EP0139566A1 - Elektro-Hydraulikblock zum Steuern der Ventile einer Brennkraftmaschine - Google Patents

Elektro-Hydraulikblock zum Steuern der Ventile einer Brennkraftmaschine Download PDF

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Publication number
EP0139566A1
EP0139566A1 EP84401876A EP84401876A EP0139566A1 EP 0139566 A1 EP0139566 A1 EP 0139566A1 EP 84401876 A EP84401876 A EP 84401876A EP 84401876 A EP84401876 A EP 84401876A EP 0139566 A1 EP0139566 A1 EP 0139566A1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
hydraulic
cylinder
distributor
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
EP84401876A
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English (en)
French (fr)
Other versions
EP0139566B1 (de
Inventor
Jacques Delesalle
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.)
Alsacienne de Constructions Mecaniques SA
Original Assignee
Alsacienne de Constructions Mecaniques SA
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Filing date
Publication date
Application filed by Alsacienne de Constructions Mecaniques SA filed Critical Alsacienne de Constructions Mecaniques SA
Publication of EP0139566A1 publication Critical patent/EP0139566A1/de
Application granted granted Critical
Publication of EP0139566B1 publication Critical patent/EP0139566B1/de
Expired legal-status Critical Current

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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
    • 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

Definitions

  • the present invention relates to internal combustion engines, in particular diesel engines, and it relates to an electro-hydraulic valve control unit for engines of this kind provided with an electronic control system.
  • valve opening law is mechanically fixed by the profile and timing of the cams which provide optimal operating conditions only for a well-defined operating point.
  • the object of the present invention is to improve the operation of internal combustion engines by controlling and controlling the valve opening law by means of an electro-hydraulic control unit controlled by a control system.
  • electronic said control block having a safe operation and a small footprint which allows the housing of two blocks (one for the intake and one for the exhaust) in a cylinder head of the existing engine.
  • an electro-hydraulic valve control unit for an internal combustion engine provided with an electronic control system providing an electrical signal for opening the valve.
  • This block comprises: a three-way solenoid valve, supply / purge, receiving said electrical signal; a three-way hydraulic distributor, supplied tion / purge, the switching member of which is actuated by a hydraulic pilot cylinder connected to said solenoid valve, said distributor comprising a first orifice connected to a high pressure source, a second orifice connected to a low pressure enclosure and a third orifice of use; a hydraulic power cylinder whose working chamber is connected to the third orifice of the distributor; means for returning the piston of said cylinder to the rest position; means for pushing the rod of said cylinder with the rod of the valve to be controlled; the three organs: solenoid valve, hydraulic distributor and power cylinder being joined in a single block mounted on an engine member secured to the cylinder head of the engine.
  • the present invention overcomes these drawbacks.
  • the switching member of the hydraulic distributor consists of a slide valve in a distributor body, said drawer being hydraulically balanced.
  • One end of said drawer is permanently subjected to high pressure, while the other end, which constitutes the piston of the pilot cylinder, is selectively subjected, via the electro-valve, to high pressure in the rest position, or else, in the power jack supply position, at the low pressure established via the solenoid valve when the latter is excited by the electrical signal produced by the electrical control system of the engine.
  • the electromagnet of the electro-valve is always only subjected to low pressure and, on the other hand, the electrical signal of excitation of the electro-valve produces a electric pressure drop signal on the pilot cylinder of the distributor, which provides a faster response than a pressurization signal.
  • the means for returning the power cylinder to the rest position are hydraulic means, the power cylinder being a differential cylinder, the second chamber of which, opposite the working chamber, is subjected permanently at high pressure.
  • a hydraulic pressure accumulator is provided and, on each block, a calibrated check valve now in the block, a residual purge pressure (low pressure) greater than atmospheric pressure.
  • the control unit comprises three parts joined and assembled to one another: an electro-valve 2, a hydraulic distributor 4 and a hydraulic power cylinder 6, this unit being mounted on the cylinder head cover 8 of the engine.
  • the pusher 10 of the hydraulic cylinder acts in thrust on the rod 12 of a valve 14 which has been shown diagrammatically mounted in the cylinder head 16 of the engine and returned to the closed position by a valve spring 18.
  • the solenoid 20 of the solenoid valve 2 receives its electrical excitation signals from an electronic control system, which is not part of the invention, and which is represented schematically by a sensor 22 of the speed and position of the motor shaft 24 and by a processing unit 26 which receives the information supplied by the sensor 22 as well as other information 28 relating to other operating parameters of the motor.
