EP0196441A1 - Système de commande de soupape - Google Patents

Système de commande de soupape Download PDF

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Publication number
EP0196441A1
EP0196441A1 EP86102176A EP86102176A EP0196441A1 EP 0196441 A1 EP0196441 A1 EP 0196441A1 EP 86102176 A EP86102176 A EP 86102176A EP 86102176 A EP86102176 A EP 86102176A EP 0196441 A1 EP0196441 A1 EP 0196441A1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
cam
annular
working space
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
EP86102176A
Other languages
German (de)
English (en)
Other versions
EP0196441B1 (fr
Inventor
Bernhard Dipl.-Ing. Geringer
Ernst Dipl.-Ing. Linder
Helmut Dipl.-Ing. Rembold
Manfred Ing.Grad. Ruoff
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0196441A1 publication Critical patent/EP0196441A1/fr
Application granted granted Critical
Publication of EP0196441B1 publication Critical patent/EP0196441B1/fr
Expired legal-status Critical Current

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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
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets
    • F01L1/25—Hydraulic tappets between cam and valve stem
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a valve control device for reciprocating piston internal combustion engines according to the preamble of claim 1.
  • valve control device with the characterizing features of claim 1 has the advantage that the harmful compression volume has been reduced by the not inconsiderable volume of the pressure spring by accommodating the cam piston pressure spring outside the work area.
  • the speed limit for the control intervention can thus be raised considerably.
  • a further reduction in the harmful compression volume is achieved by the measures taken in the embodiment of the invention according to claim 5.
  • a desired path-time characteristic adapted to the type of internal combustion engine, can be achieved by the possible design of the cylindrical axial flank of the valve piston step specified in claims 8-10.
  • the annular space is supplied with pressure medium without resistance and without generating negative pressure during the renewed piston stroke of the cam and valve pistons and flows through the check valve from the working space to the annular space.
  • the damping pressure builds up in the annular space, it is sealed off from the pressure-free working space by the check valve.
  • An advantageous embodiment of the invention also results from claim 14.
  • the compression support when opening the shut-off valve achieves very short switching times.
  • the design of the solenoid valve as a closer has the advantage that the solenoid valve opens in the event of a power failure and the inlet valve of the internal combustion engine can no longer be opened due to the associated lack of pressure in the working space. This means that no fuel mixture gets into the combustion chamber and the internal combustion engine goes out.
  • the magnetic force of the solenoid valve is designed so that the solenoid valve also against large dynamic pressures can be closed from the work space during the pressure medium drainage process. This ensures that the working space can be closed during the cam rise cycle and thus the intake valve of the internal combustion engine can only make a partial path from the outset.
  • the valve control device for a reciprocating piston internal combustion shown partially schematically in FIG. 1
  • the machine has a housing 11 mounted on a valve housing 10 of the internal combustion engine, in which a housing chamber 12 is introduced in such a way that it is essentially flush with a spring chamber 14 that accommodates two kbaxial valve closing springs 13, 66.
  • the valve closing springs 13, 66 are supported on the one hand on the bottom of the spring chamber 14 and on the other hand on a pressure piece 16 rigidly connected to a valve tappet 15.
  • the valve tappet 15, which projects into an inlet valve 17 of the internal combustion engine, carries at the end a valve member 18 which cooperates with a valve seat 19 arranged in the valve housing 10.
  • a housing block 20 having a central, axially continuous housing bore 21 is inserted from below into the housing chamber 12.
  • a valve piston 22 which is loosely connected to the valve tappet 15 and a piston part 23 of a cam piston 24 arranged above it can be axially displaced.
  • the valve piston 22 and the piston part 23 of the cam piston 24 delimit a working chamber 25 which can be filled with oil via an oil feed line 26 from a storage chamber 27 or from a spring accumulator 28 with a pressure relief valve 29.
  • the two-part cam piston 24 also has a cup or cap-like guide part 30 which concentrically overlaps the piston part 23 and is axially displaceably guided in the housing chamber 12, which also takes over the function of a guide chamber.
  • the piston part 23 lies with its end facing away from the working space 25 against the bottom of the cup-like guide part 30 and carries in this area an annular flange 31, on which one as cylindrical coil spring engages pressure spring 32.
  • the pressure spring 32 concentrically surrounds the piston part 23 and the working space 25 and is supported on the outside of the housing block 20. By means of this pressure spring 32, the piston part 23 is pressed against the guide part 30 of the cam piston 24 and the latter against a valve control cam 33 which is seated on a camshaft 34 in a rotationally fixed manner.
  • the pressure spring 32 is dimensioned such that the system described is reliably guaranteed in all acceleration states of the cam piston 24.
  • Very small bores 35 or 36 or bores with nozzles or orifices are provided centrally in the piston part 23 and in the guide part 30 of the cam piston 24. These bores can be used to express any gas inclusions in the oil of the working space 25 which rise upwards in the working space 25 to the piston surface of the piston part 23. In addition, there is a side effect of low oil leakage between valve control cam 33 and cam piston 24, so that the friction losses of the cam drive are reduced.
  • the oil supply line 26 has two parallel line branches 37, 38.
  • a check valve is arranged, which is designed as a 2/2-way solenoid valve 39.
  • a check valve 40 designed as a plate valve, the blocking direction of which is directed away from the working space.
  • a third line branch 42 which via a pump 43, opens into a branch point 41 of the oil supply line 26, which lies between the parallel line branches 37, 38 and the spring accumulator 28
