JP3564149B2 - Device for hydraulically operating an exhaust valve of a reciprocating internal combustion engine - Google Patents

Device for hydraulically operating an exhaust valve of a reciprocating internal combustion engine Download PDF

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JP3564149B2
JP3564149B2 JP28463892A JP28463892A JP3564149B2 JP 3564149 B2 JP3564149 B2 JP 3564149B2 JP 28463892 A JP28463892 A JP 28463892A JP 28463892 A JP28463892 A JP 28463892A JP 3564149 B2 JP3564149 B2 JP 3564149B2
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pipe
servo
pressure medium
liner
pressure
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JPH05195731A (en
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フランツ ヴァンデル アルフレッド
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ヴェルトジィレ シュヴァイツ アクチエンゲゼルシャフト
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    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/16—Silencing impact; Reducing wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)

Description

【０００１】
【産業上の利用分野】
本発明は往復動内燃エンジンの排気弁を液圧的に作動する装置に関する。
【０００２】
【従来の技術】
往復動内燃エンジンの排気弁を液圧的に作動する装置において、排気弁はそのシール部分から離れた端部においてサーボシリンダ内で案内されるサーボピストンに作動的に連結され、サーボシリンダは液圧媒体を弁を開く方向にエンジン速度に対応して供給され、液圧媒体は圧力媒体管を通して圧力媒体源からサーボシリンダ内の圧力室に供給され、サーボシリンダには圧縮空気管とは別に逃し管がまた漏洩管が連結されている。
【０００３】
【発明が解決しようとする課題】
そのような装置はヨーロッパ特許第４４１１００号によって公知である。この装置においては、温度変化から生ずる排気弁軸の長さ変化が、排気弁の座に弁のシール部分を設置するとき、サーボピストンの位置がサーボシリンダに対して移動するため緩衝位相を変化し、排気弁の閉鎖点の変化を生ずる。その結果、内燃エンジンとくに長衝程内燃エンジンの運転性能は悪い影響をうける。
本発明の目的は、排気弁の軸の長さ変化がその閉鎖作用に好ましくない影響をうけることのないように、従来技術の型の装置を改良することにある。
【０００４】
【課題を解決するための手段】
この目的は、本発明によれば、サーボシリンダとサーボピストンの間に前記ピストンを囲む軸方向に移動可能なライナが設けられ、ライナは圧力媒体管の連結部とまたサーボシリンダにおける逃し管の連結部と連通する少なくとも一つの開口を有しまたシール部分から離れた端部において横方向壁によって密にシールされていること、横方向壁とサーボシリンダ端部の間には圧力媒体を充満した室が設けられ、室はこの室の方向に閉鎖する逆止弁を通して圧力室にまた漏洩管の方向に閉鎖する逆止弁を通して漏洩管に連通していること、および圧力室はサーボシリンダにおける逃し管の連結部につねに連結されていることによって達成される。
弁軸の長さ変化の結果として、ライナはサーボピストンと同じ方向にかつ同じ量だけ移動し、サーボピストンとライナの相対的配置はいずれの場合にも維持される。排気弁の軸の長さ変化は本発明装置によって補償され、排気弁のサーボ装置の開閉構造は軸の長さの変化にかかわらず同じままである。
