JP2009156126A - Intake manifold device for internal combustion engine - Google Patents

Intake manifold device for internal combustion engine Download PDF

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JP2009156126A
JP2009156126A JP2007334006A JP2007334006A JP2009156126A JP 2009156126 A JP2009156126 A JP 2009156126A JP 2007334006 A JP2007334006 A JP 2007334006A JP 2007334006 A JP2007334006 A JP 2007334006A JP 2009156126 A JP2009156126 A JP 2009156126A
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passage
valve
intake
intake manifold
internal combustion
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Itaru Noguchi
格 野口
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Keihin Corp
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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
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    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
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    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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Abstract

<P>PROBLEM TO BE SOLVED: To provide an intake manifold device with a passage length change-over part for more quickly and smoothly changing over the length of an intake passage. <P>SOLUTION: On the midway of the intake passage 16 as part of an intake manifold 14, the passage length change-over part 18 is provided which has a valve 42 for freely changing over the length of the passage. At both ends of the valve 42, first and second opening ends 46, 48 are formed which have circular portions 46a, 48a shaped approximately circular in cross section. The circular portions 46a, 48a have radius centers C1, C2 offset from the center of a shaft 40 as a turning center C of the valve 42. During the turning displacement of the valve 42, sliding resistance is reduced between each of the first and second opening ends 46, 48 and each of first and second seal members 36, 38 provided at the ends of the intake passage 16. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、内燃機関用吸気マニホールド装置に関し、一層詳細には、吸入空気が流通する吸気通路の長さを切換可能な通路長切換部を有する内燃機関用吸気マニホールド装置に関する。   The present invention relates to an intake manifold device for an internal combustion engine, and more particularly to an intake manifold device for an internal combustion engine having a passage length switching portion capable of switching the length of an intake passage through which intake air flows.

従来から、自動車等の多気筒エンジンでは、シリンダヘッドの吸気ポートと吸入空気量を調整する絞り弁との間に吸気マニホールドが設けられ、前記吸気マニホールドに吸入された吸入空気を分流させて各吸気ポートへと配分している。   2. Description of the Related Art Conventionally, in a multi-cylinder engine such as an automobile, an intake manifold is provided between an intake port of a cylinder head and a throttle valve that adjusts an intake air amount, and the intake air sucked into the intake manifold is divided to each intake air. Distribution to ports.

近年、エンジンの高出力化に伴い、高速又は高負荷運転時には吸気マニホールドの吸気通路を短くし、低速又は低負荷運転時には前記吸気マニホールドの吸気通路を長くすることによってエンジンの出力を変更可能な内燃機関用吸気マニホールド装置が知られている。本出願人は、このような吸気マニホールド装置として、通路長切換部として機能するロータリーバルブを有し、前記ロータリーバルブを回転させることによって吸気マニホールドにおける吸気通路長の切り換えを行う構成を提案している（特許文献１参照）。   In recent years, with higher engine output, an internal combustion engine that can change the engine output by shortening the intake passage of the intake manifold at high speed or high load operation and lengthening the intake passage of the intake manifold at low speed or low load operation An intake manifold device for an engine is known. The present applicant has proposed a configuration in which such an intake manifold device has a rotary valve that functions as a passage length switching portion, and switches the intake passage length in the intake manifold by rotating the rotary valve. (See Patent Document 1).

特開２００３−８３０７２号公報JP 2003-83072 A

本発明は、前記の提案に関連してなされたものであり、通路長切換部による吸気通路長の切り換えをより一層円滑に行うことが可能な内燃機関用吸気マニホールド装置を提供することを目的とする。   The present invention has been made in connection with the above proposal, and an object thereof is to provide an intake manifold device for an internal combustion engine that can further smoothly switch the intake passage length by the passage length switching section. To do.

前記の目的を達成するために、本発明は、内燃機関を構成する本体部の各シリンダに独立して接続され、スロットル装置から吸入空気が導入されるチャンバーと連通する吸気通路を有する吸気マニホールドと、前記吸気通路に臨む前記吸気マニホールドの内部に設けられ、前記内燃機関の運転状況に応じて前記吸気通路の通路長を切り換える通路長切換部とを備える内燃機関用吸気マニホールド装置において、
前記通路長切換部は、前記吸気通路を構成し前記チャンバーに接続される第１通路部と、前記吸気通路を構成し前記本体部に接続される第２通路部との間に設けられ、支軸を中心として前記吸気マニホールドに回動自在に設けられた切換弁を備え、
前記切換弁には、所定半径からなる断面円弧状の円弧面を有し、前記円弧面を介して前記第１及び第２通路部の端部に当接自在な当接部を備え、前記円弧面の半径中心が前記切換弁の回動中心に対して偏心していることを特徴とする。 In order to achieve the above object, the present invention provides an intake manifold having an intake passage that is independently connected to each cylinder of a main body constituting an internal combustion engine and communicates with a chamber into which intake air is introduced from a throttle device. An intake manifold device for an internal combustion engine, provided with a passage length switching unit that is provided inside the intake manifold facing the intake passage and switches a passage length of the intake passage according to an operating state of the internal combustion engine.
The passage length switching portion is provided between a first passage portion constituting the intake passage and connected to the chamber, and a second passage portion constituting the intake passage and connected to the main body portion. A switching valve provided rotatably on the intake manifold around an axis;
The switching valve has a circular arc surface with a circular arc section having a predetermined radius, and includes a contact portion that can freely contact the end portions of the first and second passage portions via the circular arc surface. The radius center of the surface is eccentric with respect to the rotation center of the switching valve.

本発明によれば、通路長切換部を構成する切換弁において、前記切換弁の当接部に所定半径からなる断面円弧状の円弧面を設け、前記円弧面を介して吸気通路を構成する第１及び第２通路部の端部に前記切換弁を当接自在に設けると共に、前記円弧面の半径中心を、吸気マニホールドに支軸で支持された切換弁の回動中心に対して偏心させている。従って、切換弁を回動させて吸気通路の通路長を切り換える際、円弧面の半径中心と回動中心とが偏心しているため、前記円弧面が前記端部に対して離間する場合には、前記円弧面が回動変位に伴って前記端部に対して徐々に離間していくような回動軌跡で変位させ、前記円弧面が前記端部に対して接近する場合には、前記円弧面が前記端部に対して徐々に接近していくような回動軌跡で変位させることができる。   According to the present invention, in the switching valve constituting the passage length switching portion, the contact portion of the switching valve is provided with an arc surface having an arc cross section having a predetermined radius, and the intake passage is configured via the arc surface. The switching valve is provided at the end portions of the first and second passage portions so as to be able to come into contact with each other, and the radius center of the circular arc surface is decentered with respect to the rotation center of the switching valve supported by a support shaft on the intake manifold. Yes. Therefore, when the switching valve is rotated to switch the passage length of the intake passage, the radius center and the rotation center of the arc surface are eccentric, so when the arc surface is separated from the end portion, When the arc surface is displaced along a rotation trajectory that gradually moves away from the end portion with the rotation displacement, and the arc surface approaches the end portion, the arc surface Can be displaced along a turning trajectory that gradually approaches the end.

その結果、切換弁の円弧面が、第１及び第２通路部の端部に摺接しながら変位することがないため、前記切換弁と第１及び第２通路部の端部との間に生じる摺動抵抗を低減させることが可能となり、切換弁を含む通路長切換部を円滑に作動させて吸気通路の通路長の切り換えをより一層迅速且つ円滑に行うことができる。   As a result, the arc surface of the switching valve does not displace while slidingly contacting the end portions of the first and second passage portions, and thus occurs between the switching valve and the end portions of the first and second passage portions. The sliding resistance can be reduced, and the passage length switching portion including the switching valve can be smoothly operated to switch the passage length of the intake passage more quickly and smoothly.

また、第１及び第２通路部の端部に、弾性材料から形成され、円弧面が当接自在なシール部材を設けることにより、前記円弧面を介して切換弁が前記シール部材が当接した際に、吸気通路を構成する第１及び第２通路部内の気密が確実且つ好適に保持される。   Further, by providing a seal member formed of an elastic material at the end portions of the first and second passage portions so that the arc surface can come into contact with each other, the switching valve contacts the seal member via the arc surface. At this time, the airtightness in the first and second passage portions constituting the intake passage is reliably and suitably maintained.

