WO2022070828A1 - Machine frigorifique - Google Patents

Machine frigorifique Download PDF

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Publication number
WO2022070828A1
WO2022070828A1 PCT/JP2021/033176 JP2021033176W WO2022070828A1 WO 2022070828 A1 WO2022070828 A1 WO 2022070828A1 JP 2021033176 W JP2021033176 W JP 2021033176W WO 2022070828 A1 WO2022070828 A1 WO 2022070828A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
low
high temperature
temperature side
Prior art date
Application number
PCT/JP2021/033176
Other languages
English (en)
Japanese (ja)
Inventor
悠輝 難波
隆英 伊藤
篤 塩谷
寿幸 石田
Original Assignee
三菱重工サーマルシステムズ株式会社
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 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Priority to EP21875130.3A priority Critical patent/EP4198416A4/fr
Publication of WO2022070828A1 publication Critical patent/WO2022070828A1/fr

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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

  • the present disclosure has been made to solve the above problems, and an object of the present disclosure is to provide a refrigerating machine capable of achieving both low GWP and high refrigerating capacity.
  • the refrigerating machine is an evaporator that exchanges heat between the air in the refrigerating chamber and the first refrigerant, and a first compressor that compresses and supplies the first refrigerant to the evaporator.
  • a low-temperature cycle having a low-temperature side expansion valve that lowers the pressure of the first refrigerant that has passed through the first compressor, a radiator that exchanges heat between the outside air and the second refrigerant, and the second refrigerant in the radiator.
  • a second compressor that compresses and supplies the The first refrigerant or the second refrigerant provided in at least one of the low temperature cycle and the high temperature cycle to exchange heat with the second refrigerant flowing from the high temperature side expansion valve, and before being compressed.
  • the first refrigerant includes a gas injection circuit for supplying a refrigerant to at least one of the first compressor and the second compressor, and the first refrigerant is a mixed refrigerant containing carbon dioxide and an R32 refrigerant.
  • the two refrigerants are carbon dioxide.
  • the refrigerating machine 100 includes a high temperature cycle CH, a low temperature cycle CL, an intermediate heat exchanger 10 connecting these high temperature cycle CH and a low temperature cycle CL, and a gas injection circuit 9. .. That is, the refrigerating machine 100 constitutes a cascade cycle type refrigerating circuit.
  • the refrigerant that has exchanged heat with the outside air in the high temperature cycle CH (second refrigerant described later) exchanges heat with another refrigerant (first refrigerant described later) on the low temperature cycle CL side in the intermediate heat exchanger 10.
  • heat exchange is performed between the indoor air and the refrigerant.
  • the high temperature cycle CH includes the high temperature side pipe P2, the second compressor 4, the radiator 5, the high temperature side expansion valve 6 (high temperature side first expansion valve 61, and the high temperature side second expansion valve 62), and the high temperature side. It has a receiver 82 and.
  • the high temperature side pipe P2 is a pipe line connected in an annular shape, and the inside thereof is filled with a second refrigerant.
  • the second refrigerant contains only carbon dioxide.
  • a second compressor 4 On the high temperature side pipe P2, from the upstream side to the downstream side in the flow direction of the second refrigerant, a second compressor 4, a radiator 5, a high temperature side first expansion valve 61, and a high temperature side receiver 82 are provided. , The second expansion valve 62 on the high temperature side are arranged in this order.
  • the second compressor 4 compresses the 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 type two-stage compressor, in which the rotary compressor 41 is used as the low pressure side and the scroll compressor 42 is used as the high pressure side.
  • the rotary compressor 41 and the scroll compressor 42 are, as an exception, coaxially connected.
  • the high temperature and high pressure gas phase refrigerant generated by the second compressor 4 flows into the radiator 5.
  • the radiator 5 is provided outside the freezing room (room to be frozen). In the radiator 5, heat exchange is performed between the second refrigerant and the external air. It is desirable that outside air is forcibly sent to the radiator 5 by a fan (not shown). As a result, the gas phase refrigerant is condensed in the radiator 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 pressure of the high-pressure liquid-phase refrigerant drops to a certain extent by passing through the high-temperature side first expansion valve 61, and becomes a medium-pressure medium-temperature liquid-phase refrigerant.
  • This liquid phase refrigerant is stored in the high temperature side receiver 82 and separated into gas and liquid.
  • the gas phase component is supplied to the second compressor 4 (specifically, the position on the upstream side of the scroll compressor 42 on the high pressure side) through the 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 further drops in pressure by passing through the high-temperature side second expansion valve 62, and becomes a low-temperature low-pressure liquid-phase refrigerant.
  • heat exchange is performed between the second refrigerant in the high temperature cycle CH and the first refrigerant in the low temperature cycle described later. Specifically, heat exchange is performed 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. ..
  • first refrigerant high temperature and high pressure gas phase refrigerant
  • second refrigerant liquid phase refrigerant
