regulations and will impact rooftop seasonal efficiency (SEER, SCOP).
- HVAC system 100 includes an indoor heat exchanger 310 that has a first refrigerant passage 110 and a second refrigerant passage 210 that extend in opposite directions through indoor heat exchanger 310 .
- Each first passage 110 represented by an arrow, has a first inlet 110 a and a first outlet 110 b and each second passage 210 , represented by an arrow, has a second inlet 210 a and a second outlet 210 b.
- Refrigerant is illustrated passing, in the AC mode, through first passage 110 in a first direction 10 and through second passage 210 in a second direction 12 opposite the first direction.
- First and second directions 10 , 12 are reversed in HP mode.
- first direction 10 is counter-current flow in AC mode and second direction 12 is co-current flow in AC mode.
- Inlet and outlet are used to generically identify respective passage ports, for example when the circuits are in the AC mode, for ease and clarity of description.
- First refrigerant circuit 102 e.g., conduit 116 , includes a first compressor 104 , a first expansion valve 106 , a first outdoor heat exchanger 108 , first passage 110 ( FIG. 2 ) of indoor heat exchanger 310 , and a first reversing valve 112 (e.g., 4-way valve) operable between a cooling mode to direct first refrigerant 114 in the direction from the first compressor to the first outdoor heat exchanger and then to the first passage of the indoor heat exchanger, and a heating mode to direct the first refrigerant in the direction from the first compressor to the first passage of the indoor heat exchanger and then to the first outdoor heat exchanger.
- a cooling mode to direct first refrigerant 114 in the direction from the first compressor to the first outdoor heat exchanger and then to the first passage of the indoor heat exchanger
- a heating mode to direct the first refrigerant in the direction from the first compressor to the first passage of the indoor heat exchanger and then to the first outdoor heat exchanger.
- first refrigerant circuit 102 is optimized for the AC mode, whereby first refrigerant 114 is in counter-current flow in first outdoor heat exchanger 108 and indoor heat exchanger 310 when in the AC mode, and first refrigerant 114 is in co-current flow in first outdoor heat exchanger 108 and indoor heat exchanger 310 when in the HP mode.
- Second refrigerant circuit 202 e.g., conduit 216 , includes a second compressor 204 , a second expansion valve 206 , a second outdoor heat exchanger 208 , second passage 210 ( FIG. 2 ) of indoor heat exchanger 310 , and a second reversing valve 212 (e.g., 4-way valve) operable between a cooling mode to direct second refrigerant 214 in the direction from the second compressor to the second outdoor heat exchanger and then to the second passage of the indoor heat exchanger, and a heating mode to direct the second refrigerant in the direction from the second compressor to the second passage of the indoor heat exchanger and then to the second outdoor heat exchanger.
- a cooling mode to direct second refrigerant 214 in the direction from the second compressor to the second outdoor heat exchanger and then to the second passage of the indoor heat exchanger
- a heating mode to direct the second refrigerant in the direction from the second compressor to the second passage of the indoor heat exchanger and then to the second outdoor heat exchanger.
- second refrigerant circuit 202 is optimized for the HP mode, whereby second refrigerant 214 is in counter-current flow in second outdoor heat exchanger 208 and indoor heat exchanger 310 when in the HP mode, and second refrigerant 214 is in co-current flow in second outdoor heat exchanger 208 and indoor heat exchanger 310 when in the AC mode.
- Indoor heat exchanger 310 may be positioned in a fresh air inlet, e.g., duct, to the conditioned space 16 , e.g., enclosure).
- An electronic controller 18 comprising computer-readable storage medium may be in communication for example with the compressors, reversing valves, dampers, blowers, and various valves to operate the HVAC system in various modes including without limitation, a cooling part load, a cooling full load, a heating part load, and a heating full load mode.
- refrigerant passes through the refrigerant passage from the inlet to the outlet and the refrigerant flow is reversed in the HP mode to flow through the refrigerant passage from the outlet to the inlet.
- FIG. 3 illustrates HVAC system 100 operating in AC mode part load, for example during warm moderate ambient temperatures.
- First refrigerant circuit 102 which is AC optimized, is operated in AC mode and second refrigerant circuit 202 , which is HP optimized, is not operated.
- One or more of first compressors 104 of first refrigerant circuit 102 are operated.
- First refrigerant 114 flows from one or more first compressors 104 to first reversing valve 112 and then first outdoor heat exchanger 108 .
- First refrigerant 114 is in counter-current flow in first outdoor heat exchanger 108 , passing in the opposite direction of ambient airflow 20 .
- First refrigerant 114 flows from first outdoor heat exchanger 108 through first expansion valve 106 to inlets 110 a of first passage 110 ( FIG.
- First refrigerant 114 is in counter-current flow in indoor heat exchanger 310 , flowing in the opposite direction of airflow 14 .
- First refrigerant 114 exists outlets 110 b and returns to compressors 104 .
- FIG. 4 illustrates HVAC system 100 operating in AC mode full load, for example during hot ambient temperatures.
- first refrigerant circuit 102 and second refrigerant circuit 202 are operated in AC mode.
- First refrigerant circuit 102 which is AC optimized, operates as illustrated in FIG. 3 , with first refrigerant 114 in counter-current flow in first outdoor heat exchanger 108 and indoor heat exchanger 310 .
- second refrigerant circuit 202 is in co-current flow through second outdoor heat exchanger 208 and indoor heat exchanger 310 .
- Second refrigerant 214 flows from one or more of second compressors 204 through reversing valve 212 to second outdoor heat exchanger 208 .
