JPS60113008A - Hydraulically operated tappet valve device of internal- combustion engine - Google Patents
Hydraulically operated tappet valve device of internal- combustion engineInfo
- Publication number
- JPS60113008A JPS60113008A JP58220053A JP22005383A JPS60113008A JP S60113008 A JPS60113008 A JP S60113008A JP 58220053 A JP58220053 A JP 58220053A JP 22005383 A JP22005383 A JP 22005383A JP S60113008 A JPS60113008 A JP S60113008A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- piston
- oil
- passage
- pressure
- 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.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 5
- 239000010720 hydraulic oil Substances 0.000 claims description 16
- 230000035939 shock Effects 0.000 abstract description 6
- 238000007599 discharging Methods 0.000 abstract 3
- 239000003921 oil Substances 0.000 description 13
- 230000000694 effects Effects 0.000 description 3
- 230000000116 mitigating effect Effects 0.000 description 2
- 108010033040 Histones Proteins 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000012530 fluid 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)
Abstract
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ｎ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８のロンドは排気弁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。又各亀磁弁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 the figure, the rond of the piston 8 that fits into the cylinder 2 formed in the device main body 1 is in contact with the upper end of the exhaust valve 4. A hydraulic oil supply passage 6 and a discharge passage 7 are opened in the hydraulic chamber 5 in the cylinder 2, and each passage 6.7 is connected to a solenoid valve 8.
．． It has 9. Further, each control 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全開けることによって油圧室５内の作動油全排出する
とＪ図示しない弁ばねによって弁４はピストン８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 fully opened to drain all the hydraulic oil in the hydraulic chamber 5.The valve spring (not shown) moves the valve 4 upward while pushing up the piston 8 and closes it. .
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
なえるようになって小さ々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, if the valve 4 is slightly opened, 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 amount of 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
期に必要な大きな刀で弁４を作動させる構成となってお
り、直径の大きなピストン３を動かす為に、作動油量が
多く必要となって油圧ポンプの容量を太きくしなけれは
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っている
ことから、油圧ポンプの駆動馬力を大キくシておく必要
がある。However, in the above-mentioned conventional example, the valve 4 is operated by a large blade necessary at the initial stage of opening the valve and thereafter, and a large amount of hydraulic oil is required to move the piston 3 with a large diameter. Therefore, the capacity of the hydraulic pump must be increased. Also, even in the early stages 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ｈ′り成）
次の事狛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。(H' Constituent of the Invention) This is a hydraulically operated valve train for an internal combustion engine which has the following essential requirements.
←）吸気、排気弁に連動する作動ピストンを設ける。←) Provide an operating piston that is linked to the intake and exhaust valves.
（１）） 作動ピストンを高圧作動油で制御する電磁弁
を設けて、適切な弁囲閉タイミングを得るようにする。(1)) Provide a solenoid valve that controls the operating piston with high-pressure hydraulic oil to obtain appropriate valve closing timing.
（（３） 上記電磁弁を介した高圧作動油で作動する倍
力用ピストンを設ける。((3) A booster piston is provided that is operated by high-pressure hydraulic oil via the above-mentioned solenoid valve.
（１）倍力用ピストンが弁開き始めの限られたストロー
ク間のみ作動ピストンに作用して作動ピストンを作動さ
せるようにする。(1) The booster piston acts on the actuating piston only during a limited stroke at the beginning of opening the valve to operate the actuating piston.
（実施例）
第２図において、シリンダヘッド２１内に設けられた排
気ボート２２（吸気ボートでもよい）を閉じる排気弁２
３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とシリンダヘット
２■との間に縮設された弁ばね１９によって、弁２３は
常時ボート２２を閉じる方向に弾性的に付勢されている
。(Example) In FIG. 2, an exhaust valve 2 that closes an exhaust boat 22 (an intake boat may also be used) provided in a cylinder head 21
3 integrally has a valve stem 24 extending upward. The valve 23 is always elastically biased in the direction to close the boat 22 by a valve spring 19 compressed between a spring receiver 18 provided at the upper end of the valve stem 24 and the cylinder head 2.