  • 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 (low temperature side first expansion valve 31 and a low temperature side second expansion valve 32), and a low temperature side. It has a receiver 81 and.
  • the low temperature side pipe P1 is a pipe line connected in an annular shape, and the inside thereof is filled with the first refrigerant.
  • the first refrigerant is a mixed refrigerant of carbon dioxide and R32 refrigerant.
  • the R32 refrigerant is contained in the first refrigerant in the range of 16% by weight or more and 22% by weight or less.
  • the remaining component is carbon dioxide.
  • the first compressor 2 On the low temperature side pipe P1, from the upstream side to the downstream side in the flow direction of the first refrigerant, the first compressor 2, the low temperature side first expansion valve 31, the low temperature side receiver 81, and the low temperature side second The expansion valve 32 and the evaporator 1 are arranged in this order.
  • the first compressor 2 compresses the low-pressure gas-phase refrigerant supplied from the evaporator 1 to generate a high-temperature and high-pressure gas-phase refrigerant.
  • the first compressor 2 is a so-called scroll type two-stage compressor, in which the rotary compressor 21 is used as the low pressure side and the scroll compressor 22 is used as the high pressure side. ing.
  • the rotary compressor 41 and the scroll compressor 42 are, as an exception, coaxially connected.
  • the high temperature and high pressure gas phase refrigerant generated by the first compressor 2 flows into the intermediate heat exchanger 10.
  • heat exchange is performed between the second refrigerant in the high temperature cycle CH and the first refrigerant in the low temperature cycle.
  • heat exchange is performed 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 gas phase refrigerant is condensed in the intermediate heat exchanger 10 to generate a high pressure liquid phase refrigerant.
  • 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 passes through the low-temperature side first expansion valve 31 to reduce the pressure to a certain extent, and becomes a medium-pressure medium-temperature liquid-phase refrigerant.
  • This liquid phase refrigerant is stored in the low temperature side receiver 81 and separated into gas and liquid.
  • the gas phase component is supplied to the first compressor 2 (specifically, the position on the upstream side of the scroll compressor 22 on the high pressure side) through the low temperature side circuit 91 as the gas injection circuit 9. That is, the low-temperature first refrigerant (gas phase component) before compression 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 further drops in pressure by passing through the low-temperature side second expansion valve 32, and becomes a low-temperature and low-pressure liquid-phase refrigerant.
  • the evaporator 1 is provided inside the freezing chamber. In the evaporator 1, heat exchange is performed between the air in the freezing chamber and the first refrigerant. It is desirable to forcibly send the air in the freezing chamber to the evaporator 1 by a fan.
  • the heat in the freezing chamber is absorbed by the low-temperature liquid-phase refrigerant, and the temperature in the freezing chamber changes in the direction of lowering. That is, the freezing chamber is cooled.
  • the temperature of the liquid phase refrigerant flowing through the evaporator 1 rises, and at the same time, the temperature changes from the liquid phase to the gas phase.
  • the refrigerant that has passed through the evaporator 1 and becomes a gas phase is sucked into the first compressor 2 again. By performing such a cycle continuously, the temperature of the freezing chamber is adjusted to a desired value.
  • the refrigerating machine 100 constitutes a cascade cycle mainly including a low temperature cycle CL, a high temperature cycle CH, and an intermediate heat exchanger 10 provided between them.
  • the compression ratios required by the first compressor 2 and the second compressor 4 can be kept small.
  • the temperature (discharge temperature) of the refrigerant discharged from these compressors can be further lowered. That is, the refrigerating capacity of the refrigerating machine 100 can be further increased.
  • the cycle diagrams of the high temperature cycle CH and the low temperature cycle CL are superimposed on each other at an intermediate position (intermediate heat exchanger 10).
  • the temperature of the refrigerant can be lowered to a lower temperature as compared with the case where only the high temperature cycle CH is used.
  • the radiator outlet temperature of the high temperature cycle CH is 34 ° C.
  • the evaporation temperature can be set to an ultralow 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.
  • a mixed refrigerant containing R32 is used as the first refrigerant while containing carbon dioxide as the main component.
  • Carbon dioxide is used as the second refrigerant in the high temperature cycle CH.
  • the high temperature cycle CH since only carbon dioxide is used as the second refrigerant, the density does not become excessively low as compared with the case where R32 is mixed. As a result, the compression ratio required by the second compressor 4 can be kept small.
  • the gas injection circuit 9 supplies at least one of the first compressor 2 and the second compressor 4 with a low-temperature first refrigerant or a second refrigerant before being compressed.
  • the low-temperature refrigerant is supplied to an intermediate position between the plurality of stages to finally discharge the refrigerant. It is possible to further lower the temperature.
