EP3009780B2 - Fluide caloporteur - Google Patents

Fluide caloporteur Download PDF

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Publication number
EP3009780B2
EP3009780B2 EP15190213.7A EP15190213A EP3009780B2 EP 3009780 B2 EP3009780 B2 EP 3009780B2 EP 15190213 A EP15190213 A EP 15190213A EP 3009780 B2 EP3009780 B2 EP 3009780B2
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EP
European Patent Office
Prior art keywords
refrigerant
channels
heat exchanger
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
EP3009780B1 (fr
EP3009780A1 (fr
Inventor
Sarah Gorzellik
Matthias Seitz
Herbert Hofmann
Gottfried DÜRR
Arthur Bauer
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Mahle International GmbH
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Mahle International GmbH
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Publication date
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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 coolant 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 coolant channels and a plurality of coolant channels.
  • the coolant channels are formed by free spaces provided between the coolant channels, with heat-transferring surfaces being provided between a coolant guided in the coolant channels and a coolant guided in the coolant channels.
  • the coolant channels In the area of the heat transfer surfaces, the coolant channels have a coolant-carrying volume that is larger by a factor of between 4 and 6 than the coolant-carrying volume of the coolant channels in the area of the heat transfer surfaces. This is intended to achieve a so-called chiller with a compact design and high heat exchange efficiency.
  • a heat exchanger for a motor vehicle is known through which refrigerant can flow.
  • the refrigerant stream flowing into the heat exchanger is divided by a valve device into at least two separate strands in such a way that there is no mutual mixing of the incoming refrigerant partial stream. This is intended to ensure that the temperature distribution is as even as possible.
  • JP-A-2000356488 , and DE-A-102004024825 disclose a heat exchanger according to the preamble of claim 1.
  • the present invention is therefore concerned with the problem of specifying an improved or at least an alternative embodiment for a heat exchanger of the generic type, which in particular enables efficient cooling with at the same time low weight and low costs of the heat exchanger.
  • 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 a refrigerant and thereby being able to provide a compact, highly efficient and inexpensive heat exchanger, in particular for battery cooling.
  • the heat exchanger according to the invention is therefore used to cool a heat source, for example a high-voltage battery or an electronic component, in a motor vehicle and has coolant channels and coolant channels in a known manner.
  • the individual refrigerant channels in a flat tube, together with the adjoining refrigerant channels of the other flat tubes, form a refrigerant flow path. In an analogous manner, this also applies to the coolant channels, which, when lined up next to one another, form a coolant flow path.
  • the coolant flows around the flat tubes.
  • Carbon dioxide (CO 2 ) is now used as the refrigerant, with the refrigerant flow path being deflected at least once in a U-shape and the refrigerant channels also having a ratio between their wall thickness and their free diameter (inner diameter) of at least 0.4.
  • both the running length and the flow speed can be increased and thus the heat transfer rate can be increased. Due to the comparatively high pressure and the associated small volume flows, deflection on the refrigerant side is preferred, with a U-shaped deflection of the coolant flow path also being provided.
  • a U-shaped flow path can be understood as meaning a flow path that first runs in one direction and then, after a 180° turn, in the opposite direction, so that the refrigerant flows in opposite directions in the two flow path sections.
  • the refrigerant channels are positioned parallel to one another in so-called flat tubes, so that such a flat tube comprises a plurality of refrigerant channels running parallel to one another.
  • the coolant channels are located between the individual flat tubes, so that an outer wall of a respective flat tube also forms a wall of a coolant channel.
  • heat exchanger elements such as turbulence inserts or corrugated fins, which improve heat transfer.
  • the refrigerant channels themselves wear-resistant in the long term against the comparatively high pressure, they are dimensioned in such a way 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 channels of a flat tube has a width that 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 amounts. Thanks to such massive webs, it is easily possible to absorb the pressures occurring in the refrigerant channels over the long term. With a heat exchanger designed in this way, not only can a compact heat exchanger with a comparatively high heat transfer rate be achieved, but it can also be manufactured comparatively inexpensively, which is of great advantage, particularly with regard to competition in the automotive supply sector.
  • the refrigerant channels and the coolant channels are arranged in sections, that is to say locally, in cross-flow and as a whole, that is to say globally, in counter-current.
  • a particularly favorable embodiment from a thermodynamic point of view results when both the refrigerant flow path and the coolant flow path are deflected in the same way and thus a countercurrent or cross-flow can be maintained across all paths. Since the refrigerant is expected to overheat by approx. 5 Kelvin in normal operation, it is advantageous if the last section in particular before the refrigerant exits is in countercurrent.
  • the countercurrent principle is used here because the refrigerant has often already evaporated in the last flow path and is only heated up further, i.e.
  • both the coolant side and the coolant side are deflected and both the coolant and the coolant are in countercurrent in the respective flow path.
  • a 2-, 4- or 6-flow power supply is conceivable here. If both the coolant side and the refrigerant side are deflected, both flow paths can also be in cross-flow, in which case it makes particular sense to place the coolant outlet and the coolant inlet in the same section and thereby form a counterflow characteristic from a global perspective.
  • the refrigerant side can be designed with 4 or 6 channels.
  • a hydraulic diameter of the refrigerant channels is between 0.3 and 1.0 mm.
  • the hydraulic diameter is a calculated quantity that is used to calculate pressure loss and throughput in pipes and channels if the cross section of the pipe or channel deviates from the circular shape.
  • the hydraulic diameter is therefore to be determined in particular for refrigerant channels whose cross section is, for example, square with rounded corners or elliptical.
  • the hydraulic diameter indicates the diameter of the circular channel that would have the same pressure loss as the given channel with the same length and the same average flow velocity.
  • the empirically determined hydraulic diameter between 0.3 mm and 1.0 mm, both optimal pressure resistance and optimal heat transfer can be achieved.
  • round or elliptical channels are particularly advantageous.
  • the inner walls of the coolant channels are smooth, whereas the inner walls of the coolant channels are structured, i.e. H. especially rough, in order to achieve improved heat transfer.
  • the improved heat transfer is generated by the larger surface area.
  • the edges of the component lead to flow separation and thus to increased turbulence.
  • a structured inside of the refrigerant channel does not make sense. In order to generally rule out any impairment of the circuit, there are purity requirements for all media-carrying parts for the components installed in the circuit.
  • particles are only tolerated up to a certain amount and quality. Structuring on the inside makes sense for this (e.g. if the flow channels do not have round but star-shaped cross-sections.
  • Heat exchanger elements in particular turbulence inserts or corrugated fins, are expediently arranged in the coolant channels. Such heat exchanger elements increase the surface area available for heat transfer and thereby enable improved heat exchange.
  • 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, has coolant channels 2 and coolant channels 3.
  • carbon dioxide (CO 2 ) is used as a refrigerant in all heat exchangers 1 and, in addition, a refrigerant flow path 7 is deflected at least once in a U-shape. Due to the at least one-time 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 according to the invention also have a ratio between their wall thickness w and their diameter d of at least 0.4 (cf. in particular also Figures 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 preferred.
  • the individual refrigerant channels 3 are arranged in flat tubes 4 running parallel to one another, with a web 5 present between two refrigerant channels 3 having 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 (cf. again the Figures 2 and 3 ).
  • Such thick webs 5 ensure the required tensile strength.
  • the individual refrigerant channels 3 are connected evenly or progressively. Progressive means that the flow cross-sectional area of the refrigerant side increases from one flow path to the next. This takes into account the increasing volume of the refrigerant flow during evaporation. 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 (cf. Figure 3 ), but can also have a square cross section with rounded corners, as for example according to Figure 2 is shown.
  • both the coolant flow path 7 and the coolant flow path 6 are redirected, which results in particularly effective cooling.
  • the refrigerant and the coolant for example a water-glysantine mixture, are in cross-flow in both flow paths 6, 7, just as in the heat exchanger 1 according to FIG Figures 4 and 5 . It is particularly useful here to place the coolant outlet and the coolant inlet in the same section, although the coolant side can of course also be designed with 4 or 6 channels.
  • the heat exchanger 1 according to Figure 5 works in cross-flow and has two flows, both on the coolant side and on the coolant side, and each has a deflection of the coolant flow path 6 and the coolant flow path 7 in width.
  • the heat exchanger 1 according to Figure 4 is designed with 4 flutes and has one compared to that according to the Figure 5 Heat exchanger 1 shown has a higher flow velocity, which improves the heat transfer.
  • the 4-flow design also ensures better protection against overheating.
  • the refrigerant channels 3 are contained 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, preferably even less than 1.5.
  • a collector 8 is, for example, in the Figures 6 and 7 shown.
  • a hydraulic diameter d H of the refrigerant channels 3 is 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. This allows an optimal ratio of pressure drop and heat transfer to 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 coolant channels 3 is greater than 1.0, preferably this ratio is between 1.5 and 3.
  • a two-phase mixture is usually heated on the coolant side, which is usually too significantly worse heat transfer coefficients on the refrigerant side than on the coolant side.
  • heat exchanger elements 9 for example turbulence inserts or corrugated fins, are arranged in the coolant channels 2, which increase the surface area available for heat exchange.
  • the surface available for heat transfer can also be designed to be structured, which in turn increases the surface area. Due to the high pressure load and the requirement for internal cleanliness, a structured surface is required for the refrigerant side, i.e. H. However, it is not specifically suitable for the inner surface of the refrigerant channels 3.
  • the coolant flow path 7 is deflected at least once in a U-shape, specifically in width, whereby the coolant flow path 6 can be deflected in corresponding coolant collectors 10.
  • the coolant flow path 6 and the coolant flow path 7 run in countercurrent.
  • a heat exchanger 1 designed as an R744 evaporator is 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 usually attached to conventional R134a evaporators. However, for R744 and also for components with electronic expansion valves (EXV), these are usually integrated into the circuit separately from heat exchanger 1.
  • the term “unit” is understood to mean that the expansion element 11 (in particular TXV) is mechanically (possibly even cohesively) connected to the evaporator/chiller. Such a unit could be achieved, for example, by integrating the valve housing into the evaporator/chiller flange (+ soldering if necessary).
  • the heat exchanger 1 With the heat exchanger 1 according to the invention, a high performance, ie a high efficiency of the heat exchanger 1 can be achieved, with a small space requirement and a favorable connection situation, in particular if a connection for both the coolant flow path 6 and for the coolant flow path 7 is arranged on the same side of the heat exchanger 1 are.
  • the refrigerant channels 3 designed according to the invention can also ensure high pressure resistance, which enables the use of CO 2 as a 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 (9)

  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 et la voie de circulation de fluide de refroidissement (6) est déviée au moins une fois en forme de U.
  2. Échangeur de chaleur selon la revendication 1,
    caractérisé en ce que
    les canaux de fluide réfrigérant (3) présentent une section transversale carrée avec des coins arrondis.
  3. Échangeur de chaleur selon la revendication 1,
    caractérisé en ce que
    les canaux de fluide réfrigérant (3) sont réalisés de manière ronde ou elliptique.
  4. Échangeur de chaleur selon l'une des revendications 1 à 3,
    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.
  5. Échangeur de chaleur selon l'une des revendications 1 à 4,
    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).
  6. Échangeur de chaleur selon l'une des revendications 1 à 5,
    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.
  7. Échangeur de chaleur selon l'une des revendications 1 à 6,
    caractérisé en ce que
    une voie de circulation de fluide réfrigérant (7) est progressivement réalisée.
  8. Échangeur de chaleur selon l'une des revendications 1 à 7,
    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.
  9. Échangeur de chaleur selon l'une des revendications 1 à 8,
    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 EP3009780B1 (fr) 2017-05-10
EP3009780B2 true EP3009780B2 (fr) 2023-10-18

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ID=54365950

Family Applications (1)

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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 (2)

* 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
US20210285727A1 (en) * 2020-03-10 2021-09-16 University Of Maryland, College Park Cross-flow heat exchanger systems and methods for fabrication thereof

Citations (20)

* 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
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
EP1070929A2 (fr) † 1999-07-20 2001-01-24 Valeo Klimatechnik GmbH Evaporateur pour système de conditionnement d'air pour véhicule automobile
US20030080714A1 (en) † 2001-10-29 2003-05-01 Yoshimitsu Inoue Battery temperature control device for controlling the temperature of battery installed in vehicle
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
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
US20090277606A1 (en) † 2008-05-12 2009-11-12 Reiss Iii Thomas J Heat exchanger support and method of assembling a heat exchanger
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

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005020499A1 (de) 2005-04-29 2006-11-09 Behr Gmbh & Co. Kg Verdampfer, insbesondere Heckverdampfer für ein Kraftfahrzeug
DE102011107281A1 (de) 2011-07-15 2013-01-17 Volkswagen Ag Chiller

Patent Citations (20)

* 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
EP1070929A2 (fr) † 1999-07-20 2001-01-24 Valeo Klimatechnik GmbH Evaporateur pour système de conditionnement d'air pour véhicule automobile
US20030080714A1 (en) † 2001-10-29 2003-05-01 Yoshimitsu Inoue Battery temperature control device for controlling the temperature of battery installed in vehicle
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
US20090277606A1 (en) † 2008-05-12 2009-11-12 Reiss Iii Thomas J Heat exchanger support and method of assembling a heat exchanger
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
EP3009780A1 (fr) 2016-04-20

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