さらに、円弧面の半径中心を、切換弁の軸線を中心として当接部が第１及び第２通路部の端部から離間する際に前記切換弁が回動する方向に所定距離だけ偏心させて設定するとよい。これにより、切換弁を回動させた際に、その当接部を前記第１及び第２通路部の端部に対して摺接させることなく好適に変位させることが可能となる。   Further, the radius center of the circular arc surface is decentered by a predetermined distance in a direction in which the switching valve rotates when the contact portion is separated from the end portions of the first and second passage portions around the axis of the switching valve. It is good to set. As a result, when the switching valve is rotated, it is possible to suitably displace the abutting portion without sliding against the end portions of the first and second passage portions.

さらにまた、当接部を、切換弁の軸線方向に沿った両端部にそれぞれ設けると好適である。   Furthermore, it is preferable that the contact portions are provided at both end portions along the axial direction of the switching valve.

本発明によれば、以下の効果が得られる。   According to the present invention, the following effects can be obtained.

すなわち、通路長切換部を構成する切換弁に所定半径からなる断面円弧状の円弧面を設け、前記円弧面を介して吸気通路を構成する第１及び第２通路部の端部に当接自在に設けると共に、前記円弧面の半径中心を、吸気マニホールドに支軸で支持された切換弁の回動中心に対して偏心させることにより、切換弁が回動する際、その円弧面が第１及び第２通路部の端部に摺接しながら変位することがなく、前記切換弁を含む通路長切換部を円滑に作動させて吸気通路の通路長の切り換えをより一層迅速且つ円滑に行うことができる。   In other words, the switching valve constituting the passage length switching portion is provided with an arc surface having an arc cross section having a predetermined radius, and can be brought into contact with the end portions of the first and second passage portions constituting the intake passage via the arc surface. When the switching valve is rotated, the arc surface is first and the arc surface is decentered with respect to the rotation center of the switching valve supported by the intake manifold on the support shaft. Without being displaced while slidingly contacting the end of the second passage portion, the passage length switching portion including the switching valve can be smoothly operated to switch the passage length of the intake passage more quickly and smoothly. .

また、第１及び第２通路部の端部に設けられたシール部材に対する切換弁の摺接範囲を小さくすることができるため、前記シール部材の摩耗を抑制することが可能となり、それに伴って、前記シール部材の耐久性を向上させることができる。   Moreover, since the sliding contact range of the switching valve with respect to the seal member provided at the end of the first and second passage portions can be reduced, it is possible to suppress wear of the seal member, and accordingly The durability of the seal member can be improved.

本発明に係る内燃機関用吸気マニホールド装置について好適な実施の形態を挙げ、添付の図面を参照しながら以下詳細に説明する。   A preferred embodiment of an intake manifold device for an internal combustion engine according to the present invention will be described in detail below with reference to the accompanying drawings.

図１において、参照符号１０は、本発明の実施の形態に係る内燃機関用吸気マニホールド装置を示す。なお、ここでは、複数のシリンダを有する多気筒エンジンに適用される吸気マニホールド装置について説明する。   In FIG. 1, reference numeral 10 indicates an intake manifold device for an internal combustion engine according to an embodiment of the present invention. Here, an intake manifold device applied to a multi-cylinder engine having a plurality of cylinders will be described.

内燃機関用吸気マニホールド装置１０（以下、吸気マニホールド装置１０という）は、車両等に搭載される、例えば、４つのシリンダ室を有する４気筒のエンジン２２に設けられている。   An intake manifold device 10 for an internal combustion engine (hereinafter referred to as an intake manifold device 10) is provided in, for example, a four-cylinder engine 22 having four cylinder chambers mounted on a vehicle or the like.

この吸気マニホールド装置１０は、図１〜図６に示されるように、複数の分岐管１２を有する吸気マニホールド１４と、前記吸気マニホールド１４の分岐管１２に挿通され、吸入空気が流通する吸気通路１６の長さを切り換える通路長切換部１８と、前記通路長切換部１８を回動変位させるための駆動部（図示せず）とを有する。   1 to 6, the intake manifold device 10 includes an intake manifold 14 having a plurality of branch pipes 12, and an intake passage 16 that is inserted into the branch pipe 12 of the intake manifold 14 and through which intake air flows. A path length switching unit 18 that switches the length of the path, and a drive unit (not shown) for rotationally displacing the path length switching unit 18.

吸気マニホールド１４は、例えば、樹脂製材料を射出成形した複数の分割体を溶着又は接着することにより一体的に形成されている。この吸気マニホールド１４は、図示しないスロットル装置の絞り弁を通じて吸入された空気が一時的に溜められるチャンバー２０と、前記チャンバー２０に接続され、前記チャンバー２０からエンジン２２へと前記空気を導く吸気通路１６とを有する。また、吸気マニホールド１４は、エンジン２２のシリンダヘッド２４に接続される取付フランジ２６を備え、前記取付フランジ２６が、その平面状に形成された端面を介して前記シリンダヘッド２４に連結される。   The intake manifold 14 is integrally formed, for example, by welding or bonding a plurality of divided bodies obtained by injection molding of a resin material. The intake manifold 14 includes a chamber 20 that temporarily stores air sucked through a throttle valve of a throttle device (not shown), and an intake passage 16 that is connected to the chamber 20 and guides the air from the chamber 20 to the engine 22. And have. The intake manifold 14 includes a mounting flange 26 connected to the cylinder head 24 of the engine 22, and the mounting flange 26 is coupled to the cylinder head 24 through an end face formed in a planar shape.

チャンバー２０は、断面略Ｌ字状で吸気マニホールド１４の長手方向に沿って延在し、エンジン２２側に配置されて吸気通路１６の一端部が接続される第１空間部２８と、前記第１空間部２８の下部に対して前記エンジン２２から離間する方向へと延在し、前記吸気通路１６の一部が接続される第２空間部３０とを含む。   The chamber 20 has a substantially L-shaped cross section and extends along the longitudinal direction of the intake manifold 14. The chamber 20 is disposed on the engine 22 side and is connected to one end of the intake passage 16. And a second space portion 30 that extends in a direction away from the engine 22 with respect to the lower portion of the space portion 28 and to which a part of the intake passage 16 is connected.

吸気通路１６は、分岐管１２の内部に設けられ略一定径からなる管状に形成され、互いに所定間隔離間した分岐管１２の内部に沿うようにそれぞれ設けられる。すなわち、複数の吸気通路１６は、互いに所定間隔離間して略並列に配置される。   The intake passage 16 is provided inside the branch pipe 12 and is formed in a tubular shape having a substantially constant diameter, and is provided along the inside of the branch pipe 12 spaced apart from each other by a predetermined distance. That is, the plurality of intake passages 16 are arranged substantially in parallel at a predetermined interval from each other.

この吸気通路１６は、吸気マニホールド１４の長手方向に沿ってチャンバー２０を構成する第１空間部２８及び第２空間部３０の下部側に配置され、吸気マニホールド１４の外壁面に沿って上方に向かうように湾曲する湾曲部（第１通路部）３２と、前記第２空間部３０の上部とエンジン２２とを接続する接続部（第２通路部）３４とを含む。   The intake passage 16 is disposed on the lower side of the first space portion 28 and the second space portion 30 constituting the chamber 20 along the longitudinal direction of the intake manifold 14, and moves upward along the outer wall surface of the intake manifold 14. And a connecting portion (second passage portion) 34 for connecting the upper portion of the second space 30 and the engine 22 to each other.

湾曲部３２は、その一端部が第１空間部２８の下部に接続されると共に、他端部が第２空間部３０の下部に接続され、前記第１空間部２８と第２空間部３０とを連通させている。換言すれば、湾曲部３２は、湾曲することによって第１空間部２８及び第２空間部３０の下部同士を接続している。   The bending portion 32 has one end connected to the lower portion of the first space portion 28 and the other end connected to the lower portion of the second space portion 30, and the first space portion 28, the second space portion 30, and the like. Is in communication. In other words, the bending portion 32 connects the lower portions of the first space portion 28 and the second space portion 30 by bending.

また、湾曲部３２の他端部には、チャンバー２０を構成する第２空間部３０の内壁面に対して突出するように第１シール部材３６が設けられる。この第１シール部材３６は、例えば、ゴム等の弾性材料から円筒状に形成され、湾曲部３２に固定される一端部が略平面状に形成されると共に、通路長切換部１８に臨む他端部が、吸気通路１６の軸線に対する直交方向から見て前記第１シール部材３６の一端面側に窪んだ断面略円弧状に形成される。   A first seal member 36 is provided at the other end of the curved portion 32 so as to protrude from the inner wall surface of the second space portion 30 constituting the chamber 20. For example, the first seal member 36 is formed in a cylindrical shape from an elastic material such as rubber, and one end fixed to the curved portion 32 is formed in a substantially planar shape, and the other end facing the passage length switching portion 18. The portion is formed in a substantially circular arc shape that is recessed toward one end surface of the first seal member 36 when viewed from a direction orthogonal to the axis of the intake passage 16.

