JP6011088B2 - Intercooler for vehicle - Google Patents
Intercooler for vehicle Download PDFInfo
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- JP6011088B2 JP6011088B2 JP2012156431A JP2012156431A JP6011088B2 JP 6011088 B2 JP6011088 B2 JP 6011088B2 JP 2012156431 A JP2012156431 A JP 2012156431A JP 2012156431 A JP2012156431 A JP 2012156431A JP 6011088 B2 JP6011088 B2 JP 6011088B2
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- Prior art keywords
- intake
- plate
- intake air
- outlet
- tube
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Classifications
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- 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
- F02B29/0456—Air cooled heat exchangers
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
- F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
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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
- 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
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- 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
Description
本発明は、車両用インタークーラに関する。 The present invention relates to a vehicle intercooler.
一般的に、車両用インタークーラは、吸気を流通させる複数のチューブを車幅方向に配置したコア部と、過給機側に接続される入口パイプ部、及びコア部の吸気上流側に取り付けられる縦長の入口ヘッダー部を有する吸気導入部と、コア部の吸気下流側に取り付けられる縦長の出口ヘッダー部、及びエンジン側に接続される出口パイプ部を有する吸気導出部とを備えている。また、吸気導入部の入口パイプ部と入口ヘッダー部とは入口曲面部で連結されると共に、吸気導出部の出口ヘッダー部と出口パイプ部とは出口曲面部で連結されている。このような車両用インタークーラは、例えば特許文献１に記載されている。 In general, a vehicle intercooler is attached to a core portion in which a plurality of tubes for circulating intake air are arranged in the vehicle width direction, an inlet pipe portion connected to a supercharger side, and an intake upstream side of the core portion. An intake air introduction portion having a vertically long inlet header portion, a vertically long outlet header portion attached to the intake downstream side of the core portion, and an intake air derivation portion having an outlet pipe portion connected to the engine side are provided. Further, the inlet pipe portion and the inlet header portion of the intake air introduction portion are connected by an inlet curved surface portion, and the outlet header portion and the outlet pipe portion of the intake air outlet portion are connected by an outlet curved surface portion. Such a vehicle intercooler is described in Patent Document 1, for example.
ところで、従来の車両用インタークーラにおいては、出口曲面部と出口パイプ部との接続位置は、出口ヘッダー部の長手方向（上下方向）中心よりも上方に偏心されている。そのため、下方のチューブから流入する吸気は出口ヘッダー部内を上方に向かって流れて、上方のチューブから流入する吸気と合流する。そして、これら吸気の合流部付近では圧力が高くなり、チューブから出口ヘッダー部内への吸気の流入が妨げられることで、各チューブ内の吸気流速を不均一にさせている。結果として、各チューブの吸気流量も不均一になり、コア部における吸気の冷却効率を十分に発揮できない可能性がある。 By the way, in the conventional vehicle intercooler, the connection position of the outlet curved surface portion and the outlet pipe portion is eccentric above the center in the longitudinal direction (vertical direction) of the outlet header portion. Therefore, the intake air flowing in from the lower tube flows upward in the outlet header portion, and merges with the intake air flowing in from the upper tube. In addition, the pressure is increased in the vicinity of the merging portion of the intake air, and the inflow of the intake air from the tube into the outlet header portion is prevented, thereby making the intake air flow velocity in each tube non-uniform. As a result, the intake air flow rate of each tube also becomes non-uniform, and there is a possibility that the cooling efficiency of the intake air in the core portion cannot be fully exhibited.
本発明はこのような点に鑑みてなされたもので、その目的は、各チューブ内の吸気流速を効果的に均一化することができる車両用インタークーラを提供することにある。 The present invention has been made in view of such a point, and an object thereof is to provide an intercooler for a vehicle that can effectively equalize the intake air flow velocity in each tube.
上記目的を達成するため、本発明の車両用インタークーラは、エンジンへの吸気を流通させる複数のチューブを有するコア部と、前記コア部の吸気上流側に取り付けられて前記チューブに吸気を導入する入口ヘッダー部を有する吸気導入部と、前記コア部の吸気下流側に取り付けられて前記チューブから吸気が流入する出口ヘッダー部、及び該出口ヘッダー部にその中心位置から偏心して接続された出口パイプ部を有する吸気導出部とを備える車両用インタークーラにおいて、前記出口ヘッダー部内に、前記チューブの吸気流れ方向に延在するプレートを設けたことを特徴とする。 In order to achieve the above object, an intercooler for a vehicle according to the present invention introduces intake air into the core portion having a plurality of tubes that circulate intake air to the engine, and attached to the intake air upstream side of the core portion. An intake air inlet portion having an inlet header portion, an outlet header portion that is attached to the downstream side of the core portion and intake air flows from the tube, and an outlet pipe portion that is eccentrically connected to the outlet header portion from its central position In the vehicular intercooler including the intake deriving portion, a plate extending in the intake flow direction of the tube is provided in the outlet header portion.
