EP2592366A2 - Cycle de frigorigène mixte non azéotrope et réfrigérateur ainsi équipé - Google Patents

Cycle de frigorigène mixte non azéotrope et réfrigérateur ainsi équipé Download PDF

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Publication number
EP2592366A2
EP2592366A2 EP12190551.7A EP12190551A EP2592366A2 EP 2592366 A2 EP2592366 A2 EP 2592366A2 EP 12190551 A EP12190551 A EP 12190551A EP 2592366 A2 EP2592366 A2 EP 2592366A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
tube
evaporator
refrigerant tube
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.)
Withdrawn
Application number
EP12190551.7A
Other languages
German (de)
English (en)
Other versions
EP2592366A3 (fr
Inventor
Won Jae Yoon
Yong Chan Kim
Yong Han Kim
Kook Jeong Seo
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.)
Samsung Electronics Co Ltd
Korea University Research and Business Foundation
Original Assignee
Samsung Electronics Co Ltd
Korea University Research and Business Foundation
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 Samsung Electronics Co Ltd, Korea University Research and Business Foundation filed Critical Samsung Electronics Co Ltd
Publication of EP2592366A2 publication Critical patent/EP2592366A2/fr
Publication of EP2592366A3 publication Critical patent/EP2592366A3/fr
Withdrawn legal-status Critical Current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
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • Embodiments of the present disclosure relate to a non-azeotropic mixed refrigerant cycle using a non-azeotropic mixed refrigerant, and a refrigerator equipped with the same.
  • a refrigeration cycle includes a compressor to compress a refrigerant, a condenser to cool the refrigerant discharged from the compressor such that the refrigerant is condensed, an expansion valve to expand the refrigerant transferred from the condenser through pressure reduction, and an evaporator to cause the refrigerant expanded through pressure reduction to evaporate while absorbing heat.
  • LM cycle is a non-azeotropic mixed refrigerant cycle using a non-azeotropic mixed refrigerant.
  • the LM cycle includes a first heat exchanger to cause heat exchange between the refrigerant emerging from the condenser and the refrigerant emerging from the first evaporator, and a second heat exchanger to cause heat exchange between the refrigerant emerging from the condenser and the refrigerant emerging from the second evaporator.
  • the LM cycle is a refrigeration cycle capable of achieving an enhancement in cooling performance.
  • the heat exchangers are provided as separate components in the LM cycle to be combined with various refrigerant tubes, and that causes the worsening of productivities and the increase of manufacturing costs.
  • Another aspect of the present disclosure is to provide a refrigerator capable of achieving more efficient heat exchange in first and second heat exchangers thereof.
  • a non-azeotropic mixed refrigerant cycle includes a compressor to compress a refrigerant, a condenser to cool the refrigerant discharged from the compressor after receiving the refrigerant, an expansion device to expand the refrigerant received from the condenser through pressure reduction, a first evaporator to evaporate the refrigerant emerging from the expansion device after receiving the refrigerant from the expansion device, a second evaporator to evaporate the refrigerant emerging from the first evaporator after receiving the refrigerant from the first evaporator, a first refrigerant tube to guide the refrigerant from the condenser to the first evaporator, a second refrigerant tube to guide the refrigerant from the first evaporator to the second evaporator, a third refrigerant tube to guide the refrigerant from the second evaporator to the compressor, and a first heat exchanger to cause heat exchange between a portion of the
  • the refrigerant, which passes through the first refrigerant tube, and the refrigerant, which passes through the second refrigerant tube, may pass through the first heat exchanger in opposite directions, respectively.
  • the non-azeotropic mixed refrigerant cycle may further include a second heat exchanger to cause heat exchange between a portion of the first refrigerant tube and the third refrigerant tube, wherein the second heat exchanger is formed as a single unitwiht the first refrigerant tube and the third refrigerant tube.
  • the second heat exchanger may be formed with a double tube structure in which the first refrigerant tube is arranged within the third refrigerant tube.
  • the first heat exchanger and the second heat exchanger may be formed as a single unit with the first refrigerant tube, the second refrigerant tube, and the third refrigerant tube.
  • the refrigerant, which passes through the first refrigerant tube, and the refrigerant, which passes through the third refrigerant tube, may pass through the second heat exchanger in opposite directions, respectively.