弁棒２４の上端は作動ピストン２５のピストンロッド２
６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、呈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８３が開閉自在に通路８
１内に突出している。絞り３０と電磁弁３２との間で通
路３１は分岐しておシ、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 connected to the piston rod 2 of the operating piston 25.
6, and the piston 25 is in contact with the lower end of the device body 27.
It is fitted into a cylinder 28 formed therein so as to be slidable in the vertical direction. A hydraulic chamber 29 is formed in the cylinder 28 above the piston 25, and a discharge passage 31 is opened at the upper end surface of the cylinder 29 via a throttle 30. The passage 31 has a solenoid valve 32 in the middle, and the valve body 83 can open and close freely.
It stands out within 1. The passage 31 branches between the throttle 30 and the electromagnetic valve 32, and the branch passage 34 opens on the side wall surface of the cylinder "28" slightly below the upper end surface of the piston 25.
シリンダ２８側壁面の分岐路３４の関口位置と略同一円
周上反対側には供給通路３５が開口しており、分岐路３
４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８７が開閉自在に通路３
５内に突出している。電磁弁８６と７９７２２８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１」シている。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ｉ ｔした小
径部４４とからな〃、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の下方に段部全弁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
設されたコイルはね４６によっ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ｎ
＋１上端部との間は通路４７ ＶＣよって連通している
。なお４８はシリンダ２８の逃し孔、４９はシリンダ４
１の逃し孔である。A supply passage 35 opens on the opposite side of the cylinder 28 side wall surface on the same circumference as the exit position of the branch passage 34.
4 and the passage 35 are constantly in communication via an annular groove 50 formed in the circumferential direction of the cylinder 28. The passage 35 has a solenoid valve 36 in the middle, and the valve body 87 can open and close freely.
It stands out within 5. The passage 35 branches between the solenoid valve 86 and 797228, and the branch passage 38 connects to the hydraulic chamber 42 above the large diameter cylinder 41 into which the booster piston 40 fits.
There is an opening 1. The boosting piston 40 consists of a large diameter part 43 forming a hydraulic chamber 42 and a small diameter part 44 formed integrally therewith.The large diameter part 43 is slidably fitted into the large diameter cylinder 41. At the same time, the small-diameter portion 44 is slidably fitted into a small-diameter cylinder 45 that is formed concentrically with the stepped portion below the large-diameter cylinder 41 . Further, the piston 40 is constantly urged upward by a coil spring 46 compressed between the stepped portion between the cylinders 41, 45 and the large diameter portion 43. The bottom surface of the small diameter cylinder 45 and the side wall n of the cylinder 28
+1 upper end portion is communicated with through a passage 47 VC. Note that 48 is the relief hole of the cylinder 28, and 49 is the cylinder 4.
This is the first escape hole.
供給通路３５の上手側は、途中にアキュムレータ５１を
有する油路５２に連結きノ１．ており、油路５２は作動
油供給システム５３の高圧曲用ポンプ５４に連通してい
る。ポンプ５４はエンジン５５によって駆動さｉするよ
うになっており、又オイルパン５６から作動油が供給さ
れるようになっている。オイルパン５６に（法油路５７
を介して、装置本体２７の排出通路８１からの作動油が
戻されるようになっている。The upper side of the supply passage 35 is connected to an oil passage 52 having an accumulator 51 in the middle. The oil passage 52 communicates with a high-pressure bending pump 54 of a hydraulic oil supply system 53. The pump 54 is driven by an engine 55, and hydraulic oil is supplied from an oil pan 56. Oil pan 56 (Hoyou Road 57)
Hydraulic oil from the discharge passage 81 of the device main body 27 is returned via.
