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WO1999008053A1 - Cycle de refroidissement - Google Patents

Cycle de refroidissement Download PDF

Info

Publication number
WO1999008053A1
WO1999008053A1 PCT/JP1998/003555 JP9803555W WO9908053A1 WO 1999008053 A1 WO1999008053 A1 WO 1999008053A1 JP 9803555 W JP9803555 W JP 9803555W WO 9908053 A1 WO9908053 A1 WO 9908053A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
tank
cooling
pressure
main path
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.)
Ceased
Application number
PCT/JP1998/003555
Other languages
English (en)
Japanese (ja)
Inventor
Nobuhiko Suzuki
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.)
Bosch Corp
Original Assignee
Zexel Corp
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 Zexel Corp filed Critical Zexel Corp
Publication of WO1999008053A1 publication Critical patent/WO1999008053A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0415—Refrigeration circuit bypassing means for the receiver
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B2600/00—Control issues
    • F25B2600/05—Refrigerant levels
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters

Definitions

  • the present invention relates to a cooling cycle using a supercritical fluid, and more particularly to a cooling cycle including a refrigerant tank for adjusting a refrigerant amount in a cycle in a bypass path bypassing an expansion valve.
  • a compressor 2 for increasing the pressure of the refrigerant
  • a radiator 3 for cooling the refrigerant
  • a countercurrent heat for exchanging heat between the refrigerant flowing through the high-pressure line and the low-pressure line.
  • It has a main path 7 having an exchanger 4, an expansion valve 5 for reducing the pressure of the refrigerant, and an evaporator 6 for evaporating and vaporizing the refrigerant.
  • the supercritical refrigerant pressurized by the compressor 2 is cooled by the radiator 3, and further cooled by the countercurrent heat exchanger 4 before entering the expansion valve 5.
  • a main route 7 is also described in the same gazette on page 4, lines 39-44, and on page 5, lines 38-48.
  • a bypass path 9 for bypassing the expansion valve 5 is further provided, and a refrigerant tank 10 and valves 11 and 11 disposed on a high pressure side and a low pressure side with respect to the refrigerant tank 10 in the bypass path 9 are provided.
  • valve 11 In order to increase the amount of refrigerant in the main path 7, the valve 11 is closed and the valve 12 is opened to supply the refrigerant in the refrigerant tank to the main path ⁇ .
  • the valve 11 When the amount of refrigerant in the main path 7 is to be reduced, the valve 11 is opened and the valve 12 is closed, and the refrigerant in the main path 7 is collected in the refrigerant tank 10.
  • the refrigerant can be collected in the refrigerant tank 10 if the pressure in the refrigerant tank is lower than the pressure in the high-pressure side line at the time of collection. If the pressure is higher than or equal to, the refrigerant does not move from the main path 7 into the tank, and the refrigerant in the main path cannot be recovered.
  • a refrigerant in the main path is used.
  • the objective is to increase the range of adjustment of the amount of refrigerant in the main route, since it is possible to sufficiently collect the refrigerant.
  • Another issue is to reduce the required volume of the refrigerant tank by increasing the efficiency of accumulating the amount of refrigerant in the refrigerant tank. Disclosure of the invention
  • a cooling cycle according to the present invention uses a supercritical fluid as a refrigerant, a compressor that pressurizes the refrigerant, a radiator that cools the refrigerant pressurized by the compressor, and a radiator that A main path is formed by sequentially connecting pipes so as to include a pressure reducing means which is disposed downstream of the refrigerant and decompresses the cooled refrigerant, and an evaporator which heats the refrigerant depressurized by the pressure reducing means.
  • a bypass path that bypasses the expansion valve in the main path; a refrigerant tank that stores refrigerant in the bypass path; and a control valve that adjusts a passage cross-section on a refrigerant upstream side and a refrigerant downstream side of the refrigerant tank.
  • a cooling means for cooling the refrigerant in the refrigerant tank is provided.
  • the supercritical fluid fluids such as C02 and ethylene whose critical temperature is around room temperature are used. Even when the control valve is an on-off valve that switches the bypass path to closed or closed, the cross section of the passage is continuous. May be a variable valve.
  • a cooling device independent of the main path may be separately attached to the tank to adjust the cooling capacity. May be configured to cool the refrigerant. Further, the refrigerant in the refrigerant tank may be constantly cooled or may be cooled only when necessary.
  • the cycle configuration of the main path includes at least a compressor, a radiator, a pressure reducing means, and an evaporator.
  • the cycle between the radiator and the expansion valve is required.
  • a configuration in which a heat exchanger for exchanging heat between the refrigerant in the high-pressure side line and the refrigerant in the low-pressure side line is provided, or a configuration in which an accumulator is provided downstream of the refrigerant in the evaporator is included.
  • the high-temperature and high-pressure refrigerant which is pressurized by the compressor and is brought into a supercritical state is cooled by the radiator and then decompressed.
  • the pressure is reduced by the stage to become low-temperature, low-pressure wet steam, which is sent to the compressor after being evaporated and vaporized by the evaporator and pressurized again.
  • the amount of the refrigerant flowing in the main path is adjusted by controlling the control valve of the bypass path to discharge the refrigerant in the refrigerant tank to the main path, or to recover the refrigerant from the main path.
  • the refrigerant flowing into the tank from the main path during recovery is cooled by the cooling means and changes from a supercritical state to a subcritical state (liquid phase state). Therefore, it is possible to always keep the pressure lower than that required, and it is possible to reliably recover the required amount of refrigerant from the main path.
  • FIG. 1 is a diagram showing a configuration example of a cooling cycle according to the present invention.
  • FIG. 2 is a diagram showing a Mollier diagram of the cooling cycle shown in FIG. 1 together with a Mollier diagram of a conventional cycle.
  • FIG. 3 is a diagram showing a configuration of a conventional cooling cycle.
  • the cooling cycle 1 includes a compressor 2 for compressing the refrigerant, a radiator 3 for cooling the refrigerant, a countercurrent heat exchanger 4 for exchanging heat between the high-pressure side line and the low-pressure side line 4, and a refrigerant.