【０００５】
【実施例】
以下、本発明の例示的実施例を図面を参照して下記に一層詳細に記載する。
図１に示すように、二衝程ディーゼル式内燃エンジンのエンジンハウジングには、作動シリンダ１および別のハウジング１０にシリンダ１の上端に連結される排気通路４が形成されている。ハウジング１０には排気通路４の入口に排気弁２が設置され、排気弁２は図示の閉鎖位置において作動シリンダ１内の燃焼室３を排気通路４から分離している。作動シリンダ１では作動ピストン５が上下に移動しうるように案内される。作動シリンダにおいて圧縮される空気は作動シリンダの下方区域に設置された（図示しない）スリットを通してシリンダ室に導入され、かつ作動ピストン５の引続く上昇衝程の間に燃焼室３内において圧縮される。燃料は燃焼室３内に突入する（図示しない）少なくとも一つの噴射ノズルによって供給される。
燃焼室３から離れた排気弁２の端部には、ハウジング１０のシリンダ７内で案内される、ピストン６が設けられている。圧縮空気管９は逆止弁８を通してピストン６の下方に設置された図１のシリンダ室７′に接続されている。シリンダ室７′内に収容された空気は排気弁２の閉鎖方向に作用する空気ばねを形成する。
【０００６】
サーボシリンダ内で案内され、液圧制御装置１２が連結される、液圧媒体によって作動されるサーボピストン１１は、ロッド１１′を通して図１のピストン６上面に作用する。制御装置１２は、２／２切換え制御弁として構成されかつ電磁石１４によって作動されるパイロット弁１５および４／２切換え制御弁１６を有する。液圧媒体たとえばオイルは、アキュムレータとして構成された圧力媒体源１８から管１７を通して制御装置１２に供給される。アキュムレータ１８は圧力媒体をタンク２０からポンプ１９によってうけ入れ、ポンプ１９は内燃エンジンの（図示しない）クランク軸によりまたは電気的に駆動される。圧力媒体はアキュムレータ１８内に、たとえば２００バールの圧力で収容されている。アキュムレータ１８から制御装置１２に通ずる管１７は４／２切換え制御弁１６の前方で二つの支管１７′および１７″に分かれている。支管１７′は４／２切換え制御弁１６に通じ管２７としてサーボシリンダ１３における連結点２１に達している。支管１７″は絞り２２を有し、一方ではパイロット弁１５に達し他方では４／２切換え制御弁１６の前側に達している。サーボシリンダ１３には、逃し管２４用の別の連結点２３が設けられ、逃し管２４は４／２切換え制御弁１６に通じついで排出管２４′に続き、排出管２４′は逆止弁２５を通してタンク２０に開口している。排出管２４′に対しては漏洩管２６も連結され、漏洩管２６はピストン１１上方のサーボシリンダ１３から分かれかつ絞り５７を有する。逆止弁２５の上流にパイロット弁１５から続く逃し管２８が排出管２４′に開口している。
【０００７】
ロッド１１′から離れた端部にサーボピストン１１は有底孔４０を備え、該孔４０は、図１においてその下端に、横孔５６を通して連結点２１の区域の環状部５８に連結されている。転結点２３の区域には、サーボピストン１１とサーボシリンダ１３の間に環状部５９が設けられている。
図１に示す位置において、電流はパイロット弁１５の電磁石１４に通電され、支管１７″を通して供給される圧力媒体は４／２切換え制御弁１６の端面に作用し、支管１７′および管２７を通ってサーボシリンダ１３に達する圧力媒体の供給は停止される。一方、４／２切換え制御弁１６は逃し管２４から排出管２４′への通路を形成し、サーボシリンダ１３内のサーボピストン１１には圧力媒体の圧力がなくなり、排気弁２はピストン６下方の空気ばねにより閉鎖方向の力をうける。この場合圧力媒体はサーボシリンダの圧力室から連結点２３を通って逃し管２４に押出される。逆止弁２５のため、ほぼ１０バールの残留圧力がそこから上流に設置された管部分２４′および管２４ならびに２６内に維持される。電磁石１４の電流が停止されると、支管１７″と逃し管２８の間の連通がパイロット弁１５内に形成され、４／２切換え制御弁１６の端面は圧力をうけなくなる。４／２切換え制御弁１６は管２４および２４′とのこれまでの連通を停止し、支管１７′を管２７に連通し、加圧された圧力媒体は連結点２１、室５８および横孔５６を通って有底孔４０に流れ、その結果サーボピストン１１は下方に動かされ排出弁２は開口する。
【０００８】
