JP2527268Y2 - Valve train for internal combustion engine - Google Patents
Valve train for internal combustion engineInfo
- Publication number
- JP2527268Y2 JP2527268Y2 JP1990090676U JP9067690U JP2527268Y2 JP 2527268 Y2 JP2527268 Y2 JP 2527268Y2 JP 1990090676 U JP1990090676 U JP 1990090676U JP 9067690 U JP9067690 U JP 9067690U JP 2527268 Y2 JP2527268 Y2 JP 2527268Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- pressure oil
- chamber
- accumulator
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
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
-
- 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
- F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
- F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Fluid-Driven Valves (AREA)
Description
【考案の詳細な説明】 〔産業上の利用分野〕 本考案はアクチュエータにより吸排気弁の開閉を行う
形式の内燃機関の動弁装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a valve train for an internal combustion engine in which an intake and exhaust valve is opened and closed by an actuator.
従来の蓄圧式動弁装置の一例を第3図に示す。その構
成は、01が油圧の管制弁本体で、5孔を有する。02が管
制弁で、それはカム03及びローラ04によりエンジンのク
ランク軸と同期して駆動される。シリンダカバー05に取
り付けられたアクチュエータ06の内側で、吸排気弁07が
開閉する。アクチュエータ06は上部油圧室06aと下部油
圧室06bを有し、それぞれ配管08、09により管制弁01に
つながっている。010はフィルタ、ポンプで構成された
油圧の供給装置で、010aは油タンクである。011が蓄圧
器で、所要の一定油圧に保たれ管制弁01に管路で連通さ
れている。FIG. 3 shows an example of a conventional pressure accumulating valve train. In the configuration, 01 is a hydraulic control valve body and has five holes. 02 is a control valve, which is driven by a cam 03 and a roller 04 in synchronization with the crankshaft of the engine. The intake / exhaust valve 07 opens and closes inside the actuator 06 attached to the cylinder cover 05. The actuator 06 has an upper hydraulic chamber 06a and a lower hydraulic chamber 06b, and is connected to a control valve 01 by pipings 08 and 09, respectively. 010 is an oil pressure supply device composed of a filter and a pump, and 010a is an oil tank. Reference numeral 011 denotes an accumulator, which is maintained at a required constant oil pressure and is connected to the control valve 01 via a pipeline.
次に作用について述べる。第3図は、ローラ04がカム
03の基円上にあり、吸排気弁が閉じているときの状態
で、蓄圧器011からの作動油は、管制弁01から配管09を
とおり、アクチュエータの下部油圧室06bに作用し、吸
排気弁07を上に押し上げている。このとき上部油圧室06
aの油は、配管08、管制弁01を経て、油圧源010のタンク
010aに導かれ戻っている。Next, the operation will be described. FIG. 3 shows that the roller 04 is a cam.
Hydraulic oil from the pressure accumulator 011 passes through the pipe 09 from the control valve 01 and acts on the lower hydraulic chamber 06b of the actuator when the intake / exhaust valve is on the base circle of 03 and the intake / exhaust valve is closed. Pushing valve 07 up. At this time, the upper hydraulic chamber 06
The oil of a passes through piping 08, control valve 01, and the tank of hydraulic source 010
I am led back to 010a.
カム03が回転しローラ04がリフトすると、アクチュエ
ータ06の下部油圧室06bの油は、配管09、管制弁01を経
てタンク010aに排出されると同時に、蓄圧器011の高圧
作動油は、管制弁01、配管08を経て、アクチュエータ06
の上部油圧室06aに導かれ、吸排気弁07を押し下げ、開
弁させる。さらにカム03が回転しカムのリフトが減少し
基円に達すると、上部油圧室06aの油がタンク010aへ抜
け、蓄圧器011の作動油が下部油圧室06bに作用して、吸
排気弁07は上方へ上げられ閉じることになる。When the cam 03 rotates and the roller 04 lifts, the oil in the lower hydraulic chamber 06b of the actuator 06 is discharged to the tank 010a via the pipe 09 and the control valve 01, and at the same time, the high-pressure hydraulic oil of the accumulator 011 is controlled by the control valve. 01, piping 08, actuator 06
To the upper hydraulic chamber 06a to push down the intake / exhaust valve 07 to open it. When the cam 03 further rotates and the lift of the cam decreases to reach the base circle, the oil in the upper hydraulic chamber 06a escapes to the tank 010a, and the operating oil of the pressure accumulator 011 acts on the lower hydraulic chamber 06b, and the intake and exhaust valves 07 Will be raised and closed.
前述の従来技術には次のような問題点がある。 The above-mentioned prior art has the following problems.
