EP1867944A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP1867944A2
EP1867944A2 EP20070110094 EP07110094A EP1867944A2 EP 1867944 A2 EP1867944 A2 EP 1867944A2 EP 20070110094 EP20070110094 EP 20070110094 EP 07110094 A EP07110094 A EP 07110094A EP 1867944 A2 EP1867944 A2 EP 1867944A2
Authority
EP
European Patent Office
Prior art keywords
tubes
flow passage
heat exchanger
tube body
refrigerant
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.)
Granted
Application number
EP20070110094
Other languages
German (de)
English (en)
Other versions
EP1867944B1 (fr
EP1867944A3 (fr
Inventor
Akihiko VALEO SYSTEMES THERMIQUES TAKANO
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.)
Valeo Systemes Thermiques SAS
Original Assignee
Valeo Systemes Thermiques SAS
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 Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Priority to PL07110094T priority Critical patent/PL1867944T3/pl
Publication of EP1867944A2 publication Critical patent/EP1867944A2/fr
Publication of EP1867944A3 publication Critical patent/EP1867944A3/fr
Application granted granted Critical
Publication of EP1867944B1 publication Critical patent/EP1867944B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F28D7/0008—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 for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—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 for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • 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
    • 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
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • 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
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • the present invention relates to a heat exchanger comprising a tube body having a first flow passage and a second flow passage in which heat exchange is effected between a medium flowing through the first flow passage and a medium flowing through the second flow passage by way of heat transmitted to said tube body.
  • the refrigeration efficiency of a compression-type refrigeration cycle in which a refrigerant is circulated can be improved by heat exchange performed between the high-pressure side and low-pressure side of the refrigerant.
  • Refrigeration cycles that use CO 2 as a refrigerant and in which the internal pressure of the radiator exceeds the critical point of the refrigerant have become particularly well known in recent years.
  • Supercritical refrigeration cycles such as this necessitate a very high pressure resistance, and a demand exists for a heat exchanger configuration in which heat exchange is effected between the high-pressure side and the low-pressure side of the refrigerant having improved heat exchange efficiency and the capacity to withstand the pressure of the refrigerant.
  • Cited references 1 to 3 disclose a basic configuration of a heat exchanger logically configured with consideration thereof.
  • the heat exchangers disclosed in these cited references comprise a tube body through which a high-pressure side and low pressure side refrigerant flows in which heat exchange is effected between a high-pressure side and low-pressure side refrigerant by means of heat transmitted to the tube body.
  • the tube body is configured from a flat first tube through which the high-pressure side refrigerant flows and a flat second tube through which the low-pressure side refrigerant flows.
  • a configuration based on the stacking of these tubes is also disclosed in cited reference 4.
  • the invention according to Claim 1 of the subject application constitutes a heat exchanger comprising a tube body having a first flow passage and a second flow passage, an inlet port and outlet port for a medium that flows through the first flow passage, and an inlet port and outlet port for a medium that flows through the second flow passage in which heat exchange is effected between the medium flowing through said first flow passage and the medium flowing through said second flow passage by way of heat transmitted to the tube body of a configuration in which the tube body is formed by stacking of a plurality of flat first tubes in which the first flow passage is provided and a plurality of flat second tubes in which the second flow passage is provided, in which the plurality of first tubes and the plurality of second tubes are alternately stacked with uniformity in a longitudinal direction and a flatness direction thereof, and in which end parts of the plurality of first tubes and end parts of the plurality of second tubes are respectively connected at an end part of the tube body to a predetermined inlet part and outlet part with displacement therebetween in the flatness direction.
  • the invention according to Claim 2 of the subject application constitutes the heat exchanger of Claim 1 of a configuration in which the predetermined inlet part and outlet part are formed by a coupling of a first block member in which a plurality of slits through which the end parts of the plurality of first tubes and the end parts of the plurality of second tubes are inserted are provided with a second block member comprising a communication part by which the plurality of slits communicate.
  • the invention according to Claim 3 of the subject application constitutes the heat exchanger of Claim 1 or Claim 2 of a configuration in which the heat exchanger constitutes an internal heat exchanger employed in a compression-type refrigeration cycle in which a refrigerant is circulated and in which heat exchange is effected between a high-pressure side and a low-pressure side of the refrigerant.
  • the invention according to Claim 4 of the subject application constitutes the heat exchanger of Claim 3 of a configuration in which the heat exchanger is supported in a radiator of the refrigeration cycle, and a pipe through which the refrigerant flows from the radiator to the heat exchanger and the inlet part of the first flow passage are integrated.
  • a heat exchanger in which the media flow structure of the tube body is logically configured can be produced.
  • a compression-type refrigeration cycle 1 as shown in FIG. 1 refers to a vehicle air conditioner mounted in a vehicle that comprises a compressor 2 for compressing a refrigerant, a radiator 3 for cooling a refrigerant compressed by the compressor 2, a depressurizer 4 for reducing the pressure and expanding the refrigerant cooled by the radiator 3, an evaporator 5 for evaporating the refrigerant depressurized by the depressurizer 4, and an accumulator 6 for separating the refrigerant that flows out from the evaporator 5 into a gas layer and a liquid layer and feeding the gas layer refrigerant to the compressor 2.
  • CO 2 is employed as the refrigerant
  • the internal pressure of the radiator 3 exceeds the critical point of the refrigerant in accordance with usage conditions such as the gas temperature.
  • the critical point of the refrigerant refers to the high-pressure side limit of thereof in a state in which the gas layer and liquid layer are coexisting, in other words the high-pressure side limit, and on a vapour pressure curve thereof is represented as the terminus.
  • the pressure, temperature and density at the critical point are referred to as the critical pressure, critical temperature and critical density.
  • a heat exchanger 100 for performing heat exchange between a high-pressure side and low-pressure side refrigerant is provided between the radiator 3 and depressurizer 4 and between the accumulator 6 and compressor 2.
  • the heat exchanger 100 improves the efficiency of the refrigeration cycle 1 by effecting heat exchange between the high-pressure side refrigerant and low-pressure side refrigerant.
  • the white arrow in this diagram denotes the direction in which the high-pressure side refrigerant flows, and the black arrow denotes the direction in which the low-pressure side refrigerant flows.
  • the symbol 11 in the drawing denotes a pipe through which the refrigerant flows from the radiator 3 to the heat exchanger 100
  • the symbol 12 denotes a pipe through which the refrigerant flows from the heat exchanger 100 to the depressurizer 4
  • the symbol 13 denotes a pipe through which the refrigerant flows from the accumulator 6 to the heat exchanger 100
  • the symbol 14 denotes a pipe through which the refrigerant flows from the heat exchanger 100 to the compressor 2.
  • the heat exchanger 100 of this example comprises a tube body 200 through which the high-pressure side refrigerant and the low pressure side refrigerant flow, heat exchange being effected by means of heat transmitted to the tube body 200.
  • the tube body 200 comprises a first flow passage 211 and a second flow passage 221, an inlet part 310 and outlet part 320 for a medium that flows through the first flow passage 211, and an inlet part 330 and outlet part 340 for a medium that flows through the second flow passage 221, heat exchange being effected between the medium that flows through the first flow passage 211 (high-pressure side refrigerant) and the medium that flows through the second flow passage 221 (low-pressure side refrigerant) by means of heat transmitted to the tube body 200.
  • the tube body 200 is formed by stacking of a plurality of first tubes 210 in which the first flow passage 211 is provided and a plurality of flat second tubes 220 in which the second flow passage 221 is provided.
  • the first tubes 210 and the second tubes 220 are configured as extruded members in which a plurality of flow passages is arranged in a row.
  • the cross-sectional area of the first flow passage 211 is designed to be smaller than the cross-sectional area of the second flow passage 221 from the viewpoint of pressure resistance.
  • the plurality of first tubes 210 and second tubes 220 are alternately stacked with uniformity in the longitudinal direction and in the flatness direction thereof.
  • end parts 210a of the plurality of first tubes 210 and end parts 220a of the plurality of second tubes 220 are respectively connected at the end part of the tube body 200 to predetermined inlet parts 310, 330 or outlet parts 320, 340 with displacement therebetween in the flatness direction.
  • Both end parts 210a of the first tubes 210 and both end parts 220a of the second tubes 220 are subjected to a predetermined bend processing following extrusion moulding.
  • the inlet parts 310, 330 and outlet parts 320, 340 are configured by coupling of a first block member 301 with a second block member 320.
  • the first block member 301 and the second block member 302 from which the inlet part 310 of the first flow passage 211 is configured is integrated with the first block member 301 and the second block member 302 from which the outlet part 340 of the second flow passage 221 is configured
  • the first block member 301 and the second block member 302 from which the outlet part 320 of the first flow passage 211 is configured is integrated with the first block member 301 and the second block member 302 from which the inlet part 330 of the second flow passage 221 is configured.
  • the first block member 301 constitutes a member that comprises a plurality of first slits 301 a in which the end parts 210a of the plurality of first tubes 210 are inserted and a plurality of second slits 301 b into which the end parts 220a of the plurality of second tubes 220 are inserted.
  • the second block member 302 constitutes a member that comprises a first communication part 302a through which the plurality of first slits 301 a communicate, and a second communication part 302b through which the plurality of second slits 301 b communicate.
  • the end parts 210a of the first tubes 210 are inserted to around the middle of the first slits 301 a.
  • the end parts 220a of the second tubes 220 are also inserted to around the middle of the second slits 301 b.
  • the pipes 11, 12, 13 and 14 are inserted to have connection with each of the first communication part 302a and the second communication part 302b.
  • the pipe 11 in which the refrigerant flows from the radiator 3 to the heat exchanger 100 and the pipe 14 in which the refrigerant from the heat exchanger 100 flows to the compressor 2 are formed as a bundle by a block-shaped connector member 20, the pipes 11, 14 being connected by screwing of the connector member 20 to the second block member 302.
  • the pipe 12 in which the refrigerant flows from the heat exchanger 100 to the depressurizer 4 and the pipe 13 in which the refrigerant flows from the accumulator 6 to the heat exchanger 100 are formed as a bundle by the block-shaped connector member 20, and the pipes 12, 13 are connected by screwing of a connector member 20 into the second block member 302.
  • a female screw part and a through-hole penetrated by a screw bolt 21 are provided in the connector member 20 and the second block member respectively.
  • the heat exchanger 100 of this example is configured by assembly of the first tubes 210, the second tubes 220, the first block member 301 and the second block member 302, the assembly being heat-processed and soldered in a furnace. During the soldering, the solder material and flux are provided in the necessary positions of each member.
  • the configuration of this embodiment in which the end parts 210a of the plurality of first tubes 210 and the end parts 220a of the plurality of second tubes 220 are respectively connected to predetermined inlet parts 310, 330 or outlet parts 320, 340 with displacement in the flatness direction between the first tubes 210 and the second tubes 220 is advantageous in that a plurality of first tubes 210 of the same shape and a plurality of second tubes 220 of the same shape can be employed whereupon, accordingly, the shape thereof can be reliably simplified.
  • a step part 301 c may be provided in the middle region thereof, the insert amount of the end parts 210a of the first tubes 210 and the end parts 220a of the second tubes 220 being regulated as a result of abutting against the step part 301 c. Based on a configuration such as this, a state in which the first flow passage 211 or the second flow passage 221 is caused to close as a result of having abutted against the second block member 302 can be reliably prevented.
  • the first block member 301 may be configured from a plurality of members as shown in FIG. 9. Furthermore, as shown in FIG. 10, as an effective method for preventing closure of the first flow passage 211 and the second flow passage 221, a method in which the end parts 210a of the first tubes 210 or the end parts 220a of the second tubes 220 are cut to a predetermined angle may be employed.
  • the positional relationship between the inlet parts 310, 330 and the outlet parts 320, 340 can be set as appropriate.
  • the bend processing of the end parts 210a of the first tubes 210 and the end parts 220a of the second tubes 220 can be set as appropriate.
  • a bend processing administered to each of both end parts 210a of the first tubes 210 and both end parts 220a of the second tubes 220a is advantageous from the viewpoint of reducing the amount of processing.
  • Administering of this processing on both end parts 210a of the first tubes 210 only (see FIG. 12), or on both end parts 220a of the second tubes 220 only (see FIG. 13), or on one end part of the first tube and the other end part of the second tube (see FIG. 14 and FIG. 15) only is advantageous from the viewpoint of reducing the number of processing steps.
  • a heat-insulating member may be fitted around the perimeter of the tube body 200. Fitting of a heat-insulating body improves the heat insulation characteristics to the exterior whereupon, as a result, heat exchange efficiency between the high-pressure side refrigerant and low-pressure side refrigerant is further improved.
  • a second embodiment of the present invention will be hereinafter described with reference to FIG. 16 and FIG. 17.
  • the heat exchanger 100 of this example is supported in the radiator 3 of the refrigeration cycle 1, a pipe 11 in which the refrigerant flows from the radiator 3 to the heat exchanger 100 being integrated with the inlet part 310 of the first flow passage 211.
  • a bracket 30 for supporting the heat exchanger 100 is provided in the radiator 3.
  • the heat exchanger 100 and radiator 3 are manufactured by assembly of members from which the heat exchanger 100 is configured, members from which the radiator 3 is configured, and the pipe 11 and bracket 30, and is then heat-processed and soldered in a furnace.
  • the pipe 11 is connected to the radiator 3 and is inserted to connect with the first communication part 302a of the second block member 302.
  • the basic configuration of the remainder of the embodiment is the same as the embodiment described above.
  • the space occupied by the refrigeration cycle 1 can be effectively utilized.
  • the pipe 11 between the heat exchanger 100 and radiator 3 is also short.
  • the heat exchanger 100 of this example is configured from hollow tank bodies comprising inlet parts 310, 330 and outlet parts 320 and 340 respectively.
  • the pipes 11, 12, 13, 14 are inserted in and soldered to the predetermined tank bodies.
  • First slits 301 a and second slits 301b are respectively provided in the tank bodies.
  • the inlet parts 310, 330 and outlet parts 320, 340 are able to be configured in hollow tank bodies.
  • the orientation of the end parts 210a of the first tubes 210 and the end parts 220a of the second tubes 220 are able to be arbitrarily set as shown in, for example, FIG. 20.
  • the heat exchanger of the present invention is very suitable for utilization as an internal heat exchanger of a refrigeration cycle in which the internal pressure of the radiator exceeds the critical point of the refrigerant.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP07110094.5A 2006-06-15 2007-06-12 Échangeur de chaleur Active EP1867944B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07110094T PL1867944T3 (pl) 2006-06-15 2007-06-12 Wymiennik ciepła

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006165726A JP2007333304A (ja) 2006-06-15 2006-06-15 熱交換器

Publications (3)

Publication Number Publication Date
EP1867944A2 true EP1867944A2 (fr) 2007-12-19
EP1867944A3 EP1867944A3 (fr) 2012-11-21
EP1867944B1 EP1867944B1 (fr) 2015-08-12

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ID=38512447

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07110094.5A Active EP1867944B1 (fr) 2006-06-15 2007-06-12 Échangeur de chaleur

Country Status (3)

Country Link
EP (1) EP1867944B1 (fr)
JP (1) JP2007333304A (fr)
PL (1) PL1867944T3 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2144028A1 (fr) * 2006-04-14 2010-01-13 Mitsubishi Denki Kabushiki Kaisha Échangeur de chaleur et appareil de conditionnement d'air de réfrigération
DE102013217287A1 (de) * 2012-09-03 2014-03-06 Behr Gmbh & Co. Kg Innerer Wärmeübertrager für einen Kältemittelkreislauf, insbesondere für eine Klimaanlage eines Kraftfahrzeuges, und einen Kältemittelkreislauf mit einem Verdampfer
EP2708390A1 (fr) * 2011-05-11 2014-03-19 Valeo Japan Co., Ltd. Appareil de climatisation pour véhicule
EP2738507A1 (fr) * 2011-07-28 2014-06-04 Daikin Industries, Ltd. Appareil échangeur de chaleur
EP2942594A4 (fr) * 2012-12-25 2016-10-26 Daikin Ind Ltd Echangeur thermique
EP3173724A1 (fr) * 2015-11-24 2017-05-31 Hamilton Sundstrand Corporation Collecteur pour échangeur de chaleur
US9726382B2 (en) 2010-07-30 2017-08-08 Grundfos Management A/S Heat exchanger unit having connectors with identical base elements

