US20080190592A1 - Exhaust Gas Heat Exchange, in Particular an Exhaust Gas Cooler for Exhaust Gas Recirculation in a Motor Vehicle - Google Patents

Exhaust Gas Heat Exchange, in Particular an Exhaust Gas Cooler for Exhaust Gas Recirculation in a Motor Vehicle Download PDF

Info

Publication number
US20080190592A1
US20080190592A1 US11/909,530 US90953006A US2008190592A1 US 20080190592 A1 US20080190592 A1 US 20080190592A1 US 90953006 A US90953006 A US 90953006A US 2008190592 A1 US2008190592 A1 US 2008190592A1
Authority
US
United States
Prior art keywords
exhaust gas
heat exchanger
exchanger according
flow
channels
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
US11/909,530
Inventor
Rolf Bruck
Peter Geskes
Ulrich Maucher
Jens Ruckwied
Andreas Scheeder
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.)
EMISSIONSTECHNOLOGIE MBH
Mahle Behr GmbH and Co KG
Vitesco Technologies Lohmar Verwaltungs GmbH
Original Assignee
Emitec Gesellschaft fuer Emissionstechnologie mbH
Behr GmbH and Co KG
EMISSIONSTECHNOLOGIE MBH
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 Emitec Gesellschaft fuer Emissionstechnologie mbH, Behr GmbH and Co KG, EMISSIONSTECHNOLOGIE MBH filed Critical Emitec Gesellschaft fuer Emissionstechnologie mbH
Assigned to EMITEC GESELLSCHAFT FUR EMISSIONSTECHNOLOGIE MBH, BEHR GMBH & CO. KG reassignment EMITEC GESELLSCHAFT FUR EMISSIONSTECHNOLOGIE MBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MAUCHER, ULRICH, GESKES, PETER, RUCKWIED, JENS, SCHEEDER, ANDREAS, BRUCK, ROLF
Publication of US20080190592A1 publication Critical patent/US20080190592A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
    • F01N3/28—Construction of catalytic reactors
    • F01N3/2892—Exhaust flow directors or the like, e.g. upstream of catalytic device
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
    • 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
    • F02M26/30—Connections of coolers to other devices, e.g. to valves, heaters, compressors or filters; Coolers characterised by their location on the engine
    • 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
    • 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
    • F02M26/35—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with means for cleaning or treating the recirculated gases, e.g. catalysts, condensate traps, particle filters or heaters
    • 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
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • 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
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • 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
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A50/00—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE in human health protection, e.g. against extreme weather
    • Y02A50/20—Air quality improvement or preservation, e.g. vehicle emission control or emission reduction by using catalytic converters
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention concerns an exhaust gas heat exchanger, in particular an exhaust gas cooler, for exhaust gas recirculation in motor vehicles according to the introductory part of patent claim 1 .
  • Exhaust gas heat exchangers are used on the one hand for heating purposes for heating the coolant and on the other hand for cooling the exhaust gases, that is, as an exhaust gas cooler in exhaust gas recirculation in motor vehicles.
  • Exhaust gas recirculation called EGR for short, serves, as is known, to lower consumption and reduce emissions.
  • Exhaust gas recirculation systems were known from DE-C 199 06 401, for example.
  • a problem with such exhaust gas heat exchangers, in particular exhaust gas coolers, is soot deposition with diesel exhaust gases in the exhaust gas ducts of the exhaust gas cooler.
  • a catalytic converter with flow channels parallel to each other is mounted in front of the exhaust gas heat exchanger.
  • the catalytic converter is of cylindrical design and arranged in an exhaust pipe which is also cylindrical.
  • the converter has gases flowing through it rectilinearly in the direction of its axis of symmetry and so extends the exhaust pipe in which the converter is arranged. Associated with this are increased space requirements compared with an exhaust gas heat exchanger without catalyst.
  • Diesel oxidation catalysts known by the abbreviation DOC, are known in the exhaust train in motor vehicles.
  • Such catalysts have a metal or ceramic honeycomb body having a plurality of fine exhaust gas channels which are coated with a catalytic substance, e.g. a precious metal such as platinum.
  • a catalytic substance e.g. a precious metal such as platinum.
  • the hydrocarbons oxidise into carbon dioxide and water where there is an excess of oxygen in the exhaust gas.
  • the structure of such catalysts e.g. with a matrix of special steel, is described in DE-A 29 24 592 and DE-A 35 43 011.
  • the metal support consists, for example, of one smooth and one corrugated spirally wound strip which is soldered or welded after winding. Then this honeycomb body is coated with a catalytic substance by known methods.
  • the object of the invention is to provide an exhaust gas heat exchanger with reduced space requirements.
  • a basic concept of the invention is to integrate the flow conducting device in the exhaust gas heat exchanger in such a way that, by means of the flow conducting device, an exhaust flow is influenced in direction of flow, flow rate, flow cross-sectional area, flow distribution and/or other flow parameters. As a result, for example diversion and/or expansion of flow becomes possible in a space-saving manner.
  • the flow channels communicate with each other, for example via apertures in partitions separating the flow channels from each other, so that pressure equalisation between the individual flow channels is ensured and flow distribution is evened out over the flow channels.
  • the heat exchanger channels are distributed at the end face over a surface which is opposite the exhaust gas inlet or outlet surface and particularly preferably is covered thereby.
  • an exhaust flow is distributed by the flow conducting device directly onto the heat exchanger channels or from the heat exchanger channels onto the flow channels.
  • a distance between the flow conducting device and the heat exchanger channels is made so small that the flow channels and the heat exchanger channels are equally subjected to an even flow distribution.
  • the flow conducting device goes from a round exhaust gas inlet surface to a quadrangular exhaust gas outlet surface or vice versa, allowing a transition from a round to an angular flow cross-section or vice versa.
  • the angles can also be rounded off in this case.
  • the exhaust gas heat exchanger has any heat exchanger channels, e.g. discs or a tube bundle with exhaust tubes.
  • the exhaust gas heat exchanger can also have a bypass channel with exhaust gas valve.
  • the flow conducting device is integrated in the exhaust gas heat exchanger, i.e. forms part of the exhaust gas heat exchanger.
  • this integrated unit can be prefabricated and inserted in an exhaust pipe, which facilitates assembly.
  • the flow conducting device is arranged inside the inlet connection piece, gaining the advantage of an extremely short length because the flow conducting device is inserted in an existing space in the exhaust gas heat exchanger.
  • the exhaust gas heat exchanger is arranged in an EGR pipe which is connected to the exhaust pipe of the engine either in front of or behind an exhaust turbine. This results in different exhaust gas temperatures upon entering the exhaust gas heat exchanger.
  • a density of flow channels in the cross-section is, for example, 100 to 600, preferably 150 to 300 per square inch.
  • the flow channels are, for example, 15 to 100, preferably up to 80, particularly preferably 30 to 40 mm long.
  • the flow channels are preferably coated with platinum, in particular with a density of 20 to 320, in particular 40 to 200 or 250 grammes per cubic foot.
  • the exhaust gas outlet surface is preferably 30 to 150%, particularly preferably 80 to 110% of a cross-sectional area of a heat exchanger block formed by the heat exchanger channels.
  • a pressure loss of the flow conducting device is preferably less than 100%, particularly preferably less than 50%, especially less than 30%, particularly advantageously 5 to 20% of a pressure loss of the heat exchanger channels all together.
  • a liquid coolant can flow round the heat exchanger channels.
  • the exhaust gas heat exchanger has a jacket for conducting the coolant, the jacket preferably having an inlet connection piece and an outlet connection piece for the coolant.
  • the heat exchanger channels can be cooled by a gaseous coolant, in particular cooling air.
  • FIG. 1 schematically a first embodiment of the invention
  • FIG. 2 schematically a second embodiment