- Second refrigerant 214 is in co-current flow in second outdoor heat exchanger 208 , passing in the same direction as ambient airflow 20 .
- Second refrigerant 214 flows from second outdoor heat exchanger 208 through expansion valve 206 to inlets 210 a of second passage 210 ( FIG. 2 ) of indoor heat exchanger 310 .
- Second refrigerant 214 is in co-current flow in indoor heat exchanger 310 , flowing in the same direction as airflow 14 .
- FIG. 5 illustrates HVAC system 100 operating in HP mode part load, for example during cool moderate ambient temperatures.
- Second refrigerant circuit 202 which is HP optimized, is operated in HP mode and first refrigerant circuit 102 , which is AC optimized, is not operated.
- Second refrigerant 214 flows from one or more of second compressors 204 through reversing valve 212 to outlets 201 b of second passage 210 ( FIG. 2 ) of indoor heat exchanger 310 .
- Second refrigerant 214 is in counter-current flow in indoor heat exchanger 310 , flowing in the opposite direction as airflow 14 .
- Second refrigerant 214 exits inlets 210 a and flows through second outdoor heat exchanger 208 and returns to second compressors 204 .
- Second refrigerant 214 is in counter-current flow in second outdoor heat exchanger 208 , flowing in the opposite direction of ambient airflow 20 .
- FIG. 6 illustrates HVAC system 100 operating in HP mode full load, for example during cold ambient temperatures.
- first refrigerant circuit 102 and second refrigerant circuit 202 are operated in HP mode.
- Second refrigerant circuit 202 operates as illustrated in FIG. 5 , with second refrigerant 214 in counter-current flow in second outdoor heat exchanger 208 and indoor heat exchanger 310 .
- First refrigerant circuit 102 is operated in HP mode, directing first refrigerant 114 from first compressors 104 to outlet 110 b of first passage 110 ( FIG. 2 ) of indoor heat exchanger 310 .
- First refrigerant 114 is in co-current flow in indoor heat exchanger 310 , flowing it the same direction as airflow 14 .
- First refrigerant 114 exits inlets 110 a and flows through first expansion valve 106 and then first outdoor heat exchanger 108 .
- First refrigerant 114 is in co-current flow through first outdoor heat exchanger 108 , flowing in the same direction as ambient airflow 20 .
- the state-of-the-art HVAC systems do not accommodate counter-current flow in the indoor heat exchanger in the AC mode and in the HP mode.
- State-of-the-art HVAC systems are designed: 1) Full AC Optimized (CCF AC Mode) with counter-current flow (CCF) in the AC mode in the indoor coil and the outdoor coils, and co-current flow in the HP mode in the indoor coil and the outdoor coils; 2) AC Oriented (In CCF AC/Out CCF HP) with CCF in indoor coil in the AC mode and CCF in the outdoor coils in HP mode; 3) HP Oriented (In CCF HP/Out CCF AC) with CCF in the indoor coil in the HP mode and CCF in the outdoor coils in the AC mode; and 4) Full HP Optimized (CCF HP Mode) with CCF in the HP mode in the indoor coil and the outdoor coils and co-current flow in the HP mode in the indoor coil and the outdoor coils.
- Calculated efficiency of HVAC system 100 has identified unexpected improvements over the state-of-the-art HVAC
- Table 1 tabulates calculated European cooling capacity at full load and the seasonal energy efficiency ratio (SEER) calculated by combining full and part load operating energy efficiency ratios for different ambient temperatures, for an exemplary HVAC system 100 and state-of-the-art HVAC systems.
- SEER seasonal energy efficiency ratio
- HVAC system 100 shows the best compromise for operating in the cooling mode.
- the SEER of 171.2 for HVAC system 100 is substantially equivalent to the state-of-the-art full AC optimized system (CCF AC Mode) and is an improvement over the AC oriented, HP oriented, and Full HP optimized other state-of-the-art systems.
- Table 2 tabulates calculated European heating capacity at full load and the seasonal coefficient of performance (SCOP) ratio calculated by combining full and part load efficiency ratios for different ambient temperatures, for an exemplary HVAC system 100 and state-of-the-art HVAC systems.
- SFP seasonal coefficient of performance
- HVAC system 100 shows the best compromise for operating in the heating mode.
- the SCOP of 126.3 for HVAC system 100 is in the range of the Full HP optimized and the HP oriented state-of-the-art systems and a significant improvement over the full AC optimized and AC oriented state-of-the-art systems.
- HVAC system 100 is indicative of a full load best compromise providing substantially similar seasonal efficiency as the full AC optimized prior art systems in cooling mode and competitive seasonal performance relative to the full HP optimized prior art systems in the heating mode. HVAC system 100 also greater seasonal efficiency than the AC oriented and the HP oriented prior art systems in both the cooling and the heating mode.
- substantially is defined as largely but not necessarily wholly what is specified (and includes what is specified; e.g., substantially 90 degrees includes 90 degrees and substantially parallel includes parallel), as understood by a person of ordinary skill in the art.
- the terms “substantially,” “approximately,” “generally,” and “about” may vary from the stated value, for example, by 0.1, 0.5, 1, 2, 3, 4, 5, 10, or 15 percent understood by a person of ordinary skill in the art.
- a computer-readable storage medium encompasses one or more tangible computer-readable storage media possessing structures.