この第１シール部材３６の高さは、湾曲部３２の他端部に対して第１空間部２８側が低く、第２空間部３０側が高くなるように設定され、前記第１シール部材３６の他端部には、前記第１空間部２８側に断面略円弧状の円弧面３６ａが形成され、第２空間部３０側には、前記円弧面３６ａと隣接し、第１シール部材３６の軸線と略直交方向に延在する平坦面３６ｂが形成される。   The height of the first seal member 36 is set so that the first space portion 28 side is lower than the other end portion of the curved portion 32 and the second space portion 30 side is higher. At the end, an arc surface 36a having a substantially arc-shaped cross section is formed on the first space portion 28 side, and on the second space portion 30 side, the arc surface 36a is adjacent to the axis surface of the first seal member 36. A flat surface 36b extending in a substantially orthogonal direction is formed.

接続部３４の一端部は、第２空間部３０の上部に接続され、前記第２空間部３０に臨む湾曲部３２の他端部と同軸上に配置されると共に、その他端部が、前記第２空間部３０から前記エンジン２２側に向かうように湾曲してチャンバー２０の上方に配置される。そして、接続部３４の他端部は、取付フランジ２６を介してエンジン２２を構成するシリンダヘッド２４に接続され、前記接続部３４とシリンダヘッド２４とが連通する。   One end portion of the connection portion 34 is connected to the upper portion of the second space portion 30 and is disposed coaxially with the other end portion of the bending portion 32 facing the second space portion 30, and the other end portion is the first space portion. 2 Curved from the space 30 toward the engine 22 side and disposed above the chamber 20. The other end of the connecting portion 34 is connected to the cylinder head 24 constituting the engine 22 via the mounting flange 26, and the connecting portion 34 and the cylinder head 24 communicate with each other.

また、接続部３４の一端部には、湾曲部３２の他端部と同様に第２空間部３０の内壁面に対して突出するように第２シール部材３８が設けられる。この第２シール部材３８は、例えば、ゴム等の弾性材料から第１シール部材３６と略同一形状となる円筒状に形成され、接続部３４に固定される一端部が略平面状に形成されると共に、通路長切換部１８に臨む他端部が、吸気通路１６の軸線に対する直交方向から見て前記第２シール部材３８の一端面側に窪んだ断面略円弧状に形成される。   In addition, a second seal member 38 is provided at one end portion of the connection portion 34 so as to protrude from the inner wall surface of the second space portion 30 in the same manner as the other end portion of the bending portion 32. The second seal member 38 is formed in a cylindrical shape having substantially the same shape as the first seal member 36 from an elastic material such as rubber, and one end portion fixed to the connection portion 34 is formed in a substantially planar shape. At the same time, the other end facing the passage length switching portion 18 is formed in a substantially circular arc shape that is recessed toward one end surface of the second seal member 38 when viewed from the direction orthogonal to the axis of the intake passage 16.

この第２シール部材３８の高さは、接続部３４の一端部に対して第１空間部２８側が高く、第２空間部３０側が低くなるように設定され、前記第２シール部材３８の他端部には、第２空間部３０側に断面略円弧状の円弧面３８ａが形成され、第１空間部２８側には、前記円弧面３８ａと隣接し、第２シール部材３８の軸線と略直交方向に延在する平坦面３８ｂが形成される。   The height of the second seal member 38 is set so that the first space portion 28 side is higher than the one end portion of the connection portion 34 and the second space portion 30 side is lower, and the other end of the second seal member 38 is An arc surface 38a having a substantially arc-shaped cross section is formed on the second space portion 30 side, and the arc portion 38a is adjacent to the arc surface 38a on the first space portion 28 side and substantially orthogonal to the axis of the second seal member 38. A flat surface 38b extending in the direction is formed.

すなわち、第１及び第２シール部材３６、３８は、通路長切換部１８を構成するシャフト（支軸）４０を中心として対称となるように吸気通路１６に対して配設されている。   That is, the first and second seal members 36 and 38 are disposed with respect to the intake passage 16 so as to be symmetric with respect to a shaft (support shaft) 40 constituting the passage length switching unit 18.

このように、吸気通路１６を構成する湾曲部３２及び接続部３４は、チャンバー２０を構成する第２空間部３０を通じて連通し、吸気通路１６の一端部が、湾曲部３２を介して前記チャンバー２０の第１空間部２８に接続され、前記吸気通路１６の他端部が、接続部３４を介してエンジン２２のシリンダヘッド２４に接続される。   As described above, the curved portion 32 and the connecting portion 34 constituting the intake passage 16 communicate with each other through the second space portion 30 constituting the chamber 20, and one end portion of the intake passage 16 is communicated with the chamber 20 via the curved portion 32. The other end portion of the intake passage 16 is connected to the cylinder head 24 of the engine 22 via the connection portion 34.

通路長切換部１８は、チャンバー２０の内部において吸気通路１６の湾曲部３２と接続部３４との間に設けられ、吸気マニホールド１４に軸支されたシャフト４０と、前記シャフト４０に保持され、吸気通路１６の流通状態を切り換える複数のバルブ（切換弁）４２とからなる。   The passage length switching unit 18 is provided between the curved portion 32 of the intake passage 16 and the connection portion 34 inside the chamber 20, and is supported by the shaft 40 supported by the intake manifold 14 and the shaft 40. It comprises a plurality of valves (switching valves) 42 for switching the flow state of the passage 16.

シャフト４０は、一定径からなる軸状に形成され、複数の吸気通路１６に跨るように前記吸気通路１６の軸線と略直交するように貫通すると共に、前記吸気通路１６を構成する接続部３４及び湾曲部３２の軸線上となるように配置される。   The shaft 40 is formed in an axial shape having a constant diameter, passes through the plurality of intake passages 16 so as to be substantially orthogonal to the axis of the intake passage 16, and includes a connecting portion 34 that constitutes the intake passage 16 and It arrange | positions so that it may be on the axis line of the bending part 32. FIG.

また、シャフト４０は、吸気マニホールド１４に対して回転自在に保持されると共に、前記シャフト４０の端部には図示しない駆動部が接続される。そして、シャフト４０は、駆動部の駆動作用下に約９０°だけ回動変位する。この駆動部は、例えば、通電作用下に回転駆動するステッピングモータからなり、前記駆動部の回転角度は、前記駆動部に対してコントローラ（図示せず）から入力される制御信号に基づいて所望の角度に制御される。   The shaft 40 is rotatably held with respect to the intake manifold 14, and a driving unit (not shown) is connected to the end of the shaft 40. The shaft 40 is rotationally displaced by about 90 ° under the drive action of the drive unit. The drive unit is composed of, for example, a stepping motor that is driven to rotate under energization, and the rotation angle of the drive unit is set based on a control signal input from a controller (not shown) to the drive unit. Controlled by angle.

バルブ４２は、略円筒状に形成され、吸気通路１６における湾曲部３２と接続部３４との間に前記吸気通路１６の数（例えば、４本）に応じてそれぞれ配設されている。バルブ４２の略中央部にはシャフト４０が挿通され、複数のバルブ４２が所定間隔離間して並列に配設される（図３参照）。そして、複数のバルブ４２は、シャフト４０を介して吸気通路１６を構成する接続部３４及び湾曲部３２に臨むチャンバー２０内で回転自在に保持される。   The valve 42 is formed in a substantially cylindrical shape, and is disposed between the curved portion 32 and the connection portion 34 in the intake passage 16 according to the number (for example, four) of the intake passages 16. A shaft 40 is inserted through a substantially central portion of the valve 42, and a plurality of valves 42 are arranged in parallel at a predetermined interval (see FIG. 3). The plurality of valves 42 are rotatably held in the chamber 20 facing the connecting portion 34 and the curved portion 32 that constitute the intake passage 16 via the shaft 40.

