JP5866798B2 - Intercooler - Google Patents

Intercooler Download PDF

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Publication number
JP5866798B2
JP5866798B2 JP2011112903A JP2011112903A JP5866798B2 JP 5866798 B2 JP5866798 B2 JP 5866798B2 JP 2011112903 A JP2011112903 A JP 2011112903A JP 2011112903 A JP2011112903 A JP 2011112903A JP 5866798 B2 JP5866798 B2 JP 5866798B2
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inflow side
inlet pipe
core connection
connection portion
side core
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JP2012241627A (en
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聡 竹中
聡 竹中
一秀 高田
一秀 高田
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Isuzu Motors Ltd
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Isuzu Motors Ltd
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • 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

Description

本発明は、過給機からエンジン本体に供給する吸気ガスを冷却するインタークーラに関する。   The present invention relates to an intercooler that cools intake gas supplied from a supercharger to an engine body.

エンジンの出力向上を図る目的からエンジンの吸気系に過給機を装着する過給機付エンジンにおいては、過給機で過給された吸気ガス（圧縮空気）が高温となるため、この高温の吸気ガスをエンジンの燃焼室にそのまま供給してしまうと、充填効率の低下やノッキング（ガソリンエンジンの場合）の問題が生じ得る。   In a turbocharged engine in which a supercharger is installed in the intake system of the engine for the purpose of improving engine output, the intake gas (compressed air) supercharged by the supercharger becomes high temperature. If the intake gas is supplied to the combustion chamber of the engine as it is, problems such as a decrease in charging efficiency and knocking (in the case of a gasoline engine) may occur.

このため、過給機付エンジンにおいては、過給機により過給された吸気ガスを冷却するためのインタークーラをエンジンの吸気系に装着するようにしている（例えば、特許文献１、２参照）。   For this reason, in an engine with a supercharger, an intercooler for cooling the intake gas supercharged by the supercharger is mounted on the intake system of the engine (see, for example, Patent Documents 1 and 2). .

インタークーラは、例えば、吸気流入口を有する流入側ヘッダと、吸気吐出口を有する吐出側ヘッダと、これら流入側ヘッダと吐出側ヘッダとの間に配設された熱交換用のコアとから主に構成される。   The intercooler includes, for example, an inflow side header having an intake air inlet, a discharge side header having an intake air discharge port, and a heat exchange core disposed between the inflow side header and the discharge side header. Configured.

トラック用のエンジンの場合は、インタークーラがエンジンの前方に搭載されており、走行による空気流或いはクーリングファンの吸い込みによる空気流がインタークーラに流れ込むことにより、過給機による過給で高温となった吸気ガスが冷やされる。また、乗用車のエンジンにおいても搭載位置は若干異なるものの、インタークーラの前面に走行による空気流があたるようになっている。   In the case of a truck engine, an intercooler is mounted in front of the engine, and airflow from running or suction of a cooling fan flows into the intercooler, resulting in high temperature due to supercharging by the supercharger. Intake gas is cooled. In addition, although the mounting position of a passenger car engine is slightly different, an airflow caused by traveling is applied to the front surface of the intercooler.

特開２０１０−２７５９８２号公報JP 2010-275982 A 特開２０１０−２２３５０８号公報JP 2010-223508 A

このようなインタークーラにおける圧損の一部はコアの圧損であるが、コアの圧損を低減するには、例えばコアのチューブ本数を増やすことが考えられる。しかしながら、コアのチューブ本数を増やすと、インタークーラが大型化し、更にはエンジン及びエンジンに装着される各種装置類のレイアウト変更が必要となることがある。そのため、コアのチューブ本数を増やす方法によりコアの圧損を低減する方法の採用は困難であるといえる。一方、流入側ヘッダは、形状変更により圧損を低減する余地があると思われる。   A part of the pressure loss in such an intercooler is the pressure loss of the core. In order to reduce the pressure loss of the core, for example, it is conceivable to increase the number of core tubes. However, when the number of core tubes is increased, the size of the intercooler may increase, and the layout of the engine and various devices attached to the engine may need to be changed. Therefore, it can be said that it is difficult to adopt a method for reducing the core pressure loss by increasing the number of core tubes. On the other hand, the inflow side header seems to have room to reduce pressure loss by changing the shape.

