US20100243220A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US20100243220A1
US20100243220A1 US12/514,476 US51447607A US2010243220A1 US 20100243220 A1 US20100243220 A1 US 20100243220A1 US 51447607 A US51447607 A US 51447607A US 2010243220 A1 US2010243220 A1 US 2010243220A1
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US
United States
Prior art keywords
heat exchanger
exchanger according
extruded profile
flow channel
canceled
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.)
Abandoned
Application number
US12/514,476
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English (en)
Inventor
Peter Geskes
Juergen Barwig
Jens Ruckwied
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
Assigned to BEHR GMBH & CO. KG reassignment BEHR GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RUCKWIED, JENS, BARWIG, JUERGEN, GESKES, PETER
Publication of US20100243220A1 publication Critical patent/US20100243220A1/en
Abandoned legal-status Critical Current

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    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0471—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 bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0418—Layout of the intake air cooling or coolant circuit the intake air cooler having a bypass or multiple flow paths within the heat exchanger to vary the effective heat transfer surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
    • F02B29/0462—Liquid cooled heat exchangers
    • 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
    • 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
    • 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
    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • F28D7/082—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 otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
    • 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
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0082—Charged air coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0089—Oil coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0091—Radiators
    • F28D2021/0092—Radiators with particular location on vehicle, e.g. under floor or on roof
    • 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
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/02—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/067—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/02—Fastening; Joining by using bonding materials; by embedding elements in particular materials
    • F28F2275/025—Fastening; Joining by using bonding materials; by embedding elements in particular materials by using adhesives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • 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 concerns a heat exchanger, in particular, for a motor vehicle, in accordance with the preamble of claim 1 .
  • heat exchangers or heat interchangers for motor vehicles, higher requirements are increasingly demanded for exchange performance with a simultaneously restricted installation space.
  • cooling of combustion gas for the purpose of recirculating it to a combustion engine means that increasingly high heat outputs have to be removed.
  • heat interchangers such as oil coolers or charge-air coolers
  • increasingly higher requirements are being made for transfer or exchange performance.
  • the heat interchangers or heat exchangers must also withstand increasingly higher pressures.
  • a gaseous fluid for example, combustion gas or charge air
  • the performance and the resistance to pressure of a heat interchanger can be increased in that the flow channel cross sections are made smaller.
  • the pressure drop thereby rises considerably both with gas-conducting as well as oil-conducting channels, so that a high output (pump, engine) is required in order to pump the fluids through the coolers.
  • the goal of the invention is to create a heat exchanger in accordance with the preamble of claim 1 , which, with a limited installation space, has a high heat exchanger performance and can be produced at a low cost.
  • a heat exchanger in particular for a motor vehicle, with at least one flow channel with a fluid throughflow, which at least in sections has a curved shape, preferably with several flow channels with a fluid throughflow which at least in sections have a curved shape, the goal is obtained in that the flow channel which at least in sections has a curved shape is provided in an extruded profile.
  • the flow channel has a fluid throughflow for the purpose of a heat exchange.
  • the extruded profile has the advantage that it can be produced at low cost.
  • a preferred embodiment of the heat exchanger is characterized in that several flow channels, which at least in sections have a curved shape, are provided in an extruded profile. At least two flow channels arranged next to one another within an extruded profile are particularly advantageous thereby. A separating interior wall which is integrally connected with the remaining material of the extruded profile is provided between two adjacent flow channels in the extruded profile. In this way, a large contact surface between the fluid and the heat-exchanging material of the extruded profile can be created at low cost and in an operationally reliable matter.
  • the extruded profile has the advantage that the separation wall or the separation walls, which are also designated as webs, clearly increase the resistance to internal pressure of the extruded profile, so that with such profiles higher pressures can also be employed without damage or deformations appearing in the extruded profile.
  • the interior walls or separation walls or webs in the extruded profile also lead to an increase in surface area, and thus to an increase in the rate of heat release.
  • the extruded profile has at least one outside wall with a surrounding flow of a medium, in particular, a cooling agent, and at least one inside wall along which flows a fluid, in particular, a combustion gas. At least two flow channels are thereby provided within one extruded profile in a particularly advantageous manner. In this way, a large surface area of contact between the fluid and the heat-exchanging material of the extruded profile can be made available at low cost and in an operationally reliable manner.
