EP1664658A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur

Info

Publication number
EP1664658A1
EP1664658A1 EP04786925A EP04786925A EP1664658A1 EP 1664658 A1 EP1664658 A1 EP 1664658A1 EP 04786925 A EP04786925 A EP 04786925A EP 04786925 A EP04786925 A EP 04786925A EP 1664658 A1 EP1664658 A1 EP 1664658A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
passages
tube
flanks
flat
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.)
Ceased
Application number
EP04786925A
Other languages
German (de)
English (en)
Inventor
Karsten Emrich
Werner Helms
Markus Reck
Stefan Weise
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1664658A1 publication Critical patent/EP1664658A1/fr
Ceased legal-status Critical Current

Links

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
    • F28F9/04—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
    • F28F9/182—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding the heat-exchange conduits having ends with a particular shape, e.g. deformed; the heat-exchange conduits or end plates having supplementary joining means, e.g. abutments
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
    • B21D39/06—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes in openings, e.g. rolling-in
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • 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
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/08—Reinforcing means for header boxes

Definitions

  • the present invention relates to a heat exchanger, in particular a charge air cooler for a motor vehicle.
  • the air to be supplied to the combustion can be compressed, for example with a turbocharger, before it is supplied to the combustion chambers of the internal combustion engine.
  • the compression of the air also brings about a warming of the air, which is disadvantageous for an optimal course of the combustion process. For example, this can trigger premature ignition or increased nitrogen oxide emissions.
  • a heat exchanger designed as a charge air cooler is connected downstream of the turbocharger, with which the compressed air can be cooled to a permissible temperature before it is burned.
  • a charge air cooler is described for example in DE 197 57 034 A1.
  • the hot air is introduced into the heat exchanger comprises a first English Channel Sam- where it is distributed and flows into the flat tubes, which open in the Sam 'English Channel.
  • the flat tubes are next to one another and with the side surfaces containing the long sides of their cross section are arranged parallel to one another and form a stream. path through which cooling air is passed. Cooling fins are arranged in the flow path between the flat tubes, which effect an effective heat exchange between the flat tubes and the cooling air flow.
  • the flat tubes open into a second collecting duct, which feeds the cooled, compressed charge air flowing into them into the combustion in the engine.
  • the tubes are usually inserted into openings in a tube sheet and are soldered in a fluid-tight manner. With every load of compressed air, this solder joint is subject to high mechanical loads due to rapid pressure changes.
  • the narrow sides of flat tubes in particular do not meet the increasing strength requirements, which can result in leaks, particularly in the areas of such tube-base connections facing the tube plate.
  • a simple way to increase the strength of tube-to-floor connections is to use tubes and / or tube sheets with a higher wall thickness or from outer and / or inner fins with a higher material thickness.
  • the increased mechanical stability is obvious in both cases, but the additional effort in terms of material costs and weight is very high.
  • the object of the invention is to provide a heat exchanger, in particular a charge air cooler, in which mechanical loads on pipe-to-floor connections are reduced without additional material expenditure.
  • a heat exchanger has tubes which are suitable for a first medium to flow through and a second medium to flow around them, so that heat can be transferred from the first to the second medium or vice versa.
  • At least one header box communicating with the tubes comprises at least one tube plate, the tube plate being essentially flat and having passages into which the tubes can be inserted to form the communicating connection with the header box.
  • the basic idea of the invention is to design the regions of the tube sheet which surround the passages in the form of depressions or elevations such that the passages are each arranged at the “bottom” of a depression or on the “summit” of an elevation.
  • the passages are encircled by flanks, namely the flanks of the depressions or elevations.
  • flanks namely the flanks of the depressions or elevations.
  • Such a geometric shape particularly due to the circumferential design of the flank, increases the bending stiffness of the tube sheet in several directions in relation to a flat tube sheet, so that deformations which occur as a result of a pressure load on the collecting tank are reduced, as a result of which pipes are connected to the tube sheet be mechanically relieved.
  • the depressions or elevations are preferably so wide that the flanks of two adjacent passages adjoin one another to form a reinforcing bead.
  • the flanks have an essentially constant width over the circumference of a passage.
  • the bending stiffness of the tube sheet is increased substantially uniformly in all directions.
  • the tubes are designed as flat tubes and are arranged in one or more rows.
  • the passages and the beads between them formed by the flanks are then elongated in accordance with the pipe cross sections.
  • the flanks preferably each have a curve with an approximately constant radius of curvature or a plurality of curves with different radius of curvature.
  • the flanks each comprise one or more flat areas, so that the flanks or the beads between the passages have a faceted shape. This enables safe manufacturing with low manufacturing tolerances.
  • the at least one flat region with the respective passage is particularly preferably an obtuse angle.
  • the angle between the flat area of the flank and the passage is preferably between 30 ° and 60 °, particularly preferably about 45 °.
  • the width of the flank may be approximately equal to the height of the. Flank, so that there is a particularly high stability of the tube base against deformation.
