EP1293735B1 - Circuit de réfrigérant - Google Patents

Circuit de réfrigérant Download PDF

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Publication number
EP1293735B1
EP1293735B1 EP02020405A EP02020405A EP1293735B1 EP 1293735 B1 EP1293735 B1 EP 1293735B1 EP 02020405 A EP02020405 A EP 02020405A EP 02020405 A EP02020405 A EP 02020405A EP 1293735 B1 EP1293735 B1 EP 1293735B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
bypass pipe
amount control
control tank
heat exchanger
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.)
Expired - Lifetime
Application number
EP02020405A
Other languages
German (de)
English (en)
Other versions
EP1293735A2 (fr
EP1293735A3 (fr
Inventor
Kunio Sugiyama
Yoichi Yamada
Shigeo Zuiki
Yoshiki Nagasaki
Yoshihiro Sumida
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 Electric Corp
Original Assignee
Mitsubishi Electric 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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP1293735A2 publication Critical patent/EP1293735A2/fr
Publication of EP1293735A3 publication Critical patent/EP1293735A3/fr
Application granted granted Critical
Publication of EP1293735B1 publication Critical patent/EP1293735B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • 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
    • F25B2400/16—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
    • F25B45/00—Arrangements for charging or discharging refrigerant

Definitions

  • the invention relates to control of the amount of refrigerant flowing in a refrigeration cycle using a mixed refrigerant.
  • Fig. 2 shows a refrigeration cycle as described in Japanese Patent Application Laid-Open No. 120119/1995, which is a conventional refrigeration cycle utilized for a heat pump and consists of a compressor, a four-way valve, a heat exchanger, an expansion valve, and an accumulator.
  • reference numeral 101 designates a compressor
  • 102 designates a four-way valve for changing the flow of a refrigerant between a cooling operation and a heating operation
  • 103 designates an indoor heat exchanger
  • 104 through 107 designate check valves
  • 108 designates a receiver
  • 109 designates an expansion valve
  • 110 designates an outdoor heat exchanger
  • 111 designates an indoor blast fan
  • 112 designates an outdoor blast fan.
  • the refrigerant compressed by the compressor 101 flows into the outdoor heat exchanger 110 by way of the four-way valve 102, sequentially flows through the check valve 104, the receiver 108, the expansion valve 109, the check valve 107, and the indoor heat exchanger 103, and returns to the compressor 101 by way of the four-way valve 102.
  • the compressed refrigerant flows into the indoor heat exchanger 103 from the compressor 101 by way of the four-way valve 102, sequentially flows through the check valve 105, the receiver 108, the expansion valve 109, the check valve 106, and the outdoor heat exchanger 110, and returns to the compressor 101 by way of the four-way valve 102.
  • the amount of refrigerant required by the refrigerant circuit during the cooling operation is compared with that required by the same during the heating operation.
  • the indoor heat exchanger 103 is generally superior to the outdoor heat exchanger 110 in terms of an efficiency for condensing a refrigerant.
  • the content volume of a portion of the heat exchanger through which the refrigerant flows can be reduced.
  • a heating operation requires a smaller amount of refrigerant than does a cooling operation.
  • the receiver 108 provided upstream of the expansion valve 109 in a direction in which the refrigerant flows is for storing a refrigerant liquid, thereby adjusting a difference in the amount of refrigerant required for cooling operation and that required for heating operation.
  • Fig. 3 shows the refrigeration cycle of the refrigerant circuit shown in Fig. 2 in the form of a p-h diagram.
  • an interval between "a" and "b” corresponds to a compression stroke of the compressor 101
  • an interval between "b” and “c” corresponds to a condensation stroke of the heat exchanger 103 or 110
  • an interval between "c” and “d” corresponds to an expansion stroke of the expansion valve 109
  • an interval between "d” and "a” corresponds an evaporation stroke of the heat exchanger 110 or 103.
  • the refrigerant liquid and refrigerant gas are mixedly present in the receiver 108 of the refrigerant circuit.
  • the refrigerant provided in the receiver has become saturated.
