JPH04128508A - Valve system device of internal combustion engine - Google Patents

Valve system device of internal combustion engine

Info

Publication number
JPH04128508A
JPH04128508A JP2257125A JP25712590A JPH04128508A JP H04128508 A JPH04128508 A JP H04128508A JP 2257125 A JP2257125 A JP 2257125A JP 25712590 A JP25712590 A JP 25712590A JP H04128508 A JPH04128508 A JP H04128508A
Authority
JP
Japan
Prior art keywords
valve
intake
oil
pressure
valves
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
Application number
JP2257125A
Other languages
Japanese (ja)
Other versions
JP2809354B2 (en
Inventor
Yoshinori Nagae
禎範 永江
Yozo Tosa
土佐 陽三
Tadashi Fukuyoshi
福吉 正
Etsuo Kunimoto
国本 悦夫
Yasutaka Irie
入江 泰隆
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to JP2257125A priority Critical patent/JP2809354B2/en
Publication of JPH04128508A publication Critical patent/JPH04128508A/en
Application granted granted Critical
Publication of JP2809354B2 publication Critical patent/JP2809354B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02Drive, 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)

Abstract

PURPOSE:To obtain optimal opening/closing valve characteristics of an intake/exhaust valve by providing two mutually communicated logic valves for opening/closing a high pressure oil passage communicated with the upper part of a piston for driving the intake/exhaust valve, and providing two electromagnetically driven spool control valves for controlling opening/closing of both logic valves. CONSTITUTION:When an intake/exhaust valve 2 comes in a valve opening period, a opening side spool control valve 13 is driven to close an oil passage 22, and an oil passage 21 is communicated with an exhaust oil pipe 26 to open a logic valve 11. Hence, oil pressure in a pressure accumulator 16 acts from an oil passage 12 and a high pressure pipe 10 to the upper part oil pressure chamber 8a of an oil pressure cylinder 8 in a valve system actuator 7 so as to push down a hydraulic piston 9 to open the intake/exhaust valve 2. When intake/exhaust which is necessary for an engine is carried out, a closing side spool control valve 15 is driven to close an oil passage 24, and an oil passage 23 is communicated with the exhaust oil pipe 26 to open a logic valve 14. And, the intake/exhaust valve 2 is closed by compression force of air acting on an air piston 5. At this time, oil is supplied from a low oil pressure source 18 in a lower part oil pressure chamber 8b so as to return the operating piston 9 to a raised position in its stabilized condition.

Description

【発明の詳細な説明】 [産業上の利用分野〕 本発明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 [Field of Industrial Application] The present invention relates to a valve operating system for an internal combustion engine in which intake and exhaust valves are opened and closed by actuators.

[従来の技術〕 従来の蓄圧式動弁装置の一例を第5図に示す。[Conventional technology] An example of a conventional pressure accumulation type valve operating device is shown in FIG.

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に取りつ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。0
10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。
Its structure is as follows: 01 is a hydraulic control valve main body having 5 holes, 02 is a control valve, which is driven by a cam 03 and a roller 04 in synchronization with the engine crankshaft. An intake and exhaust valve 07 opens and closes inside an actuator 06 attached to a cylinder cover 05. The actuator 06 has an upper hydraulic chamber 06a and a lower hydraulic chamber 06b, each of which is connected to the control valve 01 through a pipe 08.09. 0
10 is a hydraulic pressure supply device composed of a filter and a pump, and 010a is an oil tank.

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。
011 is the pressure accumulator, which maintains the required constant oil pressure and controls the control valve 01.
It is connected by a conduit.

次に作用について述べる。本図は、ローラ04がカム0
3の基円上にあり、吸排気弁が閉し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0
9を通り、アクチュエータの下部油圧室06bに作用し
、吸排気弁07を上に押しあげている。このとき上部油
圧室06aの油は、配管08、管制弁01を経て、油圧
源010のタンクO]Oaに導かれ戻っている。
Next, we will discuss the effect. In this figure, roller 04 is cam 0.
3, and when the intake and exhaust valves are closed, the hydraulic fluid from the pressure accumulator 011 flows from the control valve 01 to the pipe 0.
9 and acts on the lower hydraulic chamber 06b of the actuator, pushing up the intake/exhaust valve 07. At this time, the oil in the upper hydraulic chamber 06a is guided back to the tank O]Oa of the hydraulic power source 010 via the pipe 08 and the control valve 01.

