EP1687580B1 - Ladeluft-/kühlmittel-kühler - Google Patents

Ladeluft-/kühlmittel-kühler Download PDF

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Publication number
EP1687580B1
EP1687580B1 EP04818135.8A EP04818135A EP1687580B1 EP 1687580 B1 EP1687580 B1 EP 1687580B1 EP 04818135 A EP04818135 A EP 04818135A EP 1687580 B1 EP1687580 B1 EP 1687580B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
coolant
charge
exchanger medium
air
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.)
Expired - Fee Related
Application number
EP04818135.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1687580A1 (de
Inventor
Daniel Hendrix
Florin Moldovan
Jürgen Wegner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Mahle Behr GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP1687580A1 publication Critical patent/EP1687580A1/de
Application granted granted Critical
Publication of EP1687580B1 publication Critical patent/EP1687580B1/de
Expired - Fee Related 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into 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
    • F28D9/0043—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 the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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

Definitions

  • the invention relates to a charge air / coolant cooler in disk construction according to the preamble of claim 1.
  • the publication WO 01/67021 A1 discloses a stacked disc radiator of stacked discs with openings for ingress and outflow of the respective medium.
  • a charge air / coolant cooler in disk construction, wherein two adjacent disks define a gap which is traversed by a heat transfer medium, in particular a coolant, preferably a mixture with water and glycol, or a second medium to be cooled or heated, wherein the inlet and / or outflow region of the heat transfer medium and / or second Medium is extended at least off or on the inflow side.
  • a heat transfer medium in particular a coolant, preferably a mixture with water and glycol, or a second medium to be cooled or heated
  • the inlet and / or outflow region of the heat transfer medium and / or second Medium is extended at least off or on the inflow side.
  • the inlet and / or outflow region of a fluid to be cooled for example charge air, which forms the second medium, is widened.
  • charge air / coolant cooler allows a good distribution of the corresponding medium on the relevant for the heat transfer surface of the individual discs, which form the heat exchanger.
  • the uniform flow distribution reduces the boiling problem in heat exchangers used in such critical areas.
  • the area preferably runs at least over one third, in particular over half, of the width of the pane straight.
  • the region extends perpendicularly or substantially over at least part of the slice width, i. at an angle of 80 ° to 100 °, transverse to the mean flow direction of the second medium, in particular a fluid to be cooled.
  • the opening for the second medium in an end region of the disk preferably extends substantially over the entire surface thereof, excluding edge regions and regions in which channels for the heat transfer medium are arranged.
  • At least two heat transfer medium channels per heat transfer medium inlet and / or outlet are provided.
  • Such a trained heat exchanger allows a good distribution of the heat transfer medium on the relevant for the heat transfer surface of the individual discs, which form the heat exchanger.
  • the uniform flow distribution reduces the boiling problem in such a way critical areas used heat overlays.
  • the heat transfer medium channels are thereby formed, as well as the inflow or outflow regions of the medium to be cooled / heated, preferably by in particular aligned apertures in the individual disks.
  • the heat transfer medium distribution is assisted by an embodiment of the disks which is axisymmetric with respect to the heat transfer medium channels with respect to their longitudinal axis. If the disks are furthermore designed to be axially symmetrical with respect to their transverse axis with regard to the heat exchanger medium channels, the assembly is simplified.
  • a single heat transfer medium inlet and / or a single heat transfer medium outlet is provided, which has a branching or merging. This allows a relatively simple structure with improved heat transfer due to the better flow distribution.
  • the branching and / or the merging are preferably circular-arc-shaped, so that a space-saving construction or the like around the individual discs together holding bolts. is possible.
  • a bend of 30 ° to 90 °, as seen in the flow direction, is preferably provided, wherein the forked part of the branching or merging is aligned parallel to the disks.
  • the heat transfer medium inlet entering the two heat transfer medium channels after the branching preferably runs parallel to the heat transfer medium channels, while the two-part part of the branching preferably takes place in a plane lying perpendicular thereto is.
  • the heat transfer medium outlet which merges into the merger from two heat transfer medium channels preferably runs parallel to the heat transfer medium channels, while the two-part part of the branch is preferably arranged in a plane lying perpendicular thereto. This allows a compact and space-saving design of the heat exchanger.
  • the supply can also be effected by means of two individual, separately formed tubes, which are connected to one another via a Y-shaped connecting piece.
  • a charge air / coolant cooler for cooling the charge air is preferred.
  • a mixture with water and glycol is preferably used as the heat transfer medium (coolant).
  • Coolant discs 2 Serving as a heat exchanger between charge air and coolant charge air / coolant radiator 1 has a plurality of stacked coolant discs 2.
  • two inlet openings 3 and two outlet openings 4 are provided in each coolant disc 2, is supplied by the heat transfer medium as coolant to the interstices of the coolant disks 2 and discharged from it.
  • the flow direction is illustrated in the figures by arrows.
  • the coolant spreads after entering through the inlet openings 3 over the entire width of the interstices of the coolant disks 2 and flows uniformly in the direction of the outlet openings 4 (see Fig.
  • the openings 3 and 4 of the stacked coolant disks 2 form coolant channels 5 and 6.
  • the areas of the openings 3 and 4 are formed correspondingly raised, so that there is sufficient space for the charge air to flow through between the coolant disks 2 and can be cooled.
  • the two coolant channels 5 begin - seen in the flow direction of the coolant - at a junction 7, which has a circular arc-shaped bifurcation 8 and a centrally arranged in the arc thereof, arranged parallel to the coolant channels 5 coolant inlet 9.
  • the coolant supplied through the coolant inlet 9 is divided equally between the two coolant channels 5.
  • the exit is formed.
  • the two coolant channels 6 end with a combination 10, which is formed according to the branch 7 and has a coolant outlet 11.
  • the charge air (second medium) is supplied via a charge air inlet 20, via a charge air channel 21, which is formed by openings 22 of the stacked coolant discs 2, the spaces between the flowed through by the coolant spaces of the coolant discs. 2 fed and passes through on the other side of the coolant disks 2 formed openings 23, which form a second charge air channel 24 to the charge air outlet 25th
  • the openings 22 and 23 are, contrary to the prior art (in Fig. 5 shown in dashed lines) are not circular, but have a portion 26 which is substantially straight according to the first embodiment, wherein it is arranged perpendicular to the normal flow direction of the charge air, so that in this region 26 tangentially with respect conventional shape, which corresponds to the inner circle of the openings 22 and 23, is arranged.
  • the openings 22 and 23 each occupy the entire end portion of the coolant disk 2, except for an outer edge 27, the two coolant channels 5 and 6 and each one surrounding the coolant channels edge 28 occupies.
  • the region 26 of the opening 23 is formed such that it extends over the entire end portion of the coolant discs 2, wherein it is arranged perpendicular to the mean flow direction of the charge air.
  • the coolant channels are arranged further offset inwards, so that the shape of a rounded triangle results.
  • the other side of the coolant disc 2 is formed accordingly.
  • coolant disc corresponds to the opening 23 about the opening 23 of the second embodiment, wherein only a coolant channel is provided, which is laterally displaced in the region of the opening 23, so that the opening 23, the end portion of the coolant disc. 2 apart from an outer edge 27, the coolant channel and a coolant channel surrounding edge 28 occupies.
  • the other side of the coolant disc 2 is designed accordingly, in particular axially symmetrical to the central transverse axis or point-symmetrical to the center of the coolant disc.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Supercharger (AREA)
EP04818135.8A 2003-11-10 2004-11-10 Ladeluft-/kühlmittel-kühler Expired - Fee Related EP1687580B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10352881A DE10352881A1 (de) 2003-11-10 2003-11-10 Wärmeübertrager, insbesondere Ladeluft-/Kühlmittel-Kühler
PCT/EP2004/012719 WO2005045344A1 (de) 2003-11-10 2004-11-10 Wärmeübertrager, insbesondere ladeluft-/kühlmittel-kühler