  • Oil filter 44 and a check valve 45 is supplied with oil from the reservoir 27.
  • the oil supply line 26 is designed to be of very small volume, in particular in the line section between the working space 25 and the solenoid valve 39.
  • the line branch 38 with the check valve 40 arranged at the beginning is relatively large in volume and serves as an oil calming space.
  • the spring accumulator 28 is designed so that during operation only relatively small amounts of oil flow through the pressure relief valve 29 into a return tank 46 and from there via a return channel 47 in the housing 11 and in the valve housing 10 to the reservoir 27.
  • valve brake is provided on the valve piston 22, which causes a damping of the end position of the valve member 18 which freely falls back into its valve seat 19 during the valve closing movement.
  • valve piston 22 and housing block 20 which is shown enlarged in FIG.
  • valve piston 22 has for this purpose a step 48 on its end face delimiting working space 25 with an annular radial shoulder 49 projecting towards wall 51 of housing bore 21 and one cylindrical axial flank 50 on from the wall 51 of the housing bore 21 is a flange-like annular projection 52 which delimits an annular space 54 with the radial shoulder 49 and whose radial extent is dimensioned such that between the axial flank 50 of the annular step fung 48 and the cylindrical annular surface 53 of the annular projection 52 an annular gap 55 adjoining the annular space 54 in the axial direction remains with an axial extension.
  • the cylindrical axial flank 50 of the step 48 is designed in a step-like manner in FIG.
  • the axial flank 50 can also be beveled or convexly curved, the beveling or the curvature beginning with a certain axial distance from the radial shoulder 49 of the step 48. In these two cases too, the distance between the axial flank 50 and the annular surface 53 of the annular projection 52 increases increasingly in the direction of the end face of the valve piston, and thus the annular gap 55.
  • annular space 54 is increasingly closed via the annular gap 55 which narrows with increasing overlap of the axial flank 50 of the gradation 48 and the annular surface 53 of the annular projection 52 and thereby causes more and more after the oil to be squeezed out here via the annular gap 55 Pressure builds up, an end position damping of the valve piston 22 and thus, via the valve tappet 15 coupled to this, an end position damping of the inlet valve 17 of the internal combustion engine.
  • a check valve 56 is integrated in the valve piston 22 so that the annular space 54 is well supplied with oil without resistance and without generating negative pressure when the movement cycle starts again, that is to say with the valve piston 22 moving downward in the drawing.
  • the axial channel 58 opening into the working space 25 carries at its mouth in the valve chamber 57 a valve seat 61, onto which a ball 62 is pressed by a spring 63.
  • the ball 62 When pressure builds up in the working space 25, the ball 62 is lifted off the valve seat 61, and oil can flow from the working space 25 via the channels 59, 60 into the annular space 54, so that the latter is supplied with oil.
  • the ball 62 seals the valve seat 61, so that no oil can flow from the annular space 54 via the axial channel 58 into the working space 25 and the end position damping is effective as described.
  • a position measuring device 64 is coupled to the valve piston 22 for the continuous monitoring of the movement of the inlet valve 17.
  • the displacement measuring device 64 is accommodated in the spring chamber 14 together with the valve closing spring 13.
  • the displacement measuring device 64 consists of a measuring bell 65 made of non-magnetic material, e.g. made of aluminum or titanium, and is applied from the one to the valve closing spring 13 coaxial valve closing spring 66 to the pressure piece 16.
  • This measuring bell 65 is immersed in the movement of the valve tappet 15 in an induction field and changes this by the eddy current field generated in it.
  • the change in the induction field is a measure of the distance traveled by the valve lifter 15.
  • the induction field is generated by an induction coil 67, which is contained in an aluminum tube 68, which in turn is held in the spring chamber 14.
  • the 2/2-way solenoid valve 39 arranged in the oil supply line 26 is designed as a closer, i.e. it closes when the magnet is excited and opens when the magnet is switched off. This has the advantage that the solenoid valve 39 remains open in the event of a power failure and releases the opening cross section of the oil supply line 26.
  • oil can thus flow out of the working space 25, so that the stroke movement of the cam piston 24 is not transmitted to the valve piston 22.
  • the valve piston 22 maintains its rest position shown in FIG. 1 and the inlet valve 17 remains closed despite the rotation of the cam 33, so that no fuel mixture can get into the combustion chamber of the internal combustion engine and the engine runs out.
  • the solenoid valve 39 works with compression support from the working space 25.
  • valve stem 69 forming the valve member is designed so that the pressure from the working space 25 acts on the annular shoulder of the stepped valve stem 69 and throws it open when the magnetic excitation is switched off.
  • the magnet of the solenoid valve 39 is designed so that the solenoid valve 39 can also be closed against high dynamic pressures during drainage processes from the work space. This ensures that the work space 25 can be closed even during the cam rising cycle.
  • the closing process of the inlet valve 17 can be initiated by switching off the solenoid valve 39 at any time - even while the cam piston 24 is moving downward in FIG. 1.
  • the solenoid valve 39 opens and, under the action of the valve closing spring 13, the valve piston 22 can move upward in the spring accumulator 28 by pushing oil out of the working space 25 via the opened solenoid valve 39.
  • the described end position damping sets in, so that the valve member 18 is damped and does not abut abruptly on the valve seat 19.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP86102176A 1985-03-30 1986-02-19 Système de commande de soupape Expired EP0196441B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3511819 1985-03-30
DE19853511819 DE3511819A1 (de) 1985-03-30 1985-03-30 Ventilsteuervorrichtung

