US20080257536A1 - Heat Exchanger, Especially Oil/Coolant Cooler - Google Patents

Heat Exchanger, Especially Oil/Coolant Cooler Download PDF

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Publication number
US20080257536A1
US20080257536A1 US10/585,971 US58597104A US2008257536A1 US 20080257536 A1 US20080257536 A1 US 20080257536A1 US 58597104 A US58597104 A US 58597104A US 2008257536 A1 US2008257536 A1 US 2008257536A1
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United States
Prior art keywords
heat exchanger
plate
base plate
outermost
depression
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
US10/585,971
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English (en)
Inventor
Rudiger Kolblin
Jens Richter
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: RICHTER, JENS, KOLBLIN, RUDIGER
Publication of US20080257536A1 publication Critical patent/US20080257536A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • 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 heat exchanger, especially a stacked plate oil cooler, having a plate-type design, in accordance with the precharacterizing clause of claim 1 .
  • EP 0 623 798 A2 discloses a plate heat exchanger with trough-shaped heat exchanger plates which are stacked on one another and the encircling edges of which bear against one another and are soldered tightly to one another, with all of the heat exchanger plates having the same shape.
  • the lowermost heat exchanger plate is closed by means of a closing plate, the closing plate bearing flat against the base of the heat exchanger plate and openings for connections being provided in the closing plate.
  • the closing plate is of completely flat design.
  • a known stacked plate oil cooler with a correspondingly designed closing plate is illustrated in FIGS. 9 and 10 .
  • a heat exchanger of this type still leaves something to be desired, in particular with regard to the stability of the same.
  • a heat exchanger in particular stacked plate oil cooler, having a plate-type design
  • the base plate has a recessed surface corresponding to the adjacent heat exchanger plate.
  • the flanks of the outermost heat exchanger plate bear, at least in their lower region, against the flanks of the contour of the base plate, which contour runs in a recessed manner.
  • the form-fitting bearing results in a large contact surface and therefore connecting surface between the outermost heat exchanger plate and the base plate, so that, with a corresponding connection by means of solder or the like, there is a good connection and therefore optimum transmission of force, so that the base plate leads to a significantly increased stability of the heat exchanger.
  • one edge of the outermost heat exchanger plate protrudes over the base plate, at least in its edge region, in which it is connected to the adjacent heat exchanger plate.
  • the depression in the base plate is greater than the material thickness of the outermost heat exchanger plate of the heat exchanger, and is preferably at least as deep as the material thickness of the heat exchanger plate of the heat exchanger plus half of the clear height between the outermost heat exchanger plate, which bears against the base plate, and the second outermost heat exchanger plate.
  • a depth of the depression which is at least as deep as the material thickness of the heat exchanger plate of the heat exchanger plus the clear height between the outermost heat exchanger plate, which bears against the base plate, and the second outermost heat exchanger plate, is optimum.
  • the contour in the base plate is preferably produced by means of embossing or machining. Other production methods are possible, for example, the base plate can be cast.
  • Heat exchangers according to the invention can be used, on the one hand, as oil coolers but also as evaporators or condensers or else, for example, as a charge-air/coolant cooler.
  • the refrigeration cycle of a device of this type can serve not only to air-condition a (vehicle) interior but also to cool heat sources, such as electrical consumers, energy stores and voltage sources or the charge air of a turbocharger.
  • the heat exchanger is a condenser when heat exchange takes place, for example, as a result of condensation of the refrigerant of an air-conditioning system in a coolant-loaded compact heat exchanger and the coolant discharges the heat in a heat exchanger to air as a further medium.
  • the evaporation or condensation of another medium in a heat exchanger designed according to the invention may also take place, for example, in applications in fuel cell systems.
  • a method according to the invention for the production of a heat exchanger makes provision for the base plate to be produced by embossing of the same, followed by a correspondingly oriented stacking of the heat exchanger plates and of the base plate and then connection by brazing takes place.
  • connection of the plates by brazing takes place such that the plates are sealingly connected to one another at their edge and, in particular, at the same time a connection of adjacent plates at the contact points of profiles takes place.
  • a stable and distortion-resistant element is thereby produced.
  • FIG. 1 a shows a section through a stacked plate oil cooler along the line A-A of FIG. 3 according to the first exemplary embodiment