  • the passages point out of the at least one collecting box. This may have the advantage that in each case an area of the flanks adjoining an edge of the tube sheet merges into an edge of the tube sheet that may be erected, which results in a further increase in the strength of the tube sheet.
  • the heat exchanger according to the invention is designed as a charge air cooler, which can be used particularly preferably in motor vehicles.
  • the intercooler two Sam- ⁇ melhimsten, of which a first is intended for distribution and a second for the collection of charge air.
  • Each of the collecting boxes advantageously has exactly one tube plate, which is provided with a number of tube openings. It is also advantageous to use a series of flat tubes with intermediate, in particular soldered corrugated fins, since this results in an increased heat transfer area.
  • Air is preferably used as the cooling medium, although other cooling media such as water or coolant are also conceivable.
  • a tube sheet is produced by setting up one or more edge regions of a flat sheet metal by means of a forming process and introducing adjacent depressions into the sheet metal.
  • the depressions each have an essentially flat base area and a flank encircling and encircling the base area.
  • the base areas of the depressions are then pierced with the aid of a pull-through process with the formation of pull-throughs. If tubes are to be inserted into the tube sheet from the side of the depressions, insertion is particularly preferred. bevelled to facilitate such insertion of pipes in the passages.
  • An embodiment of a tube sheet with one or more rows of identical flanks and / or passages is advantageous in terms of production technology.
  • FIG. 2 is a side view of a tube sheet with the tube inserted
  • Fig. 4 shows a longitudinal section through a tube sheet section with inserted tube
  • ⁇ Fig. 5 shows a longitudinal section through a tube sheet section with inserted tube.
  • FIG. 1 shows a section of a heat exchanger 10 in a perspective view.
  • a collecting box 20 for distributing a first medium consists of a tube sheet 30 and a box cover, not shown, which are welded to one another at a common contact surface 50.
  • the box cover is inserted into the tube sheet 30.
  • a tube sheet and a box cover are connected to one another by soldering, gluing or in a form-fitting manner, or are formed in one piece or in one piece, that is to say, for example, from a deformed plate.
  • the tube sheet 30 has a tube opening 60, the edge 70 of which is formed as a so-called passage out of the collecting box.
  • An essentially rectangular flat tube can be inserted into the tube opening 60 and can be soldered or welded to the tube sheet 30.
  • corrugated fins which adjoin the flat tube (also not shown) on both sides and are soldered to the latter, so that heat transfer from a medium flowing through the tube to a medium flowing around the tube and the fins or vice versa is increased.
  • the heat exchanger 10 comprises a whole series of alternating flat tubes and corrugated fins, which form a so-called tube-fin block.
  • the collecting box 20 may deform in such a way that its cross-sectional shape approximates a circular shape.
  • the passage 70 is surrounded by a circumferential flank 90 which adjoins the passage at an obtuse angle.
  • the flank has a width that is essentially constant around the passage 70. This results in a uniform stiffening of the tube sheet 30 both in the longitudinal direction of the tube sheet by the flank areas 91, 92 on the end faces of the passage 70 and in the transverse direction of the tube sheet by the flank areas 93, 94 on the long sides of the passage 70.
  • the tube 120 is inserted so far into the tube opening 160 that an upper edge region 121 of the tube 120 projects beyond the tube plate 130.
  • the protrusion of the tube 120 over the tube plate 130 must be kept as low as possible. For this reason, the tube opening 160 is located in an essentially flat central region 131 of the tube plate 130.
  • the passage 170 is framed by a flank 190, the end faces 191, 192 of which, on the one hand, at an obtuse angle into the passage 170 and, on the other hand, also at an obtuse angle, into an upright position
  • FIG. 3 shows a further exemplary embodiment of a heat exchanger 210 in a longitudinal section.
  • Pipes 220, 221, 222 are inserted in passages 270, 271, 272 of a tube sheet 230.
  • the passages 270, 271, 272 out of the collecting box, which is otherwise not shown, and the tubes 220, 221, 222 do not protrude beyond the tube sheet 230 or its passages 270, 271, 272.
  • the passages 270, 271, 272 are bordered by flanks 290, each of which has a flat portion 295.
  • the flat portion 295 forms an obtuse angle with the passage 270, which additionally reinforces the stiffening effect of the depression in the tube sheet 230 formed by the flank 290.
  • the flanks 290 adjoin one another directly, so that beads 299 are formed, which can be seen in their cross section in FIG. 3. As is clearly shown in this cross section, the beads 299 have no horizontal regions lying between the flanks 290.
  • the width b is advantageously similar to the height h of the flanks 290, particularly preferably approximately the same. For this reason, the angle between the flat portion 295 of the flank 290 and the passage 270 is approximately 45 °. For the beads 299 this results in a bead angle ⁇ of approximately 90 °, which is associated with a particularly high stiffening effect of the beads 299.
  • FIG. 4 shows the detail of a modified embodiment of the heat exchanger from FIG. 3.
  • the tube 320 protrudes beyond the passage 370, but ends below a surface 335 of the tube plate 330.
  • a soldered connection is improved by a soldering gap 376 which is additionally added to the soldering gap 375.
  • the soldering gap also serves as an insertion bevel for facilitating the insertion of the tube 320 into the tube sheet 330.
  • the tube 420 projects beyond the passage 470 and over a surface 435 of the tube sheet 430. Because of the associated greater tolerances with regard to the length of the tube 420, there is a further increase in production reliability.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Measuring Fluid Pressure (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

La présente invention concerne un échangeur de chaleur comportant des tubes et au moins un collecteur (20). Ce collecteur comprend lui-même un fond à tubes (30) pourvu de passages (70) qui sont entourés par des flancs (91-94).
EP04786925A 2003-09-17 2004-09-09 Echangeur de chaleur Ceased EP1664658A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10343239.6A DE10343239B4 (de) 2003-09-17 2003-09-17 Wärmeübertrager
PCT/EP2004/010069 WO2005028990A1 (fr) 2003-09-17 2004-09-09 Echangeur de chaleur

Publications (1)

Publication Number Publication Date
EP1664658A1 true EP1664658A1 (fr) 2006-06-07

Family

ID=34305890

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04786925A Ceased EP1664658A1 (fr) 2003-09-17 2004-09-09 Echangeur de chaleur

Country Status (9)

Country Link
US (1) US20070000657A1 (fr)
EP (1) EP1664658A1 (fr)
JP (1) JP2007506061A (fr)
CN (1) CN100472169C (fr)
BR (1) BRPI0414439B1 (fr)
DE (1) DE10343239B4 (fr)
RU (1) RU2380642C2 (fr)
WO (1) WO2005028990A1 (fr)
ZA (1) ZA200602221B (fr)

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US20100199955A1 (en) * 2009-02-06 2010-08-12 Paccar Inc Charge air cooler
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US8978746B2 (en) * 2011-02-04 2015-03-17 Modine Manufacturing Company Heat exchanger header plate
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FR3036469B1 (fr) * 2015-05-22 2017-06-09 Valeo Systemes Thermiques Plaque collectrice pour echangeur de chaleur, notamment pour vehicule automobile
FR3037388B1 (fr) * 2015-06-12 2019-07-26 Valeo Systemes Thermiques Ailette d'un echangeur thermique notamment pour vehicule automobile, et echangeur thermique correspondant
US10371464B2 (en) 2015-07-07 2019-08-06 Mahle International Gmbh Tube header for heat exchanger
FR3060726B1 (fr) * 2016-12-19 2019-10-25 Valeo Systemes Thermiques Echangeur de chaleur a plaque de renfort.
DE102017222742A1 (de) * 2017-12-14 2019-06-19 Hanon Systems Rohr, insbesondere Flachrohr für einen Abgaskühler und Abgaskühler
US11029101B2 (en) * 2019-02-11 2021-06-08 Hanon Systems Reverse header design for thermal cycle

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Also Published As

Publication number Publication date
ZA200602221B (en) 2007-05-30
RU2006112557A (ru) 2007-10-27
WO2005028990A1 (fr) 2005-03-31
DE10343239B4 (de) 2021-09-09
RU2380642C2 (ru) 2010-01-27
BRPI0414439B1 (pt) 2018-05-29
JP2007506061A (ja) 2007-03-15
CN1853083A (zh) 2006-10-25
CN100472169C (zh) 2009-03-25
DE10343239A1 (de) 2005-04-14
US20070000657A1 (en) 2007-01-04
BRPI0414439A (pt) 2006-11-14

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