図２に示すように本発明によれば、ライナ６０はサーボピストン１１とサーボシリンダ１３の間に設置され、またライナ６０は連結点２１および２３の区域において外側環状Ｔ溝形の開口それぞれ６１または６２、およびその周囲に分布されたいくつかの半径方向孔６１′および６２′を有する。ライナ６０はサーボシリンダ１３の軸方向に移動可能でまた、図２においてその上端にライナはカバーの形式の横方向壁６０′を有し、カバーはライナに着脱可能に連結されている。図２に示された位置において上端面においてカバー６０′の突出部６３に接触するサーボピストン１１は、摺動しうるようにライナ６０に内蔵されている。突出部６３を貫通する半径方向導管７１は、サーボピストン１１とライナ６０の間にこのように形成された圧力室６５から分かれている。これらの導管は角度をなす導管６６に開口し、導管６６はライナ６０を貫通しかつ上方孔の一つ６２′に突出部６３の外側端縁とサーボピストン１１の間に形成された環状Ｔ形溝を通して開口している。その結果、永久的連通が圧力室６５と連結点２３に連結された逃し管２４の間に形成される。図２に示された左側の孔５６のわずか上方のサーボピストン１１には半径方向導管７２が設けられ、導管７２は外側環状Ｔ形溝７３に開口し、Ｔ形溝７３はライナ６０に対するサーボピストンの下方運動の間の排出弁の開放作用中、孔６１′前方に設置される。
図２に示すサーボシリンダ１３の上端壁１３′は漏洩管２６の連通点６７を有する。端壁１３′とカバー６０′の間に圧力媒体を充填した室６８が設けられ、室６８は一方では前記室の方向に閉鎖する逆止弁６９を通して圧力室６５に、他方では連通点６７の方向に閉鎖する逆止弁７０を通して逃し管２６に連通する。
【０００９】
図２に示された装置の作用は下記のとおりである。もし排気弁の軸が温度上昇のため長くなると、図２においてサーボピストン１１はロッド１１′を通して上向きに動かされる。サーボピストン１１の上端面が突出部６３に接触すると、サーボピストンの移動によってライナ６０もまた同時に上向きに動かされる。この移動により、圧力媒体は室６８から開いている逆止弁６９を通して圧力室６５に排出される。このように排出された圧力媒体は導管７１，６６、環状Ｔ形溝６２および連通点２３を通って逃し管２４に排出する。しかして、ライナ６０に対するサーボピストン１１の相対的位置は排気弁軸の長さの変化にかかわらず維持され、排気弁の閉鎖作用にいかなる変化も生じない。排気弁軸の長さが短縮されるときでも、この効果は軸の短縮に応答するロッド１１′によってえられる。
ライナ６０の横方向壁６０′の直径がサーボピストン１１の直径より大きいため、また前記残留圧力のため室６８内に液圧が発生し、液圧は図２においてライナを下方に動かし、ふたたび突出部６３をサーボピストンに押し付ける。逆止弁７０を開放することにより、圧力媒体は漏洩管２６から室６８に流れ込む。この場合もまたライナ６０に対するサーボピストン１１の相対位置、したがって、排出弁の閉鎖作用もまた維持される。
【００１０】
【発明の効果】
サーボシリンダとサーボピストンの間に前記ピストンを囲む軸方向に移動可能なライナが設けられ、ライナは圧力媒体管の連結部とまたサーボシリンダにおける逃し管の連結部と連通する少なくとも一つの開口を有しまたシール部分から離れた端部において横方向壁によって密にシールされ、横方向壁とサーボシリンダ端部の間には圧力媒体を充満した室が設けられ、室はこの室の方向に閉鎖する逆止弁を通して圧力室にまた漏洩管の方向に閉鎖する逆止弁を通して漏洩管に連通し、圧力室はサーボシリンダにおける逃し管の連結部につねに連結されていることによって、弁軸の長さ変化の結果、ライナはサーボピストンと同じ方向にかつ同じ量だけ移動し、サーボピストンとライナの相対的配置はいずれの場合にも維持される。そこで、排気弁の軸の長さ変化は補償され、排気弁のサーボ装置の開閉作用は軸の長さの変化にかかわらず同じである。
【図面の簡単な説明】
【図１】従来技術によって特定された、排出弁を有する作動シリンダの上部を通る断面図ならびに制御装置の線図。
【図２】本発明によって特定されたサーボピストンを備えたサーボシリンダを通る軸方向断面図。
【符号の説明】
１１ サーボピストン
１３ サーボシリンダ
２１ 連結部
２３ 連結部
２４ 逃し管
２６ 漏洩管
６０ ライナ
６１ 開口
６２ 開口
６５ 圧力室
６８ 室
７０ 逆止弁[0001]
[Industrial applications]
The present invention relates to a device for hydraulically operating an exhaust valve of a reciprocating internal combustion engine.