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O9、管
制弁01を経てタンク010a↓二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0
11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しることになる。
When the cam 03 rotates and the roller 04 lifts, the oil in the lower hydraulic chamber 06b of the actuator 06 is discharged from the tank 010a↓2 through the pipe O9 and the control valve 01, and at the same time, the high-pressure hydraulic oil in the pressure accumulator 011 is Control valve 01, piping 08
The air is guided to the upper hydraulic chamber 06a of the actuator 06, and the intake and exhaust valves 07 are pushed down and opened. When the cam 03 further rotates and the lift of the cam decreases until it reaches the base circle, the oil in the upper hydraulic chamber 06a escapes to the tank 010a, and the pressure accumulator 0
No. 11 hydraulic oil acts on the lower hydraulic chamber 06b, and the intake/exhaust valve 07 is raised upward and closed.

(発明が解決しようとする課題〕 前述の従来技術には次のような間8点がある。(Problem to be solved by the invention) The above-mentioned prior art has the following eight points.

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 has a complicated structure.
The amount of oil required to open and close the intake and exhaust valves also needs to flow through the control valve, resulting in a large hydraulic system.

又、高圧油で弁の開、閉とも行うための配管0809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。
Furthermore, the actuator has two pipes 0809 for opening and closing the valve using high pressure oil, and the structure of the actuator is complicated, consuming a large amount of high pressure oil and requiring a large amount of 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。
Furthermore, the control valve 01 is driven by the cam 03, and the opening/closing timing of the intake and exhaust valves cannot be changed freely.

C8題を解決するための手段〕 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ないばねに蓄えられたばね力に
より行なう構造とする。
Means for Solving Problem C8] High-pressure hydraulic oil is used only to open the intake and exhaust valves, and the valves are closed using the spring force stored in the springs as the intake and exhaust valves lift.

さらに、管制弁を2個と、ロジック弁2個を設け、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。
In addition, two control valves and two logic valves are provided, and the control valve is electrically driven and only controls the action of hydraulic pressure from the pressure accumulator to the large diameter part of the logic valve, and controls the opening of the exhaust valve. The required oil is applied from the pressure accumulator to the piston of the cylinder in the valve actuator via one logic valve and one high-pressure pipe.

又、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。
Further, the small diameter sides of the two logic valves are in communication with each other, and when the valve is closed, the other logic valve is opened to release the hydraulic pressure in the cylinder and the high pressure pipe.

〔作用〕[Effect]

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4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。I!間に要する吸排気
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
閉しられる。
The high-pressure hydraulic oil stored in the pressure accumulator is electrically driven at any given time by the open-side control valve, which causes the open-side logic valve to open and act on the piston in the cylinder in the valve actuator, opening the intake and exhaust valves. After pushing down, the closing side control valve returns and the opening side logic valve closes 4. The intake and exhaust valves continue to open due to hydraulic pressure, but the compressive 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 maintained at an appropriate lift in balance with the hydraulic pressure. I! When the necessary intake and exhaust operations are completed, the closing side control valve opens the closing side logic valve and the hydraulic pressure is released, so that the air spring closes the intake and exhaust valves.

このサイクルが繰り返される。This cycle is repeated.

〔第1実施例〕 本発明の第1実施例を第1図について説明する。[First example] A first embodiment of the invention will be described with reference to FIG.

