EP1843109A2 - Kühlsystem - Google Patents

Kühlsystem Download PDF

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Publication number
EP1843109A2
EP1843109A2 EP07104133A EP07104133A EP1843109A2 EP 1843109 A2 EP1843109 A2 EP 1843109A2 EP 07104133 A EP07104133 A EP 07104133A EP 07104133 A EP07104133 A EP 07104133A EP 1843109 A2 EP1843109 A2 EP 1843109A2
Authority
EP
European Patent Office
Prior art keywords
pressure pipe
refrigerant
cooling system
low
heat exchanging
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Withdrawn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
EP07104133A
Other languages
English (en)
French (fr)
Other versions
EP1843109A3 (de
Inventor
Yukio C/o Sanden Corporation Yamaguchi
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.)
Sanden Corp
Original Assignee
Sanden Corp
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 Sanden Corp filed Critical Sanden Corp
Publication of EP1843109A2 publication Critical patent/EP1843109A2/de
Publication of EP1843109A3 publication Critical patent/EP1843109A3/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/022—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of two or more media in heat-exchange relationship being helically coiled, the coils having a cylindrical configuration
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/14—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically both tubes being bent
    • 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
    • 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
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to a cooling system used in an automatic vending machine, an air conditioner, a refrigerated and cold-storage showcase and the like.
  • a cooling system of this kind there is known the one including a refrigeration circuit constituted of a compressor, a radiator, an expansion mechanism and an evaporator, and circulating a refrigerant through the compressor, the radiator, the expansion mechanism, the evaporator and the compressor in this sequence.
  • the refrigerant which is compressed in the compressor to be at high temperature and high pressure releases heat in the radiator, and thereafter, is supplied to the expansion mechanism through a high-pressure pipe.
  • the refrigerant expanded to be at low pressure in the expansion mechanism flows into the evaporator, and evaporates by absorbing the ambient heat. Thereafter, the refrigerant is supplied to the compressor through the low-pressure pipe and is compressed again.
  • the refrigerant generally used in cooling systems is fluorocarbon, but now it becomes the problem that fluorocarbon destroys the ozone layer surrounding the earth. Therefore, in recent years, the cooling system using carbon dioxide that is natural refrigerant as a refrigerant in place of fluorocarbon has been known. In the cooling system using carbon dioxide as a refrigerant, the refrigerant at the high pressure side is in a supercritical state.
  • the cooling system using carbon dioxide as a refrigerant adopts the method for radiating heat of the refrigerant flowing in the high-pressure pipe by exchanging heat of the refrigerants flowing in respective pipes with each other by welding the outer peripheral side surface of the high-pressure pipe and the outer peripheral side surface of the low-pressure pipe.
  • An object of the present invention is to provide a cooling system capable of enhancing refrigeration efficiency even when using a carbon dioxide as the refrigerant.
  • the present invention includes a refrigeration circuit which has a compressor, a radiator an expansion mechanism and an evaporator, and in which carbon dioxide circulates as a refrigerant, a high-pressure pipe connecting the radiator and the expansion mechanism to allow a high-pressure refrigerant flowing out of the radiator to flow therethrough, a low-pressure pipe connecting the evaporator and the compressor to allow a low-pressure refrigerant flowing out of the evaporator to flow therethrough, and a heat exchanging part for performing heat exchange of the refrigerant flowing through an inside of the high-pressure pipe and the refrigerant flowing through an inside of the low-pressure pipe by disposing the high-pressure pipe in the low-pressure pipe, and an outer surface area of the high-pressure pipe in the heat exchange part is set to be in a range from 10% to 25% inclusive of an inner surface area of a heat exchanging pipe of the evaporator.
  • the coefficient of performance is larger and the refrigeration efficiency is higher than when the outer surface area of the high-pressure pipe is less than 10% of the inner surface area of the heat exchanging pipe and when the outer surface area of the high-pressure pipe is larger than 25% of the inner surface area of the heat exchanging pipe. Accordingly, if the outer surface area of the high-pressure pipe is set to be in the range from 10% to 25% inclusive of the inner surface area of the heat exchanging pipe, the refrigeration efficiency of the cooling system can be enhanced, and it is extremely advantageous when the cooling system is used in an automatic vending machine, for example.
  • FIGS. 1 to 6 show a cooling system according to a first embodiment of the present invention.