  • FIG. 3 a schematic detail of a third embodiment
  • FIG. 4 a schematic detail of a fourth embodiment
  • FIG. 5 a schematic cross-section of a fifth embodiment
  • FIG. 6 a schematic cross-section of a sixth embodiment
  • FIG. 7 schematically an exhaust gas recirculation system.
  • FIG. 1 shows an exhaust gas heat exchanger 110 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 120 , for example a pipe bundle.
  • the heat exchanger channels lead on the inflow side into a distributing chamber 130 in which is arranged a flow conducting device 140 with a planar exhaust gas inlet surface 150 and a planar exhaust gas outlet surface 160 parallel to the exhaust gas inlet surface 150 .
  • the distributing chamber 130 is welded or soldered to the heat exchanger block 120 , for example.
  • a plurality of flow channels 170 extend from the exhaust gas inlet surface 150 to the exhaust gas outlet surface 160 .
  • the flow channels 170 are inclined relative to each other, so that a cross-section of an exhaust gas flow entering the exhaust gas heat exchanger 110 from the left in FIG. 1 is increased by means of the flow conducting device 140 , the exhaust gas flow advantageously being additionally evened out in the process.
  • the exhaust gas inlet surface 150 and the exhaust gas outlet surface 160 are round. If the cross-sectional area of the heat exchanger block 120 is angled, a minimum distance is necessary between the exhaust gas outlet surface 160 and the heat exchanger block 120 , as the distributing chamber 130 has a transitional region 180 from the round to the angular cross-sectional shape.
  • FIG. 2 shows an exhaust gas heat exchanger 210 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 220 , for example a pipe bundle.
  • the heat exchanger channels lead on the inflow side into a distributing chamber 230 in which is arranged a flow conducting device 240 having a planar exhaust gas inlet surface 250 and a planar exhaust gas outlet surface 260 parallel to the exhaust gas inlet surface 250 .
  • the distributing chamber 230 is welded or soldered to the heat exchanger block 220 , for example.
  • a plurality of flow channels 270 extend from the exhaust gas inlet surface 250 to the exhaust gas outlet surface 260 .
  • the flow channels 270 are partially curved, partially rectilinear and inclined relative to each other, so that a cross-section of an exhaust gas flow entering the exhaust gas heat exchanger 210 from the left in FIG. 2 is increased by means of the flow conducting device 240 , the exhaust gas flow advantageously being additionally evened out in the process.
  • the exhaust gas inlet surface 250 is round and the exhaust gas outlet surface 260 covers the cross-sectional area of the heat exchanger block 220 or of the heat exchanger channels and is for this purpose for example angled.
  • the flow conducting device therefore causes a transition from the round to the angular cross-sectional shape, so that the distance between the exhaust gas outlet surface 260 and the heat exchanger block 220 can be left very small.
  • FIG. 3 shows an exhaust gas heat exchanger 310 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 320 , for example a pipe bundle.
  • the heat exchanger channels lead on the inflow side into a distributing chamber 330 in which is arranged a flow conducting device 340 having a planar exhaust gas inlet surface 350 and a planar exhaust gas outlet surface 360 at an angle to the exhaust gas inlet surface 350 .
  • the distributing chamber 330 is welded or soldered to the heat exchanger block 320 , for example.
  • a plurality of flow channels 370 extend from the exhaust gas inlet surface 350 to the exhaust gas outlet surface 360 .
  • the flow channels 370 are curved and arranged in such a way that a cross-section of an exhaust gas flow entering the exhaust gas heat exchanger 310 from below in FIG. 3 is increased by means of the flow conducting device 340 , the exhaust gas flow advantageously being additionally evened out in the process. Furthermore, the flow conducting device 340 causes deflection of the exhaust gas flow.
  • FIG. 4 shows an exhaust gas heat exchanger 410 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 420 , for example a pipe bundle.
  • the heat exchanger channels lead on the inflow side into a distributing chamber 430 in which is arranged a flow conducting device 440 having a planar exhaust gas inlet surface 450 and a planar exhaust gas outlet surface 460 at an angle to the exhaust gas inlet surface 450 .
  • the distributing chamber 430 is welded or soldered to the heat exchanger block 420 , for example.
  • a plurality of flow channels 470 extend from the exhaust gas inlet surface 450 to the exhaust gas outlet surface 460 .
  • the flow channels 470 are parallel to each other, but inclined to surface normals both of the exhaust gas inlet surface 450 and of the exhaust gas outlet surface 460 , so that a cross-section of an exhaust gas flow entering the exhaust gas heat exchanger 410 from below in FIG. 4 is deflected and preferably evened out by means of the flow conducting device 440 .
  • FIG. 5 shows an exhaust gas heat exchanger 510 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 520 , for example a pipe bundle.
  • the heat exchanger channels lead on the inflow side into a distributing chamber 530 in which is arranged a flow conducting device 540 having a cylindrical exhaust gas inlet surface 550 and a cylindrical exhaust gas outlet surface 560 coaxial with the exhaust gas inlet surface 550 .
  • a plurality of flow channels 570 extend in a star shape from the exhaust gas inlet surface 550 to the exhaust gas outlet surface 560 .
  • the flow channels 570 are inclined relative to each other due to the star shape, but parallel to surface normals both of the exhaust gas inlet surface 550 and of the exhaust gas outlet surface 560 , that is to say, the flow channels 570 in each case lead perpendicularly to the surfaces 550 , 560 .
  • In order for exhaust gas to act as evenly as possible on the exhaust gas inlet surface 550 it is surrounded by an annular channel 590 through which an exhaust gas flow entering the exhaust gas heat exchanger 510 from below in FIG. 5 is conducted to the flow conducting device 540 .
  • the exhaust gas In an inner chamber of the flow conducting device, that is, inside the cylinder formed by the exhaust gas outlet surface 560 , the exhaust gas is collected and delivered to the heat exchanger channels of the heat exchanger block 520 .
  • FIG. 6 shows an exhaust gas heat exchanger 610 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 620 , for example a pipe bundle.
  • the heat exchanger channels lead on the inflow side into a distributing chamber 630 in which is arranged a flow conducting device 640 having a cylindrical exhaust gas inlet surface 650 and a cylindrical exhaust gas outlet surface 660 coaxial with the exhaust gas inlet surface 650 .
  • a plurality of flow channels 670 extend in a star shape from the exhaust gas inlet surface 650 to the exhaust gas outlet surface 660 .
  • the flow channels 670 are inclined relative to each other and furthermore relative to surface normals both of the exhaust gas inlet surface 650 and of the exhaust gas outlet surface 660 , due to the star shape.
  • exhaust gas In order for exhaust gas to act as evenly as possible on the exhaust gas inlet surface 650 , it is surrounded by an annular channel 690 through which an exhaust gas flow entering the exhaust gas heat exchanger 610 from below in FIG. 6 is conducted to the flow conducting device 640 .
  • the exhaust gas is collected and delivered to the heat exchanger channels of the heat exchanger block 620 , additional deflection and hence under certain circumstances a reduction of pressure loss being achieved by the inclination of the flow channels 670 to the surface normals of the surfaces 650 , 660 .
  • the distributing chamber is attached to the heat exchanger block by a flange joint.
  • FIG. 7 shows in a schematic view an exhaust gas recirculation system 20 with a diesel engine 21 with which are associated an intake pipe 22 and an exhaust pipe 23 .
  • a turbocharger 25 which is driven by an exhaust turbine 24 and which compresses the intake air and delivers it to a boost intercooler 26 .
  • the exhaust turbine 24 is arranged in the exhaust pipe 23 and subjected to the exhaust gases of the diesel engine 21 .
  • An exhaust gas recirculation pipe 28 having an exhaust gas recirculation valve 29 and an exhaust gas heat exchanger 30 is connected to the exhaust pipe 23 at a branch point 27 and to the intake pipe 22 at connection point 31 . The exhaust gas is thus returned in cooled form.
  • the exhaust gas heat exchanger 30 corresponds to the exhaust gas heat exchanger according to the invention described above. Moreover, the exhaust gas heat exchanger 30 can also be designed as an exhaust gas heat exchanger with bypass channel and exhaust gas bypass valve, e.g. according to DE 102 03 003 A1.