】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65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。
] is the cylinder cover, 2 is the intake and exhaust valve, 3 is the air reservoir, 4
65 is a check valve, and 65 is an air piston that slides in the air cylinder 6 at the same time as the intake and exhaust valve 2. 7 is the valve actuator body, 8 is the hydraulic cylinder, 9 is the operating 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、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、141ま閉
側ロジック弁、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ζこ図示し、ないコントロー
ラにより駆動され、かつ30の管制弁である。16は蓄
圧器、I7は油圧a、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
タフに連通している。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く連通油路1,21は開
側ロジック弁の大径側と閉側スプール管制弁とをつなく
油路、22は開側スプール管制弁13と蓄圧器16とを
つなぐ油路、23は閉側ロジック弁14の大径側と閉側
スプル管制弁15とをつなく油路、24は閉側スプール
管制弁15と蓄圧器16とをつなく油路である。
10 is a high pressure pipe, 11 is an open side logic valve, and 12 is an open side logic valve oil passage, which is connected to a pressure accumulator 16. 13 is an open side spool control valve, which is controlled by a controller (not shown).
141 is a closing side logic valve which is driven in synchronization with the crank rotation of the engine; 15 is a closing side spool control valve; like the opening side spool control valve 13, it is driven by a controller not shown; control valve. Reference numeral 16 denotes a pressure accumulator, and I7 denotes a hydraulic pressure device, which supplies high-pressure oil, and is composed of a pump and a filter. Reference numeral 18 denotes a low-pressure hydraulic power source device, which is communicated with the valve actuator tough through a conduit 18a. 19 is an oil tank, 20 is a communication oil passage 1 connecting the open side logic valve and the closing side logic valve, 21 is an oil passage connecting the large diameter side of the opening side logic valve and the closing side spool control valve, 22 is an open side logic valve. 23 is an oil passage connecting the side spool control valve 13 and the pressure accumulator 16, 23 is an oil passage connecting the large diameter side of the closing side logic valve 14 and the closing side spool control valve 15, and 24 is an oil passage connecting the closing side spool control valve 15 and the pressure accumulator. It is an oil path that connects with the container 16.

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13,1.5からの排油管であ
る。
25 is an oil drain pipe from the closing side logic valve 14 to the oil tank 19, and 26 is an oil drain pipe from the spool control valves 13 and 1.5.

又、このスプール管制弁13.15は、30の管制弁で
、Pボート、Cボート、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 30 control valves, each having a P boat, a C boat, and a T port, and are electromagnetically driven.

次に、オ装置の動作について説明する。Next, the operation of the O device will be explained.

本図は空気溜め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が閉しでいる状態である。
This figure 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 and exhaust valves 2 are closed.

このとき、開側及び閉側のスプール管制弁13゜15は
蓄圧器からの油圧を開、閉側ロジック弁1】。
At this time, the open and close side spool control valves 13 and 15 open the hydraulic pressure from the pressure accumulator, and the close side logic valve 1].

14の大径側に作用させ、ロジック弁11.】4は閉し
ている。
14 on the large diameter side of the logic valve 11. ]4 is closed.

吸排気弁2の開弁時期(こなると、図示しない機関と同
期して発せられるトリガー信号により、且つ機関の運転
状Bcこ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。間管制御弁
13が作動すると、油1!122は閉しられ、油路21
が排油管26に通して、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12及び高圧管IOから動弁アクチュエータ7内の油
圧ソリンダ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
The opening side spool control valve 13 is actuated at the opening timing of the intake/exhaust valve 2 (in this case, the opening side spool control valve 13 is activated by a trigger signal issued in synchronization with the engine (not shown) and at an appropriate timing determined by the computer based on the engine operating condition Bc). When the pipe control valve 13 is operated, the oil 1!122 is closed and the oil passage 21 is closed.
passes through the oil drain pipe 26 and the hydraulic pressure on the large diameter side of the logic valve is released, so the logic valve 11 opens, and the hydraulic pressure in the pressure accumulator 16 is transferred from the oil passage 12 and the high pressure pipe IO to the upper part of the hydraulic cylinder 8 in the valve actuator 7. It acts on the hydraulic chamber 8a. This oil pressure pushes down the hydraulic piston 9 and opens the intake and exhaust valves 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力のバランス点まで吸排気
弁2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 and exhaust valves 2 are lifted to a point where the force balances with the oil 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、開側ロジック弁1
1は閉しる。
Thereafter, the open-side control valve 13 is returned to its original position, and the hydraulic pressure of the pressure accumulator 16 acts on the large diameter portion of the logic valve 11.
1 is closed.