エンジン５５にはクランク角ＩＫ二（位相）検出センサ
６１をはじめ、負荷状態、回転速度等ケ検知する種々の
センサ（図示せず）が膜島さｔしており、それらセンサ
による情報が電気的にコントロール装［６２内のマイク
ロコンピュータ６Ｂに入力されるようになっている。コ
ンピュータ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８２．８
５の電磁ソレノイド６４．６５に所定の電流を流すよう
罠なっている。The engine 55 includes a crank angle IK (phase) detection sensor 61 and various other sensors (not shown) that detect load conditions, rotational speed, etc., and information from these sensors is transmitted electrically. The information is input to the microcomputer 6B in the control device [62]. 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 controls the solenoid valves 82.8.
The trap is configured to cause a predetermined current to flow through the electromagnetic solenoids 64 and 65 of No. 5.
次に作動を説明する。排気弁２８ｖｉ−開く場合には、
まずコントロール装置６２からの指令にょシソレノイド
６５が通電されて作動し、電磁弁３６の弁本体３７が開
く。通路８５は作動ピストン２５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４ｏ
が下降するとシリンダ４５内の作動油が小径部４４によ
って押し出され、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 28vi,
First, the solenoid 65 is energized and activated according to a command from the control device 62, and the valve body 37 of the solenoid valve 36 opens. Since the passage 85 is closed by the actuating piston 25, hydraulic pressure is supplied to the hydraulic chamber 42, and the boosting piston 40
It acts on the upper surface of the large diameter portion 43 of. This allows piston 4o
When the cylinder 45 is lowered, the hydraulic oil in the cylinder 45 is pushed out by the small diameter portion 44, and hydraulic pressure is supplied to the hydraulic chamber 29 through the passage 47.
ここでピストン４０の大径部４８と小径部４４の各直径
’ｉＤ、（１とし、システム５８からの供給油圧ｔ”Ｐ
ｏとすると、油圧室２９に供給される油圧はＰｏＸ（Ｄ
／ｄ）となる。即ち（Ｄ／ｄ ）＞ １ テアルカら、
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, each diameter 'iD of the large diameter part 48 and small diameter part 44 of the piston 40 is assumed to be (1, and the supply oil pressure t''P from the system 58 is
o, the hydraulic pressure supplied to the hydraulic chamber 29 is PoX(D
/d). That is, (D/d) > 1 Tearuca et al.
The hydraulic pressure increased by (D/d) times is supplied to the hydraulic chamber 29.
油圧室２９に供給される高圧によってピストン２５が、
弁はね１９及び排気弁２８にかかる背圧に打ち勝ってわ
ずかに下降すると、排気弁２８は開いて排気ポート２２
側へ圧力が抜ける。従っ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に対して門口する。これによって油圧室２９
内の圧力はＰａに下り、その後は通路３５から直接供給
される作動油圧ＰＯによってピストン２５は弁２８が全
開位置となる迄下降音読ける。The high pressure supplied to the hydraulic chamber 29 causes the piston 25 to
When the valve spring 19 and the back pressure on the exhaust valve 28 are overcome and the exhaust valve 28 descends slightly, the exhaust valve 28 opens and the exhaust port 22 is opened.
Pressure is released to the side. Therefore, from this point 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 passage 35 and the branch passage 34 . As a result, the hydraulic chamber 29
The internal pressure drops to Pa, and then the piston 25 is moved downward by the working oil pressure PO directly supplied from the passage 35 until the valve 28 is at the fully open position.
閉弁時には、コントロール装置６２からの指令によって
電磁弁３６を閉じ、電磁弁３２を開ける。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.