  • the cooling system shown in FIG. 1 includes a refrigeration circuit constituted of a compressor 10, a radiator 11, an expansion valve 12 as an expansion mechanism and an evaporator 13.
  • the refrigerant used in this cooling system is carbon dioxide as a natural refrigerant.
  • the radiator 11 is an air cooling type heat exchanger for allowing air and the refrigerant to exchange heat.
  • the evaporator 13 includes, as shown in FIGS. 1 and 2, a heat exchanging pipe 14 which linearly extends in the direction perpendicular to the flowing direction of air to be cooled and is provided in a meandering state, and a plurality of fins 15 which are equidistantly disposed in the refrigerant flowing direction of the heat exchanging pipe 14 to increase the surface area of the heat exchanging pipe 14. Heat exchange is practically performed in the width L of the heat exchanging pipe 14 where the fins 15 are disposed.
  • the heat exchanging pipe 14 in which heat exchange is practically performed is constituted of a first heat exchanging pipe 14a, a second heat exchanging pipe 14b, a third heat exchanging pipe 14c, a fourth heat exchanging pipe 14d, a fifth heat exchanging pipe 14e and a sixth heat exchanging pipe 14f.
  • the cooling system can circulate the refrigerant through the compressor 10, the radiator 11, the expansion valve 12, the evaporator 13 and the compressor 10 in this sequence (see the solid line arrow shown in FIG. 1). At this time, the refrigerant flows through the compressor 10, the radiator 11 and the expansion valve 12 under high pressure (hereinafter, called a high-pressure side), and flows through the expansion valve 12, the evaporator 13 and the compressor 10 under low pressure (hereinafter, called a low-pressure side).
  • the radiator 11 and the expansion valve 12 provided at the high-pressure side of the cooling system are connected by a high-pressure pipe 20.
  • the evaporator 13 and the compressor 10 provided at the low-pressure side of the cooling system are connected by a low-pressure pipe 21.
  • the cooling system includes a heat exchanger 22 (see the dashed line portion shown in FIG. 1) as a heat exchanging part which performs heat exchange of the refrigerant flowing in the high-pressure pipe 20 and the refrigerant flowing in the low-pressure pipe 21.
  • the high-pressure pipe 20, the low-pressure pipe 21 and the heat exchanger 22 will be described in detail by using FIGS. 4 and 5.
  • the high-pressure pipe 20 connects the radiator 11 and the expansion valve 12, and allows the refrigerant at high pressure flowing out of the radiator 11 to pass through it (see the hollow arrows shown in FIG. 4).
  • the low-pressure pipe 21 connects the evaporator 13 and the compressor 10, and allows the refrigerant at low pressure flowing out of the evaporator 13 to pass through it (see the solid line arrows shown in FIG. 5).
  • the heat exchanger 22 is provided by disposing a part of the high-pressure pipe 20 inside a part of the low-pressure pipe 21 by using a pair of connecting members 23.
  • the heat exchanger 22 is provided so that the direction in which the refrigerant in the low-pressure pipe 21 flows and the direction in which the refrigerant in the high-pressure pipe 20 flows are opposed to each other, so that the refrigerant flowing in the low-pressure pipe 21 and the refrigerant flowing in the high-pressure pipe 20 exchange heat with each other.
  • the inside diameter of the heat exchanging pipe 14 is d
  • the pipe length of each of the first to the sixth heat exchanging pipes 14a, 14b, 14c, 14d, 14e and 14f of the heat exchanging pipe 14 in which heat exchange is practically performed is L.
  • the total inner surface area S1 of the heat exchanging pipe 14 can be regarded as 6 ⁇ dL.
  • the outside diameter of the high-pressure pipe 20 in the heat exchanger 22 is D, and the pipe length of the heat exchanger 22 is L'.
  • the outer surface area S2 of the high-pressure pipe 20 in the heat exchanger 22 can be regarded as ⁇ DL'.
  • the ratio X of the outer surface area S2 of the high-pressure pipe 20 to the total inner surface area S1 of the heat exchanging pipe 14 thus expressed is calculated, and the relationship between the ratio X and the coefficient of performance (COP) of the cooling system will be described with reference to FIG. 6.
  • the relationship between the ratio X and the coefficient of performance of the cooling system is the measurement result of the experiment in three kinds of refrigerant charge amounts.
  • the coefficient of performance becomes larger and the refrigeration efficiency becomes higher than when the outer surface area S2 of the high-pressure pipe 20 is smaller than 10% and larger than 25% of the total inner surface area S1 of the heat exchanging pipe 14.
  • the refrigerant of the cooling system circulates through compressor 10, the radiator 11, the expansion valve 12, the evaporator 13 and the compressor 10 in this sequence (see the solid line arrows in FIG. 1).
  • the refrigerant flowing in the low-pressure pipe 21 (see the solid line arrows shown in FIG. 4) and the refrigerant flowing in the high-pressure pipe 20 (see the hollow arrows shown in FIG. 4) exchange heat with each other. Namely, the refrigerant flowing out of the radiator 11 releases heat in the heat exchanger 22, and thereafter, is supplied to the expansion valve 12.
  • the refrigerant flowing out of the expansion valve 12 flows into the evaporator 13, exchanges heat with air via the heat exchanging pipe 14 and the fins 15 and evaporates. After the refrigerant absorbs heat in the heat exchanger 22, it is returned to the compressor 10.
  • the cooling system of the embodiment when the outer surface area S2 of the high-pressure pipe 20 is set to be in the range from 10% to 25% inclusive of the total inner surface area S1 of the heat exchanging pipe 14 of the evaporator 13, the coefficient of performance becomes large and the refrigeration efficiency becomes high, and therefore, the amount of energy consumed can be reduced.
  • the cooling system in an automatic vending machine the automatic vending machine becomes extremely advantageous with regard to energy conservation.
  • the heat exchanger 22 is adapted so that the direction in which the refrigerant in the low-pressure pipe 21 flows and the direction in which the refrigerant in the high-pressure pipe 20 flows are opposed to each other, and therefore, heat exchange of the refrigerant flowing in the low-pressure pipe 21 and the refrigerant flowing in the high-pressure pipe 20 can be performed efficiently.
  • the heat exchanger 22 can be of the structure corresponding to the flow of the refrigerant in the cooling system, and therefore, space of the installation place of the heat exchanger 22 can be saved.
  • the refrigerant before being supplied to the expansion valve 12 releases heat in the heat exchanger 22. Therefore, the enthalpy difference of the refrigerant increases, and the refrigeration capacity is increased.
  • FIG. 7 is a side view of a heat exchanger constituted of the high-pressure pipe and the low-pressure pipe of the cooling system according to a second embodiment of the present invention.
  • the same components as in the cooling system shown in FIGS. 1 to 6 are expressed by the same reference numerals, and the explanation of them will be omitted.
  • a heat exchanger 32 shown in FIG. 7 differs from the heat exchanger 22 shown in FIG. 4 in the respect that the high-pressure pipe 20 and the low-pressure pipe 21 constituting the heat exchanger 32 are each formed into a spiral shape.
  • the heat exchanger 32 is provided by disposing a part of the high-pressure pipe 20 inside a part of the low-pressure pipe 21 by using a pair of connecting members 23.
  • the high-pressure pipe 20 and the low-pressure pipe 21 constituting the heat exchanger 32 are each formed into the spiral shape.
  • the heat exchanger 32 performs heat exchange of the refrigerant flowing in the low-pressure pipe 21 (see the solid line arrows shown in FIG. 7) and the refrigerant flowing in the high-pressure pipe 20 (see the hollow arrows shown in FIG. 7). Further, the heat exchanger 32 allows the refrigerant in the high-pressure pipe 20 to flow upward from below, and allows the refrigerant in the low-pressure pipe 21 to flow downward from above.
  • the space of the installation place of the heat exchanger 32 can be further saved.
  • the heat exchanger 32 can prevent oil accumulation from occurring in each of the pipes 20 and 21 by allowing the refrigerant in the high-pressure pipe 20 to flow upward from below, and allowing the refrigerant in the low-pressure pipe 21 to flow downward from above. Thereby, pressure loss can be prevented from occurring in the cooling system, reduction in the refrigeration efficiency of the cooling system can be suppressed.
  • the other operation and effect are the same as in the above described first embodiment.
  • the heat exchanging pipe 14 in which heat exchange is practically performed is constituted of six pipes in total, that is, the first to the sixth heat exchanging pipes 14a to 14f, but the heat exchanging pipe is not limited to this.
  • the number of pipes of the heat exchanging pipe 14 in which heat exchange is practically performed can be increased and decreased in accordance with the desired evaporation efficiency of the evaporator 13, for example.
  • the cooling system includes only one evaporator 13, but the number of evaporators 13 is not limited to this.
  • the cooling system may include a plurality of evaporators 13 as in the cooling system shown in FIG. 8, for example.
  • a plurality of evaporators 13 may be connected via the radiator 11 and an electromagnetic valve 16. Thereby, desired evaporation efficiency of the cooling system can be obtained by controlling the electromagnetic valve 16.
  • the heat exchanger 32 is formed into a spiral shape, but the heat exchanger 32 is not limited to this.
  • it may be formed into a circinate shape as a heat exchanger 42 shown in FIG. 9.
  • the heat exchanger 42 is adapted to allow the refrigerant in the high-pressure pipe 20 to flow to the center side from the outer side and allow the refrigerant in the low-pressure pipe 21 to flow to the outer side from the center side.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP07104133A 2006-04-03 2007-03-14 Kühlsystem Withdrawn EP1843109A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006101980A JP2007278541A (ja) 2006-04-03 2006-04-03 冷却システム