機関に必要な吸排気がなされると、閉側スプール管制弁
15が駆動され、油路24が閉しられると同時に、油路
23と排油管26とがつながり、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が間き、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5へ作用している空気の圧縮力
のハネにより、吸排気弁が閉しる。このとき下部油圧室
8bには低圧油圧s18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。
When the intake and exhaust necessary for the engine are performed, 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 large diameter side of the logic valve 14 is connected. Since the oil pressure is released, the logic valve 14 is closed, and the oil pressure that was acting on the upper hydraulic chamber 8a is released from the high pressure pipe 10 and the communication oil passage 20 to the oil drain pipe 25, and the acting force of the oil pressure disappears. Then, the air compressive force acting on the air piston 5 causes the intake and exhaust valves to close. At this time, the lower hydraulic chamber 8b is replenished with oil from the low pressure hydraulic pressure s18, and the actuating piston 9 returns to the raised position in a stable state without the formation of a cavity.

なお、上記実施例では、空気ばねによる吸排気弁の戻し
装置を示したが、通常のコイルばねによるものも利用で
きる。
In the above embodiment, an air spring is used to return the intake and exhaust valves, but a normal coil spring may also be used.

次に、上記第1実施例に示した動弁装置の特性を第2図
について説明する。
Next, the characteristics of the valve train shown in the first embodiment will be explained with reference to FIG.

Aは吸排気弁リフト、Bはロジック弁連通部油圧、Cは
開側ロジック弁大径部油圧、Dは閉側ロジック弁大径部
油圧である。
A is the intake/exhaust valve lift, B is the logic valve communication section hydraulic pressure, C is the opening side logic valve large diameter section hydraulic pressure, and D is the closing side logic valve large diameter section hydraulic pressure.

第2図に示した、a、b、cはキャビテーションの発生
による高周波の油圧振動である。まずa部について説明
すると、開側スプール管制弁13が作動して、ロジック
弁大径側の油圧が抜かれると、蓄圧器16の油圧が作用
し、ロジック弁11は栄激に開き最大ストローク位置に
達し止まる。このとき多量の空洞を生しる。その後、管
制弁13がもどされると、蓄圧圧力がこの部分に作用し
、ロジック弁11は閉しられるが、先に生じた空洞がつ
ぶされるため、高周波の油圧変動がみられる。これはい
わゆるキャビテーションエロージョンの原因となるもの
で、部品の耐久性を失うものである。
In FIG. 2, a, b, and c are high-frequency hydraulic vibrations caused by cavitation. First, to explain part a, when the open side spool control valve 13 is activated and the hydraulic pressure on the large diameter side of the logic valve is released, the hydraulic pressure of the pressure accumulator 16 acts, and the logic valve 11 opens vigorously to the maximum stroke position. It reaches and stops. At this time, a large amount of cavities are created. After that, when the control valve 13 is returned to its original position, the accumulated pressure acts on this part and the logic valve 11 is closed, but the cavity created earlier is collapsed, so high-frequency oil pressure fluctuations are observed. This causes so-called cavitation erosion, which reduces the durability of the parts.

b部についでも現象的には全く同しもので、閉側ロジッ
ク弁14について起きているものである。
Regarding part b, the phenomenon is exactly the same, and it occurs with respect to the closing side logic valve 14.

又、閉側ロジック弁14が急激に開くと、高圧管10及
びdに示すロジック弁連迩部の圧力がヤ、激に下がり、
吸排気弁がeに示すように箸、激に閉しる。
Moreover, when the closing side logic valve 14 suddenly opens, the pressure in the logic valve connecting portion shown in the high pressure pipes 10 and d drops sharply.
Close the intake and exhaust valves tightly as shown in e.

このため、吸排気弁2は弁座への着座速度が高くなり損
傷のおそれがある。さらに高圧管10及びロジック弁連
通部20に空洞を生しるため、次のサイクルで吸排気弁
を開けるときCに示すような急激な圧力の立ち上がりと
なり、或はそのタイミングが変動するため開弁タイミン
グが変動することがある。
For this reason, the intake/exhaust valve 2 is seated on the valve seat at a high speed, and there is a risk of damage. Furthermore, since a cavity is created in the high pressure pipe 10 and the logic valve communication part 20, when the intake and exhaust valves are opened in the next cycle, the pressure will rise suddenly as shown in C, or the timing will fluctuate, causing the valves to open. Timings may vary.

[第2実施例〕 本発明の第2実施例を第3図について説明する。[Second example] A second embodiment of the invention will be described with reference to FIG.

開側スプール管制弁13の排油系の一部に絞り10】を
設け、閉側スプール管制#】5の排油系の一部に絞り1
02を設け、閉側ロジック弁14の排油系の一部に絞り
103を設けたもので、他の構成は第1実施例に同しで
ある。
A restriction 10 is provided in a part of the oil drainage system of the open side spool control valve 13, and a restriction 1 is provided in a part of the oil drainage system of the closing side spool control valve #]5.
02, and a throttle 103 is provided in a part of the oil drainage system of the closing side logic valve 14, and the other configurations are the same as in the first embodiment.

次に、本装置の動作について説明する。Next, the operation of this device will be explained.

第3回は空気ff13の空気圧が空気ピストン5の下部
に作用し、吸排気弁2が閉している状態である。
At the third time, the air pressure of the air ff13 acts on the lower part of the air piston 5, and the intake and exhaust valves 2 are closed.

このとき、開側及び閉側のスプール管制弁1315は蓄
圧器16からの油圧を開閉側ロジック弁1114の大径
側に作用させ、ロジック弁11.14は閉している。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。管制弁13が作動すると
、油路22は閉しられ、油路21が排油管26に通して
、ロジック弁大径側の油圧が抜ける。しかし、絞り10
1の効果により油の逃げはゆるやかになり、ロジ゛・・
り弁11の開弁もそれほど速くなく、この部分に空洞を
生L2ることがない、ロジック弁】】が開くと、蓄圧器
】6の油圧は、油路12、高圧管lOから、動弁アクチ
ュエータ内の油圧シリンダ8のに部油圧室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
弁が開かれる。このとき、空気ンリンダ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 open side and close side spool control valves 1315 act on the hydraulic pressure from the pressure accumulator 16 on the large diameter side of the open/close side logic valve 1114, and the logic valve 11.14 is closed. When it is time to open the intake and exhaust valves 2, a trigger signal is generated in synchronization with the engine (not shown) and the operating state of the engine.
The open side spool control valve 13 is driven at an appropriate time determined by the computer. When the control valve 13 operates, the oil passage 22 is closed, the oil passage 21 passes through the oil drain pipe 26, and the hydraulic pressure on the large diameter side of the logic valve is released. However, aperture 10
Due to the effect of 1, the oil escapes slowly, and the logic...
The opening of the valve 11 is not so fast, and no cavity is created in this part.When the logic valve 】】 opens, the hydraulic pressure of the pressure accumulator 6 is transferred from the oil line 12 and the high pressure pipe IO to the valve operating valve. It acts on the hydraulic chamber 8a of the hydraulic cylinder 8 in the actuator. This oil pressure pushes down the hydraulic piston 9 and opens the intake and exhaust valves. At this time, the air in the air cylinder 6 is compressed and acts as an upward force, but the intake and exhaust valves are lifted to the point of balance with the oil pressure.

その後、開側管制弁】3がもどされ、蓄圧器】6の油圧
がロジック弁11の大径部に作用しロジック弁11が閉
しるが、空洞が発生していないので、なめらかに油圧が
作用する。
After that, the open side control valve [3] is returned, and the hydraulic pressure of the pressure accumulator [6] acts on the large diameter part of the logic valve 11, closing the logic valve 11. However, since no cavity is generated, the hydraulic pressure increases smoothly. act.

次に、上記第2実施例に示した動弁装置の特性を第4図
について説明する。
Next, the characteristics of the valve train shown in the second embodiment will be explained with reference to FIG.

Aに弁リフト、Bにロジック弁連逼部油圧、Cに開側ロ
ジック弁大径部圧力、Dに閉側ロジック弁大径部圧力を
示している。
A shows the valve lift, B shows the logic valve connection oil pressure, C shows the open side logic valve large diameter part pressure, and D shows the closing side logic valve large diameter part pressure.