管制弁01が5孔を有し、構造が複雑であると同時に、
吸排気弁を開、閉するに必要な油量を管制弁部でも流す
必要があり、油圧装置が大形のものとなる。The control valve 01 has 5 holes and the structure is complicated,
The amount of oil required to open and close the intake / exhaust valve must also flow through the control valve, and the hydraulic device becomes large.
又、高圧油で弁の開、閉とも行うための配管08、09を
2本有し、アクチュエータの構造も複雑であり、高圧油
の消費量が多く、そのための動力を多く要する。Further, it has two pipes 08 and 09 for opening and closing the valve with high-pressure oil, has a complicated actuator structure, consumes a large amount of high-pressure oil, and requires much power.
さらに管制弁01がカム03により駆動され、吸排気弁の
開閉時期が自由に変えられない。Further, the control valve 01 is driven by the cam 03, and the opening / closing timing of the intake / exhaust valve cannot be freely changed.
(1)高圧の作動油は、吸排気弁の開弁のみに使用し、
閉弁は、吸排気弁のリフトに伴いばねに蓄えられたばね
力により行う構造とする。(1) High-pressure hydraulic oil is used only for opening and closing the intake and exhaust valves.
The valve is closed by the spring force stored in the spring with the lift of the intake / exhaust valve.
管制弁を2個と、ロジック弁2個を設け、特に低速機
関において吸排気弁の開弁時間が長いためこの期間中1
個の電磁弁で作動させておくと電磁弁コイルの過熱で不
安定となるのを防止するため2個用いることで開弁の瞬
間と閉弁の瞬間にそれぞれ電磁弁を作用させることで安
定した作動と耐久性を確保する。管制弁は電気的に駆動
され、蓄圧器からロジック弁大径部への油圧の作用を管
制するのみとし、排気弁の開弁に要する油は、蓄圧器か
ら1個のロジック弁、1本の高圧配管を介して、動弁ア
クチュエータ内シリンダのピストンに作用させるように
する。Two control valves and two logic valves are provided.
If two solenoid valves are used, the two valves are used to prevent instability due to overheating of the solenoid valve coil. Ensuring operation and durability. The control valve is electrically driven and only controls the action of hydraulic pressure from the pressure accumulator to the large-diameter portion of the logic valve. The oil required to open the exhaust valve requires one logic valve and one valve from the pressure accumulator. The high-pressure pipe acts on the piston of the cylinder in the valve actuator.
また、2個のロジック弁の小径側は、連通しており、
閉弁時には他方のロジック弁を開け、シリンダ内及び高
圧管内の油圧を解放するようにする。Also, the small diameter sides of the two logic valves are in communication,
When the valve is closed, the other logic valve is opened to release the hydraulic pressure in the cylinder and the high-pressure pipe.
(2)上記の手段を加えて、更に蓄圧器と開側ロジック
弁との間に、同開側ロジック弁側に開く逆止弁を配置す
る。(2) In addition to the above means, a check valve that opens on the side of the open-side logic valve is further disposed between the accumulator and the open-side logic valve.
(1)蓄圧器に蓄えられた高圧の作動油は、電気的に任
意の時期に駆動される開側管制弁により開側ロジック弁
が開き動弁アクチュエータ内シリンダのピストンに作用
し、吸排気弁を押し下げた後、閉側管制弁はもどり開側
ロジック弁が閉じる。吸排気弁は油圧により開弁をつづ
けるが、排気弁といっしょに動くエアピストンによる空
気の圧縮力が閉弁方向の力として働き、油圧とのバラン
スで適当なリフトに保持される。機関に要する吸排気が
なされると、閉側管制弁により、閉側ロジック弁が開き
油圧が解放されるため、エアばねにより吸排気弁は閉じ
られる。(1) The high-pressure hydraulic oil stored in the pressure accumulator opens the open-side logic valve by the open-side control valve that is electrically driven at an arbitrary timing, and acts on the piston of the cylinder in the valve-operating actuator, thereby causing the intake and exhaust valves to operate. After the pressure is depressed, the closed control valve returns and the open logic valve closes. The intake and exhaust valves continue to be opened by hydraulic pressure, but the compression force of the air by the air piston that moves together with the exhaust valve acts as a force in the valve closing direction, and is held at an appropriate lift in balance with the hydraulic pressure. When the intake and exhaust required for the engine are performed, the close-side control valve opens the close-side logic valve and releases the hydraulic pressure, so that the intake and exhaust valves are closed by the air spring.
このサイクルが繰り返される。 This cycle is repeated.