  • the processing unit 26 prepares and conditions the opening control signals of the various valves, with their instant, their duration and their optimal shape, each signal being transmitted to the electro-valve concerned via an interface.
  • power 30, transforming the signal received from the processing unit 26 into a power current compatible with the solenoid 20 of the solenoid valve 2.
  • the control unit has an orifice 32 for supplying high pressure oil, preferably formed in the body 34 of the distributor 4.
  • This orifice is connected to a high pressure source (for example of the order of 150 to 250 bars) comprising a pump 36, a hydraulic accumulator 38 and a reservoir 40.
  • a filter 42 is interposed, giving for example filtration at 3 microns.
  • the control unit also includes an orifice 44 for discharging low-pressure oil which is also preferably formed in the body 34 of the distributor.
  • the electro-valve 2 is a three-way valve, supply / purge, the body 46 of which is attached to the body of the distributor 34.
  • the body 46 comprises: a high pressure inlet 48 which is permanently connected to the high pressure orifice 32 by holes 50-52 drilled in the body 34 of the distributor; a low pressure outlet 54 which is permanently connected to the low pressure orifice 44 by a bore 56 drilled in the body 34; and a use orifice 58 which is in communication with a chamber 60 of the dispenser.
  • the shutter orqane of the solenoid valve 2 is constituted by a valve, such as a ball 62, on which the rod 64 of the solenoid 20 acts in thrust when the latter is excited. In the rest position (not excited) shown in the figure, the chamber 60 is under pressure. In the working position (energized), the ball 62 discovers the purge pipe 54 and closes the high-pressure line 48, which puts the chamber 60 to the low pressure.
  • the solenoid 20 and its rod 64 are always subjected to the bass pressure, which avoids any sealing system and seals likely to increase friction in the solenoid valve.
  • the electro-valve 2 plays the role of a low-flow servovalve controlling the distributor 4 which, in turn, is a high-flow power valve controlling the power cylinder 6.
  • the distributor 4 is also a three-way valve which comprises, in addition to the two high pressure and low pressure orifices 32, 44 already mentioned, a third orifice 66, orifice for use, which is connected to the working chamber 68 of the jack power.
  • the switching member of the distributor 4 is constituted by a slide 70 which slides in a bore 72 drilled in the body 34 of the distributor.
  • the drawer 70 has four openings 74 1 , 74 2 , 743 , 744 sliding in leaktight manner in the bore 72 and delimiting the switching channels of the distributor.
  • the actuation of the drawer 70 is hydraulically controlled by a pilot cylinder, the piston 76 of which is formed by one of the ends (the left end in FIG. 1) of the drawer which enters the chamber 60.
  • the other end 78 of the drawer 70 also constitutes a piston, of smaller cross section than piston 76, which opens into a chamber 80 which is formed in the distributor body 34 and which is permanently subjected to high pressure by communication with a pipe 82 communicating with it. even with 50-32 holes.
  • a pilot cylinder the piston 76 of which is formed by one of the ends (the left end in FIG. 1) of the drawer which enters the chamber 60.
  • the other end 78 of the drawer 70 also constitutes a piston, of smaller cross section than piston 76, which opens into a chamber 80 which is formed in the distributor body 34 and which is permanently subjected to high pressure by communication with a pipe 82 communicating with it. even with 50-32 holes.
  • the power jack 6 comprises a jack body 86 in which a jack cylinder 88 is hollowed out receiving the piston 90 of the jack, which is connected to the pusher 10 by a jack rod 92.
  • Return means are provided to return the piston 90 to the rest position shown in Figure 1. These return means may be constituted by a spring, but preferably a hydraulic return means is used.
  • the chamber 93 located opposite the working chamber 60 relative to the piston is permanently subjected to high pressure by a line 94-96 which is pierced in the body of the jack 86 and which communicates with the high pressure line 50-32 of the distributor body.
  • the cylinder 6 therefore functions as a double-acting differential cylinder and it is the difference in section between the piston 90 and the rod 92 which produces the displacement of the piston towards its working position.
  • End-of-travel damping members are also provided for the piston of the jack, which will be described below with reference to FIG. 2.
  • control unit The operation of the control unit is as follows: starting from the rest position shown in FIG. 1, with the high pressure supply in service, when the electronic control system 22, 24, 26, 30 issues an opening order of the valve, the finger 64 of the solenoid 20 pushes the ball 62 which closes the high pressure inlet 48 and places the line 58 in communication with the low pressure lines 54, 44.
  • the chamber 60 of the pilot cylinder 76 of the distributor is thus brought to low pressure and the drawer 70 is unbalanced, that is to say it is pushed to the left by the high pressure exerted permanently on its end. 78.
  • the opening order is an order to put the pilot cylinder 76 at low pressure, an order whose response is faster, at the high pressures used, than an order to increase in pressure. .
  • the openings 74 2 , 74 3 of the drawer 70 put the orifice 66 of the dispenser into communication with the high pressure inlet 32 and isolate this orifice 66 from the low pressure outlet 44.