[0002]
[Prior art]
In a device for hydraulically operating an exhaust valve of a reciprocating internal combustion engine, the exhaust valve is operatively connected to a servo piston guided in a servo cylinder at an end remote from a seal portion thereof, and the servo cylinder is hydraulically operated. The medium is supplied corresponding to the engine speed in the direction of opening the valve, and the hydraulic medium is supplied from the pressure medium source to the pressure chamber in the servo cylinder through the pressure medium pipe, and the servo cylinder has a relief pipe separate from the compressed air pipe. However, a leak tube is connected.
[0003]
[Problems to be solved by the invention]
Such a device is known from EP 441100. In this device, a change in the length of the exhaust valve shaft caused by a change in temperature causes a change in the buffer phase because the position of the servo piston moves with respect to the servo cylinder when the valve seal is installed in the exhaust valve seat. , Causing a change in the closing point of the exhaust valve. As a result, the operating performance of internal combustion engines, especially long-stroke internal combustion engines, is adversely affected.
SUMMARY OF THE INVENTION It is an object of the present invention to improve a device of the prior art type such that a change in the length of the shaft of the exhaust valve does not adversely affect its closing action.
[0004]
[Means for Solving the Problems]
For this purpose, according to the present invention, an axially movable liner is provided between the servo cylinder and the servo piston, surrounding the piston, the liner being connected to the connection of the pressure medium pipe and also of the relief pipe in the servo cylinder. Having at least one opening communicating with the section and being tightly sealed by a transverse wall at an end remote from the sealing portion, a chamber filled with a pressure medium between the transverse wall and the end of the servo cylinder. A chamber is connected to the pressure chamber through a check valve closing in the direction of this chamber and to the leak pipe through a check valve closing in the direction of the leak pipe, and the pressure chamber is a relief pipe in the servo cylinder. This is achieved by being always connected to the connecting portion of
As a result of the change in the length of the valve stem, the liner moves in the same direction and by the same amount as the servo piston, and the relative arrangement of the servo piston and the liner is maintained in each case. The change in the shaft length of the exhaust valve is compensated by the device according to the invention, and the opening and closing structure of the servo device of the exhaust valve remains the same regardless of the change in the shaft length.
[0005]
【Example】
Hereinafter, exemplary embodiments of the present invention will be described in more detail below with reference to the drawings.
As shown in FIG. 1, in an engine housing of a two-stroke diesel internal combustion engine, an exhaust passage 4 connected to an upper end of the cylinder 1 is formed in a working cylinder 1 and another housing 10. The housing 10 is provided with an exhaust valve 2 at the inlet of the exhaust passage 4, and the exhaust valve 2 separates the combustion chamber 3 in the working cylinder 1 from the exhaust passage 4 in the closed position shown in the drawing. In the working cylinder 1, the working piston 5 is guided so as to be able to move up and down. The air compressed in the working cylinder is introduced into the cylinder chamber through a slit (not shown) located in the lower section of the working cylinder and is compressed in the combustion chamber 3 during a subsequent rising stroke of the working piston 5. Fuel is supplied by at least one injection nozzle (not shown) which enters the combustion chamber 3.
