JPH02523B2 - - Google Patents
Info
- Publication number
- JPH02523B2 JPH02523B2 JP58220053A JP22005383A JPH02523B2 JP H02523 B2 JPH02523 B2 JP H02523B2 JP 58220053 A JP58220053 A JP 58220053A JP 22005383 A JP22005383 A JP 22005383A JP H02523 B2 JPH02523 B2 JP H02523B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- piston
- hydraulic
- supply passage
- hydraulic oil
- 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 - Lifetime
Links
- 239000010720 hydraulic oil Substances 0.000 claims description 20
- 238000002485 combustion reaction Methods 0.000 claims description 6
- 230000013011 mating Effects 0.000 claims 1
- 239000003921 oil Substances 0.000 description 8
- 230000000694 effects Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000000779 smoke Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は内燃機関の高圧作動油で作動する油圧
作動動弁装置に関する。DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a hydraulically operated valve train that operates using high pressure hydraulic oil for an internal combustion engine.
（従来技術）
第１図のような油圧作動動弁装置が知られてい
る。第１図において、装置本体１内に形成された
シリンダ２に嵌合するピストン３のロツドは排気
弁４の上端に当接している。シリンダ２内の油圧
室５には作動油供給通路６と排出通路７が開口
し、各通路６，７はそれぞれ電磁弁８，９を有し
ている。又各電磁弁８，９は図示しないコントロ
ール装置に電気的に接続されている。(Prior Art) A hydraulically operated valve train as shown in FIG. 1 is known. In FIG. 1, the rod of a piston 3 that fits into a cylinder 2 formed within a main body 1 of the apparatus is in contact with the upper end of an exhaust valve 4. A hydraulic oil supply passage 6 and a discharge passage 7 open into the hydraulic chamber 5 in the cylinder 2, and each passage 6, 7 has a solenoid valve 8, 9, respectively. Further, each electromagnetic valve 8, 9 is electrically connected to a control device (not shown).
弁４を開く場合には電磁弁９を閉じた状態で電
磁弁８を開け、油圧室５内に油圧を供給してピス
トン３を下降させる。一方弁４を閉じる場合には
電磁弁８を閉じ電磁弁９を開けることによつて油
圧室５内の作動油を排出すると、図示しない弁ば
ねによつて弁４はピストン３を押し上げながら上
方に移動して閉じる。 When opening the valve 4, the solenoid valve 8 is opened with the solenoid valve 9 closed, and hydraulic pressure is supplied into the hydraulic chamber 5 to lower the piston 3. On the other hand, when closing the valve 4, the solenoid valve 8 is closed and the solenoid valve 9 is opened to drain the hydraulic oil in the hydraulic chamber 5. Then, the valve 4 is moved upward while pushing up the piston 3 by a valve spring (not shown). Move and close.
上記作動において開弁初期には、排気弁４には
上方向の背圧がかかつていることから大きな力を
必要とする。しかし弁４がわずかに開けば、背圧
が抜けて圧力が略バランスし、その後は弁ばねに
打ち勝つだけで開弁動作が行なえるようになつて
小さな力しか必要でなくなる。 In the above-mentioned operation, at the initial stage of opening the exhaust valve 4, upward back pressure is applied to the exhaust valve 4, so a large force is required. However, when the valve 4 is opened slightly, the back pressure is released and the pressure is approximately balanced, and after that, the valve can be opened simply by overcoming the valve spring, and only a small force is required.
しかし上記従来例では、開弁初期も又それ以後
も開弁初期に必要な大きな力で弁４を作動させる
構成となつており、直径の大きなピストン３を動
かす為に、作動油量が多く必要となつて油圧ポン
プの容量を大きくしなければならない。又開弁初
期においても、単に供給通路からの作動油圧を直
接に油圧室５に供給する構成となつていることか
ら、油圧ポンプの駆動馬力を大きくしておく必要
がある。 However, in the above conventional example, the valve 4 is operated with a large force required at the initial stage of opening the valve and thereafter, and a large amount of hydraulic oil is required to move the piston 3, which has a large diameter. Therefore, the capacity of the hydraulic pump must be increased. Further, even in the early stage of opening the valve, since the configuration is such that the working hydraulic pressure is simply supplied directly to the hydraulic chamber 5 from the supply passage, it is necessary to increase the driving horsepower of the hydraulic pump.