Publications (2)

Publication Number Publication Date
EP1843109A2 true EP1843109A2 (de) 2007-10-10
EP1843109A3 EP1843109A3 (de) 2009-01-28

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Family Applications (1)

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EP07104133A Withdrawn EP1843109A3 (de) 2006-04-03 2007-03-14 Kühlsystem

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EP (1) EP1843109A3 (de)
JP (1) JP2007278541A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008142661A2 (en) * 2007-05-23 2008-11-27 Trieco - Climatização, Lda. 'acclimatization system with high energy efficiency'
WO2015024155A1 (en) * 2013-08-19 2015-02-26 Trane Air Conditioning Systems (China) Co., Ltd. Gas cooler
EP3089257A1 (de) * 2015-04-29 2016-11-02 Samsung SDI Co., Ltd. Kühlsystem für eine batterie

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6300519B2 (ja) * 2013-12-26 2018-03-28 株式会社前川製作所 Ｃｏ２冷媒を用いた冷却システム

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JP2004058863A (ja) * 2002-07-30 2004-02-26 Japan Climate Systems Corp 車両用空調装置
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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008142661A2 (en) * 2007-05-23 2008-11-27 Trieco - Climatização, Lda. 'acclimatization system with high energy efficiency'
WO2008142661A3 (en) * 2007-05-23 2009-02-05 Trieco Climatizacao Lda 'acclimatization system with high energy efficiency'
WO2015024155A1 (en) * 2013-08-19 2015-02-26 Trane Air Conditioning Systems (China) Co., Ltd. Gas cooler
EP3089257A1 (de) * 2015-04-29 2016-11-02 Samsung SDI Co., Ltd. Kühlsystem für eine batterie
US20160322678A1 (en) * 2015-04-29 2016-11-03 Samsung Sdi Co., Ltd. Cooling system for battery
CN106099241A (zh) * 2015-04-29 2016-11-09 三星Sdi株式会社 用于电池的冷却系统
US10205201B2 (en) * 2015-04-29 2019-02-12 Samsung Sdi Co., Ltd. Cooling system for battery
CN106099241B (zh) * 2015-04-29 2021-07-09 三星Sdi株式会社 用于电池的冷却系统

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Publication number Publication date
EP1843109A3 (de) 2009-01-28
JP2007278541A (ja) 2007-10-25

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