JPH04292506A - Hydraulic drive device for engine valve for internal combustion engine - Google Patents
Hydraulic drive device for engine valve for internal combustion engineInfo
- Publication number
- JPH04292506A JPH04292506A JP3057202A JP5720291A JPH04292506A JP H04292506 A JPH04292506 A JP H04292506A JP 3057202 A JP3057202 A JP 3057202A JP 5720291 A JP5720291 A JP 5720291A JP H04292506 A JPH04292506 A JP H04292506A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- hydraulic
- viscosity
- engine
- electromagnetic
- 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.)
- Pending
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 7
- 239000010720 hydraulic oil Substances 0.000 claims description 64
- 230000004044 response Effects 0.000 abstract description 16
- 239000003921 oil Substances 0.000 description 13
- 238000010586 diagram Methods 0.000 description 8
- 239000012530 fluid Substances 0.000 description 8
- 230000007423 decrease Effects 0.000 description 7
- 230000005284 excitation Effects 0.000 description 3
- 230000004323 axial length Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000005347 demagnetization Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Valve Device For Special Equipments (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
Description
【０００１】0001
【産業上の利用分野】本発明は、固定の支持部に固定さ
れるシリンダ体に、該シリンダ体との間に形成される油
圧室に背面を臨ませるとともに前端を機関弁の後端に当
接させる弁駆動ピストンが摺動可能に嵌合され、前記油
圧室には、機関弁の開弁時期に対応して油圧を発生する
油圧発生手段と、開弁時に前記作動油圧室の油圧を解放
可能な電磁開閉弁とが接続され、機関の要求に応じて機
関弁の開閉作動特性を変更すべく電磁開閉弁の開閉作動
を制御する制御手段が電磁開閉弁に接続される内燃機関
用機関弁の油圧駆動装置に関する。[Industrial Application Field] The present invention provides a cylinder body that is fixed to a fixed support part, the back side of which faces a hydraulic chamber formed between the cylinder body, and the front end of which is brought into contact with the rear end of an engine valve. A valve drive piston is slidably fitted in the hydraulic chamber, and the hydraulic chamber includes a hydraulic pressure generating means for generating hydraulic pressure corresponding to the opening timing of the engine valve, and a hydraulic pressure generating means for releasing the hydraulic pressure in the operating hydraulic chamber when the valve is opened. An engine valve for an internal combustion engine, in which a control means for controlling the opening/closing operation of the electromagnetic opening/closing valve is connected to the electromagnetic opening/closing valve in order to change the opening/closing operation characteristics of the engine valve in accordance with the requests of the engine. The present invention relates to a hydraulic drive device.
【０００２】0002
【従来の技術】従来、かかる装置は、たとえば特開昭６
１−２７５５１６号公報等により公知である。[Prior Art] Conventionally, such a device has been used, for example, in Japanese Patent Application Laid-open No. 6
It is publicly known from Publication No. 1-275516 and the like.
【０００３】0003
【発明が解決しようとする課題】ところで、作動油の粘
度はその温度が低くなるのに応じて大となるものであり
、電磁開閉弁内の作動部では、粘度が高くなると作動油
の抵抗が増大し、また粘度が低くなると作動油の抵抗が
減少する。しかるに上記従来のものでは、電磁開閉弁を
駆動する電力を作動油粘度すなわち温度にかかわらず一
定としており、このため、作動油粘度が高いときには電
磁開閉弁の応答性が低下し、作動油粘度が低いときには
電磁開閉弁の応答性が著しく増加して作動部の衝突によ
る作動音が発生する。[Problems to be Solved by the Invention] By the way, the viscosity of hydraulic oil increases as its temperature decreases, and in the operating part of an electromagnetic on-off valve, as the viscosity increases, the resistance of the hydraulic oil increases. As the viscosity increases and the viscosity decreases, the resistance of the hydraulic fluid decreases. However, in the above conventional system, the electric power that drives the electromagnetic on-off valve is constant regardless of the viscosity of the hydraulic oil, that is, the temperature. Therefore, when the viscosity of the hydraulic oil is high, the response of the electromagnetic on-off valve decreases, and the viscosity of the hydraulic oil decreases. When it is low, the responsiveness of the electromagnetic on-off valve increases significantly and an operating noise is generated due to collision of the operating parts.
【０００４】本発明は、かかる事情に鑑みてなされたも
のであり、電磁開閉弁の作動特性を作動油粘度に適合し
たものとし、作動油高粘度時の作動レスポンス改善なら
びに作動油低粘度時の作動音低減を図るようにした内燃
機関用機関弁の油圧駆動装置を提供することを目的とす
る。The present invention has been made in view of the above circumstances, and is designed to adapt the operating characteristics of an electromagnetic on-off valve to the viscosity of the hydraulic oil, thereby improving the operational response when the hydraulic oil is highly viscous and improving the operational response when the hydraulic oil is low in viscosity. An object of the present invention is to provide a hydraulic drive device for an engine valve for an internal combustion engine, which is designed to reduce operating noise.
【０００５】[0005]
【課題を解決するための手段】上記目的を達成するため
に、本発明によれば、作動油の粘度を代表する指標を検
出する検出器が制御手段に接続され、該制御手段は、電
磁開閉弁の駆動電力を作動油の粘度が大であるときに大
とするように段階的または連続的に変化すべく構成され
る。[Means for Solving the Problems] In order to achieve the above object, according to the present invention, a detector for detecting an index representative of the viscosity of hydraulic oil is connected to a control means, and the control means is configured to control electromagnetic switching. The valve driving power is configured to be changed stepwise or continuously so that the driving power of the valve is increased when the viscosity of the hydraulic oil is high.
【０００６】[0006]
【実施例】以下、図面により本発明の実施例について説
明する。Embodiments Hereinafter, embodiments of the present invention will be explained with reference to the drawings.
【０００７】図１ないし図７は本発明の一実施例を示す
ものであり、図１は油圧駆動装置の縦断面図、図２は電
磁開閉弁の拡大縦断面図、図３は作動油粘度の高、低に
応じて定められたデューティ比を示す図、図４は作動油
粘度の高、低に応じた電磁吸引力の従来との対比図、図
５は作動油粘度の高、低に応じた作動レスポンスの従来
との対比図、図６は作動油粘度の高、低に応じた作動レ
スポンスの変化を示すグラフ、図７は作動油粘度の高、
低に応じた作動音レベルの従来との対比図である。1 to 7 show an embodiment of the present invention, in which FIG. 1 is a vertical sectional view of a hydraulic drive device, FIG. 2 is an enlarged vertical sectional view of an electromagnetic on-off valve, and FIG. 3 is a diagram showing the viscosity of hydraulic oil. Fig. 4 is a comparison diagram with the conventional electromagnetic attraction force depending on the high and low viscosity of the hydraulic oil. Fig. 5 is a diagram showing the duty ratio determined depending on the high and low viscosity of the hydraulic oil. Fig. 6 is a graph showing changes in actuation response depending on high and low hydraulic oil viscosity, and Fig. 7 is a graph showing changes in operational response according to high and low hydraulic oil viscosity.
