EP1512925A2 - Verflüssiger - Google Patents

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Publication number
EP1512925A2
EP1512925A2 EP04077385A EP04077385A EP1512925A2 EP 1512925 A2 EP1512925 A2 EP 1512925A2 EP 04077385 A EP04077385 A EP 04077385A EP 04077385 A EP04077385 A EP 04077385A EP 1512925 A2 EP1512925 A2 EP 1512925A2
Authority
EP
European Patent Office
Prior art keywords
super
region
refrigerant
condenser
phase
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Withdrawn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
EP04077385A
Other languages
English (en)
French (fr)
Other versions
EP1512925A3 (de
Inventor
Soo Hong Ki
Won Chin Sim
Su Moon Dong
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 EP1512925A2 publication Critical patent/EP1512925A2/de
Publication of EP1512925A3 publication Critical patent/EP1512925A3/de
Withdrawn legal-status Critical Current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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F25B40/02—Subcoolers

Definitions

  • the present invention relates to a condenser, and more particularly to a condenser outputting a refrigerant to a super-cooled liquid region by combining a plurality of refrigerant paths on at least one of a super-heated vapor region and a two-phase region in the condenser where the refrigerant introduced from a compressor coexists in super-heated vapor, two-phase, and super-cooled liquid states, and providing a proper percentage of the super-cooled liquid region.
  • Fig. 1 shows a main engine of a general compression refrigerating cycle.
  • an air conditioner, etc. exerts its performance by cooled air which is generated by the compression refrigerating cycle.
  • the compression refrigerating cycle is completed by a compressor 5 converting a gas refrigerant of low-temperature and low pressure into a gas refrigerant of high-temperature and high-pressure, a condenser 1 converting the gas refrigerant of high-temperature and high-pressure into a liquid refrigerant of middle-temperature and high-pressure, an expansion valve 3 converting the liquid refrigerant of middle-temperature and high-pressure into a liquid refrigerant of low-temperature and low-pressure, and an evaporator 4 converting the liquid refrigerant of low-temperature and low-pressure into the gas refrigerant of low-temperature and low pressure.
  • the condenser 1 is provided with a cooling fan 2 in order to supply external or outdoor air.
  • the condenser 1 supplied with the gas refrigerant of high-temperature and high-pressure from the compressor 5 converting it into the liquid refrigerant of middle-temperature and high-pressure, and to transfers the converted result to the expansion valve 3.
  • an actuating fluid undergoes a state change in the order of a vapor state and a two-phase state in the condenser 1.
  • the gas has avolume 1000 times as much as the liquid has, and thus has a flow speed about 1000 times.
  • the pressure drop is generated, and the compressor 5 performs more work.
  • a tube is branched off.
  • either the vapor or the two-phase fluid has faster velocity of a flow than that of the liquid. Therefore, it is more advantageous to flow through a plurality of tubes divided, i . e . branched off, than to continuously flow through a single tube.
  • the pressure drop becomes reduced.
  • the meaning that the pressure drop is reduced means that a work which a compressor performs is reduced so much, consumption electric power of the compressor is reduced.
  • the liquid has a slower flow velocity and has merely one tenth of a thermal conductivity as compared to the vapor or the two-phase fluid, so that it is no necessary to flow with dispersion.
  • the tube is branched off or the tubes are combined It is a super-cooled tube that is used for this purpose.
  • Fig. 2 shows a process where a refrigerant is introduced into a condenser and then outputted through a super-heated vapor region, a two-phase region and a super-cooled liquid region.
  • the refrigerants branched and then introduced into the super-heated vapor region pass through respective two-phase regions and then are outputted through respective super-cooled liquid regions as they are branched.
  • the liquid within the super-cooled liquid region is not required to flow with dispersion due to the slow flow velocity and the low thermal conductivity having merely one tenth over the two-phase region, the liquid is outputted through each tube, so that the liquid (or super-cooled) region is increased and so the two-phase region having good thermal conductivity is decreased. Consequently, the heat exchanger having the given size results in deteriorating performance and increasing the consumption electric power.
  • An object of the invention is to solve at least the above problems and/or disadvantages and to provide at least the advantages described hereinafter.
  • one objective of the present invention is to increase a two-phase region having good heat transmission on a path where a gas refrigerant introduced into a condenser is heat-exchanged, and to provide a proper percentage of a super-cooled liquid region capable of enhancing refrigerating capability and a coefficient of performance.