そこで、本発明の目的は、エンジン及びエンジンに装着される各種装置類のレイアウト変更を行うことなく、流入側ヘッダの圧損を効果的に低減することにある。   Accordingly, an object of the present invention is to effectively reduce the pressure loss of the inflow side header without changing the layout of the engine and various devices mounted on the engine.

上述の目的を達成するために、本発明は、吸気流入口を有する流入側ヘッダと、吸気吐出口を有する吐出側ヘッダと、前記流入側ヘッダと前記吐出側ヘッダとの間に配設された熱交換用のコアとを備えるインタークーラにおいて、前記流入側ヘッダは、前記コアに接続され、前記コアの一端部に沿って延びる流入側コア接続部と、前記流入側コア接続部の後部に形成されて前記流入側コア接続部と連通すると共に、前記流入側コア接続部から筒状かつ背面側に延び、先端に前記吸気流入口が形成された入口パイプ部とを有し、前記流入側コア接続部と前記入口パイプ部との連通部分の背面側内壁面を前記流入側コア接続部の背面位置よりも前側に湾曲させ、Ｒ形状としたものである。 In order to achieve the above-mentioned object, the present invention is disposed between an inflow side header having an intake inflow port, a discharge side header having an intake discharge port, and the inflow side header and the discharge side header. in the intercooler and a core of heat exchange, the inflow-side header is connected to the core, the inlet-side core connecting portion extending along one end portion of the core, formed in the rear of the inflow-side core connecting portion The inflow side core connection part, and an inlet pipe part that extends from the inflow side core connection part to the rear side of the cylinder and has the intake air inlet formed at a tip thereof. The inner wall surface on the back surface side of the communication portion between the connecting portion and the inlet pipe portion is curved to the front side with respect to the back surface position of the inflow side core connecting portion to form an R shape.

前記流入側コア接続部と前記入口パイプ部との連通部分の背面が、前記流入側コア接続部の背面位置に対して前側に湾曲して凹曲面を形成し、前記流入側コア接続部と前記入口パイプ部との連通部分の前面を凸曲面状に湾曲させることで、前記流入側コア接続部と前記入口パイプ部との連通部分の前面側内壁面をＲ形状としたものであっても良い。 The back surface of the communication portion between the inflow side core connection portion and the inlet pipe portion is curved forward with respect to the back surface position of the inflow side core connection portion to form a concave curved surface, and the inflow side core connection portion and the The front side inner wall surface of the communicating part between the inflow side core connecting part and the inlet pipe part may be formed in an R shape by curving the front surface of the communicating part with the inlet pipe part into a convex curved surface. .

前記流入側コア接続部と前記入口パイプ部との連通部分の背面を凹曲面状に湾曲させることで、前記流入側コア接続部と前記入口パイプ部との連通部分のコア接続部長手方向内壁面をＲ形状としても良い。 The inner wall surface in the longitudinal direction of the core connection portion of the communication portion between the inflow side core connection portion and the inlet pipe portion by curving the back surface of the communication portion between the inflow side core connection portion and the inlet pipe portion into a concave curved surface May be R-shaped.

前記入口パイプ部のコア接続部長手方向の径を当該コア接続部長手方向に直交する方向の径に対して大きく形成しても良い。 You may form the diameter of the core connection part longitudinal direction of the said inlet pipe part largely with respect to the diameter of the direction orthogonal to the said core connection part longitudinal direction .

本発明によれば、エンジン及びエンジンに装着される各種装置類のレイアウト変更を行うことなく、流入側ヘッダの圧損を効果的に低減することができるという優れた効果を奏する。   According to the present invention, it is possible to effectively reduce the pressure loss of the inflow side header without changing the layout of the engine and various devices attached to the engine.