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4665045B1 (ja) 2009-09-28 2011-04-06 株式会社テイエルブイ 蒸気供給システム及びそれに用いる逆止弁
JP5786497B2 (ja) * 2011-06-30 2015-09-30 ダイキン工業株式会社 熱交換器
JP2013127346A (ja) * 2011-12-19 2013-06-27 Daikin Industries Ltd 熱交換器
JP5661205B2 (ja) * 2012-01-30 2015-01-28 三菱電機株式会社 積層型熱交換器及びそれを搭載したヒートポンプシステム、並びに積層型熱交換器の製造方法
WO2013132544A1 (fr) * 2012-03-07 2013-09-12 三菱電機株式会社 Echangeur de chaleur et système de pompe à chaleur avec échangeur de chaleur
JP2017215130A (ja) * 2016-06-02 2017-12-07 サンデンホールディングス株式会社 車両用内部熱交換器
CN111322795A (zh) 2018-12-14 2020-06-23 丹佛斯有限公司 换热器和空调系统

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3907032A (en) * 1971-04-27 1975-09-23 United Aircraft Prod Tube and fin heat exchanger
FR2332511A1 (fr) * 1975-11-18 1977-06-17 Owens Illinois Inc Ensemble tubulaire en vitroceramique pour echanges thermiques dans un recuperateur de chaleur et procede de fabrication de cet ensemble
WO2006033371A1 (fr) * 2004-09-22 2006-03-30 Showa Denko K.K. Appareil echangeur de chaleur integre
JP2006112756A (ja) * 2004-10-18 2006-04-27 Mitsubishi Electric Corp 熱交換器

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5188866A (fr) * 1975-01-20 1976-08-03
JP4718716B2 (ja) * 2001-05-01 2011-07-06 三菱重工業株式会社 ガスクーラ及び車載用空調装置
JP4348113B2 (ja) * 2003-05-23 2009-10-21 株式会社ヴァレオサーマルシステムズ 熱交換器
JP4774238B2 (ja) * 2004-05-20 2011-09-14 昭和電工株式会社 冷凍サイクルの冷媒流通部接続構造

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3907032A (en) * 1971-04-27 1975-09-23 United Aircraft Prod Tube and fin heat exchanger
FR2332511A1 (fr) * 1975-11-18 1977-06-17 Owens Illinois Inc Ensemble tubulaire en vitroceramique pour echanges thermiques dans un recuperateur de chaleur et procede de fabrication de cet ensemble
WO2006033371A1 (fr) * 2004-09-22 2006-03-30 Showa Denko K.K. Appareil echangeur de chaleur integre
JP2006112756A (ja) * 2004-10-18 2006-04-27 Mitsubishi Electric Corp 熱交換器

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2144028A1 (fr) * 2006-04-14 2010-01-13 Mitsubishi Denki Kabushiki Kaisha Échangeur de chaleur et appareil de conditionnement d'air de réfrigération
US8272233B2 (en) 2006-04-14 2012-09-25 Mitsubishi Electric Corporation Heat exchanger and refrigerating air conditioner
US9726382B2 (en) 2010-07-30 2017-08-08 Grundfos Management A/S Heat exchanger unit having connectors with identical base elements
EP2708390A1 (fr) * 2011-05-11 2014-03-19 Valeo Japan Co., Ltd. Appareil de climatisation pour véhicule
EP2708390A4 (fr) * 2011-05-11 2014-11-26 Valeo Japan Co Ltd Appareil de climatisation pour véhicule
EP2738507A1 (fr) * 2011-07-28 2014-06-04 Daikin Industries, Ltd. Appareil échangeur de chaleur
EP2738507A4 (fr) * 2011-07-28 2015-04-01 Daikin Ind Ltd Appareil échangeur de chaleur
DE102013217287A1 (de) * 2012-09-03 2014-03-06 Behr Gmbh & Co. Kg Innerer Wärmeübertrager für einen Kältemittelkreislauf, insbesondere für eine Klimaanlage eines Kraftfahrzeuges, und einen Kältemittelkreislauf mit einem Verdampfer
EP2942594A4 (fr) * 2012-12-25 2016-10-26 Daikin Ind Ltd Echangeur thermique
US9791213B2 (en) 2012-12-25 2017-10-17 Daikin Industries, Ltd. Heat exchanger
EP3173724A1 (fr) * 2015-11-24 2017-05-31 Hamilton Sundstrand Corporation Collecteur pour échangeur de chaleur

Also Published As

Publication number Publication date
JP2007333304A (ja) 2007-12-27
PL1867944T3 (pl) 2015-12-31
EP1867944B1 (fr) 2015-08-12
EP1867944A3 (fr) 2012-11-21

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