At the end of the exhaust valve 2 remote from the combustion chamber 3, is guided in the cylinder 7 in the housing 10, the piston 6 is provided. The compressed air pipe 9 is connected through a check valve 8 to a cylinder chamber 7 'shown in FIG. The air contained in the cylinder chamber 7 'forms an air spring acting in the closing direction of the exhaust valve 2.
[0006]
A servo piston 11 guided by a hydraulic medium, guided in a servo cylinder and connected to a hydraulic control device 12, acts on the upper surface of the piston 6 of FIG. 1 through a rod 11 '. The control device 12 has a pilot valve 15 and a 4/2 switching control valve 16 which are configured as a 2/2 switching control valve and are operated by an electromagnet 14. A hydraulic medium, for example oil, is supplied to the control device 12 via a pipe 17 from a pressure medium source 18 configured as an accumulator. An accumulator 18 receives pressure medium from a tank 20 by a pump 19, which is driven by a crankshaft (not shown) of the internal combustion engine or electrically. The pressure medium is stored in the accumulator 18 at a pressure of, for example, 200 bar. The pipe 17 leading from the accumulator 18 to the control device 12 is divided into two branches 17 'and 17 "in front of the 4/2 switching control valve 16. The branch 17' is connected to the 4/2 switching control valve 16 as a pipe 27. It has reached a connection point 21 in the servo cylinder 13. The branch pipe 17 "has a throttle 22, on the one hand reaching the pilot valve 15 and on the other hand reaching the front of the 4/2 switching control valve 16. The servo cylinder 13 is provided with another connection point 23 for a relief pipe 24, which leads to a 4/2 switching control valve 16 and to a discharge pipe 24 ', which is connected to a check valve 25. Through the tank 20. A leak pipe 26 is also connected to the discharge pipe 24 ′. The leak pipe 26 is separated from the servo cylinder 13 above the piston 11 and has a throttle 57. A relief pipe 28 continuing from the pilot valve 15 upstream of the check valve 25 opens to the discharge pipe 24 '.
[0007]
At the end remote from the rod 11 ', the servo piston 11 is provided with a bottomed hole 40 which is connected at its lower end in FIG. . In the area of the turning point 23, an annular portion 59 is provided between the servo piston 11 and the servo cylinder 13.
In the position shown in FIG. 1, an electric current is supplied to the electromagnet 14 of the pilot valve 15, and the pressure medium supplied through the branch pipe 17 "acts on the end face of the 4/2 switching control valve 16 and passes through the branch pipe 17 'and the pipe 27. Then, the supply of the pressure medium reaching the servo cylinder 13 is stopped, while the 4/2 switching control valve 16 forms a passage from the relief pipe 24 to the discharge pipe 24 ', and the servo piston 11 in the servo cylinder 13 has The pressure in the pressure medium is lost and the exhaust valve 2 is forced in the closing direction by the air spring below the piston 6. In this case, the pressure medium is pushed out of the pressure chamber of the servo cylinder through the connection point 23 and into the relief pipe 24. Due to the check valve 25, a residual pressure of approximately 10 bar is maintained in the tube section 24 'and the tubes 24 and 26 located upstream therefrom. If that, communication between the relief pipe 28 and branch pipe 17 "is formed in the pilot valve 15, the end faces of the 4/2 switching control valve 16 is not subjected to pressure. The 4/2 switching control valve 16 stops the previous communication with the pipes 24 and 24 ', connects the branch pipe 17' to the pipe 27, and the pressurized pressure medium is supplied to the connection point 21, the chamber 58 and the horizontal hole 56. Flows into the bottomed hole 40 so that the servo piston 11 is moved downward and the discharge valve 2 is opened.