本発明の一実施形態に係るインタークーラの背面図である。It is a rear view of the intercooler concerning one embodiment of the present invention. 本発明の一実施形態に係るインタークーラの側面図である。It is a side view of the intercooler concerning one embodiment of the present invention. 図２のＡ−Ａ線断面図である。It is the sectional view on the AA line of FIG. 本発明の一実施形態に係るインタークーラを装着した過給機付エンジンの構成図である。It is a lineblock diagram of an engine with a supercharger equipped with an intercooler concerning one embodiment of the present invention.

以下、本発明の好適な実施形態を添付図面に基づいて詳述する。   DESCRIPTION OF EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

先ず、本実施形態に係るインタークーラが装着されるエンジンについて図４を用いて説明する。なお、図４中、矢印Ｉは吸気ガスの流れを示し、矢印Ｅは排気ガスの流れを示し、矢印Ａｃは走行による空気流或いはクーリングファンの吸い込みによる空気流を示している。   First, an engine to which an intercooler according to this embodiment is mounted will be described with reference to FIG. In FIG. 4, arrow I indicates the flow of intake gas, arrow E indicates the flow of exhaust gas, and arrow Ac indicates the air flow due to running or the air flow due to suction of a cooling fan.

図４に示すエンジン１は、例えばディーゼルエンジンであって、トラック等の車両に搭載されるものである。なお、エンジン１は、ディーゼルエンジンには限定はされず、ガソリンエンジン等であっても良い。   An engine 1 shown in FIG. 4 is a diesel engine, for example, and is mounted on a vehicle such as a truck. The engine 1 is not limited to a diesel engine, and may be a gasoline engine or the like.

図４に示すように、エンジン１は、エンジン本体２と、エンジン本体２の吸気ポートに接続された吸気マニホールド３と、吸気マニホールド３に接続された吸気管４と、吸気管４に配設されエンジン本体２に供給する吸気ガスを過給する過給機５のコンプレッサ５ｃと、コンプレッサ５ｃよりも吸気後流側の吸気管４に配設され吸気ガスを冷却する空冷式のインタークーラ１０と、エンジン本体２の排気ポートに接続された排気マニホールド６と、排気マニホールド６に接続された排気管７と、排気管７に配設されコンプレッサ５ｃを駆動する過給機５のタービン５ｔと、エンジン本体２内を循環するエンジン冷却水を冷却する空冷式のラジエータ８と、エンジン本体２により回転駆動されるクーリングファン（冷却ファン）９とを備える。   As shown in FIG. 4, the engine 1 is disposed in the engine body 2, the intake manifold 3 connected to the intake port of the engine body 2, the intake pipe 4 connected to the intake manifold 3, and the intake pipe 4. A compressor 5c of a supercharger 5 that supercharges intake gas to be supplied to the engine body 2, an air-cooled intercooler 10 that is disposed in the intake pipe 4 on the intake downstream side of the compressor 5c and cools the intake gas, An exhaust manifold 6 connected to an exhaust port of the engine body 2, an exhaust pipe 7 connected to the exhaust manifold 6, a turbine 5t of a supercharger 5 disposed in the exhaust pipe 7 and driving a compressor 5c, an engine body An air-cooled radiator 8 that cools engine coolant circulating in the engine 2 and a cooling fan (cooling fan) 9 that is rotationally driven by the engine body 2 are provided.

図４に示すエンジン１では、エンジン本体２の前方から後方に向かって順に、インタークーラ１０、ラジエータ８、クーリングファン９（エンジン本体２）が一直線上に配設されている。そのため、図４に示すエンジン１においては、走行による空気流或いはクーリングファン９の吸い込みによる空気流Ａｃは、インタークーラ１０を通過し、さらにラジエータ８を通過してクーリングファン９に流れるようになっている。   In the engine 1 shown in FIG. 4, an intercooler 10, a radiator 8, and a cooling fan 9 (engine body 2) are arranged on a straight line in order from the front to the rear of the engine body 2. For this reason, in the engine 1 shown in FIG. 4, the air flow Ac due to traveling or the air flow Ac due to the suction of the cooling fan 9 passes through the intercooler 10 and further passes through the radiator 8 and flows to the cooling fan 9. Yes.

次に、本実施形態に係るインタークーラ１０について図１から図３を用いて説明する。   Next, the intercooler 10 according to the present embodiment will be described with reference to FIGS. 1 to 3.