  • the first refrigerant a mixed refrigerant with carbon dioxide containing R32 of 16% by weight or more and 22% by weight or less is used. This makes it possible to keep the GWP below 150 and below the international regulation value. As described above, according to the present embodiment, it is possible to provide the refrigerating machine 100 capable of achieving both low GWP and high refrigerating 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 inside the casing flows into the compression chamber without being severely restricted by the flow direction or the like. That is, it can be said that it is easier to add another refrigerant to the outside of the compression chamber in the scroll compressors 22 and 42 as compared with the rotary compressors 21 and 41. This makes it possible to add the refrigerant more easily and smoothly by the gas injection circuit 9.
  • the low temperature cycle CL and the high temperature cycle CH are provided with the low temperature side circuit 91 and the high temperature side circuit 92 as the gas injection circuit 9, respectively. This makes it possible to lower the discharge temperature of the compressors (first compressor 2 and second compressor 4) in both the low temperature cycle CL and the high temperature cycle CH.
  • the refrigerating machine 100 is an evaporator 1 that exchanges heat between the air in the refrigerating chamber and the first refrigerant, and a first compressor that compresses and supplies the first refrigerant to the evaporator 1.
  • a low-temperature cycle CL having a low-temperature side expansion valve 3 that lowers the pressure of the first refrigerant that has passed through the first compressor 2, a radiator 5 that exchanges heat between the outside air and the second refrigerant, and the radiator.
  • a second compressor 4 that compresses and supplies the second refrigerant to 5, a high temperature cycle CH having a high temperature side expansion valve 6 that lowers the pressure of the second refrigerant that has passed through the radiator 5, and the first compression.
  • the refrigerant is a mixed refrigerant containing carbon dioxide and an R32 refrigerant
  • the second refrigerant is carbon dioxide.
  • the refrigerating machine 100 constitutes a cascade cycle mainly including a low temperature cycle CL, a high temperature cycle CH, and an intermediate heat exchanger 10 provided between them.
  • the compression ratios required by the first compressor 2 and the second compressor 4 can be kept small.
  • the temperature (discharge temperature) of the refrigerant discharged from these compressors can be further lowered. That is, the refrigerating capacity of the refrigerating machine 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.
  • a mixed refrigerant containing R32 is used as the first refrigerant while containing carbon dioxide as the main component.
  • Carbon dioxide is used as the second refrigerant in the high temperature cycle CH.
  • the gas injection circuit 9 supplies at least one of the first compressor 2 and the second compressor 4 with a low-temperature first refrigerant or a second refrigerant before being compressed.
  • the low-temperature refrigerant is supplied to an intermediate position between the plurality of stages to finally discharge the refrigerant. It is possible to further lower the temperature.
  • the first refrigerant is a mixed refrigerant containing 16% by weight or more and 22% by weight or less of R32 refrigerant.
  • the first refrigerant a mixed refrigerant with carbon dioxide containing R32 of 16% by weight or more and 22% by weight or less is used. This makes it possible to keep the GWP below 150 and below the international regulation value.
  • the first compressor 2 and the second compressor 4 are attached to the rotary compressors 21 and 41 on the low pressure side and the rotary compressors 21 and 41, respectively.
  • the gas injection circuit 9 includes the connected high-pressure side scroll compressors 22 and 42, and is configured to supply the first refrigerant or the second refrigerant to the upstream side of the scroll compressors 22 and 42. ing.
  • 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 inside the casing flows into the compression chamber without being severely restricted by the flow direction or the like. That is, it can be said that it is easier to add another refrigerant to the outside of the compression chamber in the scroll compressors 22 and 42 as compared with the rotary compressors 21 and 41. This makes it possible to add the refrigerant more easily and smoothly by the gas injection circuit 9.
  • 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.
  • the CH further includes a low temperature side receiver 81 and a high temperature side receiver 82 respectively provided between the two expansion valves, and the gas injection circuit 9 uses the low temperature side receiver 81 to supply the first refrigerant. It has a low temperature side circuit 91 that supplies the 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 cycle CL and the high temperature cycle CH are provided with the low temperature side circuit 91 and the high temperature side circuit 92 as the gas injection circuit 9, respectively. This makes it possible to lower the discharge temperature of the compressors (first compressor 2 and second compressor 4) in both the low temperature cycle CL and the high temperature cycle CH.
  • This disclosure relates to refrigeration machinery. According to the present disclosure, it is possible to provide a refrigerating machine capable of achieving both low GWP and high refrigerating capacity.
  • Refrigerating machine 1 Evaporator 2 First compressor 3 Low temperature side expansion valve 4 Second compressor 5 Radiator 6 High temperature side expansion valve 9 Gas injection circuit 10 Intermediate heat exchanger 21
  • Rotary compressor 22 Scroll compressor 31 Low temperature side first One expansion valve 32 Low temperature side second expansion valve 41
  • Rotary compressor 42 Scroll compressor 61 High temperature side first expansion valve 62 High temperature side second expansion valve 81 Low temperature side receiver 82 High temperature side receiver 91 Low temperature side circuit 92 High temperature side circuit CH High temperature side circuit CH Cycle CL Low temperature cycle P1 Low temperature side piping P2 High temperature side piping

