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WO2002042695A1 - Systeme de pompe de refrigeration ou de chauffage avec rejet de chaleur sous pression supercritique - Google Patents

Systeme de pompe de refrigeration ou de chauffage avec rejet de chaleur sous pression supercritique Download PDF

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Publication number
WO2002042695A1
WO2002042695A1 PCT/NO2001/000454 NO0100454W WO0242695A1 WO 2002042695 A1 WO2002042695 A1 WO 2002042695A1 NO 0100454 W NO0100454 W NO 0100454W WO 0242695 A1 WO0242695 A1 WO 0242695A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
air flow
air
heat exchanger
refrigerant
Prior art date
Application number
PCT/NO2001/000454
Other languages
English (en)
Inventor
Kåre AFLEKT
Arne Bredesen
Armin Hafner
Petter NEKSÅ
Jostein Pettersen
Håvard REKSTAD
Geir Skaugen
Sivert Vist
Gholam Reza Zakeri
Original Assignee
Sinvent As
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 Sinvent As filed Critical Sinvent As
Priority to EP01983872A priority Critical patent/EP1340027A1/fr
Priority to KR10-2003-7006982A priority patent/KR20030065524A/ko
Priority to US10/432,228 priority patent/US20040069013A1/en
Priority to JP2002544591A priority patent/JP2004514868A/ja
Priority to CA002429857A priority patent/CA2429857A1/fr
Priority to AU2002215268A priority patent/AU2002215268A1/en
Publication of WO2002042695A1 publication Critical patent/WO2002042695A1/fr
Priority to NO20032343A priority patent/NO20032343L/no

Links

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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • 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
    • 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
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25D23/003—General constructional features for cooling refrigerating machinery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure

Definitions

  • the present invention relates to refrigerating or heat pump systems, in particular to refrigerating systems for retail and/or storage cabinets for cooling or freezing of food or beverages, or heat pumps for building heating, in both cases using carbon dioxide as the refrigerant.
  • Refrigerating systems for cooling or freezing cabinets usually have a refrigerant that operates in a vapour compression cycle with evaporation and condensation.
  • the refrigerant is chosen so that its critical temperature is well below the required heat rejection (condensing) temperature.
  • a relatively high air flow rate is required, with large space requirements for the condenser and the air flow system.
  • a fan is needed in most systems to circulate air over the condenser.
  • One problem with this solution is the relatively large power requirement for the fan, and the additional space requirements for the fan and its air flow system.
  • the forced air flow and the fan and its motor may also result in noise problems, and the installation of a fan gives added cost and complexity to the system.
  • Refrigerants in present refrigerating or heat pump systems are either fluorocarbon-based chemicals that are undesirable due to ozone-depleting properties and/or their contribution to man-made climate change, or they are flammable hydrocarbon-based fluids that are questioned due to safety concerns.
  • the air flow rate may be reduced and the air outlet temperature increased compared to the situation in a condenser.
  • the air outlet temperature necessarily has to be below the condensing temperature.
  • the high air temperature and reduced air flow rate will be beneficial for natural convection air flow over the heat exchanger, it will reduce noise, and will also be advantageous with respect to thermal comfort in heat pump applications.
  • an object of the present invention to provide a refrigerating system that uses a safe and environmentally friendly refrigerant in a system with a compact natural air circulation heat rejection system without fan power requirements, or with only minor fan power in high load situations.
  • the present invention describes a system using the nonflammable, nontoxic and environmentally friendly fluid carbon dioxide (CO 2 ) as the refrigerant.
  • the invention is characterized in that the refrigerant rejects heat at a supercritical pressure with gliding temperature through a heat rejecting heat exchanger which is cooled by natural upwards circulation/convection of air as defined in the attached independent claim 1.
  • heat rejection may, as stated above, take place with natural convection flow of the air, with greatly reduced air flow rate and without the need for a special air circulation fan.
  • Fig. 1 shows a trans critical vapor compression system including a compressor, an air-cooled heat rejecting unit with natural air circulation, an expansion device and an evaporator connected in a closed circuit.
  • Fig. 2 shows a cross-sectional view of a heat rejecting unit with natural air circulation including an air flow conduit and a heat rejecting heat exchanger based on round tubes in an in line layout according to the invention.
  • Fig. 3 shows a cross-sectional view of a heat rejecting unit with natural air circulation including an air flow conduit and a heat rejecting heat exchanger based on round tubes in a staggered layout according to a second embodiment of the invention.
  • Fig. 4 shows a side view of a heat rejecting unit with natural air circulation having an air flow conduit and a heat rejecting heat exchanger based on folded tubes according to a third embodiment of the invention.
  • Fig. 5 shows a cross-sectional view of a heat rejecting unit with an air flow conduit and a heat rejecting heat exchanger formed into a spiral geometry according to a fourth embodiment of the invention,.
  • Fig. 6 shows a heat rejecting unit where the tubes are attached to a plate to increase the air-side heat transfer surface according to a fifth embodiment of the invention.
  • Fig. 7 shows a fully counter-flow heat rejecting unit with natural air circulation using
  • Multi Port Extruded (MPE) heat exchanger with plate fin extended surface on one or both side of the said heat exchanger.
  • Fig. 8 shows example of the embodiment according to claim 5 used in a refrigerator or similar devices.
  • Fig.l shows an example of a vapor compression system including a compressor 20, air- cooled heat rejecting unit 21, expansion device 22 and evaporator 23.
  • the components are connected in a closed circuit that operates in a trans critical vapor compression cycle, i.e. with super critical high-side pressure.
  • the heat rejecting heat exchanger 21 is cooled by natural upwards circulation/convection of air.
  • Fig. 2 shows a cross-sectional view of a heat rejecting unit with an air flow conduit or outer air flow shell or jacket 11 and heat exchanger tubes 10.
  • the tubes are arranged in line above one each another within the shell 11. Air enters at the inlet i in the lower end of the system, and exits at the outlet o at the top. Air circulation is achieved by natural convection when the air is heated by the heat exchanger tubes. High-temperature refrigerant from the compressor enters through the heat exchanger refrigerant inlet 12 and flows through the heat exchanger while rejecting heat to the air whereby an efficient chimney effect is achieved. The cooled refrigerant exits from the heat exchanger through the outlet 13.
  • conduit 11a may be added above the heat exchanger, to increase the chimney effect.
  • the "chimney” or stack may also be built with a converging and diverging nozzle cross section, in order to improve air flow.
  • the heat transfer tubes 10 may also be arranged in a staggered fashion inside the flow conduit, to increase the surface and improve the heat transfer.
  • Fig. 4 shows a side view of a natural air circulation heat rejecting unit with air flow conduit 11 and a heat exchanger based on folded tubes 10.
  • the refrigerant should flow in a generally counter current direction to the air. With refrigerant inlet at the top 12 and outlet at the bottom, 13 as indicated in the figure the desired relationship between the two different air and refrigerant flows is achieved.
  • FIG. 5 Another possible embodiment is shown in Fig. 5, where the air flow conduit 11 has a circular cross-section, and the heat transfer tube 10 is formed into a spiral inside the air flow conduit 11.
  • an annulus containing the heat transfer tube may be established by inserting an inner circular tube into the conduit, the inserted tube being closed at the ends.
  • the heat transfer tube may form an integral part of the shell in a plate or a conduit 11, i.e. being built into the conduit or shell, in order to increase the heat transfer surface facing the air flow. If necessary, thermal conduction along the height of the conduit can be reduced or eliminated by having slots, splits or louvers 14 in the plate.
  • the shell plate or conduit may have a flat surface, or the surface may consist of vertical fins or open or closed duct-like structures that improve natural-convection air flow.
  • the invention as defined in the attached claims is not limited to the examples as shown in the figures and explained above, thus in all the above embodiments, one or several walls of the conduit or shell may be applied as heat transfer surface as well.
  • the heat transfer tube is shown with a circular cross section in the diagrams, any tube geometry may be used, including flat tubes, oval tubes, multi port tubes and more complex geometry.
  • the refrigerant tube may also be integrated into the air flow conduit material, giving an integral heat rejecting and air conduit unit which can also enhance heat transfer by radiation.
  • Several enhancements and exterior surface extensions are also possible for the heat transfer tube, including wires, fins, studs etc.
  • FIG 7 An example is shown in Fig 7 using Multi Port Extruded (MPE) heat exchanger with plate fin extended surface where high temperature refrigerant enters at the top and leaves from the bottom after being cooled by natural upwards circulation/convection of air in fully counter-flow heat exchange process which is ideal in such cases.
  • MPE Multi Port Extruded
  • Fig 8 shows example of the embodiment according to claim 5 used in a refrigerator or similar devices.
  • the heat exchanger 10 is placed in the bottom compartment, with the air flow conduit 11a behind the refrigerator, extending the air flow shell or jacket 11 in order to enhance the natural air flow/circulation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Geometry (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