Abstract

The invention relates to an exhaust gas heat exchanger, in particular, to an exhaust gas cooler for exhaust gas recirculation in a motor vehicle comprising heat exchanging conduits which are passed through by exhaust gases, surrounded by a coolant and linked to a distributing and/or collecting chambers comprising a flux guiding device which is provided with the exhaust gas input and output sides and a plurality of channels extending therebetween and inclined to each other

Description

  • The invention concerns an exhaust gas heat exchanger, in particular an exhaust gas cooler, for exhaust gas recirculation in motor vehicles according to the introductory part of patent claim 1.
  • Exhaust gas heat exchangers are used on the one hand for heating purposes for heating the coolant and on the other hand for cooling the exhaust gases, that is, as an exhaust gas cooler in exhaust gas recirculation in motor vehicles. Exhaust gas recirculation, called EGR for short, serves, as is known, to lower consumption and reduce emissions. Exhaust gas recirculation systems were known from DE-C 199 06 401, for example. A problem with such exhaust gas heat exchangers, in particular exhaust gas coolers, is soot deposition with diesel exhaust gases in the exhaust gas ducts of the exhaust gas cooler. It was therefore proposed in EP-A 677 715 and in DE-A 195 40 683 for exhaust gas coolers that turbulence devices which prevent soot deposition in the exhaust gas flow be arranged in the exhaust pipes. For this purpose, on the inside of the exhaust gas ducts are strips or projections arranged in a V shape, so-called winglets, which generate specific eddies in the exhaust gas flow. Alternatively, ribs can also be used for this purpose. These measures are, however, not always enough to prevent soot deposits which lead to a reduction of performance of the exhaust gas heat exchanger concerned—with the result that the exhaust gas coolers must be given larger dimensions.
  • In other known exhaust gas heat exchangers it is provided that a catalytic converter with flow channels parallel to each other is mounted in front of the exhaust gas heat exchanger. Usually the catalytic converter is of cylindrical design and arranged in an exhaust pipe which is also cylindrical. The converter has gases flowing through it rectilinearly in the direction of its axis of symmetry and so extends the exhaust pipe in which the converter is arranged. Associated with this are increased space requirements compared with an exhaust gas heat exchanger without catalyst.
  • Diesel oxidation catalysts, known by the abbreviation DOC, are known in the exhaust train in motor vehicles. Such catalysts have a metal or ceramic honeycomb body having a plurality of fine exhaust gas channels which are coated with a catalytic substance, e.g. a precious metal such as platinum. In the presence of the catalyst, the hydrocarbons oxidise into carbon dioxide and water where there is an excess of oxygen in the exhaust gas. The structure of such catalysts, e.g. with a matrix of special steel, is described in DE-A 29 24 592 and DE-A 35 43 011. The metal support consists, for example, of one smooth and one corrugated spirally wound strip which is soldered or welded after winding. Then this honeycomb body is coated with a catalytic substance by known methods.
  • The object of the invention is to provide an exhaust gas heat exchanger with reduced space requirements.
  • This object is achieved by an exhaust gas heat exchanger having the characteristics of claim 1.
  • A basic concept of the invention is to integrate the flow conducting device in the exhaust gas heat exchanger in such a way that, by means of the flow conducting device, an exhaust flow is influenced in direction of flow, flow rate, flow cross-sectional area, flow distribution and/or other flow parameters. As a result, for example diversion and/or expansion of flow becomes possible in a space-saving manner.
  • According to a preferred embodiment the flow channels communicate with each other, for example via apertures in partitions separating the flow channels from each other, so that pressure equalisation between the individual flow channels is ensured and flow distribution is evened out over the flow channels.
  • According to a preferred embodiment, the heat exchanger channels are distributed at the end face over a surface which is opposite the exhaust gas inlet or outlet surface and particularly preferably is covered thereby. As a result, an exhaust flow is distributed by the flow conducting device directly onto the heat exchanger channels or from the heat exchanger channels onto the flow channels.
  • Particularly preferably, a distance between the flow conducting device and the heat exchanger channels is made so small that the flow channels and the heat exchanger channels are equally subjected to an even flow distribution.
  • According to an advantageous embodiment, the flow conducting device goes from a round exhaust gas inlet surface to a quadrangular exhaust gas outlet surface or vice versa, allowing a transition from a round to an angular flow cross-section or vice versa. The angles can also be rounded off in this case.
  • According to advantageous embodiments, the exhaust gas heat exchanger has any heat exchanger channels, e.g. discs or a tube bundle with exhaust tubes. The exhaust gas heat exchanger can also have a bypass channel with exhaust gas valve.
  • Advantageously, the flow conducting device is integrated in the exhaust gas heat exchanger, i.e. forms part of the exhaust gas heat exchanger. Hence this integrated unit can be prefabricated and inserted in an exhaust pipe, which facilitates assembly. Particularly advantageously, the flow conducting device is arranged inside the inlet connection piece, gaining the advantage of an extremely short length because the flow conducting device is inserted in an existing space in the exhaust gas heat exchanger.
  • According to a further advantageous embodiment of the invention, the exhaust gas heat exchanger is arranged in an EGR pipe which is connected to the exhaust pipe of the engine either in front of or behind an exhaust turbine. This results in different exhaust gas temperatures upon entering the exhaust gas heat exchanger.
  • A density of flow channels in the cross-section is, for example, 100 to 600, preferably 150 to 300 per square inch. The flow channels are, for example, 15 to 100, preferably up to 80, particularly preferably 30 to 40 mm long. The flow channels are preferably coated with platinum, in particular with a density of 20 to 320, in particular 40 to 200 or 250 grammes per cubic foot.
  • The exhaust gas outlet surface is preferably 30 to 150%, particularly preferably 80 to 110% of a cross-sectional area of a heat exchanger block formed by the heat exchanger channels. A pressure loss of the flow conducting device is preferably less than 100%, particularly preferably less than 50%, especially less than 30%, particularly advantageously 5 to 20% of a pressure loss of the heat exchanger channels all together.
  • According to a preferred embodiment, in particular a liquid coolant can flow round the heat exchanger channels. Preferably, the exhaust gas heat exchanger has a jacket for conducting the coolant, the jacket preferably having an inlet connection piece and an outlet connection piece for the coolant.
  • According to an advantageous variant, the heat exchanger channels can be cooled by a gaseous coolant, in particular cooling air.
  • Practical examples of the invention are shown in the drawings and described in more detail below. The figures show:
  • FIG. 1 schematically a first embodiment of the invention,
  • FIG. 2 schematically a second embodiment,
  • FIG. 3 a schematic detail of a third embodiment,
  • FIG. 4 a schematic detail of a fourth embodiment,
  • FIG. 5 a schematic cross-section of a fifth embodiment,
  • FIG. 6 a schematic cross-section of a sixth embodiment, and
  • FIG. 7 schematically an exhaust gas recirculation system.
    •
  • FIG. 1 shows an exhaust gas heat exchanger 110 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 120, for example a pipe bundle. The heat exchanger channels lead on the inflow side into a distributing chamber 130 in which is arranged a flow conducting device 140 with a planar exhaust gas inlet surface 150 and a planar exhaust gas outlet surface 160 parallel to the exhaust gas inlet surface 150. The distributing chamber 130 is welded or soldered to the heat exchanger block 120, for example.
