EP2029883A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur

Info

Publication number
EP2029883A1
EP2029883A1 EP07725749A EP07725749A EP2029883A1 EP 2029883 A1 EP2029883 A1 EP 2029883A1 EP 07725749 A EP07725749 A EP 07725749A EP 07725749 A EP07725749 A EP 07725749A EP 2029883 A1 EP2029883 A1 EP 2029883A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
exchanger tube
tube
exchanger
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.)
Withdrawn
Application number
EP07725749A
Other languages
German (de)
English (en)
Inventor
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
Behr GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2029883A1 publication Critical patent/EP2029883A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F02M26/11—Manufacture or assembly of EGR systems; Materials or coatings specially adapted for EGR systems
    • 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
    • F02M26/31—Air-cooled heat exchangers
    • 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
    • F28F1/045—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular with assemblies of stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • 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
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • 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
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/06—Low pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust downstream of the turbocharger turbine and reintroduced into the intake system upstream of the compressor
    • 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
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to a heat exchanger, in particular for a motor vehicle, according to the preamble of claim 1.
  • heat exchangers have been developed for cooling gas streams for exhaust gas recirculation (EGR), which at least partially, possibly mixed with charge air, exhaust gas of an internal combustion engine.
  • EGR exhaust gas recirculation
  • the cooled exhaust gases are usually returned to the internal combustion engine to reduce pollutant emissions on the intake side.
  • These fluids to be cooled are not only of high temperature, but also very acidic.
  • condensates with a pH between about 1 and 3 can deposit, so that high demands are placed on the corrosion resistance of the heat exchanger, especially at high temperatures.
  • Regularly such heat exchangers are therefore made of stainless steel or similar materials.
  • a further preferred embodiment of the heat exchanger is characterized in that the outer wall thickness of the exchanger tube is preferably between 0.4 and 2 mm.
  • the outer wall thickness of the exchanger tube is the wall thickness of the outwardly facing wall of the tube.
  • a further preferred embodiment of the heat exchanger is characterized in that the exchanger tube has webs with a web thickness which is smaller than or equal to the outer wall thickness of the exchanger tube. This range has proved to be particularly advantageous in the context of the present invention.
  • a further preferred embodiment of the heat exchanger is characterized in that separate channels are produced by ribs which are inserted and soldered into the exchanger tubes. Through the inserted ribs all separate channels of an exchanger tube can be created. However, it is possible to create additional separate channels in an exchanger tube which already contains separate channels, for example produced by extrusion.
  • the heat exchanger comprises a bottom, wherein the exchanger tube terminates in the bottom end and is firmly connected to the bottom.
  • the exchanger tube can be fixed to the floor by means of one of the group of induction brazing, flame brazing, laser welding or welding. It is important that the connection between the exchanger tube extruded section and the floor is only local and if possible only external and as small as possible. heat experiences. It is believed that the surprising corrosion properties of the extruded-profile exchanger tubes are due to a particularly fine crystal structure, which is produced in particular during the process of extruding the aluminum alloy. Subsequent heating of the extruded-profile exchanger tubes can result in coarseness of the material and deteriorate the corrosion properties.
  • a heat treatment of the entire cooler can be implemented. Although the overall thermal treatment of the cooler block, the grain structure of the aluminum material coarser, but extruded tubes still have a good corrosion behavior due to the low material contamination and the smooth surface.
  • ribs and pipes are soldered and also the connection between pipes and soil takes place by soldering.
  • the soldering can be done in a vacuum or Nocolok process.
  • This rib e.g., rib gutter or tubulence generator
  • Such ribs can also be additionally protected against corrosion.
  • the exchanger tube can alternatively or additionally also be fixed to the floor by means of adhesion. With this possibility of fixing, no local heating of the exchanger tube takes place in the course of assembly.
  • Another alternative or supplemental fixation without heating may be by mechanical means in conjunction with a seal.
  • the exchanger tube does not undergo complete heat treatment in the course of assembly of the heat exchanger, which exceeds a temperature of extruding in the course of production of the exchanger tube. If such temperatures in the case of welding or soldering in the field of fixing the Exchanger tubes are reached on the ground, so this should be locally limited at most.
