JP6135057B2 - Intercooler for vehicle - Google Patents
Intercooler for vehicle Download PDFInfo
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- JP6135057B2 JP6135057B2 JP2012156433A JP2012156433A JP6135057B2 JP 6135057 B2 JP6135057 B2 JP 6135057B2 JP 2012156433 A JP2012156433 A JP 2012156433A JP 2012156433 A JP2012156433 A JP 2012156433A JP 6135057 B2 JP6135057 B2 JP 6135057B2
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- intake air
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- 238000011144 upstream manufacturing Methods 0.000 claims description 30
- 238000005452 bending Methods 0.000 claims description 7
- 230000002093 peripheral effect Effects 0.000 description 4
- 238000013459 approach Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000009795 derivation Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
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
- F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape
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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円筒状の入口パイプ部、及びコア部の吸気上流側に取り付けられる縦長中空状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中空状の出口ヘッダー部、及びエンジン側に接続される円筒状の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曲面中空状の入口連結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曲面中空状の出口連結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。 Generally, an intercooler for a vehicle includes a core portion in which a plurality of tubes for circulating intake air are arranged in the vehicle width direction, a cylindrical inlet pipe portion connected to the supercharger side, and an intake upstream side of the core portion An intake air intake portion having a vertically long hollow inlet header portion attached to the intake portion, a vertically long hollow outlet header portion attached to the intake downstream side of the core portion, and a cylindrical outlet pipe portion connected to the engine side And a derivation unit. The inlet pipe portion and the inlet header portion of the intake air introduction portion are connected by a curved hollow inlet connection portion, and the outlet header portion and the outlet pipe portion of the intake air outlet portion are connected by a curved hollow outlet connection portion. Has been. Such a vehicle intercooler is described in Patent Document 1, for example.
ところで、吸気の冷却効率を向上するには、各チューブ内の吸気流速を均一化することが好ましい。しかしながら、従来の車両用インタークーラの吸気導入部は、入口連結部の上部外壁の縦断面形状が吸気上流側から吸気下流側に至る全域において、外周側を斜めに切り欠いた逆Ｖ字状に形成されている（図２中の破線Ａ参照）。 By the way, in order to improve the cooling efficiency of the intake air, it is preferable to make the intake air flow velocity in each tube uniform. However, the intake section of the conventional vehicle intercooler has an inverted V-shape in which the vertical cross-sectional shape of the upper outer wall of the inlet connecting section is cut out at an outer peripheral side obliquely in the entire region from the intake upstream side to the intake downstream side. It is formed (see broken line A in FIG. 2).
そのため、入口連結部の吸気流路は上方側ほど狭くなり、上方のチューブへの吸気の流れ込みが阻害されることで、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、各チューブ内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。 Therefore, the intake flow path of the inlet connection portion becomes narrower toward the upper side, and the flow of intake air into the upper tubes is inhibited, thereby making the intake air flow velocity in each tube non-uniform. As a result, the intake air flow rate in 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横方向に配置したコア部と、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中空状の入口ヘッダー部、筒状の入口パイプ部、及び該入口ヘッダー部と該入口パイプ部とを連結する中空状の入口連結部を有する吸気導入部と、を備える車両用インタークーラにおいて、前記入口連結部は、吸気下流側の前記入口ヘッダー部との接続部から該接続部より吸気上流側の所定部位に至るまでの全域において、その上部外壁の縦断面形状を上方に突出させた円弧状に形成されていることを特徴とする。 In order to achieve the above object, an intercooler for a vehicle according to the present invention includes a core portion in which a plurality of tubes that circulate intake air to an engine are disposed in a lateral direction, and an air intake upstream side of the core portion. A vehicle interface comprising: a hollow inlet header portion for introducing intake air; a cylindrical inlet pipe portion; and an intake air inlet portion having a hollow inlet connecting portion for connecting the inlet header portion and the inlet pipe portion. In the cooler, the inlet connecting portion protrudes upward in the vertical cross-sectional shape of the upper outer wall in the entire region from the connecting portion with the inlet header portion on the intake downstream side to the predetermined portion on the intake upstream side from the connecting portion. It is characterized by being formed in a circular arc shape.
また、前記入口連結部は、吸気上流側から吸気下流側の少なくとも一箇所以上を屈曲して形成され、かつ、その屈曲位置に曲率を小さくする入口Ｒ部が設けられてもよい。 The inlet connecting portion may be formed by bending at least one portion from the intake upstream side to the intake downstream side, and an inlet R portion that reduces the curvature may be provided at the bent position.
