EP3009780B1 - Fluide caloporteur - Google Patents

Fluide caloporteur Download PDF

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Publication number
EP3009780B1
EP3009780B1 EP15190213.7A EP15190213A EP3009780B1 EP 3009780 B1 EP3009780 B1 EP 3009780B1 EP 15190213 A EP15190213 A EP 15190213A EP 3009780 B1 EP3009780 B1 EP 3009780B1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
channels
coolant
flow path
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.)
Active
Application number
EP15190213.7A
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German (de)
English (en)
Other versions
EP3009780A1 (fr
EP3009780B2 (fr
Inventor
Sarah Gorzellik
Matthias Seitz
Herbert Hofmann
Gottfried DÜRR
Arthur Bauer
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 International GmbH
Original Assignee
Mahle International 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
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Application filed by Mahle International GmbH filed Critical Mahle International GmbH
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Publication of EP3009780B1 publication Critical patent/EP3009780B1/fr
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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
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1653—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
    • 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
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • 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
    • F28D2021/0028—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cooling heat generating elements, e.g. for cooling electronic components or electric devices
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/106—Particular pattern of flow of the heat exchange media with cross flow

Definitions

  • the present invention relates to a heat exchanger for cooling a heat source of a motor vehicle with coolant channels and refrigerant channels according to the preamble of claim 1.
  • a generic heat exchanger for cooling a heat source of a motor vehicle comprising a plurality of refrigerant channels and a plurality of coolant channels.
  • the coolant passages are formed by clearances provided between the refrigerant passages, wherein heat transferring surfaces are provided between a refrigerant guided in the refrigerant passages and a coolant guided in the coolant passages.
  • the refrigerant channels In the area of the heat transfer surfaces, the refrigerant channels have a refrigerant-carrying volume which is larger by a factor between 4 and 6 than the coolant-carrying volume of the coolant channels in the region of the heat transfer surfaces. This is to achieve a so-called chiller with a compact design and a high heat exchange efficiency.
  • a heat exchanger for a motor vehicle which can be traversed by refrigerant.
  • the flowing into the heat exchanger refrigerant flow is thereby divided by a valve device to at least two separate strands such that there is no mutual mixing of each inflowing refrigerant partial flow. This is to a uniform temperature distribution can be ensured.
  • JP-A-2000356488 and DE-A-102004024825 disclose a heat exchanger according to the preamble of claim 1.
  • the present invention therefore deals with the problem of providing a heat exchanger of the generic type an improved or at least one alternative embodiment, which in particular allows efficient cooling with low weight and low cost of the heat exchanger , This problem is solved according to the invention by the subject matter of independent claim 1.
  • Advantageous embodiments are the subject of the dependent claims.
  • the present invention is based on the general idea of combining the advantages of an indirect evaporator (chiller) with the advantages of CO 2 as the refrigerant and thereby to be able to provide a compact, high-efficiency and, on the other hand, inexpensive heat exchanger, in particular for battery cooling.
  • the heat exchanger according to the invention thus serves for cooling a heat source, such as a high-voltage battery or an electronic component, in a motor vehicle and has in a known manner coolant channels and refrigerant channels.
  • the individual refrigerant channels in a flat tube together with the adjoining refrigerant channels of the other flat tubes form a refrigerant flow path.
  • the coolant channels, which lined up a coolant flow path are also for the coolant flows around the flat tubes.
  • refrigerant now carbon dioxide (CO 2 ) is used, wherein the refrigerant flow on the one hand at least once is deflected U-shaped and the refrigerant channels also have a ratio between their wall thickness and their free diameter (inner diameter) of at least 0.4. Due to the at least unique U-shaped deflection, both the run length and the flow velocity can be increased and thus the heat transfer rate can be increased. Due to the comparatively high pressure and the associated small volume flows, the deflection on the refrigerant side is preferable, it being understood that a U-shaped deflection of the coolant flow path can be provided.
  • CO 2 carbon dioxide
  • a U-shaped flow path can be understood to mean a flow path that runs first in one direction and then after a 180 ° turn in the reverse direction, so that the refrigerant flows in opposite directions in the two flow path sections.
  • the refrigerant channels are positioned parallel to each other in so-called flat tubes, so that such a flat tube comprises a plurality of mutually parallel refrigerant channels. Between the individual flat tubes are the coolant channels, so that an outer wall of a respective flat tube simultaneously forms a wall of a coolant channel.
  • the refrigerant channels may be heat transfer elements, such as turbulence inserts or corrugated fins, which improve heat transfer.
  • heat transfer elements such as turbulence inserts or corrugated fins, which improve heat transfer.
  • the refrigerant channels themselves wear-resistant over the long term against the comparatively high pressure, they are dimensioned such that the ratio of their wall thickness to the free diameter or the channel width is at least 0.4.
  • a further requirement for the refrigerant channels according to the invention is that a web present between two refrigerant passages of a flat tube has a width which is at least 40% of the channel width, ie, the diameter of the refrigerant channel, preferably even 70 or even 100% of the (inner) diameter of the refrigerant channel.
  • the refrigerant channels and the coolant channels are arranged in sections, that is to say locally, in cross flow and in the entirety, that is to say globally, in countercurrent.
  • a particularly favorable embodiment from the thermodynamic point of view arises when both the refrigerant flow path and the coolant flow path are deflected the same and thus a countercurrent or cross flow can be maintained over all paths. Since it is to be expected in a chiller in normal operation with an overheating of the refrigerant of about 5 Kelvin, it is advantageous if in particular the last section before the refrigerant discharge is in countercurrent.
  • the countercurrent principle is used here because in the last flow often the refrigerant is already evaporated and only further heated, that is superheated.
  • a hydraulic diameter of the refrigerant channels is between 0.3 and 1.0 mm.
  • the hydraulic diameter is a calculated value which is used to calculate pressure loss and throughput in pipes and channels, provided that the cross section of the pipe or of the channel deviates from the circular shape.
  • the hydraulic diameter is thus to be determined in particular for refrigerant channels whose cross-section is, for example, square with rounded corners or elliptical.
  • the hydraulic diameter is for such channels thus the diameter of that circular channel, which would have the same pressure loss as the given channel at the same length and the same average flow rate.
  • the inner walls of the refrigerant channels are smooth, whereas the inner walls of the coolant channels are structured, ie in particular rough, in order to be able to achieve improved heat transfer.
  • the improved heat transfer is generated by the larger surface.
  • the edges of the component lead to a flow separation and thus to increased turbulence. Due to the high pressure load and the requirements on the internal cleanliness, however, a structured inside of the refrigerant channel does not make sense. In order to rule out any impairment of the circulation, purity requirements for all media-carrying parts exist for the components installed in the circuit.
  • particles are only tolerated up to a certain amount and consistency.
  • structurings on the inside make sense (for example if the flow channels have not round but star-shaped cross-sections.
  • heat transfer elements in particular turbulence inserts or corrugated fins, are arranged in the coolant channels. Such heat transfer elements increase the surface area available for heat transfer and thereby enable improved heat exchange.
  • FIGS. 1 and 4 to 8 has a heat exchanger 1 according to the invention for cooling a heat source of a motor vehicle, in particular for cooling a heat pump or a high-voltage battery or an electronic component, coolant channels 2 and 3 refrigerant channels.
  • carbon dioxide (CO 2 ) is used as the refrigerant in all heat exchangers 1 and, moreover, a refrigerant flow path 7 is deflected at least once in a U-shaped manner. Due to the at least unique U-shaped deflection of at least the refrigerant flow path 7, the efficiency and also the performance of the heat exchanger 1 according to the invention can be significantly increased.
  • the refrigerant channels 3 have a ratio between their wall thickness w and their diameter d of at least 0.4 (cf. FIGS. 2 and 3 ). Due to the high pressure in the refrigerant channels 3 and the associated small volume flows, a deflection on the refrigerant side is preferable.