  • At least one rib element is arranged in thermal contact on the exchanger tube.
  • the rib element is glued to the exchanger tube in a particularly preferred manner. In this way it is prevented that the extruded exchanger tube undergoes further heating after its production process, which could worsen the corrosion resistance of the exchanger tube in the sense described above.
  • Such bonding is preferably carried out by an adhesive based on epoxy resin, wherein in particular the adhesive is mixed with metal powder.
  • the metal powder may be aluminum powder or other suitable metal powder.
  • Such adhesives are well known and have not only a high strength but also a high temperature resistance.
  • the adhesive of the bond has a temperature resistance which is at least about 180 ° C., preferably at least about 200 ° C.
  • the rib member may be resiliently pressed against the exchanger tube. Basically, it can be dispensed with a bonding with a resilient pressure. However, a combination of resilient pressure and bonding in terms of a simplified installation of the heat exchanger is advantageous.
  • a thermally conductive paste may be provided between the exchanger tube and the rib element.
  • a paste may possibly have a higher temperature resistance than known adhesives, so that the combination of a spring-elastic holder with a thermal compound is particularly preferred.
  • a further preferred embodiment of the heat exchanger is characterized in that the rib elements are soldered on the outside with the exchanger tubes. By soldering a cohesive connection is created with good thermal conductivity properties.
  • Another preferred embodiment of the heat exchanger is characterized in that the soldering takes place in a soldering oven by means of vacuum or Nocolok soldering.
  • the rib member is formed as a particular corrugated, arranged between two adjacent exchanger channels sheet metal part.
  • the heat exchanger has at least one box for supplying or discharging the fluid to the at least one exchanger tube.
  • the box consists essentially of an aluminum alloy.
  • the box on the temperature-reduced outlet side of the box but also made of a plastic, in particular a polyamide exist.
  • all known embodiments of heat exchanger boxes are possible insofar as they are compatible with the corrosive and thermal requirements of an exhaust gas heat exchanger.
  • a bypass line can be provided, the fluid flow being selectable by means of an actuator Bypass line or through which at least one exchanger tube is feasible.
  • Such bypass lines for bypassing exhaust gas cooling are often desired to account for various operating conditions of the internal combustion engine.
  • the heat exchanger can have at least one leading and at least one substantially parallel return exchanger tube, which are connected to one another in a deflection region.
  • the heat exchanger is designed as a "U-flow" heat exchanger, which allows a particularly large cooling of the gas flow at a given size.
  • the maximum operating temperature of the fluid supplied to the heat exchanger is less than about 300 ° C., in particular less than about 250 ° C. This is advantageous when the heat exchanger has adhesions.
  • the heat exchanger according to the invention is then provided as a second stage of exhaust gas cooling and preferably arranged after a liquid-cooled first exhaust gas cooler.
  • the arrangement of the heat exchanger according to the invention can be carried out in a system of high-pressure exhaust gas recirculation as well as in a system of low-pressure exhaust gas recirculation.
  • pure charge air, pure exhaust gas or a gas mixture of charge air and exhaust gas is passed through the heat exchanger according to the invention.
  • the invention also includes the use of an aluminum extruded profile as the exchanger tube of a heat exchanger according to one of claims 1 to 21.
  • Such profiles can be carried out with continuous webs or else have webs which are interrupted in order to avoid blocking by sooting. Also, icing of the cooler is avoided in cold temperatures when the hydraulic diameters are not too high be chosen small.
  • the hydraulic diameter is in the range between 1, 5 and 4 mm.
  • the distances between the webs can be less than 1-3 mm, for a gas with soot, distances greater than 1-3 mm are preferable.
  • the tube thickness, i. the shorter length of the tube is ideally in the range 4-10 mm and the tube width in the range 8-100 mm.
  • the outside wall has a thickness that exceeds the thicknesses normally used in coolers. This increased thickness is required to be sufficiently protected against corrosion attack.
  • the thickness is preferably chosen in the range 0.4-2 mm, with a thickness between 0.7 and 1.2 mm being ideal. Thickness is also called wall thickness.
  • the web thickness is equal to or equal to the wall thickness. This provides a system that is optimal in terms of corrosion, cost, pressure drop, and thermodynamics.
  • Fig. 5 is a side elevational view of a fifth embodiment of the invention.
  • the heat exchanger is arranged as a second stage after a not shown, known liquid-cooled heat exchanger in the exhaust stream.
  • the exchanger tubes or extruded profiles 4 are generally not subjected to any special corrosion protection after extrusion.