FIG. 3 is a comparison diagram of the operating sound level according to the low level and the conventional level.
【０００８】先ず図１において、内燃機関におけるシリ
ンダヘッドＨＣ には機関弁としての吸気弁Ｖが弁ばね
１１により閉弁方向に付勢されながら開閉作動可能にそ
れぞれ配設されており、各吸気弁Ｖを開閉駆動するため
の油圧駆動装置ＵがシリンダヘッドＨＣ に配設される
。First, in FIG. 1, intake valves V as engine valves are disposed in a cylinder head HC of an internal combustion engine so as to be able to open and close while being biased in the valve closing direction by a valve spring 11. A hydraulic drive device U for opening and closing V is disposed in the cylinder head HC.
【０００９】油圧駆動装置Ｕは、シリンダヘッドＨＣ
に結合される支持部としての支持ブロック１２に、吸気
弁Ｖに連動、連結される弁駆動ピストン１３と、カムシ
ャフトＳに設けられたカム２２によって駆動されて吸気
弁Ｖの開弁時期に対応して油圧を発生可能な油圧発生手
段８と、機関の要求に応じて吸気弁Ｖの開閉作動特性を
変更すべく油圧発生手段８の発生油圧を解放可能な電磁
開閉弁１５とが設けられて成るものである。[0009] The hydraulic drive device U has a cylinder head HC.
A support block 12 serving as a support unit coupled to the intake valve V is driven by a valve drive piston 13 that is interlocked and connected to the intake valve V, and a cam 22 provided on the camshaft S to correspond to the opening timing of the intake valve V. A hydraulic pressure generating means 8 capable of generating hydraulic pressure according to the request of the engine, and an electromagnetic opening/closing valve 15 capable of releasing the hydraulic pressure generated by the hydraulic pressure generating means 8 in order to change the opening/closing operation characteristics of the intake valve V according to the request of the engine are provided. It is what it is.
【００１０】支持ブロック１２には、吸気弁Ｖと同軸に
して第１シリンダ体１６が固定されており、第１シリン
ダ体１６には、吸気弁Ｖの上端に当接する弁駆動ピスト
ン１３が摺動自在に嵌合され、該弁駆動ピストン１３と
シリンダ体１６との間には弁駆動ピストン１３の背面を
臨ませるようにして油圧室１７が形成される。A first cylinder body 16 is fixed to the support block 12 coaxially with the intake valve V, and a valve driving piston 13 that abuts the upper end of the intake valve V slides on the first cylinder body 16. A hydraulic chamber 17 is formed between the valve drive piston 13 and the cylinder body 16 so that the back surface of the valve drive piston 13 is exposed.
【００１１】油圧発生手段８は、カム２２の上方で支持
ブロック１２に固定される第２シリンダ体１８と、カム
２２に摺接するとともに第２シリンダ体１８と同軸上で
支持ブロック１２に摺動自在に嵌合される有底円筒状の
リフタ１９と、該リフタ１９に下端を当接させるととも
に第２シリンダ体１８との間に油圧発生室２０を画成し
て第２シリンダ体１８に摺動自在に嵌合されるカム従動
ピストン１４とを備える。The hydraulic pressure generating means 8 includes a second cylinder body 18 fixed to the support block 12 above the cam 22, and a second cylinder body 18 that is in sliding contact with the cam 22 and is slidable on the support block 12 coaxially with the second cylinder body 18. A hydraulic pressure generation chamber 20 is defined between a bottomed cylindrical lifter 19 that is fitted into the lifter 19 and the second cylinder body 18 with its lower end abutting the lifter 19, and the lifter 19 is slid onto the second cylinder body 18. It includes a cam driven piston 14 that is freely fitted.
【００１２】油圧室１７および油圧発生室２０は、吸気
弁Ｖすなわち弁駆動ピストン１３がその全閉位置から所
定量だけ開弁方向に作動したときに連通するものであり
、しかも弁駆動ピストン１３には、油圧発生室２０から
油圧室１７への作動油の流通のみを許容するチェック弁
２１が設けられ、油圧室１７および油圧発生室２０間に
は絞り機構が配設される。The hydraulic pressure chamber 17 and the hydraulic pressure generation chamber 20 communicate with each other when the intake valve V, that is, the valve driving piston 13, moves in the valve opening direction by a predetermined amount from its fully closed position. A check valve 21 is provided that only allows flow of hydraulic oil from the oil pressure generation chamber 20 to the oil pressure chamber 17, and a throttle mechanism is provided between the oil pressure chamber 17 and the oil pressure generation chamber 20.