[0008]
According to the invention, as shown in FIG. 2, the liner 60 is installed between the servo piston 11 and the servo cylinder 13 and the liner 60 is provided in the area of the connection points 21 and 23 with an outer annular T-groove opening 61 or respectively. 62 and several radial holes 61 'and 62' distributed around it. The liner 60 is movable in the axial direction of the servo cylinder 13 and in FIG. 2 at its upper end the liner has a transverse wall 60 'in the form of a cover, which is detachably connected to the liner. At the position shown in FIG. 2, the servo piston 11 that contacts the protrusion 63 of the cover 60 ′ at the upper end surface is built in the liner 60 so as to be slidable. A radial conduit 71 passing through the projection 63 is separated from the pressure chamber 65 thus formed between the servo piston 11 and the liner 60. These conduits open into an angled conduit 66 which penetrates the liner 60 and is formed in one of the upper holes 62 'with an annular T-shape formed between the outer edge of the projection 63 and the servo piston 11. Open through the groove. As a result, a permanent communication is formed between the pressure chamber 65 and the relief pipe 24 connected to the connection point 23. The servo piston 11 slightly above the left hole 56 shown in FIG. 2 is provided with a radial conduit 72 which opens into an outer annular T-shaped groove 73, the T-shaped groove 73 being a servo piston for the liner 60. During the opening action of the discharge valve during the downward movement of the bore 61 '.
An upper end wall 13 ′ of the servo cylinder 13 shown in FIG. 2 has a communication point 67 of the leak pipe 26. A chamber 68 filled with pressure medium is provided between the end wall 13 'and the cover 60', the chamber 68 being connected on the one hand to a pressure chamber 65 through a check valve 69 closing in the direction of said chamber, and on the other hand to a communication point 67. It communicates with the relief pipe 26 through a check valve 70 which closes in a direction.
[0009]
The operation of the device shown in FIG. 2 is as follows. If the axis of the exhaust valve is lengthened due to temperature rise, the servo piston 11 is moved upward through the rod 11 'in FIG. When the upper end surface of the servo piston 11 comes into contact with the protrusion 63, the movement of the servo piston causes the liner 60 to be simultaneously moved upward. With this movement, the pressure medium is discharged from the chamber 68 to the pressure chamber 65 through a check valve 69 which is open. The pressure medium thus discharged is discharged to the relief pipe 24 through the conduits 71 and 66, the annular T-shaped groove 62 and the communication point 23. Thus, the relative position of the servo piston 11 with respect to the liner 60 is maintained regardless of the change in the length of the exhaust valve shaft, and no change occurs in the closing action of the exhaust valve. Even when the length of the exhaust valve shaft is reduced, this effect is obtained by the rod 11 'which responds to the shortening of the shaft.
Since the diameter of the lateral wall 60 'of the liner 60 is larger than the diameter of the servo piston 11 and the residual pressure creates hydraulic pressure in the chamber 68, the hydraulic pressure moves the liner downward in FIG. The part 63 is pressed against the servo piston. By opening the check valve 70, the pressure medium flows from the leak pipe 26 into the chamber 68. Again, the relative position of the servo piston 11 with respect to the liner 60, and thus the closing action of the discharge valve, is also maintained.
[0010]
【The invention's effect】
An axially movable liner surrounding the piston is provided between the servo cylinder and the servo piston, and the liner has at least one opening communicating with a connection of the pressure medium pipe and a connection of the relief pipe of the servo cylinder. And at the end remote from the sealing portion is tightly sealed by a transverse wall, between the transverse wall and the end of the servo cylinder there is provided a chamber filled with a pressure medium, the chamber closing in the direction of this chamber. The pressure chamber is connected to the pressure chamber through the check valve and to the leak pipe through the check valve which closes in the direction of the leak pipe. As a result of the change, the liner moves in the same direction and by the same amount as the servo piston, and the relative arrangement of the servo piston and the liner is maintained in each case. Therefore, the change in the shaft length of the exhaust valve is compensated, and the opening / closing action of the servo device of the exhaust valve is the same regardless of the change in the shaft length.
