EP1604163A1 - Echangeur thermique, notamment refroidisseur de gaz d'echappement pour automobiles - Google Patents

Echangeur thermique, notamment refroidisseur de gaz d'echappement pour automobiles

Info

Publication number
EP1604163A1
EP1604163A1 EP03767527A EP03767527A EP1604163A1 EP 1604163 A1 EP1604163 A1 EP 1604163A1 EP 03767527 A EP03767527 A EP 03767527A EP 03767527 A EP03767527 A EP 03767527A EP 1604163 A1 EP1604163 A1 EP 1604163A1
Authority
EP
European Patent Office
Prior art keywords
coolant
heat exchanger
channels
exhaust gas
exchanger according
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.)
Withdrawn
Application number
EP03767527A
Other languages
German (de)
English (en)
Inventor
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
Publication of EP1604163A1 publication Critical patent/EP1604163A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F28D9/0025—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 being formed by zig-zag bend 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
    • 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
    • F28F2220/00—Closure means, e.g. end caps on header boxes or plugs on conduits

Definitions

  • Heat exchangers in particular exhaust gas coolers for motor vehicles
  • the invention relates to a heat exchanger, in particular a charge air or exhaust gas cooler for motor vehicles according to the preamble of patent claim 1, known from DE-A 199 07 163 by the applicant.
  • a welded exhaust gas heat exchanger with a tube bundle of rectangular tubes is known, through which the exhaust gas flows on the inside and the coolant on the outside.
  • the tube bundle is connected via tube sheets to a housing which has coolant connections.
  • the exhaust gas enters the tube bundle via an inlet diffuser and leaves the heat exchanger via an outlet diffuser.
  • tube bundle heat exchanger in a soldered round tube construction, was known from WO 00/26514.
  • tube bundle systems of this type have potential in terms of their power density, in particular in comparison to plate systems.
  • DE-A 198 33 338 and DE-A 198 46 518 have made known plate-type exhaust gas heat exchangers in which the flow channels for the exhaust gas and the coolant are formed from the same or different types of heat exchanger plates. These known exhaust gas heat exchangers are characterized by a large number of individual parts and have the disadvantage that the heat exchanger plates sometimes have complicated plate shapes that cause high tool costs.
  • DE-A 195 11 991 made known to the applicant a plate-type heat exchanger in stacked construction, the flow channels of which have different flow channel heights because of the different heat exchange media.
  • This known heat exchanger with stacked disks is intended in particular for the cooling of charge air or exhaust gas by the coolant of the internal combustion engine.
  • this heat exchanger has an increased pressure loss due to the 90 degree deflections of gas and coolant.
  • the flow channels for both the gas, in particular the exhaust gas of an internal combustion engine or the charge air for the internal combustion engine and for the coolant are formed by a meandering, wave-shaped or trapezoidal shaped metal strip and formed by the housing. Housing and metal band form a soldered block with separate flow channels.
  • the simple construction is advantageous here, since special plates do not have to be manufactured, stacked and soldered to each flow channel, be it for the gas or for the coolant.
  • the cross section of the flow channels can be made variable, for. B. rectangular, trapezoidal, wavy or the like. Gas and coolant channels are located directly next to each other, so that efficient heat transfer between the two media can take place. The number of individual parts for the heat exchanger according to the invention is considerably reduced.
  • the coolant channels are front-end through a comb-shaped tube sheet locked.
  • the tube sheet has individual tines or dividers that are inserted into the open sides of the meander profile and then soldered.
  • the coolant side is thus sealed off from the gas side. This simplifies assembly and lowers manufacturing costs, since no tube ends of a tube bundle have to be inserted into a tube sheet and welded or soldered in.
  • the flow channels are approximately rectangular, the cross-section for the gas channels preferably being larger.
  • the rectangular cross-sectional shape of the flow channels results in a compact, pressure-resistant and largely vibration-free heat exchanger block.
  • the soldering of the comb-like tube sheet to the meander profile, d. H. Closing the coolant channels at the front is particularly easy and safe due to the rectangular profile.
  • the rectangular flow channels are particularly suitable for receiving turbulence inserts (see below).
  • the housing is composed of a U-profile and an end plate or of two U-profiles which enclose the meandering profile. This allows easy assembly and reliable soldering.
  • a distributor and a collecting channel for the coolant are arranged on the housing and the end plate, respectively, which extend transversely to the coolant channels. This results in a uniform distribution of the coolant over all coolant channels and thus a uniform cooling of the exhaust gas. It is also advantageous here if the distribution or collecting channels are formed directly from the end plate or the U-profile.
