EP1148231A1 - Refroidisseur egr - Google Patents

Refroidisseur egr Download PDF

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Publication number
EP1148231A1
EP1148231A1 EP00900811A EP00900811A EP1148231A1 EP 1148231 A1 EP1148231 A1 EP 1148231A1 EP 00900811 A EP00900811 A EP 00900811A EP 00900811 A EP00900811 A EP 00900811A EP 1148231 A1 EP1148231 A1 EP 1148231A1
Authority
EP
European Patent Office
Prior art keywords
shell
exhaust gas
cooling water
tubes
plates
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Withdrawn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
EP00900811A
Other languages
German (de)
English (en)
Other versions
EP1148231A4 (fr
Inventor
Makoto Hino Motors Ltd. TSUJITA
Keiichi Hino Motors Ltd. NAKAGOME
Katsuji Hino Motors Ltd. INOUE
Yoji Sankyo Radiator Co. Ltd. YAMASHITA
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.)
Hino Motors Ltd
Denso Sankyo Co Ltd
Original Assignee
Hino Motors Ltd
Sankyo Radiator Co Ltd
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
Priority claimed from JP11011776A external-priority patent/JP2000213424A/ja
Priority claimed from JP11158053A external-priority patent/JP2000345925A/ja
Priority claimed from JP25154699A external-priority patent/JP4248095B2/ja
Application filed by Hino Motors Ltd, Sankyo Radiator Co Ltd filed Critical Hino Motors Ltd
Publication of EP1148231A1 publication Critical patent/EP1148231A1/fr
Publication of EP1148231A4 publication Critical patent/EP1148231A4/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1653—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F28F1/405—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element and being formed of wires
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • 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
    • 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

Definitions

  • This invention relates to an EGR cooler attached to an EGR apparatus, which recirculates exhaust gas from an engine to suppress generation of nitrogen oxides, so as to cool the exhaust gas for recirculation.
  • Fig. 1 is a sectional view showing a conventional EGR cooler in which reference numeral 1 denotes a cylindrical shell with axial opposite ends to which plates 2 are respectively fixed so as to close the ends of the shell 1. Penetratingly fixed to the respective plates 2 are opposite ends of a number of tubes 3 which extend in parallel with axial extension x of the shell 1. The tubes 3 extend axially within the shell 1.
  • the shell 1 is provided with cooling water inlet 4 in the vicinity of one end of the shell 1 and with cooling water outlet 5 in the vicinity of the other end of the shell 1 so that cooling water 9 is supplied via the cooling water inlet 4 into the shell 1, flows outside of the tubes 3 and is discharged via the cooling water outlet 5 out of the shell 1.
  • the respective plates 2 have, on their sides away from the shell 1, hoods 6A and 6B fixed to the plates 2 so as to enclose end faces of the plates 2.
  • the one and the other hoods 6A and 6B provide central exhaust gas inlet and outlet 7 and 8, respectively, so that the exhaust gas 10 from the engine enters via the exhaust gas inlet 7 into the one hood 6A, is cooled, during passage through the tubes 3, by means of heat exchange with the cooling water 9 flowing outside of the tubes 3 and is discharged to the other hood 6B to be recirculated via the exhaust gas outlet 8 to the engine.
  • the one hood 6A is composed of a tapered portion 6x divergent in a linear contour from the exhaust gas inlet 7 toward the shell 1 and a cylindrical portion 6y with substantially the same diameter as that of the shell 1.
  • the flow of the exhaust gas 10 introduced via the exhaust gas inlet 7 tends to come off from the inner periphery of the tapered portion 6x to generate turbulence inside from the tapered portion 6x to the cylindrical portion 6y, leading to difficulty in introduction of the exhaust gas 10 into the tubes 3 arranged on the circumferential side of the plate 2.
  • Such non-uniform distribution of the exhaust gas 10 to the respective tubes 3 also adversely affects on heat exchange efficiency and causes a fear that the tubes 3 on the central side may have higher temperature than that of the tubes 3 on the circumferential side, leading to local thermal deformation.