  • Another preferred embodiment of the heat exchanger is characterized in that the outside wall with the surrounding flow of the medium has a cross-sectional shape which is at least partially rounded. In this way, the flexibility of the extruded profile is improved.
  • an initially linearly extruded profile is provided, in an additional processing step, with the curved shape, in particular, with an undulating profile.
  • Another preferred embodiment of the heat exchanger is characterized in that several extruded profiles are provided in a particularly integrated manner, which comprises at least one flow channel that has, at least in sections, a curved shape, preferably several flow channels that have, at least in sections, a curved shape.
  • the heat exchanger according to the invention has flow channels which are separate from one another and are preferably shaped in an undulating form. This makes it possible to implement enlarged channel cross sections, and in the case of a combustion gas cooler a clogging problem due to soot does not develop.
  • the high output density of the heat exchanger according to the invention is essentially obtained in that a preferably undulating deflection of a fluid in an undulating extruded profile leads to a vortex formation in the flow.
  • the pressure drop rises only slightly in comparison to a straight extruded profile with the same channel cross-sectional area.
  • the increased heat output can be attributed to a prolongation of the flow path and to turbulence or vortex formation—both on the side of the fluid to be cooled and also on the cooling fluid side.
  • the at least one extruded profile is made of an alloy based on aluminum.
  • Aluminum has quite good corrosion resistance and can be extruded in a low-cost manner in largely arbitrary cross-sectional forms. In particular condensation is formed during the cooling of combustion gas that has a very low pH value and is therefore very corrosive. This is the case with all combustion gas coolers—that is, both with coolers which are used in high-pressure combustion gas recycling and also with coolers which are used in low-pressure combustion gas recycling. With sufficient cooling, aluminum can definitely be used in the construction of combustion gas heat interchangers.
  • Another preferred embodiment of the heat exchanger is characterized in that the at least one flow channel has a corrosion-inhibiting coating.
  • the heat exchanger as a combustion gas heat exchanger, it is possible to prolong the service life of the heat exchanger by means of such coatings.
  • the heat exchanger is characterized in that the at least one flow channel has a 180° deflection, in addition to the shape which is curved at least in sections.
  • a heat exchanger with a U-shaped throughflow is created which is also designated as a U-flow heat exchanger.
  • two bases are used with a heat exchanger with a U-shaped throughflow. The extruded profiles fit on both sides into these bases. The deflection of the fluid to be cooled preferably takes place in a separate return cap.
  • Another preferred embodiment of the heat exchanger is characterized in that the curved shape has turbulence-producing bends or undulations.
  • the extruded profile can have different sections with different bends and/or undulations.
  • Another preferred embodiment of the heat exchanger is characterized in that the curved shape varies transversely to, and/or in the extension direction of the flow channel.
  • the turbulence-producing bends or undulations in the flow channel vary so as to reduced undesired pressure drops.
  • the at least one flow channel has an increasing undulation downstream, in particular, an increasing amplitude and/or a decreasing pitch.
  • the amplitude and the pitch of the curved shape, in particular, the undulations are changed in the longitudinal direction of the flow channel.
  • the undulation preferably increases thereby with increasing flow path of the fluid to be cooled, so as to keep as low as possible the pressure drop rise.
  • increase of the undulation means that either the amplitude increases toward the rear or the division decreases toward the rear. It is also possible to combine the change of the amplitude with the change of pitch.
  • the variability has advantages with regard to pressure drop, since the preferably hot fluid in the front area of the cooler has the tendency to produce a high pressure drop due to a low fluid density.
  • An additional, artificially produced high turbulence due to a strong undulation in the front area of the flow channel would lead to very high pressure drops there.
  • This strong turbulence is thereby not absolutely necessary in the front cooler area for a high heat output, since the large temperature differential between the fluid to be cooled and the cooling medium is sufficient to confer a high performance even with a low turbulence.
  • a strong turbulence is to be preferred in the rear cooler area since here the increased pressure drop is due less to an increased fluid density, and the temperature differential between the two fluids is too small to transfer the required heat power. Only by means of the high turbulence that is produced by a strong flow channel undulation can the performance be increased sufficiently, even with a low temperature differential between the two fluids. Basically, it is also possible thereby to increase the waviness continuously from the front to the rear.