Publications (2)

Publication Number Publication Date
EP0196441A1 true EP0196441A1 (fr) 1986-10-08
EP0196441B1 EP0196441B1 (fr) 1988-11-17

Family

ID=6266952

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86102176A Expired EP0196441B1 (fr) 1985-03-30 1986-02-19 Système de commande de soupape

Country Status (4)

Country Link
US (1) US4671221A (fr)
EP (1) EP0196441B1 (fr)
JP (1) JPH0650046B2 (fr)
DE (2) DE3511819A1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0254967A2 (fr) * 1986-07-29 1988-02-03 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Dispositif pour la commande hydraulique de soupapes
EP0255668A2 (fr) * 1986-07-29 1988-02-10 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Dispositif pour la commande hydraulique de soupapes
FR2612253A1 (fr) * 1987-03-13 1988-09-16 Duvant Crepelle Sa Moteurs Procede en vue d'ameliorer les conditions de fonctionnement d'un moteur a combustion interne
US4796573A (en) * 1987-10-02 1989-01-10 Allied-Signal Inc. Hydraulic engine valve lifter assembly
EP0317372A1 (fr) * 1987-11-19 1989-05-24 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande de soupape dans un moteur à combustion interne
EP0317371A1 (fr) * 1987-11-19 1989-05-24 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande de soupape pour moteur à combustion interne
WO1991003627A1 (fr) * 1989-09-01 1991-03-21 Robert Bosch Gmbh Dispositif de commande a soupape avec electrovanne pour moteur a combustion interne
WO1992004531A1 (fr) * 1990-08-31 1992-03-19 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Poussoir de soupape hydraulique pour moteurs a combustion interne
EP0341440B1 (fr) * 1988-05-07 1993-01-20 Robert Bosch Gmbh Dispositif de commande de soupape avec valve magnétique pour moteur à combustion interne
EP0939205A1 (fr) * 1998-02-26 1999-09-01 C.R.F. Società Consortile per Azioni Moteur à combustion interne avec commande hydraulique de soupape variable
CN107075984A (zh) * 2014-09-17 2017-08-18 Fca美国有限责任公司 具有集成液压流体保留的发动机可变气门升程系统
EP3557013A1 (fr) * 2018-04-19 2019-10-23 L.T.A.G. Ltd. Commande de soupape hydraulique pour une soupape de cylindre d'un moteur à combustion interne
CN112805485A (zh) * 2018-08-08 2021-05-14 C法尔克远程遥控公司 包括释放触发机构的转矩限制离合器

