EP1804011A2 - Réfrigérateur - Google Patents

Réfrigérateur Download PDF

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Publication number
EP1804011A2
EP1804011A2 EP06011847A EP06011847A EP1804011A2 EP 1804011 A2 EP1804011 A2 EP 1804011A2 EP 06011847 A EP06011847 A EP 06011847A EP 06011847 A EP06011847 A EP 06011847A EP 1804011 A2 EP1804011 A2 EP 1804011A2
Authority
EP
European Patent Office
Prior art keywords
suction pipe
pipe
refrigerant
heat
condensing
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Withdrawn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
EP06011847A
Other languages
German (de)
English (en)
Other versions
EP1804011A3 (fr
Inventor
Hyoung Keun Lim
Sung Jhee
Nam Soo Cho
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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 LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP1804011A2 publication Critical patent/EP1804011A2/fr
Publication of EP1804011A3 publication Critical patent/EP1804011A3/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Withdrawn legal-status Critical Current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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00—General constructional features
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle

Definitions

  • the present invention relates to a refrigerator, and more particularly, to a refrigerator having an improved cooling cycle that can reduce the power consumption and improve a coefficient of performance (COP) by efficiently using thermal energy wasted during a refrigerant is introduced into an expansion valve through a condenser.
  • COP coefficient of performance
  • a refrigerator is an electrical appliance for cooling or freezing food to preserve the food.
  • the refrigerator can be classified into a top mount refrigerator in which a freezing chamber and a chilling chamber are partitioned up and down, a bottom freezer refrigerator in which a freezing chamber and a cooling chamber are partitioned down and up, a side-by-side refrigerator in which a freezing chamber and a cooling chamber are partitioned left and right.
  • the side-by-side refrigerator has a freezing and cooling chamber doors that are opened toward both sides.
  • the side-by-side has a relatively volume compared with other types and a variety of functions. Therefore, the side-by-side refrigerators have been widely used in recent years.
  • a refrigerant flowing along a pipe connecting the condenser to a capillary maintains a temperature of about 40-45°C while a refrigerant flowing along a suction pipe connecting a vaporizer to a compressor maintains a temperature of about -25--30°C.
  • a portion of the suction pipe is designed to contact the capillary. That is, when the heat is transferred from the capillary to the suction pipe, a temperature of the suction pipe increases to pre-heat the refrigerant directing toward the compressor, thereby reducing the compressing work. The reduction of the compressing work increases the COP and reduces the electric power consumption.
  • the present invention is directed to a refrigerator that substantially obviates one or more problems due to limitations and disadvantages of the related art.
  • An object of the present invention is to provide a refrigerator having an improved cooling cycle that can reduce the power consumption and improve a coefficient of performance (COP) by efficiently using thermal energy wasted during a refrigerant is introduced into an expansion valve through a condenser.
  • COP coefficient of performance
  • a refrigerator including: a compressor for compressing a refrigerant; a condenser for heat-exchanging the compressed refrigerant with ambient air; an expansion member for expanding the heat-exchanged refrigerant; a condensing pipe interconnecting the condenser and the expansion member; a vaporizer for heat-exchanging the expanded refrigerant with a cool air in a freezing or cooling chamber; and a suction pipe interconnecting the vaporizer and the compressor and associated with the condensing pipe to allow a heat exchange between the suction pipe and the condensing pipe.