  • the expansion device may be integrated with a portion of the first refrigerant tube arranged at a side of the evaporator.
  • the non-azeotropic mixed refrigerant cycle may further include an accumulator integrated with a portion of the third refrigerant tube arranged at a side of the compressor.
  • a non-azeotropic mixed refrigerant cycle includes a compressor to compress a refrigerant, a condenser to cool the refrigerant discharged from the compressor after receiving the refrigerant, an expansion device to expand the refrigerant received from the condenser through pressure reduction, a first evaporator to evaporate the refrigerant emerging from the expansion device after receiving the refrigerant from the expansion device, a second evaporator to evaporate the refrigerant emerging from the first evaporator after receiving the refrigerant from the first evaporator, a first refrigerant tube to guide the refrigerant from the condenser to the first evaporator, a second refrigerant tube to guide the refrigerant from the first evaporator to the second evaporator, a third refrigerant tube to guide the refrigerant from the second evaporator to the compressor, and a heat exchanger to cause heat exchange between a portion of the first
  • a refrigerator includes freezing and refrigerating compartments, a compressor to compress a refrigerant, a condenser to cool the refrigerant discharged from the compressor after receiving the refrigerant, a first evaporator to cool the freezing compartment, a second evaporator to cool the refrigerating compartment, a first refrigerant tube to guide the refrigerant from the condenser to the first evaporator, a second refrigerant tube to guide the refrigerant from the first evaporator to the second evaporator, a third refrigerant tube to guide the refrigerant from the second evaporator to the compressor, a first heat exchanger to cause heat exchange between a downstream portion of the first refrigerant tube and the second refrigerant tube, a second heat exchanger to cause heat exchange between an upstream portion of the first refrigerant tube and the third refrigerant tube, wherein the first heat exchanger and the second heat exchanger are formed
  • the refrigerant, which passes through the first refrigerant tube, and the refrigerant, which passes through the second refrigerant tube, may pass through the first heat exchanger in opposite directions, respectively.
  • the second heat exchanger may be formed with a double tube structure in which the first refrigerant tube is arranged within the third refrigerant tube.
  • the first heat exchanger and the second heat exchanger may be formed as a single unit with the first refrigerant tube, the second refrigerant tube, and the third refrigerant tube.
  • the refrigerant, which passes through the first refrigerant tube, and the refrigerant, which passes through the third refrigerant tube, may pass through the second heat exchanger in opposite directions, respectively.
  • the expansion device may be integrated with a portion of the first refrigerant tube arranged at a side of the evaporator.
  • the refrigerator may further include an accumulator integrated with a portion of the third refrigerant tube arranged at a side of the compressor.
  • a refrigerator includes freezing and refrigerating compartments, a compressor to compress a refrigerant, a condenser to cool the refrigerant discharged from the compressor after receiving the refrigerant, a first evaporator to cool the freezing compartment, a second evaporator to cool the refrigerating compartment, a first refrigerant tube to guide the refrigerant from the condenser to the first evaporator, a second refrigerant tube to guide the refrigerant from the first evaporator to the second evaporator, a third refrigerant tube to guide the refrigerant from the second evaporator to the compressor, a first heat exchanger to cause heat exchange between a downstream portion of the first refrigerant tube and the second refrigerant tube, a second heat exchanger to cause heat exchange between an upstream portion of the first refrigerant tube and the third refrigerant tube, wherein the refrigerant, which passes through the first refrigerant,
  • the non-azeotropic mixed refrigerant cycle uses a mixed refrigerant containing a plurality of refrigerant elements.
  • the non-azeotropic mixed refrigerant cycle includes a compressor 1 to compress a refrigerant, a condenser 2 to cool the compressed refrigerant after receiving the refrigerant from the compressor 1, an expansion device 3 to expand the refrigerant discharged from the condenser 2 through pressure reduction, a first evaporator 4 to evaporate the expanded refrigerant after receiving the refrigerant from the expansion device 3, a second evaporator 5 to again evaporate the evaporated refrigerant after receiving the refrigerant from the first evaporator 4, and an accumulator 6 to prevent a liquid component of the refrigerant from being sucked into the compressor 1.