  • the other hood 6B is formed in the same manner as the one hood 6A described above, so that the exhaust gas 10 discharged out of the tubes 3 on the circumferential side collides against the tapered portion 6x of the hood 6A and is abruptly changed in direction of flow, which causes pressure increase of outlet portions of the tubes 3 on the circumferential side, which in turn provides ventilation resistance to the exhaust gas 10 in the tubes 3 on the circumferential side, resulting in much more difficulty in introducing the exhaust gas 10 to the tubes 3 on the circumferential side.
  • This cause also results in non-uniform distribution of the exhaust gas 10 to the respective tubes 3 to thereby deteriorate the heat exchange efficiency and results in a fear that the temperature of the tubes 3 on the central side may be increased more than that of the tubes 3 on the circumferential side, leading to local thermal deformation.
  • the conventional arrangement of the tubes 3 is such that tubes 3 are arranged in staggered layout based on triangle as shown by two-dot chain line in the figure, which provides a relatively large clearance between the cylindrical shell 1 and the tubes 3 on the circumferential side.
  • the cooling water 9 introduced via the cooling water inlet 4 tends to flow preferentially on the circumferential side where the flow resistance is low whereas the cooling water 9 flows insufficiently on the central side where the tubes 3 are arranged closely.
  • the heat exchange efficiency in the tubes 3 on the central side is deteriorated than that in the tubes 3 on the circumferential side, causing a fear that the temperature of the tubes 3 on the central side may be increased more than that of the tubes 3 on the circumferential side to thereby cause local thermal deformation.
  • the cooling water 9 supplied via the cooling water inlet 4 to the shell 1 flows toward the cooling water outlet 5 non-uniformly with respect to cross section of the shell 1.
  • a route 12 in Fig. 1 prevailing is the flow which, after flowing into the shell 1 via the cooling water inlet 4, crooks catercorner toward the cooling water outlet 5 to thereby result in stagnation of the cooling water 9 in the vicinity of corners in the shell 1 opposed to the cooling water inlet and outlet 4 and 5, respectively, thus providing cooling water stagnant areas 13; as a result, arises a problem that the heat exchange efficiency in these areas decreases.
  • the tubes 3 may locally have high temperature in the vicinity of the cooling water stagnant area 13, causing thermal deformation.
  • Figs. 5 and 6 show a further conventional EGR cooler.
  • a shell 1 is formed in a box shape flattened longitudinally (perpendicular to the axial extension x of the shell 1) due to issues raised in mounting it on a vehicle.
  • the respective hoods 6A and 6B are diverged outwardly of the longer sides of the end faces of the shell 1 (vertically in the example shown in the figure) from the exhaust gas inlet and outlet 7 and 8, respectively, to the shell 1 so as to wholly enclose the end faces of the respective plates 2.
  • the exhaust gas 10 introduced via the exhaust gas inlet 7 into the hood 6A tends to flow straight in the flow direction at the time of being introduced and is hardly diffused outwardly of the longer sides of the end face of the shell 1; also arises a disadvantage that the gas flow tends to come off in the hood 6A in the vicinity of the exhaust gas inlet 7 to readily cause turbulence.
  • Fig. 7 shows a still further conventional EGR cooler.
  • the hoods are omitted due to issues raised in mounting it on a vehicle, and gas pipings 11 extending substantially perpendicular to the axial extension x of the shell 1 are bent or turned by about 90 degrees to and directly connected with opposite ends of the shell 1. Ends of the respective gas pipings 11 on the sides connected to the shell 1 are shaped in the form of bowls imitating the conventional hoods 6A and 6B (see Fig. 1) in the prior art shown in Figs. 1 to 4.
  • the present invention was made to provide an EGR cooler which can improve the heat exchange efficiency of the exhaust gas with the cooling water more than before and which, particularly in a case where local thermal deformation may occur, can prevent such thermal deformation from occurring.