[Brief description of the drawings]
1 shows a cross section through the top of a working cylinder with a discharge valve as well as a diagram of a control device, as identified by the prior art.
FIG. 2 is an axial section through a servo cylinder with a servo piston identified according to the invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 11 Servo piston 13 Servo cylinder 21 Connecting part 23 Connecting part 24 Relief pipe 26 Leakage pipe 60 Liner 61 Opening 62 Opening 65 Pressure chamber 68 Chamber 70 Check valve

Claims (3)

サーボシリンダ（１３）内で案内され、排気弁のシール部分から離れた端部に作動的に連結され、そしてエンジンの膨張ストローク中弁開放方向に液圧媒体を入れるサーボピストン（１１）を有し、前記媒体は圧力媒体源から圧力媒体管（２７）を通してサーボシリンダ（１３）内の圧力室（６５）に供給され，該サーボシリンダ（１３）は逃し管（２４）と漏洩管（２６）とに連通し、軸方向に移動可能なライナー（６０）が前記サーボシリンダ（１３）とサーボピストン（１１）の間に配置され、該サーボピストン（１１）は前記ライナーによって包囲され、該ライナーは前記シール部分から離れた端部において横方向壁（６０‘）によって密閉され、横方向壁（６０’）とサーボシリンダの端壁（１３‘）との間には圧力媒体で満たされそして漏洩管（２６’）に対して閉じる逆止弁（７０）を経て漏洩管と連通する室（６８）が設けられている内燃ピストンエンジンの排気弁（２）の液圧制御装置において、A servo piston (11) guided in a servo cylinder (13), operatively connected to the end of the exhaust valve remote from the seal, and for receiving hydraulic medium in the valve opening direction during the expansion stroke of the engine; The medium is supplied from a pressure medium source through a pressure medium pipe (27) to a pressure chamber (65) in a servo cylinder (13), and the servo cylinder (13) is provided with a relief pipe (24) and a leak pipe (26). An axially movable liner (60) is disposed between the servo cylinder (13) and the servo piston (11), the servo piston (11) being surrounded by the liner, the liner being Sealed by a transverse wall (60 ') at the end remote from the sealing portion, the space between the transverse wall (60') and the end wall (13 ') of the servo cylinder is filled with a pressure medium. And The fluid pressure control device leakage pipe (26 ') to the closed exhaust valve of an internal combustion piston engine the check valve (70) through a chamber communicating with the leakage pipe (68) is provided (2),
単一の圧力媒体管（２７）と単一の圧力媒体逃し管（２４）を設けたことを特徴とし、更に前記圧力媒体管（２７）と前記圧力媒体逃し管（２４）は互いに別個にサーボシリンダ（１３）に接続され、前記ライナー（６０）はサーボシリンダ上の前記圧力媒体管（２７）の連結点（２１）および前記圧力逃し管（２４）の連結点（２３）と夫々連通する少なくとも１個の開口（６１‘）と１個の開口（６２’）とを有し、圧力媒体で満たされた前記室（６８）は該室（６８）に対して閉じる逆止弁（６９）を経て圧力室（６５）と連通し、該圧力室（６５）は常に逃し管（２４）のサーボシリンダ上の連結点（２３）と接続されていることを特徴とする液圧制御装置。A single pressure medium pipe (27) and a single pressure medium relief pipe (24) are provided, and the pressure medium pipe (27) and the pressure medium relief pipe (24) are separately servo-controlled. Connected to a cylinder (13), the liner (60) being at least in communication with a connection point (21) of the pressure medium pipe (27) and a connection point (23) of the pressure relief pipe (24) on the servo cylinder, respectively. Said chamber (68), having one opening (61 ') and one opening (62'), filled with a pressure medium, has a check valve (69) closed to said chamber (68). A hydraulic pressure control device, characterized in that it communicates with a pressure chamber (65) through the connection point (23) on the servo cylinder of the relief pipe (24) at all times. 