これによって作動油は油路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
によっ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４ｏでは小径部４４にかかる油圧Ｐ°とコイルば
ね４６によってピストン４０が元に戻される。ここで供
給通路３５は、ピストン２５によって油圧室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。従って絞り３ｏ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４
ｏが上方に摺動して元の状態に復帰することになる。絞
シ８ｏは、ピストン２５が分岐路３４ｔｌ−閉じた後停
止する迄のショックを軟らげる役目を有しておυ、これ
に１つと排気弁２３はスムーズに着座する。As a result, the hydraulic oil passes through the oil passage 57 to the oil pan 56.
However, due to the resistance of the passage, the piston 25
will never return to normal. 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 boosting piston 4o, the piston 40 is returned to its original state by the oil 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 from the hydraulic chamber 29 by the piston 25 . Therefore, due to the effect of the throttle 3o, the pressure inside the small diameter cylinder 45 exceeds the pressure in the hydraulic chamber 42, so the piston 4
o will slide upward and return to its original state. The restrictor 8o has the role of softening the shock until the piston 25 stops after closing the branch passage 34tl, and one and the exhaust valve 23 are seated smoothly on this.
再ひ開弁動作を行なう場合には電磁弁３２を閉じ、電磁
弁３６を打び開けることによって上記開弁動作が再び行
なわれる。このように両電磁弁３２．３６の作動をコン
トロール装置６２によっ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 solenoid valve 32 is closed and the solenoid valve 36 is punched open, whereby the valve-opening operation is performed again. By controlling the operation of both electromagnetic valves 32 and 36 by the control device 62 in this manner, the valve opening and closing operations can be performed repeatedly.
なお倍力用ピストン４ｏ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
れは足りる。Note that the actuating piston 25 due to the action of the boosting piston 4o
The sliding stroke is long enough to relieve the back pressure of the exhaust valve.
（発明の効果）
倍力用ピストン４０が弁２３開き始めの限られたストロ
ーク間のみ作動ピストン２５に作用して作動ピストン２
５を作動させるようにしたので；（〜 作動ピストン２
５及びそのシリンダ２８を小径化できる。(Effect of the invention) The boosting piston 40 acts on the operating piston 25 only during a limited stroke when the valve 23 begins to open.
5 is activated; (~ Operating piston 2
5 and its cylinder 28 can be made smaller in diameter.
（ト）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。(g) Since the amount of hydraulic oil supplied is small, the capacity of the hydraulic pump 54 can be reduced.
（Ｑ） 作動油圧を低くすることかできることから、油
圧ポンプ５４の駆動馬力を小さくできる。(Q) Since the working oil pressure can be lowered, the driving horsepower of the hydraulic pump 54 can be reduced.
（Φ 従って油圧作動動弁装置全体を小型化できる。(Φ Thus, the entire hydraulically operated valve train can be downsized.
（別の実施例）
←）油圧ポンプ５４はエンジン５５によって駆動さｔＬ
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) ←) The hydraulic pump 54 is driven by the engine 55 tL
For example, an electric motor driven type may be adopted.
（ｂ） 油圧作動動弁装置本体２７として、第３図のよ
うな構成のものを採用してもよい。第３図において、弁
棒２４の上端は／Ｊ”ｌ径の作動ピストン７１のピスト
ンロッド７２下端に当接しておシ、ヒストン７１は装置
本体２７内に嵌合両足された円筒状シリンダ７３内に上
下方向摺動自在に嵌合している。シリンダ７８内上部に
は油圧室７４が形成されており、シリンダ７３上端部に
は段部７５ｖｉ−介してシリンダ大径部７６が形成され
、大径の倍力用ピストン７７が嵌合している。即ち油圧
室７４はシリンダ７Ｂと両ピストン７１，７７に囲まれ
て形成されている。シリンダ７８の中間部にはシリンダ
７８半径方向のボート７８が開口しておシ、ボート７８
は電磁弁７９の弁本体８０を介して排出通路８１に連通
している。又ボート７８は途中で分岐してバイパス通路
８２が形成されている。(b) As the hydraulically operated valve train main body 27, a structure as shown in FIG. 3 may be adopted. In FIG. 3, the upper end of the valve stem 24 is in contact with the lower end of the piston rod 72 of the working piston 71 with a diameter of /J"l, and the histone 71 is inside the cylindrical cylinder 73 which is fitted into the device main body 27. A hydraulic chamber 74 is formed in the upper part of the cylinder 78, and a cylinder large diameter part 76 is formed at the upper end of the cylinder 73 via a stepped part 75vi. A radial force boosting piston 77 is fitted.That is, the hydraulic chamber 74 is formed surrounded by the cylinder 7B and both pistons 71 and 77.A boat 78 in the radial direction of the cylinder 78 is fitted in the middle part of the cylinder 78. Boat 78 opened.
communicates with a discharge passage 81 via a valve body 80 of the solenoid valve 79. Further, the boat 78 branches in the middle to form a bypass passage 82.
一方供給通路８５は途中に電磁弁８６を有しその弁本体
８７が開閉自在に通路８５内に突出すると共に、ボール
状逆止弁８８を介して通路８５は倍力用ピストン７７の
上方に形成された油圧室８９に連通している。逆止弁８
８と電磁弁８６との間の通路８５には上記バイパス通路
８２が開口しており、油圧室８９とバイパス通路−８２
との間には絞り９０（小径通路）が形成されている。な
お逆止弁８８とピストン７７との間には逆止弁用ばね９
１が縮設されている。又シリンダ大径部７６の下部は逃
し孔９２．９８を介して外部に連通している。On the other hand, the supply passage 85 has a solenoid valve 86 in the middle, and its valve body 87 protrudes into the passage 85 so as to be openable and closable, and the passage 85 is formed above the boosting piston 77 via a ball-shaped check valve 88. It communicates with a hydraulic chamber 89. Check valve 8
The bypass passage 82 is opened in the passage 85 between the hydraulic chamber 89 and the solenoid valve 86, and the bypass passage 82 is connected to the hydraulic chamber 89 and the bypass passage 82.
A throttle 90 (small diameter passage) is formed between the two. Note that a check valve spring 9 is provided between the check valve 88 and the piston 77.
1 has been reduced. Further, the lower portion of the cylinder large diameter portion 76 communicates with the outside via relief holes 92,98.
次に作動を説明する。作動油供給通路８５には常時油圧
ＰＱがかかつており、開弁時には電磁弁８６が開き、逆
止弁８８を通って倍力用ピストン７７上に油圧がかかる
。同時に油圧は通路８２を通ってボート７８に供給され
るが、弁７９は閉じてお〃、油圧は逃げられない。従っ
て開弁初期には油圧が倍力用ピストン７７′のみに作用
し、大きな作用力で作動ピストン７１に押し下げること
によりわずかな開弁状態とする。Next, the operation will be explained. Hydraulic pressure PQ is always present in the hydraulic oil supply passage 85, and when the valve is opened, the solenoid valve 86 opens and the hydraulic pressure is applied to the boosting piston 77 through the check valve 88. At the same time, hydraulic pressure is supplied to boat 78 through passage 82, but valve 79 is closed and no hydraulic pressure can escape. Therefore, in the early stages of opening the valve, the hydraulic pressure acts only on the boosting piston 77', and by pushing down the actuating piston 71 with a large acting force, the valve is slightly opened.
ピストン７７が下降し続けると、ピストン７７自身が逃
し孔９２を塞ぐ。続いてボート７８が油圧室７４に対し
て開口して、ボート７８からの油圧がピストン７１の上
部にかがり、又倍力用ピストン７７は段部７５に当接す
る。これ以後は作動ビス）ｙ７１分だけの油量でピスト
ン７１が下降する。As the piston 77 continues to descend, the piston 77 itself closes the escape hole 92. Subsequently, the boat 78 opens to the hydraulic chamber 74, the hydraulic pressure from the boat 78 is applied to the upper part of the piston 71, and the booster piston 77 comes into contact with the stepped portion 75. After this, the piston 71 descends with the amount of oil corresponding to the operating screw (y71).
閉弁時には電磁弁８６を閉じ、電磁弁７９を開ける。こ
れによ勺作動油は通路８１から排出され、油圧が供給さ
れなくなるので、ピストン７１は弁ばね１９（第２図）
の力によって押し上けられる。When closing the valve, the solenoid valve 86 is closed and the solenoid valve 79 is opened. As a result, the hydraulic oil is discharged from the passage 81, and no oil pressure is supplied, so that the piston 71 is removed from the valve spring 19 (Fig. 2).
pushed up by the force of
この時ピストン７１は慣性力葡有するが、非着座時のシ
ョックはピストン７７によって緩和される。At this time, the piston 71 has an inertial force, but the shock when the seat is not seated is alleviated by the piston 77.
即ちばね９１によってピストン７７は下に下がっている
ので、ピストン７１が当接して押し上げ、これにより油
圧室８９内の作動油が絞り９０から排出される。この絞
り効果によって着座寸前でブレーキが効き、ショックが
緩和される。That is, since the piston 77 is lowered by the spring 91, the piston 71 comes into contact with the piston 77 and pushes it upward, whereby the hydraulic fluid in the hydraulic chamber 89 is discharged from the throttle 90. This throttling effect applies the brakes just before the driver is seated, mitigating the shock.
つまりピストン７７は■」弁初期には倍力機構として働
き、作動終了時にはショック緩和機構として働く。In other words, the piston 77 functions as a boosting mechanism during the initial stage of the valve operation, and functions as a shock mitigation mechanism at the end of the operation.
第１図は従来の油圧作！１ｉＩＩ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
、第３図は別の実施例の縦断面略図である。
２３・排気弁（吸気、排気弁の一例）、２５．７１・・
・作動ピストン、３２．８６．７９．８６・・・電磁弁
、４０．７７・・・倍力用ピストンFigure 1 shows conventional hydraulic operation! 1iIII vertical sectional view of the valve train,
FIG. 2 is a layout diagram of a hydraulically operated valve train according to the present invention, and FIG. 3 is a schematic vertical cross-sectional view of another embodiment. 23.Exhaust valve (an example of an intake/exhaust valve), 25.71...
・Operating piston, 32.86.79.86... Solenoid valve, 40.77... Boosting piston
Claims (1)
トンを高圧作動油で制御する電磁弁を設けて、適切な弁
開閉タイミングを得るようにした内燃機関の油圧作動動
弁装置において、上記電磁弁を介した高圧作動油で作動
する倍力用ピストンを設け、倍力用ピストンが弁開き始
めの限られたストローク間のみ作動ピストンに作用して
作動ピストンを作動させるようにしたことを特徴とする
内燃機関の油圧作動製弁装置。In a hydraulically operated valve train for an internal combustion engine, the solenoid valve is provided with an operating piston linked to intake and exhaust valves, and a solenoid valve that controls the operating piston with high-pressure hydraulic oil to obtain appropriate valve opening/closing timing. A booster piston operated by high-pressure hydraulic oil via the valve is provided, and the booster piston operates the operating piston by acting on the operating piston only during a limited stroke at the beginning of opening the valve. Hydraulically operated valve device for internal combustion engines.
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 true JPS60113008A (en) | 1985-06-19 |
| JPH02523B2 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) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62231649A (en) * | 1985-09-03 | 1987-10-12 | ディ−サンジュンイダ−シュエ・ワイケイマンジュ−スオ | Blood vessel anastomotic forcept |
| US4708141A (en) * | 1985-04-04 | 1987-11-24 | Takasago Medical Industry Co., Ltd. | Soluble suturing device for an intestine |
| JPH02248607A (en) * | 1989-03-20 | 1990-10-04 | Tech Res Assoc Highly Reliab Marine Propul Plant | Valve driving system of internal combustion engine |
| AT403835B (en) * | 1994-07-29 | 1998-05-25 | Hoerbiger Ventilwerke Ag | DEVICE AND METHOD FOR INFLUENCING A VALVE |
| EP1001143A2 (en) * | 1998-11-12 | 2000-05-17 | Hydraulik Ring GmbH | Valve control for intake and exhaust valves in internal combustion engines |
| JP2008527237A (en) * | 2005-01-12 | 2008-07-24 | ボルボ ラストバグナー アーベー | Equipment for internal combustion engines |
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 |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4708141A (en) * | 1985-04-04 | 1987-11-24 | Takasago Medical Industry Co., Ltd. | Soluble suturing device for an intestine |
| JPS62231649A (en) * | 1985-09-03 | 1987-10-12 | ディ−サンジュンイダ−シュエ・ワイケイマンジュ−スオ | Blood vessel anastomotic forcept |
| JPH0463695B2 (en) * | 1985-09-03 | 1992-10-12 | Deiisanjunidaashue Waikeimanjuusuo | |
| JPH02248607A (en) * | 1989-03-20 | 1990-10-04 | Tech Res Assoc Highly Reliab Marine Propul Plant | Valve driving system of internal combustion engine |
| AT403835B (en) * | 1994-07-29 | 1998-05-25 | Hoerbiger Ventilwerke Ag | DEVICE AND METHOD FOR INFLUENCING A VALVE |
| EP1001143A2 (en) * | 1998-11-12 | 2000-05-17 | Hydraulik Ring GmbH | Valve control for intake and exhaust valves in internal combustion engines |
| EP1001143A3 (en) * | 1998-11-12 | 2000-12-06 | Hydraulik Ring GmbH | Valve control for intake and exhaust valves in internal combustion engines |
| JP2008527237A (en) * | 2005-01-12 | 2008-07-24 | ボルボ ラストバグナー アーベー | Equipment for internal combustion engines |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH02523B2 (en) | 1990-01-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102242676B (en) | Variable valve actuation and engine braking | |
| EP1549831B1 (en) | Lost motion system and method for fixed-time valve actuation | |
| KR100634641B1 (en) | Applied lost motion for optimization of fixed timed engine brake systems | |
| US7793624B2 (en) | Engine brake apparatus | |
| JP2809354B2 (en) | Valve train for internal combustion engine | |
| EP0828061A1 (en) | Exhaust pulse boosted engine compression braking method | |
| JP2005516144A (en) | Engine valve actuation system and method using reduced pressure common rail and dedicated engine valve | |
| JPH10504082A (en) | Engine compression type brake device and method | |
| JPH10504084A (en) | Engine compression type brake device and method | |
| JP2000508740A (en) | Engine braking and / or exhaust during exhaust gas recirculation | |
| JPH03233116A (en) | Valve control device for gas replacement valve in internal combustion engine | |
| JP4897216B2 (en) | Internal combustion engine equipment | |
| JPH04224215A (en) | Engine brake for air compression type internal combustion engine | |
| US5647319A (en) | Decompression braking apparatus for diesel engine | |
| EP2868876A1 (en) | Integrated engine brake | |
| JPS60113008A (en) | Hydraulically operated tappet valve device of internal- combustion engine | |
| US6321717B1 (en) | Double-lift exhaust pulse boosted engine compression braking method | |
| JP4290563B2 (en) | Device for controlling a gas exchange valve | |
| US6644271B1 (en) | Engine braking system | |
| JPS60259713A (en) | Electronic control system hydraulic valve unit for internal-combustion engine | |
| US20020069853A1 (en) | Compression brake actuation system and method | |
| US6516775B2 (en) | Compression brake actuation system and method | |
| JPS60169614A (en) | Open/close timing controller for exhaust valve | |
| JPS603436A (en) | Exhaust brake system | |
| JPS59113228A (en) | Fluid operating mechanism |