また、前記出口ヘッダー部内に、前記プレートから離間して対向する第２のプレートをさらに設けてもよい。 Moreover, you may provide further in the said exit header part the 2nd plate which spaces apart and opposes from the said plate.
また、前記吸気導出部は、前記出口ヘッダー部と前記出口パイプ部とを曲面で滑らかに連結する曲面部をさらに備え、前記プレート及び前記第２のプレートの吸気下流側をそれぞれ該曲面部の内部まで延設してもよい。 The intake air derivation unit further includes a curved surface portion that smoothly connects the outlet header portion and the outlet pipe portion with a curved surface, and the intake air downstream side of the plate and the second plate is disposed inside the curved surface portion. It may extend to.
また、前記プレートの吸気上流端部は、前記チューブの吸気下流端部の近傍、もしくは、前記チューブの吸気下流端部に隣接して配置されてもよい。 The intake upstream end of the plate may be disposed in the vicinity of the intake downstream end of the tube or adjacent to the intake downstream end of the tube.
本発明の車両用インタークーラによれば、各チューブ内の吸気流速を効果的に均一化することができる。 According to the vehicle intercooler of the present invention, it is possible to effectively equalize the intake air flow velocity in each tube.
以下、図１〜４に基づいて、本発明の一実施形態に係る車両用インタークーラについて説明する。同一の部品には同一の符号を付してあり、それらの名称および機能も同じである。したがって、それらについての詳細な説明は繰返さない。 Hereinafter, based on FIGS. 1-4, the intercooler for vehicles which concerns on one Embodiment of this invention is demonstrated. The same parts are denoted by the same reference numerals, and their names and functions are also the same. Therefore, detailed description thereof will not be repeated.
本実施形態の車両用インタークーラ１は、図１に示すように、吸気と外気との熱交換を行うコア部１０と、図示しない過給機からの吸気をコア部１０に導入する吸気導入部２０と、コア部１０から図示しないエンジンに吸気を導出する吸気導出部３０とを備えている。 As shown in FIG. 1, the vehicle intercooler 1 of the present embodiment includes a core portion 10 that performs heat exchange between intake air and outside air, and an intake air introduction portion that introduces intake air from a supercharger (not shown) into the core portion 10. 20 and an intake air deriving unit 30 for deriving intake air from the core unit 10 to an engine (not shown).
コア部１０は、吸気を流通させる車幅方向に延在する複数のチューブ１１と、各チューブ１１間に介装された複数のアウターフィン１２と、貫通形成された図示しない複数の穴に各チューブ１１の吸気上流端を挿通して固定する縦長の入口プレート１３と、貫通形成された図示しない複数の穴に各チューブ１１の吸気下流端を挿通して固定する縦長の出口プレート１４とを備えている。本実施形態において、入口プレート１３及び出口プレート１４のプレート平面は、複数のチューブ１１の軸方向と直交する。 The core portion 10 includes a plurality of tubes 11 extending in the vehicle width direction through which the intake air is circulated, a plurality of outer fins 12 interposed between the tubes 11, and a plurality of holes (not shown) formed through the tubes. 11 is provided with a vertically long inlet plate 13 for inserting and fixing the intake air upstream end of 11 and a vertically long outlet plate 14 for inserting and fixing the intake air downstream end of each tube 11 in a plurality of holes formed through it. Yes. In the present embodiment, the plate planes of the inlet plate 13 and the outlet plate 14 are orthogonal to the axial direction of the plurality of tubes 11.