Publications (2)

Publication Number Publication Date
EP1687580A1 EP1687580A1 (de) 2006-08-09
EP1687580B1 true EP1687580B1 (de) 2017-08-02

Family

ID=34559606

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04818135.8A Expired - Fee Related EP1687580B1 (de) 2003-11-10 2004-11-10 Ladeluft-/kühlmittel-kühler

Country Status (7)

Country Link
US (1) US7717165B2 (pt)
EP (1) EP1687580B1 (pt)
JP (1) JP4653756B2 (pt)
CN (1) CN1875235B (pt)
BR (1) BRPI0416363B1 (pt)
DE (1) DE10352881A1 (pt)
WO (1) WO2005045344A1 (pt)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10352880A1 (de) * 2003-11-10 2005-06-09 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Ladeluft-/Kühlmittel-Kühler
SE527716C2 (sv) * 2004-04-08 2006-05-23 Swep Int Ab Plattvärmeväxlare
DE102005029024A1 (de) * 2005-06-22 2007-01-04 Siemens Ag Düsenbaugruppe
DE102005044291A1 (de) * 2005-09-16 2007-03-29 Behr Industry Gmbh & Co. Kg Stapelscheiben-Wärmeübertrager, insbesondere Ladeluftkühler
DE102006044154A1 (de) * 2006-09-15 2008-05-21 Behr Gmbh & Co. Kg Stapelscheibenwärmetauscher zur Ladeluftkühlung
DE102008014375A1 (de) * 2008-03-17 2009-09-24 Behr Gmbh & Co. Kg Gaskühler
US8028410B2 (en) 2008-12-08 2011-10-04 Randy Thompson Gas turbine regenerator apparatus and method of manufacture
DE102013205242A1 (de) * 2013-03-25 2014-09-25 Mahle International Gmbh Abgaskühler

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JP2523689B2 (ja) 1987-09-30 1996-08-14 松下冷機株式会社 冷媒分流器の製造方法
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Also Published As

Publication number Publication date
CN1875235B (zh) 2010-10-13
EP1687580A1 (de) 2006-08-09
BRPI0416363A (pt) 2007-03-13
JP2007510883A (ja) 2007-04-26
WO2005045344A1 (de) 2005-05-19
US20070084592A1 (en) 2007-04-19
BRPI0416363B1 (pt) 2018-10-30
JP4653756B2 (ja) 2011-03-16
CN1875235A (zh) 2006-12-06
DE10352881A1 (de) 2005-06-09
US7717165B2 (en) 2010-05-18

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