EP1643202A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP1643202A1
EP1643202A1 EP05021623A EP05021623A EP1643202A1 EP 1643202 A1 EP1643202 A1 EP 1643202A1 EP 05021623 A EP05021623 A EP 05021623A EP 05021623 A EP05021623 A EP 05021623A EP 1643202 A1 EP1643202 A1 EP 1643202A1
Authority
EP
European Patent Office
Prior art keywords
longitudinal
chamber
heat exchanger
transfer openings
opening
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
EP05021623A
Other languages
German (de)
English (en)
Other versions
EP1643202B1 (fr
Inventor
Gottfried DÜRR
Wolfgang Seewald
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1643202A1 publication Critical patent/EP1643202A1/fr
Application granted granted Critical
Publication of EP1643202B1 publication Critical patent/EP1643202B1/fr
Not-in-force 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
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with 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
    • F25B39/02—Evaporators
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the invention relates to a heat exchanger, in particular an evaporator, with one of an inner medium to be tempered, in particular a refrigerant,
  • a heat exchanger in particular an evaporator
  • one of an inner medium to be tempered in particular a refrigerant
  • a heat exchanger block which is bounded by two headers, with an inlet opening, an outlet opening and in each case at least one longitudinal partition wall are provided, are provided in the transfer openings and by which the collecting tanks are divided into Lzanskammem, which communicate with each other through the transfer openings, and with outside of the flow channels with an outer medium, in particular air, acted upon guide elements, in particular ribs, wherein a flood flow channels each runs between two LCodeskammem that belong to different collection boxes and are referred to as Lekscropartner.
  • European Patent Specification EP 0 947 792 B1 discloses an evaporator for carrying out a heat exchange between coolant or refrigerant flowing through it and an external fluid which flows on the outside of the evaporator.
  • the known evaporator comprises a plurality of tubes through which the refrigerant flows.
  • the tubes are arranged in multiple rows in the flow direction of the outer fluid.
  • a container is arranged in each case.
  • a partition wall element is provided for dividing the container into a plurality of container areas.
  • the container has an inlet and an outlet for the refrigerant or refrigerant.
  • several holes are provided, which have different openings with each other. The surfaces of the holes gradually narrow in the width direction.
  • the object of the invention is a heat exchanger, in particular an evaporator, with a to be tempered by an inner medium, in particular a refrigerant,
  • an inner medium in particular a refrigerant
  • the object is in a heat exchanger, in particular an evaporator, with one of an inner medium to be tempered, in particular a refrigerant,
  • a heat exchanger in particular an evaporator
  • one of an inner medium to be tempered in particular a refrigerant
  • the inlet opening can be provided laterally, that is to say in a narrow side, or in a longitudinal side of the longitudinal chamber.
  • a preferred embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber, in which the inlet opening is arranged, is delimited by a longitudinal dividing wall which has smaller transfer openings in the longitudinal section opposite the inlet opening than in the remaining region of the longitudinal dividing wall.
  • the size of the passage cross section of the transfer openings, the temperature profile on the outlet side of the outer medium can be adjusted to a predetermined temperature profile.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the inlet opening is arranged is delimited by a longitudinal dividing wall which has no transfer openings in the longitudinal section opposite the inlet opening.
  • the object is achieved with a heat exchanger described above in that the longitudinal chamber partner of the longitudinal chamber, in which the outlet opening is arranged, is delimited by a longitudinal dividing wall which has fewer crossing openings in a longitudinal section opposite the outlet opening than in the remaining region of the longitudinal dividing wall.
  • the outlet opening can be provided laterally, that is to say in a narrow side, or in a longitudinal side of the longitudinal chamber.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the outlet opening is arranged is delimited by a longitudinal dividing wall which has smaller transfer openings in the longitudinal section opposite the outlet opening than in the remaining region of the longitudinal dividing wall.
  • the size of the passage cross section of the transfer openings, the temperature profile on the outlet side of the outer medium can be adjusted to a predetermined temperature profile.
  • Another preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the outlet opening is arranged is delimited by a longitudinal dividing wall which has no transfer openings in the longitudinal section opposite the outlet opening.
  • the above object is achieved in a heat exchanger described above with a longitudinal chamber which is delimited in the longitudinal direction by a transverse partition in which a passage opening is provided, characterized in that the Lssenshuntpartner the longitudinal chamber in which the passage opening is arranged delimited by a longitudinal partition is, which has in one of the passage opening opposite longitudinal section fewer transfer openings than in the remaining region of the longitudinal partition wall.
  • the passage opening may be provided laterally, that is to say in a narrow side, or in a longitudinal side of the longitudinal chamber.
  • the passage opening in the transverse partition wall can also be given in the context of the present invention in that the transverse partition completely eliminated, in which case preferably the Lekscropartner of a transverse partition on the level - seen in the longitudinal direction - the omitted transverse partition is limited.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the passage opening is arranged is delimited by a longitudinal dividing wall which has smaller transfer openings in the longitudinal section opposite the passage opening than in the remaining region of the longitudinal dividing wall.
  • the size of the passage cross section of the transfer openings, the temperature profile on the outlet side of the outer medium can be adjusted to a predetermined temperature profile.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the longitudinal chamber partner of the longitudinal chamber in which the passage opening is arranged is delimited by a longitudinal dividing wall which has no transfer openings in the longitudinal section opposite the passage opening.
  • the transfer openings are arranged distributed uniformly in the longitudinal partition wall.
  • the distribution according to the invention of the transfer openings in the longitudinal dividing wall ensures that the tide having the inlet opening, the outlet opening or the passage opening in the direction of flow is sufficiently and evenly supplied with refrigerant.
  • FIG. 1 shows a flat tube evaporator 1 in a schematic, perspective view.
  • the flat tube evaporator 1 comprises an evaporator block 3, which has a multiplicity of flat tubes (not shown), between which corrugated ribs are arranged.
  • the structure and function of such a flat-tube evaporator are assumed to be known and are described for example in German patent application DE 103 12 780 A1.
  • the evaporator block 3 is bounded above and below by collecting tanks 5, 6, each in L Lucasskammem 8, 9; 11,12 are divided.
  • the evaporator block 3 is laterally closed by side parts 15, 16, which form the one side, such as the narrow sides.
  • the others Pages, such as the long sides, are designated 18 and 19 in FIG.
  • the longitudinal side 18 corresponds to the air inlet side.
  • the parts of the evaporator block 3 and the manifolds 5 and 6 are preferably made of aluminum or an aluminum alloy and are preferably soldered together, the ends of the flat tubes are sealed or sealed in openings in the manifolds 5, 6 are added.
  • the ribs arranged between the flat tubes are overflowed by air in the direction of flow indicated by arrows 21 to 23.
  • the longitudinal chamber 8 extends over the entire width of the heat exchanger 1.
  • the longitudinal chamber 9 is divided by a transverse partition 25 in two Lssenskammem 26 and 27.
  • an inlet opening 29 is provided, through which a refrigerant, for example R134a, enters the evaporator 1.
  • an outlet opening 30 is provided through which the refrigerant exits the heat exchanger 1.
  • the longitudinal chamber 11 opposite the longitudinal chamber 8 is divided by a transverse dividing wall 32 into two longitudinal chambers 34 and 35.
  • the longitudinal chamber 12 opposite the longitudinal chamber 12 is divided by a transverse partition wall 37 into two longitudinal chambers 39, 40.
  • the refrigerant is, as indicated by an arrow 41, the front, that is windward longitudinal chamber 26 fed through a (not shown) pressure line.
  • the refrigerant can also be supplied to the windward longitudinal chamber 27 and the leeward longitudinal chamber 8.
  • the refrigerant is reduced to the evaporator pressure in an expansion valve (not shown), that is, the refrigerant enters the longitudinal chamber 26 as the refrigerant wet steam.
  • the refrigerant After flowing through the evaporator 1, which is explained in more detail below, the refrigerant is sucked off via a suction line (not shown).
  • an (not shown) expansion valve is arranged in the air flow direction 21 to 23 in front of the evaporator 1 and the evaporator block 3.
  • the illustrated in Figure 1 heat exchanger 1 which is also referred to as an evaporator, is flowed through in the direction of arrows 41 to 49 of refrigerant.
  • the arrows 42, 44, 46, 48 each provide a flood of flow channels
  • the heat exchanger 1 is therefore also referred to as tardflutig.
  • the arrow 43 represents a passage between the LCodeskammem 39 and 34 in the collecting box 6.
  • the arrow 47 represents a transition between the LCodeskammem 35 and 40 in the collecting box 6.
  • the Studentstrritte 43 and 47 are made possible by transfer openings in a partition are provided, through which the LHarskammem 34 and 39 and 35 and 40 are separated from each other.
  • FIGS. 2 to 4 each show the view of a section through the collecting box 6 from FIG.
  • a longitudinal partition wall 51 which is arranged in the longitudinal direction between the longitudinal chamber 34 and the longitudinal chamber 39 in the collecting box 6.
  • a longitudinal partition wall 52 which is arranged between the longitudinal chambers 35 and 40.
  • the longitudinal partition walls 51, 52 are preferably integrally connected to each other.
  • the collection box 6 shown in FIG. 2 has a longitudinal section 54 in an area opposite the entry opening (29 in FIG. 1), in which no transfer openings are provided. Between the longitudinal section 54 and the transverse partition walls 32, 37, four transfer openings 56 to 59 are recessed in the longitudinal partition wall 51, which have the shape of elongated holes.
  • a longitudinal section 61 is provided opposite the outlet opening (30 in FIG. 1), in which no transfer openings are arranged. Between the longitudinal section 61 and the transverse partition walls 32, 37, two transfer openings 63 and 64 are recessed in the longitudinal partition 52. Between the longitudinal section 61 and the side wall of the Sammieikastens 6 52 three transfer openings 66 to 68 are recessed in the longitudinal partition wall.
  • the transfer opening 68 has a smaller passage cross-section than the transfer openings 66 and 67.
  • longitudinal portion 74 is formed larger than in the embodiment shown in Figure 2.
  • three transfer openings 77 to 79 are recessed in the longitudinal partition wall 51.
  • the longitudinal section 81 opposite the outlet opening (30 in FIG. 1) is also larger in the exemplary embodiment shown in FIG. 3 than in the exemplary embodiment illustrated in FIG.
  • three transfer openings 97 to 99 are recessed between one longitudinal section 94 opposite the inlet opening (29 in FIG. 1) and the transverse partition walls 32, 37.
  • the longitudinal portion 94 is the same size as the longitudinal portion 54 in the embodiment shown in Figure 2.
  • the transfer openings 97 to 99 have a larger passage cross-section than the transfer openings in the preceding embodiments.
  • the longitudinal partition wall 52 has in the embodiment shown in Figure 4 opposite the outlet opening (30 in Figure 1) has a longitudinal portion 101 which is larger than in the embodiment shown in Figure 2, but smaller than in the embodiment shown in Figure 3.
  • two transfer openings 106, 107 are arranged, each having a larger passage cross-section than in the preceding embodiments.
  • FIG. 5 shows a flat-tube evaporator 118 with a lateral refrigerant inlet 119 and a longitudinal connection 120 for the outlet or the suction of the refrigerant.
  • This evaporator 118 is in principle the same as the evaporator 1 described above, but it is larger in the longitudinal extent and flows through five-flow, that is, in five passages I, II, III, IV, V, wherein after the passage III, a deflection in the Depth III / IV against the air flow direction L takes place. However, the deflection in depth can also take place in the air flow direction. This applies in general, also for the other embodiments.
  • the evaporator 118 has an upper header box 121 with two L Lucasskammem 121 a, 121 b and two transverse partitions 122, 123.
  • a lower header 124 has two longitudinal chambers 124a, 124b with a transverse partition 150.
  • the divider walls 122, 150 on the leeward side are staggered with respect to the longitudinal extent of the evaporator to ensure three-flow formation.
  • the partition wall 123 is arranged centrally of the evaporator. As a result, two equally distributed floods are generated on the windward side.
  • the refrigerant in the passages I, II and III on the leeward side of the evaporator 118 as wet steam with (constant) evaporation temperature, so that could result in a uniform temperature distribution on the air outlet side.
  • the refrigerant at outlet 120 should be in the form of superheated steam at a predetermined superheat temperature; therefore in the last passage V refrigerant with overheating temperature flows, possibly already in the penultimate passage IV -beide, however, are on the air inlet side. This results in a uniform temperature distribution on the air outlet side even for a five-flute evaporator.
  • the evaporator is divided on the leeward side of the windward side into different areas, as in different floods. These areas are not the same size on the leeward side of the windward side as shown.
  • the block interconnection is progressive, that is, the first row of tubes into which the refrigerant flows or is injected is divided into three areas and floods (I, II, III), while the second row of tubes, from which the one Refrigerant is sucked, divided into only two areas or floods (IV, V).
  • the block interconnection in a five-flute evaporator may also be degressive, that is, the first row of tubes into which the refrigerant flows or is injected divides into two zones (I, II), while the second row of tubes from which the refrigerant is sucked, divided into three areas or floods (III, IV, V).
  • the inlet for the refrigerant is arranged on a lower longitudinal chamber and the outlet on an upper connection.
  • the connections are arranged on the same side of the evaporator, viewed in the longitudinal direction.
  • the ports may also be arranged on opposite sides of the evaporator in the longitudinal direction.
  • a heat exchanger block is formed by the flow path sections III and IV, which is bounded by transverse partition walls 122 and 123.
  • transverse partition walls 122, 123 for example, transverse dividing walls (not shown) with passage openings are arranged which, as shown in FIG. 5, are also completely dispensed with in order to ensure an overflow from or to an adjacent heat exchanger block.
  • a heat exchanger block is formed by the first two flow path sections, viewed from the inlet 41, which is bounded by the transverse partition wall 25.
  • the transverse partition wall 25 also eliminates a fictitious transverse partition, so that refrigerant can flow over to the other two Stömungspfadabitesen.
  • the size and / or distribution of the transfer openings in a longitudinal partition 34 dividing the longitudinal partition depends either on the position of the inlet 41 or the position of the given by the attributable transverse partition overflow or both positions.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Separation By Low-Temperature Treatments (AREA)
EP05021623A 2004-10-04 2005-10-04 Echangeur de chaleur Not-in-force EP1643202B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004048569 2004-10-04
DE102004056790A DE102004056790A1 (de) 2004-10-04 2004-11-24 Wärmetauscher

Publications (2)

Publication Number Publication Date
EP1643202A1 true EP1643202A1 (fr) 2006-04-05
EP1643202B1 EP1643202B1 (fr) 2009-05-13

Family

ID=35735916

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05021623A Not-in-force EP1643202B1 (fr) 2004-10-04 2005-10-04 Echangeur de chaleur

Country Status (3)

Country Link
EP (1) EP1643202B1 (fr)
AT (1) ATE431535T1 (fr)
DE (2) DE102004056790A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2175223A1 (fr) * 2007-07-27 2010-04-14 Mitsubishi Heavy Industries, Ltd. Évaporateur de fluide de refroidissement
EP2447657A3 (fr) * 2010-10-28 2015-03-04 Samsung Electronics Co., Ltd. Échangeur multicircuit avec des collecteurs sectionnels
WO2015142615A1 (fr) * 2014-03-18 2015-09-24 Carrier Corporation Évaporateur d'échangeur de chaleur à micro-canaux
DE102015210184A1 (de) * 2015-06-02 2016-12-22 Volkswagen Aktiengesellschaft Kraftfahrzeug mit einem Klimagerät
WO2020123653A1 (fr) * 2018-12-14 2020-06-18 Modine Manufacturing Company Condenseur de fluide frigorigène

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101910775B (zh) 2007-11-09 2012-10-17 汉拏空调株式会社 热交换器
EP4163580A4 (fr) * 2020-06-04 2023-07-19 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif à cycle de réfrigération

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4305060A1 (de) * 1993-02-19 1994-08-25 Behr Gmbh & Co Gelöteter Wärmetauscher, insbesondere Verdampfer
EP0683373A1 (fr) * 1994-05-16 1995-11-22 Sanden Corporation Echangeur de chaleur et procédé pour sa fabrication
EP0947792A2 (fr) * 1998-04-03 1999-10-06 Denso Corporation Evaporateur pour réfrigérant et sa méthode de fabrication
EP1298401A2 (fr) * 2001-09-29 2003-04-02 Halla Climate Control Corporation Echangeur de chaleur
US20040159121A1 (en) * 2001-06-18 2004-08-19 Hirofumi Horiuchi Evaporator, manufacturing method of the same, header for evaporator and refrigeration system
DE10312780A1 (de) 2003-03-21 2004-11-25 Behr Gmbh & Co. Kg Wärmetauscher
WO2005052488A1 (fr) * 2003-11-28 2005-06-09 Valeo Thermal Systems Japan Corporation Echangeur de chaleur

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10056074B4 (de) * 2000-11-07 2017-03-23 Mahle International Gmbh Wärmeübertrager

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4305060A1 (de) * 1993-02-19 1994-08-25 Behr Gmbh & Co Gelöteter Wärmetauscher, insbesondere Verdampfer
EP0683373A1 (fr) * 1994-05-16 1995-11-22 Sanden Corporation Echangeur de chaleur et procédé pour sa fabrication
EP0947792A2 (fr) * 1998-04-03 1999-10-06 Denso Corporation Evaporateur pour réfrigérant et sa méthode de fabrication
EP0947792B1 (fr) 1998-04-03 2002-07-31 Denso Corporation Evaporateur pour réfrigérant et sa méthode de fabrication
US20040159121A1 (en) * 2001-06-18 2004-08-19 Hirofumi Horiuchi Evaporator, manufacturing method of the same, header for evaporator and refrigeration system
EP1298401A2 (fr) * 2001-09-29 2003-04-02 Halla Climate Control Corporation Echangeur de chaleur
DE10312780A1 (de) 2003-03-21 2004-11-25 Behr Gmbh & Co. Kg Wärmetauscher
WO2005052488A1 (fr) * 2003-11-28 2005-06-09 Valeo Thermal Systems Japan Corporation Echangeur de chaleur

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2175223A1 (fr) * 2007-07-27 2010-04-14 Mitsubishi Heavy Industries, Ltd. Évaporateur de fluide de refroidissement
EP2175223A4 (fr) * 2007-07-27 2013-12-25 Mitsubishi Heavy Ind Ltd Évaporateur de fluide de refroidissement
US10161686B2 (en) 2009-04-13 2018-12-25 Carrier Corporation Microchanel heat exchanger evaporator
EP2447657A3 (fr) * 2010-10-28 2015-03-04 Samsung Electronics Co., Ltd. Échangeur multicircuit avec des collecteurs sectionnels
US9546824B2 (en) 2010-10-28 2017-01-17 Samsung Electronics Co., Ltd. Heat exchanger
WO2015142615A1 (fr) * 2014-03-18 2015-09-24 Carrier Corporation Évaporateur d'échangeur de chaleur à micro-canaux
DE102015210184A1 (de) * 2015-06-02 2016-12-22 Volkswagen Aktiengesellschaft Kraftfahrzeug mit einem Klimagerät
WO2020123653A1 (fr) * 2018-12-14 2020-06-18 Modine Manufacturing Company Condenseur de fluide frigorigène

Also Published As

Publication number Publication date
EP1643202B1 (fr) 2009-05-13
ATE431535T1 (de) 2009-05-15
DE502005007265D1 (de) 2009-06-25
DE102004056790A1 (de) 2006-04-06

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