（発明の目的）
油圧ポンプの容量を小さくし、又駆動馬力も小
さくできる油圧作動動弁装置を提供する。(Objective of the Invention) To provide a hydraulically operated valve train in which the capacity of a hydraulic pump can be reduced and the drive horsepower can also be reduced.
（発明の構成）
次の事項を必須の要件とする内燃機関の油圧作
動動弁装置である。(Structure of the Invention) This is a hydraulically operated valve train for an internal combustion engine that has the following essential requirements.
(a) 吸気又は排気の弁に連動する作動ピストンを
油圧により作動させて弁を開閉制御するよう設
ける。(a) An operating piston linked to the intake or exhaust valve is operated by hydraulic pressure to control the opening and closing of the valve.
(b) 電磁弁で開閉制御される第１の作動油供給通
路から分岐した第２の作動油供給通路に、作動
ピストン頂面に油圧を増大して伝える倍力用ピ
ストンを設ける。(b) A booster piston that increases and transmits hydraulic pressure to the top surface of the working piston is provided in a second hydraulic oil supply passage branched from the first hydraulic oil supply passage whose opening and closing are controlled by a solenoid valve.
(c) 倍力用ピストンを、作動ピストンを開弁初期
の限られたストロークだけ移動させるよう設け
る。(c) The booster piston is provided so that the actuating piston moves only a limited stroke at the initial stage of opening the valve.
(d) 第１の作動油供給通路を、弁の全閉時には作
動ピストンにより閉塞され且つ作動ピストンが
上記ストロークだけ移動した後に作動ピストン
頂面に油圧を伝えるよう設ける。(d) The first hydraulic oil supply passage is provided so as to be closed by the working piston when the valve is fully closed and to transmit hydraulic pressure to the top surface of the working piston after the working piston has moved by the above-mentioned stroke.
（実施例）
第２図において、シリンダヘツド２１内に設け
られた排気ポート２２（吸気ポートでもよい）を
閉じる排気弁２３は、上方に延びる弁棒２４を一
体に有している。弁棒２４の上端部に設けられた
ばね受１８とシリンダヘツド２１との間に縮設さ
れた弁ばね１９によつて、弁２３は常時ポート２
２を閉じる方向に弾性的に付勢されている。(Embodiment) In FIG. 2, an exhaust valve 23 that closes an exhaust port 22 (or an intake port) provided in a cylinder head 21 integrally has a valve rod 24 extending upward. The valve 23 is always connected to the port 2 by the valve spring 19 compressed between the spring bearing 18 provided at the upper end of the valve stem 24 and the cylinder head 21.
2 is elastically biased in the direction of closing.
弁棒２４の上端は作動ピストン２５のピストン
ロツド２６の下端に当接しており、ピストン２５
は装置本体２７内に形成されたシリンダ２８内に
上下方向摺動自在に嵌合している。シリンダ２８
内にはピストン２５の上方に油圧室２９が形成さ
れ、室２９の上端面には絞り３０を介して排出通
路３１が開口している。通路３１は途中に電磁弁
３２を有し、その弁本体３３が開閉自在に通路３
１内に突出している。絞り３０と電磁弁３２との
間で通路３１は分岐しており、分岐路３４はピス
トン２５上端面よりもわずか下方のシリンダ２８
側壁面に開口している。 The upper end of the valve stem 24 is in contact with the lower end of the piston rod 26 of the actuating piston 25.
is fitted into a cylinder 28 formed in the device main body 27 so as to be slidable in the vertical direction. cylinder 28
A hydraulic chamber 29 is formed inside the piston 25 above the piston 25, and a discharge passage 31 is opened at the upper end surface of the chamber 29 via a throttle 30. The passage 31 has a solenoid valve 32 in the middle, and the valve body 33 can open and close freely.