Cette invention concerne un système de pompe de réfrigération ou de chauffage comprenant un évaporateur (23), un compresseur (20), un échangeur thermique (21) refroidi par air et rejetant de la chaleur, ainsi qu'un dispositif d'expansion (22) connecté en circuit fermé et fonctionnant selon un cycle à compression de vapeur transcritique. L'échangeur thermique à rejet de chaleur (21) est refroidi par la circulation/convection ascendante naturelle de l'air. Selon un mode de réalisation préféré, l'échangeur thermique (21) est construit dans une conduite ou un manchon d'air (11), ce qui favorise la circulation naturelle de l'air par effet de cheminée.
PCT/NO2001/000454 2000-11-24 2001-11-16 Systeme de pompe de refrigeration ou de chauffage avec rejet de chaleur sous pression supercritique WO2002042695A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP01983872A EP1340027A1 (fr) 2000-11-24 2001-11-16 Systeme de pompe de refrigeration ou de chauffage avec rejet de chaleur sous pression supercritique
KR10-2003-7006982A KR20030065524A (ko) 2000-11-24 2001-11-16 초임계 압력에서 열제거가 행해지는 냉각 또는 열펌프시스템
US10/432,228 US20040069013A1 (en) 2000-11-24 2001-11-16 Refrigerating or heat pump system with heat rejection at supercritical pressure
JP2002544591A JP2004514868A (ja) 2000-11-24 2001-11-16 超臨界圧での熱除去を用いる冷凍またはヒートポンプシステム
CA002429857A CA2429857A1 (fr) 2000-11-24 2001-11-16 Systeme de pompe de refrigeration ou de chauffage avec rejet de chaleur sous pression supercritique
AU2002215268A AU2002215268A1 (en) 2000-11-24 2001-11-16 Refrigerating or heat pump system with heat rejection at supercritical pressure
NO20032343A NO20032343L (no) 2000-11-24 2003-05-23 Kjole- eller varmepumpesystem med varmeavgivelse ved endring i temperatur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO20005974A NO20005974D0 (no) 2000-11-24 2000-11-24 Kjöle- eller varmepumpesystem med varmeavgivelse ved endring i temperatur
NO20005974 2000-11-24

Publications (1)

Publication Number Publication Date
WO2002042695A1 true WO2002042695A1 (fr) 2002-05-30

Family

ID=19911836

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NO2001/000454 WO2002042695A1 (fr) 2000-11-24 2001-11-16 Systeme de pompe de refrigeration ou de chauffage avec rejet de chaleur sous pression supercritique

Country Status (10)

Country Link
US (1) US20040069013A1 (fr)
EP (1) EP1340027A1 (fr)
JP (1) JP2004514868A (fr)
KR (1) KR20030065524A (fr)
CN (1) CN1250927C (fr)
AU (1) AU2002215268A1 (fr)
CA (1) CA2429857A1 (fr)
NO (1) NO20005974D0 (fr)
TW (1) TW528843B (fr)
WO (1) WO2002042695A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1521045A2 (fr) 2003-09-30 2005-04-06 Sanyo Electric Co., Ltd. Système de chauffage et de refroidissement
JP2005156093A (ja) * 2003-11-28 2005-06-16 Daikin Ind Ltd 空気調和装置
WO2008141626A1 (fr) * 2007-05-22 2008-11-27 Institut Für Luft- Und Kältetechnik Gemeinnützige Gmbh Condenseur de paroi arrière de réfrigérateurs de ménage
WO2012059344A3 (fr) * 2010-11-03 2012-10-26 BSH Bosch und Siemens Hausgeräte GmbH Échangeur thermique

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1853856A1 (fr) * 2005-02-18 2007-11-14 Carrier Corporation Dispositif de refrigeration au co2 avec recuperation de chaleur
US8925336B2 (en) * 2008-04-19 2015-01-06 Carrier Corporation Refrigerant system performance enhancement by subcooling at intermediate temperatures
JP5349655B1 (ja) * 2012-06-25 2013-11-20 株式会社 エコファクトリー 空気調和機のルームユニット
CN105737458A (zh) * 2016-03-14 2016-07-06 深圳智焓热传科技有限公司 自然散热换热器及其换热单元
EP3686535B1 (fr) * 2019-01-22 2024-03-06 Hitachi Energy Ltd Condensateur

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US1769119A (en) * 1928-01-06 1930-07-01 Chicago Pneumatic Tool Co Condensing system
GB540937A (en) * 1939-08-03 1941-11-06 Nils Erland Af Kleen Improvements in or relating to air cooled condensing systems for refrigerators
US2292033A (en) * 1941-08-01 1942-08-04 Gen Electric Refrigerant condenser and method of forming same
US5228311A (en) * 1990-08-16 1993-07-20 The Coca-Cola Company Cooling apparatus
WO1997018428A1 (fr) * 1995-11-13 1997-05-22 Bundy International Limited Echangeur thermique a serpentin
EP1046524A2 (fr) * 1999-04-23 2000-10-25 Valeo Klimatechnik GmbH Refroidisseur de gaz à haute pression pour un circuit frigorifique d'une climatisation de véhicule automobile
DE10043439A1 (de) * 1999-09-29 2001-04-05 Denso Corp Kühler für einen superkritischen Dampfverdichtungskältekreislauf

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US2105751A (en) * 1936-05-28 1938-01-18 Crosley Radio Corp Condenser device for refrigerators
US2344145A (en) * 1943-04-29 1944-03-14 Gen Motors Corp Refrigerating apparatus
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US2865182A (en) * 1956-09-21 1958-12-23 Temprite Products Corp Self-contained water cooler of the bubbler type
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US4972683A (en) * 1989-09-01 1990-11-27 Blackstone Corporation Condenser with receiver/subcooler
FR2704939B1 (fr) * 1993-05-06 1995-06-23 Valeo Thermique Habitacle Circuit de fluide réfrigérant à rendement amélioré.
JP3312067B2 (ja) * 1993-09-21 2002-08-05 ホシザキ電機株式会社 冷却装置
JPH11211250A (ja) * 1998-01-21 1999-08-06 Denso Corp 超臨界冷凍サイクル
JP4075129B2 (ja) * 1998-04-16 2008-04-16 株式会社豊田自動織機 冷房装置の制御方法
DE19830757A1 (de) * 1998-07-09 2000-01-13 Behr Gmbh & Co Klimaanlage
JP2000055488A (ja) * 1998-08-05 2000-02-25 Sanden Corp 冷凍装置
US6591618B1 (en) * 2002-08-12 2003-07-15 Praxair Technology, Inc. Supercritical refrigeration system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1769119A (en) * 1928-01-06 1930-07-01 Chicago Pneumatic Tool Co Condensing system
GB540937A (en) * 1939-08-03 1941-11-06 Nils Erland Af Kleen Improvements in or relating to air cooled condensing systems for refrigerators
US2292033A (en) * 1941-08-01 1942-08-04 Gen Electric Refrigerant condenser and method of forming same
US5228311A (en) * 1990-08-16 1993-07-20 The Coca-Cola Company Cooling apparatus
WO1997018428A1 (fr) * 1995-11-13 1997-05-22 Bundy International Limited Echangeur thermique a serpentin
EP1046524A2 (fr) * 1999-04-23 2000-10-25 Valeo Klimatechnik GmbH Refroidisseur de gaz à haute pression pour un circuit frigorifique d'une climatisation de véhicule automobile
DE10043439A1 (de) * 1999-09-29 2001-04-05 Denso Corp Kühler für einen superkritischen Dampfverdichtungskältekreislauf

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1521045A2 (fr) 2003-09-30 2005-04-06 Sanyo Electric Co., Ltd. Système de chauffage et de refroidissement
EP1521045A3 (fr) * 2003-09-30 2006-05-24 Sanyo Electric Co., Ltd. Système de chauffage et de refroidissement
US7487823B2 (en) 2003-09-30 2009-02-10 Sanyo Electric Co., Ltd. Heating and cooling system
JP2005156093A (ja) * 2003-11-28 2005-06-16 Daikin Ind Ltd 空気調和装置
WO2008141626A1 (fr) * 2007-05-22 2008-11-27 Institut Für Luft- Und Kältetechnik Gemeinnützige Gmbh Condenseur de paroi arrière de réfrigérateurs de ménage
WO2012059344A3 (fr) * 2010-11-03 2012-10-26 BSH Bosch und Siemens Hausgeräte GmbH Échangeur thermique

Also Published As

Publication number Publication date
US20040069013A1 (en) 2004-04-15
CA2429857A1 (fr) 2002-05-30
JP2004514868A (ja) 2004-05-20
CN1476524A (zh) 2004-02-18
NO20005974D0 (no) 2000-11-24
AU2002215268A1 (en) 2002-06-03
CN1250927C (zh) 2006-04-12
EP1340027A1 (fr) 2003-09-03
TW528843B (en) 2003-04-21
KR20030065524A (ko) 2003-08-06

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