吸気導入部２０は、過給機側の吸気管４１に接続されて車両前後方向に延在する入口パイプ部２１と、コア部１０の入口プレート１３に取り付けられた縦長中空状の入口ヘッダー部２２と、入口パイプ部２１と入口ヘッダー部２２とを滑らかに連結する曲面中空状の入口曲面部２３とを備えている。本実施形態において、入口曲面部２３の吸気下流端は、入口ヘッダー部２２の側面に車両幅方向から接続されている。また、入口パイプ部２１と入口曲面部２３との接続位置は、入口ヘッダー部２２の長手方向（上下方向）中心位置よりも上方に偏心されている。 The intake air introduction portion 20 is connected to an intake pipe 41 on the supercharger side and extends in the vehicle front-rear direction, and a vertically long hollow inlet header portion 22 attached to the inlet plate 13 of the core portion 10. And a curved hollow inlet curved surface portion 23 that smoothly connects the inlet pipe portion 21 and the inlet header portion 22. In the present embodiment, the intake downstream end of the inlet curved surface portion 23 is connected to the side surface of the inlet header portion 22 from the vehicle width direction. In addition, the connection position between the inlet pipe portion 21 and the inlet curved surface portion 23 is deviated upward from the center position in the longitudinal direction (vertical direction) of the inlet header portion 22.
入口曲面部２３の車両幅方向における外壁の縦断面形状は上下方向に略Ｓ字状に形成され、かつ、その下方内側面を内側に突出させている。また、この下方内側面は、入口ヘッダー部２２下方の内側面と連結する。さらに、入口曲面部２３は、その流路縦断面積を吸気流れに沿って次第に拡張するように形成されている。 The vertical cross-sectional shape of the outer wall in the vehicle width direction of the entrance curved surface portion 23 is formed in an approximately S shape in the vertical direction, and its lower inner surface protrudes inward. Further, the lower inner surface is connected to the inner surface below the inlet header portion 22. Furthermore, the inlet curved surface portion 23 is formed so as to gradually expand the longitudinal sectional area of the flow path along the intake flow.
吸気導出部３０は、エンジン側の吸気管４２に接続されて車両前後方向に延在する出口パイプ部３１と、コア部１０の出口プレート１４に取り付けられた縦長中空状の出口ヘッダー部３２と、出口パイプ部３１と出口ヘッダー部３２とを滑らかに連結する曲面中空状の出口曲面部３３と、堰止プレート３４と、整流プレート（第２のプレート）３５とを備えている。本実施形態において、出口曲面部３３の吸気上流端は、出口ヘッダー部３２の側面に車両幅方向から接続されている。また、出口パイプ部３１と出口曲面部３３との接続位置は、出口ヘッダー部３２の長手方向（上下方向）中心位置よりも上方に偏心されている。 The intake deriving portion 30 is connected to an intake pipe 42 on the engine side and extends in the vehicle front-rear direction, a vertically long hollow outlet header portion 32 attached to the outlet plate 14 of the core portion 10, A curved hollow outlet curved surface portion 33 that smoothly connects the outlet pipe portion 31 and the outlet header portion 32, a dam plate 34, and a rectifying plate (second plate) 35 are provided. In the present embodiment, the intake upstream end of the outlet curved surface portion 33 is connected to the side surface of the outlet header portion 32 from the vehicle width direction. Further, the connection position between the outlet pipe portion 31 and the outlet curved surface portion 33 is decentered above the center position in the longitudinal direction (vertical direction) of the outlet header portion 32.
出口曲面部３３の車両幅方向における外壁の縦断面形状は上下方向に略Ｓ字状に形成され、かつ、その下方内側面を内側に突出させている。また、この下方内側面は、出口ヘッダー部３２下方の内側面と連結する。さらに、出口曲面部３３は、その流路縦断面積を吸気流れに沿って次第に縮小するように形成されている。 The vertical cross-sectional shape of the outer wall of the exit curved surface portion 33 in the vehicle width direction is formed in an approximately S shape in the vertical direction, and the lower inner surface protrudes inward. The lower inner surface is connected to the inner surface below the outlet header 32. Further, the outlet curved surface portion 33 is formed so as to gradually reduce the longitudinal cross-sectional area of the flow path along the intake flow.
