JP4389383B2

JP4389383B2 - Valve timing control device

Info

Publication number: JP4389383B2
Application number: JP2000391282A
Authority: JP
Inventors: 和己小川
Original assignee: Aisin Seiki Co Ltd; Aisin Corp
Current assignee: Aisin Corp
Priority date: 1999-12-24
Filing date: 2000-12-22
Publication date: 2009-12-24
Anticipated expiration: 2020-12-22
Also published as: JP2001241307A

Description

【０００１】
【発明の属する技術分野】
本発明は、内燃機関の動弁装置において吸排気弁の開閉時期を制御するために使用される弁開閉時期制御装置に関する。
【０００２】
【従来の技術】
この種の弁開閉時期制御装置の１つとして、カムシャフトと共に回転する回転部材に所定範囲で相対回転可能に外装されクランクシャフトのクランクスプロケット又はプーリからの回転動力が伝達されると共に内周部に凹部を有する回転伝達部材と、回転部材に設けられた複数のベーンと、凹部と回転部材との間に形成されベーンによって進角用室と遅角用室とに二分される複数の流体圧室と、進角用室に流体を給排する第１流体通路と、遅角用室に流体を給排する第２流体通路と、回転部材と回転伝達部材の相対位相が所定の位相である時に回転部材と回転伝達部材の相対位相を規制する相対位相規制機構とを備えたものがあり、例えば特開平１−９２５０４号公報や特開平９−２５０３１０号公報に開示されている。
【０００３】
上記した各公報に開示されている弁開閉時期制御装置においては、第１流体通路を介して進角用室へ作動流体を供給すると共に第２流体通路を介して遅角用室から作動油を排出することにより、回転部材が回転伝達部材に対してベーンが凹部の進角側の周方向端面に当接する最大進角位置までの任意な位置に進角方向へ回転して弁開閉時期が進角され、第２流体通路を介して遅角用室へ作動流体を供給すると共に第１流体通路を介して進角用室から作動油を排出することにより、回転部材が回転伝達部材に対してベーンが凹部の遅角側の周方向端面に当接する最大遅角位置までの任意な位置に遅角方向へ回転して弁開閉時期が遅角される。
【０００４】
また、上記した各公報に開示されている弁開閉時期制御装置においては、内燃機関の運転中、カムシャフトに作用する変動トルクにより回転部材には常に遅角方向への力が作用しており、内燃機関の停止時に流体圧室への作動油の供給が停止されると、流体圧室の油圧によってベーンを保持できなくなり、回転部材は回転伝達部材に対して遅角方向へ回転し（クランクシャフトが完全に停止するまでの間）、回転部材と回転伝達部材は停止直前の両者の相対位相に応じた相対位相で停止する。この状態にて内燃機関が始動されると、上記した遅角方向への力により回転部材は回転伝達部材に対して遅角方向へ回転し、ベーンが凹部の遅角側の周方向端面に当接する最大遅角位置での位相となる。この状態にて内燃機関が始動されると、流体圧室の油圧が上昇し該油圧によりベーンを保持することができるようになるまでは不安定な状態となり、カムシャフトに作用する変動トルクによってベーンが振動し、凹部の周方向端面と繰り返して衝突して打音が生じたりするので、これを回避するために、相対位相規制機構により回転部材と回転伝達部材との相対位相が最大遅角位置にて規制されるようになっている。
【０００５】
【発明が解決しようとする課題】
ところで、内燃機関の高速回転域では、ピストンが上死点に向かい始めても、吸気が慣性により更にシリンダ内へ入り込もうとするため、吸気弁の閉時期を遅らせることにより体積効率が向上して内燃機関の出力向上を図ることができることが知られている。
【０００６】
しかしながら、上記した各公報に開示される弁開閉時期制御装置を吸気弁の開閉時期を制御するために用いる場合には、最大遅角位置での弁開閉時期は、上記したように内燃機関の始動時に吸気が可能な時期に設定される必要があるため、高速回転域において吸気弁の閉時期を遅らせて吸気の慣性による体積効率の向上を図ることができない。これは、最大遅角位置での弁開閉時期を吸気の慣性による体積効率の向上が可能な時期に設定すると、最大遅角位置での内燃機関の始動時に、ピストンが下死点を過ぎ上死点に向かい始めても吸気弁が開いていて、また吸気に慣性がないため、一度吸入した吸気が逆流して排出してしまい、圧縮比が上がらずに、燃焼ができない状態が発生し、内燃機関の始動が困難となるからである。尚、この問題は、最大遅角位置での弁開閉時期を吸気の慣性による体積効率の向上が可能な時期に設定しなくても、上記した各公報に開示される弁開閉時期制御装置のように、最大遅角位置での弁開閉時期を始動時に吸気が可能な時期に設定した場合であっても、吸気弁の閉時期がピストンの下死点後に設定されていると、気圧の低い高所等では発生しやすい。
【０００７】
また、上記した各公報に開示される弁開閉時期制御装置を排気弁の開閉時期を制御するために用いる場合にも、排気弁の閉時期を同様に遅らせると、吸気弁と排気弁のオーバーラップ期間が長くなり、内部ＥＧＲ量（排気ガス再循環量）が増大して内燃機関の始動性の低下を招く。
【０００８】
これら問題を解消すべく、回転部材と回転伝達部材との相対位相が吸気の慣性による体積効率の向上が可能な弁開閉時期に対応する最大遅角位置よりも所定角度だけ進角した中間位置にて相対位相規制機構により規制されるようにした装置が特開平９−３２４６１３号公報に提案されている。しかしながら、この装置においては、内燃機関の停止時に上記したように回転部材が回転伝達部材に対して遅角方向へ回転する際、回転部材と回転伝達部材の相対位相が所定の中間位置になるのは一瞬であるため、相対位相規制機構により所定の中間位置に回転部材と回転伝達部材の相対位相を規制することができない場合があり、内燃機関の始動不良及び内燃機関の始動時におけるベーンと回転伝達部材の凹部の周方向端面との衝突による打音の発生を確実に防止することはできない。
【０００９】
それゆえ、本発明は、内燃機関の始動時におけるベーンによる打音の発生及び始動不良を確実に防止しつつ、その可変制御領域を拡大させることができる弁開閉時期制御装置を提供することを、その課題とする。
【００１０】
上記課題を解決するために講じた本発明の技術的手段は、内燃機関のクランクシャフト又はカムシャフトの一方と共に回転する回転部材と、該回転部材に所定範囲で相対回転可能に外装され前記クランクシャフト又は前記カムシャフトの他方と共に回転する回転伝達部材と、前記回転部材に設けられたベーンと、前記回転部材と前記回転伝達部材との間に形成され前記ベーンによって進角用室と遅角用室とに二分される流体圧室とを備え、前記進角用室及び前記遅角用室へ印加される流体圧によって前記回転部材と前記回転伝達部材が相対回転し、前記クランクシャフトの回転位相に対する前記カムシャフトの回転位相が変更させられることによって前記カムシャフトにより駆動される弁の開閉時期を変更する弁開閉時期制御装置において、前記回転部材と前記回転伝達部材の相対回転を、前記遅角用室の容積を最小とする最大進角位置と前記進角用室の容積を最小とする最大遅角位置との間の略中間に前記ベーンが位置する前記内燃機関の始動時対応位置から前記最大遅角位置への前記回転部材と前記回転伝達部材の相対回転を規制する第１相対回転規制手段と、前記始動時対応位置から前記最大進角位置への前記回転部材と前記回転伝達部材の相対回転を規制する第２相対回転規制手段とを設け、前記第１相対回転規制手段及び前記第２相対回転規制手段のうち一方が規制している状態で前記始動時対応位置に移動すると、前記最大遅角位置及び前記最大進角位置のうち一方への前記回転部材と前記回転伝達部材の相対回転を規制し、前記第１相対回転規制手段及び前記第２相対回転規制手段のうち他方が規制し、前記始動時対応位置に保持することである。
【００１１】
上記した手段によれば、内燃機関の停止時に流体圧室への作動流体の供給が停止されると、流体圧室の流体圧によってベーンを保持できなくなり、回転部材は回転伝達部材に対して遅角方向へ回転するものの、内燃機関の始動時には第１及び第２相対回転規制手段により回転部材と回転伝達部材の相対位相がベーンが流体圧室の略中間に位置される始動時対応位置にあるときの相対位相に保持される。これにより、内燃機関の始動時にベーンが流体圧室の周方向端面に衝突して打音が発生するのが的確に防止される。
【００１２】
また、内燃機関の始動時の弁開閉時期がベーンの始動時対応位置における回転部材と回転伝達部材の相対位相時に得られるので、最大遅角位置では始動時対応位置での相対位相時よりも更に弁の開閉時期を遅らせることができ、吸気の慣性を利用して体積効率の向上を図ることが可能となると共に、始動時の弁開閉時期を進角させることができ、圧縮比低下による内燃機関の始動不良を防止することが可能となる。
【００１３】
また、上記した手段においては、前記第１相対回転規制手段は前記最大進角位置から前記最大遅角位置への前記回転部材と前記回転伝達部材の相対回転を、前記流体圧室の略中間に前記ベーンが位置する前記内燃機関の始動時対応位置にて規制すると共に、前記遅角用室へ印加される流体圧によってその規制が解除され、第２相対回転規制手段は前記最大遅角位置から前記最大進角位置への前記回転部材と前記回転伝達部材の相対回転を前記始動時対応位置にて規制すると共に、前記進角用室へ印加される流体圧によってその規制を解除するように構成することができる。
【００１４】
また、上記した手段においては、前記第１相対回転規制手段は前記最大進角位置から前記最大遅角位置への前記回転部材と前記回転伝達部材の相対回転を、前記流体圧室の略中間に前記ベーンが位置する前記内燃機関の始動時対応位置にて規制すると共に、前記遅角用室と前記進角室とに印加される流体圧によってその規制が解除され、第２相対回転規制手段は前記最大遅角位置から前記最大進角位置への前記回転部材と前記回転伝達部材の相対回転を前記始動時対応位置にて規制すると共に、前記進角用室と前記遅角室とに印加される流体圧によってその規制を解除するように構成することもできる。
【００１５】