  • A plurality of flow channels 170 extend from the exhaust gas inlet surface 150 to the exhaust gas outlet surface 160. The flow channels 170 are inclined relative to each other, so that a cross-section of an exhaust gas flow entering the exhaust gas heat exchanger 110 from the left in FIG. 1 is increased by means of the flow conducting device 140, the exhaust gas flow advantageously being additionally evened out in the process.
  • The exhaust gas inlet surface 150 and the exhaust gas outlet surface 160 are round. If the cross-sectional area of the heat exchanger block 120 is angled, a minimum distance is necessary between the exhaust gas outlet surface 160 and the heat exchanger block 120, as the distributing chamber 130 has a transitional region 180 from the round to the angular cross-sectional shape.
  • FIG. 2 shows an exhaust gas heat exchanger 210 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 220, for example a pipe bundle. The heat exchanger channels lead on the inflow side into a distributing chamber 230 in which is arranged a flow conducting device 240 having a planar exhaust gas inlet surface 250 and a planar exhaust gas outlet surface 260 parallel to the exhaust gas inlet surface 250. The distributing chamber 230 is welded or soldered to the heat exchanger block 220, for example.
  • A plurality of flow channels 270 extend from the exhaust gas inlet surface 250 to the exhaust gas outlet surface 260. The flow channels 270 are partially curved, partially rectilinear and inclined relative to each other, so that a cross-section of an exhaust gas flow entering the exhaust gas heat exchanger 210 from the left in FIG. 2 is increased by means of the flow conducting device 240, the exhaust gas flow advantageously being additionally evened out in the process.
  • The exhaust gas inlet surface 250 is round and the exhaust gas outlet surface 260 covers the cross-sectional area of the heat exchanger block 220 or of the heat exchanger channels and is for this purpose for example angled. The flow conducting device therefore causes a transition from the round to the angular cross-sectional shape, so that the distance between the exhaust gas outlet surface 260 and the heat exchanger block 220 can be left very small.
  • FIG. 3 shows an exhaust gas heat exchanger 310 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 320, for example a pipe bundle. The heat exchanger channels lead on the inflow side into a distributing chamber 330 in which is arranged a flow conducting device 340 having a planar exhaust gas inlet surface 350 and a planar exhaust gas outlet surface 360 at an angle to the exhaust gas inlet surface 350. The distributing chamber 330 is welded or soldered to the heat exchanger block 320, for example.
  • A plurality of flow channels 370 extend from the exhaust gas inlet surface 350 to the exhaust gas outlet surface 360. The flow channels 370 are curved and arranged in such a way that a cross-section of an exhaust gas flow entering the exhaust gas heat exchanger 310 from below in FIG. 3 is increased by means of the flow conducting device 340, the exhaust gas flow advantageously being additionally evened out in the process. Furthermore, the flow conducting device 340 causes deflection of the exhaust gas flow.
  • FIG. 4 shows an exhaust gas heat exchanger 410 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 420, for example a pipe bundle. The heat exchanger channels lead on the inflow side into a distributing chamber 430 in which is arranged a flow conducting device 440 having a planar exhaust gas inlet surface 450 and a planar exhaust gas outlet surface 460 at an angle to the exhaust gas inlet surface 450. The distributing chamber 430 is welded or soldered to the heat exchanger block 420, for example.
  • A plurality of flow channels 470 extend from the exhaust gas inlet surface 450 to the exhaust gas outlet surface 460. The flow channels 470 are parallel to each other, but inclined to surface normals both of the exhaust gas inlet surface 450 and of the exhaust gas outlet surface 460, so that a cross-section of an exhaust gas flow entering the exhaust gas heat exchanger 410 from below in FIG. 4 is deflected and preferably evened out by means of the flow conducting device 440.
  • FIG. 5 shows an exhaust gas heat exchanger 510 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 520, for example a pipe bundle. The heat exchanger channels lead on the inflow side into a distributing chamber 530 in which is arranged a flow conducting device 540 having a cylindrical exhaust gas inlet surface 550 and a cylindrical exhaust gas outlet surface 560 coaxial with the exhaust gas inlet surface 550.
  • A plurality of flow channels 570 extend in a star shape from the exhaust gas inlet surface 550 to the exhaust gas outlet surface 560. The flow channels 570 are inclined relative to each other due to the star shape, but parallel to surface normals both of the exhaust gas inlet surface 550 and of the exhaust gas outlet surface 560, that is to say, the flow channels 570 in each case lead perpendicularly to the surfaces 550, 560. In order for exhaust gas to act as evenly as possible on the exhaust gas inlet surface 550, it is surrounded by an annular channel 590 through which an exhaust gas flow entering the exhaust gas heat exchanger 510 from below in FIG. 5 is conducted to the flow conducting device 540. In an inner chamber of the flow conducting device, that is, inside the cylinder formed by the exhaust gas outlet surface 560, the exhaust gas is collected and delivered to the heat exchanger channels of the heat exchanger block 520.
  • FIG. 6 shows an exhaust gas heat exchanger 610 having heat exchanger channels, not shown in detail, which are combined in a heat exchanger block 620, for example a pipe bundle. The heat exchanger channels lead on the inflow side into a distributing chamber 630 in which is arranged a flow conducting device 640 having a cylindrical exhaust gas inlet surface 650 and a cylindrical exhaust gas outlet surface 660 coaxial with the exhaust gas inlet surface 650.
  • A plurality of flow channels 670 extend in a star shape from the exhaust gas inlet surface 650 to the exhaust gas outlet surface 660. The flow channels 670 are inclined relative to each other and furthermore relative to surface normals both of the exhaust gas inlet surface 650 and of the exhaust gas outlet surface 660, due to the star shape. In order for exhaust gas to act as evenly as possible on the exhaust gas inlet surface 650, it is surrounded by an annular channel 690 through which an exhaust gas flow entering the exhaust gas heat exchanger 610 from below in FIG. 6 is conducted to the flow conducting device 640. In an inner chamber of the flow conducting device, that is, inside the cylinder formed by the exhaust gas outlet surface 660, the exhaust gas is collected and delivered to the heat exchanger channels of the heat exchanger block 620, additional deflection and hence under certain circumstances a reduction of pressure loss being achieved by the inclination of the flow channels 670 to the surface normals of the surfaces 650, 660.
  • According to practical examples not shown, the distributing chamber is attached to the heat exchanger block by a flange joint.
  • FIG. 7 shows in a schematic view an exhaust gas recirculation system 20 with a diesel engine 21 with which are associated an intake pipe 22 and an exhaust pipe 23. In the intake pipe 22 is arranged a turbocharger 25 which is driven by an exhaust turbine 24 and which compresses the intake air and delivers it to a boost intercooler 26. The exhaust turbine 24 is arranged in the exhaust pipe 23 and subjected to the exhaust gases of the diesel engine 21. An exhaust gas recirculation pipe 28 having an exhaust gas recirculation valve 29 and an exhaust gas heat exchanger 30 is connected to the exhaust pipe 23 at a branch point 27 and to the intake pipe 22 at connection point 31. The exhaust gas is thus returned in cooled form. Removal of the exhaust gas at branch point 27 therefore takes place in front of the exhaust turbine 24. According to an alternative which is shown by an exhaust gas recirculation pipe 32 shown in broken lines, the exhaust gas is removed at a branch point 33 behind the exhaust turbine 24. The exhaust gas heat exchanger 30 corresponds to the exhaust gas heat exchanger according to the invention described above. Moreover, the exhaust gas heat exchanger 30 can also be designed as an exhaust gas heat exchanger with bypass channel and exhaust gas bypass valve, e.g. according to DE 102 03 003 A1.