  • the individual refrigerant channels 3 are arranged parallel to each other in flat tubes 4, wherein a web 5 present between two refrigerant channels 3 has a width b which is at least 40% of the diameter of the refrigerant channel 3, preferably even 70 or 100% of the diameter of the refrigerant channel 3 (again the FIGS. 2 and 3 ).
  • Such thick webs 5 ensure the required tensile strength.
  • the individual refrigerant channels 3 are connected evenly or progressively. In this case, progressive means that the flow cross-sectional area of the refrigerant side increases from one flow path to the next. As a result, the increasing volume of the refrigerant flow during evaporation is taken into account. This does not affect the geometric shape of the individual refrigerant channels 3 in the respective flat tube 4, but is set by the number of flat tubes 4 per flow path 6, 7.
  • the refrigerant channels 3 are preferably round or elliptical (see. FIG. 3 ), but may also have a square cross-section with rounded corners, as for example according to the FIG. 2 is shown.
  • both the refrigerant flow path 7 and the coolant flow path 6 are deflected, resulting in a particularly effective cooling.
  • the refrigerant and the coolant for example a water-glysantin mixture, are in both flow paths 6, 7 in the cross flow, as well as in the heat exchanger 1 according to Figures 4 and 5.
  • the heat exchanger 1 according to the FIG. 5 It works in cross-flow and is 2-flow, both refrigerant side and coolant side and each has a deflection of the coolant flow path 6 and the refrigerant flow path 7 in width.
  • the heat exchanger 1 according to the FIG. 4 is formed four-flow and has one compared to that according to the FIG. 5 Heat exchanger 1 shown a higher flow velocity through which the heat transfer is improved. Due to the 4-flood training also a better protection against overheating can be guaranteed.
  • the refrigerant channels 3 are taken in one or two collectors 8, in which a channel height h in relation to the material thickness w 1 (wall thickness of the collector 8) is a maximum of 3, better even less than 1.5.
  • a collector 8 is for example in the FIGS. 6 and 7 shown.
  • a hydraulic diameter d H of the refrigerant channels 3 between 0.3 and 1.0 mm.
  • a comparable hydraulic diameter d H for the coolant channels 2 is preferably between 0.5 and 2.0 mm.
  • an optimal ratio of pressure drop and heat transfer can be achieved on the coolant side.
  • a particularly advantageous ratio between the hydraulic diameter of the coolant channels 2 and the hydraulic diameter of the refrigerant channels 3 is greater than 1.0, preferably this ratio is between 1.5 and 3.
  • On the refrigerant side usually a two-phase mixture is heated, which usually too significantly worse heat transfer coefficient on the refrigerant side than on the coolant side leads.
  • heat transfer elements 9 for example turbulence inserts or corrugated fins, which increase the surface available for heat exchange, are arranged in the coolant channels 2.
  • the heat transfer available surface can be structured, which in turn increases the surface. Due to the high pressure load and the requirement for internal cleanliness, a structured surface for the refrigerant side, i. H. Concrete for the inner circumferential surface of the refrigerant channels 3, however, not suitable.
  • the refrigerant flow path 7 at least once deflected in a U-shape and indeed in width, wherein the coolant flow path 6 can be deflected in corresponding coolant headers 10.
  • the coolant flow path 6 and the refrigerant flow path 7 run in countercurrent.
  • Fig. 8 is a trained as R744 evaporator heat exchanger 1 shown with an upstream expansion element 11.
  • the expansion element 11 can be designed, for example, as an electronic expansion valve (EXV).
  • EXV electronic expansion valve
  • This expansion element 11 was typically grown on conventional R134a evaporators.
  • EXV electronic expansion valve
  • the expansion element 11 is installed in assembly with the evaporator, there are cost advantages, advantages in handling and possibly advantages in the interfaces.
  • the term "unit” is to be understood that the expansion element 11 (in particular TXV) is mechanically (possibly even cohesively) connected to the evaporator / chiller.
  • Such an assembly could, for example, by an integration of the valve housing in the evaporator / chiller flange (+ possibly a Mitlöten) take place.
  • the heat exchanger 1 according to the invention can be a high performance, ie achieve high efficiency of the heat exchanger 1, with low space requirements and favorable connection situation, especially if a connection arranged both for the coolant flow path 6 and the refrigerant flow path 7 on the same side of the heat exchanger 1 are.
  • a high pressure resistance can be ensured by the refrigerant channels 3 designed according to the invention, which enables the use of CO 2 as the refrigerant.

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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)

Claims (10)

  1. Échangeur de chaleur (1) pour le refroidissement d'une source de chaleur d'un véhicule, avec des canaux de fluide de refroidissement (2) formant une voie de circulation de fluide de refroidissement (6), et des canaux de fluide réfrigérant (3) formant une voie de circulation de fluide réfrigérant (7), dans lequel :
    - le fluide réfrigérant est le CO2,
    - la voie de circulation de fluide réfrigérant (7) est déviée au moins une fois en forme de U,
    - les canaux de fluide réfrigérant (3) présentent un rapport entre leur épaisseur de paroi (w) et leur diamètre (d) d'au moins 0,4,
    - une âme (5) présente entre deux canaux de fluide réfrigérant (3) présente une largeur b qui est d'au moins 40 % du diamètre du canal de fluide réfrigérant (3), de préférence même de 70 %, de manière particulièrement préférée même de 100 % du diamètre du canal de fluide réfrigérant (3),
    - les canaux de fluide réfrigérant (3) sont rassemblés dans un collecteur (8), caractérisé en ce que le collecteur (8) présente des canaux de distribution, pour lesquels s'applique h/w1 < 3,0, en particulier h/w1 < 1,5, dans lequel h est la hauteur du canal de distribution/collecteur et w1 est l'épaisseur de paroi du collecteur.
  2. Échangeur de chaleur selon la revendication 1,
    caractérisé en ce que
    la voie de circulation de fluide de refroidissement (6) est déviée au moins une fois en forme de U.
  3. Échangeur de chaleur selon la revendication 1 ou 2,
    caractérisé en ce que
    les canaux de fluide réfrigérant (3) présentent une section transversale carrée avec des coins arrondis.
  4. Échangeur de chaleur selon la revendication 1 ou 2,
    caractérisé en ce que
    les canaux de fluide réfrigérant (3) sont réalisés de manière ronde ou elliptique.
  5. Échangeur de chaleur selon l'une des revendications 1 à 4,
    caractérisé en ce que
    les canaux de fluide réfrigérant (3) et les canaux de fluide de refroidissement (2) sont disposés par endroits à courant croisé et dans la globalité à contre-courant.
  6. Échangeur de chaleur selon l'une des revendications 1 à 5,
    caractérisé en ce que
    des éléments d'échangeur de chaleur (9), en particulier des inserts créant des turbulences ou des cotes ondulées, sont disposés dans les canaux de fluide de refroidissement (2).
  7. Échangeur de chaleur selon l'une des revendications 1 à 6,
    caractérisé en ce que
    - un diamètre hydraulique dh des canaux de fluide réfrigérant (3) est de 0,3 mm < dh < 1,0 mm.
    - un diamètre hydraulique dh des canaux de fluide de refroidissement (2) est de 0,5 mm < dh < 2,0 mm.
  8. Échangeur de chaleur selon l'une des revendications 1 à 7,
    caractérisé en ce que
    une voie de circulation de fluide réfrigérant (7) est progressivement réalisée.
  9. Échangeur de chaleur selon l'une des revendications 1 à 8,
    caractérisé en ce que
    la distance entre deux tubes plats (4) embrassant deux canaux de fluide réfrigérant (3) forme une hauteur maximale de canal de fluide de refroidissement de 3,5 mm.
  10. Échangeur de chaleur selon l'une des revendications 1 à 9,
    caractérisé en ce que
    l'échangeur de chaleur (1) est exécuté sous la forme d'un évaporateur et est réalisé en unité modulaire avec un organe de détente (11) placé en amont, en particulier une vanne de détente électronique (EXV).
EP15190213.7A 2014-10-17 2015-10-16 Fluide caloporteur Active EP3009780B2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014221168.9A DE102014221168A1 (de) 2014-10-17 2014-10-17 Wärmeübertrager

Publications (3)

Publication Number Publication Date
EP3009780A1 EP3009780A1 (fr) 2016-04-20
EP3009780B1 true EP3009780B1 (fr) 2017-05-10
EP3009780B2 EP3009780B2 (fr) 2023-10-18

Family

ID=54365950

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15190213.7A Active EP3009780B2 (fr) 2014-10-17 2015-10-16 Fluide caloporteur

Country Status (2)

Country Link
EP (1) EP3009780B2 (fr)
DE (1) DE102014221168A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190072413A (ko) * 2017-12-15 2019-06-25 한온시스템 주식회사 열교환기

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DE3536325C2 (fr) 1984-10-12 1987-12-10 Showa Aluminium Co Ltd
US5172761A (en) 1992-05-15 1992-12-22 General Motors Corporation Heat exchanger tank and header
DE19906289A1 (de) 1998-02-16 1999-08-19 Denso Corp Wärmetauscher
US6155340A (en) 1997-05-12 2000-12-05 Norsk Hydro Heat exchanger
JP2000356488A (ja) 1999-06-11 2000-12-26 Showa Alum Corp 熱交換器用チューブ
US6564863B1 (en) 1999-04-28 2003-05-20 Valeo Thermique Moteur Concentrated or dilutable solutions or dispersions, preparation method and uses
EP1452814A1 (fr) 2001-11-08 2004-09-01 Zexel Valeo Climate Control Corporation Echangeur thermique et tube pour echangeur thermique
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JP3969254B2 (ja) † 2001-10-29 2007-09-05 株式会社デンソー バッテリ温度管理装置
DE102005020499A1 (de) 2005-04-29 2006-11-09 Behr Gmbh & Co. Kg Verdampfer, insbesondere Heckverdampfer für ein Kraftfahrzeug
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Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2877000A (en) 1955-09-16 1959-03-10 Int Harvester Co Heat exchanger
DE3536325C2 (fr) 1984-10-12 1987-12-10 Showa Aluminium Co Ltd
US5172761A (en) 1992-05-15 1992-12-22 General Motors Corporation Heat exchanger tank and header
US6155340A (en) 1997-05-12 2000-12-05 Norsk Hydro Heat exchanger
DE19906289A1 (de) 1998-02-16 1999-08-19 Denso Corp Wärmetauscher
US6564863B1 (en) 1999-04-28 2003-05-20 Valeo Thermique Moteur Concentrated or dilutable solutions or dispersions, preparation method and uses
JP2000356488A (ja) 1999-06-11 2000-12-26 Showa Alum Corp 熱交換器用チューブ
EP1452814A1 (fr) 2001-11-08 2004-09-01 Zexel Valeo Climate Control Corporation Echangeur thermique et tube pour echangeur thermique
DE102004024825A1 (de) 2003-05-23 2004-12-09 Denso Corp., Kariya Wärmetauschrohr mit mehreren Fluidpfaden
US20040256090A1 (en) 2003-06-23 2004-12-23 Yoshiki Katoh Heat exchanger
DE102005057327A1 (de) 2004-12-03 2006-06-22 Modine Manufacturing Co., Racine Herstellungsverfahren und Hochdruckwärmetauscher
DE102005016540A1 (de) 2005-04-08 2006-10-12 Behr Gmbh & Co. Kg Mehrkanalflachrohr
US20070251682A1 (en) 2006-04-28 2007-11-01 Showa Denko K.K. Heat exchanger
DE102006053702A1 (de) 2006-11-13 2008-05-15 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere Gaskühler
DE102012109038A1 (de) 2011-12-19 2013-06-20 Visteon Global Technologies Inc. Vorrichtung zur Wärmeübertragung in einem Kältemittelkreislauf
DE102012221925A1 (de) 2012-11-29 2014-06-05 Behr Gmbh & Co. Kg Wärmeübertrager
DE102012224353A1 (de) 2012-12-21 2014-06-26 Behr Gmbh & Co. Kg Wärmeübertrager

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DE102014221168A1 (de) 2016-04-21
EP3009780B2 (fr) 2023-10-18

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