図１から図３に示すように、本実施形態に係るインタークーラ１０は、吸気流入口１１を有する流入側ヘッダ１２と、吸気吐出口１３を有する吐出側ヘッダ１４と、流入側ヘッダ１２と吐出側ヘッダ１４との間に配設された熱交換用のコア１５とを備えている。コア１５は、背面視で略矩形状に形成されている。   As shown in FIGS. 1 to 3, the intercooler 10 according to the present embodiment includes an inflow side header 12 having an intake inflow port 11, a discharge side header 14 having an intake discharge port 13, an inflow side header 12, and a discharge. A heat exchange core 15 disposed between the side header 14 and the side header 14 is provided. The core 15 is formed in a substantially rectangular shape in rear view.

流入側ヘッダ１２は、コア１５に接続され、コア１５の一端部（図１中の右側）に沿って延びる流入側コア接続部１６と、流入側コア接続部１６の後部に連通され、先端に吸気流入口１１が形成された円筒状の入口パイプ部１７とから構成されている。本実施形態では、入口パイプ部１７は、流入側コア接続部１６の上部に結合されている。   The inflow side header 12 is connected to the core 15 and communicates with the inflow side core connection portion 16 extending along one end portion (right side in FIG. 1) of the core 15 and the rear portion of the inflow side core connection portion 16 at the tip. It is comprised from the cylindrical inlet pipe part 17 in which the intake inflow port 11 was formed. In the present embodiment, the inlet pipe portion 17 is coupled to the upper portion of the inflow side core connecting portion 16.

本実施形態では、流入側コア接続部１６と入口パイプ部１７との連通部分の背面（図２中の左側）を凹曲面状に湾曲させることで、流入側コア接続部１６と入口パイプ部１７との連通部分の背面側内壁面１８ａを内側に凸のＲ形状としている（図３参照）。つまり、流入側コア接続部１６と入口パイプ部１７との連通部分は、流入側コア接続部１６の背面位置よりも前側に湾曲している。即ち、流入側コア接続部１６と入口パイプ部１７との連通部分の背面を凹曲面状に湾曲させることで、流入側コア接続部１６の背面に凹部１６ａを形成すると共に、流入側コア接続部１６と入口パイプ部１７との連通部分内に内側に突出する凸部１６ｂを形成している。凹部１６ａは、流入側コア接続部１６の背面位置から前側に凹となっている。   In the present embodiment, the inflow side core connection portion 16 and the inlet pipe portion 17 are curved in a concave curved shape on the back surface (left side in FIG. 2) of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17. The back side inner wall surface 18a of the communicating part with the inner side is formed in an R shape convex inward (see FIG. 3). That is, the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved to the front side of the back surface position of the inflow side core connection portion 16. That is, the back surface of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved into a concave curved surface, thereby forming the recess 16a on the back surface of the inflow side core connection portion 16 and the inflow side core connection portion. A convex portion 16 b that protrudes inward is formed in a communicating portion between 16 and the inlet pipe portion 17. The concave portion 16 a is concave from the back surface position of the inflow side core connecting portion 16 to the front side.

本実施形態では、流入側コア接続部１６と入口パイプ部１７との連通部分の背面側内壁面１８ａの曲率半径Ｒを１０ｍｍから８０ｍｍの範囲で入口パイプ部１７の長手方向に対して徐々に変化させている。なお、流入側コア接続部１６と入口パイプ部１７との連通部分の背面側内壁面１８ａの曲率半径Ｒを入口パイプ部１７の長手方向に対して一定値としても良い。   In this embodiment, the curvature radius R of the back side inner wall surface 18a of the communication portion between the inflow side core connecting portion 16 and the inlet pipe portion 17 is gradually changed with respect to the longitudinal direction of the inlet pipe portion 17 in the range of 10 mm to 80 mm. I am letting. In addition, the curvature radius R of the back side inner wall surface 18 a of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 may be a constant value with respect to the longitudinal direction of the inlet pipe portion 17.

また、本実施形態では、流入側コア接続部１６と入口パイプ部１７との連通部分の前面（図２中の右側）を凸曲面状に湾曲させることで、流入側コア接続部１６と入口パイプ部１７との連通部分の前面側内壁面１８ｂを外側に凸のＲ形状としている（図３参照）。前面側内壁面１８ｂは、流入側コア接続部１６の前面位置で流入側コア接続部１６に連通されている。つまり、入口パイプ部１７は、流入側コア接続部１６の前面位置よりも前側に突出されていない。   Moreover, in this embodiment, the inflow side core connection part 16 and an inlet pipe are curved by curving the front surface (right side in FIG. 2) of the communication part of the inflow side core connection part 16 and the inlet pipe part 17 in the shape of a convex curve. The front side inner wall surface 18b of the communication portion with the portion 17 is formed in an outwardly convex R shape (see FIG. 3). The front side inner wall surface 18 b communicates with the inflow side core connection part 16 at the front surface position of the inflow side core connection part 16. That is, the inlet pipe portion 17 does not protrude forward from the front surface position of the inflow side core connecting portion 16.

流入側コア接続部１６と入口パイプ部１７との連通部分の前面側内壁面１８ｂの曲率半径は、入口パイプ部１７の長手方向に対して徐々に変化させても良く、入口パイプ部１７の長手方向に対して一定値としても良い。   The curvature radius of the front side inner wall surface 18b of the communication portion between the inflow side core connecting portion 16 and the inlet pipe portion 17 may be gradually changed with respect to the longitudinal direction of the inlet pipe portion 17. It may be a constant value with respect to the direction.

さらに、本実施形態では、流入側コア接続部１６と入口パイプ部１７との連通部分の背面を凹曲面状に湾曲させることで、流入側コア接続部１６と入口パイプ部１７との連通部分のコア接続部長手方向内壁面（上下方向内壁面）１９ａ、１９ｂを内側に凸のＲ形状としている（図２参照）。   Further, in the present embodiment, the back surface of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved into a concave curved surface so that the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved. The core connection portion longitudinal inner wall surfaces (vertical inner wall surfaces) 19a and 19b are formed in an R shape convex inward (see FIG. 2).

流入側コア接続部１６と入口パイプ部１７との連通部分のコア接続部長手方向内壁面１９ａ、１９ｂの曲率半径は、入口パイプ部１７の長手方向に対して徐々に変化させても良く、入口パイプ部１７の長手方向に対して一定値としても良い。   The curvature radii of the inner wall surfaces 19a, 19b in the longitudinal direction of the core connecting portion at the communicating portion between the inflow side core connecting portion 16 and the inlet pipe portion 17 may be gradually changed with respect to the longitudinal direction of the inlet pipe portion 17. It may be a constant value with respect to the longitudinal direction of the pipe portion 17.

なお、流入側コア接続部１６と入口パイプ部１７との連通部分の背面を凹曲面状に湾曲させることで入口パイプ部１７内の流量が減少する場合には、入口パイプ部１７の上下方向の径を左右方向の径に対して大きくすることで入口パイプ部１７内の流量を確保するようにしても良い。   When the flow rate in the inlet pipe portion 17 is reduced by curving the back surface of the communication portion between the inflow side core connecting portion 16 and the inlet pipe portion 17 in a concave curved surface, the vertical direction of the inlet pipe portion 17 is reduced. You may make it ensure the flow volume in the inlet pipe part 17 by enlarging a diameter with respect to the diameter of the left-right direction.

流入側ヘッダ１２（流入側コア接続部１６、入口パイプ部１７）は、例えばアルミニウムからなる。本実施形態では、流入側コア接続部１６及び入口パイプ部１７は、アルミニウムの鋳造により一体形成されている。   The inflow side header 12 (inflow side core connection part 16, inlet pipe part 17) consists of aluminum, for example. In this embodiment, the inflow side core connection part 16 and the inlet pipe part 17 are integrally formed by casting of aluminum.

吐出側ヘッダ１４は、コア１５に接続され、コア１５の他端部（図１中の左側）に沿って延びる吐出側コア接続部２０と、吐出側コア接続部２０の後部に連通され、先端に吸気吐出口１３が形成された円筒状の出口パイプ部２１とから構成されている。本実施形態では、出口パイプ部２１は、吐出側コア接続部２０の上部に結合されている。   The discharge-side header 14 is connected to the core 15 and communicates with a discharge-side core connection portion 20 that extends along the other end portion (left side in FIG. 1) of the core 15 and a rear portion of the discharge-side core connection portion 20. And a cylindrical outlet pipe portion 21 in which an intake / discharge port 13 is formed. In the present embodiment, the outlet pipe portion 21 is coupled to the upper portion of the discharge side core connection portion 20.

吐出側ヘッダ１４（吐出側コア接続部２０、出口パイプ部２１）は、例えばアルミニウムからなる。本実施形態では、吐出側コア接続部２０及び出口パイプ部２１は、アルミニウムの鋳造により一体形成されている。   The discharge side header 14 (discharge side core connection part 20, outlet pipe part 21) consists of aluminum, for example. In the present embodiment, the discharge side core connecting portion 20 and the outlet pipe portion 21 are integrally formed by aluminum casting.

コア１５は、一対のエンドプレート２２と、一対のエンドプレート２２間に架け渡された複数のチューブ２３と、隣接するチューブ２３間に各々設けられた複数の外気流通路２４とから構成されている。   The core 15 includes a pair of end plates 22, a plurality of tubes 23 spanned between the pair of end plates 22, and a plurality of external airflow passages 24 respectively provided between adjacent tubes 23. .

チューブ２３は、流入側ヘッダ１２から吐出側ヘッダ１４へと吸気ガスを流すためのものであって、扁平中空状のパイプからなる。外気流通路２４は、チューブ２３を流れる吸気ガスを冷却するための空気が流れる流路であり、インタークーラ１０の前面と背面とを貫通するように形成されている。また、外気流通路２４には、冷却効率を高めるためにフィン（コルゲートフィン）２５が配設されている。なお、図１では、フィン２５の一部のみを図示している。   The tube 23 is for flowing intake gas from the inflow side header 12 to the discharge side header 14 and is formed of a flat hollow pipe. The external airflow passage 24 is a flow path through which air for cooling the intake gas flowing through the tube 23 flows, and is formed so as to penetrate the front surface and the back surface of the intercooler 10. Further, fins (corrugated fins) 25 are disposed in the external airflow passage 24 in order to increase the cooling efficiency. In FIG. 1, only a part of the fin 25 is illustrated.

コア１５（エンドプレート２２、チューブ２３、フィン２５）は、例えばアルミニウムからなる。   The core 15 (end plate 22, tube 23, fin 25) is made of, for example, aluminum.

次に、本実施形態の作用を説明する。   Next, the operation of this embodiment will be described.

本実施形態では、流入側コア接続部１６と入口パイプ部１７との連通部分の背面を凹曲面状に湾曲させることで、流入側コア接続部１６と入口パイプ部１７との連通部分の背面側内壁面１８ａをＲ形状としている。このように、流入側コア接続部１６と入口パイプ部１７との連通部分の背面側内壁面１８ａをＲ形状とすることにより、図３中に矢印Ｘ１で示すように吸気ガスの主流を積極的に流入側コア接続部１６の背面側に導き（曲げ）、吸気ガスの主流の流入側コア接続部１６の前面への衝突を出来る限り避けることができる。従って、流入側ヘッダ１２内におけるエネルギー損失を少なくすることができ、流入側ヘッダ１２の圧損を低減することが可能となる。   In the present embodiment, the back surface side of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is formed by bending the back surface of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 into a concave curved surface. The inner wall surface 18a has an R shape. In this way, by making the back side inner wall surface 18a of the communication portion between the inflow side core connecting portion 16 and the inlet pipe portion 17 into an R shape, the main flow of the intake gas is positively shown as indicated by an arrow X1 in FIG. Then, it is guided (bent) to the back surface side of the inflow side core connection portion 16, and collision of the main flow of intake gas with the front surface of the inflow side core connection portion 16 can be avoided as much as possible. Therefore, the energy loss in the inflow side header 12 can be reduced, and the pressure loss of the inflow side header 12 can be reduced.

特に本実施形態では、流入側コア接続部１６と入口パイプ部１７との連通部分の背面を凹曲面状に湾曲させることで、流入側コア接続部１６と入口パイプ部１７との連通部分の背面側内壁面１８ａをＲ形状としているので、インタークーラ１０が大型化し、更にはエンジン１及びエンジン１に装着される各種装置類（特にラジエータ８）のレイアウト変更が必要となることはない。即ち、流入側コア接続部１６と入口パイプ部１７との連通部分の背面を凹曲面状に形成するのであれば、流入側コア接続部１６の前後方向幅を変更する必要はなく、インタークーラ１０の大型化を招くことはない。   In particular, in the present embodiment, the back surface of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved in a concave curved surface so that the back surface of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved. Since the side inner wall surface 18a has an R shape, the size of the intercooler 10 is increased, and further, the layout of the engine 1 and various devices (particularly the radiator 8) mounted on the engine 1 is not required. That is, if the back surface of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is formed in a concave curved surface shape, it is not necessary to change the front-rear direction width of the inflow side core connection portion 16 and the intercooler 10 Does not lead to an increase in size.

また、本実施形態では、流入側コア接続部１６と入口パイプ部１７との連通部分の前面を凸曲面状に湾曲させることで、流入側コア接続部１６と入口パイプ部１７との連通部分の前面側内壁面１８ｂをＲ形状としている。このように流入側コア接続部１６と入口パイプ部１７との連通部分の前面側内壁面１８ｂをＲ形状とすることにより、図３中に矢印Ｘ２で示すように吸気ガスが前面側内壁面１８ｂに沿って流れるようになる。吸気ガスの主流の流入側コア接続部１６の前面への衝突を和らげることで、流入側ヘッダ１２内におけるエネルギー損失を少なくすることができる。   Further, in the present embodiment, the front surface of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved into a convex curved surface so that the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved. The front side inner wall surface 18b has an R shape. Thus, by making the front side inner wall surface 18b of the communication part between the inflow side core connecting portion 16 and the inlet pipe portion 17 into an R shape, the intake gas flows into the front side inner wall surface 18b as shown by an arrow X2 in FIG. Will flow along. By reducing the collision of the mainstream of the intake gas with the front surface of the inflow side core connection portion 16, energy loss in the inflow side header 12 can be reduced.

さらに、本実施形態では、流入側コア接続部１６と入口パイプ部１７との連通部分の背面を凹曲面状に湾曲させることで、流入側コア接続部１６と入口パイプ部１７との連通部分のコア接続部長手方向内壁面（上下方向内壁面）１９ａ、１９ｂをＲ形状としている。このように流入側コア接続部１６と入口パイプ部１７との連通部分のコア接続部長手方向内壁面１９ａ、１９ｂもＲ形状とすることにより、図２中に矢印Ｙ１、Ｙ２で示すように吸気ガスの主流を流入側コア接続部１６の長手方向（上下方向）にも積極的に導く（曲げる）ことができ、吸気ガスの主流を全体的に均一に近づけることが可能になる。吸気ガスの主流が全体的に均一になることで、最大流速が下がり、流入側ヘッダ１２内のエネルギー損失が低減する。   Further, in the present embodiment, the back surface of the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved into a concave curved surface so that the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 is curved. The core connection part longitudinal direction inner wall surface (vertical direction inner wall surface) 19a, 19b is made into R shape. As described above, the inner wall surfaces 19a and 19b in the longitudinal direction of the core connection portion at the communication portion between the inflow side core connection portion 16 and the inlet pipe portion 17 are also formed in an R shape so that the intake air as shown by arrows Y1 and Y2 in FIG. The main flow of gas can be actively guided (bent) in the longitudinal direction (vertical direction) of the inflow-side core connecting portion 16, and the main flow of intake gas can be made uniform as a whole. Since the main flow of the intake gas becomes uniform as a whole, the maximum flow velocity is reduced and energy loss in the inflow side header 12 is reduced.

以上、本発明の好適な実施形態について説明したが、本発明は上述の実施形態には限定されず他の様々な実施形態を採ることが可能である。   The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments, and various other embodiments can be adopted.