【００１３】ところで、油圧発生室２０および油圧室１
７間は、吸気弁Ｖが全閉位置から所定量だけリフトした
状態から全開状態までの間では連通状態にあり、また吸
気弁Ｖが全閉位置から所定量だけリフトするまでは油圧
発生室２０から油圧室１７への作動油の流通のみを許容
するチェック弁２１ならびに油圧室１７から油圧発生室
２０への作動油の戻り量を制限する絞り機構を介して連
通することになる。而して吸気弁Ｖの全閉状態では、油
圧駆動装置Ｕは図１で示す状態にあり、この図１の状態
からカムシャフトＳの回転に応じてカム２２によりリフ
タ１９が押上げられる。それによりカム従動ピストン１
４が上方に押圧駆動され、油圧発生室２０の容積が収縮
せしめられ、油圧発生室２０内の作動油はチェック弁２
１および絞り機構を介して油圧室１７に導入される。し
たがって油圧室１７の油圧が大となり、弁駆動ピスン１
３が下方に押下げられて吸気弁Ｖが弁ばね１１のばね力
に抗して開弁駆動される。また吸気弁Ｖが全開状態にな
った後に、カム２２によるリフタ１９への押圧力が解除
されると、吸気弁Ｖは弁ばね１１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Ｖの閉弁作動
により弁駆動ピストン１３も上方に押上げられ、油圧室
１７の作動油は油圧発生室２０に戻されるが、その閉弁
作途中で油圧室１７および油圧発生室２０間にチェック
弁２１および絞り機構が介在するようになってからは、
油圧室１７から油圧発生室２０への作動油の戻り量が制
限され、吸気弁Ｖの上方への移動速度すなわち閉弁速度
が閉弁作動途中から緩められて着座時の衝撃が緩和され
ることになる。By the way, the hydraulic pressure generation chamber 20 and the hydraulic pressure chamber 1
7, the intake valve V is in communication between the state where it has been lifted by a predetermined amount from the fully closed position and the state where it is fully open, and the hydraulic pressure generating chamber 20 is in communication until the intake valve V is lifted by a predetermined amount from the fully closed position. The hydraulic fluid is communicated through a check valve 21 that only allows flow of hydraulic fluid from the hydraulic chamber 17 to the hydraulic chamber 17, and a throttle mechanism that limits the amount of hydraulic fluid that returns from the hydraulic chamber 17 to the hydraulic pressure generation chamber 20. When the intake valve V is fully closed, the hydraulic drive device U is in the state shown in FIG. 1, and from this state shown in FIG. 1, the lifter 19 is pushed up by the cam 22 in accordance with the rotation of the camshaft S. As a result, the cam driven piston 1
4 is pushed upward, the volume of the oil pressure generation chamber 20 is contracted, and the hydraulic oil in the oil pressure generation chamber 20 is transferred to the check valve 2.
1 and a throttle mechanism into the hydraulic chamber 17. Therefore, the hydraulic pressure in the hydraulic chamber 17 becomes large, and the valve drive piston 1
3 is pushed down, and the intake valve V is driven to open against the spring force of the valve spring 11. Further, after the intake valve V is fully opened, when the pressing force on the lifter 19 by the cam 22 is released, the intake valve V is driven upward by the spring force of the valve spring 11, that is, in the valve closing direction. Due to this valve closing operation of the intake valve V, the valve driving piston 13 is also pushed upward, and the hydraulic oil in the hydraulic chamber 17 is returned to the hydraulic pressure generation chamber 20. Since the check valve 21 and throttle mechanism have been interposed in between,
The amount of hydraulic fluid that returns from the hydraulic chamber 17 to the hydraulic pressure generation chamber 20 is limited, and the upward movement speed of the intake valve V, that is, the valve closing speed, is slowed in the middle of the valve closing operation, so that the impact when seating is alleviated. become.
【００１４】また支持ブロック１２には、吸気弁Ｖが完
全に閉弁した状態で吸気弁Ｖの上端を検出するリフトセ
ンサ２３が配設される。A lift sensor 23 is also disposed on the support block 12 to detect the upper end of the intake valve V when the intake valve V is completely closed.
【００１５】上記油圧室１７および油圧発生室２０の油
圧を、吸気弁Ｖの開弁作動途中で解放すると、油圧室１
７は弁ばね１１のばね力に打勝って吸気弁Ｖを開弁し続
けるだけの伝達機能を失うことになり、カム２２がリフ
タ１９を上方に押続けるにもかかわらず、吸気弁Ｖは前
記油圧解放時から弁ばね１１の弾発力により閉弁作動を
開始し、油圧室１７の容積は縮小する。When the hydraulic pressure in the hydraulic chamber 17 and the hydraulic pressure generation chamber 20 is released during the opening operation of the intake valve V, the hydraulic pressure in the hydraulic chamber 1
7 loses its transmission function to overcome the spring force of the valve spring 11 and keep the intake valve V open, and even though the cam 22 continues to push the lifter 19 upward, the intake valve V does not open as described above. When the hydraulic pressure is released, the valve starts to close due to the elastic force of the valve spring 11, and the volume of the hydraulic chamber 17 is reduced.
【００１６】電磁開閉弁１５は、上述の油圧室１７およ
び油圧発生室２０からの油圧の解放時期すなわち吸気弁
Ｖのリフト量および閉弁時期を制御する電磁弁であり、
油圧発生室２０に通じて支持ブロック１２に穿設された
通路１と、支持ブロック１２に配設されたアキュムレー
タ２４に連通しながら支持ブロック１２に穿設された通
路２との間に介設される。また前記両通路１，２間で電
磁開閉弁１５を迂回して支持ブロック１２に設けられた
迂回路７には一方向弁２５が配設されており、この一方
向弁２５は、第２通路２の油圧が第１通路１の油圧より
も設定圧以上大きくなったときに開弁してアキュムレー
タ２４から通路１すなわち油圧発生室２０に向けての作
動油の流通のみを許容するものである。またシリンダヘ
ッドＨＣ に設けられているオイルバス３から作動油を
汲み上げるオイルポンプ４は、フィルタ５を備える油路
６に接続されており、該油路６は、支持ブロック１２に
配設された逆止弁２６を介して通路２に接続される。而
して逆止弁２６はオイルポンプ４から通路２側に向けて
の作動油の流通のみを許容するものである。The electromagnetic on-off valve 15 is an electromagnetic valve that controls the release timing of the hydraulic pressure from the above-mentioned hydraulic chamber 17 and the hydraulic pressure generation chamber 20, that is, the lift amount and closing timing of the intake valve V.
A passageway 1 is interposed between a passageway 1 bored through the support block 12 and communicating with the hydraulic pressure generation chamber 20, and a passageway 2 bored through the support block 12 while communicating with an accumulator 24 disposed in the support block 12. Ru. Further, a one-way valve 25 is disposed in a detour 7 provided in the support block 12 by bypassing the electromagnetic on-off valve 15 between the two passages 1 and 2, and this one-way valve 25 is connected to the second passage. When the oil pressure in the first passage 1 becomes greater than the oil pressure in the first passage 1 by a set pressure or more, the valve opens and only allows the flow of hydraulic oil from the accumulator 24 toward the passage 1, that is, the oil pressure generation chamber 20. Further, an oil pump 4 that pumps up hydraulic oil from an oil bath 3 provided in the cylinder head HC is connected to an oil passage 6 provided with a filter 5. It is connected to the passage 2 via a stop valve 26. The check valve 26 only allows the hydraulic oil to flow from the oil pump 4 toward the passage 2 side.