このバルブ４２は、軸線方向に沿って貫通した貫通孔４４と、前記貫通孔４４と連通した一端部側に形成され、吸気通路１６を構成する接続部３４に接続自在な第１開口端部（当接部）４６と、前記貫通孔４４と連通した他端部側に形成され、湾曲部３２に接続自在な第２開口端部（当接部）４８とからなる。この貫通孔４４は、バルブ４２の内部を一直線上に貫通すると共に、吸気通路１６の内周径と略同等の内周径に設定される。この第１開口端部４６が、湾曲部３２に装着された第１シール部材３６に当接自在に設けられ、第２開口端部４８が、接続部３４に装着された第２シール部材３８に当接自在に設けられる（図２参照）。   The valve 42 is formed on a through hole 44 penetrating along the axial direction, and on one end side communicating with the through hole 44, and a first opening end portion (connectable to a connection portion 34 constituting the intake passage 16) ( A contact portion) 46 and a second opening end portion (contact portion) 48 formed on the other end side communicating with the through hole 44 and connectable to the bending portion 32. The through-hole 44 penetrates the inside of the valve 42 in a straight line and is set to an inner peripheral diameter substantially equal to the inner peripheral diameter of the intake passage 16. The first opening end portion 46 is provided so as to be able to contact the first seal member 36 mounted on the bending portion 32, and the second opening end portion 48 is provided on the second seal member 38 mounted on the connection portion 34. It is provided so as to be freely contactable (see FIG. 2).

また、バルブ４２の軸線方向に沿った長さは、吸気通路１６の端部に設けられた第１シール部材３６と第２シール部材３８との離間距離と同等に設定されると共に、前記バルブ４２の外周径は、前記離間距離に対して小さく設定される。   The length of the valve 42 along the axial direction is set to be equal to the distance between the first seal member 36 and the second seal member 38 provided at the end of the intake passage 16, and the valve 42. Is set smaller than the separation distance.

さらに、バルブ４２の軸線方向に沿った略中央部には、シャフト４０が前記軸線と略直交方向に挿通され、前記バルブ４２が前記シャフト４０に対して保持される。   Further, a shaft 40 is inserted in a substantially central portion along the axial direction of the valve 42 in a direction substantially orthogonal to the axial line, and the valve 42 is held with respect to the shaft 40.

第１開口端部４６の端面は、バルブ４２に挿通されたシャフト４０の軸線方向から見て断面略円弧状に形成された円弧部４６ａと、前記円弧部４６ａに隣接し、前記軸線に対して略直交方向に延在する平坦部４６ｂとを備える。詳細には、第１開口端部４６は、シャフト４０から離間する方向に膨出した断面略円弧状に形成される。   An end surface of the first opening end 46 is adjacent to the arc portion 46a formed in a substantially arc shape in cross section when viewed from the axial direction of the shaft 40 inserted through the valve 42, and with respect to the axis line. And a flat portion 46b extending in a substantially orthogonal direction. Specifically, the first opening end 46 is formed in a substantially arc shape in cross section that bulges away from the shaft 40.

この円弧部４６ａは、所定半径Ｒ１で形成され、その半径中心Ｃ１は、シャフト４０の中心Ｃに対して所定距離だけオフセットして設定される。また、シャフト４０の中心Ｃに対する半径中心Ｃ１のオフセット方向は、バルブ４２の軸線を中心として第１開口端部４６が第１シール部材３６から離間する方向（矢印Ｂ方向）に回動する際の回動方向側とに設定される。   The circular arc part 46a is formed with a predetermined radius R1, and the radius center C1 is set offset from the center C of the shaft 40 by a predetermined distance. Further, the offset direction of the radius center C1 with respect to the center C of the shaft 40 is when the first opening end 46 rotates in the direction away from the first seal member 36 (the direction of arrow B) around the axis of the valve 42. Set to the rotation direction side.

そして、バルブ４２の第１開口端部４６が第１シール部材３６に当接する際、その円弧部４６ａが前記第１シール部材３６の円弧面３６ａに当接し、平坦部４６ｂが前記第１シール部材３６の平坦面３６ｂに当接する。すなわち、第１シール部材３６の他端部は、バルブ４２の第１開口端部４６の断面形状に対応した同一断面形状で形成されている。   When the first opening end portion 46 of the valve 42 contacts the first seal member 36, the arc portion 46a contacts the arc surface 36a of the first seal member 36, and the flat portion 46b corresponds to the first seal member. 36 abuts against the flat surface 36b. That is, the other end portion of the first seal member 36 is formed with the same cross-sectional shape corresponding to the cross-sectional shape of the first opening end portion 46 of the valve 42.

換言すれば、第１開口端部４６は、バルブ４２が第１シール部材３６に当接する際、円弧部４６ａが第２空間部３０側となり、平坦部４６ｂが第１空間部２８側に配置される。   In other words, when the valve 42 abuts on the first seal member 36, the first opening end portion 46 has the arc portion 46a on the second space portion 30 side and the flat portion 46b on the first space portion 28 side. The

第２開口端部４８の端面は、第１開口端部４６の端面と同一形状で形成され、バルブ４２に挿通されたシャフト４０の軸線方向から見て断面略円弧状に形成された円弧部４８ａと、前記円弧部４８ａに隣接し、前記軸線に対して略直交方向に延在する平坦部４８ｂとを備える。詳細には、第２開口端部４８は、シャフト４０から離間する方向に膨出した断面略円弧状に形成される。この円弧部４８ａは、所定半径Ｒ２で形成され、その半径中心Ｃ２は、シャフト４０の中心Ｃに対して所定距離だけオフセットして設定される。また、シャフト４０の中心Ｃに対する半径中心Ｃ２のオフセット方向は、バルブ４２の軸線を中心として第２開口端部４８が第２シール部材３８から離間する方向（矢印Ａ方向）に回動する際の回動方向側に設定される。   The end face of the second opening end portion 48 is formed in the same shape as the end face of the first opening end portion 46, and the arc portion 48a is formed in a substantially arc shape in cross section when viewed from the axial direction of the shaft 40 inserted through the valve 42. And a flat portion 48b adjacent to the arc portion 48a and extending in a direction substantially orthogonal to the axis. Specifically, the second opening end 48 is formed in a substantially circular arc shape that swells in a direction away from the shaft 40. The circular arc portion 48a is formed with a predetermined radius R2, and the radius center C2 is set offset from the center C of the shaft 40 by a predetermined distance. Further, the offset direction of the radius center C2 with respect to the center C of the shaft 40 is when the second opening end portion 48 rotates about the axis of the valve 42 in the direction away from the second seal member 38 (arrow A direction). It is set on the rotation direction side.

そして、バルブ４２の第２開口端部４８が第２シール部材３８に当接する際、その円弧部４８ａが前記第２シール部材３８の円弧面３８ａに当接し、平坦部４８ｂが前記第２シール部材３８の平坦面３８ｂに当接する。すなわち、第２シール部材３８の他端部は、バルブ４２の第２開口端部４８の断面形状に対応した同一断面形状で形成されている。   When the second opening end 48 of the valve 42 contacts the second seal member 38, the arc portion 48a contacts the arc surface 38a of the second seal member 38, and the flat portion 48b corresponds to the second seal member. 38 abuts on the flat surface 38b. That is, the other end portion of the second seal member 38 is formed with the same cross-sectional shape corresponding to the cross-sectional shape of the second opening end portion 48 of the valve 42.

また、第２開口端部４８は、バルブ４２が第２シール部材３８に当接する際、円弧部４８ａが第１空間部２８側に配置されると共に、平坦部４８ｂが第２空間部３０側に配置される。   Further, when the valve 42 contacts the second seal member 38, the second opening end portion 48 has an arc portion 48a disposed on the first space portion 28 side and a flat portion 48b on the second space portion 30 side. Be placed.

このように、第１及び第２開口端部４６、４８は、バルブ４２の中央に挿通されたシャフト４０を中心として対称形状となるように形成されている。   As described above, the first and second open end portions 46 and 48 are formed so as to be symmetrical with respect to the shaft 40 inserted through the center of the valve 42.

そして、バルブ４２がシャフト４０と共に回動し、その第１開口端部４６が第１シール部材３６に当接すると共に、第２開口端部４８が第２シール部材３８に当接することにより、前記バルブ４２の軸線が、前記接続部３４及び湾曲部３２の軸線と同軸上となる。これにより、吸気通路１６を構成する湾曲部３２と接続部３４とがバルブ４２の貫通孔４４を通じて連通した長管吸気通路Ｌが構成される（図１参照）。   Then, the valve 42 rotates together with the shaft 40, and the first opening end portion 46 abuts on the first seal member 36 and the second opening end portion 48 abuts on the second seal member 38, whereby the valve The axis of 42 is coaxial with the axis of the connecting portion 34 and the bending portion 32. Thus, a long pipe intake passage L is formed in which the curved portion 32 and the connection portion 34 constituting the intake passage 16 communicate with each other through the through hole 44 of the valve 42 (see FIG. 1).