(2)蓄圧器より動弁アクチュエータに至る高圧配管に
油圧変動が起こり、高圧の圧力波がもどって来たとき、
逆止弁が閉じ、高圧油の作用系が蓄圧器と連通すること
がない。このためこの部分は閉止端として作動し、剛性
をもつ。したがって吸排気弁がもどろうとして油をおし
もどしても高圧となり、吸排気弁の大きな動きはなくな
る。(2) When the hydraulic pressure fluctuates in the high-pressure pipe from the pressure accumulator to the valve operating actuator, and the high-pressure pressure wave returns,
The check valve closes and the high pressure oil working system does not communicate with the accumulator. For this reason, this part operates as a closed end and is rigid. Therefore, even if the intake / exhaust valve tries to return and returns the oil, the pressure becomes high and the intake / exhaust valve does not largely move.
本考案の実施例を第1図について説明する。 An embodiment of the present invention will be described with reference to FIG.
1はシリンダカバー、2は吸排気弁、3は空気溜め、
4は逆止弁である。5は空気ピストンで、吸排気弁2と
同時に空気シリンダ6内を滑動する。7は動弁アクチュ
エータ本体、8は油圧シリンダ、9は作動ピストンで、
8aは上部油圧室、8bは下部油圧室である。1 is a cylinder cover, 2 is an intake and exhaust valve, 3 is an air reservoir,
4 is a check valve. Reference numeral 5 denotes an air piston, which slides in the air cylinder 6 simultaneously with the intake / exhaust valve 2. 7 is a valve actuator main body, 8 is a hydraulic cylinder, 9 is a working piston,
8a is an upper hydraulic chamber, and 8b is a lower hydraulic chamber.
10は高圧管、11は開側ロジック弁で該開側ロジック弁
11は蓄圧器16及び作動ピストン9の上部油圧室8aに接続
する接続室11aと蓄圧器16の圧油が給排される圧油室11b
と、接続室11aと圧油室11bとを区別するとともに圧油室
11bに圧油が供給されたとき蓄圧器16と圧油室8aとの連
通を接続室11a内で遮断する弁体11cとよりなる。12は、
開側ロジック弁油路で、蓄圧器16につながっている。13
は開側スプール管制弁で、図示しないコントローラによ
り機関のクランク回転と同期して駆動される。14は閉側
ロジック弁で、該閉側ロジック弁14は油タンク19と接続
する接続室14aと蓄圧器16の圧油が給排される圧油室14b
と、接続室14aと圧油室14bとを区別する弁体14cとより
なる。15は閉側スプール管制弁で開側スプール管制弁13
と同じように図示しないコントローラにより駆動され、
かつ3口の管制弁である。16は蓄圧器、17は油圧源装置
で、高圧油を供給するものであり、ポンプ、フィルタか
ら構成されている。18は低圧の油圧源装置で、管路18a
により動弁アクチュエータ7に連通している。19は油タ
ンク、20は開側ロジック弁と閉側ロジック弁をつなぐ連
通油路、21は開側ロジック弁の大径側と開側スプール管
制弁とをつなぐ油路、22は開側スプール管制弁13と蓄圧
器16とをつなく油路、23は閉側ロジック弁14の大径側と
閉側スプール管制弁15とをつなぐ油路、24は閉側スプー
ル管制弁15と蓄圧器16とをつなぐ油路である。10 is a high pressure pipe, 11 is an open side logic valve, and the open side logic valve
Reference numeral 11 denotes a connection chamber 11a connected to the accumulator 16 and the upper hydraulic chamber 8a of the working piston 9, and a pressure oil chamber 11b to which the pressure oil of the accumulator 16 is supplied and discharged.
And the connection chamber 11a and the pressure oil chamber 11b
When the pressure oil is supplied to 11b, it is provided with a valve body 11c which shuts off the communication between the pressure accumulator 16 and the pressure oil chamber 8a in the connection chamber 11a. 12 is
The open side logic valve oil passage is connected to the pressure accumulator 16. 13
Is an open spool control valve, which is driven by a controller (not shown) in synchronization with the crank rotation of the engine. Reference numeral 14 denotes a closing-side logic valve. The closing-side logic valve 14 includes a connection chamber 14a connected to the oil tank 19 and a pressure oil chamber 14b through which pressure oil of the accumulator 16 is supplied and discharged.
And a valve element 14c for distinguishing between the connection chamber 14a and the pressure oil chamber 14b. 15 is a closed spool control valve and 13 is an open spool control valve.