また、上記した手段においては、前記第１相対回転規制手段は前記最大進角位置から前記最大遅角位置への前記回転部材と前記回転伝達部材の相対回転を、前記流体圧室の略中間に前記ベーンが位置する前記内燃機関の始動時対応位置にて規制すると共に、前記遅角用室と前記進角室とに印加される流体圧によってその規制が解除され、第２相対回転規制手段は前記最大遅角位置から前記最大進角位置への前記回転部材と前記回転伝達部材の相対回転を前記始動時対応位置にて規制すると共に、前記進角用室と前記遅角室とに印加される流体圧によってその規制を解除されること、前記第１相対回転規制手段は、前記回転部材または前記回転伝達部材の一方にばね付勢されて収容される第１規制部材と、前記回転部材または前記回転伝達部材の他方に形成されて前記第１規制部材が嵌入することで前記回転部材と前記回転伝達部材の前記始動時対応位置から前記最大進角位置への相対回転を許容し、前記始動時対応位置から前記最大遅角位置への相対回転を規制する第１規制溝とを有し、前記第２相対回転規制手段は、前記回転部材または前記回転伝達部材の一方にばね付勢されて収容される第２規制部材と、前記回転部材または前記回転伝達部材の他方に形成されて前記第２規制部材が嵌入することで前記回転部材と前記回転伝達部材の前記始動時対応位置から前記最大進角位置への相対回転を規制し、前記始動時対応位置から前記最大遅角位置への相対回転を許容する第２規制溝とを有することが望ましい。
【００１６】
更に、上記した手段においては、前記回転部材を前記回転伝達部材に対して進角側に所定の付勢力で常時付勢する付勢部材を更に備えることが望ましい。
【００１７】
【発明の実施の形態】
以下、本発明に従った弁開閉時期制御装置の第１実施形態を図面に基づき、説明する。
【００１８】
図１乃至図４において、弁開閉時期制御装置は、内燃機関のシリンダヘッドに回転自在に支持されたカムシャフト１０の先端部（図１の左端）に一体的に組付けた内部ロータ２０からなる回転部材と、カムシャフト１０及び内部ロータ２０に所定範囲で相対回転可能に外装された外部ロータ３０、フロントプレート４０、リアプレート５０及び外部ロータ３０の外周に一体的に設けたタイミングスプロケット３１から成る回転伝達部材と、内部ロータ２０に組付けた４枚のベーン８０と、フロントプレート４０に組付られる第１ロックピン８２等からなる第１相対回転規制手段と、フロントプレート４０に組付けられる第２ロックピン８０等からなる第２相対回転規制手段と、回転部材と回転伝達部材間に介装されて回転伝達部材に対して回転部材を進角側に付勢するトーションスプリング６０（付勢部材）等によって構成されている。尚、タイミングスプロケット３１には、周知のように、図示省略したクランクシャフトからクランクスプロケットとタイミングチェーンを介して図２の時計方向に回転動力が伝達されるように構成されている。
【００１９】
カムシャフト１０は、吸気弁を開閉する図示しない周知のカムを有していて、内部にはカムシャフト１０の軸方向に延びる進角通路１１及び遅角通路１２が設けられている。進角通路１１は、カムシャフト１０に設けた取付ボルト９１用の取付孔内に形成されていて、カムシャフト１０に設けた径方向の通路及び環状溝１４とシリンダヘッドに設けた接続通路１６を通して制御弁１００の接続ポート１０１に接続されている。遅角通路１２は、カムシャフト１０に設けた径方向の通路及び環状溝１３とシリンダヘッドに設けた接続通路１５を介して制御弁１００の接続ポート１０２に接続されている。
【００２０】
制御弁１００は、ソレノイド１０３へ通電することによりハウジング内に軸方向に移動可能に嵌挿されたスプール１０４をスプリング１０５に抗して図１の左方向へ移動できるものであり、非通電時には当該内燃機関によって駆動されるオイルポンプ１１０に接続された供給ポート１０６が接続ポート１０２に連通すると共に、接続ポート１０１が排出ポート１０７に連通するように、また通電時には供給ポート１０６が接続ポート１０１に連通すると共に、接続ポート１０２が排出ポート１０７に連通するように構成されている。このため、制御弁１００のソレノイド１０３の非通電時には遅角通路１２に作動油が供給され、ソレノイド１０３の通電時には進角通路１１に作動油が供給され、ソレノイド１０３への通電が図示しない制御装置によりデューティ制御される。
【００２１】
内部ロータ２０は、単一の取付ボルト９１によってスペーサ９０を介してカムシャフト１０に一体的に固着されていて、４枚の各ベーン７０を夫々径方向に移動可能に取り付けるためのベーン溝２１を有すると共に、各ベーン７０によって区画された進角用室Ｒ１（図２において左上のものを除く）に進角通路１１から作動油を給排するように進角通路１１と各進角用室Ｒ１を内部ロータ２０の内孔とボルト９１間に形成される通路を介して連通する通路２４と、カムシャフト１０の先端面に対向する側の一端面に形成され遅角通路１２に連通する環状溝２０ａと、該環状溝２０ａから軸方向に他端面側に延びる４つの通路２５と、各ベーン７０によって区画された遅角用室Ｒ２に遅角通路１２から作動油を環状溝２０ａ及び通路２５を通して給排するように各通路２５と各遅角用室Ｒ２（図２において左下のものを除く）を連通する通路２７とを有している。尚、各ベーン７０は、ベーン溝２１の底部に収容したベーンスプリング７１によって径方向外方に付勢されている。
【００２２】
また、内部ロータ２０の他端面側には、内部ロータ２０と外部ロータ３０の相対位相が後述する内燃機関の始動時に対応する相対位相から後述する最大進角位置に対応する相対位相の間にある時に第２ロックピン８０の頭部が所定量嵌入されるように周方向に延びる第２規制溝２３ｃ（図３参照）と、内部ロータ２０と外部ロータ３０の相対位相が内燃機関の始動時に対応する相対位相から後述する最大遅角位置に対応する相対位相の間にある時に第１ロックピン８２の頭部が所定量嵌入されるように周方向に延びる第１規制溝２６ｃ（図７参照）とが形成されている。内部ロータ２０の回転方向側（進角側）の第２規制溝２３ｃの端部は、内部ロータ２０の外周面に開口されており、また内部ロータ２０の反回転方向側の端部は、内部ロータ２０の外周面に開口されている。
【００２３】
更に、内部ロータ２０には、内部ロータ２０の内孔とボルト９１間に形成される通路から径方向外方に延び、内部ロータ２０の外周面に開口する通路２３ａと、該通路２３ａと第２規制溝２３ｃを連通する通路２３ｂと、図２において左下の通路２５から径方向外方に延び、内部ロータの外周面に開口する通路２６ａと、該通路２６ａと第１規制溝２６ｃを連通する通路２６ｂとが形成されている。尚、通路２３ｂは、内部ロータ２０の反回転方向側の第２規制溝２３ｃの端部の底部に開口するように形成されており、通路２６ｂは、内部ロータ２０の回転方向側の第１規制溝２６ｃの端部の底部に開口するように形成されている。また、第２規制溝２３ｃの底部には、内部ロータ２０の反回転方向側にて通路２３ｂに連通され、周方向に延びる溝２３ｄが形成されており、第１規制溝２６ｃの底部には、内部ロータ２０の回転方向側にて通路２６ｂに連通され、周方向に延びる溝２６ｄが形成されている。
【００２４】
外部ロータ３０は、内部ロータ２０の外周に所定範囲で相対回転可能に組付けられていて、その両側にはフロントプレート４０とリアプレート５０が接合され、５本の連結ボルト９２によって一体的に連結されている。また、外部ロータ３０の内周には所定の周方向間隔で４個の突部３２が径方向内方に向けて夫々突出形成されていて、これら突部３２の内周面が内部ロータ２０の外周面に摺接する構成で外部ロータ３０が内部ロータ２０に回転自在に支承されている。フロントプレート４０には、第２ロックピン８０と第２スプリング８１を収容する第２退避孔４２と、第１ロックピン８２と第１スプリング８３を収容する第１退避孔４３とが、外部ロータ３０の軸方向に形成されている。第２退避孔４２は、内部ロータ２０と外部ロータ３０の相対位相が後述する内燃機関の始動時に対応する相対位相から後述する最大遅角位置に対応する相対位相の間にある時に、内部ロータ２０の第２規制溝２３ｃに対向するように位置されており、第１退避孔４３は、内部ロータ２０と外部ロータ３０の相対位相が内燃機関の始動時に対応する相対位相から後述する最大進角位置に対応する相対位相の間にある時に、内部ロータ２０の第１規制溝２６ｃに対向するように位置されている。
【００２５】
各ベーン７０は、先端の断面形状が円弧形状であり、両プレート４０、５０間にて内部ロータ２０のベーン溝２１に径方向に移動可能に取り付けられていて、外部ロータ３０と、外部ロータ３０の各突部３２と、内部ロータ２０と、フロントプレート４０と、リアプレート５０との間に形成される流体圧室Ｒ０を進角用室Ｒ１と遅角用室Ｒ２とに二分しており、外部ロータ３０に形成した突部３２の周方向端面に１つのベーン７０が当接することにより、当該弁開閉時期制御装置により調整される位相（内部ロータ２０と外部ロータ３０の所定の相対回転範囲）が制限されるようになっている。即ち、図１１に示すように、図示左下のベーン７０が突部３２の遅角側の周方向端面に当接する（最大進角位置）ことで内部ロータ２０の外部ロータ３０に対する進角側への相対回転が制限され、図１４に示すように図示左上のベーン７０が突部３２の進角側の周方向端面に当接する（最大遅角位置）ことで内部ロータ２０の外部ロータ３０に対する遅角側への相対回転が制限される。
【００２６】
第２ロックピン８０は、第２退避孔４２内に軸方向へ摺動可能に組み付けられていて、第２ロックピン８０と第２退避孔４２の底部間に介装される第１スプリング８１によって内部ロータ２０の他側面に向けて付勢されている。また、第１ロックピン８２は、第１退避孔４３内に軸方向へ摺動可能に組み付けられていて、第１ロックピン８２と第１退避孔４３の底部間に介装される第２スプリング８４によって内部ロータ２０の他側面に向けて付勢されている。これにより、内部ロータ２０と外部ロータ３０の相対位相が内燃機関の始動時に対応する相対位相から最大遅角位置にある時の相対位相の間になると、第２ロックピン８０の頭部が第２規制溝２３ｃ内に嵌入し、始動時に対応する位置から最大遅角位置への内部ロータ２０と外部ロータ３０の相対回転が許容されると共に、始動時に対応する位置から最大進角位置への内部ロータ２０と外部ロータ３０の相対回転が規制される。また、内部ロータ２０と外部ロータ３０の相対位相が内燃機関の始動時に対応する相対位相から最大進角位置にある時の相対位相の間になると、第１ロックピン８２の頭部が第１規制溝２６ｃ内に嵌入し、始動時に対応する位置から最大進角位置への内部ロータ２０と外部ロータ３０の相対回転が許容されると共に、始動時に対応する位置から最大遅角位置への内部ロータ２０と外部ロータ３０の相対回転が規制される。尚、内部ロータ２０と外部ロータ３０の相対位相が内燃機関の始動時に対応する相対位相にある時には、第２ロックピン８０が第２規制溝２３ｃに嵌入すると共に、第１ロックピン８２が第１規制溝２６ｃに嵌入して、内部ロータ２０と外部ロータ３０の相対位相が保持される。
【００２７】
本実施形態においては、内部ロータ２０からなる回転部材は、外部ロータ３０、フロントプレート４０及びリアプレート５０からなる回転伝達部材に対して、トーションスプリング６０により常時進角方向に付勢されている。尚、トーションスプリング６０の付勢力は、内燃機関の運転中、カムシャフト１０に作用する変動トルクの平均値（カムシャフト１０を遅角側へ回転させるように作用する平均トルク）相当となるように設定されている。トーションスプリング６０は、フロントプレート４０の円筒部４１と、該円筒部４１に連続するように内部ロータ２０の他側面に形成される環状溝内に収容されていて、一端を円筒部４１の端部に形成されるフランジ部４６に係止されると共に、他端を環状溝の底部に係止されている。
