JP4035745B2

JP4035745B2 - Valve timing control device

Info

Publication number: JP4035745B2
Application number: JP24198198A
Authority: JP
Inventors: 和己小川
Original assignee: Aisin Seiki Co Ltd; Aisin Corp
Current assignee: Aisin Corp
Priority date: 1998-08-27
Filing date: 1998-08-27
Publication date: 2008-01-23
Anticipated expiration: 2018-08-27
Also published as: JP2000073715A

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気弁又は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、内燃機関のカムシャフト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内燃機関のクランクシャフトと共に回転する回転伝達部材と、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回転部材に設けられた複数のベーンによって夫々進角用室と遅角用室とに二分される複数の流体圧室と、前記進角用室に流体を給排する複数の第１流体通路と、前記遅角用室に流体を給排する複数の第２流体通路と、前記回転伝達部材に形成され内部に前記回転部材に向けてばね付勢された係合部材を収容する退避孔と、前記回転部材に形成され前記回転部材と前記回転伝達部材の相対位相が所定の位相で同期したとき前記係合部材の一端が嵌入される受容孔と、この受容孔に流体を給排する第３流体通路とを備えたものがあり、例えば特開平１０−１８４３２１号公報に開示されている。
【０００３】
上記公報に開示されている弁開閉時期制御装置においては、回転部材が回転伝達部材に対して最遅角位置となることにより回転部材と回転伝達部材の相対位相が所定の位相となるように設定したときには、第３流体通路を遅角用室に連通させると共に、退避孔を第４流体通路を介して進角用室に連通させるようにし、回転部材が回転伝達部材に対して最進角位置となることにより回転部材と回転伝達部材の相対位相が所定の位相となるように設定したときには、第３流体通路を進角用室に連通させると共に、退避孔を第４流体通路を介して遅角用室に連通させるようにしている。
【０００４】
【発明が解決しようとする課題】
上記公報に開示されている弁開閉時期制御装置において、最遅角位置が所定の位相となるように設定した場合、最遅角位置から微小角度だけ回転部材を回転伝達部材に対して進角側に相対回転させた状態に回転部材と回転伝達部材の位相を保持するときには、第１流体通路及び第２流体通路を介して進角用室及び遅角用室へ夫々流体が供給されるが、摩擦力によりカムシャフトに遅角側へ作用するトルクによって回転部材には遅角側へのトルクが作用しているため、進角用室の流体圧＞遅角用室の流体圧となるように流体が供給される。このため、上記した位相保持時には、受容孔に第３流体通路を介して供給される遅角用室の流体圧によって係合部材を受容孔外へ移動させようとする力よりも、退避孔に第４流体通路を介して供給される進角用室の流体圧及びばね付勢力によって係合部材を回転部材に向けて移動させようとする力の方が大きくなる。
【０００５】
ところで、回転部材と回転伝達部材の位相保持時には、カムシャフトに作用するトルク変動により回転部材が回転伝達部材に対して微小振幅で振動しており、保持位置から回転部材が回転伝達部材に対して遅角側へ相対回転したときに受容孔と退避孔が対向する最遅角位置になる場合がある。この時、上記公報に開示されている弁開閉時期制御装置においては、係合部材を受容孔外へ移動させようとする力よりも係合部材を回転部材に向けて移動させようとする力の方が大きいため、係合部材の一端が受容孔内に嵌入されて、回転部材と回転伝達部材の相対位相が最遅角位置に保持されてしまい、その後に進角用室に流体を供給すると共に遅角用室内の流体を排出して回転部材を回転伝達部材に対して進角側へ相対回転させようとしても、係合部材が受容孔から退避孔へ移動しないで回転部材と回転伝達部材の相対回転が阻止され、当該弁開閉時期制御装置の作動が不能となることがある。
【０００６】
また、上記公報に開示されている弁開閉時期制御装置において、最進角位置が所定の位相となるように設定した場合に、最進角位置から微小角度だけ回転部材を回転伝達部材に対して遅角側に相対回転させた状態に回転部材と回転伝達部材の位相を保持するとき、同様に進角用室の流体圧＞遅角用室の流体圧となるように流体が進角用室及び遅角用室に供給されて、受容孔に第３流体通路を介して供給される進角用室の流体圧によって係合部材を受容孔外へ移動させようとする力よりも退避孔に第４流体通路を介して供給される遅角用室の流体圧及びばね付勢力によって係合部材を回転部材に向けて移動させようとする力の方が小さくなる。ところが、この状態にてカムシャフトに作用するトルク変動により回転部材が回転伝達部材に対して進角側へ相対回転して受容孔と退避孔が対向する最進角位置になる場合があり、この時には回転部材の移動により遅角用室内の流体圧が上昇し、係合部材を受容孔外へ移動させようとする力よりも係合部材を回転部材に向けて移動させようとする力の方が大きくなる。このため、受容孔と退避孔が対向する最進角位置になった時に、係合部材の一端が受容孔内に嵌入されて、回転部材と回転伝達部材の相対位相が最進角位置に保持されてしまい、その後に遅角用室に流体を供給すると共に進角用室内の流体を排出して回転部材を回転伝達部材に対して遅角側へ相対回転させようとしても、係合部材が受容孔から退避孔へ移動しないで回転部材と回転伝達部材の相対回転が阻止され、当該弁開閉時期制御装置の作動が不能となることがある。
【０００７】
それゆえ、本発明は、当該弁開閉時期制御装置において、係合部材による回転部材と回転伝達部材の相対位相保持作動の誤作動を防止することを、その課題とする。
【０００８】
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及び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及び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、前記回転部材と前記回転伝達部材との間に形成され、前記回転部材に設けられた複数のベーンによって夫々進角用室と遅角用室とに二分される複数の流体圧室と、前記進角用室に流体を給排する複数の第１流体通路と、前記遅角用室に流体を給排する複数の第２流体通路と、前記回転部材及び前記回転伝達部材の一方に形成され、内部に前記回転部材及び前記回転伝達部材の他方に向けてばね付勢された係合部材を収容する退避孔と、前記回転部材及び前記回転伝達部材の他方に形成され、前記回転部材と前記回転伝達部材との相対位相が所定位相にあるとき前記係合部材の一端が嵌入される受容孔と、この受容孔に前記係合部材を前記退避孔の側に付勢する流体を給排する第３流体通路とを備えた弁開閉時期制御装置において、前記第３流体通路を前記遅角用室及び前記進角用室の一方に連通させると共に、前記退避孔を前記遅角用室及び前記進角用室の他方の１つに常時連通させ、前記退避孔に前記係合部材を前記受容孔の側に付勢する流体を給排する第４流体通路と、少なくとも前記回転部材と前記回転伝達部材との相対位相が前記所定位相から所定角度変化するまでの間前記退避孔を前記遅角用室及び前記進角用室の他方の前記１つに流体を給排する前記第１流体通路の１つ又は前記第２流体通路の１つに連通させ、前記係合部材がばね付勢力に抗して移動したとき、前記係合部材の側面にてその退避孔側開口が閉塞される第５流体通路とを設け、前記遅角用室及び前記進角用室の他方の前記１つと、前記第１流体通路の前記１つ又は前記第２流体通路の前記１つとの連通を、前記回転部材と前記回転伝達部材の相対位相が前記所定位相から前記所定角度変化するまでの間遮断するようにしたことである。
【０００９】
上記した手段によれば、最遅角位置（最進角位置）から微小角度だけ回転部材を回転伝達部材に対して進角側（遅角側）に相対回転させた状態で回転部材と回転伝達部材の相対位相が保持される時、１つの第１流体通路（第２流体通路）と１つの進角用室（１つの遅角用室）との連通が遮断され、１つの第１流体通路（第２流体通路）は退避孔側一端を係合部材により閉塞された第５流体通路の他端に連通されると共に、１つの進角用室（１つの遅角用室）は第４流体通路を介して退避孔に連通される。この位相保持時に、カムシャフトに作用するトルク変動により回転部材が回転伝達部材に対して微小振幅で振動しており、保持位置から回転部材が回転伝達部材に対して遅角側（進角側）へ相対回転したときに受容孔２と退避孔が対向する最遅角位置（最進角位置）になる場合があるが、この時には、退避孔から１つの進角用室（１つの遅角用室）に至る密封された空間の容積が縮小して退避孔内の圧力が上昇するものの、受容孔には遅角用室（進角用室）から第３流体通路２３を介して作動油が供給されると共に係合部材が第５流体通路を介して供給される作動油により退避孔の一側内周面に押動されて圧接されているため、係合部材は受容孔内に嵌入されずに退避孔内にて退避位置に保持される。これにより、係合部材による回転部材と回転伝達部材の相対位相保持作動の誤作動が的確に防止され、回転部材の回転伝達部材に対する的確な相対回転が保証される。