  • turbulence inserts are arranged in the coolant channels and / or gas channels in order to improve the heat transfer and - due to the soldering - also the pressure and Vibration resistance of the entire heat exchanger (the turbulence inserts or ribs act as tie rods).
  • FIG. 2a a folded metal strip with flow channels
  • FIG. 3 the heat exchanger without a housing
  • Fig. 4 is an exhaust gas cooler with a modified housing shape
  • Fig. 4a the exhaust gas cooler without a diffuser.
  • Fig. 1 shows an exhaust gas cooler 1 in a simplified representation with a diffuser 2 for the entry of the exhaust gas, which is indicated by an arrow A.
  • the exhaust gas cooler 1 has an approximately cuboid housing 3 with an upper side 3a, where a coolant distribution channel 4 and a coolant collection channel 5 are arranged, on which coolant connections 4a, 5a are located.
  • the coolant for cooling the exhaust gas thus enters the exhaust gas cooler 1 via the coolant connection 4a and leaves it via the coolant connection 5a, the coolant being identified by arrows K.
  • An outlet diffuser, via which the exhaust gas leaves the exhaust gas cooler 1, is not shown here.
  • Such an exhaust gas cooler is used in particular in motor vehicles with exhaust gas recirculation (EGR).
  • EGR exhaust gas recirculation
  • FIG. 2 shows the heat exchanger according to FIG. 1 with its individual parts in an exploded view.
  • the same reference numbers are used for the same parts.
  • the diffuser 2 is displaced counter to the flow direction of the exhaust gas, and the housing 3 with the distribution and collection channels 4, 5 for the coolant is lifted off.
  • a heat exchanger block 6 can be seen, which consists of a metal band 7 folded in a meandering shape. This meandering profile 7 forms flow channels 8 for the exhaust gas and flow channels 9 for the coolant.
  • the flow channels 9 for the coolant are open to the upper side of the block 6, the flow channels for the exhaust gas to the lower side of the block 6.
  • Turbulence inserts 10, 11, which protrude beyond block 6 for visualization, are inserted into flow channels 8, 9, each of which has a rectangular cross section.
  • two tube plates 12, 13 can be seen, which are comb-like and have individual prongs 14, 15 or separating webs. The latter are pushed (in the drawing) from top to bottom into the flow channels 9, which are open at the top, ie the coolant channels, so that they completely close off their cross-section at the end.
  • the housing 3 is pushed over the heat exchanger block 6, so that the distributor and collecting channels 4, 5 extend across the coolant channels.
  • the area of the coolant channels 9 located between the coolant channels 4, 5 is covered and closed by the upper side 3a of the housing.
  • Fig. 2a shows the meandering folded metal band 7 as an individual part. Due to the angular folding or folding of the metal strip, rectangular flow cross sections are formed for the flow channels 8, 9, each having the same length I. However, the width is different: the exhaust gas channels 8 have a width b1 that is greater than the width b2 of the coolant channels 9.
  • FIG. 3 shows the exhaust gas cooler 1 according to FIGS. 1 and 2, but without the housing 3 and without the diffuser 2, ie the heat exchanger block 6.
  • the same reference numbers are used for the same parts.
  • the separating webs 14 simultaneously close the coolant channels 9 at the end.
  • the coolant flows in the illustrated embodiment in cocurrent with the exhaust gas, ie the coolant first enters the distribution channel 4 and is distributed there across the coolant channels 9, then flows through the coolant channels 9 in the direction of the exhaust gas flow and then reaches the collecting duct 5, from where the coolant leaves the exhaust gas cooler 1 again.
  • a counterflow with reverse flow direction of the coolant is also possible.
  • the exhaust gas cooler 1 described above is preferably made of stainless steel.
  • the heat exchanger 1 can also be used as a charge air cooler for cooling the combustion air of internal combustion engines - it is then preferably made from an aluminum alloy.
  • Fig. 4 shows a further embodiment of an exhaust gas cooler 16 with a modified housing shape, which consists of two U-profiles 17, 18. Both U-profiles 17, 18 are connected laterally with longitudinal seams, of which the front longitudinal seam 19 is visible. At the end, the exhaust gas cooler 16 has an exhaust gas inlet connection, ie. H. a diffuser 20.
  • the upper U-profile 17 has a transverse distribution channel 21 with a coolant inlet connection 22 and a likewise transverse collection channel 23 with a coolant outlet connection 24. Both channels 21, 23 can be formed from the sheet of the U-section 17.
  • FIG. 4a shows the exhaust gas cooler 16 without the diffuser 20, ie with an end face 25 for the entry of the exhaust gas, which is identified by an arrow A.
  • the end face 25 has - similar to the previous embodiment - on exhaust gas passages 27, which - are open downwards - as viewed in the drawing ⁇ .
  • the coolant channels 26, which are closed at the end, are open at the top and are thus connected to the distributor channel 21. The coolant is thus first distributed in width across all coolant channels 26 and then flows through the exhaust gas cooler 16 in the longitudinal direction until it emerges again via the collecting channel 23.
  • the two housing halves 17, 18 are clearly recognizable here as U-profiles.

Abstract

La présente invention concerne un échangeur de chaleur, notamment un refroidisseur d'air de suralimentation ou de gaz d'échappement pour automobiles. Cet échangeur de chaleur comprend des canaux d'écoulement pour un gaz à refroidir et pour un fluide de refroidissement, qui sont situés dans un boîtier (3). Ces canaux d'écoulement pour le gaz passent à travers des plaques tubulaires, dans un diffuseur d'entrée et un diffuseur de sortie (2). Le fluide de refroidissement traverse le boîtier (3) par l'intermédiaire de raccords de fluide de refroidissement (4a, 4b). Selon cette invention, les canaux d'écoulement pour le gaz (8) et pour le fluide de refroidissement (9) sont constitués d'une bande métallique en serpentin et du boîtier (3), qui sont reliés l'un à l'autre par liaison de matière.
EP03767527A 2003-01-24 2003-11-10 Echangeur thermique, notamment refroidisseur de gaz d'echappement pour automobiles Withdrawn EP1604163A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10302948A DE10302948A1 (de) 2003-01-24 2003-01-24 Wärmeübertrager, insbesondere Abgaskühler für Kraftfahrzeuge
DE10302948 2003-01-24
PCT/EP2003/012496 WO2004065876A1 (fr) 2003-01-24 2003-11-10 Echangeur thermique, notamment refroidisseur de gaz d'echappement pour automobiles

Publications (1)

Publication Number Publication Date
EP1604163A1 true EP1604163A1 (fr) 2005-12-14

Family

ID=32667841

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03767527A Withdrawn EP1604163A1 (fr) 2003-01-24 2003-11-10 Echangeur thermique, notamment refroidisseur de gaz d'echappement pour automobiles

Country Status (7)

Country Link
US (1) US20060048926A1 (fr)
EP (1) EP1604163A1 (fr)
JP (1) JP2006513394A (fr)
CN (1) CN100501295C (fr)
AU (1) AU2003292004A1 (fr)
DE (1) DE10302948A1 (fr)
WO (1) WO2004065876A1 (fr)

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Also Published As

Publication number Publication date
US20060048926A1 (en) 2006-03-09
JP2006513394A (ja) 2006-04-20
WO2004065876A1 (fr) 2004-08-05
CN1742189A (zh) 2006-03-01
DE10302948A1 (de) 2004-08-05
CN100501295C (zh) 2009-06-17
AU2003292004A1 (en) 2004-08-13

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