It stands out within 1. The passage 31 branches between the throttle 30 and the solenoid valve 32, and the branch passage 34 connects to the cylinder 28 slightly below the upper end surface of the piston 25.
It is open on the side wall.
シリンダ２８側壁部の分岐路３４の開口位置と
略同一円周上反対側には供給通路３５が開口して
おり、分岐路３４と通路３５間はシリンダ２８の
円周方向に形成される環状溝５０を介し常時連通
している。通路３５は途中に電磁弁３６を有し、
その弁本体３７が開閉自在に通路３５内に突出し
ている。電磁弁３６とシリンダ２８間において通
路３５は分岐しており、分岐路３８は倍力用ピス
トン４０の嵌合する大径シリンダ４１上部の油圧
室４２に開口している。倍力用ピストン４０は油
圧室４２を形成する大径部４３と、それと一体に
形成され小径部４４とからなり、大径部４３が大
径シリンダ４１に摺動自在に嵌合すると共に、小
径部４４が大径シリンダ４１の下方に段部を介し
て同心に形成された小径シリンダ４５内に摺動自
在に嵌合している。又ピストン４０は、シリンダ
４１，４５間の段部と大径部４３との間に縮設さ
れたコイルばね４６によつて常時上方へ付勢され
ている。小径シリンダ４５の底面とシリンダ２８
の側壁面上端部との間は通路４７によつて連通し
ている。なお４８はシリンダ２８の逃し孔、４９
はシリンダ４１の逃し孔である。 A supply passage 35 opens on the opposite side of the cylinder 28 side wall on the same circumference as the opening position of the branch passage 34, and an annular groove formed in the circumferential direction of the cylinder 28 is formed between the branch passage 34 and the passage 35. They are in constant communication via 50. The passage 35 has a solenoid valve 36 in the middle,
The valve body 37 protrudes into the passage 35 so as to be openable and closable. The passage 35 branches between the electromagnetic valve 36 and the cylinder 28, and the branch passage 38 opens into a hydraulic chamber 42 above a large diameter cylinder 41 into which a booster piston 40 is fitted. The boosting piston 40 consists of a large diameter part 43 forming a hydraulic chamber 42 and a small diameter part 44 integrally formed therewith.The large diameter part 43 is slidably fitted into the large diameter cylinder 41, and the small diameter part A portion 44 is slidably fitted into a small diameter cylinder 45 formed concentrically below the large diameter cylinder 41 via a stepped portion. Further, the piston 40 is always urged upward by a coil spring 46 compressed between the stepped portion between the cylinders 41 and 45 and the large diameter portion 43. The bottom of the small diameter cylinder 45 and the cylinder 28
A passage 47 communicates with the upper end of the side wall surface. Note that 48 is a relief hole of the cylinder 28, and 49 is a relief hole of the cylinder 28.
is a relief hole of the cylinder 41.
供給通路３５の上手側は、途中にアキユムレー
タ５１を有する油路５２に連結されており、油路
５２は作動油供給システム５３の高圧油圧ポンプ
５４に連通している。ポンプ５４はエンジン５５
によつて駆動されるようになつており、又オイル
パン５６から作動油が供給されるようになつてい
る。オイルパン５６には油路５７を介して、装置
本体２７の排出通路３１からの作動油が戻される
ようになつている。 The upper side of the supply passage 35 is connected to an oil passage 52 having an accumulator 51 in the middle, and the oil passage 52 communicates with a high-pressure hydraulic pump 54 of a hydraulic oil supply system 53. The pump 54 is an engine 55
It is designed to be driven by a pump, and hydraulic oil is supplied from an oil pan 56. Hydraulic oil from the discharge passage 31 of the device body 27 is returned to the oil pan 56 via an oil passage 57.
エンジン５５にはクランク角度（位相）検出セ
ンサ６１をはじめ、負荷状態、回転速度等を検知
する種々のセンサ（図示せず）が設置されてお
り、それらセンサによる情報が電気的にコントロ
ール装置６２内のマイクロコンピユータ６３に入
力されるようになつている。コンピユータ６３で
はそれらの情報に基づいて演算を行ない、エンジ
ン５５の状態に応じて適切な吸排気弁（例えば弁
２３）の開閉タイミングを決定し、電磁弁３２，
３６の電磁ソレノイド６４，６５に所定の電流を
流すようになつている。 The engine 55 is equipped with a crank angle (phase) detection sensor 61 and various other sensors (not shown) that detect load conditions, rotational speed, etc., and information from these sensors is electrically transmitted to the control device 62. The data is input to the microcomputer 63 of the computer. The computer 63 performs calculations based on the information, determines the appropriate opening/closing timing of the intake and exhaust valves (for example, the valve 23) according to the state of the engine 55, and determines the opening and closing timing of the solenoid valves 32,
A predetermined current is made to flow through the 36 electromagnetic solenoids 64 and 65.
次に作動を説明する。排気弁２３を開く場合に
は、まずコントロール装置６２からの指令により
ソレノイド６５が通電されて作動し、電磁弁３６
の弁本体３７が開く。通路３５は作動ピストン２
５により塞がれているので、油圧は油圧室４２に
供給され、倍力用ピストン４０の大径部４３上面
に作用する。これによりピストン４０が下降する
とシリンダ４５内の作動油が小径部４４によつて
押し出され、通路４７を介して油圧室２９に作動
油圧を供給する。 Next, the operation will be explained. When opening the exhaust valve 23, the solenoid 65 is first energized and activated by a command from the control device 62, and the solenoid valve 36 is opened.
The valve body 37 of is opened. The passage 35 is the working piston 2
5, the hydraulic pressure is supplied to the hydraulic chamber 42 and acts on the upper surface of the large diameter portion 43 of the booster piston 40. As a result, when the piston 40 descends, the hydraulic oil in the cylinder 45 is pushed out by the small diameter portion 44, and the hydraulic pressure is supplied to the hydraulic chamber 29 via the passage 47.
ここでピストン４０の大径部４３と小径部４４
の各直径をＤ，ｄとし、システム５３からの供給
油圧をP0とすると、油圧室２９に供給される油
圧はP0×（Ｄ／ｄ）となる。即ち（Ｄ／ｄ）＞１
であるから、油圧室２９には（Ｄ／ｄ）倍に拡大
された油圧が供給されることになる。 Here, the large diameter part 43 and the small diameter part 44 of the piston 40
Let the respective diameters of the hydraulic pressure chamber 29 be D and d, and the hydraulic pressure supplied from the system 53 be P 0 , then the hydraulic pressure supplied to the hydraulic chamber 29 is P 0 ×(D/d). That is, (D/d)>1
Therefore, the hydraulic pressure increased by (D/d) is supplied to the hydraulic chamber 29.
油圧室２９に供給される高圧によつてピストン
２５が、弁ばね１９及び排気弁２３にかかる背圧
に打ち勝つてわずかに下降すると、排気弁２３は
開いて排気ポート２２側へ圧力が抜ける。従つて
これ以後はピストン２５は弁ばね１９にのみ抗す
ればよいことになる。更にピストン２５が下方へ
摺動すると油圧室２９は供給油路３５及び分岐路
３４に対して開口する。これによつて油圧室２９
内の圧力はP0に下り、その後は通路３５から直
接供給される作動油圧P0によつてピストン２５
は弁２３が全開位置となる迄下降を続ける。 When the piston 25 overcomes the back pressure applied to the valve spring 19 and the exhaust valve 23 and descends slightly due to the high pressure supplied to the hydraulic chamber 29, the exhaust valve 23 opens and the pressure is released to the exhaust port 22 side. Therefore, from now on, the piston 25 only has to resist the valve spring 19. When the piston 25 further slides downward, the hydraulic chamber 29 opens to the supply oil path 35 and the branch path 34. As a result, the hydraulic chamber 29
The pressure in the piston 25 decreases to P 0 , and then the hydraulic pressure P 0 supplied directly from the passage 35 causes the piston 25 to
continues to descend until the valve 23 is in the fully open position.
閉弁時には、コントロール装置６２からの指令
によつて電磁弁３６を閉じ、電磁弁３２を開け
る。これによつて作動油は油路５７を介してオイ
ルパン５６に戻るが、通路の抵抗があるため急激
にはピストン２５が元に戻ることはない。ピスト
ン２５は弁ばね１９の力によつて初期の状態に復
帰し、このとき油圧室２９には弁ばね１９のばね
力換算油圧P′が発生する。倍力用ピストン４０で
は小径部４４にかかる油圧P′とコイルばね４６に
よつてピストン４０が元に戻される。ここで供給
通路３５は、ピストン２５によつて油圧室２９に
対して閉じられた後も環状溝５０を介して排出通
路３１に連通している。従つて絞り３０の効果に
より小径シリンダ４５内の圧力が油圧室４２の圧
力に勝るためピストン４０が上方に摺動して元の
状態に復帰することになる。絞り３０は、ピスト
ン２５が分岐路３４を閉じた後停止する迄のシヨ
ツクを軟らげる役目を有しており、これによつて
排気弁２３はスムーズに着座する。 When closing the valve, the solenoid valve 36 is closed and the solenoid valve 32 is opened according to a command from the control device 62. As a result, the hydraulic oil returns to the oil pan 56 via the oil passage 57, but the piston 25 does not return to its original position suddenly because of the resistance of the passage. The piston 25 is returned to its initial state by the force of the valve spring 19, and at this time, a hydraulic pressure P' converted to the spring force of the valve spring 19 is generated in the hydraulic chamber 29. In the booster piston 40, the piston 40 is returned to its original state by the hydraulic pressure P' applied to the small diameter portion 44 and the coil spring 46. Here, the supply passage 35 communicates with the discharge passage 31 via the annular groove 50 even after being closed to the hydraulic chamber 29 by the piston 25 . Therefore, due to the effect of the throttle 30, the pressure inside the small diameter cylinder 45 exceeds the pressure in the hydraulic chamber 42, so the piston 40 slides upward and returns to its original state. The throttle 30 has the role of softening the shock until the piston 25 stops after closing the branch passage 34, so that the exhaust valve 23 is seated smoothly.
再び開弁動作を行なう場合には電磁弁３２を閉
じ、電磁弁３６を再び開けることによつて上記開
弁動作が再び行なわれる。このように両電磁弁３
２，３６の作動をコントロール装置６２によつて
制御することにより、開閉弁動作を繰返し行なう
ことができる。 When the valve opening operation is to be performed again, the electromagnetic valve 32 is closed and the electromagnetic valve 36 is opened again, thereby performing the above-mentioned valve opening operation again. In this way, both solenoid valves 3
By controlling the operations of 2 and 36 by the control device 62, the opening and closing valve operations can be performed repeatedly.
なお倍力用ピストン４０の作用による作動ピス
トン２５の摺動ストロークは排気弁の背圧を抜く
だけの長さがあれば足りる。 Note that the sliding stroke of the operating piston 25 due to the action of the booster piston 40 only needs to be long enough to relieve the back pressure of the exhaust valve.
（発明の効果）
分岐路３８に、油圧室２９に油圧を増大して伝
える倍力用ピストン４０を、作動ピストン２５を
開弁初期の限られたストロークだけ移動させるよ
う設け、供給通路３５を、弁２３の全閉時には作
動ピストン２５により閉塞され且つ作動ピストン
２５が上記ストロークだけ移動した後に油圧室２
９に油圧を伝えるように設けたので；
(a) 作動ピストン２５及びそのシリンダ２８を小
径化できる。(Effects of the Invention) A boosting piston 40 is provided in the branch passage 38 to increase and transmit hydraulic pressure to the hydraulic chamber 29 so as to move the operating piston 25 by a limited stroke at the initial stage of valve opening, and the supply passage 35 is When the valve 23 is fully closed, it is closed by the working piston 25, and after the working piston 25 has moved by the above-mentioned stroke, the hydraulic chamber 2 is closed.