Claims (19)

1. Exhaust gas heat exchanger, in particular an exhaust gas cooler, for exhaust gas recirculation in motor vehicles, having heat exchanger channels through which exhaust gas can flow and which lead into a distributing and/or collecting chamber, having a flow conducting device arranged in the distributing and/or collecting chamber, the flow conducting device comprising an exhaust gas inlet surface, an exhaust gas outlet surface and a plurality of flow channels extending from the exhaust gas inlet surface to the exhaust gas outlet surface, wherein the flow channels are inclined relative to each other, the flow channels are inclined relative to a surface normal of the exhaust gas inlet and/or outlet surface, and/or the surface normals of the exhaust gas inlet and outlet surfaces are inclined relative to each other.
2. Exhaust gas heat exchanger according to claim 1, wherein the flow conducting device is a catalytic converter, in particular oxidation or diesel oxidation catalyst.
3. Exhaust gas heat exchanger according to claim 1, wherein the flow channels, the exhaust gas inlet surface normal and/or the exhaust gas outlet surface normal are inclined relative to a principal direction of flow of the heat exchanger channels.
4. Exhaust gas heat exchanger according to claim 1 wherein the flow channels are completely separate from each other.
5. Exhaust gas heat exchanger according to claim 1, wherein the flow channels communicate with each other via apertures.
6. Exhaust gas heat exchanger according to claim 1, wherein the exhaust gas outlet surface is as large as the exhaust gas inlet surface.
7. Exhaust gas heat exchanger according to claim 1, wherein the exhaust gas outlet surface is smaller or larger than the exhaust gas inlet surface.
8. Exhaust gas heat exchanger according to claim 1 wherein the exhaust gas inlet or outlet surface is opposite the heat exchanger channels and in particular covers all the heat exchanger channels on the outlet or inlet side.
9. Exhaust gas heat exchanger according to claim 1 wherein a distance between the exhaust gas inlet or outlet surface and the heat exchanger channels is less than 15 mm, preferably less than 10 mm, particularly preferably less than 5 mm.
10. Exhaust gas heat exchanger according to claim 1, wherein the flow channels are of rectilinear design.
11. Exhaust gas heat exchanger according to claim 1 wherein the flow channels are of curved design.
12. Exhaust gas heat exchanger according to claim 1 wherein the exhaust gas inlet and/or outlet surface is round, in particular circular.
13. Exhaust gas heat exchanger according to claim 1, wherein the exhaust gas inlet and/or outlet surface is angular, in particular quadrangular or rectangular.
14. Exhaust gas heat exchanger according to claim 1, wherein the exhaust gas inlet and/or outlet surface is curved, in particular cylindrical.
15. Exhaust gas heat exchanger according to claim 1, wherein the exhaust gas inlet or outlet surface is surrounded by an annular channel for the exhaust gas.
16. Exhaust gas heat exchanger according to claim 1, wherein the distributing and/or collecting chamber is designed as a diffuser and the flow conducting device in particular fills the diffuser cross-section.
17. Exhaust gas heat exchanger according to claim 1, wherein the heat exchanger channels are formed by pairs of discs.
18. Exhaust gas heat exchanger according to claim 1, wherein the heat exchanger channels are formed by tubes which are held with their tube ends in tube bottoms and surrounded by a housing which conducts the coolant.
19. Exhaust gas heat exchanger according to claim 1, wherein the distributing and/or collecting chamber comprises a flange for connection to an exhaust pipe, in particular to an EGR pipe.
US11/909,530 2005-03-24 2006-03-23 Exhaust Gas Heat Exchange, in Particular an Exhaust Gas Cooler for Exhaust Gas Recirculation in a Motor Vehicle Abandoned US20080190592A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005014385A DE102005014385A1 (en) 2005-03-24 2005-03-24 Exhaust gas heat exchanger, in particular exhaust gas cooler for exhaust gas recirculation in motor vehicles
DE102005014385.7 2005-03-24
PCT/EP2006/002657 WO2006100069A1 (en) 2005-03-24 2006-03-23 Exhaust gas heat exchanger, in particular an exhaust gas cooler for exhaust gas recirculation in a motor vehicle

Publications (1)

Publication Number Publication Date
US20080190592A1 true US20080190592A1 (en) 2008-08-14

Family

ID=36678526

