WO2015159529A1 - Échangeur thermique - Google Patents

Échangeur thermique Download PDF

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Publication number
WO2015159529A1
WO2015159529A1 PCT/JP2015/002038 JP2015002038W WO2015159529A1 WO 2015159529 A1 WO2015159529 A1 WO 2015159529A1 JP 2015002038 W JP2015002038 W JP 2015002038W WO 2015159529 A1 WO2015159529 A1 WO 2015159529A1
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WO
WIPO (PCT)
Prior art keywords
core plate
tube
tubes
header tank
heat exchanger
Prior art date
Application number
PCT/JP2015/002038
Other languages
English (en)
Japanese (ja)
Inventor
信太 馬渕
Original Assignee
株式会社デンソー
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 株式会社デンソー filed Critical 株式会社デンソー
Publication of WO2015159529A1 publication Critical patent/WO2015159529A1/fr

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    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • 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
    • F28F9/0226—Header boxes formed by sealing end plates into covers with resilient gaskets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • This disclosure relates to a heat exchanger and is effective when applied to a vehicle heat exchanger mounted on a vehicle.
  • a header tank of a heat exchanger such as a radiator is configured by integrating a metal core plate to which tubes are joined and a resin tank main body forming a tank internal space.
  • a packing (seal member) made of an elastic member such as rubber is disposed between the core plate and the tank main body. The core plate and the tank are compressed by compressing the packing between the core plate and the tank main body. The main body is sealed.
  • the core plate has a tube joint surface to which the tube is joined, and a groove formed at the outer peripheral edge of the tube joint surface.
  • the core plate side tip portion of the tank main body portion is inserted into the core plate groove portion, and the tank is sandwiched between the core plate groove portion and the tank main body tip portion.
  • the main body is caulked and fixed to the core plate.
  • the width direction dimension As the whole heat exchanger having such a configuration, since the groove portion is formed in the core plate, the length in the flow direction of the external fluid (air) in the core plate by the amount of the groove portion (hereinafter also referred to as the width direction dimension). Becomes longer. Thereby, there existed a problem that the width direction dimension as the whole heat exchanger became long.
  • a heat exchanger in which the width is reduced by eliminating the groove portion of the core plate is disclosed (for example, see Patent Document 1).
  • a packing is directly disposed on a tube joining surface to which a tube in a core plate is inserted and joined, and an end of a tank main body is disposed on the packing. Has been placed.
  • the plurality of tubes are arranged in parallel with each other, and are arranged at the longitudinal ends of the plurality of tubes, and extend in the juxtaposition direction of the plurality of tubes.
  • a stress concentration portion where the acting stress is concentrated is provided.
  • the stress concentration part is bent when a thermal strain due to a thermal expansion difference occurs between the tube and the core plate.
  • the core plate can be positively bent.
  • the bending amount of a core plate becomes large and can absorb the thermal distortion which arose between the tube and the core plate. Therefore, even when the size in the width direction of the header tank is reduced, it is possible to reduce the thermal distortion generated at the root portion between the header tank and the tube.
  • a plurality of tubes that are arranged in parallel with each other and in which a fluid flows inside, and arranged in longitudinal ends of the plurality of tubes, and a direction in which the plurality of tubes are arranged in parallel.
  • a header tank that communicates with a plurality of tubes, the header tank being a box-shaped heat exchanger having a tube joining surface into which a plurality of tubes are inserted and joined. It has an outer wall part that is bent from the surface toward the outside in the longitudinal direction of the tube, and a stress concentration part that concentrates the stress acting on the core plate is provided at the connection part between the tube joint surface and the outer wall part It has been.
  • the stress concentration portion when the stress concentration portion is provided at the connection portion between the tube joint surface and the outer wall portion in the header tank, the stress concentration occurs when the thermal strain due to the thermal expansion difference occurs between the tube and the header tank.
  • the part becomes a starting point of bending, and the header tank can be positively bent.
  • the amount of deflection of the header tank is increased, and the thermal strain generated between the tube and the header tank can be absorbed. Therefore, even when the size in the width direction of the header tank is reduced, it is possible to reduce the thermal distortion generated at the root portion between the header tank and the tube.
  • FIG. 3 is a cross-sectional view taken along the line III-III in FIG.
  • FIG. 3 is a schematic sectional drawing which shows the cross section which looked at the core plate in 2nd Embodiment from the tube lamination direction.
  • FIG. 3 shows the cross section which looked at the core plate in 3rd Embodiment from the tube lamination direction.
  • FIG. drawing which shows the cross section which looked at the core plate in 4th Embodiment from the tube lamination direction.
  • the radiator 1 of the present embodiment includes a core portion 4 composed of a plurality of tubes 2 and fins 3, and a pair of header tanks 5 that are assembled and arranged at both ends of the core portion 4. Yes.