  • the ratio between the amplitude and the thickness of the extruded profile is in the range of 0-2, in particular, in the range of 0-0.7, with particular preference, in the range of 0-0.3.
  • Another preferred embodiment of the heat exchanger is characterized in that the ratio between the pitch and the thickness of the extruded profile is in the range of 3-10.
  • Another preferred embodiment of the heat exchanger is characterized in that the extruded profile has a thickness in the range of 3-12 mm, preferably in the range of 5-9 mm.
  • the extruded profile has bent or curved areas and/or is reshaped to have undulations. Individual sections of the extruded profile can be reshaped to be undulating. It is, however, also possible for the extruded profile to be reshaped with undulations over its entire length or a great part of its length.
  • the extruded profile is reshaped in a sawtooth or trapezoidal manner.
  • Individual sections of the extruded profile can be reshaped in a sawtooth or trapezoidal manner.
  • the extruded profile it is also possible for the extruded profile to be reshaped in a sawtooth or trapezoidal manner over its entire length or a great part of its length.
  • the trapezoidal undulation the fluid is initially deflected and vortices are produced. In the following straight stretches, the vortices decay slowly and also increase the heat output in the straight section. Only when the turbulence and the vortices have largely subsided is the turbulence once again stirred up by renewed bends.
  • undulation modifications can be implemented in a heat exchanger with a U-shaped throughflow.
  • a front flow path before the deflection can have no undulation or a slight one and a rear flow path behind the deflection can have a strong undulation.
  • a high output with a moderate pressure rise is also obtained for a cooler with a U-shaped throughflow.
  • a bypass flap is upstream or downstream from the heat exchanger.
  • the bypass flap is used to direct the fluid, uncooled, past the area of the cooled flow channels.
  • a bypass channel must also be provided, which ideally is thermally insulated via an insulating tube.
  • the insulating tube is constructed from stainless steel.
  • the heat exchanger is characterized in that the fluid is a combustion gas of a combustion engine of a motor vehicle.
  • the goal of cooling very hot combustion gas can in general be obtained particularly well by a heat exchanger according to the invention, since it has a very high heat exchange performance for a given installation space.
  • Another preferred embodiment of the heat exchanger is characterized in that the fluid is a charge air of a combustion engine of a motor vehicle.
  • the fluid is a charge air of a combustion engine of a motor vehicle.
  • Another preferred embodiment of the heat exchanger is characterized in that the fluid is a lubricating oil from a lubricating oil circulation of a motor vehicle.
  • the fluid is a lubricating oil from a lubricating oil circulation of a motor vehicle.
  • Another preferred embodiment of the heat exchanger is characterized in that the extruded profile is fixed at the end to a base element.
  • Another preferred embodiment of the heat exchanger is characterized in that both ends of the extruded profile empty into the base element.
  • Another preferred embodiment of the heat exchanger is characterized in that the extruded profile is fixed at the end to two base elements.
  • the extruded profile extends between the two base elements.
  • Another preferred embodiment of the heat exchanger is characterized in that the ends of the extruded profile empty into one of the base elements.
  • the flow channels preferably empty, on the entry and exit sides, into a base where they are joined thermally (welded or soldered), joined mechanically (calked or sealed off), or cemented.
  • the bases are connected with a housing of the heat exchanger by welding, soldering, screwing, crimping, or cementing.
  • a diffuser is then added to the housing on both sides that is screwed on, welded, soldered, or cemented.
  • a diffuser is added only on the entry side, wherein the diffuser contains a separation wall.
  • the entry diffuser or the exit diffuser can each contain a bypass flap so as to direct the fluid, uncooled, past the area of the cooled flow channels.
  • the heat exchanger is characterized in that the base element or the base elements are preferably connected with a diffuser in a material-bonding manner.
  • the material-bonding connection can be produced, for example, by welding, soldering, or cementing.
  • the base elements can also be screwed together with the diffuser.
  • Another preferred embodiment of the heat exchanger is characterized in that the flow channels or extruded profiles are connected, in a material-bonding manner, with the base element or the base elements, for example, by cementing, furnace soldering, flame soldering, induction soldering, or welding.