また、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中空状の出口ヘッダー部、筒状の出口パイプ部、及び該出口ヘッダー部と該出口パイプ部とを連結する中空状の出口連結部を有する吸気導出部をさらに備え、前記出口連結部は、吸気上流側の前記出口ヘッダー部との接続部から該接続部より吸気下流側の所定部位に至るまでの全域において、その上部外壁の縦断面形状を上方に突出させた円弧状に形成されてもよい。 Further, a hollow outlet header portion that is attached to the intake downstream side of the core portion and receives intake air from the tube, a cylindrical outlet pipe portion, and a hollow shape that connects the outlet header portion and the outlet pipe portion. The outlet connecting portion further has an outlet connecting portion, and the outlet connecting portion is connected to the outlet header portion on the intake upstream side from the connecting portion to a predetermined portion on the intake downstream side. You may form in the circular arc shape which made the longitudinal cross-sectional shape of the upper outer wall protrude upwards.
また、前記出口連結部は、吸気上流側から吸気下流側の少なくとも一箇所以上を屈曲して形成され、かつ、その屈曲位置に曲率を小さくする出口Ｒ部が設けられてもよい。 The outlet connecting portion may be formed by bending at least one portion from the intake upstream side to the intake downstream side, and an outlet R portion that reduces the curvature may be provided at the bent position.
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１〜３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. 1-3, 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間に介装された図示しない複数のアウターフィンと、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 for circulating the intake air, a plurality of outer fins (not shown) interposed between the tubes 11, and a plurality of holes (not shown) formed through the cores 10. A vertically long inlet plate 13 for inserting and fixing the intake upstream end of the tube 11 and a vertically long outlet plate 14 for inserting and fixing the intake downstream end of each tube 11 in a plurality of holes (not shown) formed through therethrough. ing. 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（不図示）に接続されて車両前後方向に延在する略円筒状の入口パイプ部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中空状の入口連結部２３とを備えている。本実施形態において、入口パイプ部２１と入口連結部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。また、入口ヘッダー部２２は、その外壁面が何れも図示しないシャシフレームや周辺部品と干渉しないように、下方側を縮小して形成されている。 The intake air introduction part 20 is connected to an intake pipe (not shown) on the supercharger side and extends in the vehicle front-rear direction, and a vertically long pipe attached to the inlet plate 13 of the core part 10. A hollow inlet header portion 22 and a hollow inlet connecting portion 23 that smoothly connects the inlet pipe portion 21 and the inlet header portion 22 are provided. In the present embodiment, the connection position between the inlet pipe portion 21 and the inlet connecting portion 23 is eccentric above the center position in the longitudinal direction (vertical direction) of the inlet header portion 22. Further, the inlet header portion 22 is formed by reducing the lower side so that the outer wall surface does not interfere with a chassis frame and peripheral parts (not shown).
吸気導出部３０は、エンジン側の吸気管（不図示）に接続された車両前後方向に延在する略円筒状の出口パイプ部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中空状の出口連結部３３とを備えている。本実施形態において、出口パイプ部３１と出口連結部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。また、出口ヘッダー部３２は、その外壁面が何れも図示しないシャシフレームや周辺部品と干渉しないように、下方側を縮小して形成されている。 The intake air outlet 30 is a substantially cylindrical outlet pipe portion 31 extending in the vehicle front-rear direction connected to an intake pipe (not shown) on the engine side, and a vertically long hollow shape attached to the outlet plate 14 of the core portion 10. The outlet header portion 32 and a hollow outlet connecting portion 33 that smoothly connects the outlet pipe portion 31 and the outlet header portion 32 are provided. In the present embodiment, the connection position between the outlet pipe portion 31 and the outlet coupling portion 33 is eccentric above the center position in the longitudinal direction (vertical direction) of the outlet header portion 32. Further, the outlet header portion 32 is formed by reducing the lower side so that the outer wall surface does not interfere with a chassis frame and peripheral parts (not shown).
次に、図２，３に基づいて、本実施形態の入口連結部２３の詳細構成を説明する。 Next, based on FIG.2, 3, the detailed structure of the entrance connection part 23 of this embodiment is demonstrated.
図２（ａ）に示すように、入口連結部２３は、吸気上流端を入口パイプ部２１に連結された直線中空状の入口上流側直線部２３ａと、吸気下流端を入口ヘッダー部２２の側面に連結された曲面中空状の入口下流側曲面部２３ｂと、これら入口上流側直線部２３ａ及び入口下流側曲面部２３ｂを連結する直線中空状の入口中間直線部２３ｃとを備えている。 As shown in FIG. 2 (a), the inlet connecting portion 23 includes a straight hollow inlet upstream straight portion 23a in which the intake upstream end is connected to the inlet pipe portion 21, and an intake downstream end on the side surface of the inlet header portion 22. A curved hollow inlet downstream curved surface portion 23b connected to each other, and a linear hollow inlet intermediate straight portion 23c connecting the inlet upstream straight portion 23a and the inlet downstream curved surface portion 23b.
入口上流側直線部２３ａは、コア部１０の背面側に配置されたラジエータ６０との干渉を避けるように、その軸方向を入口パイプ部２１の軸方向に対して傾斜させている。入口中間直線部２３ｃは、その外周面がラジエータ６０の側面と平行になるように、軸方向を車両前後方向に向けている。すなわち、入口上流側直線部２３ａと入口中間直線部２３ｃとの連結部は所定の角度で屈曲する（図２（ａ）中の領域Ａ参照）。 The inlet upstream straight portion 23 a is inclined in the axial direction with respect to the axial direction of the inlet pipe portion 21 so as to avoid interference with the radiator 60 disposed on the back side of the core portion 10. The entrance intermediate linear portion 23c has its axial direction directed in the vehicle front-rear direction so that the outer peripheral surface thereof is parallel to the side surface of the radiator 60. That is, the connecting portion between the inlet upstream straight portion 23a and the inlet intermediate straight portion 23c is bent at a predetermined angle (see region A in FIG. 2A).
さらに、この屈曲位置には、図２（ｂ）に示すように、吸気流路の曲率を小さくする入口Ｒ部２３ｄが設けられている。これにより、入口上流側直線部２３ａ及び入口中間直線部２３ｃは、吸気上流側から吸気下流側に至る全域において、吸気流路が全体的になだらかに形成されて、吸気の流れを促進することができる。 Further, as shown in FIG. 2B, an inlet R portion 23d for reducing the curvature of the intake flow path is provided at this bent position. As a result, the inlet upstream straight portion 23a and the inlet intermediate straight portion 23c are formed so that the intake air flow path is gently formed in the entire region from the intake upstream side to the intake downstream side, thereby promoting the flow of intake air. it can.
入口下流側曲面部２３ｂは、吸気上流側から吸気下流側に向かい車両内側に湾曲する曲面状に形成されている。また、図３に示すように、入口下流側曲面部２３ｂの上部外壁２３ｅは、上方側における吸気の流路容積を確保するように、曲面開始位置の直上流側（所定位置）から入口ヘッダー部２２との連結位置に至る全域において、その縦断面形状を上方に突出させた円弧状に形成されている。さらに、入口下流側曲面部２３ｂにおける入口ヘッダー部２２との連結部は、入口ヘッダー部２２に向かうに従い拡張して形成されている（図３中の領域Ｂ参照）。すなわち、上部外壁２３ｅの吸気下流端部は、入口ヘッダー部２２に近づくに従い上方に高くなるように形成されている。これにより、入口下流側曲面部２３ｂは、その上方側における吸気の流路容積が大きく確保されて、入口ヘッダー部２２内の上部領域から上方のチューブ１１への吸気の流入を促進することができる。 The inlet downstream curved surface portion 23b is formed in a curved shape that curves inward from the intake upstream side toward the intake downstream side. Further, as shown in FIG. 3, the upper outer wall 23e of the inlet downstream curved surface portion 23b has an inlet header portion from the upstream side (predetermined position) of the curved surface start position so as to secure the intake flow passage volume on the upper side. 22 is formed in an arc shape in which the longitudinal cross-sectional shape protrudes upward in the entire region up to the connection position with 22. Furthermore, the connection part with the inlet header part 22 in the inlet downstream curved surface part 23b is extended and formed toward the inlet header part 22 (refer area | region B in FIG. 3). That is, the intake downstream end portion of the upper outer wall 23e is formed so as to become higher upward as it approaches the inlet header portion 22. As a result, the inlet downstream curved surface portion 23b has a large intake flow volume on the upper side thereof, and can promote the inflow of intake air from the upper region in the inlet header portion 22 into the upper tube 11. .
なお、詳細な説明及び図示は省略するが、出口連結部３３の形状も入口連結部２３と略同一に形成されている。すなわち、出口連結部３３の出口上流側曲面部３３ｂにおける上部外壁は、出口ヘッダー部３２との連結位置から曲面終端位置の直下流側（所定位置）に至る全域において、その縦断面形状を上方に突出させた円弧状に形成され、かつ、その吸気上流端部を出口ヘッダー部３２に近づくに従い上方に高くなるように形成されている。また、出口連結部３３の出口下流側直線部３３ａと出口中間直線部３３ｃとの連結部は所定の角度で屈曲し、かつ、その屈曲位置には吸気流路の曲率を小さくする出口Ｒ部３３ｂ（図２（ａ）参照）が設けられている。これにより、上方のチューブ１１から出口ヘッダー部３２内、及び出口ヘッダー部３２から出口連結部３３を介して出口パイプ部３１への吸気の流れが促進される。 Although the detailed description and illustration are omitted, the shape of the outlet connecting portion 33 is also substantially the same as that of the inlet connecting portion 23. That is, the upper outer wall of the outlet upstream curved surface portion 33b of the outlet connecting portion 33 has its longitudinal cross-sectional shape upward in the entire region from the connecting position with the outlet header portion 32 to the downstream side (predetermined position) of the curved surface end position. It is formed in a projecting arc shape, and is formed so that its intake upstream end becomes higher upward as it approaches the outlet header portion 32. Further, the connecting portion between the outlet downstream straight portion 33a and the outlet intermediate straight portion 33c of the outlet connecting portion 33 is bent at a predetermined angle, and the outlet R portion 33b that reduces the curvature of the intake passage at the bent position. (See FIG. 2A). Thereby, the flow of the intake air from the upper tube 11 into the outlet header portion 32 and from the outlet header portion 32 to the outlet pipe portion 31 through the outlet connecting portion 33 is promoted.
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.
吸気導入部２０において、入口連結部２３の入口下流側曲面部２３ｂにおける上部外壁２３ｅは、曲面開始位置の直上流側から入口ヘッダー部２２との連結位置に至る全域において、その縦断面形状を上方に突出させた円弧状に形成され、かつ、その吸気下流端部を入口ヘッダー部２２に近づくに従い上方に高くなるように形成されている。すなわち、入口連結部２３の入口下流側曲面部２３ｂは、その上方側における吸気の流路容積を大きく確保したことで、図３中に破線で示す従来の形状に比べて圧損が低減されて、入口ヘッダー部２２内の上部領域から上方のチューブ１１への吸気の流入が促進される。 In the intake air introduction portion 20, the upper outer wall 23 e of the inlet downstream curved surface portion 23 b of the inlet connecting portion 23 has its longitudinal cross-sectional shape upward in the entire region from the upstream side of the curved surface starting position to the connecting position with the inlet header portion 22. And is formed so that its downstream end portion of the intake air becomes higher upward as it approaches the inlet header portion 22. That is, the inlet downstream curved surface portion 23b of the inlet connecting portion 23 has a large intake flow path volume on the upper side thereof, so that the pressure loss is reduced compared to the conventional shape shown by the broken line in FIG. Inflow of intake air from the upper region in the inlet header portion 22 to the upper tube 11 is promoted.
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、入口連結部２３の入口上流側直線部２３ａと入口中間直線部２３ｃとの連結部は所定の角度で屈曲すると共に、その屈曲位置には吸気流路の曲率を小さくする入口Ｒ部２３ｄが設けられている。すなわち、屈曲位置に入口Ｒ部２３ｄを設けたことで、入口連結部２３の吸気流路は全体的になだらかに形成されている。 Further, the connecting portion between the inlet upstream straight portion 23a and the inlet intermediate straight portion 23c of the inlet connecting portion 23 is bent at a predetermined angle, and an inlet R portion 23d for reducing the curvature of the intake passage is provided at the bent position. Is provided. That is, by providing the inlet R portion 23d at the bent position, the intake flow path of the inlet connecting portion 23 is formed smoothly overall.
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、入口パイプ部２１から入口連結部２３を介した入口ヘッダー部２２への吸気の流れを効果的に促進することができる。 Therefore, according to the vehicle intercooler 1 of the present embodiment, the flow of intake air from the inlet pipe portion 21 to the inlet header portion 22 via the inlet connecting portion 23 can be effectively promoted.
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、上部外壁２３ｅが上方に突出する円弧状に形成される範囲は、入口下流側曲面部２３ｂにおける入口ヘッダー部２２との連結位置から曲面開始位置の直上流側までとしたが、入口ヘッダー部２２との連結位置から所定範囲（ゼロよりも大きい範囲）であればよく、さらに入口中間直線部２３ｃや入口上流側直線部２３ａの全域まで延長してもよい。この場合も上述の実施形態と同様の作用効果を奏することができる。 For example, the range in which the upper outer wall 23e is formed in an arc shape protruding upward is from the connection position with the inlet header portion 22 in the inlet downstream curved surface portion 23b to the upstream side of the curved surface start position. 22 may be within a predetermined range (a range larger than zero) from the connection position with 22 and may further extend to the entire region of the inlet intermediate straight portion 23c and the inlet upstream straight portion 23a. In this case, the same effects as those of the above-described embodiment can be obtained.
また、入口パイプ部２１と入口連結部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、入口連結部２３の下部外壁の縦断面形状を下方に突出させた円弧状に形成すればよい。 Moreover, although the connection position of the inlet pipe part 21 and the inlet connection part 23 was demonstrated as what deviates upwards rather than the longitudinal direction (up-down direction) center position of the inlet header part 22, you may make it decentered below. . In this case, what is necessary is just to form in the circular arc shape which protruded below the longitudinal cross-sectional shape of the lower outer wall of the entrance connection part 23. FIG.
また、入口連結部２３を屈曲させる部分は一カ所に限定されず、複数箇所を屈曲させてもよい。この場合は、全ての屈曲位置に吸気流路の曲率を小さくするＲ部を設ければよい。 Moreover, the part which bends the entrance connection part 23 is not limited to one place, You may bend several places. In this case, an R portion for reducing the curvature of the intake flow path may be provided at all the bent positions.
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 入口連結部
２３ｄ 入口Ｒ部
２３ｅ 上部外壁
３０ 吸気導出部
３１ 出口パイプ部
３２ 出口ヘッダー部
３３ 出口連結部
３３ｄ 出口Ｒ部
DESCRIPTION OF SYMBOLS 1 Vehicle intercooler 10 Core part 11 Tube 20 Intake inlet part 21 Inlet pipe part 22 Inlet header part 23 Inlet connection part 23d Inlet R part 23e Upper outer wall 30 Intake lead-out part 31 Outlet pipe part 32 Outlet header part 33 Outlet connection part 33d Exit R
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中空状の入口ヘッダー部、筒状の入口パイプ部、及び該入口ヘッダー部と該入口パイプ部とを連結する中空状の入口連結部を有する吸気導入部と、を備える車両用インタークーラにおいて、
前記入口連結部は、吸気上流部が前記入口パイプ部と連結された直線中空状の入口上流直線部と、前記入口上流直線部と前記入口ヘッダー部との間に設けられた直線中空状の入口中間直線部と、前記入口上流直線部と前記入口中間直線部とを連結する曲線中空状の連結屈曲部と、を有し、かつ、吸気下流側の前記入口ヘッダー部との接続部から該接続部より吸気上流側の所定部位に至るまでの全域において、その上部外壁の縦断面形状を上方に突出させた円弧状に形成され、
前記連結屈曲部は、前記連結屈曲部の屈曲方向内側の曲率が前記連結屈曲部の屈曲方向外側の曲率よりも小さく形成さ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 in which a plurality of tubes that distribute the intake air to the engine are arranged in a lateral direction;
A hollow inlet header portion that is attached to the intake upstream side of the core portion and introduces intake air into the tube, a cylindrical inlet pipe portion, and a hollow inlet that connects the inlet header portion and the inlet pipe portion In an intercooler for a vehicle provided with an intake air introduction portion having a connecting portion,
The inlet connecting portion includes a straight hollow inlet upstream straight portion in which an intake upstream portion is connected to the inlet pipe portion, and a straight hollow inlet provided between the inlet upstream straight portion and the inlet header portion. An intermediate straight portion, a curved hollow connecting bent portion connecting the inlet upstream straight portion and the inlet intermediate straight portion, and the connection from the inlet header portion on the intake downstream side Is formed in an arc shape in which the vertical cross-sectional shape of the upper outer wall protrudes upward in the entire region from the portion to the predetermined portion on the upstream side of the intake,
The vehicle intercooler is characterized in that the connecting bending portion is formed such that a curvature inside the bending direction of the connecting bending portion is smaller than a curvature outside the bending direction of the connecting bending portion .
