EP4198416A1 - Machine frigorifique - Google Patents

Machine frigorifique Download PDF

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Publication number
EP4198416A1
EP4198416A1 EP21875130.3A EP21875130A EP4198416A1 EP 4198416 A1 EP4198416 A1 EP 4198416A1 EP 21875130 A EP21875130 A EP 21875130A EP 4198416 A1 EP4198416 A1 EP 4198416A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
temperature
compressor
low
expansion valve
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
Application number
EP21875130.3A
Other languages
German (de)
English (en)
Other versions
EP4198416A4 (fr
Inventor
Yuki Namba
Takahide Ito
Atsushi Enya
Toshiyuki Ishida
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
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 Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP4198416A1 publication Critical patent/EP4198416A1/fr
Publication of EP4198416A4 publication Critical patent/EP4198416A4/fr
Pending legal-status Critical Current

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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
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators

Definitions

  • GWP global warming potential
  • the present disclosure has been made to solve the above problems, and an object thereof is to provide a chiller capable of achieving both a low GWP and a high cooling capacity.
  • a chiller includes: a low-temperature cycle including an evaporator that exchanges heat between an air in a freezing chamber and a first refrigerant, a first compressor that compresses the low-pressure gas-phase first refrigerant supplied from the evaporator, and a low-temperature-side expansion valve that lower a pressure of the first refrigerant that has passed through the first compressor; a high-temperature cycle including a condenser that exchanges heat between an outside air and a second refrigerant, a second compressor that compresses the second refrigerant and supplies the second refrigerant to the condenser, and a high-temperature-side expansion valve that lowers a pressure of the second refrigerant that has passed through the condenser; an intermediate heat exchanger that exchanges heat between the first refrigerant flowing from the first compressor and the second refrigerant flowing from the high-temperature-side expansion valve; and a gas injection circuit that is provided
  • the chiller 100 includes a high-temperature cycle CH, a low-temperature cycle CL, an intermediate heat exchanger 10 connecting the high-temperature cycle CH and the low-temperature cycle CL, and a gas injection circuit 9. That is, the chiller 100 forms a cascade cycle type refrigeration circuit.
  • a refrigerant (a second refrigerant described later) that exchanges heat with an outside air in the high-temperature cycle CH exchanges heat with another refrigerant (a first refrigerant described later) on the low-temperature cycle CL side at the intermediate heat exchanger 10.
  • heat is exchanged between an indoor air and the refrigerant.
  • the high-temperature cycle CH includes a high-temperature-side pipe P2, a second compressor 4, a condenser 5, a high-temperature-side expansion valve 6 (a high-temperature-side first expansion valve 61 and a high-temperature-side second expansion valve 62), and a high-temperature-side receiver 82.
  • the high-temperature-side pipe P2 is a pipeline connected in an annular shape, and an inside thereof is filled with the second refrigerant.
  • the second refrigerant contains only carbon dioxide.
  • the second compressor 4 On the high-temperature-side pipe P2, from an upstream side to a downstream side in a flow direction of the second refrigerant, the second compressor 4, the condenser 5, the high-temperature-side first expansion valve 61, the high-temperature-side receiver 82, and the high-temperature-side second expansion valve 62 are arranged in this order.
  • the second compressor 4 compresses a low-pressure gas-phase refrigerant supplied from the intermediate heat exchanger 10 to generate a high-temperature and high-pressure gas-phase refrigerant.
  • the second compressor 4 is a so-called scroll rotary type two-stage compressor, in which a rotary compressor 41 is used as a low pressure side and a scroll compressor 42 is used as a high pressure side.
  • the rotary compressor 41 and the scroll compressor 42 are, as an exception, coaxially connected to each other.
  • the condenser 5 is provided outside a freezing chamber (a room to be frozen). In the condenser 5, heat is exchanged between the second refrigerant and the outside air. It is desirable that the outside air is forcibly sent to the condenser 5 by a fan (not shown). Accordingly, the gas-phase refrigerant is condensed in the condenser 5, and a high-pressure liquid-phase refrigerant is generated.
  • the high-pressure liquid-phase refrigerant passes through the high-temperature-side first expansion valve 61, the high-temperature-side receiver 82, and the high-temperature-side second expansion valve 62 in this order.
  • the high-pressure liquid-phase refrigerant is reduced in pressure to a certain extent while passing through the high-temperature-side first expansion valve 61, and becomes a medium-pressure and medium-temperature liquid-phase refrigerant.
  • This liquid-phase refrigerant is stored in the high-temperature-side receiver 82 and is separated into a gas and a liquid.
  • the gas phase component is supplied to the second compressor 4 (specifically, a position upstream of the scroll compressor 42 on the high pressure side) through a high-temperature-side circuit 92 as the gas injection circuit 9. That is, the low-temperature second refrigerant (gas phase component) before being compressed is sent to the second compressor 4 through the high-temperature-side circuit 92.
  • the medium-temperature and medium-pressure liquid-phase refrigerant that has passed through the high-temperature-side receiver 82 passes through the high-temperature-side second expansion valve 62 and is further reduced in pressure to become a low-temperature and low-pressure liquid-phase refrigerant.
  • the intermediate heat exchanger 10 heat exchange occurs between the second refrigerant in the high-temperature cycle CH and the first refrigerant in the low-temperature cycle, which will be described later.
  • heat exchange occurs between the high-temperature and high-pressure gas-phase refrigerant (first refrigerant) flowing through the low-temperature cycle CL and the low-temperature and low-pressure liquid-phase refrigerant (second refrigerant) flowing through the high-temperature cycle CH.