【００１７】図２において、支持ブロック１２には、そ
の上部外面に開口する取付孔２７が電磁開閉弁１５を取
付けるべく穿設される。この取付孔２７は、その軸方向
に沿う内方側から順に小径孔部２８と、小径孔部２８よ
りも大径の大径孔部２９と、大径孔部２９よりも大径で
あるねじ孔部３０とが同軸に連設されて成り、通路１は
小径孔部２８に同軸に連設される。小径孔部２８には、
小径孔部２８および大径孔部２９間の段差面と面一にし
てフィルタ４０が嵌合される。また通路２は、大径孔部
２９における小径孔部２８寄りの側面に開口される。In FIG. 2, the support block 12 is provided with a mounting hole 27 opening on the outer surface of its upper part for mounting the electromagnetic on-off valve 15 therein. This mounting hole 27 has, in order from the inside along the axial direction, a small diameter hole 28, a large diameter hole 29 larger than the small diameter hole 28, and a screw thread larger in diameter than the large diameter hole 29. The passage 1 is coaxially connected to the small diameter hole 28. In the small diameter hole 28,
The filter 40 is fitted flush with the step surface between the small diameter hole 28 and the large diameter hole 29. Further, the passage 2 is opened on the side surface of the large diameter hole 29 closer to the small diameter hole 28 .
【００１８】一方、電磁開閉弁１５のハウジング３１は
、ハウジング主体３２の前端に弁ハウジング部３３が設
けられるとともにハウジング主体３２の後端に固定コア
３４が取付けられて成る。而してハウジング主体３２は
、ねじ孔部３０よりも小径である外筒部３５と、該外筒
部３５内に同軸に配置される内筒部３６と、外筒部３５
および内筒部３６の一端を連結する連結板部３７と、ね
じ孔部３０の内径よりもわずかに小さな外径を有して外
筒部３５の一端から半径方向外方に張出される鍔部３８
と、大径孔２９に嵌合する外径を有して外筒部３５およ
び内筒部３６とは反対側に延びながら連結板部３７に同
軸に連設される連結筒部３９とを有する。しかも内筒部
３６の連結板部３７からの軸方向長さは外筒部３５の連
結板部３７からの軸方向長さよりも小さく設定される。On the other hand, the housing 31 of the electromagnetic on-off valve 15 includes a valve housing portion 33 provided at the front end of a housing main body 32, and a fixed core 34 attached to the rear end of the housing main body 32. The housing main body 32 includes an outer cylinder part 35 having a smaller diameter than the screw hole part 30, an inner cylinder part 36 disposed coaxially within the outer cylinder part 35, and an outer cylinder part 35.
and a connecting plate portion 37 that connects one end of the inner cylindrical portion 36, and a collar portion that has an outer diameter slightly smaller than the inner diameter of the screw hole portion 30 and extends radially outward from one end of the outer cylindrical portion 35. 38
and a connecting cylinder part 39 that has an outer diameter that fits into the large diameter hole 29 and is coaxially connected to the connecting plate part 37 while extending on the opposite side from the outer cylinder part 35 and the inner cylinder part 36. . Moreover, the axial length of the inner cylinder part 36 from the connecting plate part 37 is set smaller than the axial length of the outer cylinder part 35 from the connecting plate part 37.
【００１９】弁ハウジング部３３は、外ガイド筒４１と
該外ガイド筒４１内に同軸に配置される内ガイド筒４２
とから成り、連結板部３７に内ガイド筒４２を当接させ
るようにして外ガイド筒４１および内ガイド筒４２を連
結筒部３９に嵌合した状態で、該連結筒部３９の先端を
外ガイド筒４１にかしめ結合することにより、弁ハウジ
ング部３３が構成されるとともに該弁ハウジング部３３
がハウジング主体３３の前端に連設される。また固定コ
ア３４は外筒部３５の後端にかしめ結合される。The valve housing portion 33 includes an outer guide cylinder 41 and an inner guide cylinder 42 disposed coaxially within the outer guide cylinder 41.
With the outer guide cylinder 41 and the inner guide cylinder 42 fitted into the connecting cylinder part 39 with the inner guide cylinder 42 in contact with the connecting plate part 37, the tip of the connecting cylinder part 39 is removed. The valve housing part 33 is configured by being caulked to the guide cylinder 41, and the valve housing part 33
is connected to the front end of the housing main body 33. Further, the fixed core 34 is caulked to the rear end of the outer cylindrical portion 35.
【００２０】このような電磁開閉弁１５のハウジング３
１は、その弁ハウジング部３３をフィルタ４０に当接さ
せるまでハウジング主体３２の連結筒部３９を大径孔２
９に嵌合するようにして取付孔２７に挿入される。また
円筒状に形成されているカラー４４が取付孔２７のねじ
孔部３０に螺合され、該カラー４４を、その先端がハウ
ジング３１の鍔部３８に当接するまで締付けることによ
り、電磁開閉弁１５のハウジング３１がカラー４４およ
び支持ブロック１２間に挟持、固定されることになる。Housing 3 of such electromagnetic on-off valve 15
1, the connecting cylinder portion 39 of the housing main body 32 is inserted into the large diameter hole 2 until the valve housing portion 33 is brought into contact with the filter 40.
9 and is inserted into the mounting hole 27. Further, a cylindrical collar 44 is screwed into the screw hole 30 of the mounting hole 27, and by tightening the collar 44 until its tip abuts against the flange 38 of the housing 31, the electromagnetic on-off valve 15 The housing 31 is sandwiched and fixed between the collar 44 and the support block 12.
【００２１】弁ハウジング部３３における外ガイド筒４
１の一端にはフィルタ４０を介して通路１に同軸に通じ
る入口ポート４７が設けられ、該入口ポート４７近傍で
外ガイド筒４１の側壁には周方向に間隔をあけた複数の
出口ポート４８が穿設される。しかも支持ブロック１２
の取付孔２７における大径孔２９内面および外ガイド筒
４１間には各出口ポート４８および通路２に通じる環状
通路４９が形成され、ハウジング主体３２の連結筒部３
９外面には、環状通路４９と外部との間のシールを果た
すための環状のシール部材５０が嵌着される。Outer guide cylinder 4 in valve housing part 33
An inlet port 47 coaxially communicating with the passage 1 via a filter 40 is provided at one end of the outer guide cylinder 41, and a plurality of outlet ports 48 are provided at intervals in the circumferential direction on the side wall of the outer guide tube 41 near the inlet port 47. drilled. Moreover, the support block 12
An annular passage 49 communicating with each outlet port 48 and the passage 2 is formed between the inner surface of the large diameter hole 29 in the mounting hole 27 and the outer guide cylinder 41, and the connecting cylinder part 3 of the housing main body 32
An annular seal member 50 for sealing between the annular passage 49 and the outside is fitted onto the outer surface of the annular passage 9 .