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/909,530 Abandoned US20080190592A1 (en) 2005-03-24 2006-03-23 Exhaust Gas Heat Exchange, in Particular an Exhaust Gas Cooler for Exhaust Gas Recirculation in a Motor Vehicle

Country Status (11)

Country Link
US (1) US20080190592A1 (en)
EP (2) EP1866591B1 (en)
JP (2) JP2008537044A (en)
KR (2) KR20100018090A (en)
CN (2) CN101650137B (en)
AT (2) ATE491130T1 (en)
DE (3) DE102005014385A1 (en)
DK (1) DK1866591T3 (en)
PL (2) PL2110636T3 (en)
RU (2) RU2511930C2 (en)
WO (1) WO2006100069A1 (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102333949A (en) * 2009-02-27 2012-01-25 株式会社小松制作所 Egr cooler
US20130312858A1 (en) * 2012-05-22 2013-11-28 Mitchell B. Cohen Flow control grid
US20140182285A1 (en) * 2012-12-30 2014-07-03 General Electric Company Charge air cooler cover and turbocharger bracket
US10443959B2 (en) * 2018-03-16 2019-10-15 Hamilton Sundstrand Corporation Integral heat exchanger manifold guide vanes and supports
CN110631044A (en) * 2019-10-14 2019-12-31 西安交通大学 Flue gas condensation heat exchanger of profile modeling flue gas runner structure
US11029102B2 (en) * 2017-01-13 2021-06-08 Hs Marston Aerospace Limited Heat exchanger
US11149591B2 (en) 2014-01-16 2021-10-19 Siemens Gamesa Renewable Energy A/S Heat accumulator comprising a diffuser portion
US11320215B2 (en) * 2019-06-24 2022-05-03 Denso International America, Inc. Radiator including thermal stress countermeasure

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009021616A1 (en) * 2009-05-15 2010-11-18 Makon Engineering Gmbh Exhaust gas post treating device for use in ship, has catalyst unit post treating exhaust gas of exhaust gas flow, and adding unit adding component during post treatment of exhaust gas, where adding unit includes fluid tank
JP2010270604A (en) * 2009-05-19 2010-12-02 Denso Corp Exhaust gas cooling device
TWI385354B (en) * 2009-11-27 2013-02-11 Univ Chienkuo Technology Automotive exhaust gas generator
AT511548A1 (en) 2011-06-06 2012-12-15 Avl List Gmbh INTERNAL COMBUSTION ENGINE WITH AT LEAST ONE CATALYST UNIT
CN102538561B (en) * 2012-03-01 2013-04-17 张家港格林沙洲锅炉有限公司 Variable-diameter connecting tube with flue gas flow guiding device
CN102661671A (en) * 2012-04-28 2012-09-12 泰州市远望换热设备有限公司 Heat exchanger air inlet buffer structure
DE102013100887A1 (en) * 2013-01-29 2014-07-31 Benteler Automobiltechnik Gmbh Guide plate in the heat exchanger
CN102840788A (en) * 2012-09-19 2012-12-26 常州大学 Inlet and outlet head of gas plate heat exchanger
EP2728155A1 (en) 2012-11-06 2014-05-07 BorgWarner Inc. Heat exchange device for exchanging heat between fluids
KR101407927B1 (en) 2012-11-13 2014-06-17 주식회사 엘지화학 Stereoscopic display device comprising a light blocking pattern using the phase change ink
CN103322833A (en) * 2013-06-19 2013-09-25 上海宝钢节能技术有限公司 Heat exchanger with high heat exchange efficiency and long service life
DE102014221326A1 (en) * 2014-10-21 2016-04-21 Thyssenkrupp Marine Systems Gmbh submarine
CN104534902B (en) * 2014-12-30 2017-01-25 黑龙江国德节能服务有限公司 Heat through-flow S-type efficient and anticorrosion heat exchanger and heat exchange method
CN105134420A (en) * 2015-09-24 2015-12-09 重庆小康工业集团股份有限公司 Air guide pipe of EGR system
RU2610972C1 (en) * 2015-11-26 2017-02-17 Общество с ограниченной ответственностью Научно-производственное объединение "Спецнефтехиммаш" Camera of product distribution, which has air cooler with tubular internal cavity and square outdoor geometry
CN106401639B (en) * 2016-04-13 2020-07-21 山东理工大学 Electric control adjusting type air intake and exhaust diversion system of ventilation air heat countercurrent oxidation device
US10539377B2 (en) 2017-01-12 2020-01-21 Hamilton Sundstrand Corporation Variable headers for heat exchangers
CN107824045A (en) * 2017-12-05 2018-03-23 中国华电科工集团有限公司 A kind of SCR methods denitration flue gas flow guiding device
JP6834929B2 (en) * 2017-12-14 2021-02-24 トヨタ自動車株式会社 EGR cooler
US11255615B2 (en) 2018-01-23 2022-02-22 Hamilton Sundstrand Corporation Heat exchanger flexible manifold
DE102018133362A1 (en) * 2018-12-21 2020-06-25 Eisenmann Se Injection device for dispensing a gas, process gas system for supplying a process gas, and device and method for the thermal or thermo-chemical treatment of material
CN111780611B (en) * 2020-07-30 2022-03-15 武汉第二船舶设计研究所(中国船舶重工集团公司第七一九研究所) Subregion flow self-adjusting heat exchanger
CN114166047B (en) * 2021-10-28 2023-06-02 中国船舶重工集团公司第七一九研究所 Printed circuit board type heat exchanger
KR102603025B1 (en) * 2021-11-25 2023-11-16 한국기계연구원 Multi-channel heat exchanger for cryogenic hydrogen liquefaction

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3313344A (en) * 1965-05-11 1967-04-11 Gen Motors Corp Plate fin heat exchanger with curved expansion tubes
US4215744A (en) * 1978-06-30 1980-08-05 Solartrap, Inc. Heat exchanger
US4381590A (en) * 1979-06-19 1983-05-03 Suddeutsche Kuhlerfabrik Julius Fr. Behr Gmbh & Co. Kg Method for manufacturing a catalytic reactor carrier matrix
US5057483A (en) * 1990-02-22 1991-10-15 Engelhard Corporation Catalyst composition containing segregated platinum and rhodium components
US5103641A (en) * 1987-10-02 1992-04-14 Emitec Gesellschaft Fur Emissionstechnologie Mbh Catalyst arrangement with flow guide body
US5886080A (en) * 1995-04-21 1999-03-23 Nok Corporation Resin composition
US20010006103A1 (en) * 1996-02-01 2001-07-05 Nash James S. Dual-density header fin for unit-cell plate-fin heat exchanger
US20030161766A1 (en) * 2000-10-18 2003-08-28 Brueck Rolf Heatable honeycomb body with two different coatings
US20040035566A1 (en) * 2002-06-28 2004-02-26 Takayuki Hayashi Exhaust heat exchanger
US20040152595A1 (en) * 2001-08-02 2004-08-05 Wolfgang Maus Honeycomb body having a contraction limiter
US20050039729A1 (en) * 2002-01-26 2005-02-24 Behr Gmbh & Co Kg Exhaust gas heat exchanger
US6944947B1 (en) * 1995-11-01 2005-09-20 Behr Gmbh & Co. Heat exchanger for cooling exhaust gas and method of manufacturing same

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR918616A (en) * 1945-08-27 1947-02-13 Fluid guiding system for heat exchanger
GB789068A (en) * 1953-03-04 1958-01-15 Andre Huet Improvements in or relating to heat exchangers
SU821835A1 (en) * 1979-01-31 1981-04-15 Производственное Объединение"Техэнергохимпром" Boiler-utilizer
DE3543011A1 (en) 1985-12-05 1987-06-11 Sueddeutsche Kuehler Behr Matrix for a catalyst
DE9406197U1 (en) * 1994-04-14 1994-06-16 Behr Gmbh & Co Heat exchanger for cooling exhaust gas from a motor vehicle engine
JPH08312340A (en) * 1995-05-11 1996-11-26 Usui Internatl Ind Co Ltd Exhaust emission control device
CN2258267Y (en) * 1996-04-24 1997-07-23 宣捍东 Heat exchanger using waste heat of air conditioner
JP2000130276A (en) * 1998-08-21 2000-05-09 Toyota Motor Corp Exhaust gas introducing device of internal combustion engine
JP2000161873A (en) * 1998-11-26 2000-06-16 Toyota Motor Corp Heat exchanger
JP2000220972A (en) * 1998-11-27 2000-08-08 Usui Internatl Ind Co Ltd Egr gas cooler
DE19906401C1 (en) * 1999-02-16 2000-08-31 Ranco Inc Of Delaware Wilmingt Exhaust gas recirculation system
JP3937635B2 (en) 1999-03-01 2007-06-27 いすゞ自動車株式会社 EGR cooler with exhaust gas purification function
CN2404087Y (en) * 2000-01-26 2000-11-01 淮阴辉煌太阳能有限公司 Assembled spiral sleeve heat exchanger
ES2198179B1 (en) * 2001-03-01 2004-11-16 Valeo Termico, S.A. HEAT EXCHANGER FOR GASES.
DE10218521A1 (en) * 2002-04-25 2003-11-06 Behr Gmbh & Co Exhaust gas heat exchanger, especially for motor vehicles
JP4031393B2 (en) * 2003-05-26 2008-01-09 日産ディーゼル工業株式会社 EGR cooler

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3313344A (en) * 1965-05-11 1967-04-11 Gen Motors Corp Plate fin heat exchanger with curved expansion tubes
US4215744A (en) * 1978-06-30 1980-08-05 Solartrap, Inc. Heat exchanger
US4381590A (en) * 1979-06-19 1983-05-03 Suddeutsche Kuhlerfabrik Julius Fr. Behr Gmbh & Co. Kg Method for manufacturing a catalytic reactor carrier matrix
US4521947A (en) * 1979-06-19 1985-06-11 Suddeutsche Kuhlerfabrik Julius Fr. Behr Gmbh & Co. Kg. Method for manufacturing a catalytic reactor carrier matrix
US5103641A (en) * 1987-10-02 1992-04-14 Emitec Gesellschaft Fur Emissionstechnologie Mbh Catalyst arrangement with flow guide body
US5057483A (en) * 1990-02-22 1991-10-15 Engelhard Corporation Catalyst composition containing segregated platinum and rhodium components
US5886080A (en) * 1995-04-21 1999-03-23 Nok Corporation Resin composition
US6944947B1 (en) * 1995-11-01 2005-09-20 Behr Gmbh & Co. Heat exchanger for cooling exhaust gas and method of manufacturing same
US20010006103A1 (en) * 1996-02-01 2001-07-05 Nash James S. Dual-density header fin for unit-cell plate-fin heat exchanger
US20030161766A1 (en) * 2000-10-18 2003-08-28 Brueck Rolf Heatable honeycomb body with two different coatings
US20040152595A1 (en) * 2001-08-02 2004-08-05 Wolfgang Maus Honeycomb body having a contraction limiter
US20050039729A1 (en) * 2002-01-26 2005-02-24 Behr Gmbh & Co Kg Exhaust gas heat exchanger
US7032577B2 (en) * 2002-01-26 2006-04-25 Behr Gmbh & Co. Kg Exhaust gas heat exchanger
US20060162706A1 (en) * 2002-01-26 2006-07-27 Behr Gmbh & Co. Kg Exhaust gas heat exchanger
US7168419B2 (en) * 2002-01-26 2007-01-30 Behr Gmbh & Co. Kg Exhaust gas heat exchanger
US20040035566A1 (en) * 2002-06-28 2004-02-26 Takayuki Hayashi Exhaust heat exchanger