  • Such formation of the plurality of streaks of spiral protrusions on the inner periphery of the tube causes the exhaust gas passing through the tube to be whirled along the spiral protrusions into turbulence and increases contact frequency and contact distance thereof to the inner periphery of the tube.
  • the exhaust gas is contacted with the inner periphery of the tube evenly and sufficiently, substantially improving the heat exchange efficiency of the EGR cooler.
  • Such fitting of the spiral wire rod into the tube causes the exhaust gas passing through the tube to be whirled along the spiral wire rod into turbulence, and increases contact frequency and contact distance thereof to the inner periphery of the tube. As a result, the exhaust gas is contacted with the inner periphery of the tube evenly and sufficiently, substantially improving the heat exchange efficiency of the EGR cooler.
  • the tubes on the circumferential side can be arranged along the cylindrical shell, thereby substantially reducing the clearance between them and substantially suppressing a tendency that the cooling water introduced into the shell preferentially flows on the circumferential side.
  • the gap between the respective tubes can be secured wider than before and the cooling water can be sufficiently supplied even into the tubes on the central side.
  • the tubes on the central side and the tubes on the circumferential side can be uniformly cooled to thereby avoid local high temperature, substantially improving the heat exchange efficiency of the exhaust gas with the cooling water.
  • An EGR cooler comprises a cylindrical shell, plates fixed to axial opposite ends of said shell so as to close the ends of the shell, hoods fixed to sides of the plates away from said shell so as to enclose end faces of the plates, tubes extending axially within the shell and having opposite ends penetratingly fixed to the respective plates, cooling water being supplied into and discharged from said shell, exhaust gas being passed through said tubes from one of the hoods to the other hood for thermal exchange of said exhaust gas with said cooling water, and is characterized in that the shell is provided, at one of axial ends thereof, with a cooling water inlet for introduction of cooling water into said shell and, at the other axial end of the shell, with a cooling water outlet for discharge of the cooling water out of said shell, there being provided a bypass outlet for pulling out part of the cooling water introduced via the cooling water inlet, at a position diametrically opposed to the cooling water inlet at the one axial end of the shell.
  • An EGR cooler comprises a cylindrical shell, plates fixed to axial opposite ends of said shell so as to close the ends of the shell, hoods fixed to sides of the plates away from said shell so as to enclose end faces of the plates, tubes extending axially within the shell and having opposite ends penetratingly fixed to the respective plates, cooling water being supplied into and discharged from said shell, exhaust gas being passed through said tubes from one of the hoods to the other hood for thermal exchange of said exhaust gas with said cooling water, and is characterized in that the hood on an inlet side of the exhaust gas is formed in a bellmouth shape in section with abrupt divergency from the exhaust gas inlet opened on the axial extension of the shell toward the shell in the direction of the longer sides of the end face of the shell, to thereby wholly enclose the end face of the plate, and having a curved portion adjacent to the exhaust gas inlet curved in a concave face facing outward, that a pair of guide plates arcuately curved from a direction along
  • An EGR cooler comprises a cylindrical shell, plates fixed to axial opposite ends of said shell so as to close the ends of the shell, hoods fixed to sides of the plates away from said shell so as to enclose end faces of the plates, tubes extending axially within the shell and having opposite ends penetratingly fixed to the respective plates, cooling water being supplied into and discharged from said shell, exhaust gas being passed through said tubes from one of the hood to the other hood for thermal exchange of said exhaust gas with said cooling water, and is characterized in that gas pipings extending substantially perpendicular to axial extension of the shell are gradually increased in diameter and gradually bent or turned to the axial opposite ends of the shell such that the gas flow does not come off, and is connected to the shell such that the axial extension x of the shell 1 and the axial line of each gas piping cross each other with a predetermined angle.
  • the exhaust gas coming out through each tube to the side of the axial other end of the shell is also smoothly changed in direction of flow to form laminar flow along the inner periphery of the gas piping and is smoothly discharged at the outlet portion of each tube, without being subjected to local ventilation resistance.
  • local high temperature of the tubes is averted and heat exchange efficiency of the exhaust gas with the cooling water is substantially improved.