  • the high pressure oil is thus introduced into the working chamber 68 of the power cylinder.
  • the high pressure oil being on either side of the piston 90, in the chambers 68 and 93, it is the difference in section which creates the displacement of the assembly 90, 92, 10 and the force to be communicated to the valve 14 to open it, against the force of the valve spring 18.
  • the electrical signal ceases and the solenoid 20 is no longer energized.
  • the ball 62 closes the return 54, 44 at the low pressure and again admits this high pressure in the chamber 60 dtr distributor.
  • the drawer 70 is again unbalanced and moves to the right until the position of FIG. 1 for which the working chamber 68 of the power cylinder is put in communication with the bass pressure.
  • the chamber 93 is still under pressure, the piston 90 rises and returns to its rest position in which the valve is closed.
  • the frequency of opening of the valves being relatively high (for example 20 to 30 Hz), one of the difficulties, for the proper functioning of a control unit according to the invention, consists in maintaining the integrity of the lines. and their correct filling, without oil emulsion or cavitation.
  • the presence of the accumulator 38 in the high pressure supply circuit promotes control of the hydraulic lines, but it is also advantageous to provide for the maintenance of a residual pressure in the low pressure circuit.
  • a tared retaining valve 98 (for example tared for 3 to 10 bars) is mounted on the low pressure outlet orifice 44, this valve preferably being incorporated in the distributor body 34.
  • the purge oil from the pilot cylinder 76, 60 and from the power cylinder returns to a tank 100 at atmospheric pressure which can advantageously be formed, when the engine oil is used. even in the hydraulic circuit of the control unit, by the cylinder head, so as to grease the mechanical connection assemblies (ball joints, rocker arms, etc.) between the pusher 10 and the valves.
  • control unit according to the invention makes it possible to obtain opening and closing speeds of the valves which would be mechanically impracticable, the mechanical system being limited by the accelerations linked to the profiles of the cams.
  • FIG. 1 This figure is a partial sectional view of the central part of Figure 1.
  • the piston 90 of the power cylinder 6 has, at its upper part, a projecting collar 102 which penetrates, with reduced clearance, into a bore 104 delimiting the working chamber 68 of the power cylinder, at the upper end of stroke of the piston 90.
  • One or more slots 106 are provided in the flange 102 to produce a rolling of the oil discharged by the piston 90 when the latter rises to 'to its rest end position.
  • a conical portion 108 is provided which, at the end of the low stroke of the piston 90, enters a damping ring 110.
  • the internal bore 112 of this ring determines, with the conical portion 108, an annular slot with variable section for the rolling of the oil at the bottom end of the piston stroke. It should be noted that, in this ring 110 are pierced the passages 96 (see FIG. 1) for supplying high pressure oil to the lower chamber 93 of the power cylinder 6.
  • damping systems it is possible to apply a high opening and closing speed to the valves, without shock to the end-of-travel components. This also makes it possible to carry out brief intermediate reopening of the exhaust valves at certain speeds to reduce the thermal load on the valves or to heat the intake air.
  • FIG. 1 shows the control of a single valve by means of the control unit according to the invention.
  • mechanical connections are provided by ball joints, similar to those of rocker arms or rocker rods, to avoid parasitic effects due to misalignments.
  • control unit provides great security because, in the event of an operating anomaly (lack of hydraulic pressure, lack of electrical signal on the electro-valve), the unit always returns to the rest position shown in Figure 1, with the corresponding valve or valves in the closed position, which avoids any risk of valve / piston impact towards top dead center.
  • control unit is very compact, which allows the accommodation of two assemblies (intake and exhaust) in an existing engine cylinder head.
  • the assembly constituted by the solenoid valve 2 and the distributor 4 can be standard regardless of the type of engine, which reduces cost prices.
  • the power cylinder 6 can also include a majority of standard components, the cylinder being simply adapted to the forces required by such or such type of motor by modification of its differential section, which allows adaptation to any existing motor.
  • the invention makes it possible to obtain durations and instants of opening of the variable valves according to the most favorable valve lift law as a function of the various operating parameters of the engine (speed, power, etc.), which was impossible with cam operated valves. It is even possible, with a suitable program, to operate on a reduced number of cylinders at low load (without losses by transfer) and, also, a simple and immediate reversibility of the engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP84401876A 1983-09-23 1984-09-21 Elektro-Hydraulikblock zum Steuern der Ventile einer Brennkraftmaschine Expired EP0139566B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8315128A FR2552492B1 (fr) 1983-09-23 1983-09-23 Bloc electro-hydraulique de commande des soupapes pour moteur a combustion interne
FR8315128 1983-09-23