- a computer-readable storage medium may include a semiconductor-based or other integrated circuit (IC) (such as, for example, a field-programmable gate array (FPGA) or an application-specific IC (ASIC), a hard disk, an HDD, a hybrid hard drive (HHD), an optical disc, an optical disc drive (ODD), a magneto-optical disc, a magneto-optical drive, a floppy disk, a floppy disk drive (FDD), magnetic tape, a holographic storage medium, a solid-state drive (SSD), a RAM-drive, a SECURE DIGITAL card, a SECURE DIGITAL drive, a flash memory card, a flash memory drive, or any other suitable tangible computer-readable storage medium or a combination of two or more of these, where appropriate.
- IC semiconductor-based or other integrated circuit
- FPGA field-programmable gate array
- ASIC application-specific
- Particular embodiments may include one or more computer-readable storage media implementing any suitable storage.
- a computer-readable storage medium implements one or more portions of a controller as appropriate.
- a computer-readable storage medium implements RAM or ROM.
- a computer-readable storage medium implements volatile or persistent memory.
- one or more computer-readable storage media embody encoded software.
- encoded software may encompass one or more applications, bytecode, one or more computer programs, one or more executables, one or more instructions, logic, machine code, one or more scripts, or source code, and vice versa, where appropriate, that have been stored or encoded in a computer-readable storage medium.
- encoded software includes one or more application programming interfaces (APIs) stored or encoded in a computer-readable storage medium.
- APIs application programming interfaces
- Particular embodiments may use any suitable encoded software written or otherwise expressed in any suitable programming language or combination of programming languages stored or encoded in any suitable type or number of computer-readable storage media.
- encoded software may be expressed as source code or object code.
- encoded software is expressed in a higher-level programming language, such as, for example, C, Python, Java, or a suitable extension thereof.
- encoded software is expressed in a lower-level programming language, such as assembly language (or machine code).
- encoded software is expressed in JAVA.
- encoded software is expressed in Hyper Text Markup Language (HTML), Extensible Markup Language (XML), or other suitable markup language.
- acts, events, or functions of any of the algorithms described herein can be performed in a different sequence, can be added, merged, or left out altogether (e.g., not all described acts or events are necessary for the practice of the algorithms).
- acts or events can be performed concurrently, e.g., through multi-threaded processing, interrupt processing, or multiple processors or processor cores or on other parallel architectures, rather than sequentially.
- certain computer-implemented tasks are described as being performed by a particular entity, other embodiments are possible in which these tasks are performed by a different entity.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
- This application relates generally to heating, ventilation, and air conditioning (HVAC) systems and more particularly, but not by way of limitation, to implementing, in a two or more thermodynamic circuit HVAC system, part load optimization and full load best compromise.
- This section provides background information to facilitate a better understanding of the various aspects of the disclosure. It should be understood that the statements in this section of this document are to be read in this light, and not as admissions of prior art.
- Thermodynamic vapor-compression systems are used to regulate environmental conditions within an enclosed space. Typically, such systems have a circulation fan that pulls air from the enclosed space through ducts and pushes the air back into the enclosed space through additional ducts after conditioning the air (e.g., heating or cooling). A refrigerant may flow in a circuit between two heat exchangers, typically coils. One heat exchanger may be “inside” the structure (the “indoor heat exchanger” or “indoor coil”) and the other heat exchanger may be outside the structure (the “outdoor heat exchanger” or “outdoor coil”). For heating, the refrigerant may absorb heat as it passes through the outdoor heat exchanger and release heat as it passes through the indoor heat exchanger. For air conditioning, the refrigerant may absorb heat as it passes through the indoor heat exchanger and release heat as it passes through the outdoor heat exchanger. Heat pumps can reverse the direction of refrigerant flow, to change between heating and air conditioning. A reversing valve typically controls the direction of refrigerant flow.
- State-of-the-art HVAC rooftop systems utilize two thermodynamic circuits, each thermodynamic circuit has a dedicated outdoor coil and shares an indoor coil with the other thermodynamic circuit. These state-of-the-art systems are designed for highest efficiency in either the cooling, air-conditioning (AC), mode or heating, heat pump (HP), mode. The state-of-the-art HVAC systems do not accommodate a configuration where the highest level of efficiency is reached in part-load for both air-conditioning and heat pump modes. Part load working conditions may be the most important for regulations and impact rooftop efficiency.
- This summary is provided to introduce a selection of concepts that are further described below in the detailed description. This summary is not necessarily intended to identify key or essential features of the claimed subject matter, nor is it intended to be used as an aid in limiting the scope of claimed subject matter.
- An exemplary HVAC system operable in a cooling (AC) mode and a heat pump (HP) mode, the HVAC system including an indoor heat exchanger having a first refrigerant passage extending in a first direction and a second refrigerant passage extending in a second direction opposite from the first direction, a first refrigerant circuit comprising a first compressor, a first expansion valve, a first outdoor heat exchanger, the first refrigerant passage, and a first reversing valve operable to control a direction of first refrigerant in the first refrigerant circuit, and a second refrigerant circuit comprising a second compressor, a second expansion valve, a second outdoor heat exchanger, the second refrigerant passage, and a second reversing valve operable to control a direction of second refrigerant in the second refrigerant circuit.
- In an exemplary embodiment, the first refrigerant circuit is AC mode optimized whereby the first outdoor heat exchanger and the first refrigerant passage are counter-current flow in the AC mode and co-current flow in the HP mode, and the second refrigerant circuit is HP mode optimized whereby the second outdoor heat exchanger and the second refrigerant passage are counter-current flow in the HP mode and co-current flow in the AC mode.