【００２８】
また、本実施形態においては、内部ロータ２０と外部ロータ３０の相対位相が内燃機関の始動時に対応する相対位相にあるときに、図示しない吸気弁の開閉時期が内燃機関の始動が可能な時期になるように設定されている。尚、本実施形態においては、この始動時に対応する相対位相の時、各ベーン７０は、流体圧室Ｒ０の略中間に位置され、最大遅角位置（図１４参照）から内部ロータ２０が外部ロータ３０に対して所定角度θだけ進角側に相対回転（図８参照）した状態にある。
【００２９】
上記のように構成した本実施形態の弁開閉時期制御装置においては、内部ロータ２０と外部ロータ３０の相対位相が図８乃至図１０に示す内燃機関の始動時に対応する相対位相にある時に、内燃機関が始動されて内燃機関によって駆動されるオイルポンプ１１０から制御弁１００を介して進角通路１１及び遅角通路１２に第１所定圧以上の作動流体が供給されるまでは、第２ロックピン８０及び第１ロックピン８２の各頭部が夫々第２規制溝２３ｃ及び第１規制溝２６ｃに嵌入されている（図９及び図１０参照）。
【００３０】
したがって、図示しない吸気弁の駆動の際にカムシャフト１０に作用する変動トルクによって内部ロータ２０と外部ロータ３０が相対回転することが第１及び第２ロックピン８０、８２によって規制されて、相対的な回転振動を発生することがなく、かかる回転振動に伴う打音（ベーン７０と突部３２との衝接音）の発生が防止される。
【００３１】
制御弁１００が非通電状態にあり、内燃機関が始動してから所定時間が経過してオイルポンプ１１０から制御弁１００を介して遅角通路１２に第１所定圧以上の作動流体が供給されると、通路２５、通路２６ａ及び通路２６ｂを介して第１規制溝２６ｃに作動油が供給され、第１ロックピン８２がスプリング８３の付勢力に抗して退避孔４３内に移動し、頭部が第１規制溝２６ｃから退避孔４３内に退避する。一方、進角通路１１は制御弁１００を介してオイル溜め１２０に連通されているため、第２ロックピン８０はスプリング８１の付勢力により頭部が第２規制溝２３ｃに嵌入した状態に維持される。したがって、内部ロータ２０が外部ロータ３０に対して始動時対応位置から最大遅角位置側に相対回転することが許容される。この状態にて、オイルポンプ１１０から制御弁１００を介して遅角通路１２に供給される作動流体の圧力が第２所定圧以上（第１所定圧＜第２所定圧）になり、同作動流体が、遅角通路１２から環状溝２０ａ、通路２５、２７及び通路２６ａ、２６ｂ、第１規制溝２６ｃを通して各遅角用室Ｒ２に供給されると共に、各進角用室Ｒ１から各通路２４及び第２規制溝２３ｃ、通路２３ｂ、２３ａと進角通路１１と制御弁１００等を通して作動油が排出されると、内部ロータ２０と各ベーン７０が外部ロータ３０等に対して遅角側に相対回転し、この相対回転量（最大遅角量）は、図８に示す始動時対応位置から内部ロータ２０が外部ロータ３０に対して所定角度θだけ遅角側に相対回転して図１４に示すように１つのベーン（図示左上のベーン）７０が突部３２の進角側周方向端面に当接することにより制限される。尚、この時には、図１５及び図１６に示すように、第２ロックピン８０の頭部は第２規制溝２３ｃに嵌入し、第１ロックピン８２の頭部は第１規制溝２６ｃに嵌入せず、内部ロータ２０の他端面に摺接している。
【００３２】
また、制御弁１００の通電状態（ソレノイド１０３へ供給される電流のデューティ比を高くした）には、第２所定圧以上の作動流体が進角通路１１と各通路２４、２３ａ、２３ｂ及び第２規制溝２３ｃを通して各進角用室Ｒ１に供給されると共に、各遅角用室Ｒ２から各通路２５、２６ａ、２６ｂ、２７と遅角通路１２と制御弁１００等を通して作動油が排出されると、内部ロータ２０と各ベーン７０が外部ロータ３０等に対して進角側に相対回転する。この相対回転量（最大遅角量）は、図１１に示すように、１つのベーン７０（図示左下のベーン）が突部３２の遅角側周方向端面に当接することにより制限される。尚、この時には、図１２及び図１３に示すように、第１退避孔４３が第１規制溝２６ｃに対向した時点でスプリング８３により第１ロックピン８２の頭部は第１規制溝２６ｃに嵌入し、第２ロックピン８０の頭部は第２規制溝２３ｃに嵌入せず、内部ロータ２０の他端面に摺接している。
【００３３】
本実施形態においては、上記したように各ベーン７０は、流体圧室Ｒ０の略中間に位置され、最大遅角位置（図１４参照）から内部ロータ２０が外部ロータ３０に対して所定角度θだけ進角側に相対回転（図８参照）した状態にある、内部ロータ２０と外部ロータ３０の所定の相対位相の時に、図示しない吸気弁の開閉時期が内燃機関の始動が可能な時期になるように設定されている。そのため、この始動時対応位置からベーン７０が突部３２の進角側の周方向端面に当接する最大遅角位置までは内燃機関が始動可能な弁開閉時期よりも更に弁の開閉時期を遅らせることができ、内燃機関の高速回転時に、上記したように制御弁１００を制御して始動時対応位置より遅角側へ位相変換し、内燃機関の始動が困難な時期まで図示しない吸気弁の閉時期を遅らせることで、吸気の慣性により体積効率が向上し、内燃機関の出力向上を図ることができる。
【００３４】
内燃機関の停止時には、オイルポンプ１００の駆動が停止されて流体圧室Ｒ０への作動油の供給が停止されると共に、制御弁１００が非通電状態とされる。これにより、進角用室Ｒ１内の進角油圧による押圧力と遅角用室Ｒ２内の遅角油圧による押圧力がベーン７０に作用しなくなり、内部ロータ２０及びカムシャフト１０には、カムシャフト１０に作用する変動トルクによる上記した遅角方向への力（内燃機関のクランク軸が完全に停止するまでの間）のみが作用しており、停止直前の内部ロータ２０と外部ロータ３０の相対位相に応じて停止時の内部ロータ２０と外部ロータ３０の相対位相が決まることになる。内燃機関の停止時の相対位相が、上記した始動時対応位置における相対位相となった場合には、スプリング８２、８４により第１及び第２ロックピン８０、８２の頭部が夫々第１及び第２規制溝２３ｃ、２６ｃに嵌入し、内部ロータ２０と外部ロータ３０の相対位相が保持（ロック）される。
【００３５】
内燃機関の停止時の内部ロータ２０と外部ロータ３０の相対位相が、図５に示すように、始動時対応位置よりも進角側にある場合には、図６及び図７に示すように、第２ロックピン８０の頭部は第２規制溝２３ｃに嵌入せず、第１ロックピン８２の頭部のみが第１規制溝２６ｃに嵌入している。したがって、内部ロータ２０と外部ロータ３０との相対回転が、始動時対応位置と最大進角位置との間のみに規制された状態にある。この状態にて、内燃機関の始動の際に図示しないクランクシャフトがスタータに回転駆動されると、カムシャフト１０に作用する変動トルクにより内部ロータ２０は外部ロータ３０に対して始動時対応位置と最大進角位置との間でのみ相対回転し、内部ロータ２０と外部ロータ３０との相対位相が始動時対応位置になった時に第２ロックピン８０の頭部が第２規制溝２３ｃに嵌入される。これにより、内部ロータ２０と外部ロータ３０の相対位相が保持（ロック）される。
【００３６】
また、内燃機関の停止時の内部ロータ２０と外部ロータ３０の相対位相が、図２に示すように、始動時対応位置よりも遅角側にある場合には、図３及び図４に示すように、第２ロックピン８０の頭部が第２規制溝２３ｃに嵌入し、第１ロックピン８２の頭部は第１規制溝２６ｃに嵌入していない。したがって、内部ロータ２０と外部ロータ３０との相対回転が、始動時対応位置と最大遅角位置との間のみに規制された状態にある。この状態にて、内燃機関の始動の際に図示しないクランクシャフトがスタータに回転駆動されると、カムシャフト１０に作用する変動トルクにより内部ロータ２０は外部ロータ３０に対して始動時対応位置と最大遅角位置との間でのみ相対回転し、内部ロータ２０と外部ロータ３０との相対位相が始動時対応位置になった時に第１ロックピン８２の頭部が第１規制溝２６ｃに嵌入される。これにより、内部ロータ２０と外部ロータ３０の相対位相が保持（ロック）される。尚、オイルポンプ１１０より供給される作動流体の圧力が第１所定圧以上になるまでには内燃機関の始動後所定時間を要するため、上記したスタータによる回転駆動には第１及び第２ロックピンは各規制溝にスプリングにより嵌入される。
【００３７】
よって、内燃機関の始動時には、大きな回転変動を伴うカムシャフト１０、内部ロータ２０及び各ベーン７０等から成る回転部材と、外部ロータ３０、フロントプレート４０及びリアプレート５０等から成る回転伝達部材の不必要な相対回転が確実に規制され、回転部材と回転伝達部材の不必要な相対回転に伴うベーン７０による打音の発生を確実に防止することができる。
【００３８】
次に、本発明に従った弁開閉時期制御装置の第２実施形態を図面に基づき、説明する。
【００３９】
図１７から図１９は本発明の第２実施形態を示す図面である。本第２実施形態は、上記した第１実施形態に対して第１、第２ロックピンに供給する作動油の油圧経路が異なるだけでそれ以外の構成は同じであるため、第１実施形態と同じ構成、作用を有するものには第１実施形態の番号符号に２００を付した番号符号を付し、説明を省略する。
【００４０】
図１７は、本発明の第２実施形態のフロントプレート２４０を取り除いた図面である。図１７において内側ロータ２２０と外側ロータ２３０は始動時に対応する位置にそれぞれ位置しており、第１ロックピン２８２と、第２ロックピン２８０はそれぞれ第１規制溝２２６ｃ、第２規制溝２２３ｃに嵌入して内側ロータ２２０と外側ロータ２３０の相対回転を規制している。
【００４１】
図１８は図１７の１８―１８断面図である。
【００４２】
図１８において、第１退避孔２４３は第１ロックピン２８２の移動方向に大径部２４３ａと小径部２４３ｂとを有する段付孔である。第１退避孔２４３の内径が変化する部分には段部が形成されている。第１退避孔２４３の大径部２４３ａは第２ロックピン２８２の移動方向に対して段部の反インナーロータ２２０側に、小径部２４３ｂは第１ロックピン２８２の移動方向に対して段部のインナーロータ２２０側にそれぞれ形成されている。第１退避孔２４３のインナーロータ２２０側の底部は通路２２６ａと通路２２６ｂとを介して通路２５と連通する。
【００４３】
第１ロックピン２８２は小径部と大径部とを有する段付形状を有する。第１ロックピンの小径部は第１退避孔２４３の小径部２４３ｂ内を、第１ロックピン２８２の大径部は第１退避孔２４３の大径部２４３ａ内をそれぞれ摺動可能である。
【００４４】
また、フロントプレート２４０には通路２０３、２０４が形成され、第１退避孔２４３の段部と連通している。
【００４５】
図１９は図１７の１９―１９断面図である。
【００４６】
図１９において、第２退避孔２４２は第２ロックピン２８０の移動方向に大径部２４２ａと小径部２４２ｂとを有する段付孔である。第２退避孔２４２の内径が変化する部分には段部が形成されている。大径部は第２ロックピン２８０の移動方向に対して段部の反インナーロータ２２０側に、小径部２４２ｂは第２ロックピン２８０の移動方向に対して段部のインナーロータ２２０側にそれぞれ形成されている。第２退避孔２４２のインナーロータ２２０側の底部は通路２２３ａを介して通路２２３ａと連通する。