  • a refrigerator including: a compressor for compressing a refrigerant; a condenser for condensing the compressed refrigerant with ambient air; an expanding valve for expanding the condensed refrigerant; and a vaporizer for heat-exchanging the expanded refrigerant with cool air of a freezing or cooling chamber, wherein a portion of a suction pipe connected to an inlet of the compressor contacts a portion of a condensing pipe connected to an outlet of the condenser to allow for a heat exchange between the suction pipe and the condensing pipe.
  • a refrigerator comprising: a suction pipe interconnecting a vaporizer and a compressor; an expansion member heat-exchanging with a refrigerant flowing along the suction pipe; and a condensing pipe heat-exchanging with the refrigerant flowing along the suction pipe at an inlet of the expansion member.
  • a refrigerator comprising: pipes connected to each other such that a refrigerant flowing toward an inlet of a compressor after passing through a vaporizer can be heat-exchanged but not mixed with a refrigerant passing through an expansion member and/or a refrigerant passed through a condenser.
  • the waste heat discharged from the refrigerant passed through the condenser is efficiently used during the compression process, thereby reducing the compressing work and increasing the COP.
  • the heat exchange area increases to improve the space efficiency of the machine room, thereby reducing the overall volume of the refrigerator.
  • FIG. 1 is a schematic view of a cooling system of a refrigerator according to an embodiment of the present invention
  • FIG. 2 is a perspective view of a second heat-exchanging portion formed on a portion of a suction pipe contacting a condensing pipe in a cooling cycle according to an embodiment of the present invention.
  • FIG. 3 is a P-H diagram illustrating a phase variation of a refrigerant during the cooling system of the present invention is operated.
  • FIG. 1 is a schematic view of a cooling system of a refrigerator according to an embodiment of the present invention.
  • a refrigerator 10 having a cooling system includes a condensing pipe along which a refrigerant passed through a condenser flows and a suction pipe along which a refrigerant introduced into the compressor flows.
  • the condensing pipe and a suction pipe contact each other to perform the heat exchange.
  • the refrigerator 10 includes a compressor 11 for compressing the refrigerant, a condenser 12 into which the refrigerant compressed with a high temperature and a high pressure by the compressor 11 is introduced, a capillary 14 for cooling the high temperature and high pressure refrigerant passed through the condenser 12 to a low temperature and a low pressure, a vaporizer 15 into which the refrigerant, which is converted into a two-phase state (a liquid phase and a vapor phase) while passing through the capillary 14, is introduced to heat-exchange with cool air of the freezing and cooling chambers, and a phase separator 16 for separating the refrigerant passed through the vaporizer 15 into vapor and liquid.
  • the refrigerator 10 further includes a dryer 13 interposed between the condenser 12 and the capillary 14, a condensing pipe 17 interconnecting the condenser 11 to the dryer 13, and a suction pipe 18 connecting the phase separator 16 to the compressor 11.
  • the suction pipe 18 has a first heat-exchanging portion 191 contacting the capillary 14 for the heat-exchange and a second heat-exchanging portion 192 contacting the condensing pipe 17 for the heat-exchange.
  • the suction pipe 18 receives heat from the capillary 14 and the condenser pipe 17 to increase the temperature of the refrigerant flowing toward the compressor 11.
  • the compressing work of the compressor is reduced.
  • the temperature of the refrigerant is reduced at the inlet of the vaporizer 15. Therefore, an amount of the heat-exchange between the cool air in the refrigerator and the refrigerant in the vaporizer 15 increases. As a result, the time for reducing the cool air to a target temperature is reduced.
  • the refrigerant flowing along the condensing pipe 17 releases its heat to the suction pipe 18, thereby increasing an amount of the refrigerant that is liquefied. Therefore, the change of success for introducing air into the capillary 14 is reduced as compared to the prior art refrigerator.