堰止プレート３４は、図２に示すように、出口ヘッダー部３２及び出口曲面部３３の形状に合わせて略Ｌ字状に屈曲して形成されている。堰止プレート３４の上流端部３４ａは、出口プレート１４の長手方向（上下方向）中心よりも上方の出口ヘッダー部３２内に、その板平面をチューブ１１の吸気流れ方向と平行にした状態で配置されている。また、堰止プレート３４の上流端部３４ａの上流側縁部は、チューブ１１の吸気下流端から僅かな隙間（微小なクリアランス）を隔てて配置されている。すなわち、図３に示すように、堰止プレート３４の上流端部３４ａは、その上流側縁部、屈曲内側縁部（車両後方側縁部）、及び屈曲外側縁部（車両前方側縁部）を、出口ヘッダー３２の中空部３２ａ内（Ｓ字状の外壁の下方内側面よりも出口プレート１４側の領域）に収容させている。これにより、下方のチューブ１１から出口ヘッダー部３２内に流入して上方に向かう吸気は、堰止プレート３４の上流端部３４ａで堰き止められる。なお、上流端部３４ａの上流側縁部とチューブ１１との間に微小なクリアランスを設ける必要はなく、この上流端部３４ａをチューブ１１の吸気下流端に接触させてもよい。 As shown in FIG. 2, the dam plate 34 is formed to be bent in a substantially L shape in accordance with the shapes of the outlet header portion 32 and the outlet curved surface portion 33. The upstream end portion 34 a of the dam plate 34 is disposed in the outlet header portion 32 above the center of the outlet plate 14 in the longitudinal direction (vertical direction) with its plate plane parallel to the intake flow direction of the tube 11. Has been. Further, the upstream edge of the upstream end 34 a of the dam plate 34 is disposed with a slight gap (minute clearance) from the intake downstream end of the tube 11. That is, as shown in FIG. 3, the upstream end 34a of the dam plate 34 includes an upstream edge, a bent inner edge (vehicle rear edge), and a bent outer edge (vehicle front edge). Is accommodated in the hollow portion 32a of the outlet header 32 (region on the outlet plate 14 side from the lower inner surface of the S-shaped outer wall). Thereby, the intake air flowing into the outlet header portion 32 from the lower tube 11 and moving upward is blocked by the upstream end portion 34 a of the blocking plate 34. Note that it is not necessary to provide a minute clearance between the upstream edge of the upstream end 34 a and the tube 11, and the upstream end 34 a may be brought into contact with the intake downstream end of the tube 11.
堰止プレート３４の下流端部３４ｂは、出口曲面部３３内に、その板平面を出口曲面部３３の上側内周面に沿わせた状態で配置されている。これにより、堰止プレート３４の上流端部３４ａで堰き止められた吸気は、出口曲面部３３内を出口パイプ部３１に向けて導かれるように構成されている。 The downstream end portion 34 b of the dam plate 34 is arranged in the outlet curved surface portion 33 in a state where the plate plane is along the upper inner peripheral surface of the outlet curved surface portion 33. Thereby, the intake air blocked by the upstream end portion 34 a of the blocking plate 34 is configured to be guided toward the outlet pipe portion 31 through the outlet curved surface portion 33.
整流プレート３５は、図２に示すように、出口ヘッダー部３２及び出口曲面部３３の形状に合わせて略Ｌ字状に屈曲して形成されている。整流プレート３５の上流端部３５ａは、堰止プレート３４よりも下方の出口ヘッダー部３２内に、その上流側縁部がチューブ１１の吸気下流端から所定のクリアランスを隔てて配置されている。これにより、下方のチューブ１１から出口ヘッダー部３２内に流入する吸気は、堰止プレート３４側と出口パイプ３１側とに分流される。 As shown in FIG. 2, the rectifying plate 35 is formed to be bent in a substantially L shape in accordance with the shape of the outlet header portion 32 and the outlet curved surface portion 33. The upstream end portion 35 a of the rectifying plate 35 is disposed in the outlet header portion 32 below the dam plate 34, and the upstream side edge portion thereof is disposed with a predetermined clearance from the intake downstream end of the tube 11. Thereby, the intake air flowing into the outlet header portion 32 from the lower tube 11 is divided into the dam plate 34 side and the outlet pipe 31 side.
また、整流プレート３５の下流端部３５ｂは、堰止プレート３４よりも下方の出口曲面部３３内に、その板平面を出口曲面部３３の下側内周面に沿わせた状態で配置されている。これにより、整流プレート３５の下流端部３５ｂで分流された吸気の一部は、出口曲面部３３内を出口パイプ部３１に向けて導かれるように構成されている。 Further, the downstream end portion 35 b of the rectifying plate 35 is disposed in the outlet curved surface portion 33 below the dam plate 34, with its plate plane along the lower inner peripheral surface of the outlet curved surface portion 33. Yes. Thus, a part of the intake air diverted at the downstream end portion 35 b of the rectifying plate 35 is configured to be guided toward the outlet pipe portion 31 through the outlet curved surface portion 33.