【００４７】
第２ロックピン２８０は小径部と大径部とを有する段付の円筒形状を有する。第２ロックピンの小径部は第２退避孔の小径部１４２ｂ内を、第２ロックピンの大径部は第２退避孔の大径部１４２ａ内をそれぞれ摺動可能である。
【００４８】
また、フロントプレート２４０には通路２０１、２０２が形成され、第２退避孔２４２の段部と連通している。これにより第２ロックピン２８０は通路２３ａ，２３ｂを介して第２ロックピン２８０の小径部に作動油が供給されるとき、遅角室Ｒ２、通路２０１、２０２を介して第２ロックピン２８０の段部に作動油が供給されるとき、あるいはその両方に作動油が供給されたときに第２ロックピン２８０はスプリングの付勢力に逆らって第２退避孔内に退避し、インナーロータ２２０とアウターロータ２３０の相対回転が許容される。
【００４９】
これにより第１ロックピン２８２は通路２５ａ、２５ｂを介して第１ロックピン２８２の小径部に作動油が供給されるときと、遅角室Ｒ２、通路２０３、２０４を介して第１ロックピン２８２の段部に作動油が供給されるとき、あるいはその両方に作動油が供給されたときに第１ロックピン２８２はスプリングの付勢力に逆らって第１退避孔２４３内に退避し、インナーロータ２２０とアウターロータ２３０の相対回転を許容するように構成されている。
【００５０】
以上のように、第１、第２実施形態によれば、内燃機関の始動時におけるベーン７０、２７０と突部３２、２３２の周方向端面との衝突による打音の発生及び内燃機関の始動不良を防止しつつ、内燃機関の高速回転域において体積効率の向上を図ることができる。
【００５１】
上記実施形態においては、吸気用のカムシャフトに組付けられる弁開閉時期制御装置に本発明を実施したが、本発明は排気用のカムシャフトに組付けられる弁開閉時期制御装置にも同様に実施し得るものである。
【００５２】
また、上記した第１実施形態においては、第２ロックピン８０の規制解除を進角用室への作動流体で行ない、第１ロックピン８２の規制解除を遅角用室への作動流体で行うようにしたが、両ロックピンの規制解除のための作動流体を進角用室及び遅角用室への通路とは異なる通路を介して供給するようにしても良い。
【００５３】
【発明の効果】
以上の如く、本発明によれば、内燃機関の停止時に流体圧室への作動流体の供給が停止されると、流体圧室の流体圧によってベーンを保持できなくなり、回転部材は回転伝達部材に対して遅角方向へ回転するものの、内燃機関の始動時には第１及び第２相対回転規制手段により回転部材と回転伝達部材の相対位相がベーンが流体圧室の略中間に位置される始動時対応位置にあるときの相対位相に保持される。これにより、内燃機関の始動時にベーンが流体圧室の周方向端面に衝突して打音が発生するのを的確に防止することができる。
【００５４】
また、内燃機関の始動時の弁開閉時期がベーンの始動時対応位置における回転部材と回転伝達部材の相対位相時に得られるので、最大遅角位置では始動時対応位置での相対位相時よりも更に弁の開閉時期を遅らせることができ、内燃機関の高速回転時に吸気の慣性を利用して体積効率の向上を図ることで内燃機関の出力を向上することができると共に、始動時の弁開閉時期を進角させることができ、圧縮比低下による内燃機関の始動不良を防止することができる。
【図面の簡単な説明】
【図１】本発明に従った弁開閉時期制御装置の第１実施形態を示す縦断側面図である。
【図２】フロントプレート等を外した状態における図１に示す第１実施形態のロック位置よりも遅角側で内燃機関が停止した状態を示す正面図である。
【図３】図２の３−３断面図である。
【図４】図２の４−４断面図である。
【図５】フロントプレート等を外した状態における図１に示す第１実施形態のロック位置よりも進角側で内燃機関が停止した状態を示す正面図である。
【図６】図５の６−６断面図である。
【図７】図５の７−７断面図である。
【図８】フロントプレート等を外した状態における図１に示す第１実施形態のロック状態を示す正面図である。
【図９】図８の９−９断面図である。
【図１０】図８の１０−１０断面図である。
【図１１】フロントプレート等を外した状態における図１に示す第１実施形態の進角作動状態を示す正面図である。
【図１２】図１１の１２−１２断面図である。
【図１３】図１１の１３−１３断面図である。
【図１４】フロントプレート等を外した状態における図１に示す第１実施形態の遅角作動状態を示す正面図である。
【図１５】図１４の１５−１５断面図である。
【図１６】図１４の１６−１６断面図である。
【図１７】フロントプレート等を外した状態における第２実施形態のロック状態を示す正面図である。
【図１８】図１７の１８−１８断面図である。
【図１９】図１７の１９−１９断面図である。
【符号の説明】
１０、２１０カムシャフト
１１、２１１進角通路
１２、２１２遅角通路
２０、２２０内部ロータ（回転部材）
２３ｃ、２２３ｃ第２規制溝（第２相対回転規制手段）
２６ｃ、２２６ｃ第１規制溝（第１相対回転規制手段）
３０、２３０外部ロータ（回転伝達部材）
４０、２４０フロントプレート（回転伝達部材）
４２、２４２第２退避孔
４３、２４３第１退避孔
５０、２５０リアプレート（回転伝達部材）
７０、２７０ベーン
８０、２８０第２ロックピン（第２相対回転規制手段）
８２、２８２第１ロックピン（第１相対回転規制手段）
１００制御弁
１１０オイルポンプ
Ｒ０流体圧室
Ｒ１進角用室
Ｒ２遅角用室[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a valve opening / closing timing control device used for controlling the opening / closing timing of an intake / exhaust valve in a valve operating apparatus for an internal combustion engine.
[0002]
[Prior art]
As one of the valve opening / closing timing control devices of this type, a rotating member that rotates together with a camshaft is externally mounted so as to be relatively rotatable within a predetermined range, and rotational power from a crank sprocket or pulley of the crankshaft is transmitted to an inner peripheral portion. A rotation transmission member having a recess, a plurality of vanes provided in the rotation member, and a plurality of fluid pressure chambers formed between the recess and the rotation member and divided into an advance chamber and a retard chamber by the vane A first fluid passage for supplying and discharging fluid to the advance chamber, a second fluid passage for supplying and discharging fluid to the retard chamber, and a relative phase of the rotation member and the rotation transmission member is a predetermined phase Some include a relative phase regulating mechanism that regulates the relative phase between the rotating member and the rotation transmitting member, and are disclosed in, for example, Japanese Patent Application Laid-Open Nos. 1-92504 and 9-250310.
[0003]
In the valve opening / closing timing control device disclosed in each of the above publications, the working fluid is supplied to the advance chamber through the first fluid passage, and the working oil is supplied from the retard chamber through the second fluid passage. By discharging, the rotation member rotates in the advance direction to any position up to the maximum advance position where the vane contacts the circumferential end surface on the advance side of the recess with respect to the rotation transmission member, and the valve opening / closing timing advances. The rotating member is supplied to the retarding chamber through the second fluid passage and discharges the hydraulic oil from the advance chamber through the first fluid passage, so that the rotating member is moved relative to the rotation transmitting member. The valve opening / closing timing is retarded by rotating in the retarding direction to any position up to the maximum retarding position where the vane contacts the circumferential end surface on the retarding side of the recess.