  • Fig. 8 is an enlarged sectional view showing an embodiment of the invention as set forth in claim 1 in which the same parts as those in Fig. 1 are denoted by the same reference numerals.
  • each tube 3 extend through plates 2 and has a plurality of streaks (two streaks in the embodiment shown in Fig. 8) of spiral protrusions 14 and 15 on an inner periphery of the tube 3.
  • the plurality of streaks of spiral protrusions 14 and 15 are formed by spirally indenting the tube 3 from outside by means of a roll or the like having spiral convex streaks so that pressed portions from outside provide the plurality of streaks of spiral protrusions 14 and 15 on the inner periphery of the tube 3.
  • the plurality of streaks of spiral protrusions 14 and 15 may be formed by cutting the inner periphery of the tube 3 so as to leave the plurality of streaks of spiral protrusions 14 and 15.
  • Such formation of the plurality of streaks of spiral protrusions 14 and 15 on the inner periphery of the tube 3 causes the exhaust gas 10 passing through the tube 3 to be whirled along the spiral protrusions 14, 15 into turbulence, and increases contact frequency and contact distance thereof to the inner periphery of the tube 3.
  • the exhaust gas 10 is contacted with the inner periphery of the tube 3 evenly and sufficiently, enabling substantial improvement in the heat exchange efficiency of the EGR cooler.
  • Fig. 12 is an enlarged sectional view showing an embodiment of the invention as set forth in claim 2.
  • Adopted in this embodiment is a structure with a shell 1 formed as a cylindrical container, opposite ends of each tube 3 passing through and being fixed to axial opposite ends of the shell 1, respectively.
  • the tube 3 is of increased diameter and of increased wall thickness so that the flow cross sectional area and strength are enhanced to reduce the required number of tubes 3 to the minimum.
  • a gas flange 16 Fitted over a tip of the tube 3 projected outside of the shell 1 is a gas flange 16 to which line for recirculation of the exhaust gas 10 is directly connected in branched manner.
  • a spiral wire rod 17 in a form of a coiled spring is fitted in the tube 3 substantially over the whole length thereof; opposite ends of this spiral wire rod 17 are fixed to the inner periphery of the tube 3 by welding 18.
  • the embodiment shown in Fig. 12 is suitable for a case where the diameter and the wall thickness of the tube 3 are large, and has an advantage that machining is easier than the case where the above-mentioned spiral protrusions 14 and 15 as shown in Fig. 8 are formed.
  • the exhaust gas 10 passing through the tube 3 is whirled along the spiral wire rod 17 into turbulence, and its contact frequency and contact distance to the inner periphery of the tube 3 increase. As a result, the exhaust gas 10 is contacted with the inner periphery of the tube 3 evenly and sufficiently, enabling substantial improvement in the heat exchange efficiency of the EGR cooler.
  • Fig. 13 shows an embodiment of the invention as set forth in claim 3.
  • a hood 6A on the inlet side of the exhaust gas 10 is formed in a bellmouth shape with a concave face facing outward so as to gradually increase the diameter in the flow direction of the exhaust gas 10.
  • Fig 14 shows an embodiment of the invention as set forth in claim 4.
  • a hood 6B on the outlet side of the exhaust gas 10 is formed in a bowl shape with a convex face facing outward so as to gradually decrease the diameter in the flow direction of the exhaust gas 10.
  • the exhaust gas 10 is uniformly distributed to the respective tubes 3 to thereby substantially increase the heat exchange efficiency; moreover, the tubes 3 on the central side and the tubes 3 on the circumferential side can be uniformly heated to thereby avoid thermal deformation due to local high temperature.
  • Fig. 15 shows an embodiment of the invention as set forth in claim 5.
  • the respective tubes 3 are arranged in multi-concentric circles about the axis O of the shell 1.
  • the same number of tubes 3 having the same diameter as in Fig. 4 are arranged.