同図Cにみられるように、スプール管制弁1315の作
動直後の圧力鋒下がゆるやかになり、ロジック弁111
4が閉しるときの従来みられた高周波圧力変動が発生し
ない。
As shown in Figure C, the pressure drop immediately after the spool control valve 1315 is activated becomes gradual, and
4 is closed, the high frequency pressure fluctuations seen in the past do not occur.

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が閉しられると同時に油
路23と排油管25がつながり、ロジック弁14の大径
側の油圧が抜ける。このとき絞り102の効果、こより
、前述の開側ロジック弁11と同様に、空洞の発生もな
く閉側ロジック弁14がゆるやかに開き、上部油圧室8
a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−・と抜ける。この時、絞り103の効
果により、油の流出はゆるやかになる。・従って、高圧
管部に空洞の発生がない。
Next, when the intake and exhaust necessary for the engine are completed, the closing side spool control valve 15 is driven, the oil passage 24 is closed, and at the same time, the oil passage 23 and the oil drain pipe 25 are connected, and the hydraulic pressure on the large diameter side of the logic valve 14 is increased. comes out. At this time, due to the effect of the throttle 102, the closing logic valve 14 opens gently without creating a cavity, similar to the opening logic valve 11 described above, and the upper hydraulic chamber 8
The oil pressure that was acting on a is released from the high pressure pipe 10, the communication oil passage 20, and the oil drain pipe 25-. At this time, the effect of the throttle 103 slows down the oil flow.・Therefore, no cavities occur in the high pressure pipe section.

油圧の作用力が小さくなると、空気ピストン5・\作用
している空気圧縮力により1、吸排気弁2が閉しる。こ
の吸排気弁2の閉弁速度は、第4図e部に示すように、
それほど大きくなく、着座時の衝望も小さい。
When the hydraulic pressure decreases, the air compression force acting on the air piston 5 causes the intake and exhaust valves 2 to close. The closing speed of this intake/exhaust valve 2 is as shown in part e of FIG.
It's not very big, and the urge when seated is also small.

第4図のDにみられるように、閉側ロジック弁14の油
圧もなめらかになり、Bに示されるロジック労連通部の
初期C部、後期d部の圧力がゆるやかに作用する。
As seen at D in FIG. 4, the hydraulic pressure of the closing side logic valve 14 becomes smooth, and the pressure at the early part C and the latter part d of the logic communication section shown in B acts gently.

(発明の効果〕 (1)本発明は、作動油を加圧ニア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ない蓄えら
ねたばね力によって吸排気弁を閉弁するように構成した
ことにより、次の効果を有する。
(Effects of the Invention) (1) The present invention has a hydraulic pressure source that pressurizes and stores hydraulic oil and a pressure accumulator, and controls the hydraulic oil in the pressure accumulator to drive an internal combustion engine that drives intake and exhaust valves. In the valve device, two mutually communicating logic valves open and close high-pressure oil passages communicating with the upper part of the piston for driving the intake and exhaust valves, and two electromagnetically driven spool controls that control the opening and closing of the two logic valves. a valve, the control hydraulic pressure for opening and closing the logic valve and the hydraulic oil for driving the opening and opening of the intake and exhaust valves are supplied from a high-pressure pressure accumulator, and as the piston for driving the intake and exhaust valves is lifted to open the valves. By configuring the intake and exhaust valves to be closed by the stored spring force, the following effects are achieved.

(イ)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。
(a) It is possible to obtain the optimal opening/closing characteristics of the intake and exhaust valves for the engine, resulting in a high-performance engine with low fuel consumption.

(ロ)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。
(b) Since the consumption of high-pressure oil for driving the valve is low, the hydraulic power source can be designed to be small and inexpensive.

また、消費動力も少なく、更に低燃費となる。In addition, the power consumption is low and the fuel consumption is further improved.

(ハ)管制弁部での油量が少なくですむので、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。
(c) Since the amount of oil in the control valve section is small, the control valve becomes compact and a device with good reliability and durability can be realized.

