WO2019031090A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2019031090A1
WO2019031090A1 PCT/JP2018/024344 JP2018024344W WO2019031090A1 WO 2019031090 A1 WO2019031090 A1 WO 2019031090A1 JP 2018024344 W JP2018024344 W JP 2018024344W WO 2019031090 A1 WO2019031090 A1 WO 2019031090A1
Authority
WO
WIPO (PCT)
Prior art keywords
end side
cylindrical portion
support member
tube support
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/024344
Other languages
English (en)
Japanese (ja)
Inventor
泰治 西山
佳史 森田
幸太郎 隅内
由樹 松浦
祥弘 鎌田
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.)
Denso Sankyo Co Ltd
Original Assignee
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
Application filed by Sankyo Radiator Co Ltd filed Critical Sankyo Radiator Co Ltd
Publication of WO2019031090A1 publication Critical patent/WO2019031090A1/fr
Priority to US16/781,637 priority Critical patent/US20200173726A1/en
Anticipated expiration legal-status Critical
Ceased 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
    • 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
    • F28D7/1684—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 the conduits having a non-circular cross-section
    • 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
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • F28F21/083—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys from stainless steel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/084—Heat exchange elements made from metals or metal alloys from aluminium or aluminium alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding

Definitions

  • the present disclosure relates to a heat exchanger.
  • Patent Document 1 describes a heat exchanger that acts as a heat barrier by interposing an adapter ring between the shell body and a casing containing a catalytic converter by welding.
  • the high temperature heat generated during welding is cooled before reaching the brazed portion between the shell body and the tube sheet, and the brazed portion between the tube sheet and the tube, so that thermal strain etc. It is described to reduce the influence of to almost negligible extent.
  • the tube sheet is shaped so as to extend only to the outside of the heat exchanger than the brazed joint with the tube. For this reason, the brazed joint between the shell body and the tube sheet is located outside the heat exchanger in the axial direction than the brazed joint between the tube and the tube sheet.
  • the axial dimension may be long.
  • the heat exchanger includes a tank in which the first fluid flows in or out, a plurality of tubes through which the first fluid flows, and a plurality of tubes joined and supported. And a shell main body which accommodates a plurality of tubes therein so as to allow the second fluid to flow around the tubes and is joined to the tube support members.
  • the tube support member is a cylindrical body extending in the direction in which the tank and the shell body are aligned, and one end side cylindrical portion provided on one end side in the axial direction in the cylindrical body and the other end in the axial direction in the cylindrical body A predetermined length in the axial direction between the one end side tubular portion and the other end side tubular portion, which is a portion having a diameter smaller than that of the other end side tubular portion provided on the side and the one end side tubular portion And an intermediate cylindrical portion provided.
  • the tank and the one end side tubular portion are joined by welding.
  • the shell body and the other end side tubular portion are joined by brazing.
  • the tube is brazed and supported with the tube support member with the outer peripheral portion in contact with the inner surface of the intermediate cylindrical portion.
  • the brazed joint between the shell body and the other end side tubular portion is located inward in the axial direction than the brazed joint between the outer peripheral portion of the tube and the intermediate tubular portion.
  • the shell main body is brazed to the tube support member at the axially inner side, ie, the other end side of the brazed joint with the tube support member in the tube, the axial length is suppressed.
  • the intermediate cylindrical portion is a portion having a diameter smaller than that of the one end side cylindrical portion welded to the tank, the heat transfer distance between the welded joint and the brazed joint can be secured.
  • the brazed joint between the shell main body and the other end side cylindrical portion is separated from the weld joint via the intermediate cylindrical portion, the strength can be secured. According to the above, this heat exchanger can suppress the thermal influence accompanying the weld joint of the tank and the tube support member, and can suppress the axial length.
  • FIG. 1 It is a sectional view showing a schematic structure of an exhaust gas cooler of a 1st embodiment. It is a fragmentary sectional view showing composition concerning joining of a tube in an exhaust gas cooler, a tube supporting member, a shell main part, and a tank. It is the elements on larger scale which showed joining of a tank and a tube support member, joining of a tube and a tube support member, and joining of a tube support member and a shell main body in 1st Embodiment. It is the enlarged view which showed joining of each part as a comparative example.
  • the heat exchanger is a device in which the first fluid flowing through the inside of the tube 30 and the second fluid flowing around the tube 30 exchange heat.
  • the exhaust heat exchange device described in the first embodiment is an example of the heat exchanger of the present disclosure.
  • the exhaust heat exchange apparatus is applied to an EGR cooler 1 (also referred to as an exhaust gas cooler 1) in an exhaust gas recirculation apparatus (EGR apparatus) such as a diesel engine for vehicles, which is an example of an internal combustion engine, or a gasoline engine.
  • EGR apparatus exhaust gas recirculation apparatus
  • the EGR cooler 1 is an exhaust heat exchanger that cools the exhaust gas (an example of a first fluid) recirculated to the intake side of the engine with a coolant (an example of a second fluid) as a cooling fluid for engine cooling.
  • the EGR cooler 1 includes a heat exchange core including a plurality of tubes 30 therein, a tank 4, a tank 5, a shell body 2, a water inflow pipe 20, a water outflow pipe 21, etc.
  • Each member is formed of, for example, a light weight and excellent in thermal conductivity, such as an aluminum material, an aluminum alloy material, and a stainless steel material, and the contact portion of each member is joined by brazing or welding.