この場合、第１開口端部４６が、第１シール部材３６に対応した形状で形成されているため、前記第１シール部材３６に当接して密着することによりシールされ、前記第１開口端部４６と第１シール部材３６との間からの吸入空気の漏出が防止される。また、同様に、第２開口端部４８が、第２シール部材３８に対応した形状で形成されているため、前記第２シール部材３８に当接して密着することによりシールされ、前記第２開口端部４８と第２シール部材３８との間からの吸入空気の漏出が防止される。   In this case, since the first opening end 46 is formed in a shape corresponding to the first seal member 36, the first opening end 46 is sealed by contacting and closely contacting the first seal member 36. Leakage of intake air from between 46 and the first seal member 36 is prevented. Similarly, since the second opening end portion 48 is formed in a shape corresponding to the second seal member 38, the second opening end portion 48 is sealed by coming into contact with and closely contacting the second seal member 38, so that the second opening Leakage of intake air from between the end portion 48 and the second seal member 38 is prevented.

一方、シャフト４０の回転作用下に第１開口端部４６が第１空間部２８側に向かい、第２開口端部４８が第２空間部３０側に向かうようにバルブ４２が回動変位し、前記バルブ４２の軸線が接続部３４の軸線と略直交した状態となることにより、湾曲部３２及び接続部３４の端部が開放されて第１及び第２空間部２８、３０を含むチャンバー２０と連通することとなる。これにより、第１及び第２空間部２８、３０に導入された吸入空気が、接続部３４へと直接流通する短管吸気通路Ｓが構成される。この場合、短管吸気通路Ｓの通路長は、吸気マニホールド１４の外壁面に沿って湾曲状に形成された湾曲部３２を含む長管吸気通路Ｌの通路長より短くなる。   On the other hand, under the rotating action of the shaft 40, the valve 42 is rotationally displaced so that the first opening end 46 faces the first space 28 side and the second opening end 48 faces the second space 30 side, When the axis of the valve 42 is substantially perpendicular to the axis of the connecting portion 34, the ends of the bending portion 32 and the connecting portion 34 are opened, and the chamber 20 including the first and second space portions 28, 30 is provided. You will communicate. As a result, a short pipe intake passage S is formed in which the intake air introduced into the first and second space portions 28 and 30 flows directly to the connection portion 34. In this case, the passage length of the short pipe intake passage S is shorter than the passage length of the long pipe intake passage L including the curved portion 32 formed in a curved shape along the outer wall surface of the intake manifold 14.

すなわち、この吸気マニホールド装置を備えたエンジン２２の高速又は高負荷運転時には、通路長切換部１８を構成するバルブ４２の回動作用下に吸気通路１６の通路長が短くなるように短管吸気通路Ｓへと切り換え、吸入空気をシリンダヘッド２４へと供給すると共に、前記エンジン２２の低速又は低負荷運転時には、前記バルブ４２を回動させて貫通孔４４と湾曲部３２及び接続部３４を連通させることにより、湾曲部３２、接続部３４及びバルブ４２の貫通孔４４を含む通路長の長い長管吸気通路Ｌを通じて前記吸入空気を前記シリンダヘッド２４へと供給する。   That is, when the engine 22 equipped with this intake manifold device is operated at high speed or high load, the short pipe intake passage is set so that the passage length of the intake passage 16 is shortened under the rotating action of the valve 42 constituting the passage length switching section 18. Switch to S to supply intake air to the cylinder head 24, and at the time of low speed or low load operation of the engine 22, the valve 42 is rotated to connect the through hole 44 with the curved portion 32 and the connecting portion 34. Thus, the intake air is supplied to the cylinder head 24 through the long pipe intake passage L having a long passage length including the curved portion 32, the connection portion 34, and the through hole 44 of the valve 42.

本発明の実施の形態に係る内燃機関用吸気マニホールド装置１０は、基本的には以上のように構成されるものであり、次にその動作並びに作用効果について説明する。   The intake manifold device 10 for an internal combustion engine according to the embodiment of the present invention is basically configured as described above. Next, the operation and effects thereof will be described.

例えば、エンジン２２が低速又は低負荷運転時には、図示しないスプリングの弾発作用下にシャフト４４が付勢されることにより、前記シャフト４４が反時計回り（矢印Ａ方向）に回動し、前記シャフト４０の回動変位に伴ってバルブ４２が反時計回り（矢印Ａ方向）に回動して吸気通路１６を構成する湾曲部３２及び接続部３４と前記バルブ４２とが同軸上となるように配置される。これにより、バルブ４２を構成する第１及び第２開口端部４６、４８が、それぞれ吸気通路１６の接続部３４及び湾曲部３２の端部に装着された第１及び第２シール部材３６、３８に当接してシールされた状態となる。   For example, when the engine 22 is operating at a low speed or under a low load, the shaft 44 is urged under the spring action of a spring (not shown), so that the shaft 44 rotates counterclockwise (in the direction of arrow A). The valve 42 is rotated counterclockwise (in the direction of arrow A) in accordance with the rotational displacement of 40, and the curved portion 32 and the connecting portion 34 constituting the intake passage 16 and the valve 42 are arranged coaxially. Is done. As a result, the first and second opening end portions 46 and 48 constituting the valve 42 are respectively attached to the connection portion 34 of the intake passage 16 and the end portion of the bending portion 32, respectively. It will be in the state where it contacted and was sealed.

詳細には、第１及び第２開口端部４６、４８の円弧部４６ａ、４８ａが、第１及び第２シール部材３６、３８の円弧面３６ａ、３８ａに対してそれぞれ当接し、前記第１及び第２開口端部４６、４８の平坦部４６ｂ、４８ｂが、前記第１及び第２シール部材３６、３８の平坦面３６ｂ、３８ｂに対してそれぞれ当接する。   Specifically, the arc portions 46a and 48a of the first and second open end portions 46 and 48 abut against the arc surfaces 36a and 38a of the first and second seal members 36 and 38, respectively. The flat portions 46b and 48b of the second opening end portions 46 and 48 abut against the flat surfaces 36b and 38b of the first and second seal members 36 and 38, respectively.

すなわち、通路長切換部１８を構成するバルブ４２によって吸気通路１６の湾曲部３２と接続部３４とが接続されて連通し、チャンバー２０が長管吸気通路Ｌを介してエンジン２２と連通した状態となる。そして、チャンバー２０からエンジン２２への吸入空気の供給が、前記チャンバー２０の第１空間部２８から湾曲部３２及び接続部３４によって構成された長管吸気通路Ｌを通じて行われる。   That is, the curved portion 32 and the connecting portion 34 of the intake passage 16 are connected and communicated by the valve 42 constituting the passage length switching portion 18, and the chamber 20 is communicated with the engine 22 through the long pipe intake passage L. Become. Then, the intake air is supplied from the chamber 20 to the engine 22 through the long pipe intake passage L constituted by the curved portion 32 and the connecting portion 34 from the first space portion 28 of the chamber 20.

この場合、吸入空気は、チャンバー２０から長管吸気通路Ｌを構成する湾曲部３２、バルブ４２及び接続部３４を経てエンジン２２へと供給されるため、通路長の長い長管吸気通路Ｌを通じて前記エンジン２２に吸入される単位時間あたりの吸入空気の流量が少なくなる。   In this case, since the intake air is supplied from the chamber 20 to the engine 22 through the curved portion 32, the valve 42, and the connection portion 34 constituting the long pipe intake passage L, the intake air is passed through the long pipe intake passage L having a long passage length. The flow rate of intake air per unit time taken into the engine 22 is reduced.

また、エンジン２２が高速又は高負荷運転時には、エンジン回転数等に基づいた制御信号がコントローラ（図示せず）から駆動部へと出力され、前記駆動部がスプリング（図示せず）の弾発力に抗して前記とは反対方向に回転駆動することによりシャフト４０を介してバルブ４２が時計回り（矢印Ｂ方向）に所定角度だけ回動する。   In addition, when the engine 22 is operating at high speed or high load, a control signal based on the engine speed or the like is output from a controller (not shown) to the drive unit, and the drive unit is a spring force of a spring (not shown). As a result, the valve 42 is rotated clockwise (in the direction of arrow B) by a predetermined angle through the shaft 40 by being rotationally driven in the opposite direction.

そして、バルブ４２の第１及び第２開口端部４６、４８は、該バルブ４２の回動作用下に円弧部４６ａ、４８ａが第１及び第２シール部材３６、３８の円弧面３６ａ、３８ａから離間して平坦面３６ｂ、３８ｂに臨む方向に徐々に変位する（図３参照）。この場合、円弧部４６ａ、４８ａは、その半径中心Ｃ１、Ｃ２がバルブ４２の回動中心Ｃ１となるシャフト４０の中心に対してオフセットするように形成されているため、前記バルブ４２の回動変位に伴って前記円弧部４６ａ、４８ａと円弧面３６ａ、３８ａとの離間距離Ｄ１が徐々に大きくなるように離間していく。換言すれば、バルブ４２の第１及び第２開口端部４６、４８は、該バルブ４２が回動し始めた瞬間から第１及び第２シール部材３６、３８に対して離間し始めて互いの当接状態が解除される。   The first and second open end portions 46 and 48 of the valve 42 are formed so that the arc portions 46 a and 48 a are moved from the arc surfaces 36 a and 38 a of the first and second seal members 36 and 38 under the rotating action of the valve 42. It is gradually displaced in the direction facing the flat surfaces 36b and 38b with separation (see FIG. 3). In this case, the circular arc portions 46a and 48a are formed such that the radius centers C1 and C2 are offset with respect to the center of the shaft 40 which is the rotation center C1 of the valve 42. Accordingly, the distances D1 between the arc portions 46a and 48a and the arc surfaces 36a and 38a are gradually increased. In other words, the first and second open end portions 46 and 48 of the valve 42 start to move away from the first and second seal members 36 and 38 from the moment when the valve 42 starts to rotate. The contact state is released.

これにより、シャフト４０を中心としてバルブ４２が回動変位する際、該バルブ４２が第１及び第２シール部材３６、３８に対して摺接しながら変位することがない。   As a result, when the valve 42 is pivotally displaced about the shaft 40, the valve 42 is not displaced while being in sliding contact with the first and second seal members 36, 38.

さらに、バルブ４２がシャフト４０を中心として回動することにより、図４に示されるように、第１及び第２シール部材３６、３８に対するバルブ４２の第１及び第２開口端部４６、４８の離間距離Ｄ２がさらに大きくなり（Ｄ１＜Ｄ２）、前記バルブ４２の軸線が吸気通路１６を構成する湾曲部３２及び接続部３４の軸線と略直交し、第１開口端部４６がチャンバー２０の第１空間部２８に臨み、第２開口端部４８が前記チャンバー２０の第２空間部３０に臨んだ状態となる（図５及び図６参照）。   Further, as the valve 42 rotates about the shaft 40, as shown in FIG. 4, the first and second open end portions 46, 48 of the valve 42 with respect to the first and second seal members 36, 38 are formed. The separation distance D2 is further increased (D1 <D2), the axis of the valve 42 is substantially perpendicular to the axes of the curved portion 32 and the connecting portion 34 constituting the intake passage 16, and the first opening end 46 is the first end of the chamber 20. It faces the first space 28 and the second opening end 48 faces the second space 30 of the chamber 20 (see FIGS. 5 and 6).

その結果、バルブ４２を通じた湾曲部３２と接続部３４との連通状態が解除され、前記湾曲部３２及び接続部３４からなる長管吸気通路Ｌを通じた吸入空気の流通が停止すると共に、第１及び第２空間部２８、３０を有するチャンバー２０から接続部３４へと吸入空気が流通する。すなわち、第１及び第２空間部２８、３０から吸気通路１６の接続部３４へと吸入空気が直接導入される短管吸気通路Ｓが構成され、前記短管吸気通路Ｓを通じてエンジン２２へと吸入空気が供給される。その結果、吸入空気が、チャンバー２０から吸気通路１６の接続部３４を通じてエンジン２２へと短時間で迅速に供給される。   As a result, the communication state between the curved portion 32 and the connection portion 34 through the valve 42 is released, the flow of intake air through the long pipe intake passage L formed of the curved portion 32 and the connection portion 34 is stopped, and the first The intake air flows from the chamber 20 having the second space portions 28 and 30 to the connection portion 34. That is, a short pipe intake passage S into which intake air is directly introduced from the first and second space portions 28 and 30 to the connection portion 34 of the intake passage 16 is configured, and the intake air is sucked into the engine 22 through the short pipe intake passage S. Air is supplied. As a result, the intake air is rapidly supplied from the chamber 20 to the engine 22 through the connection portion 34 of the intake passage 16 in a short time.

このように、エンジン２２の運転状況に応じた通路長切換部１８の切換作用下に前記エンジン２２に吸入される吸入空気の流量及び流入時間が好適に制御され、それに伴って、前記エンジン２２の出力向上を図ることができる。   Thus, the flow rate and the inflow time of the intake air sucked into the engine 22 are suitably controlled under the switching action of the passage length switching unit 18 according to the operating state of the engine 22, and accordingly, the engine 22 The output can be improved.

一方、エンジン２２が再び低速又は低負荷運転時となった場合には、駆動部から通路長切換部１８に付勢されていた駆動力が滅勢され、図示しないスプリング等の弾発作用下にバルブ４２が反時計回り（矢印Ａ方向）に付勢される。そして、シャフト４０が所定角度だけ回動し、前記シャフト４０の回動変位に伴ってバルブ４２が反時計回り（矢印Ａ方向）に回動し始める。   On the other hand, when the engine 22 becomes low speed or low load operation again, the driving force urged from the drive unit to the passage length switching unit 18 is extinguished and under the elastic action of a spring or the like (not shown). The valve 42 is urged counterclockwise (arrow A direction). Then, the shaft 40 rotates by a predetermined angle, and the valve 42 starts to rotate counterclockwise (in the direction of arrow A) in accordance with the rotational displacement of the shaft 40.

そして、バルブ４２の第１及び第２開口端部４６、４８は、第１及び第２空間部２８、３０に対峙した状態（図６参照）から前記バルブ４２の回動作用下に徐々に第１及び第２シール部材３６、３８に接近する方向へと変位し、その円弧部４６ａ、４８ａが第１及び第２シール部材３６、３８の平坦面３６ｂ、３８ｂ側から徐々に接近していく（図４参照）。この第１及び第２開口端部４６、４８が、第１及び第２シール部材３６、３８に対して接近していくことにより、前記第１及び第２開口端部４６、４８の円弧部４６ａ、４８ａと第１及び第２シール部材３６、３８との間の離間距離Ｄ２が小さくなっていく。   Then, the first and second open end portions 46 and 48 of the valve 42 gradually start from the state facing the first and second space portions 28 and 30 (see FIG. 6) under the rotating action of the valve 42. The first and second seal members 36 and 38 are displaced in a direction approaching, and the arc portions 46a and 48a gradually approach from the flat surfaces 36b and 38b side of the first and second seal members 36 and 38 ( (See FIG. 4). When the first and second opening end portions 46 and 48 approach the first and second sealing members 36 and 38, the arc portions 46a of the first and second opening end portions 46 and 48 are obtained. , 48a and the first and second seal members 36, 38 become smaller in distance D2.

このバルブ４２がさらに反時計回り（矢印Ａ方向）に回動し、図３に示されるように、前記円弧部４６ａ、４８ａが円弧面３６ａ、３８ａに臨む位置まで到達した場合においても、第１及び第２開口端部４６、４８と第１及び第２シール部材３６、３８とが未だ接触することがなく、所定間隔の離間距離Ｄ１で互いに離間した状態にある。但し、この離間距離Ｄ１は、バルブ４２の回動変位に伴って徐々に小さくなっている（Ｄ１＜Ｄ２）。   Even when the valve 42 further rotates counterclockwise (in the direction of arrow A) and reaches the position where the arc portions 46a and 48a face the arc surfaces 36a and 38a as shown in FIG. The second opening end portions 46 and 48 and the first and second seal members 36 and 38 are not yet in contact with each other and are separated from each other by a predetermined separation distance D1. However, the separation distance D1 gradually decreases with the rotational displacement of the valve 42 (D1 <D2).

そして、さらにバルブ４２が回動し、その軸線が吸気通路１６を構成する湾曲部３２及び接続部３４と同軸上となった状態で第１及び第２開口端部４６、４８が第１及び第２シール部材３６、３８に対して当接し、前記湾曲部３２と接続部３４とを接続させて連通させる。   Further, the valve 42 further rotates, and the first and second opening end portions 46 and 48 are in the first and first states in a state where the axis thereof is coaxial with the curved portion 32 and the connecting portion 34 constituting the intake passage 16. 2 Abut against the seal members 36, 38, and connect the curved portion 32 and the connecting portion 34 to communicate with each other.

すなわち、第１及び第２開口端部４６、４８の円弧部４６ａ、４８ａは、その半径中心Ｃ１、Ｃ２がバルブ４２の回動中心Ｃとなるシャフト４０の中心に対してオフセットするように形成されているため、前記バルブ４２の回動変位に伴って前記円弧部４６ａ、４８ａと円弧面３６ａ、３８ａとの離間距離が徐々に小さくなるように接近していき、バルブ４２の第１及び第２開口端部４６、４８は、該バルブ４２の回動が完了して前記バルブ４２と吸気通路１６とが同軸上となった状態で始めて当接状態となり、前記第１及び第２シール部材３６、３８に密着してシールされる。換言すれば、バルブ４２がシャフト４０を中心として回動変位する際、該バルブ４２が第１及び第２シール部材３６、３８に対して摺接しながら変位することがない。   That is, the arc portions 46a and 48a of the first and second opening end portions 46 and 48 are formed such that the radius centers C1 and C2 are offset with respect to the center of the shaft 40 which is the rotation center C of the valve 42. Therefore, the distance between the arc portions 46a, 48a and the arc surfaces 36a, 38a is gradually reduced with the rotational displacement of the valve 42, and the first and second of the valve 42 are approached. The opening end portions 46 and 48 are brought into contact with each other only when the valve 42 is completely rotated and the valve 42 and the intake passage 16 are coaxial, and the first and second seal members 36, 38 is tightly sealed. In other words, when the valve 42 is rotationally displaced about the shaft 40, the valve 42 is not displaced while being in sliding contact with the first and second seal members 36 and 38.

これにより、バルブ４２を通じて湾曲部３２と接続部３４とが連通した長管吸気通路Ｌが再び構成され、第１及び第２空間部２８、３０を有するチャンバー２０からの吸入空気が湾曲部３２、バルブ４２の貫通孔４４及び接続部３４へと流通してエンジン２２へと供給される。なお、第１及び第２空間部２８、３０から吸気通路１６の接続部３４へと吸入空気が直接導入される短管吸気通路Ｓは、バルブ４２によって遮断されている。   Thereby, the long-pipe intake passage L in which the curved portion 32 and the connecting portion 34 communicate with each other through the valve 42 is formed again, and the intake air from the chamber 20 having the first and second space portions 28 and 30 is converted into the curved portion 32, The gas flows through the through hole 44 and the connection portion 34 of the valve 42 and is supplied to the engine 22. The short pipe intake passage S through which intake air is directly introduced from the first and second space portions 28 and 30 to the connection portion 34 of the intake passage 16 is blocked by a valve 42.

以上のように、本実施の形態では、バルブ４２の両端部に設けられた第１及び第２開口端部４６、４８を構成する円弧部４６ａ、４８ａの半径中心Ｃ１、Ｃ２と、前記バルブ４２の回動中心Ｃとを所定距離だけオフセットさせると共に、前記第１及び第２開口端部４６、４８が当接する第１及び第２シール部材３６、３８の円弧面３６ａ、３８ａを前記円弧部４６ａ、４８ａに対応させて同一半径で形成している。   As described above, in the present embodiment, the radial centers C1 and C2 of the arc portions 46a and 48a constituting the first and second opening end portions 46 and 48 provided at both ends of the valve 42, and the valve 42 And the arc surfaces 36a, 38a of the first and second seal members 36, 38 with which the first and second opening end portions 46, 48 abut are offset by a predetermined distance. , 48a, with the same radius.

これにより、例えば、通路長切換部１８を構成するバルブ４２を回動させ、吸気通路１６を長管吸気通路Ｌから短管吸気通路Ｓへと切り換える際、第１及び第２開口端部４６、４８が第１及び第２シール部材３６、３８に当接した状態から前記バルブ４２の回動と共に徐々に離間させることができる。一方、吸気通路１６を短管吸気通路Ｓから長管吸気通路Ｌへと切り換える際には、バルブ４２の回動変位に伴って第１及び第２開口端部４６、４８が、第１及び第２シール部材３６、３８に向かって徐々に接近し、前記第１及び第２シール部材３６、３８に対して完全に対峙した位置で当接させることができる。すなわち、バルブ４２の第１及び第２開口端部４６、４８が、第１及び第２シール部材３６、３８の円弧面３６ａ、３８ａに摺接しながら変位することがない。   Thereby, for example, when the valve 42 constituting the passage length switching unit 18 is rotated and the intake passage 16 is switched from the long pipe intake passage L to the short pipe intake passage S, the first and second opening end portions 46, 48 can be gradually separated from the state where the valve 48 is in contact with the first and second seal members 36 and 38 as the valve 42 rotates. On the other hand, when the intake passage 16 is switched from the short-pipe intake passage S to the long-pipe intake passage L, the first and second open end portions 46 and 48 are moved in accordance with the rotational displacement of the valve 42. The two seal members 36 and 38 gradually approach each other and can be brought into contact with the first and second seal members 36 and 38 in a completely opposed position. That is, the first and second opening end portions 46 and 48 of the valve 42 are not displaced while sliding on the arc surfaces 36 a and 38 a of the first and second seal members 36 and 38.

その結果、バルブ４２の第１及び第２開口端部４６、４８と第１及び第２シール部材３６、３８との間に生じる摺動抵抗を低減させることができるため、バルブ４２を含む通路長切換部１８を円滑に作動させることができ、それに伴って、前記通路切換部による吸気通路１６の通路長の切り換えを円滑に行うことができる。   As a result, the sliding resistance generated between the first and second open end portions 46 and 48 of the valve 42 and the first and second seal members 36 and 38 can be reduced. The switching unit 18 can be smoothly operated, and accordingly, the passage length of the intake passage 16 can be smoothly switched by the passage switching unit.

これに対して、図７に示されるように、バルブ１００の回動中心Ｃ´と、前記バルブ１００における第１及び第２開口端部１０２、１０４の半径中心Ｃ１´、Ｃ２´とが一致するように構成された通路長切換部１０６を有する比較例に係る吸気マニホールド装置１０８では、前記第１及び第２開口端部１０２、１０４が当接可能な第１及び第２シール部材１１０、１１２の端面１１０ａ、１１２ａも、前記第１及び第２開口端部の断面形状に対応して断面円弧状に形成されている。そのため、バルブ１００が回動する際に、その第１及び第２開口端部１０２、１０４が第１及び第２シール部材１１０、１１２の端面１１０ａ、１１２ａに対して完全に離間した状態となるまでの間、前記第１及び第２開口端部１０２、１０４の一部が、常に第１及び第２シール部材１１０、１１２とが当接した状態のままとなる。   On the other hand, as shown in FIG. 7, the rotation center C ′ of the valve 100 coincides with the radius centers C1 ′ and C2 ′ of the first and second opening end portions 102 and 104 of the valve 100. In the intake manifold device 108 according to the comparative example having the passage length switching portion 106 configured as described above, the first and second seal members 110 and 112 with which the first and second opening end portions 102 and 104 can abut are provided. The end faces 110a and 112a are also formed in a circular arc shape corresponding to the cross-sectional shapes of the first and second opening end portions. Therefore, when the valve 100 rotates, the first and second opening end portions 102 and 104 are completely separated from the end surfaces 110a and 112a of the first and second seal members 110 and 112. During this, a part of the first and second opening end portions 102 and 104 always remains in contact with the first and second seal members 110 and 112.

すなわち、バルブ１００は、第１及び第２開口端部１０２、１０４を介して第１及び第２シール部材１１０、１１２に沿って摺動変位することとなる。その結果、バルブ１００が回動変位する際に摺動抵抗が生じ、前記バルブ１００を含む通路長切換部１０６を円滑に作動させることができないと共に、前記第１及び第２シール部材１１０、１１２の摩耗がバルブ１００の摺動によって促進され、その耐久性が低下してしまうことが懸念される。   That is, the valve 100 is slidably displaced along the first and second seal members 110 and 112 via the first and second opening end portions 102 and 104. As a result, sliding resistance is generated when the valve 100 is rotationally displaced, the passage length switching unit 106 including the valve 100 cannot be operated smoothly, and the first and second seal members 110 and 112 are not operated. There is a concern that the wear is promoted by the sliding of the valve 100 and the durability thereof is lowered.