(a) The working piston 25 and its cylinder 28 can be made smaller in diameter.
(b) 作動油供給量が少なくてすむことから、油圧
ポンプ５４の容量を小さくできる。(b) Since the amount of hydraulic oil supplied is small, the capacity of the hydraulic pump 54 can be reduced.
(c) 作動油圧を低くすることができることから、
油圧ポンプ５４の駆動馬力を小さくできる。(c) Since the hydraulic pressure can be lowered,
The driving horsepower of the hydraulic pump 54 can be reduced.
(d) 従つて油圧作動動弁装置全体を小型化でき
る。(d) Therefore, the entire hydraulically operated valve train can be downsized.
また倍力用ピストン４０に伝わる油圧は電磁弁
３６により制御されるようになつているので；
(e) クランク角に対する弁２３の開弁のタイミン
グを迅速且つ正確にコントロールすることがで
きる。従つて吸気弁又は排気弁の急速開弁動作
と急速閉弁動作によつて吸気又は排気の効率を
向上させ、内燃機関の出力の向上を図ることが
でき、また燃料を十分燃焼させた後に弁２３か
ら排気させることができ、黒煙排出を低減する
ことができる。 Furthermore, since the hydraulic pressure transmitted to the booster piston 40 is controlled by the solenoid valve 36; (e) the timing of opening of the valve 23 relative to the crank angle can be controlled quickly and accurately. Therefore, the efficiency of intake or exhaust can be improved by the rapid opening and closing of the intake or exhaust valve, and the output of the internal combustion engine can be improved. 23, and black smoke emissions can be reduced.
(f) 更に電磁弁３６のデユーテイ比を制御するこ
とにより弁２３の開閉速度を容易にコントロー
ルすることができ、弁２３の開閉を内燃機関の
作動に容易に適合させることができる。(f) Furthermore, by controlling the duty ratio of the solenoid valve 36, the opening and closing speed of the valve 23 can be easily controlled, and the opening and closing of the valve 23 can be easily adapted to the operation of the internal combustion engine.
（別の実施例）
(a) 油圧ポンプ５４はエンジン５５によつて駆動
されるタイプに限られることはなく、例えば電
動モータ駆動タイプのものを採用してもよい。(Another Embodiment) (a) The hydraulic pump 54 is not limited to the type driven by the engine 55, and may be driven by an electric motor, for example.
第１図は従来の油圧作動動弁装置の縦断面図、
第２図は本発明による油圧作動動弁装置のレイア
ウト図である。
２３……排気弁（吸気、排気弁の一例）、２５
……作動ピストン、３２，３６……電磁弁、４０
……倍力用ピストン。
Figure 1 is a longitudinal cross-sectional view of a conventional hydraulically operated valve train.
FIG. 2 is a layout diagram of a hydraulically operated valve train according to the present invention. 23...Exhaust valve (an example of an intake/exhaust valve), 25
... Operating piston, 32, 36 ... Solenoid valve, 40
... Boosting piston.
Claims (1)
ポンプからの油圧により作動させて弁を開閉制御
する内燃機関の油圧作動弁装置において、一端が
ポンプの吐出口に連結し他端が作動ピストンの嵌
合するシリンダの内壁に開口した第１の作動油供
給通路を設け、第１の作動油供給通路にその通路
を開閉制御する電磁弁を設け、第１の作動油供給
通路の電磁弁よりシリンダ寄りの部分から分岐し
て弁の全閉時における作動ピストンの頂面に油圧
を供給し得るようシリンダ内壁に開口した第２の
作動油供給通路を設け、油圧を増大して伝える倍
力用ピストンを第２の作動油供給通路に設け、第
１の作動油供給通路のシリンダ内壁への開口を、
弁の全閉時における作動ピストンにより閉塞され
且つ作動ピストンが開弁初期の限られたストロー
クだけ移動すると作動ピストン頂面に油圧を供給
し得るよう設けたことを特徴とする内燃機関の油
圧作動動弁装置。1. In a hydraulically operated valve device for an internal combustion engine in which an operating piston linked to an intake or exhaust valve is operated by hydraulic pressure from a pump to control the opening and closing of the valve, one end is connected to the discharge port of the pump and the other end is connected to the operating piston. A first hydraulic oil supply passage opened on the inner wall of the mating cylinder is provided, a solenoid valve for controlling the opening and closing of the passage is provided in the first hydraulic oil supply passage, and the first hydraulic oil supply passage is closer to the cylinder than the solenoid valve of the first hydraulic oil supply passage. A second hydraulic oil supply passage branched from the part and opened in the inner wall of the cylinder so as to supply hydraulic pressure to the top surface of the working piston when the valve is fully closed is provided, and a boosting piston for increasing and transmitting hydraulic pressure is provided. provided in the second hydraulic oil supply passage, and an opening to the cylinder inner wall of the first hydraulic oil supply passage;
Hydraulic operation of an internal combustion engine, characterized in that the valve is closed by the working piston when the valve is fully closed, and is provided so that hydraulic pressure can be supplied to the top surface of the working piston when the working piston moves by a limited stroke at the initial stage of opening the valve. Valve device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58220053A JPS60113008A (en) | 1983-11-22 | 1983-11-22 | Hydraulically operated tappet valve device of internal- combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58220053A JPS60113008A (en) | 1983-11-22 | 1983-11-22 | Hydraulically operated tappet valve device of internal- combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60113008A JPS60113008A (en) | 1985-06-19 |
| JPH02523B2 true JPH02523B2 (en) | 1990-01-08 |
Family
ID=16745186
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58220053A Granted JPS60113008A (en) | 1983-11-22 | 1983-11-22 | Hydraulically operated tappet valve device of internal- combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60113008A (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS635697Y2 (en) * | 1985-04-04 | 1988-02-17 | ||
| CN85106639B (en) * | 1985-09-03 | 1988-08-03 | 第三军医大学野战外科研究所 | Instrument for blood vessel anastomosis |
| JPH0791969B2 (en) * | 1989-03-20 | 1995-10-09 | 川崎重工業株式会社 | Valve drive for internal combustion engine |
| AT403835B (en) * | 1994-07-29 | 1998-05-25 | Hoerbiger Ventilwerke Ag | DEVICE AND METHOD FOR INFLUENCING A VALVE |
| DE19852209A1 (en) * | 1998-11-12 | 2000-05-18 | Hydraulik Ring Gmbh | Valve control for intake and exhaust valves of internal combustion engines |
| ATE448387T1 (en) * | 2005-01-12 | 2009-11-15 | Volvo Lastvagnar Ab | DEVICE FOR AN COMBUSTION ENGINE |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5487321A (en) * | 1977-12-24 | 1979-07-11 | Mitsubishi Heavy Ind Ltd | Hydraulic valve drive equipment of internal combustion engine |
| JPS55101712A (en) * | 1979-01-26 | 1980-08-04 | Nissan Motor Co Ltd | Valve driving system for internal combustion engine |
-
1983
- 1983-11-22 JP JP58220053A patent/JPS60113008A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5487321A (en) * | 1977-12-24 | 1979-07-11 | Mitsubishi Heavy Ind Ltd | Hydraulic valve drive equipment of internal combustion engine |
| JPS55101712A (en) * | 1979-01-26 | 1980-08-04 | Nissan Motor Co Ltd | Valve driving system for internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60113008A (en) | 1985-06-19 |
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