  • Each member is coated with a brazing material.
  • the brazing material clad in each member is melted in a furnace brazing step or the like to join the members in a joining relationship.
  • coated brazing material can also be used.
  • the tank 4 is an upstream exhaust gas inflow portion into which exhaust gas from the exhaust pipe flows.
  • the tank 4 is provided with a flange portion 41 connected to the exhaust pipe at the upstream end and an inlet 40 opened inside the flange portion 41.
  • the downstream end of the tank 4 is coupled to the tube support 6.
  • the tank 5 is a downstream exhaust gas outlet portion which collects the exhaust gas flowing out of the tubes 30 and flows out into a pipe connected to the intake side of the engine.
  • the tank 5 is provided with a flange portion 51 connected to a pipe at a downstream end and an outlet 50 opened to the inside of the flange portion 51.
  • the upstream end of the tank 5 is coupled to the tube support 6.
  • the heat exchange core has a plurality of tubes 30 through which the exhaust gas discharged from the engine flows.
  • the shell body 2 accommodates a plurality of tubes 30 therein.
  • the shell body 2 is provided with a water inflow pipe 20 into which the cooling water flows in and a water outflow pipe 21 in which the cooling water flows out. Cooling water is circulated around the plurality of tubes 30 inside the shell body 2.
  • water passages 2a through which the cooling water flows are provided.
  • the tube 30 is a tube member through which the exhaust gas as the first fluid flows, and is formed, for example, by joining two tube plates.
  • Each tube plate is formed in a U-shape having a shallow cross section from a flat plate by pressing or rolling.
  • the open side of each tube plate is joined to each other, so that the tube 30 is formed as an elongated tube member having a flat rectangular shape in cross section intersecting in the longitudinal direction.
  • rectangular openings are formed.
  • inner fins may be provided inside each tube 30.
  • the plurality of tubes 30 constitute a tube assembly 3 stacked so that the main surfaces of the tubes on the long side of the flat rectangular cross section face each other.
  • the tube assembly 3 is a group of tube groups in which a plurality of tubes 30 are integrally stacked in a state where adjacent tubes 30 are in contact with each other.
  • the plurality of tubes 30 constituting the tube assembly 3 are brazed and joined with adjacent tubes 30 in contact with each other at both longitudinal ends. As shown in FIG. 2, the surfaces of the adjacent tubes 30 are separated at portions other than both ends of the tube assembly 3.
  • a plurality of asperities may be formed on the main surface of the tube as temperature lowering means for reducing the temperature of the temperature boundary layer of the cooling water on the outer surface of the tube 30.
  • the form except the both ends of the tube assembly 3 may be a form which the surfaces of the adjacent tube 30 are contacting.
  • the tube support member 6 is a cylindrical body provided at each of both ends in the longitudinal direction of the plurality of tubes 30 to support the tubes 30.
  • the tube support member 6 is a cylindrical body having an axial direction in which the tank 4 or the tank 5 and the tube assembly 3 are aligned.
  • the tube support member 6 supports the tube assembly 3 and is joined to the tank 4 and the shell body 2 on the upstream side of the exhaust gas flow in the EGR cooler 1.
  • the tube support member 6 supports the tube assembly 3 and is joined to the tank 5 and the shell body 2 on the downstream side of the exhaust gas flow in the EGR cooler 1.
  • the tube support member 6 located on the upstream side of the exhaust gas flow divides the exhaust gas passage in the tank 4 from the water passage 2a as a member for partitioning the internal space of the tank 4 and the internal space of the shell main body 2 .
  • the tube support member 6 located on the downstream side of the exhaust gas flow divides the water passage 2a from the exhaust gas passage in the tank 5 as a member for partitioning the internal space of the shell main body 2 and the internal space of the tank 5. .
  • the configuration of the tube support member 6 will be described with reference to FIG.
  • the tube support member 6 includes an intermediate cylindrical portion 62 having an inside diameter size to which the longitudinal end of the tube assembly 3 can be fitted.
  • the tube support member 6 includes an end-side cylindrical portion 60 joined to the tank 4 on one end side in the axial direction of the cylindrical body.
  • the tube supporting member 6 includes the other end side cylindrical portion 61 joined to the shell main body 2 on the other end side in the axial direction of the cylindrical body.
  • One end side in the axial direction is also the axial outer side in the EGR cooler 1 (heat exchanger).
  • the other end in the axial direction is also inside in the axial direction in the EGR cooler 1 (heat exchanger).
  • the other end side cylindrical portion 61 is a portion having a diameter smaller than that of the one end side cylindrical portion 60.
  • the intermediate cylindrical portion 62 is a portion whose diameter is smaller than that of the one end side cylindrical portion 60 and the other end side cylindrical portion 61, and is axially between the one end side cylindrical portion 60 and the other end side cylindrical portion 61. It is formed to have a predetermined length.
  • the intermediate cylindrical portion 62 has an inner surface shape that conforms to the surface shape of both ends of the tube assembly 3 to be brazed and joined.
  • the shape of the intermediate cylindrical portion 62 is not limited to the shape shown in FIG. 3 as long as it conforms to the surface shape of both ends of the tube assembly 3.
  • the tube support member 6 includes a first connecting portion 63 connecting the one end side cylindrical portion 60 and the intermediate cylindrical portion 62.