  • the tubes 3 on the circumferential side can be arranged along the cylindrical shell 1, to thereby substantially reduce the clearance between them and suppress a tendency that the cooling water 9 introduced into the shell 1 via the cooling water inlet 4 preferentially flows on the circumferential side.
  • the gap between the respective tubes 3 can be secured wider than before and the cooling water 9 can be sufficiently supplied even into the tubes 3 on the central side.
  • the tubes 3 on the central side and the tubes 3 on the circumferential side can be uniformly cooled to thereby avoid local high temperature, enabling substantial improvement in the heat exchange efficiency between the exhaust gas 10 and the cooling water 9.
  • Fig. 16 shows an embodiment of the invention as set forth in claim 6.
  • a bypass outlet 19 for pulling out part of the cooling water 9 introduced via the cooling water inlet 4, at a position diametrically opposed to the cooling water inlet 4 at one axial end of the shell 1.
  • the exhaust gas 10 of the engine enters via the exhaust gas inlet 7, passing through the one hood 6A, scatters and passes through the plurality of tubes 3, enters into the other hood 6B and is recirculated to the engine via the exhaust gas outlet 8; on the other hand, the cooling water 9 is supplied via the cooling water inlet 4 into the shell 1 and flows towards the cooling water outlet 5.
  • the cooling water 9 is supplied via the cooling water inlet 4 into the shell 1 and flows towards the cooling water outlet 5.
  • part of the introduced cooling water 9 is pulled out via the bypass outlet 19 while introducing the cooling water 9 via the cooling water inlet 4 into the shell 1, no cooling water 9 stagnates at a position diametrically opposed to the cooling water inlet 4 at the one axial end of the shell 1, and hence no cooling water stagnant area is formed here.
  • local high temperature in the tubes 3 on the one axial end of the shell 1 is averted, thereby substantial improving the heat exchange efficiency of the exhaust gas 10 with the cooling water 9.
  • Fig. 17 shows an embodiment of the invention as set forth in claim 7.
  • a hood 6A on the inlet side of the exhaust gas 10 is formed in a bellmouth shape in section with abrupt divergency from the exhaust gas inlet 7 opened on the axial extension x of the shell 1 toward the shell 1 in the direction of the longer sides (in vertical direction in the example shown in the figure) of the end face of the shell 1 to thereby wholly enclose the end face of the plate 2, and having a curved portion 20 adjacent to the exhaust gas inlet 7 curved in a concave face facing outward so that the gas flow does not come off.
  • a pair of guide plates 21 arcuately curved from a direction along the axial extension x of the shell 1 to outward of the direction of the longer side of the end face of the shell 1 are arranged in the form of figure (eight) in Chinese character, in the hood 6A on the inlet side of the exhaust gas at a position facing to the exhaust gas inlet 7.
  • a round bar 22 extending in the direction of the shorter sides (corresponding to the right and left direction in Fig. 6) of the end face of the shell 1 for dividing the main stream of the exhaust gas 10.
  • Fig. 18 shows an embodiment of the invention as set forth in claim 8.
  • gas pipings 11 extending substantially perpendicular to the axial extension x of the shell 1 are gradually increased in diameter and gradually bent or turned to the axial opposite ends of the shell 1 such that the gas flow does not come off, and is connected to the shell 1 such that the axial extension x of the shell 1 and the axial line y of each gas piping 11 cross each other with a predetermined angle ⁇ .
  • the exhaust gas 10 coming out through each tube 3 to the side of the axial other end of the shell 1 is also smoothly changed in direction of flow to form laminar flow along the inner periphery of the gas piping 11 and is smoothly discharged at the outlet portion of each tube 3, without being subjected to local ventilation resistance.
  • the exhaust gas 10 flows substantially uniformly to all the tubes 3, which averts local high temperature of the tubes 3 and substantially improves the heat exchange efficiency of the exhaust gas 10 with the cooling water 9.
  • EGR cooler according to the invention is not limited to the above-described embodiments and that various modifications and changes may be made without departing from the scope of the invention.
  • any combination thereof may attain synergic effect of improving the heat exchange efficiency of the exhaust gas with the cooling water. Shown in the illustrated examples is a case where the cooling water is in parallel flow to the exhaust gas so as to perform heat exchange; however, heat exchange may be performed in counterflow.
  • the EGR cooler according to the invention is suitable for used in attachment to an EGR apparatus which recirculates exhaust gas from an engine to reduce generation of nitrogen oxides.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
EP00900811A 1999-01-20 2000-01-19 Refroidisseur egr Withdrawn EP1148231A4 (fr)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP11011776A JP2000213424A (ja) 1999-01-20 1999-01-20 Ｅｇｒク―ラ
JP1177699 1999-01-20
JP11158053A JP2000345925A (ja) 1999-06-04 1999-06-04 Ｅｇｒクーラ
JP15805399 1999-06-04
JP25154699A JP4248095B2 (ja) 1999-09-06 1999-09-06 Ｅｇｒクーラ
JP25154699 1999-09-06
PCT/JP2000/000218 WO2000043663A1 (fr) 1999-01-20 2000-01-19 Refroidisseur egr

Publications (2)

Publication Number Publication Date
EP1148231A1 true EP1148231A1 (fr) 2001-10-24
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Cited By (12)

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FR2831252A1 (fr) * 2001-07-10 2003-04-25 Denso Corp Echangeur de chaleur de gaz d'echappement
WO2003036212A1 (fr) * 2001-10-26 2003-05-01 Valeo Termico, S.A. Echangeur thermique notamment destine au refroidissement de gaz dans un systeme de recyclage de gaz d'echappement
DE10216773A1 (de) * 2002-04-15 2003-11-06 Benteler Automobiltechnik Gmbh Kühler für ein dem Hauptabgasstrom eines Verbrennungsmotors entnommenes Abgas
EP1548267A1 (fr) * 2002-10-02 2005-06-29 Hino Motors, Ltd. Refroidisseur pour recirculation des gaz d'echappement
WO2007088031A1 (fr) * 2006-02-01 2007-08-09 Sener, Ingenieria Y Sistemas, S.A. Collecteur a paroi mince ayant une section transversale variable destine a des panneaux d'absorption solaire
WO2010018083A1 (fr) * 2008-08-12 2010-02-18 Behr Gmbh & Co. Kg Système de refroidissement des gaz d'échappement d'un véhicule automobile
CN101943529A (zh) * 2010-09-29 2011-01-12 西安航天华威化工生物工程有限公司 高温气体干法降温装置及方法
DE102009034723A1 (de) * 2009-07-24 2011-01-27 Behr Gmbh & Co. Kg Wärmetauscher und Aufladesystem
CN103470409A (zh) * 2013-10-06 2013-12-25 无锡优萌汽车部件制造有限公司 一种egr冷却器
WO2016064286A1 (fr) * 2014-10-20 2016-04-28 Ferrum S.A. Échangeur de chaleur tubulaire de type gaz-gaz
FR3098579A1 (fr) * 2019-07-08 2021-01-15 Renaults S.A.S. Conduit de guidage de l’écoulement d’un flux de gaz comportant une ailette de perturbation de l’écoulement
WO2024008650A1 (fr) * 2022-07-07 2024-01-11 Valeo Systemes Thermiques Dispositif de regulation thermique, notamment de refroidissement

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US20030111209A1 (en) * 1999-01-20 2003-06-19 Hino Motors, Ltd. EGR cooler
KR102142662B1 (ko) 2014-10-17 2020-08-07 현대자동차주식회사 차량용 egr 쿨러
KR102166999B1 (ko) 2015-10-26 2020-10-16 한온시스템 주식회사 배기가스 쿨러

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GB330590A (en) * 1929-03-12 1930-06-12 William Henry Owen Improvements relating to air heaters
US3826304A (en) * 1967-10-11 1974-07-30 Universal Oil Prod Co Advantageous configuration of tubing for internal boiling
JPS50153347A (fr) * 1974-05-30 1975-12-10
JPH09310991A (ja) * 1996-05-20 1997-12-02 Usui Internatl Ind Co Ltd Ｅｇｒガス冷却装置
JPH10306995A (ja) * 1997-05-06 1998-11-17 Usui Internatl Ind Co Ltd 伝熱管およびこれを使用したｅｇｒガス冷却装置

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Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7527088B2 (en) 2001-07-10 2009-05-05 Denso Corporation Exhaust gas heat exchanger
FR2831252A1 (fr) * 2001-07-10 2003-04-25 Denso Corp Echangeur de chaleur de gaz d'echappement
WO2003036212A1 (fr) * 2001-10-26 2003-05-01 Valeo Termico, S.A. Echangeur thermique notamment destine au refroidissement de gaz dans un systeme de recyclage de gaz d'echappement
ES2199036A1 (es) * 2001-10-26 2004-02-01 Valeo Termico Sa Intercambiador de calor, especialmente para el enfriamiento de gases en un sistema de recirculacion de gases de escape.