  • heat exchanger is characterized in that the entire heat exchanger is or will be soldered in a furnace.
  • the entire cooler with all the sealing surfaces such as the tube-bottom connection or the bottom-housing connection, are soldered in a soldering furnace (vacuum or Nocolok).
  • a soldering furnace vacuum or Nocolok
  • a local, short-term thermal heating in particular, in the area of the joint sites, is advantageous. This can be obtained by a local flame soldering, induction soldering, or welding, such as laser welding.
  • the extruded profile is located in a housing with, in particular, a liquid cooling agent throughflow.
  • a particularly effective cooling of the fluid can be obtained in that the flow channels are situated in the housing.
  • the housing it is also possible for the housing to be absent and for the fluid to be cooled by means of cooling air.
  • Another preferred embodiment of the heat exchanger is characterized in that the housing has an inflow and an outflow for the cooling agent.
  • baffle plates can be preferably placed on the side with the cooling agent; they can brace the flow channels in vibrations occur and prevent damage to the cooler. Such baffle elements can direct the flow to certain areas and/or produce turbulences in the cooling agent.
  • Another preferred embodiment of the heat exchanger is characterized in that support agents in the housing are situated to hold the flow channels.
  • the support agents are used to limit the oscillation amplitude of the flow channels and thus to prevent crack formation even with strong vibrations.
  • heat exchanger is characterized in that ribs, baffle plates, or other elements, in particular, support elements, are located between the extruded profiles.
  • the support means can be designed as ribs or turbulence producers and clearly increase the transfer of heat.
  • heat exchanger is characterized in that the elements are soldered in, cemented in, or clamped in between the extruded profiles.
  • the support means in a housing are located in the liquid cooling agent, they can also be made of a thermally nondemanding material (such as plastic), so as to lower costs.
  • Another preferred embodiment of the heat exchanger is characterized in that the housing is essentially made of aluminum. Production costs are reduced in this way.
  • Another preferred embodiment of the heat exchanger is characterized in that the housing is essentially made of plastic. The production is simplified in this way.
  • the housing can also be dispensed with.
  • a cooler can then be incorporated in the cooling module or another suitable site in the engine compartment, where it is sufficiently supplied with cooling air.
  • the invention moreover concerns a method for the production of a heat exchanger which will be described first, in which an extruded tube is reshaped in such a way that it has, at least in sections, a curved shape.
  • FIG. 1 a schematic sectional view of a heat exchanger in accordance with a first embodiment, without a bypass channel;
  • FIG. 2 a schematic sectional view of a heat exchanger similar to that in FIG. 1 , with a bypass channel;
  • FIG. 3A a schematic sectional view of a heat exchanger in accordance with another embodiment, with a U-shaped throughflow and with a bypass flap;
  • FIG. 3B a heat exchanger similar to that in FIG. 3A , without a bypass flap;
  • FIG. 3C an extruded profile according to the invention, in cross section
  • FIG. 4 a schematic sectional view of a heat exchanger similar to that in FIG. 3B , according to another embodiment
  • FIG. 5 a schematic sectional view of a heat exchanger similar to that in FIG. 3B , in accordance with another embodiment
  • FIG. 6 a schematic sectional view of a heat exchanger in accordance with another embodiment
  • FIGS. 7A and B two embodiments of undulating flow channels
  • FIG. 8 another embodiment of a flow channel with trapezoidal undulations
  • FIG. 9 a schematic sectional view of a heat exchanger similar to that in FIG. 1 , without a housing;
  • FIG. 15.2 a representation of the preferred selection of a hydraulic diameter based on measurements and calculations, with a view to an improved heat transfer;
  • FIG. 17.2 a demonstration of a hydraulic diameter, based on measurements and calculations, in which a stabilization of a pressure drop can be expected at a defined level even with increasing operating time of the flow channel;
  • FIG. 18.2 a representation of a preferred selection of a hydraulic diameter based on measurements and calculations, with reference to the ratio of the circumference that can be wetted with the first fluid and an outer circumference of the flow channel;
  • FIG. 19A.2 a modification of a preferred embodiment of a cross section of a flow channel with extruded channel jacket and with the webs extruded with the channel jacket;
  • FIG. 100A.2 a modification of another embodiment as in FIG. 19A.2 , with partial webs;
  • FIGS. 111A.2 and 111 B. 2 two modifications of another embodiment as in FIG. 19A.2 , with partial webs.