  • the first connecting portion 63 is an annular plate-like portion extending in a direction intersecting the axial direction of the tube support member 6.
  • the first connecting portion 63 is shaped so as to be inclined with respect to the intermediate cylindrical portion 62 so as to approach the other end side cylindrical portion 61 in the axial direction as it gets closer to the intermediate cylindrical portion 62.
  • the tube support member 6 includes a second connecting portion 64 that connects the intermediate cylindrical portion 62 and the other end side cylindrical portion 61.
  • the second connection portion 64 is an annular plate-like portion extending in a direction intersecting the axial direction of the tube support member 6.
  • the second connecting portion 64 is shaped so as to be inclined with respect to the intermediate cylindrical portion 62 so as to approach the one end side cylindrical portion 60 in the axial direction as it gets closer to the intermediate cylindrical portion 62.
  • the tube support member 6 is a tubular body in which the one end side tubular portion 60, the first connecting portion 63, the intermediate tubular portion 62, the second connecting portion 64, and the other end side tubular portion 61 are integrally formed.
  • the tube support member 6 can be manufactured by bending a plate-like member into a predetermined shape described above by a press machine or the like into an annular shape and joining the end portions.
  • the tube support member 6 is coupled to the tank 4, the tank 5, the shell body 2, and the tube assembly 3 while supporting the tube 4 from the outside.
  • the distal end portion 22 and the other end side tubular portion 61 in the shell main body 2 are joined by brazing in a state where the inner peripheral surface of the other end side tubular portion 61 and the outer peripheral surface of the distal end portion 22 are in contact. .
  • the upstream side open end provided inside the tip end portion 22 is located on the downstream side of the exhaust gas flow with respect to the second connection portion 64 and the intermediate cylindrical portion 62 in the axial direction.
  • the tube 30 and the tube support member 6 are joined by brazing in a state where the tip end portion 300 of the tube 30 and the inner surface of the intermediate cylindrical portion 62 are in contact with each other.
  • the brazed joint portion between the tube 30 and the intermediate cylindrical portion 62 is located on the other end side in the axial direction with respect to the weld joint portion between the tank 4 and the one end side cylindrical portion 60 and is located radially inside There is.
  • the joint of the shell body 2 and the tube support member 6, and the joint of the tube assembly 3 and the tube support member 6 allow the assembly of the shell body 2, the tube support member 6 and the tube assembly 3 to dissolve the brazing material in the furnace. It can be carried out by an in-furnace brazing process that heats at a temperature.
  • a welding / joining step of joining the tank 4 and the tank 5 to the brazed-joined assembly at the contact portions of the respective members is performed.
  • the downstream end portion 42 and the one end side tubular portion 60 in the tank 4 are welded in a state where the inner peripheral surface of the one end side tubular portion 60 and the outer peripheral surface of the downstream end portion 42 are in contact It is joined and joined.
  • the downstream side open end 42a provided on the inner side of the downstream side tip end portion 42 is positioned on the upstream side of the exhaust gas flow with respect to the first connection portion 63, the intermediate cylindrical portion 62, and the distal end open end 300a of the tube 30 in the axial direction. doing.
  • the connection between the tank 5 and the tube support member 6 is the same as the description related to the connection between the tank 4 and the tube support member 6 described above. That is, the upstream end 52 of the tank 5 corresponds to the downstream end 42 of the tank 4, and the upstream open end 52 a of the tank 5 corresponds to the downstream open end 42 a of the tank 4. As a result, the upstream opening of the tank 5 and the tip opening end 300 a of the tube 30 face each other, the internal space of the tank 5 communicates with the internal passage 30 a of each tube 30, and the inside of the tank 4, The internal passage 30a and the inside of the tank 5 form a series of exhaust gas passages communicating with each other.
  • the passages in the exhaust pipe are sequentially connected to the passages in the tank 4, the internal passages 30a in the tubes 30, the passages in the tank 5, and the passages in the piping connected to the flange portion 51.
  • the EGR cooler 1 a part of the exhaust gas discharged from the engine flows down the passage in the tank 4, the internal passage 30a in each tube 30, and the passage in the tank 5 sequentially from the passage in the exhaust pipe, and the flange portion It flows out of the outlet 50 of 51.
  • the exhaust gas that has flowed out of the EGR cooler 1 is again drawn into the engine.
  • engine cooling water exchanges heat with the exhaust gas flowing through the internal passage 30 a of the tube 30 while flowing from the water inflow pipe 20 into the water passage 2 a in the shell body 2 and flowing out from the water outflow pipe 21.
  • EGR cooler 1 since heat exchange is performed between the exhaust gas and the cooling water inside the shell main body 2, after the exhaust gas is sufficiently cooled, it is drawn into the engine. This can contribute to clearing the exhaust gas regulations and improving fuel consumption.
  • FIG. 4 shows the joining relationship of each part as a comparative example with respect to the heat exchanger of the first embodiment.
  • the tube sheet 60 ⁇ / b> G is shaped so as to extend only to the tanks 4 and 5 in the axial direction with respect to the brazed joint with the tube 30. Therefore, the brazed joint between the shell body 2 and the tube sheet 60G is located outside the heat exchanger in the axial direction than the brazed joint between the tube 30 and the tube sheet 60G. The joint between the tube sheet 60G and the tank 4 is welded.