  • the tube 2 is a tube through which a fluid (engine cooling water in this embodiment) flows.
  • the tube 2 is formed in a flat shape so that the air flow direction coincides with the major axis direction.
  • a plurality of tubes 2 are arranged in parallel in the vertical direction so that the longitudinal direction thereof coincides with the horizontal direction.
  • the fin 3 is formed into a wave shape and joined to the flat surfaces on both sides of the tube 2.
  • the fins 3 increase the heat transfer area with the air and promote heat exchange between the engine cooling water flowing through the tube 2 and the air.
  • the header tank 5 extends in a direction perpendicular to the tube longitudinal direction at both ends of the tube 2 in the longitudinal direction (hereinafter referred to as the tube longitudinal direction) and communicates with the plurality of tubes 2.
  • the header tank 5 is disposed at the left and right ends of the tube 2, extends in the vertical direction, and communicates with the plurality of tubes 2.
  • the header tank 5 includes a core plate 51 into which the tube 2 is inserted and joined, and a tank main body 52 that forms a tank space together with the core plate 51.
  • side plates 6 that reinforce the core portion 4 are provided at both ends of the core portion 4 in the juxtaposing direction of the tubes 2 (hereinafter referred to as tube stacking direction).
  • the side plate 6 extends in parallel with the tube longitudinal direction, and both end portions thereof are connected to the header tank 5.
  • FIG. 2 illustration of the packing 53 mentioned later is abbreviate
  • FIG. 3 illustration of the tube 2 and the tank main-body part 52 mentioned later is abbreviate
  • the header tank 5 includes a core plate 51, a tank body 52, and a packing 53.
  • the tube 2 and the side plate 6 are inserted and joined to the core plate 51.
  • the tank body 52 and the core plate 51 constitute a tank internal space that is a space in the header tank 5.
  • the packing 53 is a seal member that seals between the core plate 51 and the tank main body 52.
  • the core plate 51 is made of an aluminum alloy.
  • the tank body 52 is made of resin such as glass reinforced polyamide reinforced with glass fiber.
  • the packing 53 has a rectangular cross-sectional shape viewed from the tube stacking direction.
  • the packing 53 of the present embodiment is made of elastically deformable rubber (in this example, ethylene-propylene-diene rubber (EPDM)).
  • the core plate 51 has a tube joint surface 511 on which the tube 2 is inserted and joined, and a seal surface 512 on which the packing 53 is disposed. A surface pressure of the packing 53 is applied to the seal surface 512 when the tank body 52 is caulked and fixed.
  • the tube joint surface 511 and the seal surface 512 are parallel to each other. Specifically, the tube joint surface 511 and the seal surface 512 are perpendicular to the tube longitudinal direction.
  • the tube joint surface 511 and the seal surface 512 are different from each other in the tube longitudinal direction distance from the tube longitudinal end surface of the tube 2 (hereinafter referred to as the tube end surface 20).
  • the distance in the tube longitudinal direction from the tube joining surface 511 to the tube end surface 20 is shorter than the distance in the tube longitudinal direction from the seal surface 512 to the tube end surface 20. That is, the seal surface 512 is disposed on the inner side in the longitudinal direction of the tube 2 (side closer to the core portion 4) than the tube joint surface 511.
  • the tube joint surface 511 and the seal surface 512 are connected via an inclined surface 513 inclined with respect to the tube longitudinal direction.
  • the inclined surface 513 is inclined with respect to each of the tube joint surface 511 and the seal surface 512.
  • the angle formed by the seal surface 512 and the inclined surface 513 and the angle formed by the tube joint surface 511 and the inclined surface 513 are obtuse angles.
  • a large number of tube insertion holes 511a into which the tube 2 is inserted and brazed are formed in the tube joining surface 511 and the inclined surface 513 along the tube stacking direction.
  • the tube 2 is inserted and joined to the tube joining surface 511 and the inclined surface 513.
  • side plate insertion holes into which the side plate 6 is inserted and brazed are formed in the tube joining surface 511 and the inclined surface 513 in the tube stacking direction in each of the tube joining surface 511 and the inclined surface 513. One is formed at each end. The side plate 6 is inserted and joined to the tube joining surface 511 and the inclined surface 513.
  • the substantially cylindrical burring part 514 which contacts the outer wall of the tube 2 is provided in the edge part of the tube insertion hole 511a.
  • the burring portion 514 is formed by subjecting the tube insertion hole 511a to burring and expanding the dimension of the tube insertion hole 511a so as to be substantially the same as the outer dimension of the tube 2.
  • a substantially cylindrical burring portion (not shown) that contacts the outer wall of the side plate 6 is also provided at the edge of the side plate insertion hole.
  • ribs 515 are provided between the adjacent tubes 2 on the inclined surface 513 of the core plate 51.
  • the rib 515 is formed so as to protrude from the inclined surface 513 toward the outer side of the header tank 5 (inner side in the longitudinal direction of the tube 2).
  • the rib 515 is formed from the inner side end of the header tank 5 to the outer side end of the inclined surface 513.
  • the core plate 51 has an outer wall portion 516 that is bent at a substantially right angle from the seal surface 512 toward the opposite side of the core portion 4 and extends in the tube stacking direction or the air flow direction.
  • a bulging portion 521 that bulges toward the outer side of the header tank 5 is formed in a portion of the tank main body 52 that faces the tube 2. Thereby, it is comprised so that the inner surface of the tank main-body part 52 and the outer surface of the tube 2 may not contact.
  • a flange portion 522 having a thickness greater than that of other portions is provided.
  • the flange portion 522 is disposed on the seal surface 512 of the core plate 51 via the packing 53.
  • the core plate 51 is provided with a plurality of caulking claw portions 517 formed so as to protrude from the outer wall portion 516 to the tank main body portion 52 side.
  • the caulking claw portion 517 is disposed at a portion corresponding to the flange portion 522 of the tank main body portion 52.
  • the tank body 52 is assembled to the core plate 51 by fixing the crimping claw 517 to the flange 522 of the tank body 52.
  • an inner column portion 21 is provided inside the tube 2, so as to connect the two flat surfaces to each other and to increase the pressure resistance of the tube 2.
  • the inner column portion 21 is disposed in the center portion in the air flow direction inside the tube 2.
  • the inner pillar 21 divides the fluid passage inside the tube 2 into two.
  • the core plate 51 is disposed between the inclined surface 513 and the outer wall portion 516 and connected to both the inclined surface 513 and the outer wall portion 516.
  • the part is referred to as the bottom 54.
  • the inclined surface 513, the outer wall portion 516, and the bottom portion 54 form a groove portion 510 for arranging the packing 53.
  • a packing 53 is disposed on the bottom 54 of the core plate 51. For this reason, a part of the inner side surface of the header tank 5 in the bottom portion 54 constitutes a seal surface 512. Therefore, the bottom portion 54 of the present embodiment can provide “a portion of the core plate 51 where the seal surface 512 is provided”.
  • a thin wall portion 55 having a smaller plate thickness than the bottom portion 54 is provided on the tube joint surface 511 side of the core plate 51 with respect to the seal surface 512 (that is, on the inner side of the header tank 5).
  • the thin portion 55 is configured by forming a recess 56 in the core plate 51. In the thin portion 55, stress acting on the core plate 51 is concentrated. Therefore, the thin portion 55 of the present embodiment can provide a “stress concentration portion”.
  • the thin wall portion 55 is provided on the surface of the core plate 51 facing the tank body portion 52, that is, the inner surface of the header tank 5. Specifically, a recess 56 is formed on the surface of the core plate 51 that faces the tank body 52. The thin portion 55 extends in the longitudinal direction of the core plate 51 (in the present embodiment, the tube stacking direction).
  • the thin portion 55 is provided at a connection portion between the bottom portion 54 and the inclined surface 513 in the core plate 51. That is, the thin portion 55 is arranged on the outer side of the tank with respect to the rib 515 in the core plate 51. The thin portion 55 is formed by pressing so that the connecting portion between the bottom portion 54 and the inclined surface 513 is crushed from the inner side of the header tank 5 when the core plate 51 is formed.
  • the thin portion 55 is provided closer to the tube joint surface 511 than the seal surface 512 in the core plate 51. According to this, when a thermal strain due to a difference in thermal expansion occurs between the tube 2 and the core plate 51, stress concentrates on the thin wall portion 55 to become a bending start point, and the core plate 51 (specifically, the bottom portion). 54 and outer wall 516) can be positively deflected. For this reason, the amount of bending of the core plate 51 is increased, and the thermal strain generated between the tube 2 and the core plate 51 can be absorbed. Therefore, even when the width direction dimension (air flow direction dimension) of the header tank 5 is reduced, it is possible to reduce the thermal distortion generated at the root portion between the header tank 5 and the tube 2.
  • the thin portion 55 is disposed on the outer side of the header tank 5 with respect to the rib 515 in the core plate 51. According to this, since both the rib 515 and the thin portion 55 can be provided on the core plate 51, the thermal strain alleviating effect by providing the rib 515, and the thermal strain absorbing effect by providing the thin portion 55, Both can be obtained.
  • the recess 56 of the present embodiment is formed on the surface of the core plate 51 that does not face the tank body 52, that is, the outer surface of the header tank 5. For this reason, the thin portion 55 is provided on the surface of the core plate 51 that does not face the tank main body 52.
  • Other configurations are the same as those of the first embodiment. Therefore, according to the exhaust heat exchanger of the present embodiment, the same effect as that of the first embodiment can be obtained.
  • the recesses 56 of the present embodiment are provided on both the surface of the core plate 51 facing the tank body 52 and the surface not facing the tank body 52. For this reason, the plate
  • the core plate 51 when the thermal distortion by a thermal expansion difference arises between the tube 2 and the core plate 51, the core plate 51 can be bent more positively. For this reason, the amount of bending of the core plate 51 becomes larger, and the thermal strain generated between the tube 2 and the core plate 51 can be more reliably absorbed.
  • the packing 53 of the present embodiment has a circular cross-sectional shape as viewed from the tube stacking direction. For this reason, the packing 53 is in point contact with the core plate 51. Therefore, the seal surface 512 of the present embodiment has a smaller area than the seal surface 512 of the first embodiment.
  • the recess 56 is provided on the surface of the bottom 54 that does not face the tank body 52.
  • an elastically deformable spring structure portion 57 is provided on the tube joint surface 511 side of the seal surface 512 in the core plate 51.
  • the spring structure portion 57 is formed by curving a connection portion between the bottom portion 54 and the inclined surface 513 in the core plate 51 in an arc shape. In the spring structure portion 57, stress acting on the core plate 51 is concentrated. Therefore, the spring structure portion 57 of this embodiment can provide a “stress concentration portion”.
  • the spring structure 57 is provided on the tube joint surface 511 side of the seal surface 512 in the core plate 51. According to this, when a thermal strain due to a difference in thermal expansion occurs between the tube 2 and the core plate 51, stress concentrates on the spring structure portion 57 to become a bending start point, and the core plate 51 (specifically, The bottom 54 and the outer wall 516) can be flexed positively. For this reason, it becomes possible to acquire the effect similar to the said 1st Embodiment.
  • the core plate 51 of the present embodiment has an inner wall portion 518 that is bent at a substantially right angle from the tube joint surface 511 toward the core portion 4 and extends in the tube stacking direction or the air flow direction. ing.
  • the tube joint surface 511 and the seal surface 512 (bottom portion 54) of the core plate 51 are connected by an inner wall portion 518.
  • the inner wall portion 518 is configured to be orthogonal to the air flow direction or the tube stacking direction.
  • the thin portion 55 of the present embodiment is provided at a connection portion between the bottom portion 54 and the inner wall portion 518 in the core plate 51.
  • the tube joint surface 511 and the seal surface 512 are arranged on the same plane.
  • the thin portion 55 is disposed between the tube joint surface 511 and the seal surface 512.
  • the header tank 5 is formed in a box shape having a tube joint surface 511 to which a plurality of tubes 2 are inserted and joined.
  • the header tank 5 is made of a metal such as an aluminum alloy.
  • the header tank 5 is formed in a substantially rectangular parallelepiped shape having a tube joining surface 511, an outer wall portion 516, and an upper wall portion 519.
  • the outer wall portion 516 is a peripheral wall member that is bent at a substantially right angle from the tube joint surface 511 toward the tube longitudinal direction outer side (the side opposite to the core portion 4) and extends in the tube stacking direction or the air flow direction.
  • the upper side wall portion 519 extends in parallel with the tube joint surface 511 and is connected to the outer side wall portion 516.
  • a spring structure 57 that can be elastically deformed is provided at a connection portion between the tube joining surface 511 and the outer wall portion 516.
  • the spring structure portion 57 is formed by curving a connection portion between the tube joint surface 511 and the outer wall portion 516 in the core plate 51 in an arc shape.
  • stress acting on the core plate 51 is concentrated. Therefore, the spring structure portion 57 of this embodiment can provide a “stress concentration portion”.
  • the spring structure portion 57 is provided at the connection portion between the tube joint surface 511 and the outer wall portion 516 in the header tank 5. According to this, when a thermal distortion due to a difference in thermal expansion occurs between the tube 2 and the header tank 5, stress concentrates on the spring structure portion 57 to be a bending start point, and the header tank 5 is positively bent. be able to. For this reason, it becomes possible to acquire the effect similar to the said 1st Embodiment.
  • the header tank 5 is comprised by combining the metal core plate 51 and the resin tank main-body part 52, it is packing between the core plate 51 and the tank main-body part 52. 53 must be sealed.
  • the header tank 5 is integrally formed in a box shape from metal, it is not necessary to provide the packing 53, and the number of parts can be reduced.
  • the stress concentration portion 57 is employed as the stress concentration portion
  • the stress concentration portion is not limited thereto.
  • a thin portion having a thinner plate thickness than other portions of the header tank 5 may be employed.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un échangeur thermique pourvu de tuyaux (2) et d'un réservoir collecteur (5) qui communique avec les tuyaux (2). Le réservoir collecteur (5) possède une plaque centrale (51) sur laquelle sont assemblés les tuyaux (2), et un corps de réservoir (52) qui est fixé à la plaque centrale (51). La plaque centrale (51) a une surface d'assemblage de tuyaux (511) dans laquelle les tuyaux (2) sont insérés et assemblés et une surface d'étanchéité (512) sur laquelle une garniture déformable élastiquement (53) est disposée. Une section à paroi mince (55) dans laquelle se concentre une contrainte agissant sur la plaque centrale (51) est formée sur le côté de la plaque centrale (51) qui est plus proche de la surface d'assemblage de tuyaux (511) que la surface d'étanchéité (512). En résultat de cette configuration, la contrainte thermique se produisant dans les parties où le réservoir collecteur (5) et les tuyaux (2) sont assemblés peut être réduite même si la largeur du réservoir collecteur (5) est réduite.
PCT/JP2015/002038 2014-04-18 2015-04-10 Échangeur thermique WO2015159529A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014086127A JP2015206507A (ja) 2014-04-18 2014-04-18 熱交換器
JP2014-086127 2014-04-18

Publications (1)

Publication Number Publication Date
WO2015159529A1 true WO2015159529A1 (fr) 2015-10-22

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Family Applications (1)

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PCT/JP2015/002038 WO2015159529A1 (fr) 2014-04-18 2015-04-10 Échangeur thermique

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WO (1) WO2015159529A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6394202B2 (ja) * 2013-11-27 2018-09-26 株式会社デンソー 熱交換器
WO2020166983A1 (fr) * 2019-02-13 2020-08-20 한온시스템 주식회사 Échangeur de chaleur
KR20200099088A (ko) * 2019-02-13 2020-08-21 한온시스템 주식회사 열교환기

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54119157A (en) * 1978-01-27 1979-09-14 Westinghouse Electric Corp Heat exchanger
JPH0417284U (fr) * 1990-05-25 1992-02-13
JP2004301455A (ja) * 2003-03-31 2004-10-28 Calsonic Kansei Corp 熱交換器用のヘッダタンク
JP2006284107A (ja) * 2005-04-01 2006-10-19 Denso Corp 熱交換器

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54119157A (en) * 1978-01-27 1979-09-14 Westinghouse Electric Corp Heat exchanger
JPH0417284U (fr) * 1990-05-25 1992-02-13
JP2004301455A (ja) * 2003-03-31 2004-10-28 Calsonic Kansei Corp 熱交換器用のヘッダタンク
JP2006284107A (ja) * 2005-04-01 2006-10-19 Denso Corp 熱交換器

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