Driven by a controller not shown in the same way as
It is a three-port control valve. Reference numeral 16 denotes a pressure accumulator, and reference numeral 17 denotes a hydraulic pressure source device for supplying high-pressure oil, and is composed of a pump and a filter. 18 is a low-pressure hydraulic power source device,
Thus, it is in communication with the valve operating actuator 7. 19 is an oil tank, 20 is a communication oil path connecting the open side logic valve and the close side logic valve, 21 is an oil path connecting the large diameter side of the open side logic valve to the open side spool control valve, and 22 is an open side spool control. An oil passage connecting the valve 13 and the pressure accumulator 16, an oil passage 23 connecting the large-diameter side of the close-side logic valve 14 and the close-side spool control valve 15, a reference numeral 24 indicating a close-side spool control valve 15 and the accumulator 16 It is an oil channel that connects
25は閉側ロジック弁14から油タンク19への排油管、26
はスプール管制弁13、15からの排油管である。101は蓄
圧器16と開側ロジック弁11との間に、同開側ロジック弁
側に開く逆止弁である。25 is an oil drain pipe from the closing logic valve 14 to the oil tank 19, 26
Is an oil drain pipe from the spool control valves 13 and 15. A check valve 101 is provided between the accumulator 16 and the open-side logic valve 11 and opens toward the open-side logic valve.
又、このスプール管制弁13、15は3口の管制弁で、P
ポート、Cポート、Tポートをもつもので電磁駆動であ
る。The spool control valves 13 and 15 are three-port control valves.
It has a port, a C port and a T port and is electromagnetically driven.
次に、本装置の動作について説明する。 Next, the operation of the present apparatus will be described.
第1図は、空気溜め3の空気圧が空気ピストン5の下
部に作用し、吸排気弁2が閉じている状態である。FIG. 1 shows a state in which the air pressure in the air reservoir 3 acts on the lower part of the air piston 5 and the intake / exhaust valve 2 is closed.
このとき、開側および閉側のスプール管制弁13、15
は、蓄圧器16からの油圧を開、閉側ロジック弁11、14の
大径側に作用させ、ロジック弁11、14は閉じている。At this time, the open and closed spool control valves 13, 15
Causes the hydraulic pressure from the accumulator 16 to act on the large-diameter sides of the open and closed logic valves 11, 14, and the logic valves 11, 14 are closed.
吸排気弁2の開弁時期になると、図示しない機関と同
期して発せられるトリガー信号と機関の運転状態によ
り、コンピュータにより判断された適当な時期に開側ス
プール管制弁13が駆動される。同管制弁13が作動すると
油路22は閉じられ、油路21が排油管26に通じてロジック
弁大径側の油圧が抜けるため、ロジック弁11が開き、蓄
圧器16の油圧は、油路12aから逆止弁101をおしあげ、油
路12b高圧管10から動弁アクチュエータ内の油圧シリン
ダ8の上部油圧室8aに作用する。この油圧により、油圧
ピストン9を押し下げ吸排気弁2が開かれる。When the intake / exhaust valve 2 is opened, the open spool control valve 13 is driven at an appropriate time determined by a computer based on a trigger signal generated in synchronization with an engine (not shown) and the operating state of the engine. When the control valve 13 is operated, the oil passage 22 is closed, and the oil passage 21 communicates with the oil drain pipe 26 to release the hydraulic pressure on the large diameter side of the logic valve. The check valve 101 is raised from 12a and acts on the upper hydraulic chamber 8a of the hydraulic cylinder 8 in the valve actuator from the oil passage 12b and the high pressure pipe 10. The hydraulic pressure pushes down the hydraulic piston 9 to open the intake / exhaust valve 2.
このとき、空気シリンダ6内の空気は圧縮され、上向
きの力として作用するが、油圧とのバランス点まで、吸
排気弁はリフトする。At this time, the air in the air cylinder 6 is compressed and acts as an upward force, but the intake / exhaust valve lifts up to the balance point with the hydraulic pressure.
その後、開側管制弁13がもどされ、蓄圧器16の油圧が
ロジック弁11の大径部に作用しロジック弁11は閉じる。Thereafter, the open-side control valve 13 is returned, and the hydraulic pressure of the accumulator 16 acts on the large-diameter portion of the logic valve 11, so that the logic valve 11 closes.
ロジック弁11が閉じた後、高圧管10内の油圧変動でロ
ジック弁11が開いたとしても、逆止弁101が閉じている
ため、油圧シリンダ8の上部油圧室8aから高圧管10、逆
止弁101までは閉ざされた系となり、圧力変動もそれ程
大きくなく、吸排気弁2のリフトの変動も小さい。After the logic valve 11 is closed, even if the logic valve 11 is opened due to a change in hydraulic pressure in the high-pressure pipe 10, the check valve 101 is closed. The system is closed up to the valve 101, the pressure fluctuation is not so large, and the fluctuation of the lift of the intake / exhaust valve 2 is small.