  • the main path 7 includes an expansion valve 5 for reducing pressure and an evaporator 6 for evaporating and evaporating a refrigerant.
  • the main path 7 connects the discharge side of the compressor 2 to the high-pressure passage 4 a of the countercurrent heat exchanger 4 via the radiator 3, and connects the outlet side of the high-pressure passage 4 a to the expansion valve 5.
  • the path from the compressor 2 to the high pressure side of the expansion valve 5 is defined as a high pressure side line 7a.
  • the low-pressure side of the expansion valve 5 is connected to an evaporator 6 via a cooling device 8 to be described later. It is connected to the low pressure passage 4 b of the container 4.
  • the outflow side of the low-pressure passage 4b is connected to the suction side of the compressor 2, and the path from the low-pressure side of the expansion valve 5 to the compressor 2 is a low-pressure line 7b.
  • C 0 2 is used as a refrigerant, and the refrigerant compressed by the compressor 2 enters the radiator 3 as a high-temperature and high-pressure supercritical refrigerant, where heat is radiated and cooled. . Thereafter, the heat is exchanged with the low-temperature refrigerant in the low-pressure side line 7 b in the counter-current heat exchanger 4 to be further cooled and sent to the expansion valve 5 without being liquefied. Then, the pressure is reduced by the expansion valve 5 to become low-temperature and low-pressure wet steam, and heat exchange with the air passing therethrough in the evaporator 6 to become gaseous, and thereafter, the high-pressure side line 7 in the countercurrent heat exchanger 4. It is heated by exchanging heat with the high-temperature refrigerant of a and returned to the compressor 2.
  • the bypass path 9 that bypasses the expansion valve 5 includes a refrigerant tank 10 for storing refrigerant and a passage on the high pressure side (between the refrigerant tank 10 and the high pressure side line 7 a) than the refrigerant tank 10.
  • a first on-off valve 11 for opening and closing the valve
  • a second on-off valve 12 for opening and closing the passage on the low pressure side (between the refrigerant tank 10 and the low pressure side line 7b).
  • a cooling device 8 that cools the coolant in the coolant tank 10 is provided between the expansion valve 5 and the evaporator 6 in the main path 7.
  • the cooling device 8 is formed on a low-pressure pipe extending from the expansion valve 5.
  • a low-pressure pipe is wound around the refrigerant tank 10, or the low-pressure pipe and the side of the refrigerant tank 10 are brought into contact with each other.
  • the refrigerant tank 10 may be constituted by a double pipe composed of an inner cylinder that stores the refrigerant and an outer cylinder that forms a passage around which the refrigerant flows.
  • the refrigerant in the refrigerant tank may be constantly cooled by the low-temperature refrigerant after passing through the expansion valve 5. It is supposed to.
  • the supercritical high-temperature and high-pressure refrigerant compressed by the compressor 2 indicated by the point A is cooled to the point B by the radiator 3, and It is further cooled to point C by the flow type heat exchanger 4. Then, the pressure is reduced by the expansion valve 5 to become a low-temperature and low-pressure wet steam indicated by a point D. Thereafter, the heat is exchanged with the refrigerant in the refrigerant tank 10 by the cooling device 8, and the evaporator 6 evaporates and reaches the point E. . The refrigerant that has passed through the evaporator 6 is further heated to the point F by the countercurrent heat exchanger 4, and then compressed again by the compressor 2 to return to the point A.
  • the cooling capacity will be reduced according to the heat load. If it is necessary to reduce the pressure, or if there is a request to reduce the high-pressure side pressure and operate at the maximum COP, the first on-off valve 11 is closed, the second on-off valve 12 is closed, and the refrigerant tank 1 is closed. Only the high pressure side of 0 is opened, and the refrigerant in the main path 7 is collected in the refrigerant tank 10. As a result, the pressure in the high pressure side line 7a decreases, and the cooling capacity decreases.
  • the pressure in the refrigerant tank 10 may be the same as that of the high-pressure side line 7a. No movement of the refrigerant to the refrigerant tank 10 occurs. Immediately after opening the first on-off valve 11, even if there is a pressure difference between the inside of the refrigerant tank and the high-pressure side line 7a, the pressure equilibrates after a while, and the high-pressure side line 7a In some cases, the refrigerant cannot be sufficiently recovered because the pressure drop P1 cannot be sufficiently large, and the refrigeration effect cannot be sufficiently reduced. In FIG. 2, this state is represented as a state change of A " ⁇ B" ⁇ C " ⁇ D" ⁇ ⁇ "indicated by a chain line.
  • the refrigerant tank 10 is constantly cooled, the refrigerant in the tank is changed to liquid-phase refrigerant and accumulated, and the pressure in the refrigerant tank 10 is changed to the high-pressure side line 7 a Lower pressure is always maintained. For this reason, the amount of refrigerant recovered from the main path 7 to the refrigerant tank 10 can be increased, and the pressure fluctuation P2 of the high-pressure side line 7a can be made larger than P1, so that the refrigeration effect can be reduced. It can be reduced sufficiently. If this state is indicated by a broken line on the Moliere diagram, as shown in FIG.
  • the adjustment range of the cooling capacity (Q to Q ′), that is, the adjustment range of the refrigerant amount can be made larger than the conventional adjustment range (Q to Q ′′). Since they can be stored in a phased state, the required volume of the tank itself can be made smaller than that of the conventional one.
  • cooling device 8 should be provided as a separate cycle independent of the main path 7. Is also good. Industrial applicability
  • the present invention in a configuration in which a refrigerant tank and control valves are provided on the outlet side and the inlet side thereof on the path bypassing the expansion valve of the main path to adjust the amount of refrigerant in the main path, Cools the refrigerant in the refrigerant tank and changes the refrigerant flowing from the main path into the refrigerant tank from the supercritical state to the subcritical state, so that the refrigerant tank is always kept at a lower pressure than the high-pressure line when recovering the refrigerant.
  • the required volume is made smaller than that of the conventional refrigerant tank without requiring the same tank volume as the conventional one.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