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US4917056A (en) * 1987-09-22 1990-04-17 Honda Giken Kogyo Kabushiki Kaisha Valve operation control system in internal combustion engine
JPH01253515A (ja) * 1987-11-19 1989-10-09 Honda Motor Co Ltd 内燃機関の動弁装置
JPH0357805A (ja) * 1989-07-26 1991-03-13 Fuji Heavy Ind Ltd 可変バルブタイミング装置
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DE3939002A1 (de) * 1989-11-25 1991-05-29 Bosch Gmbh Robert Hydraulische ventilsteuervorrichtung fuer eine mehrzylinder-brennkraftmaschine
DE3939066A1 (de) * 1989-11-25 1991-05-29 Bosch Gmbh Robert Elektrohydraulische ventilsteuervorrichtung fuer brennkraftmaschinen
DE3939003A1 (de) * 1989-11-25 1991-05-29 Bosch Gmbh Robert Hydraulische ventilsteuervorrichtung fuer brennkraftmaschinen
DE3939065A1 (de) * 1989-11-25 1991-05-29 Bosch Gmbh Robert Hydraulische ventilsteuervorrichtung fuer brennkraftmaschinen
DE4005906A1 (de) * 1990-02-24 1991-08-29 Mahle Gmbh Tauchkolben mit variabler kompressionshoehe fuer verbrennungsmotoren
JPH03260344A (ja) * 1990-03-08 1991-11-20 Honda Motor Co Ltd 内燃エンジンの制御方法
EP0680551B1 (fr) * 1991-04-01 1997-08-27 Caterpillar Inc. Procédé de fonctionnement d'un moteur à combustion interne
US5127375A (en) * 1991-04-04 1992-07-07 Ford Motor Company Hydraulic valve control system for internal combustion engines
US5158048A (en) * 1992-04-02 1992-10-27 Siemens Automotive L.P. Lost motion actuator
US5451029A (en) * 1992-06-05 1995-09-19 Volkswagen Ag Variable valve control arrangement
US5216988A (en) * 1992-10-15 1993-06-08 Siemens Automotive L.P. Dual bucket hydraulic actuator
US5255639A (en) * 1992-10-15 1993-10-26 Siemens Automotive L.P. Integral EVT/cylinder head assembly with self-purging fluid flow
US5996550A (en) * 1997-07-14 1999-12-07 Diesel Engine Retarders, Inc. Applied lost motion for optimization of fixed timed engine brake system
ITTO980060A1 (it) * 1998-01-23 1999-07-23 Fiat Ricerche Perfezionamenti ai motori a combustione intenra con valvole ad azionam ento variabile.
GB2348245B (en) 1999-03-25 2002-10-23 Ricardo Inc Valvegear for engines of reciprocating piston type
IT1307361B1 (it) * 1999-10-06 2001-11-06 Fiat Ricerche Perfezionamenti ai motori a combustione interna con valvole adazionamento variabile.
AT4872U1 (de) * 2000-11-20 2001-12-27 Avl List Gmbh Variabler ventiltrieb für ein nockenbetätigtes hubventil einer brennkraftmaschine
CN1505729A (zh) 2001-03-16 2004-06-16 �����ˡ�A������ŵ 基本无弹簧的阀驱动系统
US6953014B2 (en) * 2001-03-16 2005-10-11 Folino Frank A Thermal compensating desmodromic valve actuation system
US7082912B2 (en) * 2001-03-16 2006-08-01 Folino Frank A System and method for controlling engine valve lift and valve opening percentage
ITTO20010269A1 (it) * 2001-03-23 2002-09-23 Fiat Ricerche Motore a combustione interna, con sistema idraulico di azionamento variabile delle valvole, e mezzi di compensazione delle variazioni di vol
ITTO20010271A1 (it) 2001-03-23 2002-09-23 Fiat Ricerche Perfezionamenti ai motori a combustione interna con sistema idraulicoper l'azionamento variabile delle valvole del motore.
US6477997B1 (en) 2002-01-14 2002-11-12 Ricardo, Inc. Apparatus for controlling the operation of a valve in an internal combustion engine
ITTO20020149A1 (it) * 2002-02-21 2003-08-21 C R F Societa Con Sortile Per Motore pluricilindrico a combustione interna con dispositivo idraulico a controllo elettronico per l'azionamento variabile delle valvole, in
US6644265B2 (en) 2002-04-09 2003-11-11 Eaton Corporation Electro-hydraulic manifold assembly and method of making same for controlling de-activation of combustion chamber valves in a multicylinder engine
DE10232880A1 (de) * 2002-07-19 2004-01-29 Ina-Schaeffler Kg Nehmereinheit eines strömungsmittelbetätigten variablen Ventiltriebs einer Brennkraftmaschine
JP4324399B2 (ja) * 2003-03-28 2009-09-02 株式会社カネカ グラファイトフィルム及びポリイミドフィルム
US7555999B2 (en) * 2005-10-24 2009-07-07 Eaton Corporation Cold temperature operation for added motion valve system
US7350491B2 (en) * 2005-10-24 2008-04-01 Eaton Corporation Lash adjuster and valve system
US20080017142A1 (en) * 2006-06-30 2008-01-24 Eaton Corporation Energy Recovery System for an Added Motion System
US7677212B2 (en) * 2006-06-30 2010-03-16 Eaton Corporation Added motion hydraulic circuit with proportional valve
US8033261B1 (en) 2008-11-03 2011-10-11 Robbins Warren H Valve actuation system and related methods
US9625050B2 (en) * 2015-01-26 2017-04-18 Ningbo Hoyea Machinery Manufacture Co., Ltd. Engine valve actuation system
EP3156619B1 (fr) * 2015-10-13 2018-06-06 C.R.F. Società Consortile per Azioni Système et procédé pour actionner de manière variable une soupape d'un moteur à combustion interne, avec un dispositif pour amortir les oscillations de pression
SE546024C2 (en) * 2022-07-11 2024-04-16 Freevalve Ab An apparatus comprising a plurality of tools, wherein each tool comprises at least one hydraulic chamber