次に実施例に記載した装置の吸排気弁リフト及び油圧
に関する特性を第2図に示す。Next, FIG. 2 shows characteristics of intake and exhaust valve lifts and hydraulic pressures of the apparatus described in the embodiment.
同図において、Aは吸排気弁リフト、Bは上部油圧室
8aの入口部の高圧管10での圧力、Cはロジック弁の連通
油路20での圧力である。In the figure, A is an intake / exhaust valve lift, and B is an upper hydraulic chamber.
8a is the pressure in the high pressure pipe 10 at the inlet, and C is the pressure in the communication oil passage 20 of the logic valve.
同図にみられるように、吸排気弁2がもどろうとする
と油圧が上がり、変位が抑制される。そこで、開弁中の
吸排気弁リフトの変動が小さくなる。As can be seen from the figure, when the intake / exhaust valve 2 tries to return, the hydraulic pressure rises and the displacement is suppressed. Therefore, the fluctuation of the intake / exhaust valve lift during valve opening is reduced.
次に、機関に必要な吸排気が完了すると、閉側スプー
ル管制弁15が駆動され、油路24が閉じられると同時に油
路23と排油管26がつながり、ロジック弁14の大径側の油
圧が抜けるので、ロジック弁14が開き、上部油圧室8aに
作用していた油圧は、高圧管10、連通油路20から排油管
25へと抜け、油圧の作用力がなくなる。すると、空気ピ
ストンに作用している空気圧縮力により、吸排気弁2が
閉じる。このとき下部油圧室8bには、低圧油圧源18から
油が補給され、空洞の発生もなく、安定した状態で作動
ピストン9が上昇位置に復帰する。Next, when the intake and exhaust required for the engine are completed, the closing-side spool control valve 15 is driven, and the oil passage 24 is closed, and at the same time, the oil passage 23 and the oil drain pipe 26 are connected, and the hydraulic pressure on the large-diameter side of the logic valve 14 is The logic valve 14 opens, and the hydraulic pressure acting on the upper hydraulic chamber 8a is released from the high-pressure pipe 10 and the communication oil passage 20 to the oil discharge pipe.
25, the hydraulic force is lost. Then, the intake / exhaust valve 2 is closed by the air compression force acting on the air piston. At this time, the lower hydraulic chamber 8b is supplied with oil from the low-pressure hydraulic power source 18, and the working piston 9 returns to the raised position in a stable state without a cavity.
本考案は作動油を加圧して蓄える油圧源と蓄圧器とを
有し、蓄圧器の作動油を制御して吸排気弁を駆動する内
燃機関の動弁装置において、吸排気弁駆動用ピストンの
上部に連通した高圧油路を開閉する2個の互いに連通し
たロジック弁と、前記2個のロジック弁の開閉を制御す
る2個の電磁駆動のスプール管制弁とを具え、前記ロジ
ック弁を開閉する管制油圧と前記吸排気弁を開弁駆動す
る作動油とを高圧の蓄圧器から供給し、前記吸排気弁駆
動用ピストンの開弁のリフトに伴い蓄えられたばね力に
よって吸排気弁を閉弁する構成と蓄圧器と開側ロジック
弁との間に同開側ロジック弁側に開く逆止弁を設けた構
成としたことにより、次の効果を有する。The present invention has a hydraulic pressure source and a pressure accumulator that pressurizes and stores hydraulic oil, and in a valve operating device for an internal combustion engine that controls the hydraulic oil of the pressure accumulator to drive an intake / exhaust valve. It comprises two mutually connected logic valves for opening and closing a high-pressure oil passage connected to the upper part, and two electromagnetically driven spool control valves for controlling opening and closing of the two logic valves, and opens and closes the logic valves. A control oil pressure and hydraulic oil for driving the intake and exhaust valves to open are supplied from a high-pressure accumulator, and the intake and exhaust valves are closed by the spring force stored with the lift of the opening of the intake and exhaust valve driving piston. The configuration and the configuration in which the check valve that opens on the side of the open-side logic valve is provided between the accumulator and the open-side logic valve have the following effects.
(1)ロジック弁とこれを制御する電磁駆動のスプール
に管制弁とを2個設けることで開弁の瞬間と閉弁の瞬間
にそれぞれ電磁弁を作用させることで安定した作動と耐
久性が確保される。(1) Stable operation and durability are ensured by providing two logic valves and a control valve on the electromagnetically driven spool that controls the logic valves so that the solenoid valves act at the moment of opening and the moment of closing, respectively. Is done.
(2)機関にとって、最適な吸排気弁の開閉弁特性を得
ることができるので、低燃費の高性能な機関となる。(2) Since the engine can obtain the optimal opening / closing valve characteristics of the intake / exhaust valve, the engine becomes a high-performance engine with low fuel consumption.
(3)弁駆動のための高圧油の消費も少ないため、油圧
源を小さく設計でき、安価になる。また消費動力も少な
く、更に低燃費となる。(3) Since the consumption of high-pressure oil for driving the valve is small, the hydraulic source can be designed to be small and inexpensive. Also, the power consumption is small, and the fuel consumption is further reduced.
(4)管制弁部での油量が少なくてすむので、コンパク
トな管制弁となり、信頼性、耐久性の良好な装置を実現
できる。(4) Since the amount of oil in the control valve section can be reduced, a compact control valve can be realized, and a device having good reliability and durability can be realized.
(5)逆止弁により吸排気弁がリフト後に変動がなくな
り、安定した吸排気性能が得られる。(5) The check valve eliminates fluctuations of the intake / exhaust valve after the lift, so that stable intake / exhaust performance can be obtained.
その結果機関の性能も安定し、良好な運転状態を維持
できる。As a result, the performance of the engine is also stabilized, and a good operating state can be maintained.
第1図は本考案の実施例に係る動弁装置の系統図、第2
図は同上の弁リフト、油圧の特性図、第3図は従来の蓄
圧動弁装置の系統図である。 2…吸排気弁、5…空気ピストン、6…空気シリンダ、
9…作動ピストン、11…開側ロジック弁、13…開側スプ
ール管制弁、14…閉側ロジック弁、15…閉側スプール管
制弁、16…蓄圧器、17…油圧源、101…逆止弁。FIG. 1 is a system diagram of a valve gear according to an embodiment of the present invention.
FIG. 3 is a characteristic diagram of the valve lift and the hydraulic pressure in the above, and FIG. 3 is a system diagram of a conventional pressure accumulating valve device. 2 ... intake and exhaust valves, 5 ... air piston, 6 ... air cylinder,
9 ... working piston, 11 ... open side logic valve, 13 ... open side spool control valve, 14 ... closed side logic valve, 15 ... closed side spool control valve, 16 ... accumulator, 17 ... hydraulic power source, 101 ... check valve .
フロントページの続き (72)考案者 国本 悦夫 長崎県長崎市飽の浦町1番1号 三菱重 工業株式会社長崎研究所内 (72)考案者 入江 泰隆 神奈川県横浜市中区錦町12番地 三菱重 工業株式会社横浜製作所内 (56)参考文献 特開 平2−248607(JP,A)Continued on the front page (72) Etsuo Kunimoto 1-1, Akunoura-cho, Nagasaki-shi, Nagasaki Prefecture Mitsubishi Heavy Industries, Ltd. Nagasaki Research Laboratory (72) Inventor Yasutaka Irie 12 Nishikicho, Naka-ku, Yokohama-shi, Kanagawa Prefecture Mitsubishi Heavy Industries, Ltd. (56) References JP-A-2-248607 (JP, A)
Claims (1)
2と、上下方向に摺動自在に支持されるとともに吸排気
弁2の上端部に当接し上部油圧室8aに蓄圧器16の圧油が
供給されることにより吸排気弁2を下方に押し下げ開弁
させる作動ピストン9と、吸排気弁2に取り付けられ外
部から供給される高圧流体により上方に付勢されること
により吸排気弁2を閉弁する空気ピストン5と、蓄圧器
16および作動ピストン9の上部油圧室8aと接続する接続
室11a、蓄圧器16の圧油が給排される圧油室11b、接続室
11aと圧油室11bとを区分するとともに圧油室11bに圧油
が供給されたとき蓄圧器16と圧油室8aとの連通を接続室
11a内で遮断する弁体11cよりなる開側ロジック弁11と、
所望のタイミングで蓄圧器16および油タンク19と接続・
遮断され圧油室11bに圧油を給排する電磁駆動の開側ス
プール管制弁13と、油タンク19と接続する接続室14a、
蓄圧器16の圧油が給排される圧油室14b,接続室14aと圧
油室14bとを区分する弁体14cよりなる閉側ロジック弁14
と、所望のタイミングで蓄圧器16および油タンク19と接
続・遮断され圧油室14bに圧油を給排する電磁駆動の閉
側スプール管制弁15と、圧油室11bに圧油が供給された
とき弁体11cにより蓄圧器16との連通が遮断される接続
室11aの部位と圧油室14bに圧油が供給されたとき弁体14
cにより油タンク19との連通が遮断される接続室14aの部
位とを連通する連通油路20と、蓄圧器16と開側ロジック
弁11との間に、開側ロジック弁側に開く逆止弁101とを
具備してなることを特徴とする内燃機関の動弁装置。1. An intake / exhaust valve 2 slidably supported in a vertical direction, and a pressure accumulator 16 slidably supported in a vertical direction and abutting on an upper end of the intake / exhaust valve 2 and in an upper hydraulic chamber 8a. A working piston 9 which pushes down and opens the intake / exhaust valve 2 by supplying the pressure oil, and an intake / exhaust system which is attached to the intake / exhaust valve 2 and is urged upward by a high-pressure fluid supplied from the outside. An air piston 5 for closing the valve 2 and an accumulator
16 and a connection chamber 11a connected to the upper hydraulic chamber 8a of the working piston 9; a pressure oil chamber 11b for supplying and discharging the pressure oil of the accumulator 16;
11a and the pressure oil chamber 11b are separated from each other, and the communication between the pressure accumulator 16 and the pressure oil chamber 8a is established when the pressure oil is supplied to the pressure oil chamber 11b.
An open-side logic valve 11 comprising a valve body 11c that shuts off within 11a,
Connect to accumulator 16 and oil tank 19 at desired timing
An electromagnetically driven open-side spool control valve 13 that shuts off and supplies pressure oil to and from the pressure oil chamber 11b, and a connection chamber 14a that connects to an oil tank 19,
A closed-side logic valve 14 comprising a pressure oil chamber 14b to which the pressure oil of the accumulator 16 is supplied / discharged, and a valve body 14c for separating the connection chamber 14a from the pressure oil chamber 14b.
At the desired timing, an electromagnetically driven closed spool control valve 15 that is connected and disconnected from the pressure accumulator 16 and the oil tank 19 and supplies and discharges pressure oil to and from the pressure oil chamber 14b, and pressure oil is supplied to the pressure oil chamber 11b When pressure oil is supplied to the portion of the connection chamber 11a where the communication with the pressure accumulator 16 is interrupted by the valve body 11c and the pressure oil chamber 14b
A check valve that opens to the open-side logic valve side between the communication oil passage 20 that communicates with a portion of the connection chamber 14a where communication with the oil tank 19 is interrupted by c, and the pressure accumulator 16 and the open-side logic valve 11 A valve train for an internal combustion engine, comprising: a valve 101.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1990090676U JP2527268Y2 (en) | 1990-05-11 | 1990-08-31 | Valve train for internal combustion engine |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2-120073 | 1990-05-11 | ||
JP12007390 | 1990-05-11 | ||
JP1990090676U JP2527268Y2 (en) | 1990-05-11 | 1990-08-31 | Valve train for internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0444408U JPH0444408U (en) | 1992-04-15 |
JP2527268Y2 true JP2527268Y2 (en) | 1997-02-26 |
Family
ID=14777233
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP1990090676U Expired - Fee Related JP2527268Y2 (en) | 1990-05-11 | 1990-08-31 | Valve train for internal combustion engine |
JP2257125A Expired - Lifetime JP2809354B2 (en) | 1990-05-11 | 1990-09-28 | Valve train for internal combustion engine |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2257125A Expired - Lifetime JP2809354B2 (en) | 1990-05-11 | 1990-09-28 | Valve train for internal combustion engine |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0455937B1 (en) |
JP (2) | JP2527268Y2 (en) |
KR (1) | KR940010284B1 (en) |
DE (2) | DE455937T1 (en) |
DK (1) | DK0455937T3 (en) |
Families Citing this family (25)
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DK170122B1 (en) * | 1993-06-04 | 1995-05-29 | Man B & W Diesel Gmbh | Large two stroke internal combustion engine |
US5410994A (en) * | 1994-06-27 | 1995-05-02 | Ford Motor Company | Fast start hydraulic system for electrohydraulic valvetrain |
US5647318A (en) | 1994-07-29 | 1997-07-15 | Caterpillar Inc. | Engine compression braking apparatus and method |
AT403835B (en) * | 1994-07-29 | 1998-05-25 | Hoerbiger Ventilwerke Ag | DEVICE AND METHOD FOR INFLUENCING A VALVE |
US5540201A (en) * | 1994-07-29 | 1996-07-30 | Caterpillar Inc. | Engine compression braking apparatus and method |
US5526784A (en) | 1994-08-04 | 1996-06-18 | Caterpillar Inc. | Simultaneous exhaust valve opening braking system |
US5582141A (en) * | 1994-10-12 | 1996-12-10 | Eaton Corporation | Engine valve hydraulic actuator locating mechanism |
DE10135377A1 (en) * | 2001-07-20 | 2003-02-13 | Wolfgang Nestler | Hydraulic drive and control for IC engine gas changing valve has oil supplied to space between differential pistons acting as valve shaft for controlling valve opening |
DE10161438B4 (en) * | 2001-12-14 | 2004-07-15 | Man B&W Diesel A/S | reciprocating engine |
LU90889B1 (en) * | 2002-02-04 | 2003-08-05 | Delphi Tech Inc | Hydraulicv control system for a gas exchange valve of an internal combustion engine |
US7004122B2 (en) * | 2002-05-14 | 2006-02-28 | Caterpillar Inc | Engine valve actuation system |
US6907851B2 (en) | 2002-05-14 | 2005-06-21 | Caterpillar Inc | Engine valve actuation system |
JP2010164023A (en) * | 2009-01-19 | 2010-07-29 | Mitsui Eng & Shipbuild Co Ltd | Hydraulic passage structure of hydraulic cylinder block |
EP2295786B1 (en) * | 2009-08-04 | 2016-04-13 | Wärtsilä Schweiz AG | Connection arrangement |
DE102009046943A1 (en) * | 2009-11-20 | 2011-05-26 | Robert Bosch Gmbh | Electrohydraulic actuator |
JP5781345B2 (en) * | 2011-03-24 | 2015-09-24 | 三菱重工業株式会社 | Hydraulic actuator system |
CN103388502B (en) * | 2013-07-31 | 2016-01-27 | 哈尔滨工程大学 | A kind of full changeable electro-hydraulic air valve drive unit |
CN104632317A (en) * | 2015-01-30 | 2015-05-20 | 哈尔滨工程大学 | Vent valve device for high-power low-speed marine diesel engine |
CN104791043A (en) * | 2015-04-23 | 2015-07-22 | 哈尔滨工程大学 | Valve electro-hydraulic driving system and method for achieving Miller cycle of engine |
DK178787B1 (en) * | 2015-05-06 | 2017-02-06 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | A large turbocharged two-stroke self-igniting internal combustion engine with an exhaust valve actuation system |
CN107100689B (en) * | 2017-06-28 | 2023-04-07 | 吉林大学 | Electromagnetic control hydraulic drive type fully-variable valve mechanism |
GB2572965A (en) * | 2018-04-17 | 2019-10-23 | Caterpillar Inc | Exhaust valve actuation system |
CN110500156B (en) * | 2019-08-29 | 2024-08-02 | 佰顿新材料科技(江苏)有限公司 | Valve driving device, internal combustion engine and vehicle |
CN110671215A (en) * | 2019-11-15 | 2020-01-10 | 三一重机有限公司 | Engine air distribution system, engine and vehicle |
CN114087076B (en) * | 2022-01-24 | 2022-05-13 | 龙口中宇热管理系统科技有限公司 | Engine cylinder closing valve control device and method |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1361178A (en) * | 1963-06-27 | 1964-05-15 | Mitsubishi Shipbuilding & Eng | Quick valve control device in an internal combustion engine |
DK225982A (en) * | 1981-07-07 | 1983-01-08 | Sulzer Ag | INHIBIT OR EXHAUST VALVE TO A CYLINDER TOP OF A COMBUSTION ENGINE |
FR2619457B1 (en) * | 1987-08-14 | 1989-11-17 | Commissariat Energie Atomique | PROCESS FOR OBTAINING A PATTERN IN PARTICULAR OF FERROMAGNETIC MATERIAL HAVING DIFFERENT SLOPES AND MAGNETIC HEAD COMPRISING SUCH A PATTERN |
JP2664986B2 (en) * | 1989-04-03 | 1997-10-22 | 三菱重工業株式会社 | Valve train for internal combustion engine |
-
1990
- 1990-08-31 JP JP1990090676U patent/JP2527268Y2/en not_active Expired - Fee Related
- 1990-09-28 JP JP2257125A patent/JP2809354B2/en not_active Expired - Lifetime
-
1991
- 1991-02-01 DE DE199191101372T patent/DE455937T1/en active Pending
- 1991-02-01 DE DE69103323T patent/DE69103323T2/en not_active Expired - Lifetime
- 1991-02-01 DK DK91101372.0T patent/DK0455937T3/en active
- 1991-02-01 EP EP91101372A patent/EP0455937B1/en not_active Expired - Lifetime
- 1991-05-10 KR KR1019910007516A patent/KR940010284B1/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
EP0455937A1 (en) | 1991-11-13 |
KR910020298A (en) | 1991-12-19 |
JPH04128508A (en) | 1992-04-30 |
DE69103323T2 (en) | 1994-12-01 |
JP2809354B2 (en) | 1998-10-08 |
KR940010284B1 (en) | 1994-10-22 |
JPH0444408U (en) | 1992-04-15 |
EP0455937B1 (en) | 1994-08-10 |
DE69103323D1 (en) | 1994-09-15 |
DK0455937T3 (en) | 1994-12-12 |
DE455937T1 (en) | 1992-02-27 |
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