【００１０】
【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一実施形態を図面に基づき、説明する。
【００１１】
図１乃至図５に示した弁開閉時期制御装置は、内燃機関のシリンダヘッド１１０に回転自在に支持されたカムシャフト１０の先端部に一体的に組付けた内部ロータ２０から成る回転部材と、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、キャップ４１、リアプレート５０、及びタイミングプーリ６０等から成る回転伝達部材と、内部ロータ２０に組付けた６枚のベーン７０と、外部ロータ３０に組付けたロックピン８０等によって構成されている。タイミングプーリ６０には、周知のように、内燃機関のクランクシャフトからクランクプーリと樹脂又はゴム製のタイミングベルト（全て図示省略）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。尚、クランクシャフトから回転伝達部材への動力伝達はタイミングベルトに代えて採用されるタイミングチェーンやタイミングギヤを介して行われるようにして実施することも可能である。
【００１２】
カムシャフト１０は、吸気弁（図示省略）を開閉する周知のカム（図示省略）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と遅角通路１２が設けられている。進角通路１１は、径方向の通路１３と環状の油路１４と接続通路Ｐ２を介して制御弁１００の接続ポート１０２に接続されている。また、遅角通路１２は、環状の油路１５と接続通路Ｐ１を介して制御弁１００の接続ポート１０１に接続されている。
【００１３】
制御弁１００は、ソレノイド１０３へ通電することによってスプール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１１２に接続された供給ポート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、また通電時には供給ポート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の非通電時にはオイルポンプ１１２から遅角通路１２に作動油が供給されると共に進角通路１１からオイル溜め１１３に作動油が排出され、通電時にはオイルポンプ１１２から進角通路１１に作動油が供給されると共に遅角通路１２からオイル溜め１１３に作動油が排出される。尚、ソレノイド１０３への通電は図示しない制御装置によりデューティ制御される。
【００１４】
内部ロータ２０は、中空状のボルト１９によってカムシャフト１０に一体的に固着されていて、６枚のベーンの各ベーン７０を夫々径方向に取り付けるためのベーン溝２１を有すると共に、図２及び図３に示した状態、即ちカムシャフト１０及び内部ロータ２０と外部ロータ３０の相対位相が所定の位相（最遅角位置）となったとき、ロックピン８０の頭部８１が所定量嵌入される受容孔２２と、この受容孔２２に遅角通路１２から各ベーン７０によって区画された遅角用室Ｒ２を介して作動油を給排する通路２３と、各ベーン（図２の右上のベーンを除く）７０によって区画された進角用室Ｒ１に進角通路１１から作動油を給排する通路２４と、図２の右上のベーン７０によって区画された進角用室Ｒ１ａに進角通路１１から作動油を給排する通路２４ａ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から作動油を給排する通路２５を有している。受容孔２２は、図４にて示したように、ロックピン８０の頭部８１の外径より所定量大径の有底孔であって、ロックピン８０の頭部８１とにより形成される環状の隙間を通して受容孔２２の底部に作動油が給排されるようになっていると共にその開放端周縁に面取り部２６が形成されている。尚、各ベーン７０は、ベーン溝２１の底部に収容したスプリング７１（図１参照）によって径方向外方に付勢されている。
【００１５】
外部ロータ３０は、その内周にて内部ロータ２０の外周面に所定の隙間（作動油が介在する極小隙間）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がシール部材Ｓ１、Ｓ２を介して接合され、タイミングプーリ６０とともにボルトＢ１によって一体的に連結されている。フロントプレート４０にはキャップ４１が液密的に組付けられていて、これによりカムシャフト１０の進角通路１１と内部ロータ２０の通路２４、２４ａを接続する通路４２が形成されている。また、外部ロータ３０には、各ベーン７０を収容し各ベーン７０によって進角用室Ｒ１、Ｒ１ａと遅角用室Ｒ２とに二分される作動室Ｒ０を内部ロータ２０、フロントプレート４０及びリアプレート５０とによって形成する凹所３２が形成されると共に、ロックピン８０とこれを内部ロータ２０に向けて付勢するスプリング９１を収容する退避孔３３が外部ロータ３０の径方向に形成されている。尚、図１中、１１１はリアプレート５０のボス部５２の外周に係合するようにシリンダヘッド１１０に組付けられたオイルシールであり、ボス部５２は内周にてカムシャフト１０の外周に所定の隙間で回転自在に組付けられていて、カムシャフト１０の外周面にて実質的に支承されていない。
【００１６】
退避孔３３は、外端がプラグ９２とシール部材９３によって液密的に閉塞されていて、ロックピン８０の背部に背圧室Ｒ３が形成されている。本実施形態においては、この背圧室Ｒ３は、図２乃至図４に示すように、外部ロータ３０に設けられた通路３４と通路３５を夫々介して通路２４ａと進角用室Ｒ１ａとに連通されている。通路３４は、外部ロータ３０のフロントプレート４０側の側面に溝状に形成されていて、一端にて退避孔３３に連通すると共に他端にて通路２４ａに連通している。尚、通路３４の退避孔側開口は、通路２３を通して受容孔２２に供給される作動油によってロックピン８０がスプリング９１の付勢力に抗して頭部８１の先端が面取り部２６にある位置に移動したときに、ロックピン８０のスカート部８２によって閉塞されるように配設されている。また、通路３４の通路２４ａ側の他端は、内部ロータ２０と外部ロータ３０の相対位相が所定の位相（図２に示す最遅角位置）から内部ロータ２０が外部ロータ３０に対して所定角度進角側（図２において時計方向）に相対回転した位相までの範囲にて通路２４ａに連通し、内部ロータ２０が外部ロータ３０に対して最遅角位置から進角側に所定角度以上相対回転すると通路２４ａとの連通が遮断されるように配設されている。通路３５は、外部ロータ３０のリアプレート５０側の側面に溝状に形成されていて、一端にて退避孔３３に連通すると共に他端にて進角用室Ｒ１ａに連通している。尚、通路３５の退避孔側開口は、ロックピン８０がスプリング９１の付勢力に抗して退避孔３３内に移動したときにもロックピン８０のスカート部８２によって閉塞されないように配設されている。尚、プラグ９２はタイミングプーリ６０によって抜け止めされている。
【００１７】
また、本実施形態においては、図２の右上の作動室Ｒ０を区画する凹所３２の周方向端面の径方向内端に形成したストッパ部３６、３７に同作動室Ｒ０内に位置するベーン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（相対回転量）が制限されるようになっている。図３に示すように、この凹所３２の遅角用室Ｒ２側のストッパ部３７には、ベーン７０のストッパ部３７への当接時（最進角時）に通路２５が遅角用室Ｒ２（図３左上）に連通するように連通溝３７ａが形成されている。一方、進角用室Ｒ１ａ側のストッパ部３６には、図２に示すように、連通溝が形成されておらず、ベーン７０のストッパ部３６への当接時（最遅角時）から内部ロータ２０が外部ロータ３０に対して所定角度進角側に相対回転した位相までの範囲にて、通路２４ａと進角用室Ｒ１ａの連通が遮断されるようになっている。
【００１８】
ロックピン８０は、頭部８１とスカート部８２を有していて、スカート部８２にて退避孔３３に外部ロータ３０の径方向にて移動可能に嵌合されており、スプリング９１によって内部ロータ２０に向けて付勢されている。
【００１９】
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、内燃機関の停止時には、各部材が図１乃至図４に示した状態（遅角用室Ｒ２の容積が最大となり最遅角の状態でロックピン８０によるロックがなされている状態）にあり、またオイルポンプ１１２が停止していて各接続通路Ｐ１、Ｐ２に作動油が供給されない状態にある。この状態にて内燃機関が始動されると、非通電状態にある制御弁１００を介してオイルポンプ１１２から接続通路Ｐ１に少なくとも所定時間作動油が供給されることにより、カムシャフト１０の遅角通路１２及び通路２５を通して遅角用室Ｒ２に作動油が供給されると共に、通路２３を通して受容孔２２に作動油が供給される。同時に、非通電状態にある制御弁１００を介して接続通路Ｐ２がオイル溜め１１３に連通されることにより、進角用室Ｒ１が通路２４及び進角通路１１等を通してオイル溜め１１３に連通されると共に、進角用室Ｒ１ａが通路３５、退避孔３３、通路３４、通路２４ａ及び進角通路１１等を通してオイル溜め１１３に連通される。このとき、受容孔２２に作動油が所定量供給されるまでには所定時間を要し、内燃機関の始動開始から所定時間経過するまではロックピン８０の頭部８１は受容孔２２に嵌入されたままであるので、内燃機関始動時のカムシャフト１０の大きなトルク変動に伴う内部ロータ２０と外部ロータ３０等の不必要な相対回転が規制され、回転部材と回転伝達部材の不必要な相対回転に伴う不具合（例えば、ベーン７０による打音）を解消することができる。
【００２０】
内燃機関の始動開始から所定時間経過後には、図５に示したように、受容孔２２に供給される作動油によりロックピン８０がスプリング９１の付勢力に抗して退避孔３３に向けて移動し、スカート部８２が通路３４の退避孔側開口を閉塞して頭部８１の先端が受容孔２２の面取り部２６に位置する退避位置に保持されるとともに背圧室Ｒ３が密封空間となる。これにより、面取り部２６とロックピン８０の頭部８１の先端との隙間だけ内部ロータ２０は外部ロータ３０に対して相対回転可能となる。
【００２１】
かかる状態にて、制御弁１００のソレノイド１０３へ供給される電流のデューティ比を高くすることにより、進角通路１１に作動油が供給されるとともに遅角通路１２から作動油が排出されると、進角用室Ｒ１に供給される作動油によって内部ロータ２０が外部ロータ３０等回転伝達部材に対して最遅角位置から進角側に向けて相対回転するとともに進角用室Ｒ１ａの容積が拡大されて通路３５を介して背圧室Ｒ３内の作動油が進角用室Ｒ１ａに吸込まれロックピン８０が更に退避孔３３内に退避移動する。これにより、内燃機関の運転状態に応じて制御弁１００のソレノイド１０３へ供給される電流のデューティ比を高くして、遅角用室Ｒ２から作動油を排出すると共に進角用室Ｒ１、Ｒ１ａへ作動油を供給することにより、内部ロータ２０と外部ロータ３０等回転伝達部材を相対回転させて、ベーン７０がストッパ部３７に当接して遅角用室Ｒ２の容積が最小となる状態（最進角位置）とすることができるとともに、制御弁１００のソレノイド１０３へ供給される電流のデューティ比を低くして進角用室Ｒ１、Ｒ１ａから作動油を排出するとともに遅角用室Ｒ２へ作動油を供給することにより、内部ロータ２０と外部ロータ３０等回転伝達部材を相対回転させて、最進角状態から図２及び図３に示す最遅角位置の状態とすることができて、内燃機関の動弁装置において吸気弁の開閉時期を的確に制御することができる。また、制御弁１００のソレノイド１０３へ供給される電流のデューティ比を適宜制御して各進角用室Ｒ１、Ｒ１ａ及び各遅角用室Ｒ２へ夫々作動油を供給して、内部ロータ２０と外部ロータ３０等の相対位相を最遅角位置と最進角位置の間の任意な位相に保持することも可能である。このときには、摩擦力によりカムシャフト１０に遅角側へ作用するトルクによって内部ロータ２０には遅角側へのトルクが作用しているため、進角用室Ｒ１、Ｒ１ａの作動油圧＞遅角用室Ｒ２の作動油圧となるように作動油が供給される。
【００２２】
本実施形態においては、最遅角位置から微小角度だけ内部ロータ２０を外部ロータ３０等回転伝達部材に対して進角側に相対回転させた状態に内部ロータ２０と外部ロータ３０等回転伝達部材の位相が保持されるとき、通路２４ａと進角用室Ｒ１ａとの連通が遮断され、通路２４ａは通路３４の他端に連通される。ここで、通路３４の一端はロックピン８０のスカート部８２により閉塞され、これによりロックピン８０はオイルポンプ１１２から通路２４ａ及び通路３４を介して供給される作動油により退避孔３３の一側内周面に押動されて圧接されると共に、通路３５を介して進角用室Ｒ１ａに連通される背圧室Ｒ３にはオイルポンプ１１２からの作動油が供給されず、背圧室Ｒ３は密封状態にある。
【００２３】
ところで、上記した位相保持時には、カムシャフト１０に作用するトルク変動により内部ロータ２０が外部ロータ３０等回転伝達部材に対して微小振幅で振動しており、保持位置から内部ロータ２０が外部ロータ３０等回転伝達部材に対して遅角側へ相対回転したときに受容孔２２と退避孔３３が対向する最遅角位置になる場合がある。この時、本実施形態においては、背圧室Ｒ３から進角用室Ｒ１ａに至る密封された空間の容積が縮小して背圧室Ｒ３内の圧力が上昇するものの、受容孔２２には遅角用室Ｒ２から通路２３を介して作動油が供給されると共にロックピン８０が通路３４を介して供給される作動油により退避孔３３の一側内周面に押動されて圧接されているため、ロックピン８０は受容孔２２内に嵌入されずに退避孔３３内にて退避位置に保持される。これにより、上記した位相保持時にカムシャフト１０に作用するトルク変動により保持位置から内部ロータ２０が外部ロータ３０等回転伝達部材に対して遅角側へ相対回転して、受容孔２２と退避孔３３が対向する最遅角位置になった時に、ロックピン８０が受容孔２２に嵌入して、内部ロータ２０と外部ロータ３０等回転伝達部材の相対位相が最遅角位置に保持されてしまい、その後に進角用室Ｒ１に流体を供給すると共に遅角用室Ｒ２内の流体を排出して内部ロータ２０を外部ロータ３０等回転伝達部材に対して進角側へ相対回転させようとしても、ロックピン８０が受容孔２２から退避孔３３へ移動しないで内部ロータ２０と外部ロータ３０等回転伝達部材の相対回転が阻止され、当該弁開閉時期制御装置の作動が不能となることを的確に防止することができる。
【００２４】
上記実施形態においては、内部ロータ２０が外部ロータ３０等回転伝達部材に対して最遅角位置となることにより内部ロータ２０と外部ロータ３０等回転伝達部材の相対位相が受容孔２２と退避孔３３が対向する所定の位相となるように設定し、受容孔２２を通路２３を介して遅角用室Ｒ２に連通させると共に、退避孔３３を通路３５及び通路３４を介して進角用室Ｒ１ａ及び該進角用室Ｒ１ａに作動油を給排する通路２４ａに夫々連通させ、通路２４ａと進角用室Ｒ１ａとの連通を最遅角位置から内部ロータ２０が外部ロータ３０等回転伝達部材に対して所定角度進角側に相対回転するまでの間遮断するようにしたが、内部ロータが外部ロータ等回転伝達部材に対して最進角位置となることにより内部ロータと外部ロータ等回転伝達部材の相対位相が受容孔２２と退避孔３３が対向する所定の位相となるように設定し、受容孔を進角用室に連通させると共に、退避孔を１つの遅角用室及び該１つの遅角用室に作動油を給排する１つの第２流体通路に夫々連通させ、１つの第２流体通路と１つの遅角用室との連通を最進角位置から内部ロータが外部ロータ等回転伝達部材に対して所定角度遅角側に相対回転するまでの間遮断するようにしても良い。
【００２５】
また上記実施形態においては、吸気用のカムシャフト１０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。
【００２６】
【発明の効果】
以上の如く、本発明によれば、係合部材による回転部材と回転伝達部材の相対位相保持作動の誤作動を防止でき、回転部材の回転伝達部材に対する的確な相対回転を保証することができ、当該弁開閉時期制御装置の作動信頼性を向上することができる。
【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一実施形態を示す縦断側面図である。
【図２】図１のＡ−Ａ線に沿った断面図である。
【図３】図１のＢ−Ｂ線に沿った断面図である。
【図４】図１のＣ−Ｃ線に沿った断面図である。
【図５】係合部材（ロックピン）が退避孔へ退避した状態を示す図１に示す図１のＣ−Ｃ線に沿った断面図である。
【符号の説明】
１０カムシャフト
１１進角通路
１２遅角通路
２０内部ロータ（回転部材）
２２受容孔
２３通路（第３流体通路）
２４、２４ａ通路（第１流体通路）
２５通路（第２流体通路）
３０外部ロータ（回転伝達部材）
３２凹所
３３退避孔
３４通路（第５流体通路）
３５通路（第４流体通路）
３６、３７ストッパ部
４０フロントプレート（回転伝達部材）
５０リアプレート（回転伝達部材）
７０ベーン
８０ロックピン（係合部材）
９１スプリング
Ｒ０作動室（流体圧室）
Ｒ１、Ｒ１ａ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 valve or an 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 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 that rotates together with a crankshaft of the internal combustion engine. A plurality of fluid pressure chambers formed between the rotation member and the rotation transmission member and divided into an advance chamber and a retard chamber by a plurality of vanes provided on the rotation member; A plurality of first fluid passages for supplying and discharging fluid to and from the corner chamber; a plurality of second fluid passages for supplying and discharging fluid to and from the retardation chamber; A retraction hole that accommodates the spring-biased engagement member, and one end of the engagement member is inserted when the relative phase of the rotation member and the rotation transmission member formed in the rotation member is synchronized at a predetermined phase. The receiving hole and the receiving hole There is that a third fluid passage for supplying and discharging body, for example, disclosed in JP-A-10-184321.
[0003]
In the valve opening / closing timing control device disclosed in the above publication, the relative phase between the rotation member and the rotation transmission member is set to a predetermined phase when the rotation member is at the most retarded position with respect to the rotation transmission member. In this case, the third fluid passage is communicated with the retarding chamber and the retraction hole is communicated with the advance chamber via the fourth fluid passage so that the rotating member is at the most advanced position with respect to the rotation transmitting member. Accordingly, when the relative phase between the rotating member and the rotation transmitting member is set to be a predetermined phase, the third fluid passage is communicated with the advance angle chamber, and the escape hole is delayed via the fourth fluid passage. It communicates with the corner room.
[0004]
[Problems to be solved by the invention]
In the valve timing control apparatus disclosed in the above publication, when the most retarded angle position is set to a predetermined phase, the rotation member is advanced from the most retarded angle position by a minute angle with respect to the rotation transmission member. When the phase of the rotation member and the rotation transmission member is maintained in a state of being relatively rotated, the fluid is supplied to the advance chamber and the retard chamber via the first fluid passage and the second fluid passage, Because the torque acting on the camshaft is retarded by the frictional force, the retarding torque is acting on the rotating member, so that the fluid pressure in the advance chamber is greater than the fluid pressure in the retard chamber. Fluid is supplied. For this reason, at the time of the above-described phase holding, the retracting hole has a larger force than the force for moving the engaging member out of the receiving hole by the fluid pressure in the retarding chamber supplied to the receiving hole via the third fluid passage. The force for moving the engaging member toward the rotating member is increased by the fluid pressure and the spring biasing force of the advance chamber supplied through the fourth fluid passage.
[0005]
By the way, at the time of holding the phase of the rotating member and the rotation transmitting member, the rotating member vibrates with a minute amplitude with respect to the rotation transmitting member due to the torque fluctuation acting on the camshaft. There are cases where the receiving hole and the retracting hole are at the most retarded position where they face each other when they rotate relative to the retard side. At this time, in the valve opening / closing timing control device disclosed in the above publication, the force for moving the engaging member toward the rotating member is larger than the force for moving the engaging member out of the receiving hole. Therefore, one end of the engaging member is fitted into the receiving hole, the relative phase between the rotating member and the rotation transmitting member is held at the most retarded position, and then the fluid is supplied to the advance chamber. At the same time, even if the fluid in the retarding chamber is discharged to rotate the rotating member relative to the rotation transmitting member relative to the advance angle, the engaging member does not move from the receiving hole to the retracting hole and the rotating member and the rotation transmitting member. The relative rotation of the valve is prevented, and the operation of the valve timing control device may be disabled.
[0006]
In the valve opening / closing timing control device disclosed in the above publication, when the most advanced angle position is set to have a predetermined phase, the rotation member is moved from the most advanced angle position by a minute angle with respect to the rotation transmission member. Similarly, when the phase of the rotating member and the rotation transmitting member is maintained in a state of being relatively rotated to the retarded angle side, the fluid is similarly advanced so that the fluid pressure in the advance angle chamber is greater than the fluid pressure in the retard angle chamber. And a force that is supplied to the retarding chamber and that moves the engaging member out of the receiving hole by the fluid pressure of the advance chamber supplied to the receiving hole via the third fluid passage. The force for moving the engaging member toward the rotating member by the fluid pressure and the spring biasing force of the retarding chamber supplied through the fourth fluid passage is smaller. However, in this state, due to torque fluctuations acting on the camshaft, the rotating member may rotate relative to the rotation transmitting member toward the advance angle side to reach the most advanced position where the receiving hole and the retraction hole face each other. Sometimes the fluid pressure in the retard chamber increases due to the movement of the rotating member, and the force that moves the engaging member toward the rotating member rather than the force that moves the engaging member out of the receiving hole. Becomes larger. For this reason, when the receiving hole and the retraction hole are at the most advanced angle position where they face each other, one end of the engaging member is fitted into the receiving hole, and the relative phase between the rotating member and the rotation transmitting member is held at the most advanced angle position. After that, even if the fluid is supplied to the retarding chamber and the fluid in the advancement chamber is discharged to rotate the rotating member relative to the rotation transmitting member relative to the retarding side, Relative rotation of the rotating member and the rotation transmitting member is prevented without moving from the receiving hole to the retracting hole, and the operation of the valve opening / closing timing control device may be disabled.
[0007]
Therefore, an object of the present invention is to prevent malfunction of the relative phase holding operation of the rotation member and the rotation transmission member by the engaging member in the valve opening / closing timing control device.
[0008]
The technical means of the present invention taken in order to solve the above problems includes a rotating member that rotates together with one of a crankshaft and a camshaft of an internal combustion engine, and the rotating member that is externally rotatably mounted within a predetermined range. A rotation transmission member that rotates together with the other of the shaft and the cam shaft, and a plurality of vanes provided between the rotation member and the rotation transmission member, respectively, and for the advance angle chamber and the retard angle, respectively. A plurality of fluid pressure chambers divided into chambers, a plurality of first fluid passages for supplying and discharging fluid to the advance chamber, and a plurality of second fluid passages for supplying and discharging fluid to the retard chamber A retraction hole for accommodating an engaging member formed in one of the rotating member and the rotation transmitting member and spring-biased toward the other of the rotating member and the rotation transmitting member, and the rotating member and Rotation transmission Formed on the other timber, the relative phase between the rotation transmission member and the rotating member When in phase A receiving hole into which one end of the engaging member is inserted, and the receiving hole The engaging member is urged toward the retracting hole. In the valve timing control apparatus having a third fluid passage for supplying and discharging fluid, the third fluid passage is communicated with one of the retardation chamber and the advance chamber, and the retraction hole is provided. One of the retard chamber and the advance chamber Always connected to A fluid that urges the engaging member toward the receiving hole is supplied to and discharged from the retracting hole. A fourth fluid passage; At least until the relative phase between the rotating member and the rotation transmitting member changes from the predetermined phase to a predetermined angle The escape hole The other one of the retard chamber and the advance chamber The first fluid passage for supplying and discharging fluid to and from the first fluid passage One of A fifth fluid passage which is communicated with one of the second fluid passages and whose retraction hole side opening is closed on a side surface of the engagement member when the engagement member moves against a spring biasing force; Provided, Communication between the other one of the retarding chamber and the advance chamber and the one of the first fluid passages or the one of the second fluid passages, The relative phase of the rotation member and the rotation transmission member is From the predetermined phase This is to cut off until a predetermined angle is changed.
[0009]
According to the above-described means, the rotation member and the rotation transmission with the rotation member relatively rotated from the most retarded angle position (most advanced angle position) to the advance angle side (retard angle side) relative to the rotation transmission member by a minute angle. When the relative phase of the members is maintained, communication between one first fluid passage (second fluid passage) and one advance chamber (one retard chamber) is blocked, and one first fluid passage The (second fluid passage) communicates with the other end of the fifth fluid passage whose one end on the retreat hole side is closed by the engaging member, and one advance chamber (one retard chamber) is the fourth fluid. It communicates with the escape hole through the passage. At the time of this phase holding, the rotating member vibrates with a minute amplitude with respect to the rotation transmitting member due to the torque fluctuation acting on the camshaft, and the rotating member is retarded (advanced side) with respect to the rotation transmitting member from the holding position. In some cases, the receiving hole 2 and the retraction hole face each other at the most retarded angle position (most advanced angle position). Although the volume of the sealed space leading to the chamber is reduced and the pressure in the retraction hole is increased, the working oil is supplied from the retarding chamber (advancing chamber) to the receiving hole via the third fluid passage 23. Since the engagement member is pressed and pressed against the inner peripheral surface of one side of the retraction hole by the hydraulic oil supplied and supplied through the fifth fluid passage, the engagement member is inserted into the reception hole. Without being held in the retracted position in the retracting hole. Thereby, the malfunction of the relative phase holding operation of the rotating member and the rotation transmitting member by the engaging member is accurately prevented, and the accurate relative rotation of the rotating member with respect to the rotation transmitting member is ensured.
[0010]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of a valve timing control apparatus according to the present invention will be described with reference to the drawings.
[0011]
The valve opening / closing timing control device shown in FIG. 1 to FIG. 5 includes a rotating member comprising an internal rotor 20 that is integrally assembled with the tip of a camshaft 10 that is rotatably supported by a cylinder head 110 of an internal combustion engine, A rotation transmission member composed of an outer rotor 30, a front plate 40, a cap 41, a rear plate 50, a timing pulley 60, and the like that are externally mounted on the camshaft 10 and the inner rotor 20 so as to be relatively rotatable within a predetermined range. The six vanes 70 are attached, and the lock pins 80 are attached to the external rotor 30. As is well known, the timing pulley 60 is configured such that rotational power is transmitted in the clockwise direction of FIG. 2 from the crankshaft of the internal combustion engine via a crank pulley and a resin or rubber timing belt (all not shown). Has been. The power transmission from the crankshaft to the rotation transmission member can also be carried out through a timing chain or a timing gear that is employed instead of the timing belt.
[0012]
The camshaft 10 has a known cam (not shown) for opening and closing an intake valve (not shown), and an advance angle passage 11 and a retard angle passage 12 extending in the axial direction of the camshaft 10 are provided inside. ing. The advance passage 11 is connected to the connection port 102 of the control valve 100 through a radial passage 13, an annular oil passage 14, and a connection passage P2. The retard passage 12 is connected to the connection port 101 of the control valve 100 via an annular oil passage 15 and a connection passage P1.
[0013]
The control valve 100 can move the spool 104 to the left in FIG. 1 against the spring 105 by energizing the solenoid 103, and is connected to an oil pump 112 driven by the internal combustion engine when deenergized. The supply port 106 communicates with the connection port 101, the connection port 102 communicates with the discharge port 107, and when energized, the supply port 106 communicates with the connection port 102, and the connection port 101 communicates with the discharge port 107. It is configured as follows. For this reason, when the solenoid 103 of the control valve 100 is not energized, hydraulic oil is supplied from the oil pump 112 to the retard passage 12 and discharged from the advance passage 11 to the oil reservoir 113, and from the oil pump 112 when energized. The hydraulic oil is supplied to the advance passage 11 and discharged from the retard passage 12 to the oil reservoir 113. The energization of the solenoid 103 is duty-controlled by a control device (not shown).
[0014]
The inner rotor 20 is integrally fixed to the camshaft 10 by a hollow bolt 19 and has vane grooves 21 for attaching the vanes 70 of the six vanes in the radial direction, respectively. 3, that is, when the relative phase of the camshaft 10 and the inner rotor 20 and the outer rotor 30 reaches a predetermined phase (most retarded angle position), a receiving portion into which the head 81 of the lock pin 80 is inserted by a predetermined amount. Hole 22, passage 23 for supplying and discharging hydraulic oil from retarding passage 12 to retarding passage 12 through retarding chamber R <b> 2 defined by each vane 70, and each vane (excluding the upper right vane in FIG. 2). ) Actuate from the advance passage 11 to the advance chamber R1 partitioned by the passage 24 for supplying and discharging the hydraulic oil from the advance passage 11 to the advance chamber R1 partitioned by 70 and the advance chamber R1a partitioned by the upper right vane 70 in FIG. Supply and discharge oil That a passage 24a, and has a passage 25 for supplying and discharging hydraulic oil from the retarded angle passage 12 to the retarded angle chamber R2 sectioned by each vane 70. As shown in FIG. 4, the receiving hole 22 is a bottomed hole having a predetermined amount larger than the outer diameter of the head 81 of the lock pin 80, and is an annular formed by the head 81 of the lock pin 80. The hydraulic oil is supplied to and discharged from the bottom of the receiving hole 22 through the gap, and a chamfered portion 26 is formed at the periphery of the open end. Each vane 70 is urged radially outward by a spring 71 (see FIG. 1) housed in the bottom of the vane groove 21.
[0015]
The outer rotor 30 is assembled to the outer peripheral surface of the inner rotor 20 at its inner periphery so as to be relatively rotatable with a predetermined gap (minimum gap in which hydraulic oil intervenes), and the front plate 40 and the rear plate are disposed on both sides thereof. 50 is joined via seal members S1 and S2, and is connected together with the timing pulley 60 by a bolt B1. A cap 41 is assembled in a fluid-tight manner on the front plate 40, thereby forming a passage 42 that connects the advance passage 11 of the camshaft 10 and the passages 24, 24 a of the internal rotor 20. Further, the outer rotor 30 accommodates each vane 70, and the working chamber R0 divided into the advance chambers R1, R1a and the retard chamber R2 by each vane 70 includes the inner rotor 20, the front plate 40, and the rear plate. 50, and a recess hole 33 for accommodating a lock pin 80 and a spring 91 that biases the lock pin 80 toward the inner rotor 20 is formed in the radial direction of the outer rotor 30. In FIG. 1, reference numeral 111 denotes an oil seal assembled to the cylinder head 110 so as to be engaged with the outer periphery of the boss portion 52 of the rear plate 50. The boss portion 52 is formed on the outer periphery of the camshaft 10 on the inner periphery. The camshaft 10 is rotatably assembled with a predetermined gap and is not substantially supported on the outer peripheral surface of the camshaft 10.
[0016]
The retraction hole 33 is liquid-tightly closed at its outer end by a plug 92 and a seal member 93, and a back pressure chamber R 3 is formed at the back of the lock pin 80. In the present embodiment, the back pressure chamber R3 communicates with the passage 24a and the advance chamber R1a through a passage 34 and a passage 35 provided in the external rotor 30, respectively, as shown in FIGS. Has been. The passage 34 is formed in a groove shape on the side surface of the external rotor 30 on the front plate 40 side, and communicates with the retraction hole 33 at one end and communicates with the passage 24a at the other end. The opening on the side of the retraction hole of the passage 34 is located at a position where the tip of the head 81 is at the chamfered portion 26 against the urging force of the spring 91 by the hydraulic oil supplied to the receiving hole 22 through the passage 23. When moved, the lock pin 80 is disposed so as to be blocked by the skirt portion 82. Further, the other end of the passage 34 on the passage 24 a side is such that the relative phase between the internal rotor 20 and the external rotor 30 is a predetermined angle with respect to the external rotor 30 from the predetermined phase (the most retarded position shown in FIG. 2). The internal rotor 20 communicates with the passage 24a in the range up to the phase of relative rotation on the advance side (clockwise in FIG. 2), and the internal rotor 20 rotates relative to the external rotor 30 more than a predetermined angle from the most retarded position to the advance side. Then, it arrange | positions so that a communication with the channel | path 24a may be interrupted | blocked. The passage 35 is formed in a groove shape on the side surface of the external rotor 30 on the rear plate 50 side, and communicates with the retreat hole 33 at one end and communicates with the advance chamber R1a at the other end. The opening on the side of the retraction hole of the passage 35 is arranged so as not to be blocked by the skirt portion 82 of the lock pin 80 even when the lock pin 80 moves into the retraction hole 33 against the urging force of the spring 91. Yes. Note that the plug 92 is retained by the timing pulley 60.
[0017]
Further, in the present embodiment, the vanes 70 located in the working chamber R0 are provided at the stopper portions 36 and 37 formed at the radially inner end of the circumferential end surface of the recess 32 that defines the upper right working chamber R0 in FIG. Makes contact with each other so that the phase (relative rotation amount) adjusted by the valve timing control device is limited. As shown in FIG. 3, in the stopper portion 37 on the retard angle chamber R2 side of the recess 32, the passage 25 is provided with a retard angle chamber when the vane 70 comes into contact with the stopper portion 37 (at the most advanced angle). A communication groove 37a is formed so as to communicate with R2 (upper left in FIG. 3). On the other hand, as shown in FIG. 2, the stopper portion 36 on the advance angle chamber R1a side is not formed with a communication groove, and the internal space from when the vane 70 abuts against the stopper portion 36 (at the most retarded angle). The communication between the passage 24a and the advance angle chamber R1a is blocked in a range up to a phase where the rotor 20 rotates relative to the external rotor 30 at a predetermined angle advance side.
[0018]
The lock pin 80 has a head portion 81 and a skirt portion 82, and the skirt portion 82 is fitted in the retraction hole 33 so as to be movable in the radial direction of the external rotor 30. It is energized towards.
[0019]
In the valve opening / closing timing control apparatus of the present embodiment configured as described above, when the internal combustion engine is stopped, each member is in the state shown in FIGS. 1 to 4 (the volume of the retard chamber R2 is maximized and the most retarded angle). In this state, the lock pin 80 is locked), and the oil pump 112 is stopped and no hydraulic oil is supplied to the connection passages P1 and P2. When the internal combustion engine is started in this state, hydraulic oil is supplied from the oil pump 112 to the connection passage P1 through the non-energized control valve 100 for at least a predetermined time, whereby the retard passage of the camshaft 10 is supplied. The hydraulic oil is supplied to the retardation chamber R <b> 2 through the passage 12 and the passage 25, and is supplied to the receiving hole 22 through the passage 23. At the same time, the connection passage P2 is communicated with the oil sump 113 through the control valve 100 in the non-energized state, whereby the advance angle chamber R1 is communicated with the oil sump 113 through the passage 24, the advance angle passage 11 and the like. The advance angle chamber R1a communicates with the oil reservoir 113 through the passage 35, the retraction hole 33, the passage 34, the passage 24a, the advance passage 11 and the like. At this time, a predetermined time is required until a predetermined amount of hydraulic oil is supplied to the receiving hole 22, and the head 81 of the lock pin 80 is fitted into the receiving hole 22 until a predetermined time has elapsed since the start of the internal combustion engine. Therefore, unnecessary relative rotation of the internal rotor 20 and the external rotor 30 due to a large torque fluctuation of the camshaft 10 at the start of the internal combustion engine is restricted, and unnecessary rotation of the rotating member and the rotation transmitting member is prevented. The accompanying trouble (for example, the hitting sound by the vane 70) can be eliminated.
[0020]
After a predetermined time has elapsed since the start of the internal combustion engine, as shown in FIG. 5, the lock pin 80 moves toward the retraction hole 33 against the urging force of the spring 91 by the hydraulic oil supplied to the receiving hole 22. The skirt portion 82 closes the retreat hole side opening of the passage 34 so that the tip of the head 81 is held at the retreat position located at the chamfered portion 26 of the receiving hole 22 and the back pressure chamber R3 becomes a sealed space. As a result, the inner rotor 20 can rotate relative to the outer rotor 30 only by a gap between the chamfered portion 26 and the tip of the head 81 of the lock pin 80.
[0021]
In this state, by increasing the duty ratio of the current supplied to the solenoid 103 of the control valve 100, when hydraulic fluid is supplied to the advance passage 11 and discharged from the retard passage 12, The hydraulic fluid supplied to the advance chamber R1 causes the inner rotor 20 to rotate relative to the rotation transmission member such as the outer rotor 30 from the most retarded position toward the advance side, and the volume of the advance chamber R1a is increased. Then, the hydraulic oil in the back pressure chamber R3 is sucked into the advance angle chamber R1a via the passage 35, and the lock pin 80 is further retreated into the retreat hole 33. As a result, the duty ratio of the current supplied to the solenoid 103 of the control valve 100 is increased in accordance with the operating state of the internal combustion engine, the hydraulic oil is discharged from the retard chamber R2, and the advance chambers R1, R1a are discharged. By supplying the hydraulic oil, the rotation transmission member such as the inner rotor 20 and the outer rotor 30 is rotated relative to each other, and the vane 70 comes into contact with the stopper portion 37 so that the volume of the retarding chamber R2 is minimized (the most advanced). Angular position), the duty ratio of the current supplied to the solenoid 103 of the control valve 100 is lowered to discharge the hydraulic oil from the advance chambers R1 and R1a and to the retard chamber R2. , The internal rotor 20 and the external rotor 30 and the like can be rotated relative to each other, so that the most advanced angle state can be changed to the most retarded angle position shown in FIGS. Closing timing of the intake valve can be accurately controlled in the valve gear of the function. Further, the duty ratio of the current supplied to the solenoid 103 of the control valve 100 is appropriately controlled to supply hydraulic oil to each of the advance chambers R1, R1a and each retard chamber R2, and the internal rotor 20 and the external It is also possible to keep the relative phase of the rotor 30 or the like at an arbitrary phase between the most retarded position and the most advanced position. At this time, because the torque acting on the camshaft 10 to the retard side due to the frictional force acts on the internal rotor 20 to the retard side, the hydraulic pressure in the advance chambers R1 and R1a> the retard angle The hydraulic oil is supplied so as to be the hydraulic pressure of the chamber R2.
[0022]
In the present embodiment, the internal rotor 20 and the external rotor 30 and the like rotation transmission member are rotated relative to the rotation transmission member such as the external rotor 30 and the like at an angle of advance from the most retarded angle position by a minute angle. When the phase is maintained, the communication between the passage 24a and the advance chamber R1a is blocked, and the passage 24a is communicated with the other end of the passage 34. Here, one end of the passage 34 is closed by the skirt portion 82 of the lock pin 80, so that the lock pin 80 is moved in one side of the retraction hole 33 by the hydraulic oil supplied from the oil pump 112 through the passage 24 a and the passage 34. The hydraulic pressure from the oil pump 112 is not supplied to the back pressure chamber R3 that is pushed and pressed against the peripheral surface and communicates with the advance chamber R1a via the passage 35, and the back pressure chamber R3 is sealed. Is in a state.
[0023]
By the way, at the time of the above-described phase holding, the internal rotor 20 vibrates with a small amplitude with respect to the rotation transmitting member such as the external rotor 30 due to the torque fluctuation acting on the camshaft 10, and the internal rotor 20 is moved from the holding position to the external rotor 30 and the like. In some cases, the receiving hole 22 and the retracting hole 33 are at the most retarded angle position when the rotation transmitting member rotates relative to the retard angle side. At this time, in this embodiment, although the volume of the sealed space from the back pressure chamber R3 to the advance chamber R1a is reduced and the pressure in the back pressure chamber R3 is increased, the receiving hole 22 is retarded. The hydraulic oil is supplied from the chamber R2 through the passage 23, and the lock pin 80 is pushed and pressed against the inner peripheral surface of the retraction hole 33 by the hydraulic oil supplied through the passage 34. The lock pin 80 is held in the retracted position in the retracting hole 33 without being fitted into the receiving hole 22. As a result, due to the torque fluctuation acting on the camshaft 10 during the phase holding described above, the inner rotor 20 rotates relative to the rotation transmission member such as the outer rotor 30 from the holding position to the retard side, and the receiving hole 22 and the retreating hole 33 are thereby rotated. , The lock pin 80 is fitted into the receiving hole 22, and the relative phase of the rotation transmission member such as the inner rotor 20 and the outer rotor 30 is held at the most retarded position. Even if the fluid is supplied to the advance chamber R1 and the fluid in the retard chamber R2 is discharged to cause the internal rotor 20 to rotate relative to the rotational transmission member such as the external rotor 30 toward the advance side, the lock is applied. The pin 80 does not move from the receiving hole 22 to the retracting hole 33, so that the relative rotation of the rotation transmitting member such as the internal rotor 20 and the external rotor 30 is prevented, and the valve opening / closing timing control device cannot be operated. It is possible to prevent the.
[0024]
In the embodiment described above, the internal rotor 20 is at the most retarded position with respect to the rotation transmission member such as the external rotor 30, so that the relative phases of the internal rotor 20 and the rotation transmission member such as the external rotor 30 are the receiving hole 22 and the retraction hole 33. Are set so as to be in a predetermined phase facing each other, the receiving hole 22 is communicated with the retarding angle chamber R2 through the passage 23, and the retracting hole 33 is communicated with the advance angle chamber R1a through the passage 35 and the passage 34. The advance chamber R1a is communicated with a passage 24a for supplying and discharging hydraulic oil, and the passage between the passage 24a and the advance chamber R1a is communicated with the rotation transmission member such as the outer rotor 30 from the most retarded position. Until the relative rotation to the predetermined angle advance side, the inner rotor is at the most advanced angle position relative to the rotation transmission member such as the outer rotor, so that the rotation transmission member such as the inner rotor and the outer rotor The counter phase is set to be a predetermined phase in which the receiving hole 22 and the retracting hole 33 are opposed to each other, the receiving hole is communicated with the advance chamber, and the retract hole is provided with one retard chamber and the one retard angle. Communicating with one second fluid passage for supplying and discharging hydraulic oil to and from the working chamber, and communicating with one second fluid passage and one retarding angle chamber from the most advanced position to the internal rotor and the outer rotor, etc. You may make it interrupt | block until it rotates relatively to a predetermined angle retard side with respect to a member.
[0025]
In the above embodiment, the present invention is applied to the valve opening / closing timing control device assembled to the intake camshaft 10, but the present invention is also applied to the valve opening / closing timing control device assembled to the exhaust camshaft. Can be implemented.