Publications (2)

Publication Number Publication Date
EP0139566A1 true EP0139566A1 (de) 1985-05-02
EP0139566B1 EP0139566B1 (de) 1987-04-08

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Application Number Title Priority Date Filing Date
EP84401876A Expired EP0139566B1 (de) 1983-09-23 1984-09-21 Elektro-Hydraulikblock zum Steuern der Ventile einer Brennkraftmaschine

Country Status (4)

Country Link
EP (1) EP0139566B1 (de)
JP (1) JPS6090909A (de)
DE (1) DE3463072D1 (de)
FR (1) FR2552492B1 (de)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3806969A1 (de) * 1988-03-03 1989-09-14 Rexroth Mannesmann Gmbh Elektrohydraulische stelleinrichtung zur betaetigung von gaswechselventilen bei brennkraftmaschinen
EP0441100A1 (de) * 1990-02-08 1991-08-14 GebràœDer Sulzer Aktiengesellschaft Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine
WO1993001399A1 (en) * 1991-07-12 1993-01-21 Caterpillar Inc. Recuperative engine valve system and method of operation
EP0550925A2 (de) * 1991-12-11 1993-07-14 Koninklijke Philips Electronics N.V. Vorgesteuertes hydraulisches Ventilstellglied
EP0736671A2 (de) * 1995-04-05 1996-10-09 Ford Motor Company Limited Ausgleich der Ventilbewegung bei einer elektro-hydraulischen nockenfreien Ventilsteuerungsvorrichtung
EP0747576A1 (de) * 1995-06-06 1996-12-11 Caterpillar Inc. Dynamische Positionierungsvorrichtung für Motorbremssteuervorrichtung
EP0849439A1 (de) * 1996-12-19 1998-06-24 Eaton Corporation Ventilstellglied mit Differentialkolben für Brennkraftmaschine
FR2815076A1 (fr) * 2000-10-07 2002-04-12 Hidraulik Ring Gmbh Dispositif de commutation pour commuter des soupapes d'admission/echappement pour des moteurs a combustion interne
US7004120B2 (en) 2003-05-09 2006-02-28 Warren James C Opposed piston engine
EP1843013A2 (de) * 2006-03-30 2007-10-10 Dell'orto S.P.A. Elektrohydraulisches system und Vorrichtung zur variablen Betätigung der Ventile einer Brennkraftmaschine
CN105378299A (zh) * 2013-07-08 2016-03-02 弗瑞瓦勒夫股份公司 用于物体的轴向位移的致动器
CN110341967A (zh) * 2018-04-04 2019-10-18 林建国 气动肌肉降落伞
CN110593983A (zh) * 2019-10-29 2019-12-20 中船动力研究院有限公司 一种集成式低压补油排气阀驱动装置
CN113217135A (zh) * 2021-05-12 2021-08-06 无锡威孚高科技集团股份有限公司 电控液压全可变气门驱动机构