  • a heat exchanger 1 is represented schematically in section.
  • the heat exchanger 1 comprises a housing 2 , which emerges from a collecting box 4 .
  • the collecting box 4 represents a diffuser and is equipped with an inlet connection 5 . Gas is supplied to the collecting box 4 through the inlet connection 5 , as is indicated by an arrow 6 .
  • a collecting box 8 is located on the opposite side of the housing 2 ; it also represents a diffuser.
  • the collecting box 8 has a gas outlet connection 9 .
  • the exiting gas is indicated by an arrow 10 .
  • an inlet connection 14 for a cooling agent is provided on the housing 2 .
  • the entering cooling agent is indicated by an arrow 15 .
  • the housing 2 is equipped with an outlet connection 16 for the cooling agent.
  • the exiting cooling agent is indicated by an arrow 17 .
  • the interfaces between the housing 2 and the collecting box 4 , 8 are each defined by a base element 21 , 22 .
  • Flow channels 24 - 29 extend between the base elements 21 , 22 .
  • the flow channels 24 - 29 are formed in tubes, which are constructed as the extruded profile. In accordance with an essential aspect of the invention, the extruded profiles with the flow channels 24 - 29 do not have a straight-line, but rather an undulating shape.
  • FIG. 2 schematically represents in section a heat exchanger 31 similar to the heat exchanger 1 from FIG. 1 .
  • the same reference symbols are used. In order to avoid repetitions, reference is made to the preceding description of FIG. 1 . The differences between the embodiments of FIGS. 1 and 2 are mainly discussed below.
  • the heat exchanger 31 represented in FIG. 2 comprises a housing 32 with an integrated bypass channel 33 .
  • the bypass channel 33 creates a direct connection between the collecting boxes 4 and 8 , circumventing the cooled flow channels 24 - 29 .
  • a bypass flap 34 is provided in the collecting box 4 . In the position of the bypass flap 34 , represented with a solid line, the flow runs through the flow channels 24 - 29 and not through the bypass channel 33 . If the bypass flap 34 is moved into a position 35 , indicated with a broken line, then the flow runs only through the bypass channel 33 and not through the flow channels 24 - 29 .
  • FIGS. 3A , 3 B, and 4 various embodiments of a heat exchanger 41 with a housing 42 are depicted.
  • the housing 42 is equipped with an inlet connection 43 for the cooling agent.
  • the entering cooling agent is indicated by an arrow 43 A.
  • the housing 42 is in addition equipped with an outlet connection 44 for the cooling agent.
  • the exiting cooling agent is indicated by an arrow 44 A.
  • the housing 42 passes at one side into a collecting box 45 that is equipped with a bypass flap 46 or a mixing valve 46 .
  • An arrow 48 indicates that a gas flow is supplied to the collecting box 45 .
  • the entering gas flow 48 is cooled by the cooling agent 43 A, 44 A in the housing 42 .
  • the cooled exiting gas flow is indicated by an arrow 49 .
  • a base element 51 is located at the interface between the housing 42 and the collecting box 45 .
  • Flow channels 53 - 55 open into the base element 51 ; they also proceed from the base element 51 .
  • the flow channels 53 - 55 do not run straight but rather undulate in one section 58 and are deflected by 180° in another section 59 .
  • the mixing valve or bypass flap ( 46 in FIG. 3A ) was omitted in the embodiment depicted in FIG. 3B . Otherwise, the embodiment shown in FIG. 3B is identical with the embodiment depicted in FIG. 3A .
  • FIG. 3C indicates that the flow channel 53 from FIGS. 3A and 3B is constructed as an extruded profile.
  • the extruded profile 53 comprises four channels 61 - 64 , which are respectively separated from one another by a web 65 , 66 , 67 .
  • the webs 65 - 67 are also designated as interior walls or separation walls. Gas for the cooling is conducted through the channels 61 - 64 .