前記出口連結部は、吸気上流側の前記出口ヘッダー部との接続部から該接続部より吸気下流側の所定部位に至るまでの全域において、その上部外壁の縦断面形状を上方に突出させた円弧状に形成されている請求項１に記載の車両用インタークーラ。 A hollow outlet header portion that is attached to the intake downstream side of the core portion and into which intake air flows from the tube, a cylindrical outlet pipe portion, and a hollow outlet that connects the outlet header portion and the outlet pipe portion An intake lead-out part having a connecting part;
The outlet connecting portion is a circle in which the vertical cross-sectional shape of the upper outer wall protrudes upward in the entire region from the connecting portion with the outlet header portion on the intake upstream side to the predetermined portion on the intake downstream side from the connecting portion. The intercooler for vehicles according to claim 1 formed in the shape of an arc.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012156433A JP6135057B2 (en) | 2012-07-12 | 2012-07-12 | Intercooler for vehicle |
| CN201380036646.9A CN104471341A (en) | 2012-07-12 | 2013-07-11 | Vehicle intercooler |
| PCT/JP2013/068990 WO2014010675A1 (en) | 2012-07-12 | 2013-07-11 | Vehicle intercooler |
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| Application Number | Priority Date | Filing Date | Title |
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| JP2012156433A JP6135057B2 (en) | 2012-07-12 | 2012-07-12 | Intercooler for vehicle |
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| JP2014020590A JP2014020590A (en) | 2014-02-03 |
| JP6135057B2 true JP6135057B2 (en) | 2017-05-31 |
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| JP2012156433A Expired - Fee Related JP6135057B2 (en) | 2012-07-12 | 2012-07-12 | Intercooler for vehicle |
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| JP (1) | JP6135057B2 (en) |
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| JP6531357B2 (en) * | 2014-07-16 | 2019-06-19 | いすゞ自動車株式会社 | Corrugated fin type heat exchanger |
| US10539377B2 (en) | 2017-01-12 | 2020-01-21 | Hamilton Sundstrand Corporation | Variable headers for heat exchangers |
| US10845135B2 (en) * | 2018-03-16 | 2020-11-24 | Hamilton Sundstrand Corporation | Inlet header duct design features |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59137795A (en) * | 1983-01-28 | 1984-08-07 | Hino Motors Ltd | Intercooler for turbosupercharged engine |
| JPH02124225U (en) * | 1989-03-23 | 1990-10-12 | ||
| US5095882A (en) * | 1990-05-29 | 1992-03-17 | Paccar Inc. | Cleanable air-to-air cooling system |
| JP3675348B2 (en) * | 2001-03-23 | 2005-07-27 | 株式会社デンソー | Heat exchanger |
| JP2003314990A (en) * | 2002-04-24 | 2003-11-06 | Mitsubishi Fuso Truck & Bus Corp | Cooling device |
| DE10238205A1 (en) * | 2002-08-21 | 2004-03-04 | Bayerische Motoren Werke Ag | Heat exchanger especially compressor inter-cooler for combustion engine has cooling g pies, guide frame, with inflow and outflow apertures and chambers and protuberance in chamber wall |
| DE10302948A1 (en) * | 2003-01-24 | 2004-08-05 | Behr Gmbh & Co. Kg | Heat exchanger, in particular exhaust gas cooler for motor vehicles |
| JP2005077012A (en) * | 2003-09-01 | 2005-03-24 | Nissan Motor Co Ltd | Radiator |
| WO2005031239A1 (en) * | 2003-10-02 | 2005-04-07 | Behr Gmbh & Co. Kg | Charge-air cooler for motor vehicles |
| JP2006118436A (en) * | 2004-10-21 | 2006-05-11 | Usui Kokusai Sangyo Kaisha Ltd | Bonnet for egr gas cooling device |
| JP2006125731A (en) * | 2004-10-28 | 2006-05-18 | Calsonic Kansei Corp | Vehicular heat exchanger |
| JP4622962B2 (en) * | 2005-11-30 | 2011-02-02 | 株式会社デンソー | Intercooler inlet / outlet piping structure |
| DE102006032205A1 (en) * | 2006-07-12 | 2008-01-17 | Modine Manufacturing Co., Racine | Heat exchanger with coupling connection and coupling connection |
| JP2010038477A (en) * | 2008-08-07 | 2010-02-18 | Tokyo Radiator Mfg Co Ltd | Porous tube for heat exchange |
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| WO2014010675A1 (en) | 2014-01-16 |
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