  • the saturated liquid refrigerant flows into the evaporator by way of a liquid pipe, a strainer, a liquid line electromagnetic valve, these being not shown, and the expansion valve 109. Since the liquid refrigerant is not excessively cooled, the refrigerant is likely to enter a flash gas state in which a refrigerant liquid and the refrigerant gas are mixedly present if the liquid pipe or the like has resistance.
  • the amount of refrigerant flowing through the expansion valve 109 drops considerably, as a result of which predetermined refrigerating power is not achieved.
  • Fig. 4 shows an example of a basic refrigerant circuit disposed in another conventional air-cooling heat pump chiller.
  • the refrigerant compressed by the compressor 201 flows through the four-way valve 202, the air-side heat exchanger 203, the expansion valve 204, and the water-side heat exchanger 205, and then returns to the compressor 201 while passing through the four-way valve 202 and the accumulator 206.
  • the compressed refrigerant flows through the four-way valve 202, and sequentially flows through the water-side heat exchanger 205, the expansion valve 204, the air-side heat exchanger 2 03 and returns to the compressor 201 by way of the four-way valve 202 and the accumulator 206.
  • the amount of refrigerant required by the refrigerant circuit during the cooling operation is compared with that required by the same during the heating operation.
  • the water-side heat exchanger 205 is generally superior to the air-side heat exchanger 203 in terms of an efficiency for condensing a refrigerant. Hence, the inner volume of the heat exchanger in the refrigerant side can be reduced.
  • a heating operation requires a smaller amount of refrigerant than does a cooling operation.
  • the excessive refrigerant flows into and is stored in the refrigerant amount control tank 208 by way of the bypass pipe 207. At this time, the refrigerant amount control tank 208 is filled with a refrigerant liquid.
  • the amount of refrigerant required by the refrigerant circuit becomes deficient.
  • the refrigerant stored in the refrigerant amount control tank 208 flows into a refrigerant circuit, thereby compensating for the deficiency.
  • the refrigerant amount control tank 208 is filled with only a refrigerant gas.
  • the amount of refrigerant required during a heating operation becomes smaller than that required during a cooling operation in the coolant circuit. Hence, excessive refrigerant flows into the refrigerant amount control tank 208. Conversely, the amount of refrigerant becomes deficient during the cooling operation, and the refrigerant flowing from the refrigerant amount control tank 208 compensates for the deficiency.
  • the volume of the refrigerant amount control tank 208 is determined by the amount of excessive refrigerant arising during a heating operation.
  • the refrigerant liquid accumulating in the accumulator 206 assumes a composition largely consisting of HFC 134a, which among the components is the most susceptible to condensation.
  • the refrigerant existing in the refrigerant circuit exclusive of the accumulator 206 is largely consisting of HFC 32 and HFC 125, which are remaining components.
  • the excessive refrigerant liquid which flows into the refrigerant amount control tank 208, also assumes a composition largely consisting of HFC 32 and HFC 125.
  • the refrigerant existing in the refrigerant circuit assumes a standard composition.
  • HFC 134a which is susceptible to condensation, becomes liquefied in the water-side heat exchanger 205 prior to the remaining components; that is, HFC 32 and HFC 125, in a transient state arising during startup.
  • the excessive refrigerant liquid flowing into the refrigerant amount control tank 208 tends to contain a large amount of HFC 134a.
  • the refrigerant existing in the refrigerant circuit exclusive of the refrigerant amount control tank 208 assumes a composition largely consisting of the remaining components; that is, HFC 32 and HFC 125. In accordance with characteristics of the refrigerant, the refrigerating power tends to increase.
  • an unillustrated high-pressure switch which is a protective device to be attached to a refrigerant pipe interposed between an outlet port of the compressor 201 and the four-way valve 202 for avoiding occurrence of an increase in high pressure, becomes apt to issue a warning or to halt operation.
  • the refrigerant gas and the refrigerant liquid are simultaneously stored in the refrigerant amount control tank 208.
  • the refrigerant gas stored in the refrigerant amount control tank 208 contains HFC 32 and HFC 125, which are susceptible to evaporation, in larger quantity than does a standard composition.
  • HFC 32 and HFC 125 which are susceptible to evaporation, in larger quantity than does a standard composition.
  • the composition of the refrigerant situated in the refrigerant circuit exclusive of the refrigerant amount control tank208 changes in accordance with the quantity of refrigerant gas stored in the refrigerant amount control tank 208. In association with a decrease in the quantity of refrigerant gas, the refrigerating power changes.
  • EP-A-0 631 095 discloses another refrigerant circuit to control the amount of refrigerant in the circuit.
  • the invention has been conceived to solve the foregoing problem and aims at maintaining the composition of a mixed refrigerant flowing through a refrigerant circuit at a standard composition.
  • the invention provides an improved refrigerant circuit, in which connection is made, by way of a refrigerant pipe, between a compressor, a four-way valve, a first heat exchanger serving as a condenser or an evaporator, an expansion valve, a second heat exchanger serving as an evaporator or a condenser, and an accumulator.
  • the refrigerant circuit comprises a first bypass pipe connected to a refrigerant pipe provided between the expansion valve and the second heat exchanger.
  • a refrigerant amount control tank is connected to the first bypass pipe.
  • a second bypass pipe which is connected to the refrigerant amount control tank at one end, is connected, at another end, to a position on a refrigerant pipe interposed between the expansionvalve and the second heat exchanger, and the position is closer to the expansion valve than to a position where the first bypass pipe is attached.
  • a check valve is interposed into the second bypass pipe.
  • Fig. 1 shows an example of a basic refrigerant circuit employed in an air-cooling heat pump chiller, showing a preferred embodiment of the present invention.
  • reference numeral 1 designates a compressor
  • 2 designates a four-way valve for switching the flow of a refrigerant between a cooling operation and a heating operation
  • 3 designates an air-side heat exchanger
  • 4 designates an expansion valve
  • 5 designates a water-side heat exchanger
  • 6 designates an accumulator
  • 8 designates a refrigerant amount control tank disposed by way of a bypass pipe 7
  • 9 designates a bypass pipe, which has a check valve 10, and which returns the refrigerant accumulating in the refrigerant amount control tank 8 to a refrigerant circuit.
  • a pipe smaller in diameter than the bypass pipe 7 is used for the bypass pipe 9.
  • a pipe having an outside diameter of 9.52 mm is used for the bypass pipe 7
  • a pipe having an outside diameter of 6.4 mm is used for the bypass pipe 9.
  • Non-azeotropic mixed refrigerant HFC 407C is used as refrigerant for the refrigerant circuit.
  • a difference between them lies in that a portion of the refrigerant accumulating in the refrigerant amount control tank 8 is returned to the refrigerant circuit at all times by way of the bypass pipe 9, which is disposed at an upper portion of the refrigerant amount control tank 8 and which has the check valve 10, by virtue of the pressure developing in a position on a main pipe of the refrigerant circuit to which the bypass pipe 9 is attached being lower than the pressure developing in a position on the main pipe to which the bypass pipe 7 is attached.
  • the refrigerant circuit is assumed to operate while a liquid refrigerant accumulates in the accumulator 6.
  • the liquid refrigerant accumulating in the accumulator 6 assumes a composition largely consisting of HFC 134a, which among the components is the most susceptible to condensation.
  • the refrigerant existing in the refrigerant circuit exclusive of the accumulator 6 largely consists of HFC 32 and HFC 125, which are remaining components.
  • the excessive refrigerant liquid which flows into the refrigerant amount control tank 8, also assumes a composition largely consisting of HFC 32 and HFC 125.
  • the liquid refrigerant which largely consists of HFC 134a and is accumulated in the accumulator 206, flows through the refrigerant circuit while being evaporated.
  • the refrigerant existing in the refrigerant circuit exclusive of the refrigerant amount control tank 8 assumes a composition largely consisting of HFC 134a.
  • a portion of the refrigerant which accumulates in the refrigerant amount control tank 8 and assumes a composition largely consisting of HFC 32 and HFC 125, is returned to the refrigerant circuit by way of the bypass pipe 9, which is disposed at an upper portion of the refrigerant amount control tank 8 and which has the check valve 10, by virtue of a difference between the pressure developing in a position on a main pipe of the refrigerant circuit to which the bypass pipe 7 is attached and the pressure developing in a position on the main pipe of the refrigerant circuit to which the bypass pipe 9 is attached.
  • the portion of the refrigerant is mixed with a refrigerant largely consisting of HFC 134a.
  • the refrigerant flowing through the refrigerant circuit returns to a standard composition.
  • the quantity of refrigerant returning to the refrigerant circuit by way of the bypass pipe 9 is regulated by means of rendering the diameter of the bypass pipe 9 smaller than that of the bypass pipe 7, thus effecting a setting such that a constant quantity of excessive refrigerant can be ensured in the refrigerant amount control tank 8 during a stable heating operation.
  • the refrigerant circuit is assumed to halt operations while no liquid refrigerant has accumulated in the accumulator 6. At this time, the refrigerant flowing through the refrigerant circuit assumes a standard composition.
  • HFC 134a which is susceptible to condensation, becomes liquefied in the water-side heat exchanger 5 prior to the remaining components; that is, HFC 32 and HFC 125.
  • the excessive refrigerant liquid flowing into the refrigerant amount control tank 8 tends to contain a large amount of HFC 134a.
  • a portion of the refrigerant, which accumulates in the refrigerant amount control tank 8, is returned to the refrigerant circuit immediately before the expansion valve 4 by way of the bypass pipe 9, which is disposed at an upper portion of the refrigerant amount control tank 8 and which has the check valve 10, by virtue of a difference between the pressure developing in a position on a main pipe of the refrigerant circuit to which the bypass pipe 7 is attached and the pressure developing in a position on the main pipe of the refrigerant circuit to which the bypass pipe 9 is attached.
  • a portion of the refrigerant assuming a composition largely consisting of HFC 134a returns to the refrigerant circuit and is mixed with the refrigerant assuming a composition largely consisting of HFC 32 and HFC 125.
  • the refrigerant flowing through the refrigerant circuit is returned to a standard composition.
  • the bypass pipe 9 plays the role of draining gas from the refrigerant amount control tank 8.
  • the refrigerant can flow smoothly into the tank 8 by way of the bypass pipe 7. This effect is not limited to non-azeotropic mixed refrigerant HFC and is yielded by a single refrigerant or non-azeotropic refrigerant.
  • the embodiment has described a heat pump chiller involving a noticeable difference in the quantity of refrigerant required for heating operation and that required for cooling operation.
  • the invention can also be applied to another air conditioner capable of changing flow of a refrigerant by means of a four-way valve.
  • the invention provides an improved refrigerant circuit, in which connection is made, by way of a refrigerant pipe, between a compressor 1, a four-way valve 2, a first heat exchanger 3 serving as a condenser or an evaporator, an expansion valve 4, a second heat exchanger 5 serving as an evaporator or a condenser, and an accumulator 6.
  • the refrigerant circuit comprises a first bypass pipe 7 connected to a refrigerant pipe provided between the expansion valve 4 and the second heat exchanger 5.
  • a refrigerant amount control tank 8 is connected to the first bypass pipe 7.
  • a check valve 10 is interposed into the second bypass pipe 9.
  • the second bypass pipe 9 plays the role of draining gas from the refrigerant amount control tank 8 and enables smooth flow of refrigerant when excessive refrigerant is stored in the refrigerant amount control tank 8 during a heating operation.
  • the second bypass pipe is smaller in diameter than the first bypass pie.
  • the quantity of refrigerant accumulated in the refrigerant amount control tank is returned to the refrigerant circuit from the refrigerant amount control tank by way of the second bypass pipe.
  • the quantity of refrigerant accumulating in the refrigerant amount control tank can be maintained constant.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Details Of Measuring And Other Instruments (AREA)

Claims (3)

  1. Circuit de réfrigérant dans lequel une connexion est faite, au moyen d'un tuyau de réfrigérant, entre un compresseur (1), un distributeur à quatre voies (2), un premier échangeur de chaleur (3) servant de condenseur ou d'évaporateur, une vanne de détente (4), un deuxième échangeur de chaleur (5) servant d'évaporateur ou de condenseur, et un accumulateur (6), le circuit de réfrigérant étant caractérisé par :
    un premier tuyau de dérivation (7) raccordé à un tuyau de réfrigérant prévu entre la vanne de détente (4) et le deuxième échangeur de chaleur (5) ;
    une cuve de contrôle de quantité de réfrigérant (8) raccordée au premier tuyau de dérivation (7) ;
    un deuxième tuyau de dérivation (9) qui est raccordé- d'un côté - à la cuve de contrôle de quantité de réfrigérant (8), et qui est raccordé - de l'autre côté - à une position sur un tuyau de réfrigérant intercalée entre la soupape de dilatation (4) et le deuxième échangeur de chaleur (5), la position étant plus proche de la vanne de détente (4) que d'une position dans laquelle le premier tuyau de dérivation (7) est fixé ; et
    un clapet anti-retour (10) qui est intercalé à l'intérieur du deuxième tuyau de dérivation (9), dans lequel:
    le deuxième tuyau de dérivation (9) a pour fonction d'évacuer le gaz hors de la cuve de contrôle de quantité de réfrigérant (8) et permet de régulariser un écoulement de réfrigérant quand une quantité excessive de réfrigérant est contenue dans la cuve de contrôle de quantité de réfrigérant (8) lors d'une opération de chauffage.
  2. Circuit de réfrigérant selon la revendication 1, dans lequel un réfrigérant mélangé est employé.
  3. Circuit de réfrigérant selon la revendication 1 ou 2, dans lequel le deuxième tuyau de dérivation (9) a un diamètre plus petit que celui du premier tuyau de dérivation (7).
EP02020405A 2001-09-12 2002-09-10 Circuit de réfrigérant Expired - Lifetime EP1293735B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001276040 2001-09-12
JP2001276040A JP4848608B2 (ja) 2001-09-12 2001-09-12 冷媒回路

Publications (3)

Publication Number Publication Date
EP1293735A2 EP1293735A2 (fr) 2003-03-19
EP1293735A3 EP1293735A3 (fr) 2003-05-28
EP1293735B1 true EP1293735B1 (fr) 2007-03-14

Family

ID=19100808

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02020405A Expired - Lifetime EP1293735B1 (fr) 2001-09-12 2002-09-10 Circuit de réfrigérant

Country Status (7)

Country Link
EP (1) EP1293735B1 (fr)
JP (1) JP4848608B2 (fr)
CN (1) CN1173139C (fr)
AT (1) ATE356962T1 (fr)
DE (1) DE60218793T2 (fr)
ES (1) ES2284756T3 (fr)
PT (1) PT1293735E (fr)

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JP5157580B2 (ja) * 2008-03-28 2013-03-06 ダイキン工業株式会社 冷凍装置
JP2012077983A (ja) * 2010-09-30 2012-04-19 Daikin Industries Ltd 冷凍回路
CN101949621A (zh) * 2010-09-30 2011-01-19 广东志高空调有限公司 一种带制冷剂调节功能的节能空调
JP5765211B2 (ja) * 2011-12-13 2015-08-19 ダイキン工業株式会社 冷凍装置
AT513637B1 (de) * 2012-12-13 2016-05-15 Herz Energietechnik Gmbh Wärmepumpenverfahren und -einrichtung zur Optimierung der Unterkühlung während des Kondensationsprozesses im Kaltdampf-Kompressions-Prozess
GB2533230B (en) * 2013-08-09 2020-06-17 Trane Air Conditioning Systems China Co Ltd Transitional refrigerant migration control in refrigeration systems
KR101669971B1 (ko) * 2014-11-17 2016-10-27 엘지전자 주식회사 공기조화장치
CN105674640B (zh) * 2014-11-18 2018-04-17 上海海立电器有限公司 空调系统制冷剂充注量匹配调节装置及方法
JP6479203B2 (ja) * 2015-10-20 2019-03-06 三菱電機株式会社 冷凍サイクル装置
US11105544B2 (en) 2016-11-07 2021-08-31 Trane International Inc. Variable orifice for a chiller
CN106482303B (zh) * 2016-11-25 2022-05-17 广州华凌制冷设备有限公司 一种空调器及其制冷控制方法
JP7105903B2 (ja) * 2018-09-28 2022-07-25 三菱電機株式会社 冷凍サイクル装置
CN109974169B (zh) * 2019-02-28 2021-02-19 浙江高翔工贸有限公司 一种双工质冷暖空调
DE102019002297A1 (de) * 2019-03-31 2020-10-01 Steffen Klein Erweiterung des R718-Einsatzbereichs
JP7501257B2 (ja) 2020-09-09 2024-06-18 富士通株式会社 冷却装置、電子機器及び冷却方法

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JPH0627589B2 (ja) * 1985-11-19 1994-04-13 三洋電機株式会社 ヒ−トポンプ式冷凍装置
KR930000852B1 (ko) * 1987-07-31 1993-02-06 마쓰시다덴기산교 가부시기가이샤 히이트 펌프장치
JPH01273959A (ja) * 1988-04-25 1989-11-01 Nippon Denso Co Ltd 車両用空気調和機
JPH0745982B2 (ja) * 1988-08-31 1995-05-17 松下電器産業株式会社 ヒートポンプ装置
JPH0414975A (ja) * 1990-05-08 1992-01-20 Sharp Corp 画像再生装置
US5186012A (en) * 1991-09-24 1993-02-16 Institute Of Gas Technology Refrigerant composition control system for use in heat pumps using non-azeotropic refrigerant mixtures
JPH06341741A (ja) * 1993-06-01 1994-12-13 Daikin Ind Ltd 冷凍装置のデフロスト制御装置
JPH0712411A (ja) * 1993-06-24 1995-01-17 Hitachi Ltd 冷凍サイクルおよび冷凍サイクルの冷媒組成比制御方法
JP3168496B2 (ja) * 1993-10-28 2001-05-21 株式会社日立製作所 空気調和装置
JPH10119561A (ja) * 1996-10-14 1998-05-12 Calsonic Corp 自動車用空気調和装置
JP2000179957A (ja) * 1998-12-17 2000-06-30 Hitachi Ltd 空気調和機

Also Published As

Publication number Publication date
DE60218793T2 (de) 2007-12-06
ATE356962T1 (de) 2007-04-15
CN1405515A (zh) 2003-03-26
ES2284756T3 (es) 2007-11-16
EP1293735A2 (fr) 2003-03-19
PT1293735E (pt) 2007-05-31
JP2003083644A (ja) 2003-03-19
EP1293735A3 (fr) 2003-05-28
DE60218793D1 (de) 2007-04-26
CN1173139C (zh) 2004-10-27
JP4848608B2 (ja) 2011-12-28

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