  • FIG. 1 b shows a section through a stacked plate oil cooler along the line A-A of FIG. 3 according to a variant of the first exemplary embodiment
  • FIG. 2 shows a perspective illustration of the stacked plate oil cooler of FIG. 1 a
  • FIG. 3 shows a plan view of the stacked plate oil cooler of FIG. 1 a
  • FIG. 4 b shows a section through a stacked plate oil cooler according to a variant of the second exemplary embodiment
  • FIG. 5 shows a section through a stacked plate oil cooler according to the third exemplary embodiment
  • FIG. 6 shows a section through a stacked plate oil cooler according to the fourth exemplary embodiment
  • FIG. 7 shows a view of a detail of FIG. 6 .
  • FIG. 8 shows a heat exchanger plate according to the third and fourth exemplary embodiment
  • FIG. 9 shows a section through a stacked plate oil cooler according to the prior art.
  • FIG. 10 shows a view of the detail B from FIG. 9 .
  • a stacked plate oil cooler 1 serving as a heat exchanger has a plurality of punched and deep-drawn heat exchanger plates 2 which are stacked on one another and between which coolant and oil flows in an alternating sequence.
  • the flow direction at the coolant connections is indicated in FIG. 2 by arrows.
  • the oil is supplied and removed at the bottom.
  • a base plate 3 is attached to the lower side of the lowermost heat exchanger plate 2 .
  • this base plate 3 has a depression 5 , in the present case according to the first exemplary embodiment, a recess, on its upper side 6 , which recess is provided with a contour corresponding, at least in its lower, flat regions and in the region of the flanks, to the lower side of the lowermost heat exchanger plate 2 .
  • the depression 5 has been milled out of the rectangular base plate 3 by means of milling, with the lower side of the base plate 3 being unchanged in its shape.
  • the depression 5 has a depth which corresponds approximately to the material thickness of the lowermost heat exchanger plate 2 plus the clear height between the two lower heat exchanger plates 2 .
  • the depression 5 is formed somewhat lower than the depression 5 of the first exemplary embodiment, in the present case approximately twice the material thickness of the heat exchanger plates 2 plus the clear height between the two lowermost heat exchanger plates 2 .
  • the base plate 3 has, on its lower side, a protruding region 8 , approximately in a region as a continuation of the heat exchanger plates 2 .
  • the protruding region 8 has a flat base.
  • the depth of the depression 5 corresponds approximately to the depth of the depression 5 according to the variant of the first exemplary embodiment.
  • FIG. 5 illustrates as a third exemplary embodiment a section through a stacked plate oil cooler 1 which is formed from interconnected heat exchanger plates 2 and a base plate 3 . Cavities closed off outwardly are formed between the heat exchanger plates 2 . The cavities are alternately supplied with a first and a second medium in each case via at least one inflow and outflow line and the corresponding medium also flows through them. In this case, the plates are profiled in such a way that contact points occur between the respective profiles of the heat exchanger plates 2 .
  • the heat exchanger plates 2 are connected to one another with a cohesive material joint, as a rule are soldered, in the region of these contact points.
  • the heat exchanger plates 2 are configured in such a manner that the flow, which forms between the heat exchanger plates 2 , of the first or second medium from the corresponding inflow line to the corresponding outflow line does not run rectilinearly.
  • An example of a heat exchanger plate 2 of this type is illustrated in FIG. 8 .
  • the heat exchanger plates 2 can have a recurring wavy profile which then runs at least in a direction transverse with respect to the throughflow direction which is the straight connection from the inlet points of the medium to the outlet points.
  • the wavy profile runs around this direction in a zigzag-shaped manner.
  • Such a wavy profile in a simple manner forms flow guide regions which are suitable for guiding the flow of the medium flowing through the corresponding cavity.
  • the flow is thereby advantageously multiply deflected in its run or flows through regions in which the distance of the heat exchanger plates 2 from one another differs in size. Therefore, the flow velocity varies in these regions.
  • the effect is advantageously achieved at the same time that, overall, the medium is distributed over the entire surface of the heat exchanger plates 2 and therefore the entire heat exchange surface is utilized in as an optimized a manner as possible.
  • Even turbulent flows arise as a function of the flow behavior (viscosity) of the medium flowing through. The repeatedly occurring changes in direction of the fluid in the duct and the vortexes which, under some circumstances, form in the region of the opening wave duct repeatedly break up the boundary layer formed. This leads to an improved heat transmission.
  • the wavy profile can have legs running rectilinearly between flow regions, the run of the wavy profile being characterized by the leg length of the legs, by the leg angle defined between the legs and by the profile depth of the wavy profile.
  • the profile of a wavy profile is fixed in its cross section by the run in the region of the legs and in the region of curvature, with it being possible for preferred refinements to provide a deviation in the cross-sectional form in these regions.