  • Yet another objective of the present invention to further provide a super-cooled liquid region in a condenser performing a compression refrigerating cycle to thereby increase refrigerating capability in a refrigerating system such as an air conditioner.
  • an apparatus including a compressor and a condenser where a refrigerant introduced from the compressor is coexisting in super-heated vapor, two-phase and super-cooled liquid states, providing the condenser combining a plurality of refrigerant paths within at least one of super-heated vapor and two-phase regions to extend to a super-cooled liquid region formed at a rear end portion of the two-phase region.
  • the super-cooled liquid region of the condenser has a percentage ranging from 7% to 20% of the refrigerant path region.
  • the refrigerant is outputted to the super-cooled liquid region through the combined refrigerant path, so that the two-phase region having good heat transmission is substantially increased. Further, the super-cooled liquid region is provided at a proper percentage, so that a super-cooled degree is increased to thereby enhance performance of an air conditioner and to reduce its consumption electric power.
  • Fig. 1 illustrates main components of a general compression refrigerating cycle
  • Fig. 2 illustrates a process where a refrigerant is introduced into a condenser a nd then outputted through super-heated vapor, two-phase, and super-cooled liquid regions;
  • Fig. 3 is a block diagram schematically showing a structure including a condenser according to the invention.
  • Fig. 4 shows a state of a refrigerant, and path and region through which the refrigerant passes in a condenser; and Fig. 5 shows graph and table showing relation between a super-cooled tube and a coefficient of performance (COP).
  • COP coefficient of performance
  • Fig. 3 is a block diagram schematically illustrating a structure including a condenser according to the present invention
  • Figs. 4A and 4B show a state of a refrigerant in the condenser, and path and region through which the refrigerant passes
  • Fig. 5 is graph and table showing relation between a super-cooled tube and a coefficient of performance.
  • a refrigerant outputted from an indoor unit is branched off into one or more paths through a service valve and a discharge valve of a compressor, and then inputted into a condenser 1.
  • the branched paths of the invention pass through tubes of super-heated vapor and two-phase regions and are combined into a tube of a super-cooled liquid region.
  • the tube for the super-cooled liquid region has a proper percentage of 7-20% of the total length of the tubes.
  • C OP coefficient of performance
  • a working fluid is subjected to change of its state into vapor, two-phase and liquid in that order.
  • the liquid has a volume of about 1/1000 as compared with the gas, thus having a flow velocity of only about 1/1000. For this reason, it will do if the liquid is not branched off.
  • Figs. 4A and 4B show a process where the refrigerant is introduced into the condenser through a plurality of paths (e.g. two or three paths) and outputted through the super-heated vapor region, the two-phase region and the super-cooled liquid region in the invention.
  • a plurality of paths e.g. two or three paths
  • the refrigerants branched and introduced into the super-heated vapor region each pass through the two-phase regions to flow into the super-cooled liquid region on the combined refrigerant path, and then outputted to the expansion valve (main LEV of Fig. 3).
  • the tube for the super-cooled liquid region has a proper percentage when amounting to 7-20% of the length of the whole tubes.
  • the air conditioner has the highest COP and performance of the consumption electric power.
  • Figs. 5A and 5B are a graph and table showing relation between the super-cooled tube and the COP.
  • Fig. 3 the number of the whole tubes within the condenser 1 is set to have two rows and 26 steps.
  • a test shows the relation between the super-cooled tube of the whole tubes and the COP.
  • the consumption electric power used was measured to be 569W, while capability of refrigeration was measured to be 2692W.
  • the COP was 4.73.
  • the consumption electric power used was measured to be 567W, while capability of refrigeration was measured to be 2745W.
  • the COP was 4.84, which was a little increased compared to the super-cooled tube arranged in two steps.
  • the consumption electric power used was measured to be 586W, while capability of refrigeration was measured to be 2726W.
  • the COP was 4.65, which was decreased a gain compared to the super-cooled tube arranged in two steps.
  • the COP can be obtained to the optimal level.
  • the refrigerant paths of the two-phase region are combined to extend to the super-cooled liquid region, and the proper percentage of the super-cooled liquid region is represented, so that the two-phase region is increased. Consequently, it is possible to enhance the efficiency of heat transmission and the COP and to reduce the consumption electric power.
  • the invention may be applicable to a refrigerator performing condensation and other products performing the similar function.

