EP2031336A2 - Echangeur de chaleur pour un moteur à combustion interne - Google Patents

Echangeur de chaleur pour un moteur à combustion interne Download PDF

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Publication number
EP2031336A2
EP2031336A2 EP08104442A EP08104442A EP2031336A2 EP 2031336 A2 EP2031336 A2 EP 2031336A2 EP 08104442 A EP08104442 A EP 08104442A EP 08104442 A EP08104442 A EP 08104442A EP 2031336 A2 EP2031336 A2 EP 2031336A2
Authority
EP
European Patent Office
Prior art keywords
section
channel
fluid
flow
cooled
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.)
Granted
Application number
EP08104442A
Other languages
German (de)
English (en)
Other versions
EP2031336B1 (fr
EP2031336A3 (fr
Inventor
Hans-Jürgen Hüsges
Hans-Ulrich Kühnel
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.)
Pierburg GmbH
Original Assignee
Pierburg GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP2031336A2 publication Critical patent/EP2031336A2/fr
Publication of EP2031336A3 publication Critical patent/EP2031336A3/fr
Application granted granted Critical
Publication of EP2031336B1 publication Critical patent/EP2031336B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F28F3/048—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 ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • 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
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow 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
    • 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
    • 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

Definitions

  • the invention relates to a heat transfer unit for an internal combustion engine, in particular for cooling exhaust gases, having a channel through which a fluid to be cooled with an inlet and an outlet and a flowed through by a cooling fluid channel having an inlet and an outlet, wherein the fluid to be cooled flowed through channel and the channel through which the cooling fluid flows are separated from each other by at least one partition, from which ribs extend into the channel through which the fluid to be cooled flows.
  • Heat transfer units for internal combustion engines are well known and are described in a variety of applications. They are used both for cooling gases, such as charge air or exhaust gas or for cooling liquids such as oil.
  • heat exchangers are known.
  • tube bundle coolers plate-type coolers or die-cast coolers.
  • coolers produced in particular by the die casting method have been developed in which ribs protrude from the partitions between a channel through which the cooling fluid flows and a channel through which a fluid to be cooled flows into the channel through which the fluid to be cooled flows. These ribs significantly improve the heat transfer, especially at high temperature gradients.
  • Such a heat exchanger is for example from the DE 10 2005 058 204 A1 known.
  • the heat exchanger disclosed here has an inner and an outer shell, wherein the cooling fluid flows between the outer shell and the inner shell, while the fluid to be cooled flows in a U-shaped manner through the inner shell, ie first via the inlet into an inflow section and from there via a deflection region and a subsequent return flow section to the outlet.
  • the cooling fluid flows between the outer shell and the inner shell, while the fluid to be cooled flows in a U-shaped manner through the inner shell, ie first via the inlet into an inflow section and from there via a deflection region and a subsequent return flow section to the outlet.
  • the channel projecting from the partition wall between the two channels over the entire length of the fluid flow channel ribs In the channel projecting from the partition wall between the two channels over the entire length of the fluid flow channel ribs.
  • a cross-sectional area between the walls delimited by the fluid to be cooled channel is greater in a first portion than in a second portion, wherein the ribs are distributed over the length of the channel such that a flow-through cross section in the first flowed through Section is less than or equal to the flow-through cross section in the second flow-through section.
  • the second section of the channel through which the fluid to be cooled flows is designed as a free cross section.
  • this free cross section in the second section of the pressure loss can be reduced by the missing internals in the channel of the heat transfer unit compared to the known designs and the space required for the second section can be minimized.
  • the channel through which the fluid to be cooled flows is U-shaped, wherein the first section serves as an inflow, to which a deflection adjoins, followed by the second section, which serves as remindströmabêt.
  • the inflow portion and the backflow portion are juxtaposed.
  • the inflow section can thereby be made wider with the same overall width and equipped with additional ribs, whereby the improvement of the cooling performance in the range of high temperature gradients can be achieved.
  • the pressure loss is kept substantially constant over the entire area or possibly reduced in size compared with the known embodiment with ribs.
  • the deflection region is designed essentially as a free cross section.
  • the figure shows a side view of a heat transfer unit according to the invention in a sectional view.
  • the heat transfer unit shown in the figure which is used in particular for cooling exhaust gases of an internal combustion engine, consists of a housing 1 in which a channel 2 through which a fluid to be cooled and a channel 3 through which a cooling fluid flows are arranged.
  • the housing 1 consists of a single or multi-part inner shell 4 and an outer shell 5 surrounding the inner shell 4, which is arranged substantially at a distance from the inner shell 4.
  • the flowed through by the cooling fluid channel 3 is arranged in the present embodiment between the inner shell 4 and the outer shell 5, while the flow-through of the fluid to be cooled channel 2 is limited by the inner shell 4.
  • the inner shell 4 forms a partition wall 6 between the two fluids in heat exchange.
  • the inner shell 4, like the outer shell 5, is open on one side and has on its open end side a first inlet 7 and a first outlet 8 arranged next to it.
  • Adjoining the inlet 7 is a first section 9, which serves as an inflow section, which is separated by a middle wall 10 from a second section 12, which serves as a return flow section, which in turn opens into the outlet 8.
  • a deflection region 13 is flowed through, with the beginning of which the middle wall 10 ends.
  • a plurality of ribs 14 is formed, which extend from the inner shell 4 and thus the partition wall 6 in the flowed through by the fluid to be cooled channel 2.
  • the inner shell 4 is still provided with partial ribs 15 only in the first section, while the remaining deflection region 13 has no further ribs.
  • the ribs 14 in the deflection has the advantage that thereby an otherwise frequently observed sooting in this area can be largely avoided.
  • Ribs 14 are also continued in the form of protrusions 19 on the middle wall 10 and the partitions 6, so that even with offset in rows one behind the other arranged ribs 14, the flow-through cross sections in the range of a row of ribs can be kept largely constant without having to change the rib shape.
  • Such a structure is chosen because in the region of the inflow section 9, the temperature gradient between the hot inflowing fluid, in particular exhaust gas, and the circulating cooling fluid is particularly large. For this reason, the available cooling surface and the dwell time in this area is increased in this area by the comparison of known designs, which require the same space, additional ribs over the cross section. Although this also the flow resistance and thus the pressure loss is increased, but this is compensated by the larger flow-through cross-section in the second section again. In the rear regions with a lower temperature gradient, although less cooling power is generated in such an embodiment, this is more than compensated by the generated cooling power in the first section. Thus, overall, the cooling capacity over the run length is increased at about the same residence time and the same space compared to known designs with uniform cross-sections and rib distributions.
  • the inner shell 4 additionally has a flange-shaped enlargement 16, via which the outer shell 5 can be fastened to the inner shell 4, for example by welding. At the same time, this flange-shaped enlargement 16 serves to close the channel 3 through which the cooling fluid flows.
  • the outer shell 5 in turn has an inlet 17 and an outlet 18, which are arranged laterally on the outer shell 5 in the present embodiment in the front and rear of the heat transfer unit.
  • webs for positive guidance of the cooling fluid can additionally be arranged, which extend to the outer shell 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • General Details Of Gearings (AREA)
  • Exhaust Gas After Treatment (AREA)
EP08104442A 2007-08-31 2008-06-17 Echangeur de chaleur pour un moteur à combustion interne Not-in-force EP2031336B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007041338A DE102007041338B3 (de) 2007-08-31 2007-08-31 Wärmeübertragungseinheit für eine Verbrennungskraftmaschine