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2585765B1 (fr) * 1985-08-02 1989-06-30 Alsacienne Constr Meca Dispositif de commande electro-hydraulique des soupapes pour moteur a combustion interne
US4724801A (en) * 1987-01-15 1988-02-16 Olin Corporation Hydraulic valve-operating system for internal combustion engines
SU1621816A3 (ru) * 1987-02-10 1991-01-15 Интератом Гмбх (Фирма) Гидравлическое устройство управлени клапанами двигател внутреннего сгорани
JPH0541207Y2 (de) * 1987-10-12 1993-10-19
JPH0614412U (ja) * 1991-05-30 1994-02-25 自動車部品工業株式会社 エンジンの油圧式弁駆動装置
US5255641A (en) 1991-06-24 1993-10-26 Ford Motor Company Variable engine valve control system
US5647318A (en) 1994-07-29 1997-07-15 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
US6067946A (en) * 1996-12-16 2000-05-30 Cummins Engine Company, Inc. Dual-pressure hydraulic valve-actuation system
KR100254636B1 (ko) * 1997-12-29 2000-05-01 정몽규 디젤 엔진용 밸브 개폐 장치
DE102009052586A1 (de) 2009-11-10 2011-05-12 Valeo Schalter Und Sensoren Gmbh Gehäuse für eine Kamera
SE540409C2 (sv) * 2013-10-16 2018-09-11 Freevalve Ab Förbränningsmotor samt kåpsammansättning därför

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2962013A (en) * 1957-12-13 1960-11-29 Ferdinando C Reggio Engine valve mechanism
FR2059174A5 (de) * 1969-08-30 1971-05-28 Bosch
DE2151331A1 (de) * 1971-10-15 1973-04-19 Bosch Gmbh Robert Steuerung von ein- und auslassventilen bei brennkraftmaschinen durch fluessigkeit
US3877483A (en) * 1974-05-10 1975-04-15 Konan Electric Co Solenoid operated four port valve
US4000756A (en) * 1974-03-25 1977-01-04 Ule Louis A High speed engine valve actuator
US4313468A (en) * 1977-07-13 1982-02-02 Dynex/Rivett Inc. Servo valve

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR938061A (fr) * 1943-03-31 1948-09-03 Autocostruzioni Diatto Dispositif de commande de soupapes et organes analogues de distribution dans les moteurs à combustion interne
FR1378676A (fr) * 1964-01-02 1964-11-13 Ruston & Hornsby Ltd Dispositif hydraulique pour la commande des soupapes de moteurs à combustion interne
GB1205700A (en) * 1968-11-11 1970-09-16 Parker Hannifin Corp Pilot valve operated valve assemblies
DE2904293A1 (de) * 1979-02-05 1980-08-07 Claas Ohg Hydraulisches steuerventil