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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0254967A2 (fr) * 1986-07-29 1988-02-03 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Dispositif pour la commande hydraulique de soupapes
EP0255668A2 (fr) * 1986-07-29 1988-02-10 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Dispositif pour la commande hydraulique de soupapes
EP0255668A3 (en) * 1986-07-29 1988-03-23 Bayerische Motoren Werke Aktiengesellschaft Hydraulic valve control device
EP0254967A3 (en) * 1986-07-29 1988-03-30 Bayerische Motoren Werke Aktiengesellschaft Hydraulic valve control device
FR2612253A1 (fr) * 1987-03-13 1988-09-16 Duvant Crepelle Sa Moteurs Procede en vue d'ameliorer les conditions de fonctionnement d'un moteur a combustion interne
US4796573A (en) * 1987-10-02 1989-01-10 Allied-Signal Inc. Hydraulic engine valve lifter assembly
WO1989002975A1 (fr) * 1987-10-02 1989-04-06 Siemens Aktiengesellschaft Poussoir de soupape de moteur hydraulique
EP0317371A1 (fr) * 1987-11-19 1989-05-24 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande de soupape pour moteur à combustion interne
EP0317372A1 (fr) * 1987-11-19 1989-05-24 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande de soupape dans un moteur à combustion interne
EP0341440B1 (fr) * 1988-05-07 1993-01-20 Robert Bosch Gmbh Dispositif de commande de soupape avec valve magnétique pour moteur à combustion interne
WO1991003627A1 (fr) * 1989-09-01 1991-03-21 Robert Bosch Gmbh Dispositif de commande a soupape avec electrovanne pour moteur a combustion interne
WO1992004531A1 (fr) * 1990-08-31 1992-03-19 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Poussoir de soupape hydraulique pour moteurs a combustion interne
US5315961A (en) * 1990-08-31 1994-05-31 Dr. Ing. H.C.F. Porsche Ag Hydraulic valve tappet for an internal-combustion engine
EP0939205A1 (fr) * 1998-02-26 1999-09-01 C.R.F. Società Consortile per Azioni Moteur à combustion interne avec commande hydraulique de soupape variable
CN107075984A (zh) * 2014-09-17 2017-08-18 Fca美国有限责任公司 具有集成液压流体保留的发动机可变气门升程系统
CN107075984B (zh) * 2014-09-17 2019-08-02 Fca美国有限责任公司 具有集成液压流体保留的发动机可变气门升程系统
EP3557013A1 (fr) * 2018-04-19 2019-10-23 L.T.A.G. Ltd. Commande de soupape hydraulique pour une soupape de cylindre d'un moteur à combustion interne
CN112805485A (zh) * 2018-08-08 2021-05-14 C法尔克远程遥控公司 包括释放触发机构的转矩限制离合器

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Publication number Publication date
EP0196441B1 (fr) 1988-11-17
DE3661217D1 (en) 1988-12-22
US4671221A (en) 1987-06-09
DE3511819A1 (de) 1986-10-09
JPH0650046B2 (ja) 1994-06-29
JPS61275516A (ja) 1986-12-05

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