  • the wavy profile, which runs in a zigzag-shaped manner, of the heat exchanger plates 2 is characterized in this case particularly by the leg length, the leg angle between adjacent legs and the profile depth.
  • Preferred refinements of the invention make provision for the leg length to be in the range of 8 to 15 mm, preferably in the range of 9 to 12 mm.
  • the leg angle between two legs of the wavy profile is preferably between 45° and 135°.
  • a connection of the heat exchanger plates 2 takes place in the region of the contact points by brazing, for which purpose the heat exchanger plates 2 are coated at least on one side with a soldering aid, such as a solder.
  • the selection of leg length and leg angle takes place preferably as a function of the medium flowing through and its viscosity.
  • the leg length and leg angle have a great influence on the flow velocities occurring and on the heat exchange associated therewith, so that these are adapted to the respective intended use.
  • the abovementioned values in this case relate particularly to the use of heat exchangers as oil coolers in vehicles where the heat exchange takes place between engine oil and cooling water. Furthermore, they also depend, of course, on the dimensioning of the heat exchanger plates 2 and of the interspace occurring due to the distance between the heat exchanger plates 2 .
  • the configuration of the wavy profile is fixed essentially by the form of the cross section perpendicularly to the outer edge of the profile in this region and by the profile sequence, fixed by the division, in the run transverse with respect to the direction of extent of a wavy profile over the heat exchanger plate 2 .
  • Preferred refinements provide a constant division, that is to say a fixed distance between any two wavy profiles adjacent to one another.
  • the configuration of the wavy profile is advantageous particularly when it has a flat region on the outside of the wave back.
  • the flat region in this case has, in particular, a width of 0.1 to 0.4 mm.
  • the flat region makes it possible for heat exchanger plates 2 adjacent to one another to bear effectively against one another over a large area and consequently allows easy and stable production of the support or connection—such as by brazing—of adjacent heat exchanger plates 2 to one another.
  • the heat exchanger plates 2 may be configured identically or correspondingly or similarly to one another or differently from one another. Heat exchanger plates 2 which are identical to one another have identical properties in terms of the characteristic properties of the wavy profile and the configuration of the wavy profile. Heat exchanger plates 2 corresponding to one another are identical to one another in construction, but is it possible, for example, for the heat exchanger plates 2 to have different leg angles from one another. Heat exchanger plates 2 corresponding to one another preferably have configurations of the wavy profile which are different from one another and/or values, which are different from one another, of characterizing parameters, but correspond to one another in terms of the design of the edge and the design of the front and the rear side of the heat exchanger plates 2 .
  • the alternating use of, for example, two heat exchanger plates 2 which correspond to one another and differ only in different leg angles in the characteristic parameters, has the advantage that the position and relative situation of contact points of the heat exchanger plates 2 against one another in the profiled region can be optimized in a simple manner in terms of the required rigidity and the required throughflow.
  • the material of the heat exchanger plates 2 and of the base plate 3 in the present case is aluminum.
  • the advantage of this material is that it has low density and at the same time makes it possible to produce the wavy profile, for example, by embossing in a simple manner.
  • soldering aid such as brazing alloy
  • coating on both sides with soldering aid may also be provided.
  • the coating with soldering aid is to serve, in particular in the region of the edges and of the inflow and outflow lines in the block, for the reliable production of a fluid-tight connection of two plates to each other in a joining operation by means of a joining tool (brazing furnace), without the use of further aids or auxiliaries.
  • connection between the heat exchanger plates 2 and between the lowermost heat exchanger plate 2 and the base plate 3 is produced, in particular, by brazing.
  • the heat exchanger plates 2 may be provided to have a bent edge, the height of which is selected such that at least two heat exchanger plates 2 adjacent to one another bear against one another and mutually overlap in this edge region.
  • the number of heat exchanger plates 2 overlapping in the edge region may in this case be up to five. The larger the number of overlapping heat exchanger plates 2 is, the more rigid is the wall formed thereby and outwardly closing off the heat exchanger.
  • FIGS. 6 and 7 show a modification, corresponding to the third exemplary embodiment, with a base plate 3 which has, on its lower side, a protruding region 8 approximately as a continuation of the heat exchanger plates 2 . Also according to this exemplary embodiment, the protruding region 8 has a flat base.