  • Channels 61 - 64 are delimited on the outside by an outer wall 68 .
  • the outer wall 68 essentially has a rectangular cross section with rounded-off corners.
  • flow channels 71 - 73 can also be located in the housing 42 ; they run curved only in one section 75 . After a section 76 in which the flow channels 71 - 73 are deflected by 180°, the flow channels 71 - 73 run in a straight line in another section 77 .
  • a heat exchanger 81 is depicted schematically in section that comprises a housing 82 .
  • a collecting box 84 is provided which is itself subdivided.
  • the entering gas is indicted by an arrow 85 .
  • the exiting gas is indicated by an arrow 86 .
  • the housing 82 is in addition equipped with an inlet connection 91 for the cooling agent.
  • the entering cooling agent is indicated by an arrow 92 .
  • the housing 82 is in addition equipped with an outlet connection 94 for the cooling agent.
  • the exiting cooling agent is indicated by an arrow 95 .
  • a base element 98 is provided at the interface between the collecting box 84 and the housing 82 .
  • Another base element 99 is provided on the adjacent end of the housing 82 .
  • the housing 82 has a deflection section 100 .
  • Flow channels 101 A, 102 A, 103 A, 104 A, 105 A, and 106 A extend between the two base elements 98 and 99 .
  • the flow channels 101 A have an undulating shape.
  • the entering gas 85 from the collecting box 84 arrives at the base element 99 via the flow channels 104 A- 106 A.
  • the gas exiting from the flow channels 104 A- 106 A is deflected jointly in the deflection section 100 of the housing 82 and arrives at the collecting box 84 once again via the flow channels 101 A- 103 A.
  • FIG. 6 represents in section a heat exchanger 101 that comprises a housing 102 .
  • the housing 102 proceeds from a collecting box 104 . Gas is supplied to the collecting box 104 , as is indicated by an arrow 105 . On the opposite side, the housing 102 is delimited by a collecting box 106 . The exiting gas is indicated by an arrow 107 .
  • the housing 102 is in addition equipped with an inlet connection 109 for the cooling agent.
  • the entering cooling agent is indicated by an arrow 110 .
  • the housing 102 is in addition equipped with an outlet connection 111 for the cooling agent.
  • the exiting cooling agent is indicated by an arrow 112 .
  • a base element 114 , 115 is in each case provided at the interfaces between the housing 102 and the collecting boxes 104 , 106 .
  • Flow channels 121 or 126 extend between the two base elements 114 and 115 .
  • the flow channels 121 - 126 are provided in a section 131 with a flatter undulation than in another section 132 .
  • FIG. 7A a section of a tube 140 is depicted in a top view.
  • the tube 140 is constructed as an extruded profile and is equipped with a flow channel 141 .
  • the tube 140 can also be equipped, however, with several flow channels.
  • the tube 140 has an essentially sinusoidal undulating form. The amplitude of the undulating shape is designated by A.
  • the pitch is designated by T.
  • the thickness of tube 140 is designated by d.
  • FIG. 7B indicates that a tube 145 , constructed as an extruded profile with a flow channel 146 , can also be undulating in sawtooth form.
  • the amplitude of the sawtooth-like undulation is designated with A.
  • the pitch is designated by T.
  • the thickness of the tube 145 is designated by d.
  • FIG. 8 depicts a tube 148 with a flow channel 149 , which has a trapezoidal undulation.
  • the amplitude of the trapezoidal undulation is designated with A.
  • the pitch of the trapezoid undulation is designated by T.
  • the thickness of the tube 148 constructed as an extruded profile, is designated by d.
  • FIG. 9 shows a heat exchanger 151 schematically in section.
  • the heat exchanger 151 comprises an inlet element 152 for a fluid.
  • the entering fluid is indicated by an arrow 153 .
  • the heat exchanger 151 comprises, moreover, an outlet element 154 for the fluid.
  • the exiting fluid is indicated by an arrow 155 .
  • Flow channels 161 - 166 run between the inlet element 152 and the outlet element 154 ; they are provided in extruded profiles.
  • Conducting elements 157 for cooling air are situated between the individual extruded profiles.
  • the conducting elements 157 are used simultaneously or alternatively as support elements, and can be cemented, soldered, or wedged with the extruded profiles.