  • the liquid-phase refrigerant flowing through the intermediate heat exchanger 10 increases in temperature and changes from a liquid phase to a gas phase.
  • the refrigerant that has become the gas phase after passing through the intermediate heat exchanger 10 is suctioned into the second compressor 4 again.
  • the high-temperature cycle CH such a cycle is continuously performed.
  • the low-temperature cycle CL includes a low-temperature-side pipe P1, a first compressor 2, an evaporator 1, a low-temperature-side expansion valve 3 (a low-temperature-side first expansion valve 31 and a low-temperature-side second expansion valve 32), and a low-temperature-side receiver 81.
  • the low-temperature-side pipe P1 is a pipeline connected in an annular shape, and an inside thereof is filled with the first refrigerant.
  • the first refrigerant is a mixed refrigerant of carbon dioxide and an R32 refrigerant.
  • the R32 refrigerant is contained in the first refrigerant in a range of 16 wt% or more and 22 wt% or less. A component remaining therein is carbon dioxide.
  • the first compressor 2 On the low-temperature-side pipe P1, from an upstream side to a downstream side in a flow direction of the first refrigerant, the first compressor 2, the low-temperature-side first expansion valve 31, the low-temperature-side receiver 81, the low-temperature-side second expansion valve 32, and the evaporator 1 are arranged in this order.
  • the first compressor 2 compresses a low-pressure gas-phase refrigerant supplied from the evaporator 1 to generate a high-temperature and high-pressure gas-phase refrigerant. Similar to the second compressor 4, the first compressor 2 is a so-called scroll rotary type two-stage compressor, in which a rotary compressor 21 is used as a low pressure side and a scroll compressor 22 is used as a high pressure side. The rotary compressor 21 and the scroll compressor 22 are, as an exception, coaxially connected to each other.
  • the high-temperature and high-pressure gas-phase refrigerant generated by the first compressor 2 flows into the intermediate heat exchanger 10.
  • the intermediate heat exchanger 10 heat exchange occurs between the second refrigerant in the high-temperature cycle CH and the first refrigerant in the low-temperature cycle. Specifically, heat exchange occurs between the high-temperature and high-pressure gas-phase refrigerant (first refrigerant) flowing through the low-temperature cycle CL and the low-temperature and low-pressure liquid-phase refrigerant (second refrigerant) flowing through the high-temperature cycle CH. Accordingly, the gas-phase refrigerant is condensed in the intermediate heat exchanger 10, and a high-pressure liquid-phase refrigerant is generated.
  • the high-pressure liquid-phase refrigerant passes through the low-temperature-side first expansion valve 31, the low-temperature-side receiver 81, and the low-temperature-side second expansion valve 32 in this order.
  • the high-pressure liquid-phase refrigerant is reduced in pressure to a certain extent while passing through the low-temperature-side first expansion valve 31, and becomes a medium-pressure and medium-temperature liquid-phase refrigerant.
  • the liquid-phase refrigerant is stored in the low-temperature-side receiver 81 and is separated into a gas and a liquid.
  • the gas phase component is supplied to the first compressor 2 (specifically, a position upstream of the scroll compressor 22 on the high pressure side) through a low-temperature-side circuit 91 as the gas injection circuit 9. That is, the low-temperature first refrigerant (gas phase component) before being compressed is sent to the first compressor 2 through the low-temperature-side circuit 91.
  • the medium-temperature and medium-pressure liquid-phase refrigerant that has passed through the low-temperature-side receiver 81 passes through the low-temperature-side second expansion valve 32 and is further reduced in pressure to become a low-temperature and low-pressure liquid-phase refrigerant.
  • the evaporator 1 is provided inside the freezing chamber. In the evaporator 1, heat exchange occurs between an air in the freezing chamber and the first refrigerant. It is desirable that the air in the freezing chamber is forcibly sent to the evaporator 1 by a fan. Heat in the freezing chamber is absorbed by the low-temperature liquid-phase refrigerant, so that the temperature in the freezing chamber changes to descend. That is, the freezing chamber is cooled.
  • the liquid-phase refrigerant flowing through the evaporator 1 increases in temperature and changes from a liquid phase to a gas phase. The refrigerant that has become the gas phase after passing through the evaporator 1 is suctioned into the first compressor 2 again. By continuously performing such a cycle, the temperature of the freezing chamber is adjusted to a desired value.
  • the chiller 100 forms the cascade cycle mainly including the low-temperature cycle CL, the high-temperature cycle CH, and the intermediate heat exchanger 10 provided therebetween. Accordingly, compression ratios respectively required for the first compressor 2 and the second compressor 4 can be minimized. As a result, the temperature (discharge temperature) of the refrigerant discharged from these compressors can be further lowered. That is, a cooling capacity of the chiller 100 can be further increased.
  • cycle diagrams of the high-temperature cycle CH and the low-temperature cycle CL are superimposed on each other at intermediate positions (intermediate heat exchanger 10). Accordingly, the temperature of the refrigerant can be lowered to a lower temperature compared to a case where only the high-temperature cycle CH is used. For example, in a case where a condenser outlet temperature of the high-temperature cycle CH is 34°C, an evaporation temperature can be set to an ultra low temperature of about -68°C in the low-temperature cycle CL.
  • the cascade cycle it becomes possible to use different types of refrigerants in the low-temperature cycle CL and the high-temperature cycle CH.
  • the mixed refrigerant that contains R32 while mainly containing carbon dioxide is used as the first refrigerant.
  • carbon dioxide is used as the second refrigerant.
  • the high-temperature cycle CH since only carbon dioxide is used as the second refrigerant, an excess decrease in density does not occur compared to a case where R32 is mixed. Accordingly, the compression ratio required for the second compressor 4 can be minimized.