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  • 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)
US10/585,971 2004-01-23 2004-12-06 Heat Exchanger, Especially Oil/Coolant Cooler Abandoned US20080257536A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004003790.6 2004-01-23
DE102004003790A DE102004003790A1 (de) 2004-01-23 2004-01-23 Wärmetauscher, insbesondere Öl-/Kühlmittel-Kühler
PCT/EP2004/013828 WO2005071342A1 (de) 2004-01-23 2004-12-06 Wärmetauscher, insbesondere öl-/kühlmittel-kühler

Publications (1)

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US20080257536A1 true US20080257536A1 (en) 2008-10-23

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US10/585,971 Abandoned US20080257536A1 (en) 2004-01-23 2004-12-06 Heat Exchanger, Especially Oil/Coolant Cooler

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US (1) US20080257536A1 (pt)
EP (1) EP1711768A1 (pt)
JP (1) JP2007518958A (pt)
BR (1) BRPI0418440A (pt)
DE (1) DE102004003790A1 (pt)
MX (1) MXPA06008292A (pt)
WO (1) WO2005071342A1 (pt)

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US20110024095A1 (en) * 2009-07-30 2011-02-03 Mark Kozdras Heat Exchanger with End Plate Providing Mounting Flange
US20120118546A1 (en) * 2008-12-17 2012-05-17 Swep International Ab High pressure port peninsula
US20120175092A1 (en) * 2009-07-16 2012-07-12 Klaus Otahal Plate heat exchanger having a plurality of plates stacked one upon the other
US20120175093A1 (en) * 2009-09-15 2012-07-12 Swen-Juri Bauer Plate heat exchanger
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US9732708B2 (en) 2015-01-16 2017-08-15 Mahle International Gmbh Internal combustion engine
US9863715B2 (en) 2011-08-11 2018-01-09 Mahle International Gmbh Plate heat exchanger with flanged base or connecting plate
US9933215B2 (en) 2012-04-26 2018-04-03 Dana Canada Corporation Heat exchanger with adapter module
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JP4966633B2 (ja) * 2006-12-06 2012-07-04 株式会社マーレ フィルターシステムズ オイルクーラ
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JP5298100B2 (ja) 2010-11-15 2013-09-25 トヨタ自動車株式会社 車両用熱交換器
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MXPA06008292A (es) 2007-01-26
DE102004003790A1 (de) 2005-08-11
EP1711768A1 (de) 2006-10-18
WO2005071342A1 (de) 2005-08-04
BRPI0418440A (pt) 2007-05-22
JP2007518958A (ja) 2007-07-12

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