  • the extruded profiles with the flow channels 161 - 166 preferably have a surrounding flow of cooling air. Therefore, in the heat exchanger 151 shown in FIG. 9 , it is possible to dispense with a housing.
  • the heat exchanger 151 can be incorporated in a cooling module or on another suitable site in the engine compartment where it is provided with sufficient cooling air.
  • FIG. 15.2 shows a heat transfer behavior or degree of exchange, and thus the exemplary behavior of a heat transfer performance of a heat interchanger with reference to a calculation based on measurement data, for an example of a heat interchanger designed as a combustion gas cooler.
  • the data are indicated for typical inlet conditions, wherein a combustion gas pressure in the range of 1 bar was selected for simplification. The results, however, are exemplary also for other combustion gas pressures.
  • a curve A shows the behavior of a heat interchanger when not dirtied; a curve B, the behavior of a heat interchanger in the dirtied state.
  • FIG. 15.2 represents the degree of exchange as a function of the hydraulic diameter.
  • the concept of the invention thus provides for the flow channel to be characterized by a hydraulic diameter which is formed as four times the ratio of the area of the throughflow cross section to a circumference which is wettable by the combustion gas, and which lies in a range between 1.5 mm and 6 mm.
  • the hydraulic diameter should be in a range between 2 mm and 5 mm.
  • the comparatively flat upper level of a degree of exchange in a dirtied heat interchanger is in the preferred range of a hydraulic diameter between 2.5 and 3.5 mm or 2.8 mm and 3.8 mm, wherein the latter range is relevant above all for a high-pressure heat interchanger.
  • FIG. 18.2 represents the ratio of the circumference that is wettable by a combustion gas and an outer circumference of the flow channel, as a function of the hydraulic diameter.
  • a preferred ratio is produced from the previously explained, shaded areas of a preferred hydraulic diameter of 2 mm to 5 mm, in particular, 2.8 mm to 3.8 mm.
  • the aforementioned ratio lies in the range between 0.1 and 0.5 in order to obtain improved degrees of exchange and degrees of pressure drop.
  • a comparable tendency can also be determined with the additional constructive designs, described in more detail below, of a cross section in a flow channel with a throughflow.
  • FIG. 18 represents the ratio of the circumference that is wettable by a combustion gas and an outer circumference of the flow channel, as a function of the hydraulic diameter.
  • a preferred ratio is produced from the previously explained, shaded areas of a preferred hydraulic diameter of 2 mm to 5 mm, in particular, 2.8 mm to 3.8 mm.
  • the aforementioned ratio lies in the range between 0.1 and 0.5 in order
  • the ratio k should be in a range below 0.8 mm, preferably in a range between 0.3 mm and 0.7 mm.
  • the ratio k of a distance e between two opposite partial webs to a height b of the tube cross section increases from 0.25-0.75 in the direction of the arrow.
  • FIG. 19A.2 to FIG. 111B.2 describe, by way of example, constructive designs of a cross section of different preferred flow channels. It should be equally clear thereby that modifications of the same and an arbitrary combination of features of the embodiments specifically described in the figures are possible, and a hydraulic diameter in the range between 1.5 mm and 6 mm, preferably between 2 mm and 5 mm, preferably between 2.8 mm and 3.8 mm, can nevertheless be obtained.
  • a modification is shown in which a channel jacket thickness and a web thickness d are the same or similar, and another modification is shown in which a ratio of a web thickness d and a channel jacket thickness s is less than 1.0 mm. Accordingly, it is also possible to vary and adapt the wall thicknesses of partial webs or similar dimensions, depending on the objective to be attained.
  • FIG. 19A.2 shows two modifications of a flow channel 1061 , wherein the jacket thickness s and the web thickness d are essentially the same. Moreover, the same reference symbols are used for the same features.
  • the flow channel 1061 is formed as a profile which is, as a whole, extruded—that is, as an extruded channel jacket together with the extruded webs. Accordingly, the flow channel 1061 has a channel jacket 1063 with an interior space 1067 that is surrounded by a channel jacket inner side 1065 , which in this case is designed for the heat-exchanging conduction of the first fluid in the form of a combustion gas. Furthermore, the flow channel 1061 , in this case, has five webs 1069 , situated in the interior space 1067 on the channel jacket inner side 1065 , which are formed together with the channel jacket 1063 as an integral extruded profile.
  • a web 1069 runs entirely parallel to a flow channel axis, standing perpendicular to the drawing plane, uninterrupted along the flow path formed in the housing of a heat interchanger.
  • the throughflow cross section shown, transverse to the flow channel axis, is designed to conduct the combustion gas in the interior space 1067 .
  • Dimensioning is effected based on the hydraulic diameter d h for the flow channel profile 1061 under consideration, with reference to the distances a, b.
  • the hydraulic diameter turns out to be four times the ratio of the of the throughflow cross-sectional area to a circumference which can be wetted by the combustion gas.
  • the area of the throughflow cross section is in this case a multiple of the product of a and b.
  • the wettable circumference is in this case also the multiple of double the sum of a and b.
  • a gives the width of the free cross section of a flow path 1074 that is subdivided by the webs 1069 in the flow channel
  • b in this case gives the free height of the flow path 1074 .
  • a wall thickness s is in the range between 0.2 mm and 2 mm, preferably in the range between 0.8 mm and 1.4 mm.
  • a height b of a line of flow 1074 or a height of the interior space 1067 is, in this case, in the range between 2.5 mm and 10 mm, preferably in the range between 4.5 mm and 7.5 mm.
  • a width a of a line of flow 1074 is in the range between 3 mm and 10 mm, preferably in the range between 4 mm and 6 mm.
  • FIG. 100A.2 shows a modification of a particularly preferred embodiment of a flow channel 1071 , which—as explained previously—differs merely in the wall thickness of the channel jacket 1073 relative to the wall thickness of a web 1079 .
  • the flow channel 1071 also has the webs 1079 in the form of whole webs and in addition, partial webs 1079 ′, situated alternately relative to the whole webs 1079 .
  • the flow channel 1071 is in turn formed entirely as an extruded profile, wherein a line of flow 1074 is formed in turn by the distance between two whole webs 1079 .
  • two partial webs 1079 ′ are situated with front ends 1076 opposite one another.
  • FIG. 111A.2 and FIG. 111B.2 two other modifications 1081 , 1081 ′ of a particularly preferred embodiment of a flow channel 1081 , 1081 ′ are shown in which two partial webs 1089 ′ are located with front ends 1086 that are staggered laterally with respect to one another.
  • a ratio of a distance a 3 , from a first partial web 1089 ′ to a whole web 1089 , to a distance a 4 , from a second partial web 1089 ′ to the whole web 1089 lies in a range between 0.5 mm and 0.9 mm, preferably in a range between 0.6 mm and 0.8 mm.
  • the distance e between two opposite partial webs 1079 ′ and/or between two partial webs 1089 ′, staggered with respect to one another, to a height b of the tube cross section is in a range below 0.8 mm, in particular, in a range between 0.3 mm and 0.7 mm.
  • the extrusion materials have the following percentages by mass, especially for corrosion protection.
  • Silicon Si ⁇ 1%, in particular Si ⁇ 0.6%, in particular Si ⁇ 0.15%
  • Iron Fe ⁇ 1.2%, in particular Fe ⁇ 0.7%, in particular Fe ⁇ 0.35%
  • Copper Cu ⁇ 0.5%, in particular Fe ⁇ 0.2%, in particular Cu ⁇ 0.1%
  • Chromium Cr ⁇ 0.5%, in particular 0.05% ⁇ Cr ⁇ 0.25%, in particular 0.1% ⁇ Cr ⁇ 0.25%
  • Magnesium 0.02% ⁇ Mg ⁇ 0.5%, in particular 0.05% ⁇ Mg ⁇ 0.3%
  • Zinc Zn ⁇ 0.5%, in particular 0.05% ⁇ Zn ⁇ 0.3%
  • Titanium Ti ⁇ 0.5%, in particular 0.05% ⁇ Ti ⁇ 0.25%
  • the grain sizes measured in the section of the component in the extrusion direction, ⁇ 250 micrometers, in particular, ⁇ 100 micrometers, in particular, ⁇ 50 micrometers.

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DE102006054221.5 2006-11-15
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