Publications (3)

Publication Number Publication Date
EP2031336A2 true EP2031336A2 (fr) 2009-03-04
EP2031336A3 EP2031336A3 (fr) 2011-05-18
EP2031336B1 EP2031336B1 (fr) 2012-12-05

Family

ID=39942384

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08104442A Not-in-force EP2031336B1 (fr) 2007-08-31 2008-06-17 Echangeur de chaleur pour un moteur à combustion interne

Country Status (3)

Country Link
US (1) US8245767B2 (fr)
EP (1) EP2031336B1 (fr)
DE (1) DE102007041338B3 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090114373A1 (en) * 2007-11-02 2009-05-07 Calsonic Kansei Corporation Heat exchanger
DE102008049253B4 (de) * 2008-09-26 2012-12-20 Pierburg Gmbh Kfz-Abgaskühler
DE102008051268A1 (de) * 2008-10-10 2010-04-15 Mahle International Gmbh Kühleinrichtung

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005058204A1 (de) 2005-12-02 2007-06-14 Pierburg Gmbh Kühlvorrichtung für eine Verbrennungskraftmaschine

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5099913A (en) * 1990-02-05 1992-03-31 General Motors Corporation Tubular plate pass for heat exchanger with high volume gas expansion side
CN1109232C (zh) * 1993-12-28 2003-05-21 昭和电工株式会社 板式热交换器
JP3719453B2 (ja) * 1995-12-20 2005-11-24 株式会社デンソー 冷媒蒸発器
US6206089B1 (en) * 1996-10-29 2001-03-27 Denso Corporation Heat exchanger and method for manufacturing the same
JP3361475B2 (ja) * 1998-05-18 2003-01-07 松下電器産業株式会社 熱交換器
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
DE10010266A1 (de) * 2000-03-02 2001-11-15 Behr Gmbh & Co Wärmeübertrager und diesen enthaltende Heizungs- oder Klimaanlage eines Kraftfahrzeuges
JP4069570B2 (ja) * 2000-03-16 2008-04-02 株式会社デンソー 排気熱交換器
EP1370818A4 (fr) * 2001-02-19 2006-04-26 Showa Denko Kk Echangeur thermique
DE102005029321A1 (de) * 2005-06-24 2006-12-28 Behr Gmbh & Co. Kg Wärmeübertrager
DE202006009464U1 (de) * 2005-09-23 2006-09-14 Pierburg Gmbh Wärmetauscher
DE102006029043B4 (de) * 2006-06-24 2015-04-23 Pierburg Gmbh Wärmeübertragungseinheit für eine Verbrennungskraftmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005058204A1 (de) 2005-12-02 2007-06-14 Pierburg Gmbh Kühlvorrichtung für eine Verbrennungskraftmaschine

Also Published As

Publication number Publication date
US8245767B2 (en) 2012-08-21
US20090056321A1 (en) 2009-03-05
EP2031336B1 (fr) 2012-12-05
DE102007041338B3 (de) 2008-12-11
EP2031336A3 (fr) 2011-05-18

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