L'invention concerne un cycle de refroidissement utilisant un fluide supercritique en tant que réfrigérant capable de réguler la quantité du réfrigérant sur une large plage, et adapté pour réduire une capacité requise d'un réservoir de réfrigérant destiné à augmenter et diminuer la quantité du réfrigérant, dans lequel un chemin principal (7) est formé par raccordement d'un compresseur (2), d'un radiateur (3), d'une soupape de détente (5) et d'un évaporateur (6) en série, et un chemin de dérivation (9) est prévu dans le chemin principal (7) de manière à contourner la soupape de détente (5) et est doté d'un réservoir de réfrigérant (10) destiné à stocker le réfrigérant, ainsi que des soupapes de marche-arrêt (11, 12) destinées à fermer l'entrée et la sortie du réservoir du réfrigérant (10). Le réfrigérant se trouvant dans ledit réservoir de réfrigérant est refroidi avec le réfrigérant circulant dans le chemin principal (7) et lequel vient de passer à travers la soupape de détente afin de maintenir la température dans le réservoir de réfrigérant (10) inférieure à celle du conduit latéral à haute pression (7a), de manière à pouvoir récupérer la quantité requise de réfrigérant.
PCT/JP1998/003555 1997-08-12 1998-08-11 Cycle de refroidissement Ceased WO1999008053A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP23043597A JPH1163686A (ja) 1997-08-12 1997-08-12 冷却サイクル
JP9/230435 1997-08-12

Publications (1)

Publication Number Publication Date
WO1999008053A1 true WO1999008053A1 (fr) 1999-02-18

Family

ID=16907865

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1998/003555 Ceased WO1999008053A1 (fr) 1997-08-12 1998-08-11 Cycle de refroidissement

Country Status (2)

Country Link
JP (1) JPH1163686A (fr)
WO (1) WO1999008053A1 (fr)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1059495A3 (fr) * 1999-06-08 2002-01-02 Mitsubishi Heavy Industries, Ltd. Cycle de compression à vapeur surcritique
US6385980B1 (en) 2000-11-15 2002-05-14 Carrier Corporation High pressure regulation in economized vapor compression cycles
US6418735B1 (en) 2000-11-15 2002-07-16 Carrier Corporation High pressure regulation in transcritical vapor compression cycles
EP1207360A3 (fr) * 2000-11-15 2002-08-28 Carrier Corporation Echangeur de chaleur avec conduite d'aspiration et réservoir de stockage pour cycle de compression à vapeur surcritique
WO2004010060A1 (fr) * 2002-07-23 2004-01-29 Daikin Industries, Ltd. Cycle de refrigeration
US6739141B1 (en) 2003-02-12 2004-05-25 Carrier Corporation Supercritical pressure regulation of vapor compression system by use of gas cooler fluid pumping device
EP1467158A3 (fr) * 2003-04-09 2004-12-01 Hitachi, Ltd. Appareil a cycle de réfrigération
FR2869098A1 (fr) * 2003-12-23 2005-10-21 Tecumseh Products Co
US7424807B2 (en) 2003-06-11 2008-09-16 Carrier Corporation Supercritical pressure regulation of economized refrigeration system by use of an interstage accumulator
EP2233860A4 (fr) * 2007-12-07 2013-12-25 Mitsubishi Heavy Ind Ltd Circuit de fluide frigorigène
US10041713B1 (en) 1999-08-20 2018-08-07 Hudson Technologies, Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
DE102007043162B4 (de) * 2006-09-14 2021-02-25 Konvekta Ag Klimaanlage mit automatischer Kältemittelverlagerung
JPWO2021111605A1 (fr) * 2019-12-05 2021-06-10
CN116018486A (zh) * 2021-08-24 2023-04-25 株式会社日本伊藤美珂 热泵装置

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3714305B2 (ja) * 2002-07-11 2005-11-09 ダイキン工業株式会社 冷凍装置及び冷凍装置の冷媒充填方法
DE60335110D1 (de) * 2002-08-02 2011-01-05 Daikin Ind Ltd Kühleinrichtung
WO2004025199A1 (fr) * 2002-09-10 2004-03-25 Tokyo Electron Limited Dispositif de traitement et procede de maintenance pour ce dernier
JP5324749B2 (ja) 2006-09-11 2013-10-23 ダイキン工業株式会社 冷凍装置
JP5223550B2 (ja) * 2008-09-09 2013-06-26 富士電機株式会社 自動販売機
SG11202104998WA (en) 2019-02-25 2021-09-29 Ats Japan Co Ltd Refrigerant control system and cooling system

Citations (3)

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Publication number Priority date Publication date Assignee Title
JPS555893Y2 (fr) * 1974-09-05 1980-02-09
JPH01193561A (ja) * 1988-01-28 1989-08-03 Ebara Res Co Ltd ヒートポンプ
JPH03503206A (ja) * 1989-01-09 1991-07-18 シンヴェント・アクシェセルスカープ 超臨界蒸気圧縮サイクルの運転方法およびその装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS555893Y2 (fr) * 1974-09-05 1980-02-09
JPH01193561A (ja) * 1988-01-28 1989-08-03 Ebara Res Co Ltd ヒートポンプ
JPH03503206A (ja) * 1989-01-09 1991-07-18 シンヴェント・アクシェセルスカープ 超臨界蒸気圧縮サイクルの運転方法およびその装置

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1059495A3 (fr) * 1999-06-08 2002-01-02 Mitsubishi Heavy Industries, Ltd. Cycle de compression à vapeur surcritique
US10041713B1 (en) 1999-08-20 2018-08-07 Hudson Technologies, Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
US6385980B1 (en) 2000-11-15 2002-05-14 Carrier Corporation High pressure regulation in economized vapor compression cycles
US6418735B1 (en) 2000-11-15 2002-07-16 Carrier Corporation High pressure regulation in transcritical vapor compression cycles
EP1207360A3 (fr) * 2000-11-15 2002-08-28 Carrier Corporation Echangeur de chaleur avec conduite d'aspiration et réservoir de stockage pour cycle de compression à vapeur surcritique
US6606867B1 (en) 2000-11-15 2003-08-19 Carrier Corporation Suction line heat exchanger storage tank for transcritical cycles
WO2004010060A1 (fr) * 2002-07-23 2004-01-29 Daikin Industries, Ltd. Cycle de refrigeration
US6739141B1 (en) 2003-02-12 2004-05-25 Carrier Corporation Supercritical pressure regulation of vapor compression system by use of gas cooler fluid pumping device
EP1467158A3 (fr) * 2003-04-09 2004-12-01 Hitachi, Ltd. Appareil a cycle de réfrigération
US7424807B2 (en) 2003-06-11 2008-09-16 Carrier Corporation Supercritical pressure regulation of economized refrigeration system by use of an interstage accumulator
FR2869098A1 (fr) * 2003-12-23 2005-10-21 Tecumseh Products Co
DE102007043162B4 (de) * 2006-09-14 2021-02-25 Konvekta Ag Klimaanlage mit automatischer Kältemittelverlagerung
EP2233860A4 (fr) * 2007-12-07 2013-12-25 Mitsubishi Heavy Ind Ltd Circuit de fluide frigorigène
JPWO2021111605A1 (fr) * 2019-12-05 2021-06-10
WO2021111605A1 (fr) * 2019-12-05 2021-06-10 三菱電機株式会社 Dispositif à cycle frigorifique
CN114746704A (zh) * 2019-12-05 2022-07-12 三菱电机株式会社 制冷循环装置
JP7386894B2 (ja) 2019-12-05 2023-11-27 三菱電機株式会社 冷凍サイクル装置
CN114746704B (zh) * 2019-12-05 2024-04-30 三菱电机株式会社 制冷循环装置
CN116018486A (zh) * 2021-08-24 2023-04-25 株式会社日本伊藤美珂 热泵装置
CN116018486B (zh) * 2021-08-24 2024-01-26 株式会社日本伊藤美珂 热泵装置及其控制方法

Also Published As

Publication number Publication date
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