(2)また本発明は、上記(1)項の構成に加えて、閉
側ロジック弁の排油系及び2個のスプール管制弁の排油
系にそれぞれ絞りを設けることにより、上記(イ)〜(
ハ)の効果に加えて次の効果を有する。
(2) In addition to the configuration in item (1) above, the present invention provides the above (a) by providing a restriction in the oil drain system of the closing side logic valve and the oil drain system of the two spool control valves. ~(
In addition to the effect of c), it has the following effect.

(ニ)ロン“シフ弁部での空洞の発生がなく、キャビテ
ーションエロージョン乙こよる損傷を防止できる。
(d) There is no cavity formation in the Ron's shift valve part, and damage caused by cavitation erosion can be prevented.

(ホ)高圧管部での空洞の発生もなくなるので、エロー
ジョンの発生はもとより、安定した開弁タイミングを維
持できると同時に、閉弁時の速度もコントロールされる
ので、弁及び弁座の衝Vによる損傷も防止できる。
(E) Since the formation of cavities in the high-pressure pipe section is eliminated, stable valve opening timing can be maintained without the occurrence of erosion, and at the same time, the valve closing speed can be controlled, so the collision between the valve and valve seat can be controlled. It can also prevent damage caused by

(へ)上記(ニ)、(ホ)項により、安定な作動と高い
信軌性及び耐久性を達成できる。
(f) With the above items (d) and (e), stable operation, high reliability and durability can be achieved.

【図面の簡単な説明】[Brief explanation of the drawing]

第1図は本発明の第1実施例に係る動弁2置の系統図、
第2同は第1実施例二二おける吸排気弁リフト及び油圧
の状況を示す特性図、第3図は本発明の第2実施例に係
る動弁装置の系統図、第4Vは第2実施例における吸排
気弁リフト及び油圧の状況を示す特性図、第5図は従来
の蓄圧式動弁装置の系統図である。 2・・・吸排気弁、 6・・・空気ノリンダ、 11・・開側ロジック弁、 14・・・閉側ロジック弁、 16・・・蓄圧器、 5・・・空気ピストン、 9・・・作動ピストン、 13・・・開側スプール管制弁、 15・・・閉側スプール管制弁、 17・・・油圧源
FIG. 1 is a system diagram of a two-position valve train according to the first embodiment of the present invention,
No. 2 is a characteristic diagram showing the intake/exhaust valve lift and oil pressure status in the first embodiment, FIG. 3 is a system diagram of the valve train according to the second embodiment of the present invention, and No. 4V is a characteristic diagram showing the situation of the intake/exhaust valve lift and oil pressure in the first embodiment. FIG. 5 is a characteristic diagram showing the intake/exhaust valve lift and oil pressure status in this example, and is a system diagram of a conventional pressure accumulation type valve operating system. 2... Intake and exhaust valve, 6... Air nolinda, 11... Opening side logic valve, 14... Closing side logic valve, 16... Pressure accumulator, 5... Air piston, 9... Operating piston, 13... Opening side spool control valve, 15... Closing side spool control valve, 17... Hydraulic pressure source

Claims (2)

