EP1531309A2 - Condenseur - Google Patents

Condenseur Download PDF

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Publication number
EP1531309A2
EP1531309A2 EP04257015A EP04257015A EP1531309A2 EP 1531309 A2 EP1531309 A2 EP 1531309A2 EP 04257015 A EP04257015 A EP 04257015A EP 04257015 A EP04257015 A EP 04257015A EP 1531309 A2 EP1531309 A2 EP 1531309A2
Authority
EP
European Patent Office
Prior art keywords
tube
tubes
arrangement
hydraulic diameter
condenser
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Withdrawn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
EP04257015A
Other languages
German (de)
English (en)
Other versions
EP1531309A3 (fr
Inventor
Adrian Lionel Calsonic Kansei UK Limited Frost
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.)
Marelli Automotive Systems UK Ltd
Original Assignee
Calsonic Kansei UK Ltd
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 Calsonic Kansei UK Ltd filed Critical Calsonic Kansei UK Ltd
Publication of EP1531309A2 publication Critical patent/EP1531309A2/fr
Publication of EP1531309A3 publication Critical patent/EP1531309A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • 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
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers

Definitions

  • the present invention relates to a condenser, and in particular to a condenser comprising part of an automotive airconditioning system.
  • EP0219974 discloses that optimum performance maybe achieved where the hydraulic diameter is between about 0.4mm and 1mm.
  • the tubes comprise discrete flow channels or ports between 8 and 20 in number for each tube.
  • a condenser comprising a first heat transfer tube arrangement in a relatively upstream portion of the condenser, and a second heat transfer tube arrangement relatively downstream of the first tube arrangement, wherein the hydraulic diameter of the first tube arrangement is different to the hydraulic diameter of the second tube arrangement.
  • hydraulic diameter of the second tube arrangement is greater than the hydraulic diameter of the first tube arrangement.
  • the second tube arrangement is in the sub cooled region of the condenser.
  • the second tube arrangement is preferably provided in the sub cooled region of the condenser and also immediately upstream of the sub cooled region of the condenser.
  • a receiver dryer may be positioned flowise between the sub cooled region of the condenser and the immediately upstream tube arrangement.
  • the external depth dimension of tubes in the first and second tube arrangements is substantially the same.
  • a so called unified (or combined) condenser and radiator arrangement where banks of radiator and condenser tubes are arranged side by side, it is beneficial to have the radiator tubes and condenser tubes in line with one another in order to streamline airflow through the combined radiator and condenser arrangement.
  • the external depth dimension of tubes in the first and second tube arrangements being substantially different, where the hydraulic diameter ofthe second tube arrangement is greater than the hydraulic diameter of the first tube arrangement, in such embodiments the external depth dimension of the second tube arrangement will preferably be substantially greater than that of the first tube arrangement.
  • the spacing between adjacent tubes in the first tube arrangement is substantially the same as the spacing between adj acent tubes in the second tube arrangement.
  • the spacing between adjacent tube major axes in the first tube arrangement is substantially the same as the spacing between adjacent tube major axes in the second tube arrangement.
  • a so called unified (or combined) condenser and radiator arrangement where banks of radiator and condenser tubes are arranged side by side, it is beneficial to have the radiator tubes and condenser tubes in line with one another in order to streamline airflow through the combined radiator and condenser arrangement.
  • the hydraulic diameter of the tubes of the second tube arrangement is substantially at or above 1.3 times the hydraulic diameter of the tubes of the second arrangement. More preferably, the hydraulic diameter of the tubes of the second tube arrangement is substantially at or above 1.5 times the hydraulic diameter of the tubes of the second arrangement. More preferably still, the hydraulic diameter of the tubes of the second tube arrangement is substantially at or above 1.7 times the hydraulic diameter of the tubes of the second arrangement. In certain embodiments, the hydraulic diameter of the tubes of the second tube arrangement may be substantially at or above 2 or even 2.5 times the hydraulic diameter of the tubes of the second arrangement. For example, suitable performance has been achieved using first tube arrangement of hydraulic diameter (HD) of 0.71 mm and second tube arrangement of tube hydraulic diameter (HD) of 2mm giving a ratio for the second tube arrangement of 2.8 times the first tube arrangement hydraulic diameter.
  • first tube arrangement of hydraulic diameter (HD) of 0.71 mm and second tube arrangement of tube hydraulic diameter (HD) of 2mm giving a ratio for the second tube arrangement of 2.8 times the first tube arrangement hydraulic diameter.
  • the hydraulic diameter ofthe tubes ofthe second arrangement is substantially in the range 0.8mm to 3mm. In some embodiments, it is preferred that the hydraulic diameter of the tubes of the second arrangement is substantially in the range 1.2mm to 3mm, more preferably 1.4mm to 3mm, more preferably 1.7mm to 3mm.
  • respective tubes of the second arrangement each include a plurality of channels extending in the longitudinal direction of the tube. In some preferred embodiments between 2 and 6 channels are provided, more preferably 4 or 5 channels are provided.
  • respective tubes of the first arrangement each include a plurality of channels extending in the longitudinal direction ofthe tube.
  • 10 or more channels may be provided.
  • first and second tube arrangements comprise extruded tubes.
  • first and second tube arrangements comprise aluminium material tubes.
  • FIG. 1 there is shown schematically an exemplary condenser 1 for use in an automotive air conditioning system.
  • the condenser 1 comprises a pair of spaced headers 2, 3 and interconnecting headers 2, 3, plurality of heat exchange tubes 4 arranged in a bank with air gaps intermediate respectively tubes 4.
  • An air way matrix of fins (not shown) is typically provided intermediate adjacent spaced tubes in the bank.
  • the headers 2, 3 contain internal baffles ensuring that refrigerant flow through the condenser takes place in a number of discrete passes between headers 2, 3 as shown by the arrows in Figure 1.
  • the refrigerant enters condenser 1 via inlet 5 in vapour form and is condensed during passage through the condenser.
  • the refrigerant Prior to exiting the condenser via outlet 6 the refrigerant passes through a receiver dryer 7 (which includes a desiccant cartridge or the like) ensuring that all gasses are removed from the refrigerant.
  • the refrigerant leaving receiver dryer 7 is directed via line 9 into a sub-cool section 10 of the condenser which cools the refrigerant further to ensure that all refrigerant exiting outlet 6 is in liquid form.
  • FIG. 1 An important feature of the present invention is the relationship between the heat exchange refrigerant tubes 4 present in the sub-cool section 10 and the upstream section within the condenser.
  • Shown in Figure 1 at reference 4a is a multiported refrigerant tube 4 which is present in the portion of the condenser upstream of the sub-cool section 10 and receiver dryer 7.
  • Shown at reference 4b in Figure 1 is a refrigerant tube which is present in the sub-cool section 10 of the condenser 1.
  • Tube 4a has 14 internal ports or channels extending along the length of tube 4a and a hydraulic diameter which is typically in the range 0.4 to 1.0 mm.
  • Tube 4b has only four ports and a hydraulic diameter which is significantly greater than the hydraulic diameter of tube 4a.
  • the hydraulic diameter will be between 1.3 and 2.5 or more times the hydraulic diameter of tube 4a.
  • the hydraulic diameter of tubes 4b will typically be varied between 1.2mm and 2 to 3mm plus.
  • the hydraulic diameter (HD) is defined as four times the cross-sectional area of the tube (or channel) divided by the wetted perimeter of the tube (or channel).
  • the arrangement shown in Figure 2 is generally similar to the arrangement shown in Figure 1, however in this embodiment the tubes 4b are also provided upstream ofthe sub-cool section 10 in the last pass (from header 2 to header 3) prior to entering the receiver dryer 7. In this last pass 11, the refrigerant is mostly in liquid phase and therefore benefits from the increased hydraulic diameter of the tubes 4b present in this last pass.
  • the tubes 4 in the sub-cool section 10 are of the configuration 4c. These tubes 4c have larger free flow area ports and increased hydraulic diameter relative to the tubes 4a upstream of the receiver dryer. However the tube depth h is the same for tubes 4c and 4a. This ensures that, for regularly spaced tubes in the condenser bank, the spacing between the major axes of adjacent tubes is identical for the sub-cool section and also the section upstream of the sub-cool section and receiver dryer. Additionally, the spacing between adjacent tubes in the sub-cool section 10 and the tube bank section upstream of the sub-cool section and receiver dryer 7 are also the same. This enables the condenser arrangement to be conveniently used in so-called unified (or combined) condenser and radiator arrangements.
  • Figures 5A to 5D show various multi-port configurations of heat exchange tubes 4.
  • the tubes of Figures 5A, 5D and 5E will be suitable for use in the sub-cool section of the condenser.
  • the tubes of Figures 5B and 5C will be used in the section of the condenser upstream of the sub-cool section and receiver dryer 7.
  • the tube of Figure 5A has 4 ports and a hydraulic diameter (HD) of 1.2mm.
  • the tube of Figure 5B has 15 ports and a hydraulic diameter (HD) of 0.65mm.
  • the tube of Figure 5C has 14 ports and a hydraulic diameter (HD) of 0.71mm.
  • the tube of Figure 5D has 4 ports and a hydraulic diameter (HD) of 2mm.
  • the tube of Figure 5C has 3 ports and a hydraulic diameter (HD) of 3mm.
  • Figure 4 shows a plot of pressure drop versus free flow area for condenser tubes. It can be seen that increasing the tube port size and hydraulic diameter for the sub-cool phase of a typical sized heat exchanger can reduce the refrigerant pressure losses dramatically (experimental results show by up to 84 per cent). It should be noted that while a hydraulic diameter step change has been shown for condenser tubes between the sub-cool section and condenser bank tubes upstream of the sub-cool section and receiver dryer, the step change in hydraulic diameter does not need to take place but could rather be more gradual having adj acent tubes in successive passes having tube hydraulic diameters slightly increased over the previous pass up to a maximum hydraulic diameter in the sub-cool section. Therefore whilst condensers have been shown having only tube configurations of two alternative hydraulic diameters (the largest hydraulic diameter being in the sub-cool section 10), it is envisaged that multiple tubes of increasing hydraulic diameter towards the outlet end of the condenser could be provided.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP04257015A 2003-11-13 2004-11-12 Condenseur Withdrawn EP1531309A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0326443A GB0326443D0 (en) 2003-11-13 2003-11-13 Condenser
GB0326443 2003-11-13

Publications (2)

Publication Number Publication Date
EP1531309A2 true EP1531309A2 (fr) 2005-05-18
EP1531309A3 EP1531309A3 (fr) 2005-07-20

Family

ID=29726450

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04257015A Withdrawn EP1531309A3 (fr) 2003-11-13 2004-11-12 Condenseur

Country Status (2)

Country Link
EP (1) EP1531309A3 (fr)
GB (1) GB0326443D0 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1816424A1 (fr) * 2006-02-02 2007-08-08 Behr GmbH & Co. KG Echangeur thermique pour un cycle frigorifique
DE102006035993A1 (de) * 2006-08-02 2008-02-07 Behr Gmbh & Co. Kg Kraftfahrzeug-Klimaanlage und Wärmeübertrager, insbesondere Heizkörper, für eine Kraftfahrzeug-Klimaanlage
WO2008064238A1 (fr) * 2006-11-22 2008-05-29 Johnson Controls Technology Company Échangeur de chaleur multicanaux à tubes multicanaux dissemblables
WO2008071511A1 (fr) * 2006-12-14 2008-06-19 Valeo Systemes Thermiques Echangeur de chaleur comprenant au moins trois parties d'echanges de chaleur et systeme de gestion de l'energie thermique comportant un tel echangeur
CN101600919B (zh) * 2006-11-22 2011-06-01 约翰逊控制技术公司 具有不同多通路管道的多通路热交换器
WO2012022807A1 (fr) * 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Module de condenseur à réfrigérant
WO2012022806A1 (fr) * 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Module de condenseur à réfrigérant
DE102011005177A1 (de) * 2011-03-07 2012-09-13 Behr Gmbh & Co. Kg Kondensator
EP2667134A1 (fr) * 2011-01-21 2013-11-27 Daikin Industries, Ltd. Échangeur de chaleur et climatiseur
WO2016092655A1 (fr) * 2014-12-10 2016-06-16 三菱電機株式会社 Dispositif à cycle de réfrigération
US20180038661A1 (en) * 2015-06-03 2018-02-08 Bayerische Motoren Werke Aktiengesellschaft Heat Exchanger for a Cooling System, Cooling System, and Assembly
WO2019006887A1 (fr) * 2017-07-05 2019-01-10 南通远征冷冻设备有限公司 Condenseur efficace
EP4166871A4 (fr) * 2020-06-15 2023-08-09 Mitsubishi Electric Corporation Dispositif à cycle de réfrigération

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0219974A2 (fr) 1985-10-02 1987-04-29 Modine Manufacturing Company Condenseur à branche d'écoulement à petit diamètre hydraulique
JPH09178299A (ja) 1995-12-25 1997-07-11 Showa Alum Corp 受液部一体型凝縮器
US20010029748A1 (en) 2000-04-14 2001-10-18 Behr Gmbh & Co. Condenser for a vehicle air-conditioning system

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WO1992015833A1 (fr) * 1991-03-11 1992-09-17 Modine Manufacturing Company Condenseur a passage d'ecoulement de diametre hydraulique reduit
FR2694080B1 (fr) * 1992-07-24 1996-06-21 Furukawa Electric Co Ltd Tube condenseur plat et poreux.
JP3627382B2 (ja) * 1996-06-24 2005-03-09 株式会社デンソー 冷媒凝縮装置、および冷媒凝縮器
FR2759447B1 (fr) * 1997-02-11 1999-04-30 Valeo Thermique Moteur Sa Condenseur a reservoir integre pour installation de climatisation, notamment de vehicule automobile
KR100264815B1 (ko) * 1997-06-16 2000-09-01 신영주 다단기액분리형응축기
JP3131774B2 (ja) * 1997-09-26 2001-02-05 漢拏空調株式会社 車両エアコン用の多重流動型凝縮器
FR2786259B1 (fr) * 1998-11-20 2001-02-02 Valeo Thermique Moteur Sa Echangeur de chaleur combine, en particulier pour vehicule automobile
GB2346680A (en) * 1999-02-11 2000-08-16 Llanelli Radiators Ltd Condenser
JP2002031436A (ja) * 2000-05-09 2002-01-31 Sanden Corp サブクールタイプコンデンサ
US6494059B2 (en) * 2000-08-11 2002-12-17 Showa Denko K.K. Receiver tank for use in refrigeration cycle, heat exchanger with said receiver tank, and condensing apparatus for use in refrigeration cycle
CZ20032352A3 (cs) * 2001-03-02 2004-09-15 Showa Denko K.K. Tepelný výměník se sběrnou nádrží a chladicí systém
JP2002318034A (ja) * 2001-04-19 2002-10-31 Zexel Valeo Climate Control Corp コンデンサ
JP2003021432A (ja) * 2001-07-09 2003-01-24 Zexel Valeo Climate Control Corp コンデンサ
TWI280340B (en) * 2002-02-20 2007-05-01 Showa Denko Kk Heat exchanger with receiver tank, receiver tank connecting member, receiver tank mounting structure of heat exchanger and refrigeration system
JP2003254641A (ja) * 2002-02-28 2003-09-10 Showa Denko Kk 冷凍システム、冷凍サイクル用凝縮装置及びその装置の冷媒出口構造
JP3941555B2 (ja) * 2002-03-22 2007-07-04 株式会社デンソー 冷凍サイクル装置および凝縮器
US7337832B2 (en) * 2003-04-30 2008-03-04 Valeo, Inc. Heat exchanger

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0219974A2 (fr) 1985-10-02 1987-04-29 Modine Manufacturing Company Condenseur à branche d'écoulement à petit diamètre hydraulique
JPH09178299A (ja) 1995-12-25 1997-07-11 Showa Alum Corp 受液部一体型凝縮器
US20010029748A1 (en) 2000-04-14 2001-10-18 Behr Gmbh & Co. Condenser for a vehicle air-conditioning system

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1816424A1 (fr) * 2006-02-02 2007-08-08 Behr GmbH & Co. KG Echangeur thermique pour un cycle frigorifique
DE102006035993A1 (de) * 2006-08-02 2008-02-07 Behr Gmbh & Co. Kg Kraftfahrzeug-Klimaanlage und Wärmeübertrager, insbesondere Heizkörper, für eine Kraftfahrzeug-Klimaanlage
WO2008064238A1 (fr) * 2006-11-22 2008-05-29 Johnson Controls Technology Company Échangeur de chaleur multicanaux à tubes multicanaux dissemblables
US7757753B2 (en) 2006-11-22 2010-07-20 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar multichannel tubes
CN101600919B (zh) * 2006-11-22 2011-06-01 约翰逊控制技术公司 具有不同多通路管道的多通路热交换器
WO2008071511A1 (fr) * 2006-12-14 2008-06-19 Valeo Systemes Thermiques Echangeur de chaleur comprenant au moins trois parties d'echanges de chaleur et systeme de gestion de l'energie thermique comportant un tel echangeur
FR2910121A1 (fr) * 2006-12-14 2008-06-20 Valeo Systemes Thermiques Echangeur de chaleur pour vehicule automobile et systeme de gestion de l'energie thermique developpee par un moteur comportant un tel echangeur
WO2012022806A1 (fr) * 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Module de condenseur à réfrigérant
WO2012022807A1 (fr) * 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Module de condenseur à réfrigérant
US9970694B2 (en) 2010-08-19 2018-05-15 Mahle International Gmbh Coolant condenser assembly
EP2667134A1 (fr) * 2011-01-21 2013-11-27 Daikin Industries, Ltd. Échangeur de chaleur et climatiseur
EP2667134A4 (fr) * 2011-01-21 2014-07-09 Daikin Ind Ltd Échangeur de chaleur et climatiseur
DE102011005177A1 (de) * 2011-03-07 2012-09-13 Behr Gmbh & Co. Kg Kondensator
WO2016092655A1 (fr) * 2014-12-10 2016-06-16 三菱電機株式会社 Dispositif à cycle de réfrigération
JPWO2016092655A1 (ja) * 2014-12-10 2017-04-27 三菱電機株式会社 冷凍サイクル装置
US20180038661A1 (en) * 2015-06-03 2018-02-08 Bayerische Motoren Werke Aktiengesellschaft Heat Exchanger for a Cooling System, Cooling System, and Assembly
WO2019006887A1 (fr) * 2017-07-05 2019-01-10 南通远征冷冻设备有限公司 Condenseur efficace
EP4166871A4 (fr) * 2020-06-15 2023-08-09 Mitsubishi Electric Corporation Dispositif à cycle de réfrigération

Also Published As

Publication number Publication date
EP1531309A3 (fr) 2005-07-20
GB0326443D0 (en) 2003-12-17

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