US20040069013A1 - Refrigerating or heat pump system with heat rejection at supercritical pressure - Google Patents

Refrigerating or heat pump system with heat rejection at supercritical pressure Download PDF

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Publication number
US20040069013A1
US20040069013A1 US10/432,228 US43222803A US2004069013A1 US 20040069013 A1 US20040069013 A1 US 20040069013A1 US 43222803 A US43222803 A US 43222803A US 2004069013 A1 US2004069013 A1 US 2004069013A1
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US
United States
Prior art keywords
heat
air flow
air
heat exchanger
conduit
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
US10/432,228
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English (en)
Inventor
Kare Aflekt
Arne Bredesen
Armin Hafner
Petter Neksa
Jostein Pettersen
Havard Rekstad
Geir Skaugen
Sivert Vist
Gholan Zakeri
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Sinvent AS
Original Assignee
Sinvent AS
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Filing date
Publication date
Application filed by Sinvent AS filed Critical Sinvent AS
Assigned to SINVENT AS reassignment SINVENT AS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AFLEKT, KARE, BREDESEN, ARNE, HAFNER, ARMIN, NEKSA, PETTER, PETTERSEN, JOSTEIN, REKSTAD, HAVARD, SKAUGEN, GEIR, VIST, SIVERT, ZAKERI, GHOLAM REZA
Publication of US20040069013A1 publication Critical patent/US20040069013A1/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
    • 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.
  • condensing heat rejection
  • 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.
  • 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.
  • MPE Multi Port Extruded
  • FIG. 8 shows example of the embodiment according to claim 5 used in a refrigerator or similar devices.
  • FIG. 1 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 11 a 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. An example is shown in FIG.
  • 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 11 a behind the refrigerator, extending the air flow shell or jacket 11 in order to enhance the natural air flow/circulation.

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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)
  • 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)
US10/432,228 2000-11-24 2001-11-16 Refrigerating or heat pump system with heat rejection at supercritical pressure Abandoned US20040069013A1 (en)

Applications Claiming Priority (3)

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

Publications (1)

Publication Number Publication Date
US20040069013A1 true US20040069013A1 (en) 2004-04-15

Family

ID=19911836

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/432,228 Abandoned US20040069013A1 (en) 2000-11-24 2001-11-16 Refrigerating or heat pump system with heat rejection at supercritical pressure

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 (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110041524A1 (en) * 2008-04-19 2011-02-24 Carrier Corporation Refrigerant system performance enhancement by subcooling at intermediate temperatures
US11656011B2 (en) * 2019-01-22 2023-05-23 Hitachi Energy Switzerland Ag Condenser

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005106404A (ja) 2003-09-30 2005-04-21 Sanyo Electric Co Ltd 加熱冷却システム
JP2005156093A (ja) * 2003-11-28 2005-06-16 Daikin Ind Ltd 空気調和装置
CN101124438B (zh) * 2005-02-18 2010-08-04 卡里尔公司 具有热回收的co2制冷设备
EP2158434A1 (fr) * 2007-05-22 2010-03-03 INSTITUT FÜR LUFT- UND KÄLTETECHNIK GEMEINNÜTZIGE GESELLSCHAFT mbH Condenseur de paroi arrière de réfrigérateurs de ménage
DE102010043243A1 (de) * 2010-11-03 2012-05-03 BSH Bosch und Siemens Hausgeräte GmbH Wärmetauscher
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

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US1769119A (en) * 1928-01-06 1930-07-01 Chicago Pneumatic Tool Co Condensing system
US2105751A (en) * 1936-05-28 1938-01-18 Crosley Radio Corp Condenser device for refrigerators
US2189494A (en) * 1932-11-26 1940-02-06 Gen Motors Corp Refrigerating apparatus
US2292033A (en) * 1941-08-01 1942-08-04 Gen Electric Refrigerant condenser and method of forming same
US2344145A (en) * 1943-04-29 1944-03-14 Gen Motors Corp Refrigerating apparatus
US2478617A (en) * 1948-03-18 1949-08-09 Pierce John B Foundation Air conditioning system
US2865182A (en) * 1956-09-21 1958-12-23 Temprite Products Corp Self-contained water cooler of the bubbler type
US3595029A (en) * 1969-09-08 1971-07-27 Heatransfer Corp Air conditioning for volkswagen-type automobiles
US4972683A (en) * 1989-09-01 1990-11-27 Blackstone Corporation Condenser with receiver/subcooler
US5228311A (en) * 1990-08-16 1993-07-20 The Coca-Cola Company Cooling apparatus
US5544498A (en) * 1993-05-06 1996-08-13 Valeo Thermique Habitacle Efficieny cooling fluid circuit
US5636528A (en) * 1993-09-21 1997-06-10 Hoshizaki Denki Kabushiki Kaisha Cooling method and system therefor
US6105380A (en) * 1998-04-16 2000-08-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerating system and method of operating the same
US6134900A (en) * 1998-01-21 2000-10-24 Denso Corporation Supercritical refrigerating system
US6185955B1 (en) * 1998-08-05 2001-02-13 Sanden Corp. Refrigerating system which can favorably use as a refrigerant, a fluid smaller in specific volume than a general refrigerant
US6189334B1 (en) * 1998-07-09 2001-02-20 Behr Gmbh & Co. Air conditioner
US6591618B1 (en) * 2002-08-12 2003-07-15 Praxair Technology, Inc. Supercritical refrigeration system

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GB540937A (en) * 1939-08-03 1941-11-06 Nils Erland Af Kleen Improvements in or relating to air cooled condensing systems for refrigerators
IT1284421B1 (it) * 1995-11-13 1998-05-21 Bundy S P A Scambiatore di calore a serpentina, in particolare condensatore per circuiti frigorigeni.
DE19918617C2 (de) * 1999-04-23 2002-01-17 Valeo Klimatechnik Gmbh Gaskühler für einen überkritischen CO¶2¶-Hochdruck-Kältemittelkreislauf einer Kraftfahrzeugklimaanlage
JP4016544B2 (ja) * 1999-09-29 2007-12-05 株式会社デンソー 超臨界蒸気圧縮式冷凍サイクル用の放熱器

Patent Citations (17)

* 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
US2189494A (en) * 1932-11-26 1940-02-06 Gen Motors Corp Refrigerating apparatus
US2105751A (en) * 1936-05-28 1938-01-18 Crosley Radio Corp Condenser device for refrigerators
US2292033A (en) * 1941-08-01 1942-08-04 Gen Electric Refrigerant condenser and method of forming same
US2344145A (en) * 1943-04-29 1944-03-14 Gen Motors Corp Refrigerating apparatus
US2478617A (en) * 1948-03-18 1949-08-09 Pierce John B Foundation Air conditioning system
US2865182A (en) * 1956-09-21 1958-12-23 Temprite Products Corp Self-contained water cooler of the bubbler type
US3595029A (en) * 1969-09-08 1971-07-27 Heatransfer Corp Air conditioning for volkswagen-type automobiles
US4972683A (en) * 1989-09-01 1990-11-27 Blackstone Corporation Condenser with receiver/subcooler
US5228311A (en) * 1990-08-16 1993-07-20 The Coca-Cola Company Cooling apparatus
US5544498A (en) * 1993-05-06 1996-08-13 Valeo Thermique Habitacle Efficieny cooling fluid circuit
US5636528A (en) * 1993-09-21 1997-06-10 Hoshizaki Denki Kabushiki Kaisha Cooling method and system therefor
US6134900A (en) * 1998-01-21 2000-10-24 Denso Corporation Supercritical refrigerating system
US6105380A (en) * 1998-04-16 2000-08-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerating system and method of operating the same
US6189334B1 (en) * 1998-07-09 2001-02-20 Behr Gmbh & Co. Air conditioner
US6185955B1 (en) * 1998-08-05 2001-02-13 Sanden Corp. Refrigerating system which can favorably use as a refrigerant, a fluid smaller in specific volume than a general refrigerant
US6591618B1 (en) * 2002-08-12 2003-07-15 Praxair Technology, Inc. Supercritical refrigeration system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110041524A1 (en) * 2008-04-19 2011-02-24 Carrier Corporation Refrigerant system performance enhancement by subcooling at intermediate temperatures
US8925336B2 (en) * 2008-04-19 2015-01-06 Carrier Corporation Refrigerant system performance enhancement by subcooling at intermediate temperatures
US11656011B2 (en) * 2019-01-22 2023-05-23 Hitachi Energy Switzerland Ag Condenser

Also Published As

Publication number Publication date
EP1340027A1 (fr) 2003-09-03
JP2004514868A (ja) 2004-05-20
AU2002215268A1 (en) 2002-06-03
TW528843B (en) 2003-04-21
NO20005974D0 (no) 2000-11-24
CN1476524A (zh) 2004-02-18
CN1250927C (zh) 2006-04-12
CA2429857A1 (fr) 2002-05-30
WO2002042695A1 (fr) 2002-05-30
KR20030065524A (ko) 2003-08-06

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