  • the refrigerant expanded through pressure reduction by the expansion device 3 is first transferred to the first evaporator 4.
  • the first evaporator 4 receives a liquid-phase refrigerant
  • the second evaporator 5 receives a refrigerant, a portion of which has been evaporated during passage thereof through the first evaporator 4, namely, a mixed refrigerant containing a gas-phase refrigerant and a liquid-phase refrigerant.
  • the first evaporator 4 may perform cooling at a lower temperature than the second evaporator 5.
  • the non-azeotropic mixed refrigerant cycle also includes a plurality of refrigerant tubes to connect the above-described constituent elements such that the refrigerant is circulated through the constituent elements via the refrigerant tubes.
  • the plurality of refrigerant tubes may include a first refrigerant tube P1 to guide the refrigerant from the condenser 2 to the first evaporator 4, a second refrigerant tube P2 to guide the refrigerant from the first evaporator 4 to the second evaporator 5, a third refrigerant tube P3 to guide the refrigerant from the second evaporator 5 to the compressor 1, and a fourth refrigerant tube P4 to guide the refrigerant from the compressor 1 to the condenser 2.
  • the non-azeotropic mixed refrigerant cycle further includes a first heat exchanger 7 to cause heat exchange between the refrigerant condensed by the condenser 2 and the refrigerant emerging from the first evaporator 4, and a second heat exchanger 8 to cause heat exchange between the refrigerant condensed by the condenser 2 and the refrigerant emerging from the second evaporator 5.
  • the first heat exchanger 7 causes heat exchange between a downstream portion of the first refrigerant tube P1 and the second refrigerant tube P2.
  • the second heat exchanger 9 causes heat exchange between an upstream portion of the first refrigerant tube P1 and the third refrigerant tube P3.
  • the first heat exchanger 7 is not provided as a separate component which needs to be connected to the first refrigerant tube P1 and the second refrigerant tube P2 respectively.
  • the first heat exchanger 7 is formed with a double tube structure such that the first refrigerant tube P1 is arranged within the second refrigerant tube P2.
  • the second heat exchanger 8 is formed in similar way to the first heat exchanger 7.
  • the second heat exchanger 8 is formed with a double tube structure such that the first refrigerant tube P1 is arranged within the third refrigerant tube P3.
  • the refrigerant which passes through the first refrigerant tube P1, exchanges heat with the refrigerant passing through the third refrigerant tube P3 arranged outside the first refrigerant tube P1 and the refrigerant passing through the second refrigerant tube P2 arranged outside the first refrigerant tube P1 in a sequential manner.
  • each of the first and second heat exchangers 7 and 8 is configured to be formed with the refrigerant tubes themselves such as a double tube structure in which the second refrigerant tube P2 or third refrigerant tube P3 is arranged outside the first refrigerant tube P1 without providing further components for exchanging the heat between two different temperature refrigerants, it may be possible to simplify the configurations of the first and second heat exchangers 7 and 8. As a result, it may be possible to greatly reduce the space occupied by the first and second heat exchangers 7 and 8. Further, the first heat exchanger 7 and the second heat exchanger 8 may be integrally formed as a single unit according to the above mentioned structure.
  • the construction of the heat exchangers 7 or 8 is not limited to the double tube structure of the refrigerant tubes.
  • the first and second heat exchangers 7 or 8 may be formed as a single unit with the refrigerant tubes P1 and P2 or refrigerant tubes P1 and P3 in parallel. As long as the heat can be exchanged directly by the refrigerant tubes themselves, any structures of the heat exchanges 7 or 8 may be adopted.
  • the expansion device 3 may be constituted by a capillary tube integrated with a portion of the first refrigerant tube P1 arranged at the side of the first evaporator 4.
  • the accumulator 6 may be integrated with a portion of the third refrigerant tube P3 arranged at the side of the compressor 1. In this case, it may be possible to unify the first heat exchanger 7, second heat exchanger 8, expansion device 3 and accumulator 6 through the first refrigerant tube P1, second refrigerant tube P2 and third refrigerant tube P3 in the form of a single unit. Accordingly, the configuration of the non-azeotropic mixed refrigerant cycle may be further simplified.
  • the refrigerant passing through the first refrigerant tube P1 and the refrigerant passing through the second refrigerant tube P2 pass through the first heat exchanger 7 in opposite directions, respectively, as shown in FIG. 2 .