Landscapes

  • 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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
EP04077385A 2003-09-02 2004-08-23 Verflüssiger Withdrawn EP1512925A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR2003061149 2003-09-02
KR1020030061149A KR20050023758A (ko) 2003-09-02 2003-09-02 응축기

Publications (2)

Publication Number Publication Date
EP1512925A2 true EP1512925A2 (de) 2005-03-09
EP1512925A3 EP1512925A3 (de) 2007-12-26

Family

ID=34132223

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04077385A Withdrawn EP1512925A3 (de) 2003-09-02 2004-08-23 Verflüssiger

Country Status (5)

Country Link
US (1) US20050044882A1 (de)
EP (1) EP1512925A3 (de)
JP (1) JP2005077088A (de)
KR (1) KR20050023758A (de)
CN (1) CN100494814C (de)

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KR100490722B1 (ko) 2004-07-23 2005-05-19 엘지전자 주식회사 냉장고의 응축기
KR100710352B1 (ko) 2004-11-23 2007-04-23 엘지전자 주식회사 공기조화기의 냉매 바이패스 여과장치 및 그 제어방법
US7365973B2 (en) 2006-01-19 2008-04-29 American Power Conversion Corporation Cooling system and method
US8672732B2 (en) 2006-01-19 2014-03-18 Schneider Electric It Corporation Cooling system and method
US8322155B2 (en) 2006-08-15 2012-12-04 American Power Conversion Corporation Method and apparatus for cooling
US8327656B2 (en) * 2006-08-15 2012-12-11 American Power Conversion Corporation Method and apparatus for cooling
US9568206B2 (en) 2006-08-15 2017-02-14 Schneider Electric It Corporation Method and apparatus for cooling
US7681404B2 (en) 2006-12-18 2010-03-23 American Power Conversion Corporation Modular ice storage for uninterruptible chilled water
US8425287B2 (en) 2007-01-23 2013-04-23 Schneider Electric It Corporation In-row air containment and cooling system and method
AU2008255030B2 (en) 2007-05-15 2014-02-20 Schneider Electric It Corporation Methods and systems for managing facility power and cooling
US8219362B2 (en) 2009-05-08 2012-07-10 American Power Conversion Corporation System and method for arranging equipment in a data center
US8688413B2 (en) 2010-12-30 2014-04-01 Christopher M. Healey System and method for sequential placement of cooling resources within data center layouts
US9830410B2 (en) 2011-12-22 2017-11-28 Schneider Electric It Corporation System and method for prediction of temperature values in an electronics system
WO2013095516A1 (en) 2011-12-22 2013-06-27 Schneider Electric It Corporation Analysis of effect of transient events on temperature in a data center
CN102798203B (zh) * 2012-08-29 2014-08-27 海信（山东）空调有限公司 空调室外机冷凝器及安装有该冷凝器的空调室外机
US9791221B1 (en) * 2012-10-30 2017-10-17 Whirlpool Corporation Condenser assembly system for an appliance
CN102954626B (zh) * 2012-11-08 2015-07-08 南京师范大学 一种同步换热的多支路室内换热器
JP6351494B2 (ja) * 2014-12-12 2018-07-04 日立ジョンソンコントロールズ空調株式会社 空気調和機
CN105987539B (zh) * 2015-02-03 2018-09-18 上海海立电器有限公司 空调器及其换热器
JP6573484B2 (ja) * 2015-05-29 2019-09-11 日立ジョンソンコントロールズ空調株式会社 熱交換器
CN106322853B (zh) * 2015-06-30 2019-02-05 青岛海尔空调器有限总公司 一种单冷式冷凝器管路系统、空调器及其使用方法
CN105972845A (zh) * 2016-03-16 2016-09-28 合肥天鹅制冷科技有限公司 节能经济耐高温空调制冷系统
CN107300266B (zh) * 2017-06-12 2019-10-15 广东美的制冷设备有限公司 空调系统、空调系统的控制方法
JPWO2019106755A1 (ja) * 2017-11-29 2020-07-02 三菱電機株式会社 空気調和機

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0374895A2 (de) * 1988-12-22 1990-06-27 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Verflüssiger für ein Kältemittel einer Fahrzeugklimaanlage
US5224358A (en) * 1990-10-04 1993-07-06 Nippondenso Co., Ltd. Refrigerating apparatus and modulator
JPH109714A (ja) * 1996-06-25 1998-01-16 Hitachi Ltd 冷凍装置
FR2754886A1 (fr) * 1996-10-23 1998-04-24 Valeo Thermique Moteur Sa Condenseur a tube serpentin pour circuit de refrigeration, notamment de vehicule automobile
JPH10141884A (ja) * 1996-11-13 1998-05-29 Daikin Ind Ltd 熱交換器

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JP3301169B2 (ja) * 1992-11-06 2002-07-15 株式会社デンソー 冷凍装置
DE4238853C2 (de) * 1992-11-18 2001-05-03 Behr Gmbh & Co Kondensator für eine Klimaanlage eines Fahrzeuges
JP3116996B2 (ja) * 1996-10-30 2000-12-11 株式会社デンソー 受液器一体型冷媒凝縮器
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KR100264815B1 (ko) * 1997-06-16 2000-09-01 신영주 다단기액분리형응축기
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DE19918616C2 (de) * 1998-10-27 2001-10-31 Valeo Klimatechnik Gmbh Verflüssiger zum Kondensieren des inneren Kältemittels einer Kraftfahrzeugklimatisierung
JP2002031436A (ja) * 2000-05-09 2002-01-31 Sanden Corp サブクールタイプコンデンサ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0374895A2 (de) * 1988-12-22 1990-06-27 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Verflüssiger für ein Kältemittel einer Fahrzeugklimaanlage
US5224358A (en) * 1990-10-04 1993-07-06 Nippondenso Co., Ltd. Refrigerating apparatus and modulator
JPH109714A (ja) * 1996-06-25 1998-01-16 Hitachi Ltd 冷凍装置
FR2754886A1 (fr) * 1996-10-23 1998-04-24 Valeo Thermique Moteur Sa Condenseur a tube serpentin pour circuit de refrigeration, notamment de vehicule automobile
JPH10141884A (ja) * 1996-11-13 1998-05-29 Daikin Ind Ltd 熱交換器

Also Published As

Publication number Publication date
EP1512925A3 (de) 2007-12-26
CN100494814C (zh) 2009-06-03
JP2005077088A (ja) 2005-03-24
KR20050023758A (ko) 2005-03-10
CN1590924A (zh) 2005-03-09
US20050044882A1 (en) 2005-03-03

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