- An exemplary method includes operating an HVAC system in a cooling mode or a heating mode, the HVAC system including an indoor heat exchanger having a first refrigerant passage extending in a first direction and a second refrigerant passage extending in a second direction opposite from the first direction, wherein fresh air flows generally in the second direction across the indoor heat exchanger, a first refrigerant circuit comprising a first refrigerant, a first compressor, a first outdoor heat exchanger, and the first refrigerant passage, and a second refrigerant circuit comprising a second refrigerant, a second compressor, a second outdoor heat exchanger, and the second refrigerant passage. In an exemplary embodiment, the first refrigerant circuit is AC optimized whereby, in the AC mode, the first refrigerant is in counter-current flow in the first outdoor heat exchanger and the indoor heat exchanger, and the second refrigerant circuit is HP optimized whereby, in the HP mode, the second refrigerant is in counter-current flow in the second outdoor heat exchanger and the indoor heat exchanger.
- An exemplary heating and/or cooling method includes operating the HVAC system in an AC mode part load, an AC mode full load, a HP mode part load, or a HP mode full load, the HVAC system including an indoor heat exchanger having a first refrigerant passage extending in a first direction and a second refrigerant passage extending in a second direction opposite from the first direction, wherein fresh air flows generally in the second direction across the indoor heat exchanger, a first refrigerant circuit comprising a first refrigerant, a first compressor, a first outdoor heat exchanger, and the first refrigerant passage, and a second refrigerant circuit comprising a second refrigerant, a second compressor, a second outdoor heat exchanger, and the second refrigerant passage. Operating in the AC mode part load includes operating only the first refrigerant circuit and directing the first refrigerant in a direction from the first compressor through the first outdoor heat exchanger and then the first refrigerant passage, wherein the first refrigerant is in counter-current flow through the first outdoor heat exchanger and the first refrigerant passage. Operating in the AC mode full load includes directing the first refrigerant in a direction from the first compressor through the first outdoor heat exchanger and then the first refrigerant passage, where the first refrigerant is in counter-current flow through the first outdoor heat exchanger and the first refrigerant passage, and directing the second refrigerant in a direction from the second compressor through the second outdoor heat exchanger and then the second refrigerant passage, where the second refrigerant is in co-current flow in the second outdoor heat exchanger and in the second refrigerant passage. Operating in the HP mode part load includes operating only the second refrigerant circuit and directing the second refrigerant in a direction from the second compressor through the second refrigerant passage and then the second outdoor heat exchanger, wherein the second refrigerant is in counter-current flow in the second outdoor heat exchanger and in the second refrigerant passage. Operating in the HP mode full load includes directing the second refrigerant in a direction from the second compressor through the second refrigerant passage and then the second outdoor heat exchanger, where the second refrigerant is in counter-current flow in the second outdoor heat exchanger and in the second refrigerant passage, and directing the first refrigerant in a direction from the first compressor through the first refrigerant passage and then the first outdoor heat exchanger, where the first refrigerant is in co-current flow in the first outdoor heat exchanger and in the first refrigerant passage.
- The disclosure is best understood from the following detailed description when read with the accompanying figures. It is emphasized that, in accordance with standard practice in the industry, various features are not drawn to scale. In fact, the dimensions of various features may be arbitrarily increased or reduced for clarity of discussion.
-
FIG. 1 is a block diagram of an exemplary HVAC system that implements counter-current flow in both cooling and heating modes for part load optimization; -
FIG. 2 schematically illustrates a portion of an exemplary indoor heat exchanger implementing first and second refrigerant passages; -
FIG. 3 is a block diagram of an exemplary HVAC system operating in cooling mode part load; -
FIG. 4 is a block diagram of an exemplary HVAC system operating in cooling mode full load; -
FIG. 5 is a block diagram of an exemplary HVAC system operating in heating mode part load; and -
FIG. 6 is a block diagram of an exemplary HVAC system operating in heating mode full load. - Various embodiments will now be described more fully with reference to the accompanying drawings. The disclosure may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein.
-
FIG. 1 is a schematic illustration of anexemplary HVAC system 100.HVAC system 100 is a vapor-compression system comprising afirst refrigerant circuit 102 that can implement a thermodynamic heat recovery process in the cooling (AC) mode and the heating (HP) mode and asecond refrigerant circuit 202 that can implement a thermodynamic heat recovery process in the cooling mode and the heating mode.HVAC system 100 may be implemented for example as a rooftop unit. One of the first refrigerant circuit and the second refrigerant circuit is optimized for the cooling mode and the other refrigerant circuit is optimized for the heating mode. The full load performance ofsystem 100 is a compromise between an AC designed unit and a HP designed unit and the highest level of efficiency will be reached in part load. Part load working conditions are the most important for eco-design regulations and will impact rooftop seasonal efficiency (SEER, SCOP). - With additional reference to
FIG. 2 ,HVAC system 100 includes anindoor heat exchanger 310 that has a first refrigerant passage 110 and a second refrigerant passage 210 that extend in opposite directions throughindoor heat exchanger 310. Each first passage 110, represented by an arrow, has afirst inlet 110 a and afirst outlet 110 b and each second passage 210, represented by an arrow, has asecond inlet 210 a and asecond outlet 210 b. Refrigerant is illustrated passing, in the AC mode, through first passage 110 in a first direction 10 and through second passage 210 in a second direction 12 opposite the first direction. First and second directions 10, 12 are reversed in HP mode. Relative to the direction ofairflow 14, e.g., blown air, across indoor heat exchanger, first direction 10 is counter-current flow in AC mode and second direction 12 is co-current flow in AC mode. Inlet and outlet are used to generically identify respective passage ports, for example when the circuits are in the AC mode, for ease and clarity of description. -
First refrigerant circuit 102, e.g.,conduit 116, includes afirst compressor 104, afirst expansion valve 106, a firstoutdoor heat exchanger 108, first passage 110 (FIG. 2 ) ofindoor heat exchanger 310, and a first reversing valve 112 (e.g., 4-way valve) operable between a cooling mode to directfirst refrigerant 114 in the direction from the first compressor to the first outdoor heat exchanger and then to the first passage of the indoor heat exchanger, and a heating mode to direct the first refrigerant in the direction from the first compressor to the first passage of the indoor heat exchanger and then to the first outdoor heat exchanger. In this example,first refrigerant circuit 102 is optimized for the AC mode, wherebyfirst refrigerant 114 is in counter-current flow in firstoutdoor heat exchanger 108 andindoor heat exchanger 310 when in the AC mode, andfirst refrigerant 114 is in co-current flow in firstoutdoor heat exchanger 108 andindoor heat exchanger 310 when in the HP mode. -
Second refrigerant circuit 202, e.g.,conduit 216, includes asecond compressor 204, asecond expansion valve 206, a secondoutdoor heat exchanger 208, second passage 210 (FIG. 2 ) ofindoor heat exchanger 310, and a second reversing valve 212 (e.g., 4-way valve) operable between a cooling mode to directsecond refrigerant 214 in the direction from the second compressor to the second outdoor heat exchanger and then to the second passage of the indoor heat exchanger, and a heating mode to direct the second refrigerant in the direction from the second compressor to the second passage of the indoor heat exchanger and then to the second outdoor heat exchanger. In this example,second refrigerant circuit 202 is optimized for the HP mode, wherebysecond refrigerant 214 is in counter-current flow in secondoutdoor heat exchanger 208 andindoor heat exchanger 310 when in the HP mode, andsecond refrigerant 214 is in co-current flow in secondoutdoor heat exchanger 208 andindoor heat exchanger 310 when in the AC mode. -
Indoor heat exchanger 310 may be positioned in a fresh air inlet, e.g., duct, to the conditionedspace 16, e.g., enclosure). Anelectronic controller 18 comprising computer-readable storage medium may be in communication for example with the compressors, reversing valves, dampers, blowers, and various valves to operate the HVAC system in various modes including without limitation, a cooling part load, a cooling full load, a heating part load, and a heating full load mode. For example, in the AC mode refrigerant passes through the refrigerant passage from the inlet to the outlet and the refrigerant flow is reversed in the HP mode to flow through the refrigerant passage from the outlet to the inlet. -
FIG. 3 illustratesHVAC system 100 operating in AC mode part load, for example during warm moderate ambient temperatures.First refrigerant circuit 102, which is AC optimized, is operated in AC mode andsecond refrigerant circuit 202, which is HP optimized, is not operated. One or more offirst compressors 104 offirst refrigerant circuit 102 are operated.First refrigerant 114 flows from one or morefirst compressors 104 to firstreversing valve 112 and then firstoutdoor heat exchanger 108. First refrigerant 114 is in counter-current flow in firstoutdoor heat exchanger 108, passing in the opposite direction ofambient airflow 20. First refrigerant 114 flows from firstoutdoor heat exchanger 108 throughfirst expansion valve 106 toinlets 110 a of first passage 110 (FIG. 2 ) ofindoor heat exchanger 310. First refrigerant 114 is in counter-current flow inindoor heat exchanger 310, flowing in the opposite direction ofairflow 14. First refrigerant 114 existsoutlets 110 b and returns to compressors 104. -
FIG. 4 illustratesHVAC system 100 operating in AC mode full load, for example during hot ambient temperatures. In AC mode full load, firstrefrigerant circuit 102 and secondrefrigerant circuit 202 are operated in AC mode. Firstrefrigerant circuit 102, which is AC optimized, operates as illustrated inFIG. 3 , with first refrigerant 114 in counter-current flow in firstoutdoor heat exchanger 108 andindoor heat exchanger 310. In AC mode, secondrefrigerant circuit 202 is in co-current flow through secondoutdoor heat exchanger 208 andindoor heat exchanger 310.Second refrigerant 214 flows from one or more ofsecond compressors 204 through reversingvalve 212 to secondoutdoor heat exchanger 208.Second refrigerant 214 is in co-current flow in secondoutdoor heat exchanger 208, passing in the same direction asambient airflow 20.Second refrigerant 214 flows from secondoutdoor heat exchanger 208 throughexpansion valve 206 toinlets 210 a of second passage 210 (FIG. 2 ) ofindoor heat exchanger 310.Second refrigerant 214 is in co-current flow inindoor heat exchanger 310, flowing in the same direction asairflow 14. -
FIG. 5 illustratesHVAC system 100 operating in HP mode part load, for example during cool moderate ambient temperatures. Secondrefrigerant circuit 202, which is HP optimized, is operated in HP mode and firstrefrigerant circuit 102, which is AC optimized, is not operated.Second refrigerant 214 flows from one or more ofsecond compressors 204 through reversingvalve 212 to outlets 201 b of second passage 210 (FIG. 2 ) ofindoor heat exchanger 310. -
Second refrigerant 214 is in counter-current flow inindoor heat exchanger 310, flowing in the opposite direction asairflow 14.Second refrigerant 214exits inlets 210 a and flows through secondoutdoor heat exchanger 208 and returns tosecond compressors 204.Second refrigerant 214 is in counter-current flow in secondoutdoor heat exchanger 208, flowing in the opposite direction ofambient airflow 20. -
FIG. 6 illustratesHVAC system 100 operating in HP mode full load, for example during cold ambient temperatures. In HP mode full load, firstrefrigerant circuit 102 and secondrefrigerant circuit 202 are operated in HP mode. Secondrefrigerant circuit 202 operates as illustrated inFIG. 5 , with second refrigerant 214 in counter-current flow in secondoutdoor heat exchanger 208 andindoor heat exchanger 310. Firstrefrigerant circuit 102 is operated in HP mode, directing first refrigerant 114 fromfirst compressors 104 tooutlet 110 b of first passage 110 (FIG. 2 ) ofindoor heat exchanger 310. First refrigerant 114 is in co-current flow inindoor heat exchanger 310, flowing it the same direction asairflow 14. First refrigerant 114exits inlets 110 a and flows throughfirst expansion valve 106 and then firstoutdoor heat exchanger 108. First refrigerant 114 is in co-current flow through firstoutdoor heat exchanger 108, flowing in the same direction asambient airflow 20. - The state-of-the-art HVAC systems do not accommodate counter-current flow in the indoor heat exchanger in the AC mode and in the HP mode. State-of-the-art HVAC systems are designed: 1) Full AC Optimized (CCF AC Mode) with counter-current flow (CCF) in the AC mode in the indoor coil and the outdoor coils, and co-current flow in the HP mode in the indoor coil and the outdoor coils; 2) AC Oriented (In CCF AC/Out CCF HP) with CCF in indoor coil in the AC mode and CCF in the outdoor coils in HP mode; 3) HP Oriented (In CCF HP/Out CCF AC) with CCF in the indoor coil in the HP mode and CCF in the outdoor coils in the AC mode; and 4) Full HP Optimized (CCF HP Mode) with CCF in the HP mode in the indoor coil and the outdoor coils and co-current flow in the HP mode in the indoor coil and the outdoor coils. Calculated efficiency of
HVAC system 100 has identified unexpected improvements over the state-of-the-art HVAC systems in particular in the important seasonal energy efficiency ratio (SEER) and the seasonal coefficient of performance (SCOP), as illustrated in Tables 1 and 2 below. - Table 1 tabulates calculated European cooling capacity at full load and the seasonal energy efficiency ratio (SEER) calculated by combining full and part load operating energy efficiency ratios for different ambient temperatures, for an
exemplary HVAC system 100 and state-of-the-art HVAC systems. -
TABLE 1 (AC Mode) Eur. Cool HVAC System Optimization Cap. (Kw) SEER CCF AC MODE Full AC Optimized 110.0 171.9 In CCF AC/Out CCF HP AC Oriented 109.7 168.9 In CCF HP/Out CCF AC HP Oriented 107.8 169.3 CCF HP MODE Full HP Optimized 107.6 166.7 HVAC System 100Part Load Optimized 108.8 171.2 - Table 1 illustrates that
HVAC system 100 shows the best compromise for operating in the cooling mode. The SEER of 171.2 forHVAC system 100 is substantially equivalent to the state-of-the-art full AC optimized system (CCF AC Mode) and is an improvement over the AC oriented, HP oriented, and Full HP optimized other state-of-the-art systems. - Table 2 tabulates calculated European heating capacity at full load and the seasonal coefficient of performance (SCOP) ratio calculated by combining full and part load efficiency ratios for different ambient temperatures, for an
exemplary HVAC system 100 and state-of-the-art HVAC systems. -
TABLE 2 (HP Mode) Eur. Heat HVAC System Optimization Cap. (kW) SCOP CCF AC MODE Full AC Optimized 104.2 117.5 In CCF AC/Out CCF HP AC Oriented 104.3 118.0 In CCF HP/Out CCF AC HP Oriented 106.8 128.1 CCF HP MODE Full HP Optimized 107.4 128.5 HVAC System 100Part Load Optimized 105.8 126.3 - Table 2 illustrates that
HVAC system 100 shows the best compromise for operating in the heating mode. The SCOP of 126.3 forHVAC system 100 is in the range of the Full HP optimized and the HP oriented state-of-the-art systems and a significant improvement over the full AC optimized and AC oriented state-of-the-art systems. - Accordingly,
HVAC system 100 is indicative of a full load best compromise providing substantially similar seasonal efficiency as the full AC optimized prior art systems in cooling mode and competitive seasonal performance relative to the full HP optimized prior art systems in the heating mode.HVAC system 100 also greater seasonal efficiency than the AC oriented and the HP oriented prior art systems in both the cooling and the heating mode. - The term “substantially” is defined as largely but not necessarily wholly what is specified (and includes what is specified; e.g., substantially 90 degrees includes 90 degrees and substantially parallel includes parallel), as understood by a person of ordinary skill in the art. In any disclosed embodiment, the terms “substantially,” “approximately,” “generally,” and “about” may vary from the stated value, for example, by 0.1, 0.5, 1, 2, 3, 4, 5, 10, or 15 percent understood by a person of ordinary skill in the art.
- For purposes of this disclosure, the term computer-readable storage medium encompasses one or more tangible computer-readable storage media possessing structures. As an example and not by way of limitation, a computer-readable storage medium may include a semiconductor-based or other integrated circuit (IC) (such as, for example, a field-programmable gate array (FPGA) or an application-specific IC (ASIC), a hard disk, an HDD, a hybrid hard drive (HHD), an optical disc, an optical disc drive (ODD), a magneto-optical disc, a magneto-optical drive, a floppy disk, a floppy disk drive (FDD), magnetic tape, a holographic storage medium, a solid-state drive (SSD), a RAM-drive, a SECURE DIGITAL card, a SECURE DIGITAL drive, a flash memory card, a flash memory drive, or any other suitable tangible computer-readable storage medium or a combination of two or more of these, where appropriate.
- Particular embodiments may include one or more computer-readable storage media implementing any suitable storage. In particular embodiments, a computer-readable storage medium implements one or more portions of a controller as appropriate. In particular embodiments, a computer-readable storage medium implements RAM or ROM. In particular embodiments, a computer-readable storage medium implements volatile or persistent memory. In particular embodiments, one or more computer-readable storage media embody encoded software.
- In this patent application, reference to encoded software may encompass one or more applications, bytecode, one or more computer programs, one or more executables, one or more instructions, logic, machine code, one or more scripts, or source code, and vice versa, where appropriate, that have been stored or encoded in a computer-readable storage medium. In particular embodiments, encoded software includes one or more application programming interfaces (APIs) stored or encoded in a computer-readable storage medium. Particular embodiments may use any suitable encoded software written or otherwise expressed in any suitable programming language or combination of programming languages stored or encoded in any suitable type or number of computer-readable storage media. In particular embodiments, encoded software may be expressed as source code or object code. In particular embodiments, encoded software is expressed in a higher-level programming language, such as, for example, C, Python, Java, or a suitable extension thereof. In particular embodiments, encoded software is expressed in a lower-level programming language, such as assembly language (or machine code). In particular embodiments, encoded software is expressed in JAVA. In particular embodiments, encoded software is expressed in Hyper Text Markup Language (HTML), Extensible Markup Language (XML), or other suitable markup language.
- Depending on the embodiment, certain acts, events, or functions of any of the algorithms described herein can be performed in a different sequence, can be added, merged, or left out altogether (e.g., not all described acts or events are necessary for the practice of the algorithms). Moreover, in certain embodiments, acts or events can be performed concurrently, e.g., through multi-threaded processing, interrupt processing, or multiple processors or processor cores or on other parallel architectures, rather than sequentially. Although certain computer-implemented tasks are described as being performed by a particular entity, other embodiments are possible in which these tasks are performed by a different entity.
- Conditional language used herein, such as, among others, “can,” “might,” “may,” “e.g.,” and the like, unless specifically stated otherwise, or otherwise understood within the context as used, is generally intended to convey that certain embodiments include, while other embodiments do not include, certain features, elements and/or states. Thus, such conditional language is not generally intended to imply that features, elements and/or states are in any way required for one or more embodiments or that one or more embodiments necessarily include logic for deciding, with or without author input or prompting, whether these features, elements and/or states are included or are to be performed in any particular embodiment.
- While the above detailed description has shown, described, and pointed out novel features as applied to various embodiments, it will be understood that various omissions, substitutions, and changes in the form and details of the devices or algorithms illustrated can be made without departing from the spirit of the disclosure. As will be recognized, the processes described herein can be embodied within a form that does not provide all of the features and benefits set forth herein, as some features can be used or practiced separately from others. The scope of protection is defined by the appended claims rather than by the foregoing description. All changes which come within the meaning and range of equivalency of the claims are to be embraced within their scope.
Claims (20)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US17/342,657 US20220397312A1 (en) | 2021-06-09 | 2021-06-09 | Counter-current flow in both ac and hp modes for part load optimization |
EP22175454.2A EP4102152A1 (en) | 2021-06-09 | 2022-05-25 | Counter-current flow in both ac and hp modes for part load optimization |
CA3161909A CA3161909A1 (en) | 2021-06-09 | 2022-06-08 | Counter-current flow in both ac and hp modes for part load optimization |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US17/342,657 US20220397312A1 (en) | 2021-06-09 | 2021-06-09 | Counter-current flow in both ac and hp modes for part load optimization |
Publications (1)
Publication Number | Publication Date |
---|---|
US20220397312A1 true US20220397312A1 (en) | 2022-12-15 |
Family
ID=81850391
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US17/342,657 Pending US20220397312A1 (en) | 2021-06-09 | 2021-06-09 | Counter-current flow in both ac and hp modes for part load optimization |
Country Status (3)
Country | Link |
---|---|
US (1) | US20220397312A1 (en) |
EP (1) | EP4102152A1 (en) |
CA (1) | CA3161909A1 (en) |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4332137A (en) * | 1979-10-22 | 1982-06-01 | Carrier Corporation | Heat exchange apparatus and method having two refrigeration circuits |
JPH1073395A (en) * | 1996-08-14 | 1998-03-17 | Samsung Electron Co Ltd | Refrigerant path array apparatus of heat exchanger for air conditioning equipment |
US6644049B2 (en) * | 2002-04-16 | 2003-11-11 | Lennox Manufacturing Inc. | Space conditioning system having multi-stage cooling and dehumidification capability |
WO2004018946A2 (en) * | 2002-08-23 | 2004-03-04 | Hebert Thomas H | Integrated dual circuit evaporator |
US20040107709A1 (en) * | 2002-12-10 | 2004-06-10 | Lg Electronics Inc. | Method for operating compressors of air conditioner |
US20050279111A1 (en) * | 2004-06-10 | 2005-12-22 | Samsung Electronics Co., Ltd. | Air conditioner and method for performing oil equalizing operation in the air conditioner |
JP3952510B2 (en) * | 1996-09-20 | 2007-08-01 | 株式会社日立製作所 | Air conditioner and medium on which operation control program is recorded |
WO2012114719A1 (en) * | 2011-02-23 | 2012-08-30 | ダイキン工業株式会社 | Heat exchanger for air conditioner |
US20220404072A1 (en) * | 2019-11-18 | 2022-12-22 | Mitsubishi Electric Hydronics & IT Cooling Systems S.p.A. | Air-Cooled Refrigeration Cycle Arrangement |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE390209C (en) * | 1974-01-21 | 1979-01-15 | Svenska Flaektfabriken Ab | DEVICE FOR AIR TREATMENT OF ONE OR SEVERAL PREMISES |
JPH0327249Y2 (en) * | 1984-10-26 | 1991-06-12 | ||
CA2415993A1 (en) * | 2003-01-09 | 2004-07-09 | Refrigeration Noel Inc. | Air conditioning system, interior heat exchanger coil unit and method for conditioning ambient air |
JP5805833B1 (en) * | 2014-07-28 | 2015-11-10 | 木村工機株式会社 | Heat pump air conditioner |
-
2021
- 2021-06-09 US US17/342,657 patent/US20220397312A1/en active Pending
-
2022
- 2022-05-25 EP EP22175454.2A patent/EP4102152A1/en not_active Withdrawn
- 2022-06-08 CA CA3161909A patent/CA3161909A1/en active Pending
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4332137A (en) * | 1979-10-22 | 1982-06-01 | Carrier Corporation | Heat exchange apparatus and method having two refrigeration circuits |
JPH1073395A (en) * | 1996-08-14 | 1998-03-17 | Samsung Electron Co Ltd | Refrigerant path array apparatus of heat exchanger for air conditioning equipment |
JP3952510B2 (en) * | 1996-09-20 | 2007-08-01 | 株式会社日立製作所 | Air conditioner and medium on which operation control program is recorded |
US6644049B2 (en) * | 2002-04-16 | 2003-11-11 | Lennox Manufacturing Inc. | Space conditioning system having multi-stage cooling and dehumidification capability |
WO2004018946A2 (en) * | 2002-08-23 | 2004-03-04 | Hebert Thomas H | Integrated dual circuit evaporator |
US20040107709A1 (en) * | 2002-12-10 | 2004-06-10 | Lg Electronics Inc. | Method for operating compressors of air conditioner |
US20050279111A1 (en) * | 2004-06-10 | 2005-12-22 | Samsung Electronics Co., Ltd. | Air conditioner and method for performing oil equalizing operation in the air conditioner |
WO2012114719A1 (en) * | 2011-02-23 | 2012-08-30 | ダイキン工業株式会社 | Heat exchanger for air conditioner |
US20220404072A1 (en) * | 2019-11-18 | 2022-12-22 | Mitsubishi Electric Hydronics & IT Cooling Systems S.p.A. | Air-Cooled Refrigeration Cycle Arrangement |
Non-Patent Citations (3)
Title |
---|
JP-3952510-B2 English Translation (Year: 2007) * |
JP-H1073395-A English Translation (Year: 1998) * |
WO-2012114719-A1 English Translation (Year: 2012) * |
Also Published As
Publication number | Publication date |
---|---|
CA3161909A1 (en) | 2022-12-09 |
EP4102152A1 (en) | 2022-12-14 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6644049B2 (en) | Space conditioning system having multi-stage cooling and dehumidification capability | |
CN102252371B (en) | There is the computer room air conditioner of precooler | |
US9347676B2 (en) | Enhanced dehumidification control with variable condenser reheat | |
US4104890A (en) | Air conditioning apparatus | |
WO2018047331A1 (en) | Air conditioning device | |
KR101223199B1 (en) | Airconditioing Circulation System | |
JP4182494B2 (en) | Large temperature difference air conditioning system | |
JP6949130B2 (en) | Refrigeration cycle equipment | |
US11859849B2 (en) | HVAC systems with evaporator bypass and supply air recirculation and methods of using same | |
JPH0842938A (en) | Dehumidifying device and method of air conditioner | |
US20220397312A1 (en) | Counter-current flow in both ac and hp modes for part load optimization | |
US20210302073A1 (en) | Heating, Ventilation, and Air-Conditioning System with Reheat | |
US20240191918A1 (en) | Systems and methods for defrost of heat pump systems | |
JP2018204823A (en) | Ventilation system | |
JP2002286327A (en) | Dehumidifying/air conditioning apparatus | |
US11859875B2 (en) | Thermodynamic heat recovery without an additional thermodynamic circuit | |
CN112178835B (en) | Air treatment unit and method for controlling such an air treatment unit | |
US11143417B2 (en) | Method and apparatus for reduction of water re-evaporation in a dedicated dehumidifier/water heater | |
EP3982059A1 (en) | Heat management system | |
KR102637895B1 (en) | Heat management system of vehicle | |
WO2021100098A1 (en) | Ventilation device | |
WO2024201674A1 (en) | Refrigeration cycle device | |
US11629864B2 (en) | Multi-type air conditioner | |
JPH0894207A (en) | Air conditioner | |
WO2023148854A1 (en) | Heat-exchange-type ventilation device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: LGL FRANCE S.A.S., FRANCE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:JOVET, BASTIEN;CHAPUIS, ERIC;REEL/FRAME:056495/0690 Effective date: 20210607 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: RESPONSE AFTER FINAL ACTION FORWARDED TO EXAMINER |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
AS | Assignment |
Owner name: LENNOX INDUSTRIES INC., TEXAS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:LGL FRANCE, S.A.S.;REEL/FRAME:065060/0309 Effective date: 20230921 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: RESPONSE AFTER FINAL ACTION FORWARDED TO EXAMINER |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: ADVISORY ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |