EP1996888B1 - Échangeur thermique pour véhicule automobile - Google Patents

Échangeur thermique pour véhicule automobile Download PDF

Info

Publication number
EP1996888B1
EP1996888B1 EP07723149.6A EP07723149A EP1996888B1 EP 1996888 B1 EP1996888 B1 EP 1996888B1 EP 07723149 A EP07723149 A EP 07723149A EP 1996888 B1 EP1996888 B1 EP 1996888B1
Authority
EP
European Patent Office
Prior art keywords
flow path
flow
heat exchanger
exchanger according
ducts
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
EP07723149.6A
Other languages
German (de)
English (en)
Other versions
EP1996888A1 (fr
Inventor
Christian Domes
Peter Geskes
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
Mahle 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 Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP1996888A1 publication Critical patent/EP1996888A1/fr
Application granted granted Critical
Publication of EP1996888B1 publication Critical patent/EP1996888B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • 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
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F28D7/0075—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the same heat exchange medium flowing through sections having different heat exchange capacities or for heating or cooling the same heat exchange medium at different temperatures
    • 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
    • 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
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/14—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by endowing the walls of conduits with zones of different degrees of conduction of heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/50—Arrangements or methods for preventing or reducing deposits, corrosion or wear caused by impurities
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
    • 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
    • F28F2250/06—Derivation channels, e.g. bypass

Definitions

  • the present invention relates to a heat exchanger for a motor vehicle according to the preamble of claim 1.
  • the document JP2001027157 discloses in Figures 4 and 5 such a heat exchanger.
  • the fluid is the exhaust gas of an internal combustion engine of the motor vehicle.
  • a particularly large temperature difference of typically several 100 ° C is achieved in the fluid cooling, so that the adjustment of the flow resistance of the two downstream flow paths in the course of cooling of the exhaust gas is particularly effective.
  • the first flow path has a smaller flow resistance than the second flow path.
  • the region of the first flow path on average there is a higher temperature difference to the coolant than in the region of the second flow path.
  • a high cooling capacity is already given due to the temperature difference. Due to the temperature of at least gaseous fluids, high pressure losses are present anyway in this region, so that the flow resistance, in particular the generation of turbulence to improve the heat transfer, can be kept relatively small in the first flow path.
  • the fluid is already partially cooled, so that in the second flow path to obtain a sufficient heat transfer advantageously a greater flow resistance, in particular a larger proportion of turbulent flows, is present. In this way, an overall optimization of the heat exchanger performance is achieved taking into account the lowest possible total pressure drop across the heat exchanger.
  • turbulence-generating means are provided in at least one of the two flow paths, whereby the heat exchanger performance is improved.
  • the turbulence-generating means are formed as protruding into the flow path formations of walls of the flow path. These may be dimples or so-called " winglets" (V-shaped aligned embossed webs).
  • the turbulence-generating means may also be deposits defined in the flow path. Such inserts may be, for example, rib ribs or corrugated ribs or the like.
  • all turbulence-generating agents which are known from the prior art are suitable for the purposes of the present invention. What is essential is only the different design of the flow resistances in the first flow path and in the second flow path.
  • ribs are arranged to increase a contact area with the fluid, wherein the ribs in the first flow path and in the second flow path have a different density. Even in a case where, for example, are longitudinal ribs such as corrugated fins, in which predominantly laminar and less turbulent flows are formed, a different density of the ribs leads to different flow resistances.
  • the flow resistances of the flow paths can therefore be influenced in principle both by generating turbulences and by influencing laminar flow fractions.
  • first flow path and the second flow path may each comprise a plurality of separate, parallel flow channels.
  • the number of channels of the first flow path is different, in particular smaller, than the number of channels of the second flow path.
  • the channels of the first flow path can each have a different, in particular larger, cross-sectional area than the channels of the second flow path.
  • the channels of a flow path have different flow resistances among one another.
  • the flow resistance of an outer channel with respect to the deflection region is greater than the flow resistance of an inner channel of the same flow path.
  • the first flow path preferably has a different, in particular larger, free cross-sectional area than the second flow path.
  • free cross-sectional area is meant the geometric cross-sectional area for free flow of the fluid.
  • the flow paths are arranged in a housing through which the coolant flows.
  • the coolant is advantageously a liquid, in particular cooling liquid of a main cooling circuit of the motor vehicle. As a result, an overall effective cooling of the fluid is ensured.
  • the heat exchanger comprises a connection region with a first connection for supplying the fluid to the first flow path and a second connection for discharging the fluid from the second flow path, thereby enabling a compact and cost-saving design of the heat exchanger.
  • an adjusting element is provided in the connection region, by means of which a direct connection of the first connection and the second connection for bypassing the flow paths is selectably adjustable. This makes it possible to bypass the cooling of the fluid selectable, which is desired especially in internal combustion engines of motor vehicles under certain operating conditions such as the warm-up phase of the engine.
  • the flow paths and / or the flow channels are made of aluminum.
  • the flow paths and / or the flow channels are made of stainless steel.
  • the flow paths and / or the flow channels are made of aluminum and stainless steel.
  • the fluid is exhaust gas of an internal combustion engine of the motor vehicle.
  • turbulence-generating means are formed as defined in the flow path deposits.
  • the flow paths are arranged in a housing through which the coolant flows.
  • the flow paths in particular the flow channels made of aluminum and / or stainless steel are formed.
  • Fig. 1 shows a U-flow heat exchanger for cooling recirculated exhaust gas of a motor vehicle diesel engine, in which a first flow path 1 and a second flow path 2 are arranged in parallel and side by side within a housing 3.
  • the housing 3 is flowed through by means of two ports 4, 5 of a liquid coolant, which is branched off from a main cooling circuit of the diesel engine.
  • the flow paths 1, 2 each comprise a number of flow channels 6, 7, which in the present case are designed as flat tubes with a rectangular cross-section.
  • the cross section can in principle also have another, approximately round, shape.
  • the connection region 8 has a first connection 9 for supplying exhaust gas of a diesel engine of the motor vehicle and a second connection 10 for discharging the cooled exhaust gas.
  • a control element 11 designed as a pivotable flap is provided, which is adjustable via a rotary shaft 12.
  • the exhaust gas is passed from the first port 9 in the first flow path 1, where it first undergoes a first cooling. After flowing through the first flow path 1, the exhaust gas enters a deflecting region 13 arranged at the end of the housing 3.
  • the deflection region 13 here is a substantially semi-cylindrical, hollow housing part, in which the exhaust gas flow is deflected by 180 °, after which it enters the second flow path 2.
  • the second flow path 2 flows through the exhaust gas in the opposite direction to the first flow path 1, wherein it undergoes a further cooling.
  • When leaving the second Flow path 2 enters the exhaust gas again in the connection area 8, where it in the case of the first position of the actuating element 11 according to Fig. 1 is guided in the second terminal 10.
  • each of the flow paths 1, 2 comprises a bundle of nine flow channels 6, 7 each of rectangular cross-section.
  • the outer dimensions of the flow channels 6, 7 are each identical.
  • the flow channels 6 of the first flow path 1 and the flow channels 7 of the second flow path 2 turbulence generating means in the form of indentations 6a, 7a, which have a different size.
  • the impressions 6a of the first flow channels 6 protrude less deeply into the channel cross section than the impressions 7a of the second flow channels 7. In this way, the geometric free flow cross section of the second flow channels 7 becomes smaller compared to the geometric free cross section of the first flow channels 6.
  • more turbulence is introduced into the exhaust gas flow in the second flow channels 7 through the deeper protruding turbulence-generating means 7a than in the first flow channels 6.
  • the turbulence-generating means 6a, 7a can be dimples and / or winglets. Alternatively or in addition, it may also be in itself act known structured deposits, which are inserted into the flow channels 6, 7 and welded.
  • the second heat exchanger In the second heat exchanger according to Fig. 3 is the first flow path 1 as well as constructed in the first heat exchanger.
  • the second flow path 2 In contrast to the first heat exchanger, the second flow path 2 not only has different turbulence-generating means 7a, but also has a smaller number of flow channels 7 than the first flow path 1, which have a different outer dimension relative to the flow channels 6 of the first flow path 1.
  • the second flow path comprises fewer flow channels 7 with a larger external dimension, a greater flow resistance is generated for the second flow path 2 by the deeper projecting turbulence-generating means 7a than for the first flow path 1. Due to the changed number and outer geometry of the flow channels 7 the flow resistance of the second flow path in the second embodiment is slightly smaller than the flow resistance of the second flow path in the first heat exchanger.
  • each of the flow paths 1, 2 each have three parallel flat tubes 6, 7 as flow channels, each having identical outer dimensions.
  • the flow channels 6, 7 are provided with rib-like inserts 6b, 7b, whereby the contact area between the exhaust gas flow and heat-conducting metal is increased.
  • fewer fins are provided in the case of the flow channels 6 of the first flow path 1 than in the case of the flow channels 7 of the second flow path 2. Due to the greater fin density of the second flow path 2 with otherwise identical dimensions and numbers the flow channels 6, 7, the second flow path 2 has a greater flow resistance than the first flow path 1.
  • the embodiment illustrates that even with predominantly laminar flows by appropriate design of the flow channels 6, 7 different flow resistance can be generated.
  • the fluid to be cooled is in particular exhaust gas.
  • the fluid to be cooled charge air, oil, especially transmission oil, a water-containing cooling liquid, refrigerant of an air conditioner such as CO2.
  • the heat exchanger is at least one exhaust gas cooler.
  • the heat exchanger is at least one intercooler and / or an oil cooler and / or a coolant radiator and / or a condenser of an air conditioner and / or an evaporator of an air conditioner and / or a gas cooler of an air conditioner.
  • the heat exchanger is a combination of at least one exhaust gas cooler and at least one other of the aforementioned heat exchangers.
  • the heat exchanger has a flow resistance of the flow path 1, which is between 0.1% and 300%, in particular between 1% and 100%, in particular between 5% and 80%, between 10% and 70%, between 20 % and 60%, between 30% and 50% is above the flow resistance of the flow path 2, preferably only 10% above the flow resistance of the flow path. 2
  • the flow resistance of the first flow path 1 is below the flow resistance of the flow path 2.
  • Heat exchangers with a deflection region 13 are referred to as U-flow heat exchangers, since the fluid to be cooled flows in a first flow path as far as a deflection section and flows back in a first flow path in the first flow path after deflection in a second flow path substantially in the opposite direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (14)

  1. Echangeur de chaleur pour un véhicule automobile, comprenant un carter, une première voie d'écoulement (1), une zone de retour de flux (13) disposée en aval de la première voie d'écoulement (1), et comprenant une seconde voie d'écoulement (2) disposée en aval de la zone de retour de flux (13), où le carter est traversé par un moyen de refroidissement, et les voies d'écoulement sont disposées dans le carter, où la première et la seconde voie d'écoulement (1, 2) sont traversées par un fluide à refroidir, et où la première et la seconde voie d'écoulement (1, 2) sont baignées par le moyen de refroidissement servant à la dissipation de la chaleur, où la seconde voie d'écoulement (2) présente une résistance d'écoulement différente de celle de la première voie d'écoulement (1), caractérisé en ce que des nervures (6b, 7b) sont disposées dans les voies d'écoulement (1, 2), lesdites nervures servant à augmenter une surface de contact avec le fluide, où les nervures (6b, 7b) présentent une densité différente dans la première voie d'écoulement (1) et dans la seconde voie d'écoulement (2).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que la première voie d'écoulement (1) présente une résistance d'écoulement plus faible que celle de la seconde voie d'écoulement (2).
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que la première voie d'écoulement (1) présente une résistance d'écoulement plus forte que celle de la seconde voie d'écoulement (2).
  4. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que des moyens (6a, 7a) produisant des turbulences sont prévus dans au moins l'une des deux voies d'écoulement (1, 2).
  5. Echangeur de chaleur selon la revendication 4, caractérisé en ce que les moyens (6a, 7a) produisant des turbulences sont conçus comme des parties saillantes de parois de la voie d'écoulement, lesdites parties saillantes pénétrant dans le canal d'écoulement (6, 7).
  6. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que la première voie d'écoulement (1) et la seconde voie d'écoulement (2) comprennent respectivement une pluralité de conduits d'écoulement (6, 7) parallèles et séparés.
  7. Echangeur de chaleur selon la revendication 6, caractérisé en ce que le nombre des conduits (6) de la première voie d'écoulement est différent, en particulier inférieur au nombre des conduits (7) de la seconde voie d'écoulement.
  8. Echangeur de chaleur selon l'une des revendications 6 ou 7, caractérisé en ce que les conduits (6) de la première voie d'écoulement présentent à chaque fois une surface de section transversale différente, en particulier plus grande que celle des conduits (7) de la seconde voie d'écoulement.
  9. Echangeur de chaleur selon l'une quelconque des revendications 6 à 8, caractérisé en ce que les conduits (6, 7) d'une voie d'écoulement présentent des résistances d'écoulement différentes les unes des autres.
  10. Echangeur de chaleur selon la revendication 9, caractérisé en ce que la résistance d'écoulement d'un conduit se trouvant à l'extérieur par rapport à la zone de retour de flux (13) est plus importante que la résistance d'écoulement d'un conduit de la même voie d'écoulement, ledit conduit se trouvant à l'intérieur.
  11. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que la première voie d'écoulement (1) présente une surface de section transversale libre qui est différente, en particulier plus grande par rapport à celle de la seconde voie d'écoulement (2).
  12. Echangeur de chaleur selon l'une quelconque des revendications 1 à 11, caractérisé en ce que le moyen de refroidissement est un liquide, en particulier un liquide de refroidissement d'un circuit de refroidissement principal du véhicule automobile.
  13. Echangeur de chaleur selon l'une quelconque des revendications précédentes, comprenant en outre une zone de raccordement (8) comportant un premier raccord (9) destiné à la conduite d'alimentation du fluide fourni à la première voie d'écoulement (1) et un second raccord (10) servant à l'évacuation du fluide provenant de la seconde voie d'écoulement (2).
  14. Echangeur de chaleur selon la revendication 13, caractérisé en ce que la zone de raccordement (8) comprend un actionneur (11) au moyen duquel une connexion directe du premier raccord (9) et du second raccord (10) peut être réglée de manière sélective pour le contournement des voies d'écoulement (1, 2).
EP07723149.6A 2006-03-10 2007-03-09 Échangeur thermique pour véhicule automobile Active EP1996888B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006011592 2006-03-10
PCT/EP2007/002084 WO2007104491A1 (fr) 2006-03-10 2007-03-09 Échangeur thermique pour véhicule automobile

Publications (2)

Publication Number Publication Date
EP1996888A1 EP1996888A1 (fr) 2008-12-03
EP1996888B1 true EP1996888B1 (fr) 2019-07-24

Family

ID=38222113

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07723149.6A Active EP1996888B1 (fr) 2006-03-10 2007-03-09 Échangeur thermique pour véhicule automobile

Country Status (5)

Country Link
US (1) US8573286B2 (fr)
EP (1) EP1996888B1 (fr)
CN (1) CN101400960B (fr)
DE (1) DE102007011953A1 (fr)
WO (1) WO2007104491A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10333577A1 (de) * 2003-07-24 2005-02-24 Bayer Technology Services Gmbh Verfahren und Vorrichtung zur Entfernung von flüchtigen Substanzen aus hochviskosen Medien
ATE464459T1 (de) * 2003-10-02 2010-04-15 Behr Gmbh & Co Kg Ladeluftkühler eines kraftfahrzeuges
DE102008018594A1 (de) * 2007-04-11 2008-10-16 Behr Gmbh & Co. Kg Wärmetauscher
FR2923859B1 (fr) * 2007-11-15 2009-12-18 Valeo Systemes Thermiques Branche Thermique Habitacle Echangeur de chaleur pour circuit d'alimentation en air d'un moteur de vehicule automobile
US20110100342A1 (en) * 2009-11-02 2011-05-05 International Engine Intellectual Property Company Llc Forced convection egr cooling system
DE102011007748A1 (de) * 2011-04-20 2012-10-25 Behr Gmbh & Co. Kg Abgaskühler zum Kühlen von Verbrennungsabgas einer Verbrennungskraftmaschine, Wassersammeladapter, Abgaskühlsystem und Verfahren zum Herstellen eines Abgaskühlsystems
WO2013085771A1 (fr) * 2011-12-08 2013-06-13 Carrier Corporation Procédé et appareil de formation de tubes d'échangeur de chaleur
DE102012202883A1 (de) * 2012-02-24 2013-08-29 Bayerische Motoren Werke Aktiengesellschaft Wärmetauscher
DE102013221151A1 (de) * 2013-10-17 2015-04-23 MAHLE Behr GmbH & Co. KG Wärmeübertrager
DE102013224038A1 (de) * 2013-11-25 2015-05-28 MAHLE Behr GmbH & Co. KG Abgaswärmetauscher zur Abgaskühlung einer Brennkraftmaschine, vorzugsweise für ein Kraftfahrzeug
US10690233B2 (en) * 2016-07-27 2020-06-23 Ford Global Technologies, Llc Bypass control for U-flow transmission oil coolers
US20180156165A1 (en) * 2016-12-07 2018-06-07 Ford Global Technologies, Llc Charge air cooler with an integrated bypass
JP2018169073A (ja) * 2017-03-29 2018-11-01 株式会社デンソー 熱交換器
JP6915460B2 (ja) * 2017-08-30 2021-08-04 株式会社デンソー 空調ユニット
CN110043975B (zh) * 2019-04-19 2024-06-18 青岛海尔空调器有限总公司 一种散热器、空调室外机和空调器
KR20210066557A (ko) * 2019-11-28 2021-06-07 현대자동차주식회사 차량의 인터쿨러

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1834070A (en) * 1928-05-14 1931-12-01 Parkinson Heater Corp Heating device
US3161234A (en) * 1962-10-16 1964-12-15 United Aircraft Corp Multipass evaporator
US3211217A (en) * 1963-07-12 1965-10-12 Westinghouse Electric Corp Fluid reversing valve structure
US3447602A (en) * 1967-06-22 1969-06-03 David Dalin Heat exchanger especially adapted for indirect heat transfer by convection
DE3103198A1 (de) 1981-01-30 1982-08-26 Oskar Dr.-Ing. 8031 Stockdorf Schatz Waermetauscher fuer den betrieb mit abgasen von kolbenmotoren, insbesondere fuer die beheizung von kraftfahrzeugen
DE3140687A1 (de) 1981-10-13 1983-04-28 Michael 8011 Putzbrunn Behncke Rohrwaermetauscher
US5314009A (en) * 1992-10-08 1994-05-24 Gas Research Institute Exhaust gas recuperator
JP2001027157A (ja) 1999-07-13 2001-01-30 Mitsubishi Motors Corp Ｅｇｒクーラの構造
US6318455B1 (en) * 1999-07-14 2001-11-20 Mitsubishi Heavy Industries, Ltd. Heat exchanger
GB0001283D0 (en) * 2000-01-21 2000-03-08 Serck Heat Transfer Limited Twin flow valve gas cooler
DE10216773B4 (de) 2002-04-15 2004-09-16 Benteler Automobiltechnik Gmbh Kühler für ein dem Hauptabgasstrom eines Verbrennungsmotors entnommenes Abgas
US6634419B1 (en) * 2002-05-31 2003-10-21 Honeywell International Inc. Multi-pass exhaust gas recirculation cooler
DE10302948A1 (de) * 2003-01-24 2004-08-05 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Abgaskühler für Kraftfahrzeuge
US6948559B2 (en) * 2003-02-19 2005-09-27 Modine Manufacturing Company Three-fluid evaporative heat exchanger
US7337832B2 (en) * 2003-04-30 2008-03-04 Valeo, Inc. Heat exchanger
ES2234398B1 (es) 2003-04-30 2006-12-01 Valeo Termico, S.A. Intercambiador de calor, en especial de los gases de escape de un motor.
US7073573B2 (en) * 2004-06-09 2006-07-11 Honeywell International, Inc. Decreased hot side fin density heat exchanger