[0004]
Further, in the valve opening / closing timing control device disclosed in each of the above-mentioned publications, during the operation of the internal combustion engine, a force in the retarding direction always acts on the rotating member due to the variable torque acting on the camshaft, If the supply of hydraulic oil to the fluid pressure chamber is stopped when the internal combustion engine is stopped, the vane cannot be held by the hydraulic pressure in the fluid pressure chamber, and the rotating member rotates in a retarded direction with respect to the rotation transmission member (crankshaft). Until the rotation is completely stopped), the rotation member and the rotation transmission member are stopped at a relative phase corresponding to the relative phase between the rotation member and the rotation transmission member. When the internal combustion engine is started in this state, the rotating member rotates in the retarding direction with respect to the rotation transmitting member by the force in the retarding direction, and the vane hits the circumferential end surface on the retarding side of the recess. It is the phase at the maximum retard angle position that touches. When the internal combustion engine is started in this state, the hydraulic pressure in the fluid pressure chamber rises and becomes unstable until the vane can be held by the hydraulic pressure, and the vane is caused by the fluctuation torque acting on the camshaft. In order to avoid this, the relative phase between the rotating member and the rotation transmitting member is set to the maximum retarded angle position by the relative phase restricting mechanism. Is now regulated.
[0005]
[Problems to be solved by the invention]
By the way, in the high-speed rotation region of the internal combustion engine, even if the piston starts to approach the top dead center, the intake air tends to further enter the cylinder due to inertia, so that the volume efficiency is improved by delaying the closing timing of the intake valve. It is known that the output can be improved.
[0006]
However, when the valve opening / closing timing control device disclosed in each of the above publications is used to control the opening / closing timing of the intake valve, the valve opening / closing timing at the maximum retard position is determined as described above. Since it is sometimes necessary to set the timing at which intake is possible, the volumetric efficiency cannot be improved due to the inertia of the intake by delaying the closing timing of the intake valve in the high-speed rotation range. This is because if the valve opening / closing timing at the maximum retarded position is set to a time when volumetric efficiency can be improved by the inertia of the intake air, the piston will pass the bottom dead center at the time of starting the internal combustion engine at the maximum retarded position and top dead. The intake valve is open even if it starts to reach the point, and since there is no inertia in the intake air, the intake air once sucked back flows out and is discharged, the compression ratio does not increase, and the combustion cannot be performed, and the internal combustion engine This is because it becomes difficult to start. Note that this problem is not caused by the valve opening / closing timing control device disclosed in each of the above publications, even if the valve opening / closing timing at the maximum retardation position is not set to a time at which volumetric efficiency can be improved by the inertia of intake air. Even when the valve opening / closing timing at the maximum retarded angle position is set to a timing at which intake is possible at start-up, if the closing timing of the intake valve is set after the bottom dead center of the piston, It is likely to occur in places.
[0007]
Further, when the valve opening / closing timing control device disclosed in each of the above publications is used to control the opening / closing timing of the exhaust valve, if the closing timing of the exhaust valve is similarly delayed, the overlap between the intake valve and the exhaust valve is also achieved. The period becomes longer, the internal EGR amount (exhaust gas recirculation amount) increases, and the startability of the internal combustion engine decreases.
[0008]
In order to solve these problems, the relative phase between the rotating member and the rotation transmitting member is set to an intermediate position advanced by a predetermined angle from the maximum retarded position corresponding to the valve opening / closing timing at which volumetric efficiency can be improved by inertia of intake air. Japanese Patent Laid-Open No. 9-324613 has proposed a device that is regulated by a relative phase regulating mechanism. However, in this apparatus, when the rotating member rotates in the retarding direction with respect to the rotation transmitting member as described above when the internal combustion engine is stopped, the relative phase between the rotating member and the rotation transmitting member becomes a predetermined intermediate position. Since the relative phase restriction mechanism may not be able to restrict the relative phase of the rotating member and the rotation transmitting member to a predetermined intermediate position, the internal phase engine may fail to start and the vane and the rotation at the start of the internal combustion engine may occur. It is not possible to reliably prevent the generation of hitting sound due to a collision with the circumferential end surface of the recess of the transmission member.
[0009]
Therefore, the present invention provides a valve opening / closing timing control device capable of expanding the variable control region while reliably preventing the occurrence of a hammering sound caused by a vane at the time of starting the internal combustion engine and starting failure. Let that be the issue.
[0010]
The technical means of the present invention taken in order to solve the above problems includes a rotating member that rotates together with either a crankshaft or a camshaft of an internal combustion engine, and the crankshaft that is mounted on the rotating member so as to be relatively rotatable within a predetermined range. Or a rotation transmission member that rotates together with the other of the camshaft, a vane provided in the rotation member, and an advance chamber and a retard chamber formed by the vane formed between the rotation member and the rotation transmission member. And the rotation member and the rotation transmission member are rotated relative to each other by the fluid pressure applied to the advance chamber and the retard chamber, and the rotation phase of the crankshaft is In the valve opening / closing timing control device for changing the opening / closing timing of the valve driven by the camshaft by changing the rotational phase of the camshaft, The relative rotation of the rotating member and the rotation transmitting member is approximately halfway between the maximum advance position that minimizes the volume of the retard chamber and the maximum retard position that minimizes the volume of the advance chamber. A first relative rotation restricting means for restricting relative rotation of the rotating member and the rotation transmitting member from the corresponding position at the start of the internal combustion engine where the vane is located to the maximum retarded angle position; There is provided second relative rotation restricting means for restricting relative rotation of the rotating member and the rotation transmitting member to the maximum advance position. Therefore, when one of the first relative rotation restricting means and the second relative rotation restricting means is restricted and moves to the start corresponding position, one of the maximum retard position and the maximum advance position. Restricting relative rotation of the rotating member and the rotation transmitting member to each other, and restricting the other of the first relative rotation restricting means and the second relative rotation restricting means, and holding the start relative position. It is.
[0011]
According to the above means, if the supply of the working fluid to the fluid pressure chamber is stopped when the internal combustion engine is stopped, the vane cannot be held by the fluid pressure in the fluid pressure chamber, and the rotating member is delayed with respect to the rotation transmitting member. Although rotating in the angular direction, when the internal combustion engine is started, the relative phase between the rotating member and the rotation transmitting member is at the starting corresponding position where the vane is positioned approximately in the middle of the fluid pressure chamber by the first and second relative rotation restricting means. Is held at the relative phase. As a result, it is possible to accurately prevent the vane from colliding with the circumferential end surface of the fluid pressure chamber and generating sound when starting the internal combustion engine.
[0012]
Further, since the valve opening / closing timing at the time of starting the internal combustion engine is obtained at the relative phase of the rotating member and the rotation transmitting member at the start corresponding position of the vane, the maximum retarded position is further than at the relative phase at the corresponding position at the start. The valve opening and closing timing can be delayed, and it is possible to improve the volumetric efficiency by utilizing the inertia of the intake air, and the valve opening and closing timing at the time of starting can be advanced, and the internal combustion engine due to a decrease in the compression ratio It is possible to prevent the starting failure.
[0013]
In the above-described means, the first relative rotation restricting means causes the relative rotation of the rotating member and the rotation transmitting member from the maximum advance angle position to the maximum retard angle position to be approximately in the middle of the fluid pressure chamber. The internal combustion engine where the vane is located is regulated at a start corresponding position, and the regulation is released by the fluid pressure applied to the retard chamber, and the second relative rotation regulating means is moved from the maximum retard position. The relative rotation of the rotation member and the rotation transmission member to the maximum advance angle position is restricted at the start time corresponding position, and the restriction is released by the fluid pressure applied to the advance angle chamber. can do.
[0014]
In the above-described means, the first relative rotation restricting means causes the relative rotation of the rotating member and the rotation transmitting member from the maximum advance angle position to the maximum retard angle position to be approximately in the middle of the fluid pressure chamber. The internal combustion engine where the vane is located is regulated at a start corresponding position, and the regulation is released by the fluid pressure applied to the retard chamber and the advance chamber, and the second relative rotation regulating means is The relative rotation of the rotation member and the rotation transmission member from the maximum retard angle position to the maximum advance angle position is restricted at the start corresponding position, and is applied to the advance angle chamber and the retard angle chamber. The restriction can also be released by the fluid pressure.
[0015]
In the above-described means, the first relative rotation restricting means causes the relative rotation of the rotating member and the rotation transmitting member from the maximum advance angle position to the maximum retard angle position to be approximately in the middle of the fluid pressure chamber. The internal combustion engine where the vane is located is regulated at a start corresponding position, and the regulation is released by the fluid pressure applied to the retard chamber and the advance chamber, and the second relative rotation regulating means is The relative rotation of the rotation member and the rotation transmission member from the maximum retard angle position to the maximum advance angle position is restricted at the start corresponding position, and is applied to the advance angle chamber and the retard angle chamber. The first relative rotation restricting means includes a first restricting member that is spring-biased and accommodated in one of the rotating member or the rotation transmitting member, and the rotating member or The rotation transmission member When the first restricting member is formed on the other side, the rotation member and the rotation transmission member are allowed to rotate relative to the maximum advance angle position from the start corresponding position, and the start position corresponds to the position. A first restriction groove for restricting relative rotation to the maximum retarded angle position, and the second relative rotation restriction means is accommodated by being biased by one of the rotation member and the rotation transmission member. The restriction member and the rotation member or the rotation transmission member are formed on the other and the second restriction member is fitted into the rotation member and the rotation transmission member from the start corresponding position to the maximum advance angle position. It is desirable to have a second restricting groove that restricts relative rotation and allows relative rotation from the start corresponding position to the maximum retard position.
[0016]
Furthermore, it is desirable that the above-described means further includes a biasing member that constantly biases the rotating member with a predetermined biasing force toward the advance side with respect to the rotation transmitting member.
[0017]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a first embodiment of a valve timing control apparatus according to the present invention will be described with reference to the drawings.
[0018]
1 to 4, the valve opening / closing timing control device includes an internal rotor 20 that is integrally assembled with a tip portion (left end in FIG. 1) of a camshaft 10 that is rotatably supported by a cylinder head of an internal combustion engine. The rotary member includes an outer rotor 30 that is externally mounted on the camshaft 10 and the inner rotor 20 so as to be relatively rotatable within a predetermined range, a front plate 40, a rear plate 50, and a timing sprocket 31 that is integrally provided on the outer periphery of the outer rotor 30. A first relative rotation restricting means including a rotation transmitting member, four vanes 80 assembled to the inner rotor 20, a first lock pin 82 assembled to the front plate 40, and a first assembled to the front plate 40. 2 The second relative rotation restricting means including the lock pin 80 and the like, and interposed between the rotating member and the rotation transmitting member and rotating with respect to the rotation transmitting member. It is constituted by a torsion spring 60 (urging member) or the like for biasing the member to the advance side. As is well known, the timing sprocket 31 is configured such that rotational power is transmitted in a clockwise direction in FIG. 2 from a crankshaft (not shown) via a crank sprocket and a timing chain.