  • the gas injection circuit 9 supplies the low-temperature first refrigerant or second refrigerant before being compressed to at least one of the first compressor 2 and the second compressor 4. Accordingly, for example, in a case where the first compressor 2 and the second compressor 4 are configured by a plurality of stages of compressors, a final discharge temperature of the refrigerant can be further lowered by supplying the low-temperature refrigerant to an intermediate position between the plurality of stages.
  • the mixed refrigerant containing 16 wt% or more and 22 wt% or less of R32 and carbon dioxide is used. Accordingly, it becomes possible to suppress a GWP to 150 or less to be equal to or lower than an international regulation value. As described above, according to the present embodiment, it is possible to provide the chiller 100 capable of achieving both a low GWP and a high cooling capacity.
  • the gas injection circuit 9 is configured to supply the refrigerant to the upstream side of the scroll compressors 22 and 42 on the high pressure side.
  • the scroll compressors 22 and 42 a configuration is adopted in which the refrigerant flowing through an inside of a casing flows into a compression chamber without being significantly restricted in the flow direction or the like. That is, it can be said that in the scroll compressors 22 and 42, it is easier to add another refrigerant to an outside of the compression chamber than in the rotary compressors 21 and 41. Accordingly, the gas injection circuit 9 can more easily and smoothly add the refrigerant.
  • the low-temperature-side circuit 91 and the high-temperature-side circuit 92 as the gas injection circuit 9 are provided in the low-temperature cycle CL and the high-temperature cycle CH, respectively. Accordingly, it is possible to lower the discharge temperature of the compressors (the first compressor 2 and the second compressor 4) in both the low-temperature cycle CL and the high-temperature cycle CH.
  • the chiller described in each of the embodiments is identified, for example, as follows.
  • the chiller 100 forms a cascade cycle mainly including the low-temperature cycle CL, the high-temperature cycle CH, and the intermediate heat exchanger 10 provided therebetween. Accordingly, compression ratios respectively required for the first compressor 2 and the second compressor 4 can be minimized. As a result, a temperature (discharge temperature) of the refrigerant discharged from these compressors can be further lowered. That is, a cooling capacity of the chiller 100 can be further increased.
  • the cascade cycle it becomes possible to use different types of refrigerants in the low-temperature cycle CL and the high-temperature cycle CH.
  • the mixed refrigerant that contains R32 while mainly containing carbon dioxide is used as the first refrigerant.
  • carbon dioxide is used as the second refrigerant.
  • the high-temperature cycle CH since only carbon dioxide is used as the second refrigerant, an excess decrease in density does not occur compared to a case where R32 is mixed. Accordingly, the compression ratio required for the second compressor 4 can be minimized.
  • the gas injection circuit 9 supplies the low-temperature first refrigerant or second refrigerant before being compressed to at least one of the first compressor 2 and the second compressor 4. Accordingly, for example, in a case where the first compressor 2 and the second compressor 4 are configured by a plurality of stages of compressors, a final discharge temperature of the refrigerant can be further lowered by supplying the low-temperature refrigerant to an intermediate position between the plurality of stages.
  • the first refrigerant is a mixed refrigerant containing 16 wt% or more and 22 wt% or less of the R32 refrigerant.
  • the mixed refrigerant containing 16 wt% or more and 22 wt% or less of R32 and carbon dioxide is used. Accordingly, it becomes possible to suppress a GWP to 150 or less to be equal to or lower than an international regulation value.
  • the first compressor 2 and the second compressor 4 each include a rotary compressor 21, 41 on a low pressure side and a scroll compressor 22, 42 on a high pressure side connected to the rotary compressor 21, 41, and the gas injection circuit 9 is configured to supply the first refrigerant or the second refrigerant to an upstream side of the scroll compressor 22, 42.
  • the gas injection circuit 9 is configured to supply the refrigerant to the upstream side of the scroll compressor 22, 42 on the high pressure side.
  • the scroll compressor 22, 42 a configuration is adopted in which the refrigerant flowing through an inside of a casing flows into a compression chamber without being significantly restricted in a flow direction or the like. That is, it can be said that in the scroll compressor 22, 42, it is easier to add another refrigerant to an outside of the compression chamber than in the rotary compressor 21, 41. Accordingly, the gas injection circuit 9 can more easily and smoothly add the refrigerant.
  • the low-temperature-side expansion valve 3 and the high-temperature-side expansion valve 6 each have two expansion valves
  • the low-temperature cycle CL and the high-temperature cycle CH respectively further include a low-temperature-side receiver 81 and a high-temperature-side receiver 82 provided between the two expansion valves
  • the gas injection circuit 9 has a low-temperature-side circuit 91 that supplies the first refrigerant from the low-temperature-side receiver 81 to the first compressor 2, and a high-temperature-side circuit 92 that supplies the second refrigerant from the high-temperature-side receiver 82 to the second compressor 4.
  • the low-temperature-side circuit 91 and the high-temperature-side circuit 92 as the gas injection circuit 9 are provided in the low-temperature cycle CL and the high-temperature cycle CH, respectively. Accordingly, it is possible to lower the discharge temperature of the compressors (the first compressor 2 and the second compressor 4) in both the low-temperature cycle CL and the high-temperature cycle CH.
  • the present disclosure relates to a chiller. According to the present disclosure, it is possible to provide a chiller capable of achieving both a low GWP and a high cooling capacity.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP21875130.3A 2020-09-29 2021-09-09 Machine frigorifique Pending EP4198416A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020163122A JP7391811B2 (ja) 2020-09-29 2020-09-29 冷凍機械
PCT/JP2021/033176 WO2022070828A1 (fr) 2020-09-29 2021-09-09 Machine frigorifique

