EP3620727A1 - Condenseur à élément d'insertion pour une climatisation, en particulier pour un véhicule automobile - Google Patents

Condenseur à élément d'insertion pour une climatisation, en particulier pour un véhicule automobile Download PDF

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Publication number
EP3620727A1
EP3620727A1 EP18192976.1A EP18192976A EP3620727A1 EP 3620727 A1 EP3620727 A1 EP 3620727A1 EP 18192976 A EP18192976 A EP 18192976A EP 3620727 A1 EP3620727 A1 EP 3620727A1
Authority
EP
European Patent Office
Prior art keywords
condenser
heat exchanger
refrigerant
insert
exchanger channels
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.)
Pending
Application number
EP18192976.1A
Other languages
German (de)
English (en)
Inventor
Condro SEKTI
Michael GENGER
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 Klimasysteme GmbH
Original Assignee
Valeo Klimasysteme GmbH
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 Klimasysteme GmbH filed Critical Valeo Klimasysteme GmbH
Priority to EP18192976.1A priority Critical patent/EP3620727A1/fr
Priority to CN201980068214.3A priority patent/CN113167515A/zh
Priority to PCT/EP2019/073139 priority patent/WO2020048870A1/fr
Publication of EP3620727A1 publication Critical patent/EP3620727A1/fr
Pending 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • 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
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
    • 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
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0441—Condensers with an integrated receiver containing a drier or a filter
    • 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
    • F25B2339/0444—Condensers with an integrated receiver where the flow of refrigerant through the condenser receiver is split into two or more flows, each flow following a different path through the condenser receiver
    • 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 invention relates to a condenser with a first and a second manifold, a plurality of heat exchanger channels arranged one above the other, which extend between the two manifolds, an inlet for essentially gaseous refrigerant, which is arranged on one of the two manifolds, and an outlet for essentially liquid Refrigerant, which is arranged on one of the two header tubes, one of the two header tubes being provided with an insert.
  • Such a condenser is part of a refrigerant circuit as used for a vehicle air conditioning system.
  • air conditioning systems are also known for motor vehicles under the name HVAC.
  • the essential components of such an air conditioning system are a compressor, the condenser and an evaporator.
  • the function of the condenser is to extract heat from the gaseous refrigerant so that it condenses.
  • the refrigerant is passed through the heat exchanger channels, which are surrounded by ambient air on the outside.
  • the inlet and the outlet for the refrigerant are usually arranged at a distance from one another.
  • the refrigerant inlet is on one of the manifolds and the refrigerant outlet is on the other manifold.
  • the inlet and the outlet are on the same manifold, the inlet is usually located at one end, while the outlet is at the other end (e.g. up and down).
  • a condenser of the type mentioned in which one of the manifolds is provided with an insert which defines a flow channel.
  • the flow channel is connected at one end to the refrigerant inlet and at the other end by means of an overflow opening to the interior of the header.
  • additional line which is achieved in this way, increases the flexibility when connecting the condenser to a refrigerant line without increasing the installation space requirement.
  • the object of the present invention is to improve the flow conditions in the condenser.
  • the condenser according to the invention for an air conditioning system in particular for a motor vehicle, comprises a first and a second manifold as well as a plurality of heat exchanger channels arranged one above the other, which extend between the two manifolds.
  • the condenser further comprises an inlet for essentially gaseous refrigerant, which is arranged on one of the two manifolds, and an outlet for essentially liquid refrigerant, which is arranged on one of the two manifolds.
  • One of the two manifolds is equipped with an insert. The insert defines a flow pattern in the header pipe, which distributes the refrigerant over a large number of the heat exchanger channels.
  • the externally arranged additional line (“jumper line”) or the flow channel additionally created by means of an insert part ensures that the refrigerant is directed to a specific point in a collecting pipe and on the Way there does not enter adjacent heat exchanger channels in order in this way to specify a specific flow of the refrigerant through different groups of heat exchanger channels in the condenser.
  • an insert which defines a flow pattern in the header pipe, which causes the refrigerant to be distributed over a large number of heat exchanger channels. So no additional flow path should be created, but a targeted - ideally as even as possible - distribution of the refrigerant over a large number of heat exchanger channels is created.
  • a targeted distribution of the refrigerant within a header pipe of the condenser is important, since a large number of heat exchanger channels arranged one above the other typically results in the case that less refrigerant flows through some of the heat exchanger channels than through others.
  • the flow is less than in those closer to the refrigerant inlet.
  • This disadvantageous flow behavior is avoided in the condenser according to the invention. Thanks to the insert part provided according to the invention, which ensures a targeted distribution of the refrigerant over the large number of heat exchanger channels, a similar flow can be achieved through all of these channels.
  • the invention is particularly suitable for condensers in which only a single change of flow direction of the refrigerant is provided.
  • the refrigerant flows through a first group of heat exchanger channels from the first into the second header and then through a second group of heat exchanger channels from the second into the first header.
  • the insert supports the distribution of the refrigerant to one of the heat exchanger channel groups.
  • an insert can also be arranged in the other collecting tube, in order to include the Support distribution of the refrigerant to the other heat exchanger channel group.
  • the insert part provided according to the invention preferably has a plurality of geometric structures which influence the flow of the refrigerant in the header in the desired manner.
  • Such structures can e.g. B. certain obstacles, openings, guide or guide sections, etc.
  • the insert has a first side wall facing the heat exchanger channels, in which a plurality of outlet openings are formed.
  • the outlet openings ensure that only a certain amount of the refrigerant reaches the adjacent heat exchanger channels at predetermined points, while the remaining portion of the refrigerant is supplied to other heat exchanger channels.
  • the outlet openings are preferably elongated, the longitudinal extension of the outlet openings running in the direction of the arrangement of the heat exchanger channels one above the other. It has been shown that such a shape of the outlet openings is advantageous for a uniform distribution of the refrigerant.
  • the outlet openings preferably have a length in the range from 5 mm to 15 mm, preferably 10 mm, and a width in the range from 1 mm to 10 mm, preferably 5 mm.
  • the insert preferably has a second side wall facing away from the heat exchanger channels, which is interrupted by a recess.
  • An open section is preferably formed between an upper end of the first side wall and an upper edge of the recess provided in the second side wall.
  • the open section preferably has a length in the range from 30 mm to 70 mm, preferably 50 mm, and a width in the range from 5 mm to 20 mm, preferably 12.5 mm.
  • the insert part has an inclined transition section which extends from a lower edge of the recess provided in the second side wall in the direction of the heat exchanger channels and merges into the first side wall.
  • the transition section forms an inclined guide surface for the refrigerant, which slows down the flow only insignificantly.
  • an oil separation opening can be formed, through which at least a substantial part of the oil, which is transported into the condenser with the gaseous refrigerant, can be separated immediately and can thus be led to another location in the condenser so that it is the condenser again as quickly as possible leaves.
  • the oil separation opening preferably has a surface area in the range from 0.75 mm 2 to 9 mm 2 , preferably 5 mm 2 to 7.5 mm 2 .
  • the invention is particularly suitable for condensers in which two groups of heat exchanger channels are provided, the refrigerant flowing from the first header pipe through a first heat exchanger channel group in the direction of the second header pipe and through a second heat exchanger channel group in the opposite direction.
  • the two groups more precisely the access areas in the respective header pipe to the inlet openings of the two heat exchanger channel groups, must be separated from one another, for which purpose a simple partition plate is usually used.
  • the inlet openings of the plurality of heat exchanger channels, over which the refrigerant is distributed through the insert part are arranged in a region which differs from a lower end of the header extends up to the divider in the header.
  • the insert has an elongated shape and extends from the lower end of the collecting pipe to the separating plate in the collecting pipe.
  • the insert can be firmly connected to a cover, e.g. B. by clinching.
  • the cover can in turn be tightly connected to the manifold, e.g. B. by soldering.
  • a complete, externally sealed refrigerant distributor with the functionality according to the invention can be produced from a few components.
  • FIG. 1 A condenser 10 is shown, which is part of a refrigerant circuit of a motor vehicle air conditioning system.
  • the condenser 10 has a first header pipe 12, a second header pipe 14 and a plurality of heat exchanger channels 16 arranged one above the other, each of which extends between the first and the second header pipes 12, 14.
  • a dryer bottle 18 is attached to the second collecting pipe 14.
  • the first header pipe 12 is here provided with an inlet 20, through which refrigerant is supplied to the condenser 10 in the gaseous state.
  • An outlet 22 is also attached to the first header pipe 12 through which the refrigerant is discharged in the (at least for the most part) liquid state.
  • arrows A and B show the flow paths of the refrigerant through the condenser 10. It can be seen that the refrigerant not only enters the heat exchanger channels 16 at the level of the refrigerant inlet 20, but is also distributed over a large area to a large number of heat exchanger channels 16. In the exemplary embodiment shown, this area extends from the lower end of the first header pipe 12 up to a separating plate 24.
  • the insert 26 has an elongated shape.
  • the insert part 26 extends from the lower end of the collecting tube 12 to the separating plate 24. More precisely, the lower end of the insert part 26 is arranged just below the refrigerant inlet 20, while the upper end is located at approximately three quarters of the height of the condenser 10.
  • the insert 26 has and a first side wall 28 facing away from the refrigerant inlet 20 and facing the heat exchanger channels 16 and a second side wall 30 facing the refrigerant inlet 20 and facing away from the heat exchanger channels 16.
  • Two edges 32, 34 rise from the longitudinal edges of the second side wall 30 in the direction of the heat exchanger channels 16.
  • the second side wall 30 is recessed over a larger area. In the exemplary embodiment shown, this recess 36 extends from the height of the refrigerant inlet 20 to approximately one third of the height of the condenser 10.
  • An inclined transition section 38 extends from the lower edge of the recess 36, that is to say approximately at the level of the refrigerant inlet 20, in the direction of the heat exchanger channels 16.
  • the transition section 38 merges into the first side wall 28, which runs parallel to the second side wall 30.
  • first side wall 28 extends only to a height which is less than the height of the upper edge of the recess 36.
  • An open section 40 thus remains between the upper end of the first side wall 28 and the upper edge of the recess 36.
  • the open section In the illustrated embodiment, 40 has a width of approximately 12.5 mm and a height (in the longitudinal direction of the insert 26) of approximately 50 mm.
  • a plurality of elongated outlet openings 42 arranged one above the other are formed in the first side wall 28.
  • the outlet openings 42 have a width of approximately 5 mm and a height (in the longitudinal direction of the insert 26) of approximately 10 mm.
  • transition section 38 there is only a small oil separation opening 44. This has an area of the order of about 5 mm 2 to 7.5 mm 2 .
  • the refrigerant to be condensed is supplied to the condenser 10 via the refrigerant inlet 20 in a (substantially) gaseous state. Oil carried by the gas collects at the transition section 38 and is discharged downward through the oil separation opening 44 due to the prevailing pressure conditions.
  • the gaseous refrigerant is largely directed upward from the insert 26, with a certain portion of the refrigerant in the lower section of the header tube 12 which is actually blocked by the first side wall 28 through the elongated outlet openings 42 from the insert 26 and into the lower heat exchanger channels 16 can occur.
  • the gaseous refrigerant can freely enter the upper heat exchanger channels 16 below the separating plate 24.
  • the insert 26 with the elongated outlet openings 42 in the first side wall 28, the interrupted second side wall 30 and the open section 40 results in a largely homogeneous distribution of the refrigerant over the plurality of heat exchanger channels 16 up to the separating plate 24. Because of the uniform distribution of the refrigerant on the plurality of heat exchanger channels 16, the pressure loss of the refrigerant in the condenser 10 is minimized.
  • the gaseous refrigerant flows in the direction of arrow A and is cooled in the process.
  • the second header pipe 14 it flows into the dryer bottle 18 and upwards in order to return in a region of the condenser 10 defined above the separating plate 24 through the heat exchanger channels 16 there in the direction of arrow B back to the first header pipe 12 and thus to the refrigerant outlet 22 to pour.
  • the coolant As the refrigerant cools, the proportion of the liquid phase increases. In the area of the refrigerant outlet 22, the coolant is (at least almost) completely liquid.
  • the oil contained in the gaseous refrigerant which is discharged downward through the oil separating opening 44, is carried along by the liquid refrigerant and reintroduced into the refrigerant circuit via the refrigerant outlet 22.
  • the main advantage of the flow behavior of the refrigerant in the collecting tube 12 achieved with the insert part 26 is that the gaseous refrigerant can be distributed very evenly over a large number of heat exchanger channels 16 without any external add-on parts and without changing the installation space required for the condenser 10.
  • the starting point is a blank in the form of a rectangular sheet metal blank.
  • the wall thickness of the sheet can be of the order of 0.5 mm.
  • basically the same material can be used that is also used for the manifold 12 and the other components of the capacitor 10.
  • the openings which later form the open section 40, the elongated outlet openings 42 and the oil separation opening 44, are then punched at the two narrow ends of the blank facing away from one another.
  • the insert 26 is then attached to a cover 46, as in FIG Figure 4 shown.
  • the cover 46 is elongated and curved in cross section.
  • the insert 26 is connected to the cover 46 such that a flow channel is formed between the concave side of the cover 46 and the first side wall 28 of the insert 26.
  • the flow channel is not closed on the side facing the heat exchanger channels 16 due to the elongated outlet openings 42.
  • the cover 46 additionally has a lower section 48, in which the refrigerant inlet 20 is located.
  • the cover can have an upper section in which the refrigerant outlet 22 is located.
  • the insert 26 and the cover 46 can be clipped together.
  • the cover 46 is attached to the manifold 12.
  • the collector tube 12 is provided on its side facing away from the cover 46 with a large number of inlet openings which open into the heat exchanger channels 16.
  • the cover 46 and the manifold 12 are preferably soldered together.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP18192976.1A 2018-09-06 2018-09-06 Condenseur à élément d'insertion pour une climatisation, en particulier pour un véhicule automobile Pending EP3620727A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP18192976.1A EP3620727A1 (fr) 2018-09-06 2018-09-06 Condenseur à élément d'insertion pour une climatisation, en particulier pour un véhicule automobile
CN201980068214.3A CN113167515A (zh) 2018-09-06 2019-08-29 用于特别是用于机动车辆的空调的具有插入件的冷凝器
PCT/EP2019/073139 WO2020048870A1 (fr) 2018-09-06 2019-08-29 Condenseur à insert pour un climatiseur, en particulier pour un véhicule à moteur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18192976.1A EP3620727A1 (fr) 2018-09-06 2018-09-06 Condenseur à élément d'insertion pour une climatisation, en particulier pour un véhicule automobile

Publications (1)

Publication Number Publication Date
EP3620727A1 true EP3620727A1 (fr) 2020-03-11

Family

ID=63524168

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18192976.1A Pending EP3620727A1 (fr) 2018-09-06 2018-09-06 Condenseur à élément d'insertion pour une climatisation, en particulier pour un véhicule automobile

Country Status (3)

Country Link
EP (1) EP3620727A1 (fr)
CN (1) CN113167515A (fr)
WO (1) WO2020048870A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09189498A (ja) * 1996-01-09 1997-07-22 Nippon Light Metal Co Ltd 熱媒体分流促進機構付ヘッダ及びその成形方法
JP2002303499A (ja) * 2001-03-30 2002-10-18 Hisaka Works Ltd プレート式熱交換器
CN102287969A (zh) * 2011-06-16 2011-12-21 广东美的电器股份有限公司 平行流换热器
WO2018091710A1 (fr) * 2016-11-21 2018-05-24 Valeo Klimasysteme Gmbh Condenseur de climatiseur, en particulier d'un véhicule automobile

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10155001A1 (de) * 2001-11-08 2003-05-22 Behr Gmbh & Co Kältemittelkondensator
DE10234890A1 (de) * 2002-07-31 2004-02-19 Behr Gmbh & Co. Filteranlage zum Reinigen eines Mediums, Wärmetauscher und Kältemittelkreislauf
JP5717475B2 (ja) * 2010-04-16 2015-05-13 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
DE102011002976A1 (de) * 2011-01-21 2012-07-26 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
JP2012247148A (ja) * 2011-05-30 2012-12-13 Keihin Thermal Technology Corp コンデンサ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09189498A (ja) * 1996-01-09 1997-07-22 Nippon Light Metal Co Ltd 熱媒体分流促進機構付ヘッダ及びその成形方法
JP2002303499A (ja) * 2001-03-30 2002-10-18 Hisaka Works Ltd プレート式熱交換器
CN102287969A (zh) * 2011-06-16 2011-12-21 广东美的电器股份有限公司 平行流换热器
WO2018091710A1 (fr) * 2016-11-21 2018-05-24 Valeo Klimasysteme Gmbh Condenseur de climatiseur, en particulier d'un véhicule automobile
DE102016122310A1 (de) 2016-11-21 2018-05-24 Valeo Klimasysteme Gmbh Kondensator für eine Klimaanlage, insbesondere für ein Kraftfahrzeug

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Publication number Publication date
CN113167515A (zh) 2021-07-23
WO2020048870A1 (fr) 2020-03-12

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