  • the axial dimension becomes long due to the shape of such a tube sheet 60G. According to the heat exchanger of the first embodiment, the axial length can be reduced by solving the problem of the comparative example.
  • both are brazed and joined in the state through which each tube 30 was penetrated by the opening part 60G1 which penetrates the tube sheet 60G in the plate
  • the contact area between the tube 30 and the tube sheet 60G is small, and the brazed joint strength between the tube 30 and the tube sheet 60G can not be sufficiently obtained. Therefore, the heat quantity density given per unit area of the brazed joint is large due to the amount of heat transferred from the welded joint of the tanks 4 and 5 and the tube sheet 60G, and the joint strength of the brazed joint is reduced by the heat by the welded joint. Can be assumed.
  • the heat exchanger includes a tank 4, 5, a plurality of tubes 30, a tube support member 6 joined to and supported by the plurality of tubes 30 and a plurality of tubes 30. And a shell main body 2 accommodated and joined to the tube support member 6.
  • the tube support member 6 is a cylindrical body extending in the direction in which the tanks 4 and 5 and the shell body 2 are aligned.
  • the tube support member 6 includes a first end cylindrical portion 60 provided on one end side in the axial direction in the cylindrical body, a second end cylindrical portion 61 provided on the other end side in the axial direction, and a first end side cylindrical shape
  • An intermediate cylindrical portion 62 having a diameter smaller than that of the portion 60 and having a predetermined length in the axial direction between the one end side cylindrical portion 60 and the other end side cylindrical portion 61; It has formed.
  • the tanks 4 and 5 and the one end side cylindrical portion 60 are joined by welding.
  • the shell body 2 and the other end side tubular portion 61 are joined by brazing.
  • the tube 30 is brazed and supported with the tube support member 6 in a state where the outer peripheral portion is in contact with the inner surface of the intermediate cylindrical portion 62.
  • the brazed joint between the shell main body 2 and the other end side cylindrical portion 61 is located inward in the axial direction from the brazed joint between the outer peripheral portion of the tube 30 and the intermediate cylindrical portion 62.
  • the shell main body 2 is brazed to the tube support member 6 at the axially inner side, that is, the other end side of the brazed joint with the intermediate cylindrical portion 62 in the tube 30.
  • the axial length of the heat exchanger can be reduced.
  • the intermediate cylindrical portion 62 is a portion having a diameter smaller than that of the one end side cylindrical portion 60 welded to the tanks 4 and 5 by welding. With this configuration, the heat transfer distance between the welded joint and the brazed joint can be secured.
  • the tube support member 6 in the state where the outer peripheral portion of the tube 30 is in contact with the inner surface of the intermediate cylindrical portion 62 having a predetermined length in the axial direction, The tube support member 6 is joined by brazing.
  • the surface area of the intermediate tubular portion 62 and the brazed joint of the tube 30 can be formed large, so that the amount of heat received per unit area in the brazed joint among the heat transferred from the welded joint can be suppressed. .
  • the thermal shock to the brazed joint can be mitigated, so that damage to the brazed joint due to the weld joint can be suppressed.
  • this heat exchanger can improve the joint area of the tube 30 and the tube support member 6, and can suppress the thermal influence from the weld joint to the brazed joint.
  • the intermediate cylindrical portion 62 is a portion whose diameter is smaller than that of the other end side cylindrical portion 61. According to this configuration, the heat transfer distance between the intermediate cylindrical portion 62 and the other end side cylindrical portion 61 can be secured at least half the diameter dimension difference. Therefore, since the heat transfer distance from the weld joint to the brazed joint of the other end side cylindrical portion 61 can be long, the brazed joint of the tube support member 6 and the shell main body 2 is received from the weld joint It is possible to provide a heat exchanger with reduced thermal influence.
  • the tube support member 6 has a plate shape extending in a direction intersecting with the axial direction, and a first connecting portion 63 connecting the intermediate cylindrical portion 62 and the one end side cylindrical portion 60 in a direction intersecting with the axial direction And a second connecting portion 64 that connects the intermediate cylindrical portion 62 and the other end side cylindrical portion 61 in an extending plate shape.
  • the heat transfer distance between the intermediate cylindrical portion 62 and the one end side cylindrical portion 60 includes the length of the longitudinal section of the first connecting portion 63, and the intermediate cylindrical portion 62 and the other end side cylinder
  • the heat transfer distance to the first portion 61 includes the length of the longitudinal cross section of the second connection portion 64.
  • the heat transfer distance from the weld joint to the brazed joint of the intermediate cylindrical portion 62 and the heat transfer distance from the weld joint to the brazed joint of the other end side cylindrical portion 61 can be made longer. Therefore, it is possible to provide a heat exchanger in which the thermal influence of each brazed joint from the welded joint is reduced.
  • the EGR cooler 1 of the second embodiment is different from the EGR cooler 1 of the first embodiment in the positional relationship between the shell main body 2 and the other end side cylindrical portion 161. As shown in FIG. 5, the distal end portion 22 of the shell main body 2 and the other end side cylindrical portion 161 of the tube support member 106 are in contact with the outer peripheral surface of the other end side cylindrical portion 161 and the inner peripheral surface of the front end portion 22. It is brazed and joined in the state.