  • the parallel exchanger tubes 4 open into an outlet-side collection box 5, which comprises a bottom 6 and the inlet-side box 2 is substantially equal.
  • each rib elements 7 are arranged.
  • the row of exchanger tubes 4 terminates in each case with a side part 8, which on the one hand has covering and protective functions and on the other hand terminates an end-side rib 7 on a respective outer exchanger tube 4.
  • the exchanger tubes 4 by means of a local soldering, z.
  • a local soldering As flame brazing, induction brazing or the like. It is important that the exchanger tubes 4 after their extrusion no complete heating to temperatures experienced, which are comparable to the temperatures of the extrusion process or are higher. This ensures that the microcrystalline structure of the exchanger tubes 4 caused by the extrusion is maintained. This in turn, according to previous findings, is essential for a good corrosion resistance of the exchanger tubes 4.
  • the local soldering of the exchanger tubes 4 to the bottoms 3, 6 is preferably carried out such that at least the surfaces of the exchanger tubes facing the exhaust gas do not experience a thermally induced change in their crystal structure and thus their corrosion resistance.
  • the rib elements 7 each consist of sheets extending over the entire width of the heat exchanger, which have gills 11 to increase their surface area. As shown in the lateral plan view, the rib elements 7" form a stack of by suitable means Each of the rib elements 7 "in this case comprises a number of exchanger tubes 4 corresponding number of mutually aligned punched-out. In the course of assembly, the exchanger tubes 4 are inserted through the stack of rib elements 7 "or the aligned punched-out portions In the present exemplary embodiment, the exchanger tubes 4 and the associated stampings are of substantially elliptical cross-section.
  • FIG. 5 is similar to the first embodiment of FIG. 1, wherein a frame of transverse struts 13 is provided, so that a mechanical tension of the exchanger tubes 4 and rib elements 7 is given between the end-side side parts 8.
  • a bracing can be dispensed with bonding of the rib elements 7 to the exchanger tubes 4.
  • the bracing tion according to FIG. 5 an overall improved mechanical stability of the heat exchanger.
  • FIG. 6 shows a heat exchanger corresponding to the first embodiment with respect to the exchanger tubes 4 and fin elements 7.
  • a first box 14 has both an inlet-side connecting piece 15 and an outlet-side connecting piece 16.
  • the relative to the exchanger tubes 4 opposite box 17 is closed and causes only a connection of the exchanger tubes 4 with each other.
  • An actuator 18 within the first box 14 connects depending on its position, the inlet nozzle 15 directly to the outlet 16 (dashed line) or separates the nozzle 15, 16 from each other.
  • the box 14 forms a bypass channel, bypassing the exchanger tubes 4.
  • the heat exchanger works on the principle of a U-flow heat exchanger.
  • the exhaust gas enters through the first port, flows through the two according to FIG. 6, the two exchanger tubes 4, is deflected in the second box 17 and flows in the opposite direction, the upper two exchanger tubes 4, after which it exits the outlet 16.
  • FIGS. 7 to 10 a heat exchanger tube is shown in cross section according to further embodiments.
  • the illustrated heat exchanger tubes 4 are each designed as extruded profiles with a closed rectangular cross section 40. Inside the rectangular cross-section 40, an overall substantially rectangular cavity 41 is divided into individual channels 4a or chambers. The individual channels 4a are separated from one another by webs 43, 44.
  • the cavity 41 in the interior of the rectangular cross section 40 is divided by a total of seven continuous webs 43, 44 in eight channels or chambers 4a.
  • the webs 43, 44 extend parallel to the short sides and perpendicular to the long sides of the rectangular cross section 40.
  • the extent of the rectangular cross section in the direction of the short sides is shown in FIG. records.
  • the extent rd is also referred to as thickness.
  • the extension of the rectangular cross-section 40 in the direction of the long sides is designated rb in FIG.
  • the expansion rb is also referred to as tube width.
  • the thickness of the outer wall of the rectangular cross-section 40 is designated by d in FIG. 7 and is also referred to as wall thickness or wall thickness.
  • the thickness of the webs 43, 44 is designated s in FIG. 7 and is also referred to as web thickness s.
  • the hydraulic diameters, that is, the inner diameters, of the channels 4a should not be too small to avoid undesirable freezing of the cooler at cold temperatures.
  • the hydraulic diameter of the channels 4a is in the range between 1, 5 and 4 mm.
  • the rectangular cross-section 40 can also be equipped with interrupted webs 48.
  • the web 48 comprises two web portions 49, 50, each extending from the long sides of the rectangular cross section 40 vertically inward, but not touching.
  • the interrupted design of the webs 48 serves to avoid undesirable fouling by sooting.
  • an interrupted web 48 alternates with a continuous web 43, 44.
  • the outer channels or chambers 64, 65 are each provided with two stiffening ribs 66, 67; Equipped 68, 69, which extend like a truss in the corners of the associated chamber 64, 65.
  • the stiffening ribs 66 to 68 increase the strength, especially at pressure pulsations and thermal cycling.

Landscapes

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

Abstract

L'invention concerne un échangeur de chaleur, en particulier pour un véhicule automobile, lequel échangeur comporte au moins un tube échangeur (4) permettant le passage d'un fluide gazeux. Ce fluide contient ou peut contenir des gaz d'échappement d'un moteur à combustion, au moins en mélange, et un réfrigérant destiné à refroidir le flux de fluide peut circuler autour du tube échangeur (4). Selon ladite invention, ce tube échangeur (4) est réalisé sous la forme d'un profilé extrudé à partir d'un alliage à base d'aluminium.
EP07725749A 2006-06-01 2007-06-01 Échangeur de chaleur Withdrawn EP2029883A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006026037 2006-06-01
PCT/EP2007/004869 WO2007137863A1 (fr) 2006-06-01 2007-06-01 Échangeur de chaleur

Publications (1)

Publication Number Publication Date
EP2029883A1 true EP2029883A1 (fr) 2009-03-04

Family

ID=38480567

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07725749A Withdrawn EP2029883A1 (fr) 2006-06-01 2007-06-01 Échangeur de chaleur

Country Status (3)

Country Link
EP (1) EP2029883A1 (fr)
CN (1) CN101454559B (fr)
WO (1) WO2007137863A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8113269B2 (en) * 2007-02-22 2012-02-14 Thomas & Betts International, Inc. Multi-channel heat exchanger
DE102008031158A1 (de) * 2008-07-03 2010-01-07 Behr Gmbh & Co. Kg Stangpressrohr für einen Wärmetauscher
ES2385952B1 (es) * 2009-04-22 2013-06-17 Valeo Termico, S.A. Intercambiador de calor para gases, en especial de los gases de escape de un motor.
US9404691B2 (en) * 2013-07-24 2016-08-02 Cale Patrick Collins Kaupp Condensing heat recovery unit for a portable fluid heater
DE102014213088A1 (de) * 2014-07-04 2016-01-07 Mahle International Gmbh Flachrohr
CN207688684U (zh) * 2015-06-11 2018-08-03 谢彦君 波形翅片式换热器
CN106323043A (zh) * 2016-09-30 2017-01-11 如东双洋机械设备有限公司 一种压缩空气预冷器

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3113100B2 (ja) * 1992-11-05 2000-11-27 株式会社デンソー 多穴管押出用ダイス及び多穴管
US5323851A (en) * 1993-04-21 1994-06-28 Wynn's Climate Systems, Inc. Parallel flow condenser with perforated webs
JPH1047879A (ja) * 1996-07-26 1998-02-20 Mitsubishi Materials Corp 熱交換器
US6397939B1 (en) * 2000-12-13 2002-06-04 Modine Manufacturing Company Tube for use in serpentine fin heat exchangers
KR100906769B1 (ko) * 2002-01-31 2009-07-10 한라공조주식회사 오뚜기형 유로를 갖는 열교환기용 튜브 및 이를 이용한열교환기
US6793012B2 (en) * 2002-05-07 2004-09-21 Valeo, Inc Heat exchanger
CA2425233C (fr) * 2003-04-11 2011-11-15 Dana Canada Corporation Echangeur thermique a plaques a ailettes a refroidissement sur surface froide
DE10349140A1 (de) * 2003-10-17 2005-05-12 Behr Gmbh & Co Kg Wärmeübertrager, insbesondere für Kraftfahrzeuge
US7661415B2 (en) * 2004-09-28 2010-02-16 T.Rad Co., Ltd. EGR cooler

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007137863A1 *

Also Published As

Publication number Publication date
CN101454559B (zh) 2012-07-18
WO2007137863A1 (fr) 2007-12-06
CN101454559A (zh) 2009-06-10

Similar Documents

Publication Publication Date Title
EP2092259B1 (fr) Échangeur de chaleur
EP1800078B1 (fr) Échangeur de chaleur de gaz d'échappement refroidi par air, en particulier refroidisseur de gaz d'échappement pour véhicules automobiles
EP1279805B1 (fr) Refroidisseur de l'air de charge aéroréfrigérée
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
EP1901020B1 (fr) Echangeur thermique à plaques superposées destiné au refroidissement d'air de suralimentation
EP1999423A2 (fr) Échangeur thermique pour véhicule automobile
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
WO2008092677A1 (fr) Échangeur de chaleur
WO2007137863A1 (fr) Échangeur de chaleur
EP1604163A1 (fr) Echangeur thermique, notamment refroidisseur de gaz d'echappement pour automobiles
DE102004013682A1 (de) Wärmeübertrager, insbesondere Luft/Luft-Kühler
EP1996888A1 (fr) Échangeur thermique pour véhicule automobile
EP2088299B1 (fr) Echangeur thermique destiné au refroidissement de l'air de suralimentation, procédé destiné à la fabrication d'un échangeur thermique destiné au refroidissement de l'air de suralimentation
DE102007031824A1 (de) Wärmetauscher
EP1522813A1 (fr) Echangeur de chaleur et son procédé de fabrication
DE102005055482A1 (de) Wärmetauscher für einen Verbrennungsmotor
EP2064510B1 (fr) Echangeur de chaleur a double flux avec canal de derivation integre
DE102007025883A1 (de) Wärmetauscher
EP1706698A1 (fr) Echangeur de chaleur
DE102006055122A1 (de) Wärmeübertrager
EP1491843A2 (fr) Echangeur de chaleur, en particulier refroidisseur d'air de suralimentation pour vehicules utilitaires
EP3039372B1 (fr) Échangeur de chaleur
DE102008020230A1 (de) Wärmetauscher sowie Wärmetauscherrohr
EP1563239B1 (fr) Echangeur de chaleur
EP3009780B2 (fr) Fluide caloporteur

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: 20090105

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

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

DAX Request for extension of the european patent (deleted)
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: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20150106