[0019]
The camshaft 10 has a well-known cam (not shown) for opening and closing the intake valve, and an advance angle passage 11 and a retard angle passage 12 extending in the axial direction of the camshaft 10 are provided therein. The advance passage 11 is formed in a mounting hole for the mounting bolt 91 provided in the camshaft 10, and passes through a radial passage provided in the camshaft 10, an annular groove 14, and a connection passage 16 provided in the cylinder head. It is connected to the connection port 101 of the control valve 100. The retard passage 12 is connected to the connection port 102 of the control valve 100 via a radial passage provided in the camshaft 10 and a connection passage 15 provided in the annular groove 13 and the cylinder head.
[0020]
The control valve 100 can move the spool 104, which is inserted in the housing so as to be movable in the axial direction by energizing the solenoid 103, to move to the left in FIG. 1 against the spring 105. The supply port 106 connected to the oil pump 110 driven by the internal combustion engine communicates with the connection port 102, and the connection port 101 communicates with the discharge port 107, and the supply port 106 communicates with the connection port 101 when energized. In addition, the connection port 102 is configured to communicate with the discharge port 107. Therefore, hydraulic oil is supplied to the retard passage 12 when the solenoid 103 of the control valve 100 is not energized, and hydraulic oil is supplied to the advance passage 11 when the solenoid 103 is energized. Is duty controlled.
[0021]
The inner rotor 20 is integrally fixed to the camshaft 10 through a spacer 90 by a single mounting bolt 91, and has vane grooves 21 for mounting each of the four vanes 70 so as to be movable in the radial direction. And the advance passage 11 and each advance chamber R1 so as to supply and discharge hydraulic fluid from the advance passage 11 to the advance chamber R1 (except for the upper left in FIG. 2) partitioned by the vanes 70. Are connected to each other through a passage formed between the inner hole of the inner rotor 20 and the bolt 91, and an annular groove formed on one end face of the camshaft 10 facing the front end face and communicating with the retard passage 12. 20a, four passages 25 extending in the axial direction from the annular groove 20a to the other end surface side, and hydraulic oil from the retarding passage 12 into the retarding chamber R2 defined by each vane 70. Through Feeding each passage 25 to discharge the retarded angle chamber R2 and a passage 27 which communicates (excluding those in the lower left in FIG. 2). Each vane 70 is urged radially outward by a vane spring 71 housed in the bottom of the vane groove 21.
[0022]
Further, on the other end surface side of the internal rotor 20, the relative phase between the internal rotor 20 and the external rotor 30 is between the relative phase corresponding to the starting time of the internal combustion engine described later and the relative phase corresponding to the maximum advance angle position described later. Sometimes the second regulating groove 23c (see FIG. 3) extending in the circumferential direction so that a predetermined amount of the head of the second lock pin 80 is inserted, and the relative phase of the internal rotor 20 and the external rotor 30 correspond to when the internal combustion engine is started. The first restricting groove 26c extending in the circumferential direction so that a predetermined amount of the head of the first lock pin 82 is inserted when the relative phase corresponds to the maximum retardation position described later (see FIG. 7). And are formed. The end portion of the second restricting groove 23c on the rotation direction side (advance side) of the internal rotor 20 is opened on the outer peripheral surface of the internal rotor 20, and the end portion on the counter-rotation direction side of the internal rotor 20 Opened to the outer peripheral surface of the rotor 20.
[0023]
Further, the inner rotor 20 includes a passage 23a that extends radially outward from a passage formed between the inner hole of the inner rotor 20 and the bolt 91 and opens to the outer peripheral surface of the inner rotor 20, and the passage 23a and the second passage. A passage 23b communicating with the restriction groove 23c, a passage 26a extending radially outward from the lower left passage 25 in FIG. 2 and opening to the outer peripheral surface of the internal rotor, and a passage communicating the passage 26a and the first restriction groove 26c 26b. The passage 23b is formed so as to open at the bottom of the end of the second restriction groove 23c on the counter-rotation direction side of the internal rotor 20, and the passage 26b is a first restriction on the rotation direction side of the internal rotor 20. It is formed so as to open at the bottom of the end of the groove 26c. Further, a groove 23d that extends in the circumferential direction and communicates with the passage 23b on the counter-rotation direction side of the internal rotor 20 is formed at the bottom of the second restriction groove 23c, and at the bottom of the first restriction groove 26c, A groove 26d that communicates with the passage 26b on the rotation direction side of the inner rotor 20 and extends in the circumferential direction is formed.
[0024]
The outer rotor 30 is assembled to the outer periphery of the inner rotor 20 so as to be relatively rotatable within a predetermined range. A front plate 40 and a rear plate 50 are joined to both sides of the outer rotor 30 and are integrally connected by five connecting bolts 92. Has been. In addition, four protrusions 32 are formed on the inner periphery of the outer rotor 30 at predetermined intervals in the radial direction, and the inner peripheral surface of these protrusions 32 is the inner rotor 20. The outer rotor 30 is rotatably supported by the inner rotor 20 so as to be in sliding contact with the outer peripheral surface. The front plate 40 includes a second retraction hole 42 that accommodates the second lock pin 80 and the second spring 81, and a first retraction hole 43 that accommodates the first lock pin 82 and the first spring 83. It is formed in the axial direction. When the relative phase between the internal rotor 20 and the external rotor 30 is between the relative phase corresponding to the start time of the internal combustion engine, which will be described later, and the relative phase corresponding to the maximum retard position, which will be described later, the second retraction hole 42. The first retraction hole 43 has a maximum advance angle position, which will be described later, from a relative phase corresponding to the relative phase of the internal rotor 20 and the external rotor 30 at the start of the internal combustion engine. Is positioned so as to face the first restricting groove 26c of the inner rotor 20 when the relative phase corresponds to.
[0025]
Each vane 70 has a circular cross-sectional shape at the tip, and is attached to the vane groove 21 of the inner rotor 20 between the plates 40 and 50 so as to be movable in the radial direction. The fluid pressure chamber R0 formed between each of the protrusions 32, the internal rotor 20, the front plate 40, and the rear plate 50 is divided into an advance chamber R1 and a retard chamber R2. A phase adjusted by the valve timing control device (a predetermined relative rotation range of the internal rotor 20 and the external rotor 30) when one vane 70 contacts the circumferential end surface of the protrusion 32 formed on the external rotor 30. Is now restricted. That is, as shown in FIG. 11, the lower left vane 70 shown in FIG. 11 abuts the circumferential end surface on the retard side of the protrusion 32 (maximum advance position), so that the inner rotor 20 moves toward the advance side with respect to the outer rotor 30. The relative rotation is limited, and the upper left vane 70 shown in FIG. 14 is in contact with the circumferential end surface on the advance side of the protrusion 32 (maximum retard position), whereby the retard angle of the inner rotor 20 relative to the outer rotor 30 is reached. Relative rotation to the side is limited.
[0026]
The second lock pin 80 is assembled in the second retraction hole 42 so as to be slidable in the axial direction, and is provided by a first spring 81 interposed between the second lock pin 80 and the bottom of the second retraction hole 42. The inner rotor 20 is biased toward the other side. The first lock pin 82 is assembled in the first retraction hole 43 so as to be slidable in the axial direction, and is interposed between the first lock pin 82 and the bottom of the first retraction hole 43. 84 is biased toward the other side of the inner rotor 20. As a result, when the relative phase between the internal rotor 20 and the external rotor 30 is between the relative phase corresponding to the start of the internal combustion engine and the relative phase when it is at the maximum retard position, the head of the second lock pin 80 is The inner rotor 20 is inserted into the restriction groove 23c, and relative rotation of the internal rotor 20 and the external rotor 30 from the position corresponding to the start to the maximum retard angle position is allowed, and the internal rotor from the position corresponding to the start to the maximum advance position The relative rotation of 20 and the external rotor 30 is restricted. When the relative phase between the internal rotor 20 and the external rotor 30 is between the relative phase corresponding to the start of the internal combustion engine and the relative phase at the maximum advance position, the head of the first lock pin 82 is in the first restriction. The internal rotor 20 is inserted into the groove 26c, and relative rotation of the internal rotor 20 and the external rotor 30 from the corresponding position at the start to the maximum advance angle position is allowed, and the internal rotor 20 from the corresponding position at the start to the maximum retard position. And the relative rotation of the external rotor 30 is restricted. When the relative phase between the internal rotor 20 and the external rotor 30 is a relative phase corresponding to when the internal combustion engine is started, the second lock pin 80 is fitted into the second restriction groove 23c, and the first lock pin 82 is the first lock pin. The relative phase between the inner rotor 20 and the outer rotor 30 is maintained by fitting into the restriction groove 26c.
[0027]
In the present embodiment, the rotating member composed of the inner rotor 20 is constantly urged in the advance direction by the torsion spring 60 with respect to the rotation transmitting member composed of the outer rotor 30, the front plate 40 and the rear plate 50. The urging force of the torsion spring 60 corresponds to the average value of the fluctuation torque acting on the camshaft 10 (the average torque acting to rotate the camshaft 10 to the retard side) during operation of the internal combustion engine. Is set. The torsion spring 60 is accommodated in a cylindrical portion 41 of the front plate 40 and an annular groove formed on the other side surface of the inner rotor 20 so as to be continuous with the cylindrical portion 41, and one end thereof is an end portion of the cylindrical portion 41. The other end is locked to the bottom of the annular groove.
[0028]
In the present embodiment, when the relative phase between the internal rotor 20 and the external rotor 30 is a relative phase corresponding to when the internal combustion engine is started, the opening / closing timing of an intake valve (not shown) is set to a time when the internal combustion engine can be started. It is set to be. In the present embodiment, each vane 70 is positioned substantially in the middle of the fluid pressure chamber R0 at the relative phase corresponding to this start-up, and the internal rotor 20 is moved from the maximum retard position (see FIG. 14) to the external rotor. It is in a state of relative rotation (see FIG. 8) to the advance side by a predetermined angle θ with respect to 30.