Publications (2)

Publication Number Publication Date
EP4198416A1 true EP4198416A1 (fr) 2023-06-21
EP4198416A4 EP4198416A4 (fr) 2024-01-10

Family

ID=80950385

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21875130.3A Pending EP4198416A4 (fr) 2020-09-29 2021-09-09 Machine frigorifique

Country Status (3)

Country Link
EP (1) EP4198416A4 (fr)
JP (1) JP7391811B2 (fr)
WO (1) WO2022070828A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117267971A (zh) * 2022-10-31 2023-12-22 付朝乾 一种两级压缩三级复叠型冷热双供热泵
JP2024088181A (ja) * 2022-12-20 2024-07-02 三菱重工業株式会社 冷凍装置

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4543469B2 (ja) 1999-12-27 2010-09-15 ダイキン工業株式会社 冷凍装置
KR20110056061A (ko) 2009-11-20 2011-05-26 엘지전자 주식회사 히트 펌프식 급탕장치
JP5645502B2 (ja) 2010-06-25 2014-12-24 三菱重工業株式会社 ヒートポンプ給湯装置
CN104813120B (zh) 2012-11-20 2016-08-17 三菱电机株式会社 冷冻装置
JP6594707B2 (ja) * 2015-08-27 2019-10-23 三菱重工サーマルシステムズ株式会社 ２段圧縮冷凍システム
WO2017221382A1 (fr) 2016-06-23 2017-12-28 三菱電機株式会社 Dispositif de réfrigération binaire
EP4019862B1 (fr) * 2017-06-23 2024-05-01 Daikin Industries, Ltd. Système de transport de chaleur
JP7193706B2 (ja) * 2018-10-02 2022-12-21 ダイキン工業株式会社 冷凍サイクル装置
JP7189423B2 (ja) * 2018-10-02 2022-12-14 ダイキン工業株式会社 冷凍サイクル装置
JP7078338B2 (ja) 2020-03-10 2022-05-31 株式会社大一商会 遊技機

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Publication number Publication date
WO2022070828A1 (fr) 2022-04-07
JP7391811B2 (ja) 2023-12-05
EP4198416A4 (fr) 2024-01-10
JP2022055607A (ja) 2022-04-08

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