DE10216773A1 (de) * 2002-04-15 2003-11-06 Benteler Automobiltechnik Gmbh Kühler für ein dem Hauptabgasstrom eines Verbrennungsmotors entnommenes Abgas
DE10216773B4 (de) * 2002-04-15 2004-09-16 Benteler Automobiltechnik Gmbh Kühler für ein dem Hauptabgasstrom eines Verbrennungsmotors entnommenes Abgas
EP1548267A1 (fr) * 2002-10-02 2005-06-29 Hino Motors, Ltd. Refroidisseur pour recirculation des gaz d'echappement
EP1548267A4 (fr) * 2002-10-02 2010-09-08 Hino Motors Ltd Refroidisseur pour recirculation des gaz d'echappement
AU2007211610B2 (en) * 2006-02-01 2011-08-11 Sener, Ingenieria Y Sistemas, S.A. Thin wall header with a variable cross-section for solar absorption panels
WO2007088031A1 (fr) * 2006-02-01 2007-08-09 Sener, Ingenieria Y Sistemas, S.A. Collecteur a paroi mince ayant une section transversale variable destine a des panneaux d'absorption solaire
US8186341B2 (en) 2006-02-01 2012-05-29 Sener, Ingenieria Y Sistemas, S.A. Thin wall header with a variable cross-section for solar absorption panels
US8671669B2 (en) 2008-08-12 2014-03-18 Behr Gmbh & Co. Kg Exhaust gas cooler for a motor vehicle
WO2010018083A1 (fr) * 2008-08-12 2010-02-18 Behr Gmbh & Co. Kg Système de refroidissement des gaz d'échappement d'un véhicule automobile
DE102009034723A1 (de) * 2009-07-24 2011-01-27 Behr Gmbh & Co. Kg Wärmetauscher und Aufladesystem
EP2278149A3 (fr) * 2009-07-24 2014-07-02 Behr GmbH & Co. KG Echangeur thermique et système de chargement
CN101943529A (zh) * 2010-09-29 2011-01-12 西安航天华威化工生物工程有限公司 高温气体干法降温装置及方法
CN103470409A (zh) * 2013-10-06 2013-12-25 无锡优萌汽车部件制造有限公司 一种egr冷却器
WO2016064286A1 (fr) * 2014-10-20 2016-04-28 Ferrum S.A. Échangeur de chaleur tubulaire de type gaz-gaz
FR3098579A1 (fr) * 2019-07-08 2021-01-15 Renaults S.A.S. Conduit de guidage de l’écoulement d’un flux de gaz comportant une ailette de perturbation de l’écoulement
WO2024008650A1 (fr) * 2022-07-07 2024-01-11 Valeo Systemes Thermiques Dispositif de regulation thermique, notamment de refroidissement
FR3137752A1 (fr) * 2022-07-07 2024-01-12 Valeo Systemes Thermiques Dispositif de régulation thermique, notamment de refroidissement

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KR20010102981A (ko) 2001-11-17
EP1148231A4 (fr) 2008-02-13

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