次に、本実施形態に係る車両用インタークーラ１による作用効果を説明する。 Next, the effect by the vehicle intercooler 1 which concerns on this embodiment is demonstrated.
例えば、図４（ａ）に示すように、吸気導出部６０内に堰止プレートや整流プレートを備えていない従来の車両用インタークーラにおいては、下方のチューブ５１から流入する吸気が出口ヘッダー部６２内を長手方向に沿って上方に流れて、上方のチューブ５１から流入する吸気と合流する。このため、これら吸気の合流部付近では圧力が高くなり、チューブ５１から出口ヘッダー部６２への吸気の流れ込みが妨げられることで、各チューブ５１内の吸気流速を不均一にさせている。 For example, as shown in FIG. 4A, in a conventional vehicle intercooler that does not include a dam plate or a rectifying plate in the intake air derivation unit 60, the intake air flowing from the lower tube 51 flows into the outlet header unit 62. The inside flows upward along the longitudinal direction, and merges with the intake air flowing in from the upper tube 51. For this reason, the pressure becomes high in the vicinity of the merging portion of these intake air, and the flow of the intake air from the tube 51 to the outlet header portion 62 is prevented, thereby making the intake air flow velocity in each tube 51 uneven.
これに対し、本実施形態の車両用インタークーラ１では、出口ヘッダー部３２内に、下方から上方に流れる吸気を堰き止める堰止プレート３４が配置されている。すなわち、図４（ｂ）に示すように、下方のチューブ１１から流入する吸気は、上方のチューブ１１から流入する吸気と合流することなく、堰止プレート３４の上流端部３４ａにより堰き止められた後、下流端部３４ｂに沿って出口パイプ部３１へと導かれる。 On the other hand, in the vehicle intercooler 1 of the present embodiment, a dam plate 34 that dams intake air flowing upward from below is disposed in the outlet header portion 32. That is, as shown in FIG. 4B, the intake air flowing in from the lower tube 11 is blocked by the upstream end 34 a of the blocking plate 34 without joining the intake air flowing in from the upper tube 11. Then, it guide | induces to the exit pipe part 31 along the downstream end part 34b.
したがって、本実施形態の車両用インタークーラ１によれば、各チューブ１１内の吸気流速を効果的に均一化することができると共に、各チューブ１１の吸気流量も均一化されて吸気の冷却効率を向上することができる。 Therefore, according to the vehicle intercooler 1 of the present embodiment, the intake air flow velocity in each tube 11 can be effectively made uniform, and the intake air flow rate in each tube 11 is also made uniform, thereby improving the intake air cooling efficiency. Can be improved.
また、本実施形態の車両用インタークーラ１では、堰止プレート３４よりも下方の出口ヘッダー部３２内及び出口曲面部３３内に整流プレート３５が配置されている。この整流プレート３５の上流端部３５ａとチューブ１１の吸気下流端との間には、下方から上方に流れる吸気の一部を通過させる所定のクリアランスが設けられている。 Further, in the vehicle intercooler 1 of the present embodiment, the rectifying plate 35 is disposed in the outlet header portion 32 and the outlet curved surface portion 33 below the dam plate 34. A predetermined clearance is provided between the upstream end 35a of the rectifying plate 35 and the intake downstream end of the tube 11 so as to allow a part of the intake air flowing upward from below.
すなわち、図４（ｂ）に示すように、下方のチューブ１１から流入する吸気は、整流プレート３５の上流端部３５ａにより堰止プレート３４側と出口パイプ部３１側とに分流される。そして、出口パイプ３１側に分流された吸気は整流プレート３５の下流端部３５ｂに沿って出口パイプ部３１に導かれる一方、堰止プレート３４側に分流された吸気は堰止プレート３４の上流端部３４ａで堰き止められた後、堰止プレート３４と整流プレート３５とで区画形成される流路を流れて出口パイプ部３１に導かれる。 That is, as shown in FIG. 4B, the intake air flowing from the lower tube 11 is divided into the dam plate 34 side and the outlet pipe portion 31 side by the upstream end portion 35 a of the rectifying plate 35. The intake air divided into the outlet pipe 31 side is guided to the outlet pipe portion 31 along the downstream end portion 35 b of the rectifying plate 35, while the intake air divided into the dam plate 34 side is upstream of the dam plate 34. After being dammed by the portion 34 a, it flows through a flow path defined by the dam plate 34 and the rectifying plate 35 and is guided to the outlet pipe portion 31.
したがって、本実施形態の車両用インタークーラ１によれば、堰止プレート３４の下方に整流プレート３５を設けたことで、出口曲面部３３内における吸気の流れが促進されて、吸気の抵抗を効果的に低減することができる。 Therefore, according to the vehicle intercooler 1 of the present embodiment, the flow of the intake air in the outlet curved surface portion 33 is promoted by providing the rectifying plate 35 below the dam plate 34, and the intake resistance is effective. Can be reduced.
なお、本発明は、上述の実施形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲で、適宜変形して実施することが可能である。 In addition, this invention is not limited to the above-mentioned embodiment, In the range which does not deviate from the meaning of this invention, it can change suitably and can implement.
例えば、出口パイプ部３１と出口曲面部３３との接続位置は、出口ヘッダー部３２の長手方向（上下方向）中心位置よりも上方に偏心されるものとして説明したが、下方に偏心させてもよい。この場合は、堰止プレート３４の上流端部３４ａを出口ヘッダー部３２内の下方に配置すればよい。 For example, the connection position between the outlet pipe portion 31 and the outlet curved surface portion 33 has been described as being deviated upward from the center position in the longitudinal direction (vertical direction) of the outlet header portion 32, but may be decentered downward. . In this case, the upstream end 34 a of the dam plate 34 may be disposed below the outlet header 32.
また、出口ヘッダー部３２と出口パイプ部３１とを出口曲面部３３で連結する必要はなく、これら出口ヘッダー部３２と出口パイプ部３１とを直接的に接続してもよい。 Further, it is not necessary to connect the outlet header portion 32 and the outlet pipe portion 31 with the outlet curved surface portion 33, and the outlet header portion 32 and the outlet pipe portion 31 may be directly connected.
１ 車両用インタークーラ
１０ コア部
１１ チューブ
２０ 吸気導入部
２１ 入口パイプ部
２２ 入口ヘッダー部
２３ 入口曲面部
３０ 吸気導出部
３１ 出口パイプ部
３２ 出口ヘッダー部
３３ 出口曲面部（曲面部）
３４ 堰止プレート（プレート）
３５ 整流プレート（第２のプレート）
DESCRIPTION OF SYMBOLS 1 Intercooler for vehicles 10 Core part 11 Tube 20 Intake inlet part 21 Inlet pipe part 22 Inlet header part 23 Inlet curved surface part 30 Inlet lead-out part 31 Outlet pipe part 32 Outlet header part 33 Outlet curved surface part (curved surface part)
34 Dam plate (plate)
35 Rectification plate (second plate)
Claims (2)
前記コア部の吸気上流側に取り付けられて前記チューブに吸気を導入する入口ヘッダー部を有する吸気導入部と、
前記コア部の吸気下流側に取り付けられて前記チューブから吸気が流入する出口ヘッダー部、及び該出口ヘッダー部にその長手方向の中心位置から偏心して接続された出口パイプ部を有する吸気導出部と、を備える車両用インタークーラにおいて、
前記出口ヘッダー部内に、前記チューブの吸気流れ方向に延在するプレート、及び該プレートから離間して対向すると共に前記チューブの吸気流れ方向に延在する第２のプレートが設けられ、
前記プレートは、前記第２のプレートよりも前記長手方向において前記出口パイプ側に設けられ、
前記プレートの吸気上流端部は、前記第２のプレートの吸気上流端部よりも、前記チューブの吸気下流端部に近い位置に設けられていることを特徴とする車両用インタークーラ。 A core portion having a plurality of tubes for circulating intake air to the engine;
An intake air introduction portion attached to the intake air upstream side of the core portion and having an inlet header portion for introducing intake air into the tube;
An intake header having an outlet header portion that is attached to the intake downstream side of the core portion and into which the intake air flows from the tube, and an outlet pipe portion that is eccentrically connected to the outlet header portion from the longitudinal center position; In a vehicle intercooler comprising:
In the outlet header section, plate extending in the intake flow direction of the tube, and a second plate extending in the intake flow direction of the tube is provided with opposed spaced from the plate,
The plate is provided closer to the outlet pipe in the longitudinal direction than the second plate,
The vehicular intercooler , wherein the intake upstream end of the plate is provided closer to the intake downstream end of the tube than the intake upstream end of the second plate .
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012156431A JP6011088B2 (en) | 2012-07-12 | 2012-07-12 | Intercooler for vehicle |
| PCT/JP2013/068988 WO2014010673A1 (en) | 2012-07-12 | 2013-07-11 | Vehicle intercooler |
| CN201380036648.8A CN104471342B (en) | 2012-07-12 | 2013-07-11 | Vehicle intercooler |
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| Application Number | Priority Date | Filing Date | Title |
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| JP2012156431A JP6011088B2 (en) | 2012-07-12 | 2012-07-12 | Intercooler for vehicle |
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| JP2014020588A JP2014020588A (en) | 2014-02-03 |
| JP6011088B2 true JP6011088B2 (en) | 2016-10-19 |
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| JP2012156431A Expired - Fee Related JP6011088B2 (en) | 2012-07-12 | 2012-07-12 | Intercooler for vehicle |
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| JP (1) | JP6011088B2 (en) |
| CN (1) | CN104471342B (en) |
| WO (1) | WO2014010673A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US20150013329A1 (en) * | 2013-07-11 | 2015-01-15 | Caterpillar Inc. | Inlet device for an aftercooler |
| JP6531357B2 (en) * | 2014-07-16 | 2019-06-19 | いすゞ自動車株式会社 | Corrugated fin type heat exchanger |
| US9810150B2 (en) | 2014-10-21 | 2017-11-07 | United Technologies Corporation | Heat exchanger assembly |
| JP6550970B2 (en) * | 2015-06-30 | 2019-07-31 | 三菱自動車工業株式会社 | Engine intake supply structure |
| JP6577282B2 (en) * | 2015-08-07 | 2019-09-18 | カルソニックカンセイ株式会社 | Heat exchanger |
| KR20180087986A (en) | 2017-01-26 | 2018-08-03 | 한온시스템 주식회사 | Air cooler for vehicle |
| JP6843707B2 (en) * | 2017-06-26 | 2021-03-17 | マレリ株式会社 | Heat exchanger header tank |
| US10563570B2 (en) * | 2017-08-29 | 2020-02-18 | Caterpillar Inc. | High temperature capable joint assembly for use in air-to-air aftercoolers (ATAAC) |
| US11262144B2 (en) | 2017-12-29 | 2022-03-01 | General Electric Company | Diffuser integrated heat exchanger |
| FR3082928B1 (en) * | 2018-06-21 | 2020-07-03 | Valeo Systemes Thermiques | COLLECTOR BOX AND CORRESPONDING HEAT EXCHANGER |
| US11320215B2 (en) * | 2019-06-24 | 2022-05-03 | Denso International America, Inc. | Radiator including thermal stress countermeasure |
| JP7375636B2 (en) * | 2020-03-17 | 2023-11-08 | いすゞ自動車株式会社 | intercooler |
| CN111504119B (en) * | 2020-03-30 | 2022-05-31 | 浙江龙泉凯利达汽车空调有限公司 | D-shaped collecting pipe heat exchanger |
| CN113028866B (en) * | 2021-04-13 | 2022-10-21 | 浙江银轮机械股份有限公司 | Intercooler core, air chamber assembly and intercooler |
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| JPS57100086U (en) * | 1980-12-10 | 1982-06-19 | ||
| JPS6118394U (en) * | 1984-06-30 | 1986-02-03 | カルソニックカンセイ株式会社 | Heat exchanger |
| CN100516478C (en) * | 2005-12-09 | 2009-07-22 | 株式会社电装 | Outlet/inlet piping structure for intercooler |
| US20100199955A1 (en) * | 2009-02-06 | 2010-08-12 | Paccar Inc | Charge air cooler |
| CN201568133U (en) * | 2009-12-14 | 2010-09-01 | 宋洪刚 | Aluminum plate finned intercooler |
| JP2011133198A (en) * | 2009-12-25 | 2011-07-07 | Tokyo Radiator Mfg Co Ltd | Vehicular intercooler |
| JP5764365B2 (en) * | 2010-04-23 | 2015-08-19 | カルソニックカンセイ株式会社 | Heat exchanger header tank |
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| CN104471342B (en) | 2017-05-17 |
| CN104471342A (en) | 2015-03-25 |
| JP2014020588A (en) | 2014-02-03 |
| WO2014010673A1 (en) | 2014-01-16 |
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