  • the refrigerant passing through the first refrigerant tube P1 and the refrigerant passing through the third refrigerant tube P3 pass through the first heat exchanger 7 in opposite directions, respectively, as shown in FIG. 3 .
  • the refrigerant passing through the first refrigerant tube P1 may more efficiently exchange heat with the refrigerant passing through the second refrigerant tube P2 in the first heat exchanger 7 and the refrigerant passing through the third refrigerant tube P2 in the second heat exchanger 8.
  • the refrigerant is compressed in accordance with operation of the compressor 1.
  • the compressed refrigerant is transferred to the condenser 2 via the fourth refrigerant tube P4.
  • the refrigerant is cooled such that it is condensed into a liquid phase.
  • the refrigerant is transferred from the condenser 2 to the first evaporator 4 via the first refrigerant tube P1.
  • the refrigerant is expanded through pressure reduction while passing through the expansion device 3 provided at the first refrigerant tube P1. After expansion, the refrigerant is transferred to the first evaporator 4.
  • the refrigerant When the refrigerant passes through the first evaporator 4, it absorbs heat, such that a portion thereof is evaporated. Since the first evaporator 4 is arranged in a freezing compartment of the refrigerator, as described above, the refrigerant absorbs heat from the freezing compartment.
  • the refrigerant Since the refrigerant is partially evaporated during passage thereof through the first evaporator 4, it is transferred to the second evaporator 5 in the form of a mixture of a liquid-phase refrigerant and a gas-phase refrigerant. In the second evaporator 5, the liquid component of the refrigerant is evaporated while absorbing heat. Since the second evaporator 5 is arranged in a refrigerating compartment of the refrigerator, as described above, the refrigerant absorbs heat from the refrigerating compartment.
  • the refrigerant emerging from the second evaporator 5 is transferred to the compressor 1 via the third refrigerant tube P3. Since the accumulator 6 is arranged in the third refrigerant tube P3, as described above, the liquid component of the refrigerant, which is sucked into the compressor 1, is separated from the refrigerant such that only the gas-phase refrigerant is sucked into the compressor 1.
  • the refrigerant which passes through the first refrigerant tube P1 is cooled in a sequential manner while sequentially passing through the first and second heat exchangers 7 and 8. Accordingly, the refrigerant is transferred to the expansion device 3 in a state of being cooled to a further reduced temperature. As a result, the refrigerant expanded through pressure reduction while passing through the expansion device 3 enters a state capable of absorbing a further increased amount of heat. Thus, it may be possible to enhance the cooling performances of the first and second evaporators 4 and 5.
  • the refrigerant which passes through the second refrigerant tube P2, absorbs heat from the refrigerant passing through the first refrigerant tube P1. Accordingly, the temperature of the refrigerant introduced into the second evaporator 5 is increased. Thus, it may be possible to reduce irreversible loss that may occur when the refrigerant is supplied to the second evaporator 5 at low temperature.
  • the refrigerant which passes through the third refrigerant tube P3, is heated while absorbing heat from the refrigerant passing through the first refrigerant tube P1. Accordingly, the liquid component of the refrigerant, which is still in a liquid phase without being evaporated even after passage thereof through the second evaporator 5, is evaporated while passing through the second heat exchanger 8. Thus, the amount of a liquid refrigerant transferred to the compressor 1 is reduced.
  • each of the first and second heat exchangers is constituted by refrigerant tubes having a double tube structure or being formed as a single unit. Accordingly, the configuration of the non-azeotropic mixed refrigerant cycle is simplified.
  • the refrigerant passing through the first refrigerant tube and the refrigerant passing through the second refrigerant tube pass through the first heat exchanger in opposite directions, respectively.
  • the refrigerant passing through the first refrigerant tube and the refrigerant passing through the third refrigerant tube pass through the first heat exchanger in opposite directions, respectively. Accordingly, the refrigerant passing through the first refrigerant tube P1 may more efficiently exchange heat with the refrigerant passing through the second refrigerant tube P2 and the refrigerant passing through the third refrigerant tube P3.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)
EP12190551.7A 2011-11-08 2012-10-30 Cycle de frigorigène mixte non azéotrope et réfrigérateur ainsi équipé Withdrawn EP2592366A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020110115819A KR20130050639A (ko) 2011-11-08 2011-11-08 비공비 혼합 냉매사이클 및 냉장고