１０ インタークーラ
１１ 吸気流入口
１２ 流入側ヘッダ
１３ 吸気吐出口
１４ 吐出側ヘッダ
１５ コア
１６ 流入側コア接続部
１７ 入口パイプ部
１８ａ 背面側内壁面
１８ｂ 前面側内壁面
１９ａ、１９ｂ コア接続部長手方向内壁面（上下方向内壁面） DESCRIPTION OF SYMBOLS 10 Intercooler 11 Intake inlet 12 Inlet side header 13 Inlet outlet 14 Outlet header 15 Core 16 Inlet side core connection part 17 Inlet pipe part 18a Rear side inner wall surface 18b Front side inner wall surface 19a, 19b In the core connection part longitudinal direction Wall surface (upper and lower inner wall surface)

Claims (4)

吸気流入口を有する流入側ヘッダと、吸気吐出口を有する吐出側ヘッダと、前記流入側ヘッダと前記吐出側ヘッダとの間に配設された熱交換用のコアとを備えるインタークーラにおいて、
前記流入側ヘッダは、前記コアに接続され、前記コアの一端部に沿って延びる流入側コア接続部と、前記流入側コア接続部の後部に形成されて前記流入側コア接続部と連通すると共に、前記流入側コア接続部から筒状かつ背面側に延び、先端に前記吸気流入口が形成された入口パイプ部とを有し、
前記流入側コア接続部と前記入口パイプ部との連通部分の背面側内壁面を前記流入側コア接続部の背面位置よりも前側に湾曲させ、Ｒ形状としたことを特徴とするインタークーラ。 In an intercooler comprising an inflow header having an intake inlet, a discharge header having an intake discharge port, and a heat exchange core disposed between the inflow header and the discharge header,
The inflow side header is connected to the core and is formed at an inflow side core connection portion extending along one end portion of the core, and a rear portion of the inflow side core connection portion, and communicates with the inflow side core connection portion. And an inlet pipe portion extending from the inflow side core connection portion to the back surface side in a cylindrical shape and having the intake air inlet formed at a tip thereof.
An intercooler characterized in that a rear inner wall surface of a communication portion between the inflow side core connection portion and the inlet pipe portion is curved to the front side with respect to the back surface position of the inflow side core connection portion to form an R shape. 前記流入側コア接続部と前記入口パイプ部との連通部分の背面が、前記流入側コア接続部の背面位置に対して前側に湾曲して凹曲面を形成し、
前記流入側コア接続部と前記入口パイプ部との連通部分の前面を凸曲面状に湾曲させることで、前記流入側コア接続部と前記入口パイプ部との連通部分の前面側内壁面をＲ形状とした請求項１に記載のインタークーラ。 The back surface of the communication portion between the inflow side core connection portion and the inlet pipe portion is curved forward with respect to the back surface position of the inflow side core connection portion to form a concave curved surface ,
By curving the front surface of the communication portion between the inflow side core connection portion and the inlet pipe portion into a convex curved surface, the front side inner wall surface of the communication portion between the inflow side core connection portion and the inlet pipe portion has an R shape. The intercooler according to claim 1. 前記流入側コア接続部と前記入口パイプ部との連通部分の背面を凹曲面状に湾曲させることで、前記流入側コア接続部と前記入口パイプ部との連通部分のコア接続部長手方向内壁面をＲ形状とした請求項１又は２に記載のインタークーラ。 The inner wall surface in the longitudinal direction of the core connection portion of the communication portion between the inflow side core connection portion and the inlet pipe portion by curving the back surface of the communication portion between the inflow side core connection portion and the inlet pipe portion into a concave curved surface The intercooler according to claim 1 or 2, which has an R shape. 前記入口パイプ部のコア接続部長手方向の径を当該コア接続部長手方向に直交する方向の径に対して大きく形成した請求項１から３のいずれかに記載のインタークーラ。 The intercooler according to any one of claims 1 to 3, wherein a diameter in a longitudinal direction of the core connecting portion of the inlet pipe portion is formed larger than a diameter in a direction orthogonal to the longitudinal direction of the core connecting portion .
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