また、図７に示される通路長切換部１０６を有する吸気マニホールド装置１０８と比較し、第１及び第２シール部材３６、３８に対するバルブ４２の摺接範囲を小さくすることができるため、前記第１及び第２シール部材３６、３８の摩耗を抑制することが可能となり、それに伴って、前記第１及び第２シール部材３６、３８の耐久性を向上させることができる。   Further, as compared with the intake manifold device 108 having the passage length switching unit 106 shown in FIG. 7, the sliding contact range of the valve 42 with respect to the first and second seal members 36 and 38 can be reduced. And it becomes possible to suppress wear of the 2nd seal members 36 and 38, and the durability of the 1st and 2nd seal members 36 and 38 can be improved in connection with it.

さらに、通路長切換部１８を切換動作させるための駆動部への負荷も小さくなるため、前記駆動部の小型化を図ることができて好適である。   Furthermore, since the load on the drive unit for switching the path length switching unit 18 is also reduced, the drive unit can be reduced in size, which is preferable.

さらにまた、第１及び第２シール部材３６、３８の摩耗を抑制可能とすることにより、前記第１及び第２シール部材３６、３８をゴム等の弾性材料から形成することが可能となり、前記第１及び第２シール部材３６、３８に対してバルブ４２を当接させた際の吸気通路１６内の気密をより一層確実に保持することができる。   Furthermore, by making it possible to suppress wear of the first and second seal members 36, 38, the first and second seal members 36, 38 can be formed from an elastic material such as rubber. The airtightness in the intake passage 16 when the valve 42 is brought into contact with the first and second seal members 36 and 38 can be more reliably maintained.

本発明に係る内燃機関用吸気マニホールド装置は、上述の実施の形態に限らず、本発明の要旨を逸脱することなく、種々の構成を採り得ることはもちろんである。   The intake manifold device for an internal combustion engine according to the present invention is not limited to the above-described embodiment, and it is needless to say that various configurations can be adopted without departing from the gist of the present invention.

本発明の実施の形態に係る内燃機関用吸気マニホールド装置の全体縦断面図である。1 is an overall longitudinal sectional view of an intake manifold device for an internal combustion engine according to an embodiment of the present invention. 図１の吸気マニホールド装置における通路長切換部近傍を示す拡大断面図である。FIG. 2 is an enlarged cross-sectional view showing the vicinity of a passage length switching portion in the intake manifold device of FIG. 1. 図２に示す通路長切換部を構成するバルブが所定角度だけ回動し、バルブの第１及び第２開口端部が第１及び第２シール部材から離間した状態を示す拡大断面図である。FIG. 3 is an enlarged cross-sectional view illustrating a state in which a valve constituting the passage length switching unit illustrated in FIG. 2 rotates by a predetermined angle and first and second opening end portions of the valve are separated from first and second seal members. 図３のバルブがさらに所定角度だけ回動した状態を示す拡大断面図である。FIG. 4 is an enlarged cross-sectional view showing a state where the valve of FIG. 3 is further rotated by a predetermined angle. 図１の内燃機関用吸気マニホールド装置において、吸気通路長が切り換えられた状態を示す全体縦断面図である。FIG. 2 is an overall longitudinal sectional view showing a state where an intake passage length is switched in the intake manifold device for an internal combustion engine of FIG. 1. 図５の吸気マニホールド装置における通路長切換部近傍を示す拡大断面図である。FIG. 6 is an enlarged cross-sectional view showing the vicinity of a passage length switching portion in the intake manifold device of FIG. 5. 内燃機関用吸気マニホールド装置の比較例を示す拡大断面図である。It is an expanded sectional view showing a comparative example of an intake manifold device for an internal combustion engine.

符号の説明Explanation of symbols

１０…吸気マニホールド装置 １２…分岐管
１４…吸気マニホールド １６…吸気通路
１８…通路長切換部 ２０…チャンバー
２２…エンジン ２８…第１空間部
３０…第２空間部 ３２…湾曲部
３４…接続部 ３６、１１０…第１シール部材
３６ａ、３８ａ…円弧面 ３６ｂ、３８ｂ…平坦面
３８、１１２…第２シール部材 ４２…バルブ
４６…第１開口端部 ４６ａ、４８ａ…円弧部
４６ｂ、４８ｂ…平坦部 ４８…第２開口端部 DESCRIPTION OF SYMBOLS 10 ... Intake manifold apparatus 12 ... Branch pipe 14 ... Intake manifold 16 ... Intake passage 18 ... Passage length switching part 20 ... Chamber 22 ... Engine 28 ... 1st space part 30 ... 2nd space part 32 ... Curved part 34 ... Connection part 36 110 ... first seal members 36a, 38a ... arc surfaces 36b, 38b ... flat surfaces 38, 112 ... second seal members 42 ... valve 46 ... first opening end portions 46a, 48a ... arc portions 46b, 48b ... flat portions 48 ... Second opening end

Claims (4)

内燃機関を構成する本体部の各シリンダに独立して接続され、スロットル装置から吸入空気が導入されるチャンバーと連通する吸気通路を有する吸気マニホールドと、前記吸気通路に臨む前記吸気マニホールドの内部に設けられ、前記内燃機関の運転状況に応じて前記吸気通路の通路長を切り換える通路長切換部とを備える内燃機関用吸気マニホールド装置において、
前記通路長切換部は、前記吸気通路を構成し前記チャンバーに接続される第１通路部と、前記吸気通路を構成し前記本体部に接続される第２通路部との間に設けられ、支軸を中心として前記吸気マニホールドに回動自在に設けられた切換弁を備え、
前記切換弁には、所定半径からなる断面円弧状の円弧面を有し、前記円弧面を介して前記第１及び第２通路部の端部に当接自在な当接部を備え、前記円弧面の半径中心が前記切換弁の回動中心に対して偏心していることを特徴とする内燃機関用吸気マニホールド装置。 An intake manifold that is independently connected to each cylinder of the main body constituting the internal combustion engine and has an intake passage communicating with a chamber into which intake air is introduced from a throttle device, and provided inside the intake manifold facing the intake passage An intake manifold device for an internal combustion engine comprising a passage length switching unit that switches a passage length of the intake passage according to an operating state of the internal combustion engine,
The passage length switching portion is provided between a first passage portion constituting the intake passage and connected to the chamber, and a second passage portion constituting the intake passage and connected to the main body portion. A switching valve provided rotatably on the intake manifold around an axis;
The switching valve has a circular arc surface with a circular arc section having a predetermined radius, and includes a contact portion that can freely contact the end portions of the first and second passage portions via the circular arc surface. An intake manifold device for an internal combustion engine, wherein a radius center of a surface is eccentric with respect to a rotation center of the switching valve. 請求項１記載の装置において、
前記第１及び第２通路部の端部には、弾性材料から形成され、前記円弧面が当接自在なシール部材が設けられることを特徴とする内燃機関用吸気マニホールド装置。 The apparatus of claim 1.
An intake manifold device for an internal combustion engine, characterized in that end portions of the first and second passage portions are provided with a seal member made of an elastic material and capable of abutting against the arc surface. 請求項１又は２記載の装置において、
前記円弧面の半径中心は、前記切換弁の軸線を中心として前記当接部が前記第１及び第２通路部の端部から離間する際に前記切換弁が回動する方向に所定距離だけ偏心して設定されることを特徴とする内燃機関用吸気マニホールド装置。 The apparatus according to claim 1 or 2,
The center of the radius of the arcuate surface is deviated by a predetermined distance in the direction in which the switching valve rotates when the abutting portion is separated from the ends of the first and second passage portions around the axis of the switching valve. An intake manifold device for an internal combustion engine, characterized by being set with heart. 請求項１〜３のいずれか１項に記載の装置において、
前記当接部は、前記切換弁の軸線方向に沿った両端部にそれぞれ設けられることを特徴とする内燃機関用吸気マニホールド装置。 The device according to any one of claims 1 to 3,
The intake manifold device for an internal combustion engine, wherein the contact portions are provided at both end portions along the axial direction of the switching valve.
JP2007334006A 2007-12-26 2007-12-26 Intake manifold device for internal combustion engine Withdrawn JP2009156126A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011106406A (en) * 2009-11-19 2011-06-02 Aisin Seiki Co Ltd Intake device for internal combustion engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011106406A (en) * 2009-11-19 2011-06-02 Aisin Seiki Co Ltd Intake device for internal combustion engine

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