[0029]
In the valve timing control apparatus of the present embodiment configured as described above, when the relative phase between the internal rotor 20 and the external rotor 30 is in the relative phase corresponding to the start of the internal combustion engine shown in FIGS. The second lock pin until the working fluid of the first predetermined pressure or higher is supplied from the oil pump 110 driven by the internal combustion engine to the advance passage 11 and the retard passage 12 through the control valve 100 after the engine is started. The heads of 80 and the first lock pin 82 are fitted into the second restriction groove 23c and the first restriction groove 26c, respectively (see FIGS. 9 and 10).
[0030]
Accordingly, the first and second lock pins 80 and 82 restrict relative rotation of the inner rotor 20 and the outer rotor 30 due to fluctuating torque acting on the camshaft 10 when driving an intake valve (not shown), and Therefore, the occurrence of a striking sound (a contact sound between the vane 70 and the protrusion 32) associated with the rotational vibration is prevented.
[0031]
When the control valve 100 is in a non-energized state and a predetermined time elapses after the internal combustion engine is started, the working fluid having the first predetermined pressure or higher is supplied from the oil pump 110 to the retard passage 12 through the control valve 100. Then, hydraulic oil is supplied to the first restriction groove 26c through the passage 25, the passage 26a, and the passage 26b, and the first lock pin 82 moves into the retraction hole 43 against the urging force of the spring 83, Retracts from the first restricting groove 26c into the retracting hole 43. On the other hand, since the advance passage 11 communicates with the oil reservoir 120 via the control valve 100, the second lock pin 80 is maintained in a state where the head is fitted in the second restriction groove 23c by the biasing force of the spring 81. The Therefore, the inner rotor 20 is allowed to rotate relative to the outer rotor 30 from the start-time corresponding position to the maximum retarded angle position side. In this state, the pressure of the working fluid supplied from the oil pump 110 to the retard passage 12 via the control valve 100 becomes equal to or higher than the second predetermined pressure (first predetermined pressure <second predetermined pressure). Are supplied from the retard passage 12 to the retard chambers R2 through the annular grooves 20a, the passages 25 and 27, the passages 26a and 26b, and the first restriction grooves 26c, and from the advance chambers R1 to the passages 24 and When hydraulic fluid is discharged through the second restriction groove 23c, the passages 23b, 23a, the advance passage 11, the control valve 100, etc., the internal rotor 20 and the vanes 70 rotate relative to the retard side with respect to the external rotor 30, etc. The relative rotation amount (maximum retardation amount) is as shown in FIG. 14 as the internal rotor 20 rotates relative to the external rotor 30 by a predetermined angle θ from the start corresponding position shown in FIG. One vane (the upper left vane in the figure) 70 is limited by abutting the advance side circumferential end surface of the projection 32. At this time, as shown in FIGS. 15 and 16, the head of the second lock pin 80 is fitted into the second restriction groove 23c, and the head of the first lock pin 82 is fitted into the first restriction groove 26c. Instead, it is in sliding contact with the other end surface of the internal rotor 20.
[0032]
Further, when the control valve 100 is energized (the duty ratio of the current supplied to the solenoid 103 is increased), the working fluid having a pressure equal to or higher than the second predetermined pressure is supplied to the advance passage 11 and the passages 24, 23a, 23b, and the second. When the hydraulic oil is supplied to each advance angle chamber R1 through the restriction groove 23c and discharged from each retard angle chamber R2 through the passages 25, 26a, 26b, 27, the retard passage 12, the control valve 100, and the like. The inner rotor 20 and the vanes 70 rotate relative to the outer rotor 30 and the like on the advance side. As shown in FIG. 11, the relative rotation amount (maximum retardation amount) is limited when one vane 70 (lower left vane in the drawing) abuts against the retardation side circumferential end surface of the protrusion 32. At this time, as shown in FIGS. 12 and 13, when the first retraction hole 43 faces the first restriction groove 26c, the head of the first lock pin 82 is fitted into the first restriction groove 26c by the spring 83. The head of the second lock pin 80 does not fit into the second restriction groove 23 c and is in sliding contact with the other end surface of the internal rotor 20.
[0033]
In the present embodiment, as described above, each vane 70 is positioned substantially in the middle of the fluid pressure chamber R0, and the internal rotor 20 is only a predetermined angle θ from the maximum retard angle position (see FIG. 14) with respect to the external rotor 30. When a predetermined relative phase between the internal rotor 20 and the external rotor 30 is in a state of relative rotation (see FIG. 8) toward the advance side, the opening / closing timing of an intake valve (not shown) is set to a timing at which the internal combustion engine can be started. Is set to For this reason, the valve opening / closing timing is further delayed from the valve opening / closing timing at which the internal combustion engine can be started from the start corresponding position to the maximum retarded position where the vane 70 contacts the circumferential end surface of the protrusion 32 on the advance side. When the internal combustion engine rotates at high speed, the control valve 100 is controlled as described above to perform phase conversion from the start position to the retarded angle side, and the closing timing of the intake valve (not shown) until the start of the internal combustion engine is difficult By delaying, the volumetric efficiency is improved by the inertia of the intake air, and the output of the internal combustion engine can be improved.
[0034]
When the internal combustion engine is stopped, the drive of the oil pump 100 is stopped, the supply of hydraulic oil to the fluid pressure chamber R0 is stopped, and the control valve 100 is turned off. Thereby, the pressing force by the advance hydraulic pressure in the advance chamber R1 and the press force by the retard hydraulic pressure in the retard chamber R2 do not act on the vane 70, and the internal rotor 20 and the camshaft 10 are connected to the camshaft. 10, only the force in the above-described retarded direction (until the crankshaft of the internal combustion engine completely stops) due to the fluctuating torque acting on the rotor 10 acts, and the relative phase between the internal rotor 20 and the external rotor 30 immediately before the stop is applied. Accordingly, the relative phase between the internal rotor 20 and the external rotor 30 at the time of stopping is determined. When the relative phase when the internal combustion engine is stopped becomes the relative phase at the start corresponding position, the heads of the first and second lock pins 80 and 82 are moved by the springs 82 and 84, respectively. 2 Fits into the regulation grooves 23c and 26c, and the relative phase between the inner rotor 20 and the outer rotor 30 is maintained (locked).
[0035]
As shown in FIGS. 6 and 7, when the relative phase between the internal rotor 20 and the external rotor 30 when the internal combustion engine is stopped is on the advance side as shown in FIG. The head of the second lock pin 80 does not fit into the second restriction groove 23c, and only the head of the first lock pin 82 fits into the first restriction groove 26c. Therefore, the relative rotation between the internal rotor 20 and the external rotor 30 is in a state restricted only between the start corresponding position and the maximum advance angle position. In this state, when a crankshaft (not shown) is rotationally driven by the starter at the time of starting the internal combustion engine, the internal rotor 20 has a maximum position corresponding to the start time relative to the external rotor 30 due to fluctuating torque acting on the camshaft 10. The head of the second lock pin 80 is fitted into the second restricting groove 23c when the relative rotation between the lead angle position and the inner rotor 20 and the outer rotor 30 becomes the corresponding position at the start. . Thereby, the relative phase of the internal rotor 20 and the external rotor 30 is maintained (locked).
[0036]
Also, as shown in FIG. 2, when the relative phase between the internal rotor 20 and the external rotor 30 when the internal combustion engine is stopped is on the retard side with respect to the start corresponding position, as shown in FIG. 3 and FIG. Furthermore, the head of the second lock pin 80 is fitted into the second restriction groove 23c, and the head of the first lock pin 82 is not fitted into the first restriction groove 26c. Therefore, the relative rotation between the internal rotor 20 and the external rotor 30 is restricted only between the start-time corresponding position and the maximum retard angle position. In this state, when a crankshaft (not shown) is rotationally driven by the starter at the time of starting the internal combustion engine, the internal rotor 20 has a maximum position corresponding to the start time relative to the external rotor 30 due to fluctuating torque acting on the camshaft 10. The head of the first lock pin 82 is inserted into the first restricting groove 26c when the relative rotation between the internal rotor 20 and the external rotor 30 reaches the start-up corresponding position. . Thereby, the relative phase of the internal rotor 20 and the external rotor 30 is maintained (locked). In addition, since it takes a predetermined time after the internal combustion engine is started until the pressure of the working fluid supplied from the oil pump 110 exceeds the first predetermined pressure, the first and second lock pins are used for the rotational drive by the starter described above. Is inserted into each regulation groove by a spring.
[0037]
Therefore, when the internal combustion engine is started, there is no rotation member composed of the camshaft 10, the internal rotor 20, each vane 70 and the like accompanied by large rotational fluctuations, and the rotation transmission member composed of the external rotor 30, the front plate 40, the rear plate 50 and the like. Necessary relative rotation is reliably regulated, and it is possible to reliably prevent occurrence of hitting sound by the vane 70 accompanying unnecessary relative rotation between the rotating member and the rotation transmitting member.
[0038]
Next, a second embodiment of the valve timing control device according to the present invention will be described with reference to the drawings.
[0039]
17 to 19 are drawings showing a second embodiment of the present invention. Since the second embodiment is the same as the first embodiment except for the hydraulic path of the hydraulic oil supplied to the first and second lock pins, the other configurations are the same as the first embodiment. Those having the same configuration and function are denoted by reference numerals with 200 added to the reference numerals of the first embodiment, and description thereof is omitted.
[0040]
FIG. 17 is a view in which the front plate 240 according to the second embodiment of the present invention is removed. In FIG. 17, the inner rotor 220 and the outer rotor 230 are respectively located at corresponding positions at the time of starting, and the first lock pin 282 and the second lock pin 280 are fitted in the first restriction groove 226 c and the second restriction groove 223 c, respectively. Thus, the relative rotation of the inner rotor 220 and the outer rotor 230 is restricted.
[0041]
18 is a cross-sectional view taken along the line 18-18 in FIG.
[0042]
In FIG. 18, the first retraction hole 243 is a stepped hole having a large diameter part 243 a and a small diameter part 243 b in the moving direction of the first lock pin 282. A step portion is formed at a portion where the inner diameter of the first retraction hole 243 changes. The large diameter portion 243 a of the first retraction hole 243 is on the side opposite to the inner rotor 220 with respect to the moving direction of the second lock pin 282, and the small diameter portion 243 b is on the step portion with respect to the moving direction of the first lock pin 282. Each is formed on the inner rotor 220 side. The bottom of the first retraction hole 243 on the inner rotor 220 side communicates with the passage 25 via the passage 226a and the passage 226b.
[0043]
The first lock pin 282 has a stepped shape having a small diameter portion and a large diameter portion. The small diameter portion of the first lock pin can slide in the small diameter portion 243b of the first retraction hole 243, and the large diameter portion of the first lock pin 282 can slide in the large diameter portion 243a of the first retraction hole 243.
[0044]
In addition, passages 203 and 204 are formed in the front plate 240 and communicate with the stepped portion of the first retraction hole 243.
[0045]
19 is a cross-sectional view taken along line 19-19 in FIG.
[0046]
In FIG. 19, the second retraction hole 242 is a stepped hole having a large diameter portion 242 a and a small diameter portion 242 b in the moving direction of the second lock pin 280. A step portion is formed at a portion where the inner diameter of the second retraction hole 242 changes. The large diameter portion is formed on the inner rotor 220 side of the step portion with respect to the moving direction of the second lock pin 280, and the small diameter portion 242b is formed on the inner rotor 220 side of the step portion with respect to the moving direction of the second lock pin 280. Has been. The bottom of the second retraction hole 242 on the inner rotor 220 side communicates with the passage 223a through the passage 223a.
[0047]
The second lock pin 280 has a stepped cylindrical shape having a small diameter portion and a large diameter portion. The small diameter portion of the second lock pin can slide in the small diameter portion 142b of the second retraction hole, and the large diameter portion of the second lock pin can slide in the large diameter portion 142a of the second retraction hole.
[0048]
Further, passages 201 and 202 are formed in the front plate 240 and communicate with the stepped portion of the second retraction hole 242. As a result, when the hydraulic oil is supplied to the small diameter portion of the second lock pin 280 via the passages 23a and 23b, the second lock pin 280 of the second lock pin 280 passes through the retard chamber R2 and the passages 201 and 202. When hydraulic fluid is supplied to the stepped portion or when hydraulic fluid is supplied to both of them, the second lock pin 280 is retracted into the second retracting hole against the biasing force of the spring, and the inner rotor 220 and the outer The relative rotation of the rotor 230 is allowed.
[0049]
As a result, when the hydraulic oil is supplied to the small diameter portion of the first lock pin 282 via the passages 25a and 25b, the first lock pin 282 passes through the retard chamber R2 and the passages 203 and 204. The first lock pin 282 is retracted into the first retraction hole 243 against the urging force of the spring when the hydraulic oil is supplied to the step portion or when the hydraulic oil is supplied to both of them. And the outer rotor 230 are allowed to rotate relative to each other.
[0050]
As described above, according to the first and second embodiments, the generation of sound caused by the collision between the vanes 70 and 270 and the circumferential end surfaces of the protrusions 32 and 232 at the start of the internal combustion engine and the start failure of the internal combustion engine. The volumetric efficiency can be improved in the high speed rotation region of the internal combustion engine.
[0051]
In the above embodiment, the present invention is applied to the valve opening / closing timing control device assembled to the intake camshaft. However, the present invention is similarly applied to the valve opening / closing timing control device assembled to the exhaust camshaft. It is possible.
[0052]
In the first embodiment described above, the restriction release of the second lock pin 80 is performed with the working fluid to the advance angle chamber, and the restriction release of the first lock pin 82 is performed with the working fluid to the retard angle chamber. However, the working fluid for releasing the regulation of both lock pins may be supplied through a passage different from the passage to the advance angle chamber and the retard angle chamber.
[0053]
【The invention's effect】
As described above, according to the present invention, when the supply of the working fluid to the fluid pressure chamber is stopped when the internal combustion engine is stopped, the vane cannot be held by the fluid pressure in the fluid pressure chamber, and the rotating member becomes the rotation transmitting member. However, when the internal combustion engine is started, the relative phase between the rotating member and the rotation transmitting member is positioned approximately in the middle of the fluid pressure chamber by the first and second relative rotation restricting means. The relative phase when in position is maintained. Thereby, it is possible to accurately prevent the vane from colliding with the circumferential end surface of the fluid pressure chamber and generating sound when starting the internal combustion engine.
[0054]
Further, since the valve opening / closing timing at the time of starting the internal combustion engine is obtained at the relative phase of the rotating member and the rotation transmitting member at the start corresponding position of the vane, the maximum retarded position is further than at the relative phase at the corresponding position at the start. The opening and closing timing of the valve can be delayed, and the output of the internal combustion engine can be improved by utilizing the inertia of the intake air at the time of high speed rotation of the internal combustion engine to improve the volume efficiency. It is possible to advance the angle, and to prevent starting failure of the internal combustion engine due to a decrease in the compression ratio.
[Brief description of the drawings]
FIG. 1 is a longitudinal side view showing a first embodiment of a valve timing control apparatus according to the present invention.
2 is a front view showing a state in which the internal combustion engine has stopped on the retard side from the lock position of the first embodiment shown in FIG. 1 with the front plate and the like removed.
3 is a cross-sectional view taken along the line 3-3 in FIG.
4 is a cross-sectional view taken along line 4-4 of FIG.
5 is a front view showing a state in which the internal combustion engine has stopped on the advance side from the lock position of the first embodiment shown in FIG. 1 with the front plate and the like removed.
6 is a cross-sectional view taken along the line 6-6 in FIG.
7 is a cross-sectional view taken along the line 7-7 in FIG.
8 is a front view showing a locked state of the first embodiment shown in FIG. 1 with a front plate and the like removed. FIG.
9 is a cross-sectional view taken along line 9-9 in FIG.
10 is a cross-sectional view taken along the line 10-10 in FIG.
11 is a front view showing an advanced angle operating state of the first embodiment shown in FIG. 1 with a front plate and the like removed. FIG.
12 is a cross-sectional view taken along the line 12-12 of FIG.
13 is a cross-sectional view taken along line 13-13 of FIG.
14 is a front view showing a retarded operation state of the first embodiment shown in FIG. 1 with a front plate and the like removed. FIG.
15 is a cross-sectional view taken along the line 15-15 in FIG. 14;
16 is a cross-sectional view taken along the line 16-16 in FIG. 14;
FIG. 17 is a front view showing a locked state of the second embodiment with the front plate and the like removed.
18 is a cross-sectional view taken along line 18-18 in FIG. 17;
19 is a cross-sectional view taken along line 19-19 of FIG.
[Explanation of symbols]
10, 210 Camshaft
11, 211 advance passage
12, 212 retarded passage
20, 220 Internal rotor (rotary member)
23c, 223c second restriction groove (second relative rotation restriction means)
26c, 226c first restriction groove (first relative rotation restriction means)
30, 230 External rotor (rotation transmission member)
40, 240 Front plate (rotation transmission member)
42, 242 second retraction hole
43, 243 First retraction hole
50, 250 Rear plate (Rotation transmission member)
70, 270 Vane
80, 280 Second lock pin (second relative rotation restricting means)
82, 282 First lock pin (first relative rotation restricting means)
100 Control valve
110 Oil pump
R0 fluid pressure chamber
R1 advance angle chamber
R2 retarding chamber

Claims

A rotating member that rotates together with one of a crankshaft or a camshaft of an internal combustion engine, a rotation transmission member that is mounted on the rotating member so as to be relatively rotatable within a predetermined range, and rotates with the other of the crankshaft or the camshaft; and the rotating member And a fluid pressure chamber formed between the rotating member and the rotation transmitting member and divided into an advance chamber and a retard chamber by the vane, and the advance chamber Further, the rotation member and the rotation transmission member are rotated relative to each other by the fluid pressure applied to the retardation chamber, and the camshaft is driven by the camshaft by changing the rotation phase of the camshaft with respect to the rotation phase of the crankshaft. In the valve opening / closing timing control device for changing the opening / closing timing of the valve, the relative rotation between the rotating member and the rotation transmitting member is set to the retard angle. A maximum advance angle position that minimizes the volume of the chamber and a maximum retard angle position that minimizes the volume of the advance angle chamber; A first relative rotation restricting means for restricting relative rotation of the rotating member and the rotation transmitting member to the retarded angle position; and a relative relationship between the rotating member and the rotation transmitting member from the start corresponding position to the maximum advanced angle position. setting a second relative rotation restricting means for restricting the rotation,
When one of the first relative rotation restricting means and the second relative rotation restricting means is regulated and moves to the corresponding position at the time of starting, it is moved to one of the maximum retard position and the maximum advance position. Relative rotation between the rotation member and the rotation transmission member is restricted, and the other of the first relative rotation restriction means and the second relative rotation restriction means is restricted and held at the start corresponding position. Valve opening / closing timing control device.

The internal combustion engine in which the first relative rotation restricting means is configured so that the relative rotation of the rotation member and the rotation transmission member from the maximum advance angle position to the maximum delay angle position is approximately halfway between the fluid pressure chambers. And the restriction is released by the fluid pressure applied to the retard chamber, and the second relative rotation restricting means moves the maximum retard position from the maximum retard position to the maximum advance position. The relative rotation between the rotation member and the rotation transmission member is restricted at the start corresponding position, and the restriction is released by the fluid pressure applied to the advance angle chamber. Valve timing control device.

The internal combustion engine in which the first relative rotation restricting means is configured so that the relative rotation of the rotation member and the rotation transmission member from the maximum advance angle position to the maximum delay angle position is approximately halfway between the fluid pressure chambers. And the restriction is released by the fluid pressure applied to the retard chamber and the advance chamber, and the second relative rotation restricting means is moved from the maximum retard position to the maximum. The relative rotation of the rotating member and the rotation transmitting member to the advance angle position is restricted at the start corresponding position, and the restriction is released by the fluid pressure applied to the advance angle chamber and the retard angle chamber. The valve opening / closing timing control device according to claim 1, wherein

The first relative rotation restricting means is formed on the other of the rotation member or the rotation transmission member, and is formed on the other of the rotation member or the rotation transmission member. 1 When the restricting member is inserted, the rotation member and the rotation transmission member are allowed to rotate relative to the maximum advance position from the start corresponding position, and relative to the maximum retard position from the start corresponding position. A first restriction groove for restricting rotation, wherein the second relative rotation restriction means is a second restriction member that is housed by being biased by one of the rotation member or the rotation transmission member, and the rotation member. Alternatively, the second restricting member is formed on the other of the rotation transmitting members to restrict relative rotation of the rotating member and the rotation transmitting member from the start corresponding position to the maximum advance position, Start-up response Valve timing control apparatus according to claim 2 or 3, characterized in that a second regulating groove to permit relative rotation to put al the maximum retard angle position.

The valve opening / closing according to any one of claims 1 to 4 , further comprising an urging member that constantly urges the rotation member with a predetermined urging force toward the advance side with respect to the rotation transmission member. Timing control device.