  • the tube support member 106 is joined in a state in which it is sandwiched between the tanks 4 and 5 and the shell main body 2 between the radially inner side and the radially outer side. .
  • the external force in the opposite direction acts on the tube support member 106 at both ends, the external force is not concentrated on the tube support member 106 in one direction by joining the tank 4, 5 and the shell main body 2, and the load is reduced. can do.
  • the shape of the tube support member 206 is different from the EGR cooler 1 of the first embodiment in the EGR cooler 1 of the third embodiment. As shown in FIG. 6, the tube support member 206 does not have a portion corresponding to the second connection portion 64 of the tube support member 6.
  • the tube support member 206 is a tubular body in which the one end side tubular portion 60, the first connecting portion 63, the intermediate tubular portion 62, and the other end side tubular portion 261 are integrally formed.
  • the intermediate cylindrical portion 62 and the other end side cylindrical portion 261 are configured to have approximately the same diameter.
  • the intermediate cylindrical portion 62 and the other end side cylindrical portion 261 form a cylindrical portion whose vertical cross-sectional shape is linear.
  • the tip end 22 of the shell body 2 and the other end side cylindrical portion 261 of the tube support member 206 are brazed and joined in a state where the inner peripheral surface of the other end side cylindrical portion 261 and the outer peripheral surface of the end portion 22 are in contact It is connected.
  • the tube support member 206 is coupled to the tank 4, the tank 5, the shell main body 2, and the tube assembly 3 while supporting the tank 4, the shell body 2 and the tube assembly 3 from the outside.
  • a force acts on the tube support member 206 radially outward from the tank 4, the tank 5, the shell main body 2, and the plurality of tubes 30, so that the tubes in the same direction are utilized.
  • the bonding force of the support member 206 can be secured.
  • the EGR cooler 1 of the fourth embodiment differs from the EGR cooler 1 of the third embodiment in the positional relationship between the shell main body 2 and the other end side cylindrical portion 261. As shown in FIG. 7, the outer peripheral surface of the other end side cylindrical portion 261 is in contact with the inner peripheral surface of the front end portion 22 of the front end portion 22 of the shell main body 2 and the other end side cylindrical portion 261 of the tube support member 206. It is brazed and joined in the state.
  • the tube support member 206 is joined by the tanks 4 and 5 and the shell main body 2 in a state in which the tube support member 206 is sandwiched between the inside and the outside .
  • the external force in the opposite direction acts on the tube support member 206 at both ends, the external force is not concentrated on the tube support member 206 in one direction by joining the tank 4, 5 and the shell main body 2, and the load is reduced. can do.
  • the EGR cooler 1 of the fifth embodiment is the same as the EGR cooler 1 of the first embodiment in the shape of the tube support member 306, the end shapes of the tanks 4 and 5 joined with the tube support member 306, and the shell main body 2
  • the end shapes are different.
  • the tube support member 306 is a tubular body in which the one end side tubular portion 360, the intermediate tubular portion 62 and the other end side tubular portion 361 are integrally formed.
  • the tube support member 306 includes an end-side cylindrical portion 360 joined to the tanks 4 and 5 on one end side in the axial direction of the cylindrical body.
  • the one end side cylindrical portion 360 is an annular plate portion extending in a direction intersecting the axial direction.
  • the one end side cylindrical portion 360 is shaped to extend along the downstream end portion 142 of the tank 4 to be welded and the upstream end portion 152 of the tank 5.
  • the one end side cylindrical portion 360 is an annular portion extending in the direction orthogonal to the axial direction, as with the downstream end portion 142 and the upstream end portion 152.
  • the one end side cylindrical portion 360 is a portion whose diameter is larger than that of the intermediate cylindrical portion 62.
  • the tube support member 306 includes the other end side cylindrical portion 361 joined to the shell main body 2 on the other end side in the axial direction of the cylindrical body.
  • the other end side tubular portion 361 is an annular plate portion extending in a direction intersecting the axial direction.
  • the other end side tubular portion 361 is shaped to extend along the tip end portion 122 of the shell main body 2 to be brazed and joined.
  • the other end side tubular portion 361 is an annular portion extending in the direction orthogonal to the axial direction, similarly to the tip end portion 122.
  • the other end cylindrical portion 361 is a portion having a diameter larger than that of the intermediate cylindrical portion 62.
  • the heat transfer distance between the one end side cylindrical portion 360 and the intermediate cylindrical portion 62 can be secured at least half the diameter dimension difference between the two. . Therefore, since the heat transfer distance from the weld joint to the brazed joint of the intermediate cylindrical portion 62 can be long, the brazed joint of the tube support member 306 and the tube 30 is received from the weld joint It is possible to provide a heat exchanger with reduced thermal influence.
  • the heat transfer distance between the other end side cylindrical portion 361 and the intermediate cylindrical portion 62 is secured by at least half the diameter dimension difference between the both. Can. Therefore, the heat transfer distance from the weld joint to the brazed joint of the intermediate cylindrical portion 62 and the heat transfer distance from the weld joint to the brazed joint of the other end cylindrical portion 361 can be made longer. Therefore, it is possible to provide a heat exchanger in which the thermal influence of each brazed joint from the welded joint is reduced.
  • the shape of the tube support member 406 is different from the EGR cooler 1 of the first embodiment in the EGR cooler 1 of the sixth embodiment.