Publications (2)

Publication Number Publication Date
EP2592366A2 true EP2592366A2 (fr) 2013-05-15
EP2592366A3 EP2592366A3 (fr) 2014-06-18

Family

ID=47172429

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12190551.7A Withdrawn EP2592366A3 (fr) 2011-11-08 2012-10-30 Cycle de frigorigène mixte non azéotrope et réfrigérateur ainsi équipé

Country Status (4)

Country Link
US (1) US20130111943A1 (fr)
EP (1) EP2592366A3 (fr)
KR (1) KR20130050639A (fr)
CN (1) CN103090602A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2857778A1 (fr) 2013-10-03 2015-04-08 Whirlpool Corporation Réfrigérateur avec mélange non azéotropique de réfrigérants d'hydrocarbures
EP3073210A1 (fr) 2015-03-27 2016-09-28 Whirlpool Corporation Réfrigérateur avec une efficacité

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160123537A1 (en) * 2013-07-26 2016-05-05 Bruker Biospin Corporation Flexible interface closed cycle cryocast with remotely located point of cooling
KR101438155B1 (ko) * 2014-05-21 2014-09-05 주식회사 지엠에스 극초저온 냉동고
CN105202791A (zh) * 2015-09-09 2015-12-30 江苏宝奥兰空调设备有限公司 一种制冷系统及方法
US10782048B2 (en) * 2016-01-15 2020-09-22 Lg Electronics Inc. Deep freezer
KR102446555B1 (ko) * 2016-01-15 2022-09-23 엘지전자 주식회사 심온 냉동고
JP2020034248A (ja) * 2018-08-31 2020-03-05 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 冷蔵庫
WO2020045868A1 (fr) * 2018-08-31 2020-03-05 Samsung Electronics Co., Ltd. Réfrigérateur
KR20210022933A (ko) * 2019-08-21 2021-03-04 엘지전자 주식회사 비공비혼합냉매를 사용하는 냉장고

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4439996A (en) * 1982-01-08 1984-04-03 Whirlpool Corporation Binary refrigerant system with expansion valve control
US4416119A (en) * 1982-01-08 1983-11-22 Whirlpool Corporation Variable capacity binary refrigerant refrigeration apparatus
GB2143014B (en) * 1983-05-16 1986-09-17 Hotpoint Ltd Refrigerator/freezer units
US5207077A (en) * 1992-03-06 1993-05-04 The University Of Maryland Refrigeration system
CN2358964Y (zh) * 1997-07-10 2000-01-19 卢柱华 气液分离器
SG88804A1 (en) * 1999-12-07 2002-05-21 Sanyo Electric Co Air conditioner
WO2004051155A1 (fr) * 2002-12-03 2004-06-17 Nihon Freezer Co.,Ltd. Systeme refrigerant a melange non-azeotrope, et melange non-azeotrope pour tres basses temperatures utilise pour ce systeme
US7089760B2 (en) * 2003-05-27 2006-08-15 Calsonic Kansei Corporation Air-conditioner
JP4387974B2 (ja) * 2005-04-25 2009-12-24 パナソニック株式会社 冷凍サイクル装置
DE102009001677A1 (de) * 2009-03-19 2010-09-23 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät, Drosselrohr für ein Kältegerät und Verfahren zu dessen Herstellung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2857778A1 (fr) 2013-10-03 2015-04-08 Whirlpool Corporation Réfrigérateur avec mélange non azéotropique de réfrigérants d'hydrocarbures
EP3073210A1 (fr) 2015-03-27 2016-09-28 Whirlpool Corporation Réfrigérateur avec une efficacité

Also Published As

Publication number Publication date
KR20130050639A (ko) 2013-05-16
CN103090602A (zh) 2013-05-08
EP2592366A3 (fr) 2014-06-18
US20130111943A1 (en) 2013-05-09

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