前記横方向壁（６０ ’ ）はライナー（６０）から取外しうるカバーとして構成されていることを特徴とする、請求項１に記載の装置。 It said lateral wall (60 ') is characterized in that it is constructed as a cover which can be detached from the liner (60), Apparatus according to claim 1. 導管（７２）がサーボピストン（１１）に設けられ、該導管は排気弁（２）の開放作用中前記圧力室（６５）を圧力媒体管（２７）の連結点（２１）と連通しているライナー（６０）の孔（６１’）と接続することを特徴とする請求項１または２に記載の装置。A conduit (72) is provided in the servo piston (11) which communicates the pressure chamber (65) with the connection point (21) of the pressure medium pipe (27) during the opening action of the exhaust valve (2). Device according to claim 1 or 2, characterized in that it connects with a hole (61 ') in the liner (60).
JP28463892A 1991-10-23 1992-10-22 Device for hydraulically operating an exhaust valve of a reciprocating internal combustion engine Expired - Fee Related JP3564149B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH03098/91-6 1991-10-23
CH309891 1991-10-23

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JPH05195731A JPH05195731A (en) 1993-08-03
JP3564149B2 true JP3564149B2 (en) 2004-09-08

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JP28463892A Expired - Fee Related JP3564149B2 (en) 1991-10-23 1992-10-22 Device for hydraulically operating an exhaust valve of a reciprocating internal combustion engine

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JP (1) JP3564149B2 (en)
KR (1) KR100222139B1 (en)
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US5531192A (en) * 1994-08-04 1996-07-02 Caterpillar Inc. Hydraulically actuated valve system
DK1114918T3 (en) 2000-01-06 2004-09-06 Waertsilae Nsd Schweiz Ag Gas exchange system for an internal combustion engine and method for operating one
GB0017425D0 (en) 2000-07-14 2000-08-30 Lotus Car A valve system for controlling flow of gas into or out of a variable volume chamber of an internal combustion engine or a compressor
DE10311493B4 (en) * 2003-03-15 2005-01-05 Man B & W Diesel A/S Two-stroke diesel engine
ITBO20030389A1 (en) * 2003-06-23 2004-12-24 Magneti Marelli Powertrain Spa ELECTROHYDRAULIC VALVE OPERATION GROUP
DE10361221B4 (en) * 2003-12-24 2006-03-09 Man B&W Diesel A/S Device for controlling the time-shifted connection of two acted upon by a pressure medium units with a pressure medium source
US7290509B2 (en) * 2005-08-01 2007-11-06 Zheng Lou Variable valve actuator
US7587863B2 (en) * 2006-08-17 2009-09-15 Fike Corporation Seal for sanitary overpressure vent structure
CN102787878B (en) * 2012-07-27 2014-07-30 长城汽车股份有限公司 Hydraulic drive engine air distributing mechanism
CN105756739B (en) * 2016-05-04 2018-05-18 哈尔滨工程大学 Electromagnetic hydraulic pressure drive-type air distribution system
CN109372607A (en) * 2018-10-23 2019-02-22 中船动力研究院有限公司 Multistage draining exhaust valve and its working method

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EP0539320A1 (en) 1993-04-28
CN1071733A (en) 1993-05-05
KR930008317A (en) 1993-05-21
DK0539320T3 (en) 1995-03-20
DE59201193D1 (en) 1995-02-23
CN1032381C (en) 1996-07-24
KR100222139B1 (en) 1999-10-01
EP0539320B1 (en) 1995-01-11
JPH05195731A (en) 1993-08-03

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