【特許請求の範囲】[Claims] (1)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ない蓄えられたばね力に
よって吸排気弁を開弁するように構成したことを特徴と
する内燃機関の動弁装置。
(1) In a valve train for an internal combustion engine that has a hydraulic pressure source that pressurizes and stores hydraulic oil and a pressure accumulator, and controls the hydraulic oil in the pressure accumulator to drive the intake and exhaust valves, a piston for driving the intake and exhaust valves is used. two logic valves that communicate with each other to open and close high-pressure oil passages that communicate with the upper part of the logic valve, and two electromagnetically driven spool control valves that control the opening and closing of the two logic valves, and the logic valve opens and closes the logic valve. Control hydraulic pressure to open the intake and exhaust valves and hydraulic oil to open the intake and exhaust valves are supplied from a high-pressure pressure accumulator, and the intake and exhaust valves are opened by the spring force stored as the intake and exhaust valve driving piston lifts to open the valves. A valve train for an internal combustion engine, characterized in that it is configured to operate a valve.
(2)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
開側ロジック弁及び閉側ロジック弁と、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2個の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
トに伴ない蓄えられたばね力によって吸排気弁を開弁す
るように構成し、更に前記閉側ロジック弁の排油系及び
前記2個のスプール管制弁の排油系にそれぞれ絞りを設
けたことを特徴とする内燃機関の動弁装置。
(2) In a valve train for an internal combustion engine that has a hydraulic pressure source that pressurizes and stores hydraulic oil and a pressure accumulator, and controls the hydraulic oil in the pressure accumulator to drive the intake and exhaust valves, a piston for driving the intake and exhaust valves is used. Two mutually communicating open-side logic valves and closing-side logic valves that open and close high-pressure oil passages communicating with the upper part of the valve, and two electromagnetically driven spool control valves that control opening and closing of the two logic valves. Control hydraulic pressure for opening and closing the two logic valves and hydraulic oil for driving the opening of the intake and exhaust valves are supplied from a high-pressure pressure accumulator, and as the piston for driving the intake and exhaust valves is lifted to open, The intake and exhaust valves are configured to open by the stored spring force, and furthermore, throttles are provided in the oil drainage system of the closing side logic valve and the oil drainage system of the two spool control valves, respectively. Valve gear for internal combustion engines.
JP2257125A 1990-05-11 1990-09-28 Valve train for internal combustion engine Expired - Lifetime JP2809354B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2257125A JP2809354B2 (en) 1990-05-11 1990-09-28 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
JP2257125A JP2809354B2 (en) 1990-05-11 1990-09-28 Valve train for internal combustion engine

Publications (2)

Publication Number Publication Date
JPH04128508A true JPH04128508A (en) 1992-04-30
JP2809354B2 JP2809354B2 (en) 1998-10-08

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 Before (1)

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

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)

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LU90889B1 (en) * 2002-02-04 2003-08-05 Delphi Tech Inc Hydraulicv control system for a gas exchange valve of an internal combustion engine
KR100933540B1 (en) * 2001-12-14 2009-12-23 맨 디젤 필리얼 아프 맨 디젤 에스이, 티스크랜드 Piston engine
JP2010164023A (en) * 2009-01-19 2010-07-29 Mitsui Eng & Shipbuild Co Ltd Hydraulic passage structure of hydraulic cylinder block
JP2016211548A (en) * 2015-05-06 2016-12-15 エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド Large-scaled turbo supercharger type two-stroke self-ignition type internal combustion engine with exhaust valve operation system
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US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
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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

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US5582141A (en) * 1994-10-12 1996-12-10 Eaton Corporation Engine valve hydraulic actuator locating mechanism
KR100933540B1 (en) * 2001-12-14 2009-12-23 맨 디젤 필리얼 아프 맨 디젤 에스이, 티스크랜드 Piston 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
WO2003067035A1 (en) * 2002-02-04 2003-08-14 Delphi Technologies, Inc. Hydraulic control system for a gas exchange valve of an internal combustion engine
JP2010164023A (en) * 2009-01-19 2010-07-29 Mitsui Eng & Shipbuild Co Ltd Hydraulic passage structure of hydraulic cylinder block
JP2016211548A (en) * 2015-05-06 2016-12-15 エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド Large-scaled turbo supercharger type two-stroke self-ignition type internal combustion engine with exhaust valve operation system
CN107100689A (en) * 2017-06-28 2017-08-29 吉林大学 A kind of solenoid-operated hydraulic drive-type fully variable valve actuator for air

Also Published As

Publication number Publication date
KR910020298A (en) 1991-12-19
EP0455937A1 (en) 1991-11-13
DE69103323D1 (en) 1994-09-15
JP2527268Y2 (en) 1997-02-26
DE69103323T2 (en) 1994-12-01
JP2809354B2 (en) 1998-10-08
KR940010284B1 (en) 1994-10-22
DE455937T1 (en) 1992-02-27
EP0455937B1 (en) 1994-08-10
DK0455937T3 (en) 1994-12-12
JPH0444408U (en) 1992-04-15

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