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102007011953A1 (de) 2007-11-15
US20090090495A1 (en) 2009-04-09
WO2007104491A1 (fr) 2007-09-20
US8573286B2 (en) 2013-11-05
EP1996888A1 (fr) 2008-12-03
CN101400960A (zh) 2009-04-01
CN101400960B (zh) 2010-12-29

Similar Documents

Publication Publication Date Title
EP1996888B1 (fr) Échangeur thermique pour véhicule automobile
EP1999423B1 (fr) Refroidisseur de gaz d'echappement pour véhicule automobile
EP1985953B1 (fr) Echangeur thermique, en particulier destiné au refroidissement des gaz d'échappement, procédé d'utilisation d'un tel échangeur et système comprenant un refroidisseur EGR
EP1800078B1 (fr) Échangeur de chaleur de gaz d'échappement refroidi par air, en particulier refroidisseur de gaz d'échappement pour véhicules automobiles
EP1837499B1 (fr) Dispositif destiné au refroidissement d'un flux de gaz d'échappement
WO2004065876A1 (fr) Echangeur thermique, notamment refroidisseur de gaz d'echappement pour automobiles
DE102008036222B3 (de) Wärmeübertragungseinheit für eine Verbrennungskraftmaschine
DE102006012219B4 (de) Wärmeübertragungseinheit mit einem verschließbaren Fluidteileinlass
EP1941224A1 (fr) Echangeur thermique
EP2044319A1 (fr) Dispositif de refroidissement d'un flux de gaz d'un moteur à combustion interne
EP1454106A1 (fr) Echangeur thermique
EP1911946A2 (fr) Dispositif de refroidissement de l'air de suralimentation pour un moteur à combustion interne, système doté d'un dispositif de refroidissement de l'air de suralimentation
DE112013007041B4 (de) Wärmetauscher
DE102007005370A1 (de) Wärmetauscher
EP2134941B1 (fr) Canal d'écoulement, échangeur de chaleur, système de recyclage des gaz d'échappement, système d'apport d'air de suralimentation et utilisation d'un échangeur de chaleur
DE102007013302A1 (de) Wärmetauscher für ein Kraftfahrzeug
EP2159394A2 (fr) Refroidisseur de gaz d'échappement pour un moteur à combustion
DE102015110974B4 (de) Abgaswärmeübertrager mit mehreren Wärmeübertragerkanälen
EP2863157B1 (fr) Échangeur de chaleur
DE102006029043B4 (de) Wärmeübertragungseinheit für eine Verbrennungskraftmaschine
DE102007033148A1 (de) Vorrichtung zur Kühlung eines Gasstroms eines Verbrennungsmotors
DE102007041338B3 (de) Wärmeübertragungseinheit für eine Verbrennungskraftmaschine
DE102005036045B4 (de) Kühlvorrichtung für Verbrennungskraftmaschinen
DE102007041357A1 (de) Wärmetauscher, insbesondere für ein Kraftfahrzeug
EP2278149A2 (fr) Echangeur thermique et système de chargement

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20081010

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20150224

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAHLE BEHR GMBH & CO. KG

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20190327

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAL Information related to payment of fee for publishing/printing deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR3

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

GRAR Information related to intention to grant a patent recorded

Free format text: ORIGINAL CODE: EPIDOSNIGR71

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

INTC Intention to grant announced (deleted)
AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

INTG Intention to grant announced

Effective date: 20190617

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502007016732

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1158697

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190815

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190724

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191125

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191024

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191025

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191124

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200224

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502007016732

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG2D Information on lapse in contracting state deleted

Ref country code: IS

26N No opposition filed

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20200331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200331

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200309

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200331

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200309

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1158697

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190724

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240320

Year of fee payment: 18

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20240521