US20130111943A1 - Non-azeotropic mixed refrigerant cycle and refrigerator equipped therewith - Google Patents

Non-azeotropic mixed refrigerant cycle and refrigerator equipped therewith Download PDF

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Publication number
US20130111943A1
US20130111943A1 US13/661,662 US201213661662A US2013111943A1 US 20130111943 A1 US20130111943 A1 US 20130111943A1 US 201213661662 A US201213661662 A US 201213661662A US 2013111943 A1 US2013111943 A1 US 2013111943A1
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US
United States
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.)
Abandoned
Application number
US13/661,662
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English (en)
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
Assigned to SAMSUNG ELECTRONICS CO., LTD., KOREA UNIVERSITY RESEARCH AND BUSINESS FOUNDATION reassignment SAMSUNG ELECTRONICS CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SEO, KOOK JEONG, KIM, YONG CHAN, KIM, YONG HAN, YOON, WON JAE
Publication of US20130111943A1 publication Critical patent/US20130111943A1/en
Abandoned 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 unit with 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,
  • FIG. 1 is a schematic view illustrating a non-azeotropic mixed refrigerant cycle according to an exemplary embodiment of the present disclosure
  • FIG. 2 is an enlarged view of a portion A of FIG. 1 ;
  • FIG. 3 is an enlarged view of a portion B of FIG. 1 .
  • 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 refrigerant passes through the first evaporator 4 , a portion of the refrigerant is evaporated.
  • the resultant refrigerant is then transferred to the second evaporator 5 .
  • 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 P 1 to guide the refrigerant from the condenser 2 to the first evaporator 4 , a second refrigerant tube P 2 to guide the refrigerant from the first evaporator 4 to the second evaporator 5 , a third refrigerant tube P 3 to guide the refrigerant from the second evaporator 5 to the compressor 1 , and a fourth refrigerant tube P 4 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 P 1 and the second refrigerant tube P 2 .
  • the second heat exchanger 9 causes heat exchange between an upstream portion of the first refrigerant tube P 1 and the third refrigerant tube P 3 .
  • the first heat exchanger 7 is not provided as a separate component which needs to be connected to the first refrigerant tube P 1 and the second refrigerant tube P 2 respectively.
  • the first heat exchanger 7 is formed with a double tube structure such that the first refrigerant tube P 1 is arranged within the second refrigerant tube P 2 .
  • 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 P 1 is arranged within the third refrigerant tube P 3 .
  • the refrigerant which passes through the first refrigerant tube P 1 , exchanges heat with the refrigerant passing through the third refrigerant tube P 3 arranged outside the first refrigerant tube P 1 and the refrigerant passing through the second refrigerant tube P 2 arranged outside the first refrigerant tube P 1 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 P 2 or third refrigerant tube P 3 is arranged outside the first refrigerant tube P 1 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 P 1 and P 2 or refrigerant tubes P 1 and P 3 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 P 1 arranged at the side of the first evaporator 4 .
  • the accumulator 6 may be integrated with a portion of the third refrigerant tube P 3 arranged at the side of the compressor 1 .
  • the refrigerant passing through the first refrigerant tube P 1 and the refrigerant passing through the second refrigerant tube P 2 pass through the first heat exchanger 7 in opposite directions, respectively, as shown in FIG. 2 .
  • the refrigerant passing through the first refrigerant tube P 1 and the refrigerant passing through the third refrigerant tube P 3 pass through the first heat exchanger 7 in opposite directions, respectively, as shown in FIG. 3 .
  • the refrigerant passing through the first refrigerant tube P 1 may more efficiently exchange heat with the refrigerant passing through the second refrigerant tube P 2 in the first heat exchanger 7 and the refrigerant passing through the third refrigerant tube P 2 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 P 4 .
  • 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 P 1 .
  • the refrigerant is expanded through pressure reduction while passing through the expansion device 3 provided at the first refrigerant tube P 1 . 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 P 3 . Since the accumulator 6 is arranged in the third refrigerant tube P 3 , 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 P 1 , 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 P 2 , absorbs heat from the refrigerant passing through the first refrigerant tube P 1 . 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 P 3 , is heated while absorbing heat from the refrigerant passing through the first refrigerant tube P 1 . 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 P 1 may more efficiently exchange heat with the refrigerant passing through the second refrigerant tube P 2 and the refrigerant passing through the third refrigerant tube P 3 .
US13/661,662 2011-11-08 2012-10-26 Non-azeotropic mixed refrigerant cycle and refrigerator equipped therewith Abandoned US20130111943A1 (en)

Applications Claiming Priority (2)

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KR10-2011-115819 2011-11-08
KR1020110115819A KR20130050639A (ko) 2011-11-08 2011-11-08 비공비 혼합 냉매사이클 및 냉장고

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US13/661,662 Abandoned US20130111943A1 (en) 2011-11-08 2012-10-26 Non-azeotropic mixed refrigerant cycle and refrigerator equipped therewith

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US (1) US20130111943A1 (de)
EP (1) EP2592366A3 (de)
KR (1) KR20130050639A (de)
CN (1) CN103090602A (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150096325A1 (en) * 2013-10-03 2015-04-09 Whirlpool Corporation Refrigerators with a non-azeotropic mixtures of hydrocarbons refrigerants
US20160123537A1 (en) * 2013-07-26 2016-05-05 Bruker Biospin Corporation Flexible interface closed cycle cryocast with remotely located point of cooling
US20160282031A1 (en) * 2015-03-27 2016-09-29 Whirlpool Corporation Refrigerator with enhanced efficiency
US20190024948A1 (en) * 2016-01-15 2019-01-24 Lg Electronics Inc. Deep freezer
WO2021034133A1 (en) * 2019-08-21 2021-02-25 Lg Electronics Inc. Refrigerating apparatus using non-azeotropic mixed refrigerant
US11674732B2 (en) * 2018-08-31 2023-06-13 Samsung Electronics Co., Ltd. Refrigerator

Families Citing this family (4)

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Publication number Priority date Publication date Assignee Title
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
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

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Cited By (7)

* 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
US20150096325A1 (en) * 2013-10-03 2015-04-09 Whirlpool Corporation Refrigerators with a non-azeotropic mixtures of hydrocarbons refrigerants
US20160282031A1 (en) * 2015-03-27 2016-09-29 Whirlpool Corporation Refrigerator with enhanced efficiency
US20190024948A1 (en) * 2016-01-15 2019-01-24 Lg Electronics Inc. Deep freezer
US10782048B2 (en) * 2016-01-15 2020-09-22 Lg Electronics Inc. Deep freezer
US11674732B2 (en) * 2018-08-31 2023-06-13 Samsung Electronics Co., Ltd. Refrigerator
WO2021034133A1 (en) * 2019-08-21 2021-02-25 Lg Electronics Inc. Refrigerating apparatus using non-azeotropic mixed refrigerant

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KR20130050639A (ko) 2013-05-16
CN103090602A (zh) 2013-05-08
EP2592366A2 (de) 2013-05-15
EP2592366A3 (de) 2014-06-18

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