  • the tube support member 406 has a longitudinal cross-sectional shape in which the intermediate cylindrical portion 462 protrudes radially inward of the one end side cylindrical portion 460 and the other end side cylindrical portion 461.
  • the tube support member 406 has a block-like longitudinal cross-sectional shape whose radial thickness dimension is thicker than the plate thickness of each of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the thickness dimension based on the difference in dimension in the radial direction of the outer peripheral surface with the inner peripheral surface of the one end side cylindrical portion 460 is larger than each thickness of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the thickness dimension based on the difference in dimension in the radial direction of the outer peripheral surface of the other end side cylindrical portion 461 with the inner peripheral surface is larger than the thickness of each of the tube 30, the tanks 4, 5 and the shell main body 2.
  • the thickness dimension of the one end side tubular portion 460 and the thickness dimension of the other end side tubular portion 461 are preferably twice or more the thickness dimensions of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the thickness dimension based on the radial dimension difference of the outer circumferential surface of the intermediate cylindrical portion 462 with the inner circumferential surface is larger than the thickness dimension of the one end side cylindrical portion 460 and the thickness dimension of the other end side cylindrical portion 461.
  • the thickness dimension of the intermediate cylindrical portion 462 is preferably twice or more the thickness dimension of the one end side cylindrical portion 460 or the thickness dimension of the other end side cylindrical portion 461.
  • the tube support member 406 has a block-like longitudinal cross-sectional shape that is thicker than the thickness of each of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the intermediate cylindrical portion 462 is provided so as to be located radially inward of the one end side cylindrical portion 460 and the other end side cylindrical portion 461.
  • the joint portions with the other members in each of the one end side cylindrical portion 460, the intermediate cylindrical portion 462, and the other end side cylindrical portion 461 are provided at intervals in the axial direction.
  • the tube support member 406 is a block-shaped member having a larger heat capacity per unit length in the axial direction than the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the heat of the welded joint is less likely to be transmitted to the brazed joint of the intermediate cylindrical portion 462, which contributes to suppressing the thermal effect on the brazed joint. Furthermore, since the welded joint of one end side cylindrical portion 460 and the brazed joint of intermediate cylindrical portion 462 are provided at intervals in the axial direction, the transmission between the welded joint and the brazed joint is It contributes to securing the heat distance. Further, the axial distance between the weld joint of the one end side tubular portion 460 and the brazed joint of the other end side tubular portion 461 is the same as the heat transfer distance between the weld joint and the braze joint. It contributes to securing.
  • the intermediate cylindrical portion 462 is an annular convex portion that protrudes radially inward of the one end side cylindrical portion 460 and the other end side cylindrical portion 461 in the tube support member 406. According to this configuration, the heat of the welded joint is delayed from being transmitted to the intermediate cylindrical portion 462, and the tube support member 406 presses the tank 4, the tank 5, the shell main body 2 and the tube assembly 3 from the outside. It can be combined with these in a supported manner. For this reason, since a force acts on the tube support member 406 radially outward from the tank 4, the tank 5, the shell main body 2 and the plurality of tubes 30, the tube support by utilizing the acting force in the same direction from each member The bonding force of the member 406 can be secured.
  • the radial thickness dimension of the intermediate cylindrical portion 462 is twice or more the radial thickness dimension of the one end side cylindrical portion 460. According to this configuration, the heat capacity of the intermediate cylindrical portion 562 can be further increased, which can contribute to suppressing the thermal influence exerted on the brazed joint.
  • the shape of the tube support member 506 is different from the EGR cooler 1 of the sixth embodiment in the EGR cooler 1 of the seventh embodiment.
  • the tube support member 506 has a longitudinal cross section in which the radial thickness dimension of the intermediate tubular portion 562 is larger than the radial thickness dimension of the one end side tubular portion 560 and the other end side tubular portion 561 It is a shape.
  • the tube support member 506 has a block-like longitudinal cross-sectional shape whose radial thickness dimension is thicker than the plate thickness of each of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the thickness dimension based on the dimension difference in the radial direction of the outer peripheral surface of the one end side cylindrical portion 560 with the inner peripheral surface is larger than the thickness of each of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the thickness dimension based on the difference in dimension in the radial direction of the outer peripheral surface of the other end side cylindrical portion 561 with the inner peripheral surface is larger than the thickness of each of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the thickness dimension of the one end side tubular portion 560 and the thickness dimension of the other end side tubular portion 561 are preferably twice or more the thickness dimensions of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the thickness dimension based on the radial dimension difference of the outer circumferential surface of the intermediate cylindrical portion 562 with the inner circumferential surface is larger than the thickness dimension of the one end side cylindrical portion 560 and the thickness dimension of the other end side cylindrical portion 561.
  • the thickness dimension of the intermediate tubular portion 562 is preferably twice or more the thickness dimension of the one end side tubular portion 560 or the thickness dimension of the other end side tubular portion 561.
  • the downstream end portion 42 of the tank 4 and the upstream end portion 52 of the tank 5 and the one end side cylindrical portion 560 are joined by welding.
  • the distal end portion 22 and the other end side cylindrical portion 561 of the shell main body 2 are joined by brazing in a state where the inner peripheral surface of the distal end portion 22 and the outer peripheral surface of the other end side cylindrical portion 561 are in contact .
  • the tube support member 506 has a block-like longitudinal cross-sectional shape that is thicker than the plate thickness of each of the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the intermediate cylindrical portion 562 is provided to be located radially inward of the one end side cylindrical portion 560 and the other end side cylindrical portion 561.
  • the joint portions with the other members in each of the one end side cylindrical portion 560, the intermediate cylindrical portion 562 and the other end side cylindrical portion 561 are provided at intervals in the axial direction.
  • the tube support member 506 is a cross-sectional block-like member having a larger heat capacity per unit length in the axial direction than the tube 30, the tanks 4 and 5, and the shell main body 2.
  • the heat of the welded joint is less likely to be transmitted to the brazed joint of the intermediate cylindrical portion 562, which contributes to suppressing the thermal effect on the brazed joint. Furthermore, since the welded joint of one end side cylindrical portion 560 and the brazed joint of intermediate cylindrical portion 562 are provided at intervals in the axial direction, the transmission between the welded joint and the brazed joint is It contributes to securing the heat distance.
  • the axial distance between the weld joint of the one end side tubular portion 560 and the brazed joint portion of the other end side tubular portion 561 is the same as the heat transfer distance between the weld joint and the braze joint. It contributes to securing.
  • the intermediate cylindrical portion 562 is a portion to be brazed in a state where the intermediate cylindrical portion 562 is in contact with the outer peripheral portion of the tube 30 on the inner peripheral surface.
  • the one end side cylindrical portion 560 is a portion to be welded and joined in a state of being in contact with the tanks 4 and 5 on the outer peripheral surface.
  • the other end side tubular portion 561 is a portion to be brazed and joined in a state in contact with the shell main body 2 on the outer peripheral surface.
  • the radial thickness dimension of the intermediate cylindrical portion 562 is twice or more the radial thickness dimension of the one end side cylindrical portion 560. According to this configuration, it is possible to further increase the radial distance between the weld joint of the one end side cylindrical portion 560 and the brazed joint of the intermediate cylindrical portion 562, and the thermal effect on the brazed joint Can contribute to reducing
  • the shape of the tube support member 606 is different from the EGR cooler 1 of the seventh embodiment in the EGR cooler 1 of the eighth embodiment.
  • the tube support member 606 has a groove on one end side recessed from the end surface on the one end side and a groove on the other end side recessed from the end surface on the other end side to the one end. Is provided.
  • the groove on the one end side and the groove on the other end are annularly provided in the tube support member 606.
  • the downstream end portion 42 of the tank 4 and the upstream end portion 52 of the tank 5 are fitted in the groove portion on one end side, and the one end side cylindrical portion 660 forms a groove portion on one end side.
  • the front end portion 22 of the shell main body 2 is fitted in the groove on the other end side, and the other end side cylindrical portion 661 forms a groove on the other end side.
  • the downstream end portion 42 and the upstream end portion 52 in a state of being fitted in the groove portion on one end side are joined by welding to the one end side cylindrical portion 660.
  • the distal end portion 22 in a state of being fitted in the groove on the other end side is brazed and joined to the other end side cylindrical portion 661.
  • the intermediate cylindrical portion 662 is a portion to be brazed in contact with the outer peripheral portion of the tube 30 on the inner peripheral surface.
  • the one end side cylindrical portion 660 is a portion that forms a groove recessed from the end surface on one end side of the tube support member 606 toward the other end, and is welded to the tanks 4 and 5 fitted in the groove.
  • the other end side cylindrical portion 661 is a portion that forms a groove recessed from the end face on the other end side of the tube support member 606 toward one end side, and is brazed and joined to the shell main body 2 fitted in this groove .
  • the tube support member 606 has a heat capacity portion capable of storing heat on both sides of the radially outer side and the radially inner side with respect to the weld joint in the one end side cylindrical portion 660.
  • the heat of the welded joint can be made less likely to be transmitted to the brazed joint of the intermediate cylindrical portion 662, which contributes to suppressing the thermal influence exerted on the brazed joint.
  • the ninth embodiment The heat exchanger of the ninth embodiment will be described with reference to FIG.
  • the configurations, operations, and effects not particularly described in the ninth embodiment are the same as those of the first embodiment, and only differences from the first embodiment and the seventh embodiment will be described below.
  • the EGR cooler 1 of the ninth embodiment differs from the EGR cooler 1 of the first embodiment in the shape of the tube support member 706 and the end shapes of the tanks 4 and 5 joined to the one end side cylindrical portion 760. ing.
  • the tube support member 706 is a cylindrical body in which the one end side cylindrical portion 760, the intermediate cylindrical portion 762 and the other end side cylindrical portion 761 are integrally formed.
  • the tube support member 706 includes an end side cylindrical portion 760 joined to the tanks 4 and 5 on one end side in the axial direction of the cylindrical body.
  • the one end side cylindrical portion 760 is an annular plate portion extending in a direction intersecting the axial direction.
  • the one end side cylindrical portion 760 is shaped to extend along the downstream end portion 142 of the tank 4 to be welded and the upstream end portion 152 of the tank 5.
  • the one end side cylindrical portion 760 is an annular portion extending in a direction orthogonal to the axial direction, as with the downstream end portion 142 and the upstream end portion 152.
  • the one end side cylindrical portion 760 is a portion having a larger diameter than the intermediate cylindrical portion 762.
  • the other end side cylindrical portion 761 corresponds to the other end side cylindrical portion 61 of the first embodiment.
  • the disclosure of this specification is not limited to the illustrated embodiments.
  • the disclosure includes the illustrated embodiments and variations based on them by those skilled in the art.
  • the disclosure is not limited to the combination of parts and elements shown in the embodiments, and can be implemented with various modifications.
  • the disclosure can be implemented in various combinations.
  • the disclosure can have additional parts that can be added to the embodiments.
  • the disclosure includes the parts and components of the embodiments omitted.
  • the disclosure includes replacements of parts, components, or combinations between one embodiment and another embodiment.
  • the disclosed technical scope is not limited to the description of the embodiments.
  • the first fluid is an exhaust gas
  • the second fluid is a cooling water, but is not limited to this form.
  • the first fluid may be a fluid cooler than the second fluid.
  • the heat exchanger disclosed in the above-described embodiment is configured to include the tube assembly 3 integrally stacked in a state in which the adjacent tubes 30 are in contact with each other, but the heat exchanger of the present disclosure takes this form. It is not limited.
  • the tube assembly 3 may be stacked in a state where adjacent tubes 30 are in contact with each other at a part such as an end.
  • the tube 30 shall be formed by overlapping two tube plates, it may be made to be formed not only from this but from an integral tube member.
  • the cross-sectional shape of the tube 30 is not limited to the flat rectangular shape, and may be another shape such as a round shape.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

La présente invention concerne un refroidisseur de gaz d'échappement qui est pourvu de : réservoirs (4, 5) dans lesquels ou depuis lesquels un gaz d'échappement s'écoule ; une pluralité de tubes (30) à travers lesquels un gaz d'échappement s'écoule ; un élément de support de tube (6) assemblé à et soutenant la pluralité de tubes ; et un corps d'enveloppe (2) assemblé à l'élément de support de tube. L'élément de support de tube est un corps cylindrique comprenant : une section cylindrique (60) sur un côté d'extrémité, une section cylindrique (61) sur l'autre côté d'extrémité, et une section cylindrique intermédiaire (62) qui a un diamètre inférieur à la section cylindrique sur un côté d'extrémité et ayant une longueur prédéterminée dans une direction axiale entre la section cylindrique sur un côté d'extrémité et la section cylindrique sur l'autre côté d'extrémité. Les réservoirs et la section cylindrique sur un côté d'extrémité sont assemblés par soudage. Le corps d'enveloppe et la section cylindrique sur l'autre côté d'extrémité sont assemblés par brasage. Les tubes sont soutenus par l'élément de support de tube tout en étant assemblés par brasage, les périphéries externes des tubes étant en contact avec la surface interne de la section cylindrique intermédiaire. En conséquence, une influence thermique causée par l'assemblage par soudage entre les réservoirs et l'élément de support de tube peut être supprimée et une longueur axiale peut être limitée.
PCT/JP2018/024344 2017-08-09 2018-06-27 Échangeur de chaleur Ceased WO2019031090A1 (fr)

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US16/781,637 US20200173726A1 (en) 2017-08-09 2020-02-04 Heat exchanger

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JP2017153985A JP6904154B2 (ja) 2017-08-09 2017-08-09 熱交換器
JP2017-153985 2017-08-09

Related Child Applications (1)

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US10823509B2 (en) * 2016-04-20 2020-11-03 Denso Corporation Heat exchanger and manufacturing method thereof

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5197050A (fr) * 1975-02-24 1976-08-26
JPS6446681U (fr) * 1987-09-11 1989-03-22
JPH11237192A (ja) * 1998-02-24 1999-08-31 Tennex Corp 内燃機関のｅｇｒガスクーラ
JP2002156196A (ja) * 2000-11-17 2002-05-31 Usui Internatl Ind Co Ltd 多管式熱交換器
JP2007077839A (ja) * 2005-09-12 2007-03-29 Usui Kokusai Sangyo Kaisha Ltd Ｅｇｒガス冷却装置
EP3153806A1 (fr) * 2012-05-15 2017-04-12 Zhejiang Yinlun Machinery Co., Ltd. Structure d'entrée de gaz d'échappement d'un refroidisseur de recirculation de gaz d'échappement

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4926892B2 (ja) * 2007-08-30 2012-05-09 株式会社ティラド 熱交換器のフランジ接続構造
JP5842598B2 (ja) * 2011-12-22 2016-01-13 マツダ株式会社 熱交換器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5197050A (fr) * 1975-02-24 1976-08-26
JPS6446681U (fr) * 1987-09-11 1989-03-22
JPH11237192A (ja) * 1998-02-24 1999-08-31 Tennex Corp 内燃機関のｅｇｒガスクーラ
JP2002156196A (ja) * 2000-11-17 2002-05-31 Usui Internatl Ind Co Ltd 多管式熱交換器
JP2007077839A (ja) * 2005-09-12 2007-03-29 Usui Kokusai Sangyo Kaisha Ltd Ｅｇｒガス冷却装置
EP3153806A1 (fr) * 2012-05-15 2017-04-12 Zhejiang Yinlun Machinery Co., Ltd. Structure d'entrée de gaz d'échappement d'un refroidisseur de recirculation de gaz d'échappement

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US20200173726A1 (en) 2020-06-04
JP6904154B2 (ja) 2021-07-14
JP2019032127A (ja) 2019-02-28

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