  • FIG. 2 is a perspective view of a second heat-exchanging portion formed on a portion of the suction pipe contacting the condensing pipe in the cooling cycle according to an embodiment of the present invention.
  • the second heat exchange portion 192 is formed by a helix or spiral contact between the condensing pipe 17 and the suction pipe 18.
  • each length of the condensing and suction pipes 17 and 18 is about 80-100cm. Therefore, when the condensing pipe 17 contacts the suction pipe linearly, it is difficult to take a space for the pipes 17 and 18 in a machine room. To solve this problem, the pipes 17 and 18 are coiled in the helix or spiral shape.
  • the length of the pipes 17 and 18 is reduced to 10-12cm that is almost identical to that of the dryer 13. Therefore, the space for receiving the second heat-exchanging portion 192 in the machine room can be sufficiently obtained.
  • the contacting portion between the condensing pipe 17 and the suction pipe 18 may be spirally coiled or bent or curved at a plurality of locations.
  • the condensing pipe 17 may extends through the inside of the suction pipe 18.
  • the refrigerant of the suction pipe 18 flows in a direction opposite to that where the refrigerant of the condensing pipe 17 flows to enhance the heat exchange efficiency.
  • the waste heat discharged through the condensing pipe 17 is fully transferred to the refrigerant flowing along the suction pipe 18, thereby increasing the thermal transfer rate up to 100% and thus dramatically reducing the electric power consumption as compared to the case where the suction and condensing pipe contact each other at their outer surfaces.
  • the contacting area between the condensing and suction pipes 17 and 18 can increase to the maximum level in the limited machine room by properly adjusting a diameter of the helix.
  • FIG. 3 is a P-H diagram illustrating a phase variation of the refrigerant during the cooling system of the present invention is operated.
  • the refrigerant is compressed to a high temperature and high pressure by the compressor 11.
  • the compressed refrigerant flows into the condenser 12 to be phase-changed into liquid by heat exchange with ambient air.
  • the liquid refrigerant passed through the condenser 12 is directed to the capillary 14 via the dryer 13.
  • moisture contained in the refrigerant flowing into the capillary 14 is eliminated by the dryer.
  • the refrigerant introduced into the capillary 14 is phase-changed into two-phase state (i.e., vapor and liquid states) with a low temperature and low pressure through a throttling process. Then, the two-phase refrigerant is introduced into the vaporizer 15 and heat-exchanged with the cool air of the freezing or cooling chambers. A part of the refrigerant is phase-changed from a liquid-phase into a vapor-phase by the heat transferred from the cool air in the freezing or cooling chambers. Then, the refrigerant passed through the vaporizer 15 passes through the phase-separator, in the course of which the liquid is filtered. Therefore, only the liquid refrigerant is reintroduced into the compressor 11.
  • two-phase state i.e., vapor and liquid states
  • a heat exchange between the refrigerants is realized by the heat conduction at the first heat-exchanging portion 191 where the suction pipe 18 contacts the capillary 14.
  • an additional heat exchange between the refrigerants is realized by the heat conduction at the second heat-exchanging portion 192 where the suction pipe 18 contacts the condensing pipe 17.
  • Vaporizing Heat[(q in ) ideal ] h a - h d .
  • Vaporizing Heat[(q in ) real ] h a - h g
  • Vaporizing Heat[(q in ) present ] h a - h k .
  • the compression work can be dramatically reduced depending on a contacting length of the condensing pipe 17 and the suction pipe 18 as compared to the prior art cooling cycle.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP06011847A 2006-01-03 2006-06-08 Réfrigérateur Withdrawn EP1804011A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020060000375A KR100785116B1 (ko) 2006-01-03 2006-01-03 냉장고

Publications (2)

Publication Number Publication Date
EP1804011A2 true EP1804011A2 (fr) 2007-07-04
EP1804011A3 EP1804011A3 (fr) 2010-12-08

Family

ID=37895973

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06011847A Withdrawn EP1804011A3 (fr) 2006-01-03 2006-06-08 Réfrigérateur

Country Status (4)

Country Link
US (1) US20070180853A1 (fr)
EP (1) EP1804011A3 (fr)
KR (1) KR100785116B1 (fr)
CN (1) CN1995877A (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022161841A1 (fr) * 2021-02-01 2022-08-04 BSH Hausgeräte GmbH Appareil frigorifique

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20071419A1 (it) * 2007-07-16 2009-01-17 Ilpea Ind Spa Circuito di raffreddamento
CN103851853A (zh) * 2014-03-28 2014-06-11 合肥华凌股份有限公司 一种换热器及使用该换热器的冰箱
CN104729134A (zh) * 2015-04-07 2015-06-24 合肥华凌股份有限公司 用于冰箱的制冷系统和具有其的冰箱
DE112017000376T5 (de) * 2016-01-15 2018-09-27 Lg Electronics Inc. Tiefkühlschrank
CN105758046A (zh) * 2016-04-28 2016-07-13 浙江和利制冷设备有限公司 超低温触摸屏拆分装置及其工作原理
KR102658801B1 (ko) * 2017-02-02 2024-04-19 엘지전자 주식회사 차량용 냉장고, 및 차량
CN109869973B (zh) * 2017-12-05 2022-03-29 松下电器产业株式会社 冷冻冷藏库
KR20210022932A (ko) 2019-08-21 2021-03-04 엘지전자 주식회사 비공비혼합냉매를 사용하는 냉동시스템
KR20220016648A (ko) 2020-08-03 2022-02-10 엘지전자 주식회사 냉각 사이클
US11828504B2 (en) * 2020-09-21 2023-11-28 Whirlpool Corporation Heat exchanger for an appliance
CN112556276A (zh) * 2020-12-14 2021-03-26 海信（山东）冰箱有限公司 制冷系统及冷柜
CN112856588B (zh) * 2021-01-22 2022-11-15 青岛海尔空调器有限总公司 空调室内机和空调器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2434118A (en) * 1945-07-18 1948-01-06 Gen Electric Restrictor tube for refrigerating systems
FR1516944A (fr) * 1967-01-20 1968-02-05 Siemens Elektrogeraete Gmbh Machine frigorifique à compresseur incorporée à un réfrigérateur à isolement par mousse plastique
WO2001057454A1 (fr) * 2000-02-07 2001-08-09 Andrzej Sokulski Appareil frigorifique
WO2002025179A1 (fr) * 2000-09-25 2002-03-28 Temppia Co., Ltd Cycle de refrigeration
US6848268B1 (en) * 2003-11-20 2005-02-01 Modine Manufacturing Company CO2 cooling system
EP1577619A1 (fr) * 2002-12-03 2005-09-21 Nihon Freezer Co., Ltd. Systeme refrigerant a melange non-azeotrope, et melange non-azeotrope pour tres basses temperatures utilise pour ce systeme

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2099493A (en) * 1936-06-16 1937-11-16 Vogt & Co Inc Henry Double pipe heat exchanger
JPH0375475A (ja) * 1989-05-16 1991-03-29 Mitsubishi Electric Corp 冷蔵庫
JPH1019418A (ja) 1996-07-03 1998-01-23 Toshiba Corp 冷凍冷蔵庫
JP2003021473A (ja) 2001-07-03 2003-01-24 Nihon Freezer Kk 非共沸冷媒を用いた冷凍循環システム用熱交換器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2434118A (en) * 1945-07-18 1948-01-06 Gen Electric Restrictor tube for refrigerating systems
FR1516944A (fr) * 1967-01-20 1968-02-05 Siemens Elektrogeraete Gmbh Machine frigorifique à compresseur incorporée à un réfrigérateur à isolement par mousse plastique
WO2001057454A1 (fr) * 2000-02-07 2001-08-09 Andrzej Sokulski Appareil frigorifique
WO2002025179A1 (fr) * 2000-09-25 2002-03-28 Temppia Co., Ltd Cycle de refrigeration
EP1577619A1 (fr) * 2002-12-03 2005-09-21 Nihon Freezer Co., Ltd. Systeme refrigerant a melange non-azeotrope, et melange non-azeotrope pour tres basses temperatures utilise pour ce systeme
US6848268B1 (en) * 2003-11-20 2005-02-01 Modine Manufacturing Company CO2 cooling system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022161841A1 (fr) * 2021-02-01 2022-08-04 BSH Hausgeräte GmbH Appareil frigorifique

Also Published As

Publication number Publication date
EP1804011A3 (fr) 2010-12-08
KR100785116B1 (ko) 2007-12-11
US20070180853A1 (en) 2007-08-09
KR20070089260A (ko) 2007-08-31
CN1995877A (zh) 2007-07-11

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