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2962013A (en) * 1957-12-13 1960-11-29 Ferdinando C Reggio Engine valve mechanism
FR2059174A5 (de) * 1969-08-30 1971-05-28 Bosch
DE2151331A1 (de) * 1971-10-15 1973-04-19 Bosch Gmbh Robert Steuerung von ein- und auslassventilen bei brennkraftmaschinen durch fluessigkeit
US4000756A (en) * 1974-03-25 1977-01-04 Ule Louis A High speed engine valve actuator
US3877483A (en) * 1974-05-10 1975-04-15 Konan Electric Co Solenoid operated four port valve
US4313468A (en) * 1977-07-13 1982-02-02 Dynex/Rivett Inc. Servo valve

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3806969A1 (de) * 1988-03-03 1989-09-14 Rexroth Mannesmann Gmbh Elektrohydraulische stelleinrichtung zur betaetigung von gaswechselventilen bei brennkraftmaschinen
EP0441100A1 (de) * 1990-02-08 1991-08-14 GebràœDer Sulzer Aktiengesellschaft Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine
WO1993001399A1 (en) * 1991-07-12 1993-01-21 Caterpillar Inc. Recuperative engine valve system and method of operation
EP0550925A2 (de) * 1991-12-11 1993-07-14 Koninklijke Philips Electronics N.V. Vorgesteuertes hydraulisches Ventilstellglied
EP0550925A3 (en) * 1991-12-11 1993-10-27 Philips Nv Pilot operated hydraulic valve actuator
EP0736671A2 (de) * 1995-04-05 1996-10-09 Ford Motor Company Limited Ausgleich der Ventilbewegung bei einer elektro-hydraulischen nockenfreien Ventilsteuerungsvorrichtung
EP0736671A3 (de) * 1995-04-05 1997-11-12 Ford Motor Company Limited Ausgleich der Ventilbewegung bei einer elektro-hydraulischen nockenfreien Ventilsteuerungsvorrichtung
EP0747576A1 (de) * 1995-06-06 1996-12-11 Caterpillar Inc. Dynamische Positionierungsvorrichtung für Motorbremssteuervorrichtung
EP0849439A1 (de) * 1996-12-19 1998-06-24 Eaton Corporation Ventilstellglied mit Differentialkolben für Brennkraftmaschine
FR2815076A1 (fr) * 2000-10-07 2002-04-12 Hidraulik Ring Gmbh Dispositif de commutation pour commuter des soupapes d'admission/echappement pour des moteurs a combustion interne
US7004120B2 (en) 2003-05-09 2006-02-28 Warren James C Opposed piston engine
EP1843013A2 (de) * 2006-03-30 2007-10-10 Dell'orto S.P.A. Elektrohydraulisches system und Vorrichtung zur variablen Betätigung der Ventile einer Brennkraftmaschine
EP1843013A3 (de) * 2006-03-30 2009-09-09 Dell'orto S.P.A. Elektrohydraulisches system und Vorrichtung zur variablen Betätigung der Ventile einer Brennkraftmaschine
CN105378299A (zh) * 2013-07-08 2016-03-02 弗瑞瓦勒夫股份公司 用于物体的轴向位移的致动器
CN105378299B (zh) * 2013-07-08 2017-08-08 弗瑞瓦勒夫股份公司 用于物体的轴向位移的致动器
CN110341967A (zh) * 2018-04-04 2019-10-18 林建国 气动肌肉降落伞
CN110593983A (zh) * 2019-10-29 2019-12-20 中船动力研究院有限公司 一种集成式低压补油排气阀驱动装置
CN110593983B (zh) * 2019-10-29 2024-05-14 中船动力研究院有限公司 一种集成式低压补油排气阀驱动装置
CN113217135A (zh) * 2021-05-12 2021-08-06 无锡威孚高科技集团股份有限公司 电控液压全可变气门驱动机构
CN113217135B (zh) * 2021-05-12 2022-02-08 无锡威孚高科技集团股份有限公司 电控液压全可变气门驱动机构

Also Published As

Publication number Publication date
DE3463072D1 (en) 1987-05-14
EP0139566B1 (de) 1987-04-08
JPS6090909A (ja) 1985-05-22
FR2552492B1 (fr) 1988-01-15
FR2552492A1 (fr) 1985-03-29

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