EP4102152A1 - Flux de contre-courant en mode ca et hp pour optimisation de la charge de pièce - Google Patents

Flux de contre-courant en mode ca et hp pour optimisation de la charge de pièce Download PDF

Info

Publication number
EP4102152A1
EP4102152A1 EP22175454.2A EP22175454A EP4102152A1 EP 4102152 A1 EP4102152 A1 EP 4102152A1 EP 22175454 A EP22175454 A EP 22175454A EP 4102152 A1 EP4102152 A1 EP 4102152A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
outdoor heat
mode
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.)
Withdrawn
Application number
EP22175454.2A
Other languages
German (de)
English (en)
Inventor
Jovet Bastien
Eric CHAPUIS
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LGL France SAS
Original Assignee
LGL France SAS
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by LGL France SAS filed Critical LGL France SAS
Publication of EP4102152A1 publication Critical patent/EP4102152A1/fr
Withdrawn legal-status Critical Current

Links

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.
  • 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 110a and a first outlet 110b and each second passage 210, represented by an arrow, has a second inlet 210a and a second outlet 210b.
  • 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 110a of first passage 110 ( FIG. 2 ) of indoor heat exchanger 310.
  • 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 110b and returns to compressor
  • 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 Figure 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 210a 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 201b 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 210a 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 Figure 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 110b 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 110a 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.
  • SCOP Heat Cap.
  • SCOP 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
  • 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)
EP22175454.2A 2021-06-09 2022-05-25 Flux de contre-courant en mode ca et hp pour optimisation de la charge de pièce Withdrawn EP4102152A1 (fr)

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
EP4102152A1 true EP4102152A1 (fr) 2022-12-14

Family

ID=81850391

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22175454.2A Withdrawn EP4102152A1 (fr) 2021-06-09 2022-05-25 Flux de contre-courant en mode ca et hp pour optimisation de la charge de pièce

Country Status (3)

Country Link
US (1) US20220397312A1 (fr)
EP (1) EP4102152A1 (fr)
CA (1) CA3161909A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3995809A (en) * 1974-01-21 1976-12-07 Aktiebolaget Svenska Flaktfabriken Arrangement for air-conditioning of one or more rooms
US4676072A (en) * 1984-10-26 1987-06-30 Kabushiki Kaisha Toshiba Bypass system for a dual refrigeration cycle air conditioner
US20040134218A1 (en) * 2003-01-09 2004-07-15 Alex Alexandre Air conditioning system, interior heat exchanger coil unit and method for conditioning ambient air
US20160025384A1 (en) * 2014-07-28 2016-01-28 Kimura Kohki Co., Ltd. Heat pump air conditioner

Family Cites Families (8)

* Cited by examiner, † Cited by third party
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
KR100210076B1 (ko) * 1996-08-14 1999-07-15 윤종용 공기조화기용 열교환기 냉매패스배열장치
JP3952510B2 (ja) * 1996-09-20 2007-08-01 株式会社日立製作所 空気調和機及びその運転制御プログラムを記録した媒体
US6644049B2 (en) * 2002-04-16 2003-11-11 Lennox Manufacturing Inc. Space conditioning system having multi-stage cooling and dehumidification capability
KR100505231B1 (ko) * 2002-12-10 2005-08-03 엘지전자 주식회사 복수개의 압축기를 갖는 공기조화기의 압축기 운전 방법
JP3939314B2 (ja) * 2004-06-10 2007-07-04 三星電子株式会社 空気調和装置及びその均油運転方法
JP5163763B2 (ja) * 2011-02-23 2013-03-13 ダイキン工業株式会社 空気調和機用熱交換器
IT201900021486A1 (it) * 2019-11-18 2021-05-18 Mitsubishi Electric Hydronics & It Cooling Systems S P A Disposizione migliorata di ciclo di refrigerazione raffreddato ad aria

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3995809A (en) * 1974-01-21 1976-12-07 Aktiebolaget Svenska Flaktfabriken Arrangement for air-conditioning of one or more rooms
US4676072A (en) * 1984-10-26 1987-06-30 Kabushiki Kaisha Toshiba Bypass system for a dual refrigeration cycle air conditioner
US20040134218A1 (en) * 2003-01-09 2004-07-15 Alex Alexandre Air conditioning system, interior heat exchanger coil unit and method for conditioning ambient air
US20160025384A1 (en) * 2014-07-28 2016-01-28 Kimura Kohki Co., Ltd. Heat pump air conditioner

Also Published As

Publication number Publication date
US20220397312A1 (en) 2022-12-15
CA3161909A1 (fr) 2022-12-09

Similar Documents

Publication Publication Date Title
US6644049B2 (en) Space conditioning system having multi-stage cooling and dehumidification capability
US9347676B2 (en) Enhanced dehumidification control with variable condenser reheat
EP4190663A1 (fr) Climatiseur et procédé de déshumidification
EP2660539A1 (fr) Procédé de fonctionnement pour un système de conditionnement d'espace avec réchauffage de gaz chaud
US11859849B2 (en) HVAC systems with evaporator bypass and supply air recirculation and methods of using same
KR101223199B1 (ko) 환기 및 냉난방 일체형 시스템
JPH0842938A (ja) 空気調和機の除湿装置及び方法
EP4102152A1 (fr) Flux de contre-courant en mode ca et hp pour optimisation de la charge de pièce
WO2021202297A1 (fr) Système de chauffage, de ventilation et de climatisation avec réchauffage
CN112178835B (zh) 空气处理单元和用于控制此类空气处理单元的方法
US11859875B2 (en) Thermodynamic heat recovery without an additional thermodynamic circuit
JPH0387535A (ja) 空調システム及び空気調和装置
US11143417B2 (en) Method and apparatus for reduction of water re-evaporation in a dedicated dehumidifier/water heater
JP2018204823A (ja) 換気システム
KR102637895B1 (ko) 차량의 열관리 시스템
JP2915788B2 (ja) マルチタイプ空気調和機
JP2004239453A (ja) 超臨界冷媒を用いたヒートポンプサイクル
JPH0894207A (ja) 空気調和装置
KR102637896B1 (ko) 차량의 열관리 시스템
WO2023148854A1 (fr) Dispositif de ventilation de type à échange de chaleur
JP4326389B2 (ja) マルチ型空気調和装置
WO2021100098A1 (fr) Dispositif de ventilation
JPH07239157A (ja) 空調機の運転制御方法
KR20200061459A (ko) 전기자동차용 냉난방 시스템
CN117190305A (zh) 一种空调及其控制方法

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: LGL FRANCE S.A.S.

18D Application deemed to be withdrawn

Effective date: 20230615