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102333949A (en) * 2009-02-27 2012-01-25 株式会社小松制作所 Egr cooler
US20130312858A1 (en) * 2012-05-22 2013-11-28 Mitchell B. Cohen Flow control grid
US9409124B2 (en) * 2012-05-22 2016-08-09 Alstom Technology Ltd Flow control grid
US20140182285A1 (en) * 2012-12-30 2014-07-03 General Electric Company Charge air cooler cover and turbocharger bracket
US9599012B2 (en) * 2012-12-30 2017-03-21 General Electric Company Charge air cooler cover and turbocharger bracket
US11149591B2 (en) 2014-01-16 2021-10-19 Siemens Gamesa Renewable Energy A/S Heat accumulator comprising a diffuser portion
US11029102B2 (en) * 2017-01-13 2021-06-08 Hs Marston Aerospace Limited Heat exchanger
US10443959B2 (en) * 2018-03-16 2019-10-15 Hamilton Sundstrand Corporation Integral heat exchanger manifold guide vanes and supports
US11320215B2 (en) * 2019-06-24 2022-05-03 Denso International America, Inc. Radiator including thermal stress countermeasure
CN110631044A (en) * 2019-10-14 2019-12-31 西安交通大学 Flue gas condensation heat exchanger of profile modeling flue gas runner structure

Also Published As

Publication number Publication date
WO2006100069A1 (en) 2006-09-28
DE502006008484D1 (en) 2011-01-20
ATE491130T1 (en) 2010-12-15
RU2395752C2 (en) 2010-07-27
ATE445820T1 (en) 2009-10-15
EP2110636A1 (en) 2009-10-21
DE102005014385A1 (en) 2006-09-28
KR20100018090A (en) 2010-02-16
EP1866591B1 (en) 2009-10-14
JP2008537044A (en) 2008-09-11
DE502006005106D1 (en) 2009-11-26
RU2007139326A (en) 2009-04-27
JP2010133428A (en) 2010-06-17
PL1866591T3 (en) 2010-03-31
CN101147039A (en) 2008-03-19
PL2110636T3 (en) 2011-05-31
DK1866591T3 (en) 2010-03-01
RU2010113892A (en) 2011-10-20
EP2110636B1 (en) 2010-12-08
CN101650137B (en) 2012-08-29
EP1866591A1 (en) 2007-12-19
CN100526789C (en) 2009-08-12
CN101650137A (en) 2010-02-17
RU2511930C2 (en) 2014-04-10
KR20070121805A (en) 2007-12-27

Similar Documents

Publication Publication Date Title
US20080190592A1 (en) Exhaust Gas Heat Exchange, in Particular an Exhaust Gas Cooler for Exhaust Gas Recirculation in a Motor Vehicle
US8544454B2 (en) Heat exchanger for a motor vehicle
US7481040B2 (en) Exhaust-gas heat exchanger, in particular exhaust-gas cooler for exhaust gas recirculation in motor vehicles
US7210469B1 (en) Oxidation catalyst coating in a heat exchanger
US7931013B2 (en) Three-pass heat exchanger for an EGR system
JP5952787B2 (en) Heat exchanger for cooling automobile exhaust gas
JP2001159377A (en) Exhaust gas recirculation cooler
US8141359B2 (en) System and method for locomotive exhaust gas recirculation cooling and catalyst heating
US7594536B2 (en) EGR cooler
US7866305B2 (en) Flow channel, heat exchanger, exhaust gas recirculation system, charge air supply system, use of a heat exchanger
US9086003B2 (en) Exhaust gas cleaning device for a watercraft, method for operating an exhaust gas cleaning device and watercraft
US20150047619A1 (en) Exhaust gas radiator
JP2011157866A (en) Fluid filtering and cooling device of internal combustion engine
CN1325775C (en) Exhaust system for V-type engine
JP2004191035A (en) Heat transfer pipe internally provided with resin pipe
JP2010156272A (en) Egr device and egr filter of internal combustion engine
JPH11193993A (en) Multitubular egr gas-cooling device
JP2019127931A (en) Intake and exhaust device of engine
US20140216018A1 (en) Internal combustion engine having at least one catalyst unit
JPH1136995A (en) Exhaust gas cooling device
JP2017133783A (en) Exhaust heat exchanger

Legal Events

Date Code Title Description
AS Assignment

Owner name: BEHR GMBH & CO. KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BRUCK, ROLF;GESKES, PETER;MAUCHER, ULRICH;AND OTHERS;REEL/FRAME:020293/0735;SIGNING DATES FROM 20070918 TO 20071107

Owner name: EMITEC GESELLSCHAFT FUR EMISSIONSTECHNOLOGIE MBH,

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BRUCK, ROLF;GESKES, PETER;MAUCHER, ULRICH;AND OTHERS;REEL/FRAME:020293/0735;SIGNING DATES FROM 20070918 TO 20071107

Owner name: BEHR GMBH & CO. KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BRUCK, ROLF;GESKES, PETER;MAUCHER, ULRICH;AND OTHERS;SIGNING DATES FROM 20070918 TO 20071107;REEL/FRAME:020293/0735

Owner name: EMITEC GESELLSCHAFT FUR EMISSIONSTECHNOLOGIE MBH,

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BRUCK, ROLF;GESKES, PETER;MAUCHER, ULRICH;AND OTHERS;SIGNING DATES FROM 20070918 TO 20071107;REEL/FRAME:020293/0735

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION