JPH079168B2 - Valve drive for internal combustion engine - Google Patents
Valve drive for internal combustion engineInfo
- Publication number
- JPH079168B2 JPH079168B2 JP62292618A JP29261887A JPH079168B2 JP H079168 B2 JPH079168 B2 JP H079168B2 JP 62292618 A JP62292618 A JP 62292618A JP 29261887 A JP29261887 A JP 29261887A JP H079168 B2 JPH079168 B2 JP H079168B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- hydraulic
- hydraulic pressure
- cam
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Valve Device For Special Equipments (AREA)
Description
【発明の詳細な説明】 A.発明の目的 （１） 産業上の利用分野 本発明は、クランク軸により駆動されるカムシャフトに
設けられたカムと、閉弁方向にばね付勢された吸気弁あ
るいは排気弁との間に、一端がカムに連動、連結された
カム側ピストンの他端に臨む作動油室の油圧増大に応じ
て吸気弁あるいは排気弁を開弁作動すべく弁側ピストン
が吸気弁あるいは排気弁に連動、連結されて成る油圧駆
動機構が介装され、開弁作動時に油圧を解放すべく該作
動油室には油圧解放弁が接続される内燃機関の動弁装置
に関する。DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Field of Industrial Application The present invention relates to a cam provided on a camshaft driven by a crankshaft and an intake valve spring-biased in a valve closing direction. Alternatively, the valve-side piston intakes to open the intake valve or the exhaust valve in response to an increase in the hydraulic pressure of the hydraulic oil chamber facing the other end of the cam-side piston that is linked to the cam and connected to the exhaust valve. The present invention relates to a valve operating system of an internal combustion engine in which a hydraulic drive mechanism that is interlocked with and connected to a valve or an exhaust valve is interposed, and a hydraulic pressure release valve is connected to the hydraulic oil chamber to release hydraulic pressure when the valve is opened.
（２） 従来の技術 従来、かかる動弁装置は、たとえば特開昭61-229912号
公報により公知である。(2) Conventional Technology Conventionally, such a valve operating device is known, for example, from Japanese Patent Application Laid-Open No. 61-229912.
（３） 発明が解決しようとする問題点 ところで、かかる動弁装置では機関の高回転時には油圧
解放弁の作動を速やかにする必要があるが、上記従来の
ものでは、電磁弁を油圧解放弁として用いており、この
電磁弁の応答速度を機関の高回転に対応させるのは困難
である。(3) Problems to be Solved by the Invention By the way, in such a valve operating device, it is necessary to promptly activate the hydraulic release valve when the engine is rotating at a high speed. It is difficult to make the response speed of this solenoid valve correspond to the high engine speed.
本発明は、かかる事情に鑑みてなされたものであり、油
圧解放弁の作動を機関の回転に対応させて高回転時にも
充分対処し得るようにした内燃機関の動弁装置を提供す
ることを目的とする。The present invention has been made in view of such circumstances, and it is an object of the present invention to provide a valve operating system for an internal combustion engine, in which the operation of the hydraulic pressure release valve is made to correspond to the rotation of the engine, and it is possible to sufficiently cope with it even at a high rotation speed. To aim.
B.発明の構成 （１） 問題点を解決するための手段 本発明によれば、油圧解放弁は、作動油室に連通する出
口油路を有するハウジングと、出口油路に常時連通すべ
く周方向に長く延びて側壁に穿設された第１弁孔を有し
て円筒状に形成されるとともに前記ハウジングに軸線ま
わりの回動を可能として嵌合されるアウタシャフトと、
内部に形成された油圧解放路に通じるべく半径方向に延
びる第２弁孔を前記第１弁孔に対応する位置の側壁に有
する円筒状に形成されたアウタシャフト内に回転自在に
嵌合されるとともにカムシャフトに連動、連結されるイ
ンナシャフトとを備える。B. Configuration of the Invention (1) Means for Solving the Problems According to the present invention, the hydraulic pressure release valve is provided with a housing having an outlet oil passage communicating with the hydraulic oil chamber and a circumferential opening for constantly communicating with the outlet oil passage. An outer shaft that is formed in a cylindrical shape having a first valve hole that is elongated in the direction and is bored in the side wall, and that is fitted into the housing so as to be rotatable about an axis.
It is rotatably fitted in a cylindrical outer shaft having a second valve hole extending in a radial direction on a side wall at a position corresponding to the first valve hole so as to communicate with an oil pressure release passage formed inside. And an inner shaft that is linked and connected to the cam shaft.
（２） 作用 上記構成によれば、アウタシャフトを回動させることに
より、第１および第２弁孔が相互に連通するタイミング
をずらせることができ、それにより油圧解放弁の開弁時
期を調整することができる。しかもインナシャフトはカ
ムシャフトに連動、連結されるので、油圧解放弁の作動
を機関の回転数に対応させることができ機関の高回転に
も対応することができる。(2) Operation According to the above configuration, by rotating the outer shaft, it is possible to shift the timing at which the first and second valve holes communicate with each other, thereby adjusting the valve opening timing of the hydraulic pressure release valve. can do. Moreover, since the inner shaft is interlocked with and connected to the cam shaft, the operation of the hydraulic pressure release valve can be made to correspond to the rotation speed of the engine, and it is also possible to cope with the high rotation of the engine.
（３） 実施例 以下、図面により本発明の一実施例について説明する
と、先ず第１図および第２図において、図示しない機関
本体には弁ばね１により閉弁方向に付勢された一対の吸
気弁２が開閉作動すべく配設されており、これらの吸気
弁２の上方で回転自在に配設されたカムシャフト３には
各吸気弁２に対応する位置にカム４が固設される。カム
シャフト３には図示しないクランク軸が連動、連結され
ており、カムシャフト３は機関の回転に応じて1/2の減
速比で回転駆動される。(3) Embodiment Hereinafter, one embodiment of the present invention will be described with reference to the drawings. First, in FIGS. 1 and 2, a pair of intake air urged in a valve closing direction by a valve spring 1 is applied to an engine body (not shown). The valves 2 are arranged to open and close, and the cam shaft 3 rotatably arranged above the intake valves 2 is provided with the cams 4 at positions corresponding to the intake valves 2. A crank shaft (not shown) is interlocked and connected to the cam shaft 3, and the cam shaft 3 is rotationally driven at a speed reduction ratio of 1/2 according to the rotation of the engine.
カム４および吸気弁２間にはカム４のプロフィルに応じ
て吸気弁２を開閉駆動するための油圧駆動機構５がそれ
ぞれ介装され、吸気弁２を下方に押圧するための油圧駆
動機構５の押圧力を開弁作動途中で遮断するための油圧
解放弁６が油圧駆動機構５に接続される。A hydraulic drive mechanism 5 for driving the intake valve 2 to open and close according to the profile of the cam 4 is interposed between the cam 4 and the intake valve 2, and the hydraulic drive mechanism 5 for pressing the intake valve 2 downward. A hydraulic release valve 6 for shutting off the pressing force during the valve opening operation is connected to the hydraulic drive mechanism 5.
油圧駆動機構５は、機関本体に固設される支持部７に設
けられるものであり、吸気弁２の上方で上下に延びて支
持部７に嵌合、固定されるシリンダ体８と、吸気弁２の
上端に当接してシリンダ体８の下部に摺動可能に嵌合さ
れる弁側ピストン９と、カムシャフト３のカム４に摺接
するリフタ10と、該リフタ10に上端を当接させてシリン
ダ体８の上部に摺動可能に嵌合されるカム側ピストン11
とを備える。The hydraulic drive mechanism 5 is provided on a support portion 7 fixed to the engine body, and extends vertically above the intake valve 2 and is fitted and fixed to the support portion 7. The valve-side piston 9 that abuts on the upper end of 2 and is slidably fitted on the lower part of the cylinder body 8, the lifter 10 that slides on the cam 4 of the cam shaft 3, and the upper end abuts on the lifter 10. Cam-side piston 11 slidably fitted on the top of the cylinder body 8
With.
シリンダ体８の中間部には、該シリンダ体８内を上下に
仕切る仕切壁12が設けられており、弁側ピストン９は、
該仕切壁12との間にダンパ室13を画成してシリンダ体８
の下部に摺動可能に嵌合され、カム側ピストン11は前記
仕切壁12との間に作動油室14を画成してシリンダ体８の
上部に摺動可能に嵌合される。また仕切壁12の中央部に
はダンパ室13および作動油室14間を連通可能な連通孔15
が形成される。A partition wall 12 for partitioning the inside of the cylinder body 8 into upper and lower parts is provided in the middle portion of the cylinder body 8, and the valve side piston 9 is
A damper chamber 13 is defined between the partition wall 12 and the cylinder body 8
Is slidably fitted to the lower part of the cylinder side, and the cam side piston 11 is slidably fitted to the upper part of the cylinder body 8 by defining a hydraulic oil chamber 14 between the cam side piston 11 and the partition wall 12. A communication hole 15 is formed in the center of the partition wall 12 to allow communication between the damper chamber 13 and the hydraulic oil chamber 14.
Is formed.
弁側ピストン９内には、油室16が形成される。しかも弁
側ピストン９の上端中央部には、前記連通孔15に連通可
能な短円筒部17が油室16内に連通可能にして同軸に突設
されており、この短円筒部17と前記連通孔15とで絞り18
が構成される。すなわち短円筒部17の外径は、連通孔15
の内面との間に数十ないし数百μｍの間隔が生じるよう
に設定されており、これにより短円筒部17が連通孔15に
挿通されている状態では、該短円筒部17および連通孔15
間に微小の環状通路が形成され、この環状通路によりダ
ンパ室13から作動油室14への作動油の流通が制限され
る。しかも環状通路すなわち絞り18が形成されるのは、
短円筒部17が連通孔15に挿通されるときのみであり、短
円筒部17の軸方向長さは、吸気弁２の閉弁作動途中すな
わち弁側ピストン９が弁ばね１により上方に押上げられ
ている途中で連通孔15に挿通されるように設定される。An oil chamber 16 is formed in the valve side piston 9. Moreover, a short cylindrical portion 17 that can communicate with the communication hole 15 is coaxially projected at the center of the upper end of the valve-side piston 9 so that it can communicate with the oil chamber 16. Aperture 15 and aperture 18
Is configured. That is, the outer diameter of the short cylindrical portion 17 is equal to the communication hole 15
It is set so that a space of several tens to several hundreds of μm is formed between the short cylinder portion 17 and the communication hole 15 in a state where the short cylinder portion 17 is inserted into the communication hole 15.
A minute annular passage is formed between them, and this annular passage restricts the flow of the hydraulic oil from the damper chamber 13 to the hydraulic oil chamber 14. Moreover, the annular passage, that is, the throttle 18 is formed
It is only when the short cylindrical portion 17 is inserted into the communication hole 15, and the axial length of the short cylindrical portion 17 is upward during the closing operation of the intake valve 2, that is, the valve side piston 9 is pushed upward by the valve spring 1. It is set so as to be inserted into the communication hole 15 during the course.
弁側ピストン９の油室16内には、短円筒部17内の油圧が
油室16よりも一定値だけ高いときに開弁して作動油を短
円筒部17から油室16内に導く一方向弁19が収納され、ま
た弁側ピストン９には油室16をダンパ室13に連通する透
孔20が穿設される。このため短円筒部17が連通孔15に挿
通されている状態で作動油室14の油圧が高められたとき
に、該作動油室14の作動油は油室16からダンパ室13に導
かれる。The oil chamber 16 of the valve side piston 9 is opened when the hydraulic pressure in the short cylindrical portion 17 is higher than the oil chamber 16 by a certain value to guide the working oil from the short cylindrical portion 17 into the oil chamber 16. The directional valve 19 is housed, and the valve side piston 9 is provided with a through hole 20 for communicating the oil chamber 16 with the damper chamber 13. Therefore, when the hydraulic pressure in the hydraulic oil chamber 14 is increased while the short cylindrical portion 17 is inserted in the communication hole 15, the hydraulic oil in the hydraulic oil chamber 14 is guided from the oil chamber 16 to the damper chamber 13.
したがって上記絞り18は、短円筒部17が連通孔15よりも
下方にある状態、すなわち吸気弁２を押下げて開弁作動
しているとき、ならびに吸気弁２の全開状態から弁ばね
１により上方に押上げられて途中まで閉弁作動している
ときには、絞り作用を行なわず、閉弁作動の途中で短円
筒部17が連通孔15に挿通されて吸気弁２が全閉状態にな
るまでの間だけ絞り作用を行なうことになる。Therefore, the throttle 18 is moved upward by the valve spring 1 when the short cylindrical portion 17 is below the communication hole 15, that is, when the intake valve 2 is pushed down to perform the valve opening operation. When the valve is pushed up to the halfway and the valve is partially closed, the throttle action is not performed, and the short cylindrical portion 17 is inserted into the communication hole 15 during the valve closing operation until the intake valve 2 is fully closed. The squeezing action will be performed only for a while.
カム側ピストン11は、閉塞端を下方にした有底円筒状に
形成されており、このカム側ピストン11の上部開口端は
リフタ10に当接し得る閉塞部材21で閉塞される。またリ
フタ10は、その閉塞端外面をカム４に摺接させるように
して有底円筒状に形成されており、支持部７の上部に摺
動可能に嵌合される。The cam-side piston 11 is formed in a bottomed cylindrical shape with the closed end facing downward, and the upper open end of the cam-side piston 11 is closed by a closing member 21 capable of contacting the lifter 10. The lifter 10 is formed into a cylindrical shape with a bottom so that the outer surface of the lifter 10 is brought into sliding contact with the cam 4, and is slidably fitted on the upper portion of the support portion 7.
カム側ピストン11と閉塞部材21との間には、貯留室22が
形成されており、閉塞部材21には、貯留室22に貯留され
た作動油をリフタ10との摺接部に導く透孔23が穿設され
る。またカム側ピストン11の閉塞端には、作動油室14に
連通し得る油孔24が穿設されるとともに、貯留室22から
作動油室14側への作動油の流通のみを許容する逆止弁25
が配設される。A storage chamber 22 is formed between the cam side piston 11 and the closing member 21, and the closing member 21 has a through hole for guiding the working oil stored in the storage chamber 22 to a sliding contact portion with the lifter 10. 23 is drilled. Further, an oil hole 24 that can communicate with the hydraulic oil chamber 14 is formed at the closed end of the cam side piston 11, and a check valve that allows only the hydraulic oil to flow from the storage chamber 22 to the hydraulic oil chamber 14 side. Valve 25
Is provided.
シリンダ体８には作動油室14に連通する入口孔26が穿設
されており、この入口孔26に連通する入口油路27が支持
部７に穿設される。しかもこの入口油路27は、作動油室
14側からの作動油の流通を阻止する逆止弁25を介して油
圧供給源29に接続される。この油圧供給源29は、油タン
ク30から作動油を汲上げる油圧ポンプ31と、その油圧ポ
ンプ31から吐出される作動油を貯留するリザーブチャン
バ32とを備えるものであり、前記入口油路27は逆止弁28
を介してリザーブチャンバ32に接続される。An inlet hole 26 communicating with the hydraulic oil chamber 14 is bored in the cylinder body 8, and an inlet oil passage 27 communicating with the inlet hole 26 is bored in the support portion 7. Moreover, this inlet oil passage 27 is a hydraulic oil chamber.
It is connected to a hydraulic pressure supply source 29 via a check valve 25 that blocks the flow of hydraulic oil from the 14th side. The hydraulic supply source 29 includes a hydraulic pump 31 that pumps hydraulic oil from an oil tank 30, and a reserve chamber 32 that stores hydraulic oil discharged from the hydraulic pump 31, and the inlet oil passage 27 is Check valve 28
Is connected to the reserve chamber 32 via.
シリンダ体８には作動油室14に連通する出口孔33が穿設
されており、この出口孔33は、支持部７に設けられた第
１出口油路34、油圧解放弁６、第２出口油路35、ならび
に逆止弁36を介して前記油圧供給源29のリザーブチャン
バ32に接続される。しかも逆止弁36は、リザーブチャン
バ32側からの作動油の流通を阻止する機能を有する。An outlet hole 33 communicating with the hydraulic oil chamber 14 is bored in the cylinder body 8, and the outlet hole 33 includes a first outlet oil passage 34, a hydraulic pressure release valve 6, and a second outlet provided in the support portion 7. It is connected to the reserve chamber 32 of the hydraulic pressure supply source 29 via an oil passage 35 and a check valve 36. Moreover, the check valve 36 has a function of blocking the flow of hydraulic oil from the reserve chamber 32 side.
このような油圧駆動機構５では、吸気弁２の全閉状態で
は第１図示の状態にあり、この第１図の状態からカムシ
ャフト３の回転によりリフタ10が押下げられる。このリ
フタ10によりカム側ピストン11が下方に押圧駆動され、
作動油室14の容積が縮小せしめられ、油圧解放弁６が閉
弁している状態では、作動油室14内の作動油が一方向弁
19を経てダンパ室13に導入される。これにより弁側ピス
トン９が下方に押圧駆動され、吸気弁２が弁ばね１のば
ね力に抗して開弁駆動される。In such a hydraulic drive mechanism 5, the intake valve 2 is in the fully closed state as shown in the first illustration, and the lifter 10 is pushed down by the rotation of the camshaft 3 from this first illustration. The cam side piston 11 is pressed downward by this lifter 10,
When the volume of the hydraulic oil chamber 14 is reduced and the hydraulic pressure release valve 6 is closed, the hydraulic oil in the hydraulic oil chamber 14 is a one-way valve.
It is introduced into the damper chamber 13 via 19. As a result, the valve side piston 9 is pressed downward, and the intake valve 2 is driven to open against the spring force of the valve spring 1.
吸気弁２が全開状態になった後に、カム４によるリフタ
10への押圧力が解除されると、吸気弁２は弁ばね１のば
ね力により上方すなわち閉弁方向に駆動される。この吸
気弁２の閉弁作動により弁側ピストン９も上方に押上げ
られ、ダンパ室13の作動油は連通孔15を経て作動油室14
に戻されるが、その閉弁作動途中で短円筒部17が連通孔
15に挿通されてからは、絞り18による絞り作用が開始さ
れ、ダンパ室13から作動油室14への作動油の流れが制限
される。このため、吸気弁２の上方への移動速度すなわ
ち閉弁速度がその閉弁作動途中から緩められ、吸気弁２
は緩やかに閉弁することになる。したがって着座時の衝
撃が緩和され、吸気弁２および図示しない弁座部材等の
損傷を極力防止することができる。After the intake valve 2 is fully open, the cam 4 lifts the lifter.
When the pressing force on 10 is released, the intake valve 2 is driven upward by the spring force of the valve spring 1, that is, in the valve closing direction. The valve-side piston 9 is also pushed upward by the closing operation of the intake valve 2, and the hydraulic oil in the damper chamber 13 passes through the communication hole 15 and the hydraulic oil chamber 14
However, the short cylindrical part 17 has a communication hole during the valve closing operation.
After being inserted in 15, the throttle action by the throttle 18 is started, and the flow of the hydraulic oil from the damper chamber 13 to the hydraulic oil chamber 14 is restricted. Therefore, the moving speed of the intake valve 2 in the upward direction, that is, the valve closing speed is relaxed during the valve closing operation.
Will slowly close. Therefore, the impact at the time of seating is mitigated, and damage to the intake valve 2, the valve seat member (not shown), etc. can be prevented as much as possible.
油圧解放弁６は、ハウジングとしての支持部７と、第１
出口油路34に常時連通すべく周方向に長く延びて側壁に
穿設された第１弁孔37を有して円筒状に形成されるとと
もに前記支持部７に軸線まわりの回動を可能として嵌合
されるアウタシャフト38と、内部に形成された油圧解放
路39に通じるべく半径方向に延びる第２弁孔40を前記第
１弁孔37に対応する位置の側壁に有する円筒部41aを有
してアウタシャフト38内に回転自在に嵌合されるインナ
シャフト41とを備える。The hydraulic pressure release valve 6 includes a support portion 7 as a housing and a first support portion 7.
It is formed in a cylindrical shape having a first valve hole 37 which is long in the circumferential direction and is bored in the side wall so as to be constantly in communication with the outlet oil passage 34, and enables the support portion 7 to rotate about the axis. An outer shaft 38 to be fitted and a cylindrical portion 41a having a second valve hole 40 extending in the radial direction so as to communicate with a hydraulic pressure release passage 39 formed inside are provided on a side wall at a position corresponding to the first valve hole 37. And an inner shaft 41 that is rotatably fitted in the outer shaft 38.
支持部７には、油圧駆動機構５におけるシリンダ体８の
軸線と直交する方向に延びる支持孔42が穿設されてお
り、この支持孔42の内面には軸方向に間隔をあけた位置
に一対の凹部43が設けられる。これらの凹部43は支持孔
42の周方向に長く円弧状に形成されるものであり、一対
の油圧駆動機構５における作動油室14にそれぞれ連通す
る一対の第１出口油路34が各凹部43にそれぞれ連通され
る。支持孔42には、アウタシャフト38が軸線まわりに回
動自在に嵌合されており、軸方向に沿う前記凹部43の両
側をシールすべく支持孔42の内面およびアウタシャフト
38間には３つのシール部材44,45,46が介装される。また
支持孔42の内面には、第２出口油路35に連通する環状溝
47が前記凹部43とは軸方向にずれた位置に穿設される。The support portion 7 is provided with a support hole 42 extending in a direction orthogonal to the axis of the cylinder body 8 of the hydraulic drive mechanism 5, and a pair of support holes 42 are formed on the inner surface of the support hole 42 at positions axially spaced from each other. A recess 43 is provided. These recesses 43 are support holes
A pair of first outlet oil passages 34, which are formed in an arc shape long in the circumferential direction of 42 and communicate with the hydraulic oil chambers 14 of the pair of hydraulic drive mechanisms 5, respectively communicate with the respective recesses 43. An outer shaft 38 is fitted in the support hole 42 so as to be rotatable about its axis, and the inner surface of the support hole 42 and the outer shaft 42 are sealed to seal both sides of the recess 43 along the axial direction.
Three seal members 44, 45, 46 are interposed between the 38. In addition, an annular groove communicating with the second outlet oil passage 35 is formed on the inner surface of the support hole 42.
47 is formed at a position axially displaced from the recess 43.
アウタシャフト38には前記凹部43にそれぞれ対応する位
置に第１弁孔37がそれぞれ穿設され、これらの第１弁孔
37は、アウタシャフト38が軸線まわりに回動しても前記
凹部43に常時連通すべくアウタシャフト38の周方向に長
く形成される。またアウタシャフト38の外面には歯車48
が刻設されており、この歯車48に噛合するラック49がア
ウタシャフト38の軸線とは直角な方向に移動自在にして
支持部７に支承され、該ラック49は図示しない駆動手段
に連結される。したがってラック49をその長手方向に駆
動することによりアウタシャフト38が軸線まわりに角変
位する。さらにアウタシャフト38には前記環状溝47に常
時連通する油孔50が穿設される。First valve holes 37 are formed in the outer shaft 38 at positions corresponding to the recesses 43, respectively.
37 is formed to be long in the circumferential direction of the outer shaft 38 so as to always communicate with the recess 43 even when the outer shaft 38 rotates about its axis. The outer shaft 38 also has a gear 48 on the outer surface.
A rack 49 meshing with the gear 48 is movably supported in a direction perpendicular to the axis of the outer shaft 38 and supported by the support portion 7, and the rack 49 is connected to a driving means (not shown). . Therefore, by driving the rack 49 in its longitudinal direction, the outer shaft 38 is angularly displaced about the axis. Further, the outer shaft 38 is provided with an oil hole 50 which is in constant communication with the annular groove 47.
インナシャフト41の一端側には円筒部41aが形成されて
おり、この円筒部41aがアウタシャフト38内に回転自在
に嵌合される。しかも円筒部41a内にはインナシャフト4
1の端部に嵌合されたキャップ51で閉塞されて油圧解放
路39が形成され、この油圧解放路39に通じる第２弁孔40
が前記第１弁孔37に対応する位置で半径方向に延びてそ
れぞれ穿設される。しかも円筒部41aの外面には前記油
孔50に通じる環状溝52が設けられ、この環状溝52および
油圧解放路39間に油路53で連通される。したがって油圧
解放路39は第２出口油路35に常時連通することになる。
またインナシャフト41およびアウタシャフト38間には第
１および第２弁孔37,40の接続部をシールすべく３つの
シール部材54,55,56が介装される。A cylindrical portion 41a is formed on one end side of the inner shaft 41, and the cylindrical portion 41a is rotatably fitted in the outer shaft 38. Moreover, the inner shaft 4 is provided in the cylindrical portion 41a.
The hydraulic pressure release passage 39 is formed by being closed by the cap 51 fitted to the end portion of the first valve hole 40, and the second valve hole 40 communicating with the hydraulic pressure release passage 39 is formed.
Are radially extended at positions corresponding to the first valve holes 37. Moreover, an annular groove 52 communicating with the oil hole 50 is provided on the outer surface of the cylindrical portion 41a, and an oil passage 53 is connected between the annular groove 52 and the hydraulic pressure release passage 39. Therefore, the hydraulic pressure release passage 39 always communicates with the second outlet oil passage 35.
Further, three seal members 54, 55, 56 are interposed between the inner shaft 41 and the outer shaft 38 to seal the connecting portions of the first and second valve holes 37, 40.
インナシャフト41は、支持部７に回転自在に支承された
被動軸57に図示しない継手を介して同軸に連結されてお
り、この被動軸57にセラシ機構を有して設けられた被動
ギヤ58に、カムシャフト３に固設された駆動ギヤ59が噛
合される。The inner shaft 41 is coaxially connected to a driven shaft 57 rotatably supported by the support portion 7 via a joint (not shown), and a driven gear 58 provided with a serrated mechanism on the driven shaft 57. The drive gear 59 fixed to the camshaft 3 is meshed.
したがってインナシャフト41はカムシャフト３に連動、
連結されることになる。Therefore, the inner shaft 41 is interlocked with the cam shaft 3,
Will be connected.
かかる油圧解放弁６においては、インナシャフト41がカ
ムシャフト３の回転に応じて回転することにより第１お
よび第２弁孔37,40が相互に連通して開弁するが、その
開弁タイミングは、アウタシャフト38をラック49で角変
位することにより変化する。In the hydraulic pressure release valve 6, the inner shaft 41 rotates in response to the rotation of the cam shaft 3 so that the first and second valve holes 37 and 40 communicate with each other to open the valve. , The outer shaft 38 is angularly displaced by the rack 49.
次にこの実施例の作用について説明すると、油圧駆動機
構５において、カム側ピストン11がカム４により下方に
押圧駆動され、吸気弁２を開弁駆動している途中で、油
圧解放弁６が開弁作動すると、作動油室14およびダンパ
室13の油圧がリザーブチャンバ32に逃がされるので、弁
側ピストン９にかかっていた下向きの力が解消し、弁側
ピストン９および吸気弁２は弁ばね１のばね力により上
方に反転駆動され、閉弁作動し始める。すなわち吸気弁
２が全開状態に至らないうちに吸気弁２は閉弁作動し始
める。したがって油圧解放弁６の開弁時期を選択するこ
とにより、第３図で示すように、吸気弁２の閉弁時期を
自在にかつ容易に設定することが可能となる。Next, the operation of this embodiment will be described. In the hydraulic drive mechanism 5, the cam side piston 11 is pressed downward by the cam 4 to open the hydraulic release valve 6 while the intake valve 2 is being opened. When the valve is actuated, the hydraulic pressures of the hydraulic oil chamber 14 and the damper chamber 13 are released to the reserve chamber 32, so that the downward force applied to the valve side piston 9 is canceled, and the valve side piston 9 and the intake valve 2 have the valve spring 1 The valve is driven upward by the spring force of and the valve closing operation starts. That is, the intake valve 2 starts to close before the intake valve 2 reaches the fully open state. Therefore, by selecting the opening timing of the hydraulic pressure release valve 6, it becomes possible to freely and easily set the closing timing of the intake valve 2 as shown in FIG.
しかも油圧解放弁６の開弁時期は、ラック49によりアウ
タシャフト38を角変位することにより任意に設定可能で
あり、したがって吸気弁２の閉弁時期すなわちリフト量
も任意に設定可能である。また油圧解放弁６のインナシ
ャフト41は、カムシャフト３に連動、連結されるので、
油圧解放弁６の作動速度は機関の運転状態に対応するこ
とになり、したがって機関が高回転になっても充分に対
応することができる。Moreover, the opening timing of the hydraulic pressure release valve 6 can be arbitrarily set by angularly displacing the outer shaft 38 by the rack 49, and therefore, the closing timing of the intake valve 2, that is, the lift amount can also be arbitrarily set. Further, since the inner shaft 41 of the hydraulic pressure release valve 6 is interlocked with and connected to the camshaft 3,
The operating speed of the hydraulic pressure release valve 6 corresponds to the operating state of the engine, and therefore can sufficiently correspond to the high engine speed.
以上の実施例では、吸気弁２の動弁装置について述べた
が、本発明は、排気弁の動弁装置について実施し得るの
は言うまでもない。Although the valve operating device for the intake valve 2 has been described in the above embodiment, it goes without saying that the present invention can be implemented for the valve operating device for the exhaust valve.
C.発明の効果 以上のように本発明によれば、油圧解放弁は、作動油室
に連通する出口油路を有するハウジングと、出口油路に
常時連通すべく周方向に長く延びて側壁に穿設された第
１弁孔を有して円筒状に形成されるとともに前記ハウジ
ングに軸線まわりの回動を可能として嵌合されるアウタ
シャフトと、内部に形成された油圧解放路に通じるべく
半径方向に延びる第２弁孔を前記第１弁孔に対応する位
置の側壁に有する円筒状に形成されてアウタシャフト内
に回転自在に嵌合されるとともにカムシャフトに連動、
連結されるインナシャフトとを備えるので、油圧解放弁
の作動速度を機関の運転状態に対応させることができ、
機関が高回転になっても充分に対応することができる。C. Effects of the Invention As described above, according to the present invention, the hydraulic pressure release valve is provided with a housing having an outlet oil passage communicating with the hydraulic oil chamber and a circumferentially long side wall so as to always communicate with the outlet oil passage. An outer shaft that is formed in a cylindrical shape with a first valve hole that is bored and that is fitted into the housing so that it can rotate about an axis, and a radius that leads to a hydraulic pressure release path that is formed inside. Is formed in a cylindrical shape having a second valve hole extending in the direction on the side wall at a position corresponding to the first valve hole, is rotatably fitted in the outer shaft, and is interlocked with the cam shaft,
With the inner shaft connected, the operating speed of the hydraulic release valve can be made to correspond to the operating state of the engine.
Even if the engine has a high rotation speed, it can respond sufficiently.
図面は本発明の一実施例を示すもので、第１図は全体構
成を示す縦断側面図であって第２図のＩ−Ｉ線に沿う断
面図、第２図は第１図のII−II線拡大断面図、第３図は
特性線図である。 ２……吸気弁、３……カムシャフト、４……カム、５…
…油圧駆動機構、６……油圧解放弁、７……ハウジング
としての支持部、９……弁側ピストン、11……カム側ピ
ストン、34,35……出口油路、37……第１弁孔、38……
アウタシャフト、39……油圧解放路、40……第２弁孔、
41……インナシャフトThe drawings show one embodiment of the present invention. FIG. 1 is a vertical cross-sectional side view showing the overall structure and is a cross-sectional view taken along the line II of FIG. 2, and FIG. 2 is II- of FIG. II line enlarged sectional view, FIG. 3 is a characteristic diagram. 2 ... intake valve, 3 ... cam shaft, 4 ... cam, 5 ...
... Hydraulic drive mechanism, 6 ... Hydraulic release valve, 7 ... Housing support, 9 ... Valve side piston, 11 ... Cam side piston, 34,35 ... Outlet oil passage, 37 ... First valve Hole, 38 ……
Outer shaft, 39 ... hydraulic release path, 40 ... second valve hole,
41 …… Inner shaft
Claims (1)
に設けられたカムと、閉弁方向にばね付勢された吸気弁
あるいは排気弁との間に、一端がカムに連動、連結され
たカム側ピストンの他端に臨む作動油室の油圧増大に応
じて吸気弁あるいは排気弁を開弁作動すべく弁側ピスト
ンが吸気弁あるいは排気弁に連動、連結されて成る油圧
駆動機構が介装され、開弁作動時に油圧を解放すべく該
作動油室には油圧解放弁が接続される内燃機関の動弁装
置において、油圧解放弁は、作動油室に連通する出口油
路を有するハウジングと、出口油路に常時連通すべく周
方向に長く延びて側壁に穿設された第１弁孔を有して円
筒状に形成されるとともに前記ハウジングに軸線まわり
の回動を可能として嵌合されるアウタシャフトと、内部
に形成された油圧解放路に通じるべく半径方向に延びる
第２弁孔を前記第１弁孔に対応する位置の側壁に有する
円筒状に形成されてアウタシャフト内に回転自在に嵌合
されるとともにカムシャフトに連動、連結されるインナ
シャフトとを備えることを特徴とする内燃機関の動弁装
置。1. A cam side in which one end is interlocked with and connected to a cam provided on a cam shaft driven by a crankshaft and an intake valve or an exhaust valve which is spring-biased in a valve closing direction. A hydraulic drive mechanism, in which a valve side piston is linked and linked to an intake valve or an exhaust valve to open the intake valve or the exhaust valve in response to an increase in the hydraulic pressure of the hydraulic oil chamber facing the other end of the piston, is interposed. In a valve operating system of an internal combustion engine, wherein a hydraulic pressure release valve is connected to the hydraulic oil chamber to release the hydraulic pressure when the valve is opened, the hydraulic pressure release valve includes a housing having an outlet oil passage communicating with the hydraulic oil chamber, and an outlet. An outer that is formed in a cylindrical shape and has a first valve hole that is long in the circumferential direction and is bored in the side wall so as to be in continuous communication with the oil passage, and that is fitted into the housing so as to be rotatable about its axis. Shaft and hydraulic pressure formed inside A second valve hole extending in the radial direction to communicate with the discharge passage is formed in a cylindrical shape on a side wall at a position corresponding to the first valve hole, rotatably fitted in the outer shaft, and interlocked with the cam shaft, A valve train for an internal combustion engine, comprising: an inner shaft connected to the inner shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62292618A JPH079168B2 (en) | 1987-11-19 | 1987-11-19 | Valve drive for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62292618A JPH079168B2 (en) | 1987-11-19 | 1987-11-19 | Valve drive for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01134014A JPH01134014A (en) | 1989-05-26 |
| JPH079168B2 true JPH079168B2 (en) | 1995-02-01 |
Family
ID=17784132
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62292618A Expired - Fee Related JPH079168B2 (en) | 1987-11-19 | 1987-11-19 | Valve drive for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH079168B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20120017982A (en) * | 2010-08-20 | 2012-02-29 | 현대자동차주식회사 | Electro-hydraulic variable vavlve lift apparatus |
| EP3023607B1 (en) * | 2013-07-15 | 2017-06-21 | Shan Dong University | Oil control device for fully variable hydraulic valve system of internal combustion engine |
-
1987
- 1987-11-19 JP JP62292618A patent/JPH079168B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01134014A (en) | 1989-05-26 |
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| LAPS | Cancellation because of no payment of annual fees |