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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)

Abstract

L'invention concerne une machine frigorifique qui comprend : un cycle à basse température ayant un évaporateur qui effectue un échange de chaleur entre l'air à l'intérieur d'une chambre de réfrigération et un premier fluide frigorigène, un premier compresseur qui comprime le premier fluide frigorigène et fournit le premier fluide frigorigène comprimé à l'évaporateur, et un détendeur côté basse température qui abaisse la pression du premier fluide frigorigène qui a traversé le premier compresseur ; un cycle à haute température ayant un dissipateur de chaleur qui effectue un échange de chaleur entre l'air extérieur et un second fluide frigorigène, un second compresseur qui comprime un second fluide frigorigène et fournit le second fluide frigorigène comprimé au dissipateur de chaleur, et un détendeur côté haute température qui abaisse la pression du second fluide frigorigène qui a traversé le dissipateur thermique ; un échangeur de chaleur intermédiaire qui effectue un échange de chaleur entre le premier fluide frigorigène s'écoulant à partir du premier compresseur et le second fluide frigorigène s'écoulant à partir du détendeur côté haute température ; et un circuit d'injection de gaz qui est fourni à au moins l'un parmi le cycle à basse température et le cycle à haute température, et qui fournit le fluide frigorigène avant compression à au moins l'un du premier compresseur et du second compresseur, le premier fluide frigorigène étant un fluide frigorigène mélangé contenant du dioxyde de carbone et du fluide frigorigène R32, et le second fluide frigorigène étant du dioxyde de carbone.
PCT/JP2021/033176 2020-09-29 2021-09-09 Machine frigorifique WO2022070828A1 (fr)

Priority Applications (1)

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

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020163122A JP7391811B2 (ja) 2020-09-29 2020-09-29 冷凍機械
JP2020-163122 2020-09-29

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WO2022070828A1 true WO2022070828A1 (fr) 2022-04-07

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

Citations (7)

* 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
US20110120179A1 (en) * 2009-11-20 2011-05-26 Sim Won Chin Heat pump type cooling/heating apparatus
JP2012007825A (ja) * 2010-06-25 2012-01-12 Mitsubishi Heavy Ind Ltd ヒートポンプ給湯装置
WO2014080436A1 (fr) * 2012-11-20 2014-05-30 三菱電機株式会社 Dispositif de réfrigération
JP2017044420A (ja) * 2015-08-27 2017-03-02 三菱重工業株式会社 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
JP2020163122A (ja) 2020-03-10 2020-10-08 株式会社大一商会 遊技機

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11293670B2 (en) * 2017-06-23 2022-04-05 Daikin Industries, Ltd. Chiller with an outdoor unit transferring heat to an indoor unit using carbon dioxide
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
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

Patent Citations (7)

* 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
US20110120179A1 (en) * 2009-11-20 2011-05-26 Sim Won Chin Heat pump type cooling/heating apparatus
JP2012007825A (ja) * 2010-06-25 2012-01-12 Mitsubishi Heavy Ind Ltd ヒートポンプ給湯装置
WO2014080436A1 (fr) * 2012-11-20 2014-05-30 三菱電機株式会社 Dispositif de réfrigération
JP2017044420A (ja) * 2015-08-27 2017-03-02 三菱重工業株式会社 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
JP2020163122A (ja) 2020-03-10 2020-10-08 株式会社大一商会 遊技機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4198416A4

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Publication number Publication date
JP2022055607A (ja) 2022-04-08
JP7391811B2 (ja) 2023-12-05
EP4198416A1 (fr) 2023-06-21
EP4198416A4 (fr) 2024-01-10

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