[0026]
【The invention's effect】
As described above, according to the present invention, it is possible to prevent erroneous operation of the relative phase holding operation between the rotation member and the rotation transmission member by the engagement member, and it is possible to ensure accurate relative rotation of the rotation member with respect to the rotation transmission member. The operational reliability of the valve timing control device can be improved.
[Brief description of the drawings]
FIG. 1 is a longitudinal side view showing an embodiment of a valve timing control apparatus according to the present invention.
FIG. 2 is a cross-sectional view taken along line AA in FIG.
3 is a cross-sectional view taken along line BB in FIG. 1. FIG.
4 is a cross-sectional view taken along the line CC in FIG. 1. FIG.
5 is a cross-sectional view taken along the line CC of FIG. 1 shown in FIG. 1 showing a state in which the engaging member (lock pin) is retracted into the retracting hole.
[Explanation of symbols]
10 Camshaft
11 Advance passage
12 retarded passage
20 Internal rotor (rotating member)
22 Receiving hole
23 passage (third fluid passage)
24, 24a passage (first fluid passage)
25 passage (second fluid passage)
30 External rotor (rotation transmission member)
32 recess
33 Retraction hole
34 passage (5th fluid passage)
35 passage (fourth fluid passage)
36, 37 Stopper
40 Front plate (Rotation transmission member)
50 Rear plate (Rotation transmission member)
70 Vane
80 Lock pin (engagement member)
91 Spring
R0 working chamber (fluid pressure chamber)
R1, R1a Lead angle chamber
R2 retarding chamber

Claims

A rotating member that rotates with one of the crankshaft and camshaft of the internal combustion engine;
A rotation transmitting member which is externally mounted on the rotating member so as to be relatively rotatable within a predetermined range, and rotates together with the other of the crankshaft and the camshaft;
A plurality of fluid pressure chambers formed between the rotation member and the rotation transmission member and divided into an advance angle chamber and a retard angle chamber by a plurality of vanes provided in the rotation member;
A plurality of first fluid passages for supplying and discharging fluid to the advance chamber;
A plurality of second fluid passages for supplying and discharging fluid to the retardation chamber;
A retraction hole that is formed in one of the rotation member and the rotation transmission member and accommodates an engagement member that is spring-biased toward the other of the rotation member and the rotation transmission member.
A receiving hole that is formed on the other of the rotation member and the rotation transmission member and into which one end of the engagement member is fitted when the relative phase between the rotation member and the rotation transmission member is in a predetermined phase ;
A valve opening / closing timing control device comprising a third fluid passage for supplying and discharging a fluid for urging the engaging member toward the retreating hole in the receiving hole;
Communicating the third fluid passage with one of the retard chamber and the advance chamber;
The retraction hole is always in communication with the other one of the retardation chamber and the advance chamber, and a fluid for urging the engagement member toward the receiving hole is supplied to and discharged from the retraction hole . A fluid passage;
Fluid is supplied to the other one of the retard chamber and the advance chamber until the relative phase between the rotating member and the rotation transmitting member changes at a predetermined angle from the predetermined phase. When one of the first fluid passages to be exhausted or one of the second fluid passages communicates and the engagement member moves against a spring biasing force, a retraction hole is formed on a side surface of the engagement member. Providing a fifth fluid passage whose side opening is closed;
The retarded angle chamber and the advanced angle chamber of the other of the one, the one communicating said one or said second fluid passage of said first fluid passageway, said rotary member and the rotation transmitting member A valve opening / closing timing control device characterized in that the relative phase is interrupted until the predetermined angle changes from the predetermined phase to the predetermined angle.

A rotating member that rotates with one of the crankshaft and camshaft of the internal combustion engine;
A rotation transmitting member which is externally mounted on the rotating member so as to be relatively rotatable within a predetermined range, and rotates together with the other of the crankshaft and the camshaft;
A plurality of fluid pressure chambers formed between the rotation member and the rotation transmission member and divided into an advance angle chamber and a retard angle chamber by a plurality of vanes provided in the rotation member;
A plurality of first fluid passages for supplying and discharging fluid to the advance chamber;
A plurality of second fluid passages for supplying and discharging fluid to the retardation chamber;
A retraction hole that is formed in one of the rotation member and the rotation transmission member and accommodates an engagement member that is spring-biased toward the other of the rotation member and the rotation transmission member.
A receiving hole that is formed on the other of the rotation member and the rotation transmission member, and into which one end of the engagement member is fitted when the relative phase between the rotation member and the rotation transmission member is in the most retarded phase ;
A valve opening / closing timing control device comprising a third fluid passage for supplying and discharging a fluid for urging the engaging member toward the retreating hole in the receiving hole;
The third fluid passage communicates with either one of the retard chamber and the second fluid passage;
A fourth fluid passage that constantly communicates the escape hole with one of the advance chambers;
The first fluid passage for supplying and discharging fluid to the one of the advance chambers through the retraction hole at least until the relative phase between the rotation member and the rotation transmission member changes by a predetermined angle from the most retarded position. A fifth fluid passage having a retraction hole side opening closed on a side surface of the engagement member when the engagement member moves against a spring biasing force.
The retraction hole communicates with one of the advance chamber and one of the first fluid passages via the fourth fluid passage and the fifth fluid passage,
Blocking period from the most retarded position one of one of the communication of the advanced angle chamber of the first fluid passage to said rotary member to rotate relative to said predetermined angle advance side with respect to the rotation transmission member A valve opening / closing timing control device characterized by comprising:

A rotating member that rotates with one of the crankshaft and camshaft of the internal combustion engine;
A rotation transmitting member which is externally mounted on the rotating member so as to be relatively rotatable within a predetermined range, and rotates together with the other of the crankshaft and the camshaft;
A plurality of fluid pressure chambers formed between the rotation member and the rotation transmission member and divided into an advance angle chamber and a retard angle chamber by a plurality of vanes provided in the rotation member;
A plurality of first fluid passages for supplying and discharging fluid to the advance chamber;
A plurality of second fluid passages for supplying and discharging fluid to the retardation chamber;
A retraction hole that is formed in one of the rotation member and the rotation transmission member and accommodates an engagement member that is spring-biased toward the other of the rotation member and the rotation transmission member.
A receiving hole that is formed on the other of the rotation member and the rotation transmission member, and into which one end of the engagement member is fitted when the relative phase between the rotation member and the rotation transmission member is at the most advanced angle position ;
A valve opening / closing timing control device comprising a third fluid passage for supplying and discharging a fluid for urging the engaging member toward the retreating hole in the receiving hole;
The third fluid passage communicates with one of the advance chamber and the first fluid passage;
A fourth fluid passage that constantly communicates the retraction hole with one of the retardation chambers;
The second fluid passage for supplying and discharging fluid to the one of the retarding chambers through the retracting hole until at least the relative phase between the rotating member and the rotation transmitting member changes by a predetermined angle from the most advanced position. A fifth fluid passage having a retraction hole side opening closed on a side surface of the engagement member when the engagement member moves against a spring biasing force.
The escape hole communicates with one of the retardation chamber and one of the second fluid passages via the fourth fluid passage and the fifth fluid passage,
Blocking period from the most advanced position one of one of the communication of the retarded angle chamber of the second fluid passage to said rotary member to rotate relative to the predetermined angle retard side with respect to the rotation transmission member A valve opening / closing timing control device characterized by comprising: