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WO2018123334A1 - Refroidisseur intermédiaire - Google Patents

Refroidisseur intermédiaire Download PDF

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Publication number
WO2018123334A1
WO2018123334A1 PCT/JP2017/041352 JP2017041352W WO2018123334A1 WO 2018123334 A1 WO2018123334 A1 WO 2018123334A1 JP 2017041352 W JP2017041352 W JP 2017041352W WO 2018123334 A1 WO2018123334 A1 WO 2018123334A1
Authority
WO
WIPO (PCT)
Prior art keywords
communication portion
flow path
outlet
inlet
duct
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/JP2017/041352
Other languages
English (en)
Japanese (ja)
Inventor
和貴 鈴木
幸貴 西山
彰洋 大井
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 Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Priority to DE112017006546.1T priority Critical patent/DE112017006546T5/de
Priority to CN201780079228.6A priority patent/CN110100143B/zh
Publication of WO2018123334A1 publication Critical patent/WO2018123334A1/fr
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
    • 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
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
    • F02B29/0462—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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/0056—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0248—Arrangements for sealing connectors to header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0082—Charged air coolers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This disclosure relates to intercoolers.
  • an intercooler that cools compressed air that is compressed by a supercharger and supplied to an internal combustion engine is known.
  • the intercooler described in Patent Document 1 cools the compressed air by heat exchange between the cooling liquid flowing through the two cooling systems and the compressed air.
  • This intercooler has a plurality of cooling plates stacked inside a duct through which compressed air flows.
  • the cooling plate has a first channel through which the first coolant of the first cooling system flows and a second channel through which the second coolant of the second cooling system flows.
  • An outer fin that promotes heat exchange between the compressed air and the coolant is provided between the plurality of stacked cooling plates.
  • the first flow paths and the second flow paths included in the plurality of cooling plates are respectively communicated in the stacking direction by a plurality of communication portions.
  • the inlet pipe and the outlet pipe of each of the first cooling system and the second cooling system communicate with the end portions in the stacking direction of the plurality of communication parts.
  • the coolant supplied from the inlet pipe flows through the flow paths of the plurality of cooling plates via the communication part communicating therewith, and via the other communication part. Outflow from the outlet pipe.
  • the coolant flowing through the first flow path and the second flow path of the plurality of cooling plates and the compressed air flowing between the plurality of cooling plates exchange heat through the outer fins. Thereby, the intercooler can cool the compressed air.
  • the intercooler described in Patent Document 1 has a direction that intersects the direction in which the first flow path and the second flow path are aligned among the outer walls of the duct that is located in one of the stacking directions of the plurality of cooling plates.
  • An inlet pipe and an outlet pipe are respectively provided on both sides.
  • this intercooler has both sides of the outer wall of the duct in a direction intersecting with the stacking direction of the plurality of cooling plates and in a direction intersecting with the direction in which the first flow path and the second flow path are aligned.
  • An inlet pipe and an outlet pipe are respectively provided at the parts.
  • the communication portions communicate with the inlet pipe and the outlet pipe, respectively.
  • a communication portion is provided in each of the portions on both sides of the direction intersecting the stacking direction of the plurality of cooling plates and the direction intersecting the direction in which the first flow path and the second flow path are arranged. Will be. Therefore, this intercooler has a problem that the space in which the outer fin can be provided in the duct is reduced by the communication portion, and the efficiency of heat exchange between the compressed air and the coolant is lowered.
  • the width of the first flow path becomes more than necessary.
  • the width of the second flow path is smaller than that of the communication portion when the width of the first flow path and the width of the second flow path are set to an appropriate balance in design. Therefore, there arises a problem that the size of the intercooler is increased in the direction in which the first flow path and the second flow path are arranged, that is, in the direction in which the inlet pipe and the outlet pipe are arranged.
  • This disclosure aims to provide an intercooler capable of improving heat exchange efficiency and reducing the size of the physique.
  • the intercooler performs heat exchange between the compressed air compressed by the supercharger and the coolant flowing through each of the plurality of cooling systems, A duct having an air passage through which compressed air flows; A plurality of cooling plates having a first flow path through which the first cooling liquid of the first cooling system flows and a second flow path through which the second cooling liquid of the second cooling system flows and are stacked inside the duct
  • An outer fin that is provided between the plurality of cooling plates and promotes heat exchange between the compressed air, the first coolant, and the second coolant;
  • a first inlet communication portion and a first outlet communication portion that communicate the first flow paths of the plurality of cooling plates in the stacking direction;
  • a second inlet communication part and a second outlet communication part for communicating the second flow paths of the plurality of cooling plates in the stacking direction;
  • a first inlet pipe communicating with an end portion in the stacking direction of the first inlet communication portions;
  • a first outlet pipe communicating with an end portion in the stacking direction of the first outlet communicating portions;
  • the outer fin is provided in the duct. It is possible to increase the space that can be provided. Therefore, this intercooler can increase the heat exchange efficiency between the compressed air and the coolant.
  • the inner dimensions of the first inlet communication section and the first outlet communication section are made smaller than the inner dimensions of the second inlet communication section and the second outlet communication section.
  • this intercooler can be downsized in the direction in which the first flow path and the second flow path are aligned.
  • FIG. 6 is a partial cross-sectional view taken along line IX-IX in FIGS. 3 and 5.
  • FIG. 6 is a partial cross-sectional view taken along line XX in FIGS. 3 and 5. It is a disassembled perspective view of an intercooler. It is a top view of the cooling plate with which the intercooler of a 2nd embodiment is provided. It is a top view of the cooling plate with which the intercooler of a 3rd embodiment is provided. It is the figure which contrasted the intercooler of 1st Embodiment, and the intercooler of a 1st comparative example. It is the figure which contrasted the cooling plate of 1st Embodiment, and the cooling plate of a 2nd comparative example.
  • the intercooler according to the present embodiment is mounted on the intake system of the internal combustion engine, and is supplied to the internal combustion engine by exchanging heat between the compressed air compressed by the supercharger and the coolant flowing through each of the plurality of cooling systems.
  • This is a water-cooled intercooler that cools compressed air.
  • the intercooler 1 is connected to a first cooling system 10 and a second cooling system 20. Therefore, the first coolant that circulates through the first cooling system 10 and the second coolant that circulates through the second cooling system 20 flow through the intercooler 1.
  • the first coolant flowing through the first cooling system 10 is coolant for cooling the internal combustion engine. Examples of the first coolant and the second coolant include antifreeze containing ethylene glycol or water.
  • an internal combustion engine 11, a main pump 12, a main radiator 13, a heater core 14, the intercooler 1 and the like are connected by a pipe 15.
  • the main pump 12 circulates the first coolant through the pipe 15 in each component of the first cooling system 10.
  • the main radiator 13 is a radiator that radiates heat of the first coolant by heat exchange with outside air.
  • the heater core 14 is a heat exchanger that heats the conditioned air in order to perform air conditioning in the vehicle interior using the heat of the first coolant.
  • the first cooling system 10 is configured to flow the first cooling liquid around the main radiator 13 and the like when the first cooling liquid becomes low temperature (for example, 80 ° C. or lower).
  • the bypass passage and an opening / closing valve for opening and closing the bypass passage are provided.
  • the temperature of the first coolant is adjusted to a range of about 80 ° C. to 100 ° C. by the bypass passage and the on-off valve.
  • a sub pump 21, a sub radiator 22, an intercooler 1, and the like are connected by a pipe 23.
  • the sub-pump 21 circulates the second coolant through the piping 23 in each component of the second cooling system 20.
  • the sub radiator 22 is a radiator that radiates heat of the second coolant by heat exchange with outside air.
  • the second cooling system 20 is not connected to the internal combustion engine. Therefore, the 2nd cooling fluid which flows through the 2nd cooling system 20 is lower temperature (for example, about 40 ° C) than the 1st cooling fluid.
  • the intercooler 1 is connected to the first cooling system 10 and the second cooling system 20 to adjust the compressed air to a target temperature using the first and second cooling liquids having different temperatures. This makes it possible to improve the charging efficiency of the intake air of the internal combustion engine 11.
  • the intercooler 1 is a so-called drone cup type heat exchanger in which a plurality of cooling plates 40 and the like are laminated inside a substantially rectangular tube-shaped duct 30.
  • the component that becomes the core of the intercooler 1 is formed of, for example, a clad material in which a brazing material is clad on the surface of aluminum.
  • the component parts that become the core of the intercooler 1 are heated by applying a flux to the surface of the clad material, whereby the respective component parts are joined to each other by brazing.
  • the duct 30 has a first duct plate 31 and a second duct plate 32 provided so as to face the first duct plate 31 joined in a cylindrical shape, thereby forming an air passage inside thereof.
  • the first duct plate 31 includes a rectangular top plate 33 and two side plates 34 extending substantially vertically from both sides of the top plate 33.
  • the second duct plate 32 includes a rectangular bottom plate 35 and two side plates 36 extending substantially vertically from both sides of the bottom plate 35.
  • the first duct plate 31 and the second duct plate 32 are joined in a state where a part of the side plate 36 of the second duct plate 32 overlaps the inside of the side plate 34 of the first duct plate 31.
  • Two rectangular frame-shaped caulking plates 37 are joined to one opening and the other opening in the air flow direction of the air passage formed inside the first duct plate 31 and the second duct plate 32, respectively.
  • Two tanks (not shown) are caulked and fixed to the two caulking plates 37 via packing (not shown).
  • the two tanks are connected to an intake passage (not shown) between the supercharger and the internal combustion engine 11. Therefore, the compressed air compressed by the supercharger flows from one tank through the air passage formed inside the duct 30 and is supplied to the internal combustion engine 11 from the intake passage through the other tank.
  • a plurality of cooling plates 40, a plurality of spacer plates 55, a plurality of outer fins 57, and the like are stacked inside the duct 30.
  • the cooling plate 40 includes a first cooling plate 41 and a second cooling plate 42 that are pressed into a predetermined shape.
  • the cooling plate 40 may be configured by folding a single plate pressed into a predetermined shape at the center and superimposing them.
  • a first flow path 43 and a second flow path 44 are formed between the first cooling plate 41 and the second cooling plate 42.
  • the first coolant of the first cooling system 10 flows through the first flow path 43
  • the second coolant of the second cooling system 20 flows through the second flow path 44.
  • Both the first flow path 43 and the second flow path 44 are formed so that the coolant flows in a U shape.
  • the width of the first flow path 43 is smaller than the width of the second flow path 44.
  • the first flow path 43 through which the first coolant, which is the cooling water of the internal combustion engine, circulates is arranged upstream in the flow direction of the compressed air in the air passage inside the duct 30, and the second flow path 44 is the compressed air. It is arrange
  • the 1st cooling plate 41 and the 2nd cooling plate 42 have the holes 45 and 46 respectively connected to the edge part of the 1st flow path 43 and the 2nd flow path 44 which were formed in the U-shape. .
  • the holes 45 provided in the end portions of the first flow path 43 form the first inlet communication portion 47 and the first outlet communication portion 48, respectively.
  • the holes 46 provided in the end portions of the second flow path 44 form the second inlet communication portion 49 and the second outlet communication portion 50, respectively.
  • the first cooling plate 41 and the second cooling plate 42 have a plurality of claw-shaped burrings 51 and 52 around the holes 45 and 46.
  • the burring 51 of the first cooling plate 41 and the burring 52 of the second cooling plate 42 are provided at different positions in the circumferential direction or radial direction of the hole so as not to interfere with each other.
  • a plate-like spacer plate 55 is provided between the cooling plate 40 and the cooling plate 40 stacked inside the duct 30.
  • the spacer plate 55 has a hole 56 that communicates in the thickness direction at a position corresponding to each of the hole of the first cooling plate 41 and the hole of the second cooling plate 42.
  • the burring 51 of the first cooling plate 41 and the burring 52 of the second cooling plate 42 can be inserted into the holes 56 of the spacer plate 55.
  • the first cooling plate 41, the second cooling plate 42, and the spacer plate 55 are fixed by brazing. Thereby, the 1st entrance communication part 47, the 1st exit communication part 48, the 2nd entrance communication part 49, and the 2nd exit communication part 50 are formed.
  • the first inlet communication portion 47 and the first outlet communication portion 48 communicate the first flow paths 43 included in the plurality of cooling plates 40 in the stacking direction. Further, the second inlet communication portion 49 and the second outlet communication portion 50 communicate the second flow paths 44 included in the plurality of cooling plates 40 in the stacking direction.
  • the second cooling plate 42 has a cup portion 53 that is recessed outside the first flow path 43 and the second flow path 44 around the hole 46.
  • a space is formed between the plurality of cooling plates 40 stacked with the spacer plate 55 interposed therebetween.
  • Outer fins 57 are provided in the space.
  • the sum of the depth of the cup portion 53 and the thickness of the spacer plate 55 is a height at which the outer fin 57 can be provided.
  • the spacer plate 55 described above has the first inlet communication portion 47, the first outlet communication portion 48, the second inlet communication portion 49, and the second outlet communication portion in the direction in which the first flow path 43 and the second flow path 44 are arranged. It is formed in a plate shape continuous with the portion where 50 is formed. Therefore, as shown in FIG.
  • the outer fin 57 is provided in a space FS formed between the inner wall of the duct 30 located on the side opposite to the spacer plate 55 and the spacer plate 55.
  • the outer fin 57 promotes heat exchange between the compressed air, the first coolant, and the second coolant.
  • the stacking direction of the plurality of cooling plates 40 is simply referred to as stacking direction H.
  • a direction in which the first flow path 43 and the second flow path 44 are arranged is referred to as a duct width direction W.
  • a direction that intersects the stacking direction H and intersects the duct width direction W is referred to as a duct length direction L.
  • the first inlet communication portion 47, the first outlet communication portion 48, the second inlet communication portion 49, and the second outlet communication portion 50 are collectively referred to as four communication portions 47 to 50.
  • the four communication portions 47 to 50 are provided at a site on one side in the duct length direction L.
  • this intercooler 1 can provide the outer fin 57 inside the duct 30.
  • FIG. It is possible to increase the space FS.
  • the portion on the outer fin 57 side is in a position aligned in the duct length direction L.
  • the portion on the outer fin 57 side is the portion of the inner walls of the second inlet communication portion 49 and the second outlet communication portion 50 on the outer fin 57 side.
  • the outer fin 57 may be located on the opposite side.
  • the outer fin 57 side portion of the inner walls of the first inlet communication portion 47 and the first outlet communication portion 48 is the outer fin 57 side portion of the inner walls of the second inlet communication portion 49 and the second outlet communication portion 50.
  • the intercooler 1 can increase the space FS in which the outer fins 57 can be provided inside the duct 30.
  • the inner dimension D1 of the first inlet communication part 47 and the first outlet communication part 48 is smaller than the inner dimension D2 of the second inlet communication part 49 and the second outlet communication part 50.
  • the first inlet communication portion 47 and the first outlet communication portion 48 have an elongated hole shape in which the inner dimension D1 in the duct width direction W is smaller than the inner dimension D3 in the duct length direction L.
  • the second inlet communication portion 49 and the second outlet communication portion 50 are circular. Accordingly, the width A of the first flow path 43 can be made smaller than the inner dimension D2 of the second inlet communication portion 49 and the second outlet communication portion 50. In addition, the interval between the adjacent first flow paths 43 can be reduced.
  • the first inlet pipe 61 communicates with one end of the first inlet communication portion 47 in the stacking direction H.
  • the first inlet pipe 61 is provided on the top plate 33 of the first duct plate 31.
  • the first outlet pipe 62 communicates with the other end of the first outlet communicating portion 48 in the stacking direction H.
  • the first outlet pipe 62 is provided on the bottom plate 35 of the second duct plate 32. Therefore, the first inlet pipe 61 is provided on one outer wall of the duct 30 in the stacking direction H, and the first outlet pipe 62 is provided on the other outer wall of the duct 30 in the stacking direction H. Further, as shown in FIG. 3, the first inlet pipe 61 and the first outlet pipe 62 are disposed so as to overlap each other when viewed from the stacking direction H.
  • the second inlet pipe 63 communicates with one end of the second inlet communication portion 49 in the stacking direction H.
  • the second outlet pipe 64 communicates with one end of the second outlet communication portion 50 in the stacking direction H.
  • the second inlet pipe 63 and the second outlet pipe 64 are provided on the top plate 33 of the first duct plate 31.
  • the first inlet pipe 61, the first outlet pipe 62, the second inlet pipe 63, and the second outlet pipe 64 are collectively referred to as four pipes 61 to 64.
  • the four pipes 61 to 64 are provided at a site on one side in the duct length direction L on the outer wall of the duct 30, similarly to the four communication portions 47 to 50.
  • the first inlet pipe 61, the second inlet pipe 63, and the second outlet pipe 64 are provided on one outer wall of the duct 30 in the stacking direction H
  • a first outlet pipe 62 is provided on the other outer wall of the duct 30 in the stacking direction H.
  • the four pipes 61 to 64 which pipe is provided on the outer wall of one or the other duct 30 in the stacking direction H depends on the mounting space of the vehicle on which the intercooler 1 is mounted or the vehicle-side piping 60. It can be set arbitrarily according to the configuration of That is, in the present embodiment, at least one of the four pipes 61 to 64 is provided on one outer wall of the duct 30 in the stacking direction H, and at least one pipe excluding the pipe is stacked in the duct 30. It can be provided on the other outer wall in the direction H.
  • the vehicle-side piping 60 is connected to each of the four pipes 61 to 64.
  • the vehicle-side piping 60 constituting the first cooling system 10 is connected to the outer periphery of the first inlet pipe 61 and the first outlet pipe 62.
  • a vehicle-side pipe 60 constituting the second cooling system 20 is connected to the outer circumferences of the second inlet pipe 63 and the second outlet pipe 64. 3 to 5, the vehicle-side piping 60 connected to the outer circumferences of the four pipes 61 to 64 is indicated by a one-dot chain line.
  • the four pipes 61 to 64 are provided at a predetermined distance or more so that the vehicle side pipes 60 do not interfere with each other.
  • the first inlet pipe 61 is provided on one outer wall of the duct 30 in the stacking direction H
  • the first outlet pipe 62 is provided on the other outer wall of the duct 30 in the stacking direction H.
  • the four pipes 61 to 64 are arranged separately on the top and bottom of the duct 30 so that a sufficient space is formed around them, so that each of the four pipes interferes with other pipes. In addition, it is possible to arbitrarily change the direction setting of the four pipes 61 to 64. Therefore, even if the vehicle-side piping 60 extends from any direction, it is possible to change the arrangement and orientation settings of the four pipes 61 to 64 according to the vehicle-side piping 60.
  • the first inlet pipe 61 and the first outlet pipe 62 are flattened to reduce the amount of protrusion of the pipe in the stacking direction H from the outer wall of the duct 30. Thereby, the enlargement of the physique of the stacking direction H of the intercooler 1 is suppressed. Moreover, at the time of manufacture of the intercooler 1, a conveyance operation
  • the first inlet pipe 61 and the first outlet pipe 62 are connected to the connecting portion 65 to which the vehicle-side piping 60 can be connected, and extend from the connecting portion 65 to the outer wall of the duct 30.
  • a fixing portion 66 to be fixed is provided.
  • the fixing portion 66 is formed in a flat shape whose height in the stacking direction H is smaller than the outer diameter of the connecting portion 65.
  • the fixing portion 66 has a hole 67 in the stacking direction H.
  • the hole 67 of the fixing portion 66 included in the first inlet pipe 61 and the first inlet communication portion 47 communicate with each other.
  • FIG. 10 the first inlet pipe 61 and the first outlet pipe 62 are connected to the connecting portion 65 to which the vehicle-side piping 60 can be connected, and extend from the connecting portion 65 to the outer wall of the duct 30.
  • a fixing portion 66 to be fixed is provided.
  • the fixing portion 66 is formed in a flat shape whose height in the stacking direction H is smaller than the outer diameter of the connecting
  • a brazing plate 68 is provided between the outer wall of the duct 30 and the fixed portion 66.
  • the brazing plate 68 is formed of a clad material in which a brazing material is clad on the surface of a base material such as aluminum in order to braze the outer wall of the duct 30 and the fixing portion 66.
  • the brazing plate 68 may be omitted if a brazing material is provided on the outer wall of the duct 30 or the fixed portion 66.
  • the axial center 69 of the connecting portion 65 of the first inlet pipe 61 and the first outlet pipe 62 is located closer to the center of the duct 30 than the outer wall surface in the stacking direction H of the duct 30. . Therefore, the first inlet pipe 61 and the first outlet pipe 62 have a small protruding amount that protrudes from the outer wall of the duct 30 in the stacking direction H.
  • the four pipes 61 to 64 which one of the pipes has a flat shape is arbitrarily set according to the mounting space of the vehicle on which the intercooler 1 is mounted or the configuration of the vehicle-side piping 60. be able to. That is, in the present embodiment, at least one of the four pipes 61 to 64 can have a flat shape.
  • the first coolant circulating in the first cooling system 10 flows from the first inlet pipe 61 into the first inlet communication portion 47, and passes through the first flow path 43. After flowing, it flows out from the first outlet pipe 62 through the first outlet communication portion 48.
  • the second coolant circulating in the second cooling system 20 flows from the second inlet pipe 63 into the second inlet communication portion 49, flows through the second flow path 44, and then passes through the second outlet communication portion 50. , And flows out from the second outlet pipe 64.
  • the compressed air flowing through the air passage inside the duct 30 exchanges heat with the first coolant and the second coolant via the outer fins 57 and the cooling plate 40, and is cooled to a target temperature.
  • the compressed air thus cooled is supplied to the internal combustion engine 11.
  • FIG. 14A is a plan view of the intercooler 1 described in the first embodiment
  • FIG. 14B is a plan view of the intercooler 101 of the first comparative example.
  • the first inlet pipe 61, the second inlet pipe 63, and the second outlet pipe 64 are in the duct length direction L of the outer wall of the duct 30. It is provided on one side.
  • the first outlet pipe 62 is provided on the other side of the outer wall of the duct 30 in the duct length direction L.
  • the intercooler 101 of the first comparative example has a problem that the space FS in which the outer fins 57 can be provided inside the duct 30 is reduced, and the heat exchange efficiency between the compressed air and the coolant is lowered.
  • FIG. 15A is a plan view showing a part of the cooling plate 40 described in the first embodiment
  • FIG. 15B shows a part of the cooling plate 400 of the second comparative example. It is a top view.
  • the inner dimensions D4 of the four communicating portions 47 to 50 are all the same.
  • the four communication portions 47 to 50 are all circular.
  • the inner dimension D3 of the four communicating portions 47 to 50 of the first embodiment and the inner dimension D4 of the four communicating portions 47 to 50 of the second comparative example are the same.
  • the width A of the first flow path 43 of the first embodiment and the width A of the first flow path 43 of the second comparative example are the same.
  • the width B of the second flow path 44 of the first embodiment and the width B of the second flow path 44 of the second comparative example are the same. Therefore, in the second comparative example, the distance FD1 between the first flow path 43 and the first flow path 43 formed adjacent to each other in the U shape is the distance between the first inlet communication portion 47 and the first outlet communication portion 48. Limited by FD2. Therefore, in the second comparative example, the interval FD1 between the first flow path 43 and the first flow path 43 that are formed in a U shape and are adjacent to each other is the first flow path 43 and the first flow path 43 of the first embodiment. Is wider than the distance FD3.
  • the space outside the first flow path 43 including the interval FD1 between the first flow path 43 and the first flow path 43 is a dead space where the cooling efficiency of compressed air is low because the first coolant does not flow. .
  • the intercooler of the second comparative example has a problem that the physique in the duct width direction W increases due to the dead space outside the first flow path 43.
  • the intercooler 1 of the first embodiment has the following operational effects.
  • the four communication portions 47 to 50 are provided on one side of the duct length direction L. According to this, it is possible to enlarge the space FS in which the outer fins 57 can be provided inside the duct 30. Therefore, the heat exchange efficiency between the compressed air and the coolant is improved. Therefore, the intercooler 1 can adjust the compressed air to a target temperature and improve the charging efficiency of the intake air of the internal combustion engine 11.
  • the inner dimension D1 of the first inlet communication part 47 and the first outlet communication part 48 is the inner dimension of the second inlet communication part 49 and the second outlet communication part 50. It is smaller than D2. According to this, the width A of the first flow path 43 can be made smaller than the inner dimension D2 of the second inlet communication portion 49 and the second outlet communication portion 50. Furthermore, the interval FD3 between the adjacent first flow paths 43 can be reduced. Therefore, this intercooler 1 can reduce the physique in the duct width direction W.
  • the portions on the outer fin 57 side of the inner walls of the first inlet communication portion 47 and the first outlet communication portion 48 are the inner walls of the second inlet communication portion 49 and the second outlet communication portion 50. Of these, it is in a position aligned with the portion on the outer fin 57 side.
  • a portion of the inner wall of the first inlet communication portion 47 and the first outlet communication portion 48 on the outer fin 57 side is a portion of the inner wall of the second inlet communication portion 49 and the second outlet communication portion 50 on the outer fin 57 side. On the other hand, it is located on the opposite side to the outer fin 57.
  • the part of the inner wall of the first inlet communication part 47 and the first outlet communication part 48 on the outer fin 57 side is the outer fin 57 of the inner wall of the second inlet communication part 49 and the second outlet communication part 50. It is not provided on the outer fin 57 side than the side portion. Therefore, it is possible to prevent the space FS where the outer fins 57 are provided in the air passage inside the duct 30 from being reduced. Therefore, the intercooler 1 can increase the heat exchange efficiency between the compressed air and the coolant.
  • the width A of the first flow path 43 is smaller than the width B of the second flow path 44 in the duct width direction W, and the inside of the first inlet communication section 47 and the first outlet communication section 48
  • the dimension D1 is smaller than the width A of the first flow path 43.
  • this intercooler 1 can reduce the physique in the duct width direction W.
  • the first inlet pipe 61 is provided on one outer wall of the duct 30 in the stacking direction H, and the first outlet pipe 62 is formed on the other outer wall of the duct 30 in the stacking direction H. Is provided. Further, when viewed from the stacking direction H, the first inlet pipe 61 and the first outlet pipe 62 are disposed so as to overlap each other.
  • this intercooler 1 can reduce the physique in the duct width direction W.
  • the intercooler 1 includes the spacer plate 55 at a site where the four communication portions 47 to 50 are formed.
  • the outer fins 57 are provided in a space FS formed between the inner wall of the duct 30 located on the opposite side of the spacer plate 55 and the spacer plate 55.
  • the intercooler 1 can prevent the coolant from leaking from the communication portion.
  • the first inlet communication portion 47 and the first outlet communication portion 48 have an ellipse whose inner dimension D1 in the duct width direction W is smaller than the inner dimension D3 in the duct length direction L. It has a shape.
  • the second inlet communication portion 49 and the second outlet communication portion 50 are circular. In the duct width direction W, the inner dimension D1 of the first inlet communication part 47 and the first outlet communication part 48 is smaller than the inner dimension D2 of the second inlet communication part 49 and the second outlet communication part 50.
  • a portion of the inner wall on the outer fin 57 side is in a position aligned in the duct length direction L.
  • the second embodiment can also exhibit the same effects as the first embodiment.
  • a third embodiment will be described.
  • the third embodiment is obtained by changing the configuration of the communication unit with respect to the first and second embodiments, and is otherwise the same as the first and second embodiments, and thus the first and second embodiments. Only different parts will be described.
  • the first inlet communication portion 47 and the first outlet communication portion 48 are circular.
  • the inner dimension D5 of the first inlet communication part 47 and the first outlet communication part 48 is smaller than the inner dimension D2 of the second inlet communication part 49 and the second outlet communication part 50.
  • the outer fin 57 side portion of the inner walls of the first inlet communication portion 47 and the first outlet communication portion 48 is the outer fin of the inner walls of the second inlet communication portion 49 and the second outlet communication portion 50. It is located on the opposite side to the outer fin 57 with respect to the portion on the 57 side. This is indicated by broken lines M1 and M2 in FIG. That is, the outer fin 57 side portion of the inner wall of the first inlet communication portion 47 and the first outlet communication portion 48 is the outer fin 57 side portion of the inner wall of the second inlet communication portion 49 and the second outlet communication portion 50. On the other hand, it is provided at a position away from the outer fin 57. Also with this configuration, the space FS in which the outer fins 57 can be provided inside the duct 30 can be increased.
  • 3rd Embodiment can also have the same effect as 1st and 2nd embodiment.
  • the shape of the communicating portion is a long hole shape, an elliptical shape, or a small circular shape.
  • the shape of the communicating portion can be arbitrarily set, such as a polygonal shape.
  • the first inlet pipe and the first outlet pipe have a flat shape
  • the second inlet pipe and the second outlet pipe have a bent shape.
  • all four pipes may have a flat shape or a bent shape according to the mounting space of the vehicle on which the intercooler is mounted or the configuration of the vehicle-side piping.
  • any one of the four pipes may have a flat shape, and the other pipes may have a bent shape.
  • all four pipes are directed in the same direction.
  • any one of the four pipes in accordance with the mounting space of the vehicle on which the intercooler is mounted or the configuration of the vehicle-side piping, any one of the four pipes has a different direction from the other pipes. You may turn to.
  • an intercooler performs heat exchange with the compressed air compressed with the supercharger, and the cooling fluid which each flows through several cooling systems.
  • the intercooler includes a duct, a plurality of cooling plates, an outer fin, a first inlet communication portion, a first outlet communication portion, a second inlet communication portion, a second outlet communication portion, a first inlet pipe, a first outlet pipe, Two inlet pipes and a second outlet pipe are provided.
  • the duct has an air passage through which compressed air flows.
  • the plurality of cooling plates have a first flow path through which the first cooling liquid of the first cooling system flows and a second flow path through which the second cooling liquid of the second cooling system flows, and are stacked in the duct.
  • the outer fin is provided between the plurality of cooling plates and promotes heat exchange between the compressed air, the first coolant, and the second coolant.
  • the first inlet communication portion and the first outlet communication portion communicate the first flow paths of the plurality of cooling plates in the stacking direction.
  • the second inlet communication portion and the second outlet communication portion communicate the second flow paths of the plurality of cooling plates in the stacking direction.
  • a 1st inlet pipe is connected to the edge part of the lamination direction among the 1st inlet communication parts.
  • the first outlet pipe communicates with an end portion in the stacking direction of the first outlet communication portions.
  • the second inlet pipe communicates with an end portion in the stacking direction of the second inlet communication portion.
  • the second outlet pipe communicates with an end portion in the stacking direction of the second outlet communication portions.
  • the first inlet communication portion, the first outlet communication portion, the second inlet communication portion, and the second outlet communication portion are in a direction intersecting the stacking direction of the plurality of cooling plates, and the first flow path and the second flow path It is provided in the site
  • the inner dimensions of the first inlet communication section and the first outlet communication section are larger than the inner dimensions of the second inlet communication section and the second outlet communication section. small.
  • the outer fin includes a first inlet communication portion, a first outlet communication portion, a second inlet communication portion, and a second outlet communication portion in a space formed between the plurality of cooling plates. It is provided in the part except for. Whether the outer fin side portion of the inner wall of the first inlet communication portion and the first outlet communication portion is in a position aligned with the outer fin side portion of the inner wall of the second inlet communication portion and the second outlet communication portion, Or it is located on the opposite side to the outer fin.
  • the outer fin side portion of the inner wall of the first inlet communication portion and the first outlet communication portion is outer than the outer fin side portion of the inner wall of the second inlet communication portion and the second outlet communication portion. It is not provided on the fin side. Therefore, it is possible to prevent the space where the outer fin is provided in the duct from being reduced. Therefore, this intercooler can increase the heat exchange efficiency between the compressed air and the coolant.
  • the width of the first flow path is smaller than the width of the second flow path, and the first inlet communication portion and the first outlet communication portion. Is smaller than the width of the first flow path.
  • this intercooler can be downsized in the direction in which the first flow path and the second flow path are aligned.
  • the first inlet pipe is provided on one outer wall of the duct in the stacking direction
  • the first outlet pipe is provided on the other outer wall of the duct in the stacking direction.
  • the first inlet pipe and the first outlet pipe are disposed so as to overlap each other when viewed from the stacking direction.
  • this intercooler can be downsized in the direction in which the first flow path and the second flow path are aligned.
  • the intercooler is provided between the plurality of cooling plates in a portion where the first inlet communication portion, the first outlet communication portion, the second inlet communication portion, and the second outlet communication portion are formed.
  • a spacer plate is provided.
  • the outer fin is provided in a space formed between the inner wall of the duct located on the side opposite to the spacer plate and the spacer plate.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)

Abstract

Selon l'invention, une pluralité de plaques de refroidissement (40), empilées à l'intérieur d'un conduit (30), comprennent des premiers circuits d'écoulement (43) et des seconds circuits d'écoulement (44). Une première partie de communication d'entrée (47) et une première partie de communication de sortie (48) permettent la communication des premiers circuits d'écoulement (43) entre eux, dans la direction d'empilement (H). Une seconde partie de communication d'entrée (49) et une seconde partie de communication de sortie (50) permettent la communication des seconds circuits d'écoulement (44) entre eux, dans la direction d'empilement (H). La première partie de communication d'entrée (47), la première partie de communication de sortie (48), la seconde partie de communication d'entrée (49) et la seconde partie de communication de sortie (50) sont disposées dans une région au niveau d'un côté dans une direction (L) croisant la direction d'empilement (H) des plaques de refroidissement (40), et croisant une direction (W) de disposition des premiers circuits d'écoulement (43) et des seconds circuits d'écoulement (44). La dimension interne (D1) de la première partie de communication d'entrée (47) et de la première partie de communication de sortie (48), dans la direction (W) de disposition des premiers circuits d'écoulement (43) et des seconds circuits d'écoulement (44), est plus petite que la dimension interne (D2) de la seconde partie de communication d'entrée (49) et de la seconde partie de communication de sortie (50).
PCT/JP2017/041352 2016-12-26 2017-11-16 Refroidisseur intermédiaire Ceased WO2018123334A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112017006546.1T DE112017006546T5 (de) 2016-12-26 2017-11-16 Ladeluftkühler
CN201780079228.6A CN110100143B (zh) 2016-12-26 2017-11-16 中冷器

Applications Claiming Priority (2)

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JP2016251187A JP2018105534A (ja) 2016-12-26 2016-12-26 インタークーラ
JP2016-251187 2016-12-26

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WO2018123334A1 true WO2018123334A1 (fr) 2018-07-05

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CN (1) CN110100143B (fr)
DE (1) DE112017006546T5 (fr)
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JP2015042928A (ja) * 2013-08-26 2015-03-05 昭和電工株式会社 熱交換器
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CN110100143A (zh) 2019-08-06
CN110100143B (zh) 2021-02-02
JP2018105534A (ja) 2018-07-05
DE112017006546T5 (de) 2019-09-19

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