【００２２】弁ハウジング部３３内には、有底円筒状に
形成される主弁体５１が、その外面を外ガイド筒４１内
面に摺接させるようにして嵌合されており、該主弁体５
１は、入口ポート４７の内端縁を囲むようにして外ガイ
ド筒４１に設けられるテーパ状の弁座５２に着座して入
口ポート４７および出口ポート４８間を遮断する位置と
、弁座５２から離反して入口ポート４７および出口ポー
ト４８間を連通する位置との間で移動可能である。A main valve body 51 formed in the shape of a cylinder with a bottom is fitted into the valve housing portion 33 so that its outer surface is in sliding contact with the inner surface of the outer guide cylinder 41. 5
1 is located at a position where it seats on a tapered valve seat 52 provided on the outer guide tube 41 so as to surround the inner edge of the inlet port 47 and blocks the connection between the inlet port 47 and the outlet port 48; and at a position where it is separated from the valve seat 52. and a position communicating between the inlet port 47 and the outlet port 48.
【００２３】主弁体５１の背面を臨ませるようにして弁
ハウジング部３３内には背圧室５３が形成されており、
該背圧室５３内には、主弁体５１を弁座５２に着座せし
める方向のばね力を発揮するばね５４が収納される。し
たがって主弁体５１には、入口ポート４７の流体圧が開
弁方向に作用し、背圧室５３の流体圧が閉弁方向に作用
し、ばね５３のばね力が閉弁方向に作用することになる
。しかも主弁体５１には、入口ポート４７および背圧室
５３間を連通する絞り５５が軸線からずれた位置に穿設
される。A back pressure chamber 53 is formed in the valve housing portion 33 so as to face the back side of the main valve body 51.
A spring 54 is housed in the back pressure chamber 53, which exerts a spring force in a direction to seat the main valve body 51 on the valve seat 52. Therefore, on the main valve body 51, the fluid pressure of the inlet port 47 acts in the valve opening direction, the fluid pressure in the back pressure chamber 53 acts in the valve closing direction, and the spring force of the spring 53 acts in the valve closing direction. become. Furthermore, a throttle 55 that communicates between the inlet port 47 and the back pressure chamber 53 is bored in the main valve body 51 at a position offset from the axis.
【００２４】弁ハウジング部３３における内ガイド筒４
２は、主弁体５１の開弁作動時に該主弁体５１に当接し
てストッパとしての機能を果たすものであり、主弁体５
１の背面に対向する内ガイド筒４２の先端部にはパイロ
ット弁孔５６が同軸に穿設される。また内ガイド筒４２
内にパイロット弁孔５６を閉鎖可能なパイロット弁体５
７が摺動自在に嵌合されており、該パイロット弁体５７
は、弁ハウジング部３３との間に介設したばね５８によ
り開弁方向すなわち後退方向に付勢される。しかもパイ
ロット弁体５７には、その開弁時にパイロット弁孔５６
に通じる連通路６０が同軸に穿設されており、該連通路
６０はパイロット弁体５７の後端で開口される。Inner guide cylinder 4 in valve housing portion 33
2 serves as a stopper by coming into contact with the main valve body 51 when the main valve body 51 is opened.
A pilot valve hole 56 is coaxially formed at the tip of the inner guide cylinder 42 facing the back surface of the inner guide cylinder 42 . In addition, the inner guide tube 42
A pilot valve body 5 in which a pilot valve hole 56 can be closed
7 is slidably fitted, and the pilot valve body 57
is biased in the valve opening direction, that is, in the backward direction, by a spring 58 interposed between the valve housing portion 33 and the valve housing portion 33 . Moreover, the pilot valve body 57 has a pilot valve hole 56 when the valve is opened.
A communication passage 60 communicating with the pilot valve body 57 is coaxially bored, and the communication passage 60 is opened at the rear end of the pilot valve body 57.
【００２５】ハウジング主体３２における内筒部３６内
にはスリーブ５９を介して駆動ロッド６１が軸方向移動
自在に配置されており、該駆動ロッド６１の先端はパイ
ロット弁体５７の後端に同軸に当接される。また内筒部
３６の端部と固定コア３４との間には、軸方向の移動を
可能として可動コア６２が配置されており、前記駆動ロ
ッド６１の後端が該可動コア６２に結合される。しかも
可動コア６２および固定コア３４間にはばね６３が縮設
されており、可動コア６２はばね６３により内筒部３６
側に付勢される。さらに駆動ロッド６１および固定コア
３４には、前記連通路６０に通じる連通路６４および連
通孔６５が穿設されている。A drive rod 61 is disposed within the inner cylindrical portion 36 of the housing main body 32 via a sleeve 59 so as to be movable in the axial direction, and the tip of the drive rod 61 is coaxially connected to the rear end of the pilot valve body 57. be touched. Furthermore, a movable core 62 is disposed between the end of the inner cylindrical portion 36 and the fixed core 34 so as to be movable in the axial direction, and the rear end of the drive rod 61 is coupled to the movable core 62. . Moreover, a spring 63 is compressed between the movable core 62 and the fixed core 34, and the movable core 62 is moved to the inner cylinder part 36 by the spring 63.
Forced to the side. Further, a communication passage 64 and a communication hole 65 communicating with the communication passage 60 are bored in the drive rod 61 and the fixed core 34.
【００２６】ハウジング主体３２の外筒部３５および内
筒部３６間には、ボビン６６に巻装されたコイル６７が
配設されており、該コイル６７に接続されるリード線６
８が固定コア３４から外部に引出される。A coil 67 wound around a bobbin 66 is disposed between the outer cylindrical portion 35 and the inner cylindrical portion 36 of the housing main body 32, and a lead wire 6 connected to the coil 67 is provided.
8 is pulled out from the fixed core 34.
【００２７】このような電磁開閉弁１５では、コイル６
７の励磁により可動コア６２および駆動ロッド６１がば
ね６３のばね力に抗して後退し、駆動ロッド６１に追随
してパイロット弁体５７が後退することによりパイロッ
ト弁孔４７が開放される。それにより背圧室５３の油圧
が解放され、主弁体５１の両面に作用する油圧のバラン
スがくずれ、その前面に作用している入口ポート４７の
油圧による開弁力が、背圧室５３の油圧およびばね５４
による閉弁力に打勝って開弁作動する。またコイル６７
の消磁状態では可動コア６２および駆動ロッド６１がば
ね６３のばね力により前進し、パイロット弁体５７はパ
イロット弁孔５６を閉塞するまで前進する。これにより
絞り５５を介して背圧室５３に入口ポート４７の油圧が
作用し、主弁体５１が閉弁作動する。In such an electromagnetic on-off valve 15, the coil 6
7, the movable core 62 and the drive rod 61 retreat against the spring force of the spring 63, and the pilot valve body 57 retreats following the drive rod 61, thereby opening the pilot valve hole 47. As a result, the hydraulic pressure in the back pressure chamber 53 is released, the balance of the hydraulic pressure acting on both sides of the main valve body 51 is disrupted, and the valve opening force due to the hydraulic pressure of the inlet port 47 acting on the front surface of the main valve body 51 is transferred to the back pressure chamber 53. Hydraulics and springs 54
The valve opens by overcoming the valve closing force. Also coil 67
In the demagnetized state, the movable core 62 and the drive rod 61 move forward by the spring force of the spring 63, and the pilot valve body 57 moves forward until it closes the pilot valve hole 56. As a result, the hydraulic pressure of the inlet port 47 acts on the back pressure chamber 53 via the throttle 55, and the main valve body 51 is operated to close.
【００２８】再び図１において、電磁開閉弁１５のコイ
ル６７の励磁および消磁はコンピュータから成る制御手
段Ｃにより制御されるものであり、開弁時にコイル６７
には、励磁電力として断続的な電流が印加される。しか
も制御手段Ｃは、電磁開閉弁１５を開弁すべくコイル６
７に印加する断続電流のデューティ比を作動油粘度に応
じて変化させるものであり、制御手段Ｃには作動油粘度
を代表する指標として作動油温度を検出する検出器７０
が接続される。而して制御手段Ｃでは、検出器７０で検
出された作動油温度が高いときすなわち作動油粘度が低
いときにコイル６７に印加する断続電流のデューティ比
が図３（ａ）で示すように設定されるのに対し、検出器
７０で検出された作動油温度が低いときすなわち作動油
粘度が高いときにコイル６７に印加する断続電流のデュ
ーティ比が図３（ｂ）で示すように設定されている。す
なわち作動油粘度が高いときのデューティ比は低粘度の
ときのテューティ比よりも大きく設定される。これに対
し、従来のものでは、鎖線で示すように作動油粘度の変
化にかかわらずデューティ比が定められていたものであ
る。Referring again to FIG. 1, the excitation and demagnetization of the coil 67 of the electromagnetic on-off valve 15 is controlled by a control means C consisting of a computer, and when the valve is opened, the coil 67 is
An intermittent current is applied as excitation power. Moreover, the control means C controls the coil 6 to open the electromagnetic on-off valve 15.
The control means C includes a detector 70 that detects the temperature of the hydraulic oil as an index representative of the viscosity of the hydraulic oil.
is connected. In the control means C, the duty ratio of the intermittent current applied to the coil 67 is set as shown in FIG. 3(a) when the hydraulic oil temperature detected by the detector 70 is high, that is, when the hydraulic oil viscosity is low. On the other hand, when the hydraulic oil temperature detected by the detector 70 is low, that is, when the hydraulic oil viscosity is high, the duty ratio of the intermittent current applied to the coil 67 is set as shown in FIG. 3(b). There is. That is, the duty ratio when the viscosity of the hydraulic oil is high is set larger than the duty ratio when the viscosity is low. In contrast, in the conventional system, the duty ratio is determined regardless of changes in the viscosity of the hydraulic oil, as shown by the chain line.
【００２９】次にこの実施例の作用について説明すると
、電磁開閉弁１５における内部の作動部、すなわち主弁
体５１、パイロット弁体５７および可動コア６２の周囲
には作動油が満たされており、コイル６７の励磁によっ
て生じる可動コア６２の固定コア３４側への電磁吸引力
が一定であるならば、それらの作動部の作動レスポンス
は周囲の作動油の粘度に左右されることになる。しかる
に、制御手段Ｃは、作動油粘度が高いときのデューティ
比を高くし、作動油粘度が低いときのデューテ比を低く
するようにしてコイル６７を励磁する。このため、可動
コア６２の固定コア３４側への電磁吸引力は、図４で示
すように、従来のものが白抜き部で示すように作動油粘
度にかかわらず一定であったのに対し、上述のように作
動油粘度の高、低に応じてデューティ比を変化させるこ
とにより斜線部で示すように変化するものであり、作動
油粘度の高いときには電磁吸引力が従来のものよりも強
くなり、作動油粘度の低いときには電磁吸引力が従来の
ものよりも弱くなる。Next, the operation of this embodiment will be explained. The internal operating parts of the electromagnetic on-off valve 15, that is, the main valve body 51, the pilot valve body 57, and the movable core 62 are filled with hydraulic oil. If the electromagnetic attraction force of the movable core 62 toward the fixed core 34 side generated by the excitation of the coil 67 is constant, the operational response of these operating parts will depend on the viscosity of the surrounding hydraulic oil. However, the control means C excites the coil 67 by increasing the duty ratio when the viscosity of the hydraulic oil is high and decreasing the duty ratio when the viscosity of the hydraulic oil is low. Therefore, as shown in FIG. 4, the electromagnetic attraction force of the movable core 62 toward the fixed core 34 is constant regardless of the viscosity of the hydraulic oil as shown by the white area in the conventional case. As mentioned above, by changing the duty ratio depending on whether the viscosity of the hydraulic oil is high or low, it changes as shown in the shaded area, and when the viscosity of the hydraulic oil is high, the electromagnetic attraction force becomes stronger than that of conventional ones. , When the viscosity of the hydraulic oil is low, the electromagnetic attraction force becomes weaker than that of the conventional one.
【００３０】このように作動油粘度の変化に応じて電磁
吸引力を変化させるようにすると、電磁開閉弁１５にお
ける作動部の作動レスポンスは、作動油粘度の高、低に
応じて図５の斜線部で示すようになる。すなわち作動油
粘度が高いときには白抜き部で示す従来のものよりも作
動レスポンスが向上し、作動油粘度が低いときには白抜
き部で示す従来のものよりも作動レスポンスが低下する
ことになる。このようにして、電磁開閉弁１５の作動レ
スポンスは、従来のものが図６の破線で示す曲線のよう
に作動油粘度の変化に応じて変化するものであったのに
対し、図６の実線で示すように作動油粘度の変化にかか
わらずほぼ一定となる。これにより、作動油粘度が高い
ときすなわち低温時に電磁開閉弁１５の作動レスポンス
を向上することが可能となる。また電磁開閉弁１５の作
動レスポンスを作動油粘度の変化にかかわらずほぼ一定
とすることにより、図７で示すように、作動音レベルを
作動油粘度の変化にかかわらずほぼ一定とすることがで
きる。すなわち作動油粘度が高いときには作動速度が従
来のものよりも早くなることにより、白抜き部で示す従
来のものよりも作動音レベルを斜線部で示すようにわず
かに増加させ、また作動油粘度が低いときには作動速度
の低下に応じて作動音レベルを白抜き部で示す従来のも
のよりも斜線部で示すように大幅に低下させることがで
きる。When the electromagnetic attraction force is changed in accordance with changes in the viscosity of the hydraulic oil in this way, the operational response of the actuating part of the electromagnetic on-off valve 15 changes as indicated by the diagonal lines in FIG. 5 depending on whether the viscosity of the hydraulic oil is high or low. It becomes as shown in the section. That is, when the viscosity of the hydraulic oil is high, the operational response is improved compared to the conventional type shown by the white area, and when the viscosity of the hydraulic oil is low, the operational response is lower than the conventional type shown by the white area. In this way, the operational response of the electromagnetic on-off valve 15 changes according to changes in the viscosity of the hydraulic fluid, as shown by the broken line in FIG. As shown in , it remains almost constant regardless of changes in hydraulic oil viscosity. This makes it possible to improve the operational response of the electromagnetic on-off valve 15 when the viscosity of the hydraulic oil is high, that is, when the temperature is low. Furthermore, by making the operating response of the electromagnetic on-off valve 15 almost constant regardless of changes in the viscosity of the hydraulic oil, the operating sound level can be kept almost constant regardless of changes in the viscosity of the hydraulic oil, as shown in FIG. . In other words, when the viscosity of the hydraulic oil is high, the operating speed is faster than that of the conventional type, so the operating noise level is slightly increased as shown by the shaded area compared to the conventional type shown in the white area, and the viscosity of the hydraulic oil is also increased. When the operating speed is low, the operating sound level can be significantly lowered as shown by the hatched area compared to the conventional system shown by the white area.
【００３１】本発明の他の実施例として、図８で示すよ
うに、電磁開閉弁１５のコイル６７に印加する電圧を、
作動油粘度が低くなるにつれて低くなるように段階的に
変化させるようにしても、上記実施例と同様の効果を奏
することができる。As another embodiment of the present invention, as shown in FIG. 8, the voltage applied to the coil 67 of the electromagnetic on-off valve 15 is
Even if the viscosity of the hydraulic oil is changed stepwise so that the viscosity decreases as the viscosity of the hydraulic oil decreases, the same effect as in the above embodiment can be obtained.
【００３２】以上の実施例では、作動油粘度を代表する
指標として作動油温度を検出するようにしたが、機関冷
却水温を検出するようにしてもよい。また本発明は、排
気弁の油圧駆動装置についても適用可能である。In the embodiments described above, the temperature of the hydraulic oil is detected as an index representative of the viscosity of the hydraulic oil, but the temperature of the engine cooling water may also be detected. The present invention is also applicable to a hydraulic drive device for an exhaust valve.
【００３３】[0033]
【発明の効果】以上のように本発明によれば、作動油の
粘度を代表する指標を検出する検出器が制御手段に接続
され、該制御手段は、電磁開閉弁の駆動電力を作動油の
粘度が大であるときに大とするように段階的または連続
的に変化すべく構成されるので、作動油高粘度時の作動
レスポンス向上を図るとともに作動油低粘度時の作動音
低減を図ることが可能となる。As described above, according to the present invention, a detector for detecting an index representative of the viscosity of hydraulic oil is connected to the control means, and the control means controls the driving power of the electromagnetic on-off valve to the viscosity of the hydraulic oil. Since the viscosity is configured to change stepwise or continuously so as to increase when the viscosity is high, it is possible to improve the operational response when the hydraulic oil is high in viscosity and to reduce the operational noise when the hydraulic oil is low in viscosity. becomes possible.
【図１】本発明の一実施例の油圧駆動装置の縦断面図で
ある。FIG. 1 is a longitudinal sectional view of a hydraulic drive device according to an embodiment of the present invention.
【図２】電磁開閉弁の拡大縦断面図である。FIG. 2 is an enlarged vertical cross-sectional view of the electromagnetic on-off valve.
【図３】作動油粘度の高、低に応じて定められたデュー
ティ比を示す図である。FIG. 3 is a diagram showing duty ratios determined according to high and low viscosity of hydraulic oil.
【図４】作動油粘度の高、低に応じた電磁吸引力の従来
との対比図である。FIG. 4 is a comparison diagram of the electromagnetic attraction force with the conventional one depending on the high and low viscosity of the hydraulic oil.
【図５】作動油粘度の高、低に応じた作動レスポンスの
従来との対比図である。FIG. 5 is a diagram comparing the operational response according to the high and low viscosity of the hydraulic oil with the conventional one.
【図６】作動油粘度の高、低に応じた作動レスポンスの
変化を示すグラフである。FIG. 6 is a graph showing changes in operational response depending on whether the viscosity of the hydraulic oil is high or low.
【図７】作動油粘度の高、低に応じた作動音レベルの従
来との対比図である。FIG. 7 is a comparison diagram of the operating sound level according to the high and low viscosity of the hydraulic oil with the conventional one.
【図８】本発明の他の実施例の作動油粘度の高、低に応
じた印加電圧の変化を示すグラフである。FIG. 8 is a graph showing changes in applied voltage according to high and low viscosity of hydraulic oil in another embodiment of the present invention.
８ 油圧発生手段１２
支持部としての支持ブロック１３
弁駆動ピストン１５
電磁開閉弁
１６ シリンダ体
１７ 油圧室
７０ 検出器
Ｃ 制御手段8 Hydraulic pressure generating means 12
Support block 13 as a support part
Valve drive piston 15
Electromagnetic on-off valve 16 Cylinder body 17 Hydraulic chamber 70 Detector C Control means
Claims (3)
リンダ体（１６）に、該シリンダ体（１６）との間に形
成される油圧室（１７）に背面を臨ませるとともに前端
を機関弁（Ｖ）の後端に当接させる弁駆動ピストン（１
３）が摺動可能に嵌合され、前記油圧室（１７）には、
機関弁（Ｖ）の開弁時期に対応して油圧を発生する油圧
発生手段（８）と、開弁時に前記油圧室（１７）の油圧
を解放可能な電磁開閉弁（１５）とが接続され、機関の
要求に応じて機関弁（Ｖ）の開閉作動特性を変更すべく
電磁開閉弁（１５）の開閉作動を制御する制御手段（Ｃ
）が電磁開閉弁（１５）に接続される内燃機関用機関弁
の油圧駆動装置において、作動油の粘度を代表する指標
を検出する検出器（７０）が制御手段（Ｃ）に接続され
、該制御手段（Ｃ）は、電磁開閉弁（１５）の駆動電力
を作動油の粘度が大であるときに大とするように段階的
または連続的に変化すべく構成されることを特徴とする
内燃機関用機関弁の油圧駆動装置。Claim 1: A cylinder body (16) fixed to a fixed support part (12) is provided with its rear face facing a hydraulic chamber (17) formed between the cylinder body (16) and its front end facing toward the engine. The valve drive piston (1) is brought into contact with the rear end of the valve (V).
3) is slidably fitted in the hydraulic chamber (17), and
A hydraulic pressure generating means (8) that generates hydraulic pressure in accordance with the opening timing of the engine valve (V) is connected to an electromagnetic on-off valve (15) that can release the hydraulic pressure in the hydraulic chamber (17) when the valve is opened. , a control means (C) for controlling the opening/closing operation of the electromagnetic on-off valve (15) to change the opening/closing operation characteristics of the engine valve (V) in accordance with the request of the engine;
) is connected to an electromagnetic on-off valve (15) in a hydraulic drive system for an engine valve for an internal combustion engine. The control means (C) is configured to stepwise or continuously change the driving power of the electromagnetic on-off valve (15) so as to increase the driving power when the viscosity of the hydraulic oil is high. Hydraulic drive system for engine valves.
弁（１５）に印加する断続的な電流のデューティ比を作
動油粘度に応じて変化させるべく構成されることを特徴
とする請求項１記載の内燃機関用機関弁の油圧駆動装置
。2. The control means (C) is configured to change the duty ratio of the intermittent current applied to the electromagnetic on-off valve (15) according to the viscosity of the hydraulic oil. 1. The hydraulic drive device for an engine valve for an internal combustion engine according to 1.
１５）に印加する電圧を作動油粘度に応じて変化させる
べく構成されることを特徴とする請求項１記載の内燃機
関用機関弁の油圧駆動装置。3. The control means (C) includes an electromagnetic on-off valve (
15. The hydraulic drive device for an engine valve for an internal combustion engine according to claim 1, wherein the hydraulic drive device is configured to change the voltage applied to the valve in accordance with the viscosity of the hydraulic oil.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3057202A JPH04292506A (en) | 1991-03-20 | 1991-03-20 | Hydraulic drive device for engine valve for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3057202A JPH04292506A (en) | 1991-03-20 | 1991-03-20 | Hydraulic drive device for engine valve for internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH04292506A true JPH04292506A (en) | 1992-10-16 |
Family
ID=13048914
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3057202A Pending JPH04292506A (en) | 1991-03-20 | 1991-03-20 | Hydraulic drive device for engine valve for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH04292506A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0667805U (en) * | 1993-03-05 | 1994-09-22 | 川崎重工業株式会社 | Hydraulic valve drive for internal combustion engine |
| DE10306456A1 (en) * | 2003-02-17 | 2004-09-02 | Robert Bosch Gmbh | Regulator for motor vehicle internal combustion engine valve has hydraulic fluid viscosity sensor to adjust valve control action |
| EP1378636A3 (en) * | 2002-07-01 | 2006-06-07 | C.R.F. Società Consortile per Azioni | An internal-combustion engine with an electronically controlled hydraulic system for actuation of the valves and means for compensating changes in the operating conditions of the hydraulic fluid |
| EP2657470A1 (en) * | 2012-04-26 | 2013-10-30 | C.R.F. Società Consortile per Azioni | A method for controlling a valve control system with variable valve lift of an internal combustion engine by operating a compensation in response to the deviation of the characteristics of a working fluid with respect to nominal conditions |
| CN103939169A (en) * | 2014-05-05 | 2014-07-23 | 王欣亮 | Electro-hydraulic valve for engine and working system thereof |
| EP2733333A4 (en) * | 2011-07-12 | 2015-03-11 | Aisin Seiki | Valve opening/closing time adjustment system |
-
1991
- 1991-03-20 JP JP3057202A patent/JPH04292506A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0667805U (en) * | 1993-03-05 | 1994-09-22 | 川崎重工業株式会社 | Hydraulic valve drive for internal combustion engine |
| EP1378636A3 (en) * | 2002-07-01 | 2006-06-07 | C.R.F. Società Consortile per Azioni | An internal-combustion engine with an electronically controlled hydraulic system for actuation of the valves and means for compensating changes in the operating conditions of the hydraulic fluid |
| DE10306456A1 (en) * | 2003-02-17 | 2004-09-02 | Robert Bosch Gmbh | Regulator for motor vehicle internal combustion engine valve has hydraulic fluid viscosity sensor to adjust valve control action |
| DE10306456B4 (en) * | 2003-02-17 | 2006-11-30 | Robert Bosch Gmbh | Adjusting device for electrohydraulic actuation of gas exchange valves of an internal combustion engine |
| EP2733333A4 (en) * | 2011-07-12 | 2015-03-11 | Aisin Seiki | Valve opening/closing time adjustment system |
| US9057292B2 (en) | 2011-07-12 | 2015-06-16 | Aisin Seiki Kabushiki Kaisha | Valve timing adjustment system |
| EP2657470A1 (en) * | 2012-04-26 | 2013-10-30 | C.R.F. Società Consortile per Azioni | A method for controlling a valve control system with variable valve lift of an internal combustion engine by operating a compensation in response to the deviation of the characteristics of a working fluid with respect to nominal conditions |
| US8733303B2 (en) | 2012-04-26 | 2014-05-27 | C.R.F. Societa Consortile Per Azioni | Method for controlling a valve control system with variable valve lift of an internal combustion engine by operating a compensation in response to the deviation of the characteristics of a working fluid with respect to nominal conditions |
| CN103939169A (en) * | 2014-05-05 | 2014-07-23 | 王欣亮 | Electro-hydraulic valve for engine and working system thereof |
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