EP0405187A1 - Dispositif électromagnétique de positionnement - Google Patents

Dispositif électromagnétique de positionnement Download PDF

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Publication number
EP0405187A1
EP0405187A1 EP90110559A EP90110559A EP0405187A1 EP 0405187 A1 EP0405187 A1 EP 0405187A1 EP 90110559 A EP90110559 A EP 90110559A EP 90110559 A EP90110559 A EP 90110559A EP 0405187 A1 EP0405187 A1 EP 0405187A1
Authority
EP
European Patent Office
Prior art keywords
actuating device
transmission system
spring
armature
equilibrium position
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
EP90110559A
Other languages
German (de)
English (en)
Other versions
EP0405187B1 (fr
Inventor
Peter Dr.-Ing. Kreuter
Armin Dipl.-Ing. Zoschke
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.)
FEV Europe GmbH
Original Assignee
FEV Motorentechnik GmbH and Co KG
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 FEV Motorentechnik GmbH and Co KG filed Critical FEV Motorentechnik GmbH and Co KG
Priority to AT90110559T priority Critical patent/ATE95277T1/de
Publication of EP0405187A1 publication Critical patent/EP0405187A1/fr
Application granted granted Critical
Publication of EP0405187B1 publication Critical patent/EP0405187B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • F01L1/182—Centre pivot rocking arms the rocking arm being pivoted about an individual fulcrum, i.e. not about a common shaft
    • 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
    • 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
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • 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
    • F01L1/18—Rocking arms or levers
    • F01L2001/188—Fulcrums at upper surface
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/20—Control lever and linkage systems
    • Y10T74/20576—Elements
    • Y10T74/20882—Rocker arms

Definitions

  • the invention relates to an electromagnetically operating control device for oscillatingly movable control elements on displacement machines, in particular for flat slide valves and globe valves, consisting of a spring system and two electrically operating switching magnets, by means of which an armature actuating the control element can be moved into two discrete, opposite switching positions and from there one of the switching magnets is durable, the location of the equilibrium position of the spring system between the two switching positions.
  • Such an actuator is known from DE-OS 30 24 109.
  • the control element of a displacement machine is held in the closed state by a compression spring in an actuating device of the type listed.
  • Another compression spring acts on a magnet armature interacting with the control element, so that the equilibrium position of the spring system lies in the middle or near the middle between the end positions of the movement of the magnet armature.
  • the end positions of the armature movement are each located on an electrically operated switching magnet. To switch this device, one switching magnet is energized and the other switched off. Due to the force of the prestressed spring, the armature is accelerated to the equilibrium position and decelerated on its further path by the then counteracting force of the other spring. Due to friction, the armature cannot reach the opposite end position. On the missing remaining path, the armature is attracted by the tensile force of the switching magnet.
  • this system achieves a substantial reduction in size since the radial dimension of the winding window can be kept small due to the smaller air gap to be bridged. This is particularly important with regard to the use of the actuating device on displacement machines.
  • the working stroke of such an actuating device is to be dimensioned such that a sufficient opening cross-section is available for the largest mass flow occurring at the control element of a displacement machine and thus throttling is avoided.
  • operation of the actuating device at this maximum working stroke is uneconomical, since the electrical energy to be supplied for changing the position of the control element increases as a function of the stroke of the control element.
  • the reduction in the opening cross-section results in an increase in the flow speed at the control element, which contributes to the improvement of the preparation of multiphase mixtures, in particular an air-fuel mixture in internal combustion engines.
  • the executable maximum stroke of the control valve is, however, limited in the known design by the dimensions of the actuating device and by the predetermined positioning in the extension of the valve axis and cannot be changed.
  • the present invention has for its object to achieve a flexible adaptation of the actuating device to the respective operating conditions and at the same time energy savings with the most compact possible dimensions of the actuating device and free arrangement of the actuating device in the receptacle, in particular in a cylinder head for an internal combustion engine.
  • This object is achieved in that the switching stroke of the actuating device via a gear ratio variable transmission system, in particular a rocker arm or rocker arm, is transmitted to the control element, that is to say, in the case of displacement machines, to the globe valve or the flat slide valve.
  • a gear ratio variable transmission system in particular a rocker arm or rocker arm
  • the transmission system is designed as a hydraulic transmission which is variable in the transmission ratio.
  • the vibratory spring-mass system with compression springs on both sides of the armature is designed according to a further embodiment of the invention so that the springs or spring assemblies are divided into springs arranged on the magnet side and springs arranged on the control element.
  • a plurality of control elements cooperate with one transmission system each, with valve displacement machines each having a transmission system per valve or a common transmission system for several valves.
  • the non-moving base point of one or more springs of the vibratable system is designed to be adjustable.
  • the aim here is that the adjustment in the receiving housing, in particular in the cylinder head of an internal combustion engine, is arranged so that it is easily accessible, since the correct setting of the equilibrium position takes place under operating conditions.
  • this adjustment takes place either directly by shifting wedge surfaces relative to one another or via a transmission member which is designed as a rocker arm or finger follower.
  • a hydraulic compensation element is provided for the play-free actuation of the oscillating components.
  • the compensating element can be arranged at different positions within the moving components, in particular in the transmission system or in the magnet armature.
  • the hydraulic compensating element is arranged between the receiving housing and the switching magnet assigned to the closed valve position, the axial displacement of the switching magnet compensating for the changes in length that occur in the moving components.
  • a further advantageous embodiment of the invention consists in the arrangement of the hydraulic compensating element between the mounting of the transmission element and the receiving housing or the adjusting element.
  • Another advantageous embodiment of the invention consists in the use of permanent magnets in the switching magnets.
  • Another embodiment of the invention relates to damping the armature movement shortly before reaching the end positions.
  • the base point of one of the springs or spring assemblies assigned to the oscillatory system can be adjusted according to further developments of the invention.
  • the magnetic resistance of the magnetic circuit of one or both working magnets is changed when the ratio of the transmission system changes and thus when the effective spring forces change, with the aim of changing the time between the switching off of the current Keep working magnets and the beginning of the armature movement, hereinafter called fall time, constant.
  • both the change in the magnetic resistance and the adjustment of the translation of the transmission element and the equilibrium position of the vibrating system are carried out by a common device.
  • the invention advantageously changes the switching stroke of the adjusting device and thus the effective opening cross-section of the lifting valve or flat slide valve while largely maintaining the compact dimensions of the adjusting device. Furthermore, compared to the arrangement of an actuating device in a direct extension of the shaft of the control element, an increase in the maximum stroke of the control element is possible. A further advantage is that the actuating device can be arranged around the valve stem within a radius predetermined by the transmission system, and thus greater freedom of design for the receiving housing is achieved. The invention also enables an exact adjustment of the equilibrium position of the vibrating system in the installed state, and the tracking of the equilibrium position of the vibrating system when the transmission ratio of the transmission system changes.
  • FIG. 1 shows an example of an electromagnetically operating actuating device with electromagnets 1 and 2, windings 3 and 4 and armature 5.
  • the electromagnets 1 and 2 are fixed in by a cover 6 and with the interposition of a cam ring 7 Housing 8 clamped.
  • the armature 5 is guided in a sleeve 53 and actuates a valve 12 via a rocker arm 10.
  • Pressure springs 13, 14 and 50 form the oscillating system, taking into account the transmission ratio of the rocker arm 10 with the armature 5, the rocker arm 10 and the valve 12.
  • the spring 14 is supported on the stem of the valve 12 via a spring plate 17.
  • the movement of the armature 5 is delayed near the pole face of the magnet 2 by compressing air.
  • the cam ring 7 is provided with shoulders such that the outflow cross-section 58 between the armature 5 and the cam ring 7 is reduced before the armature 5 hits the pole face.
  • the rocker arm 10 is supported in the adjusting member 52 via a hydraulic length compensation element 51.
  • the acting force of the prestressed compression spring 14 is supported on the valve seat 16 via the spring plate 17, the stem of the valve 12 and the valve plate 15.
  • the armature 5 rests on the switching magnet 2, with a holding force that is greater than the force of the prestressed compression spring 13 minus the force of the spring 50.
  • the rocker arm 10 is force-free, so that the hydraulic compensating element 51 used compensate for the lengthening that occurs can and thus ensures that when the armature 5 rests on the pole face of the electromagnet 2, the valve plate 15 rests in the valve seat 16.
  • a soft magnetic bushing 55 supported in the adjusting member 52 on an inclined plane 54 changes the prestressing of the spring 50 when the adjusting member 52 is actuated and thus corrects the equilibrium position of the oscillating system. Furthermore, the soft magnetic sleeve 55 contains an annular recess 56 which, when the sleeve 55 moves, is displaced relative to a magnetically non-permeable ring 57 arranged in the magnet 1. Depending on the position of the soft magnetic sleeve 55, this results in a different magnetic resistance in the magnetic circuit of the magnet 1.
  • the adjusting member 52 is moved to the left. This shortens lever arm 1 and lever arm 1 is extended. This increases both the biasing force of the spring 14 acting on the armature 5 and the spring stiffness which is reduced on the armature side.
  • the biasing force of the spring 50 is reduced by the movement of the sleeve 55.
  • the increasing with increasing stroke holding forces on the opening magnet 1 are compensated for by reducing the magnetic resistance in the magnet 1, so that the required holding current and the fall time of the armature remain constant. This change is also caused by the movement of the sleeve 55.
  • the process is analogous when the stroke is reduced.
  • Figure 2 shows an electromagnetically operating actuator with a hydraulic transmission system consisting of the electromagnets 1 and 2, the armature 5, the valve 12 and the springs 13, 14 and 50.
  • the armature 5 displaces oil from a space 60 during its movement is located in cover 63 of the actuating device, through line 61 in cylinder 62.
  • cylinder 62 there is a three-part piston consisting of mushroom 64 and bushes 65 and 66. These have a bore 67 and 68 on the circumference, as well as cylinder 62 The bores of all three components are aligned when the valve 12 is in the closed position.
  • the adjusting member 69 has at its end a pin-shaped projection 70 which is guided in a bore 71 of the cylinder 62 and can engage in the bores 67 and 68 when the adjusting member 69 is displaced . This allows the sockets 65 and 66 to be locked.
  • the transmission ratio results from the ratio of the diameters of the acting cylinders d1 to d2, d3 and d4.
  • the adjusting member 69 has an inclined plane 73 which adjusts the prestress of the spring 50 via a bush 74 and a spring plate 75 and thus the equilibrium position of the oscillating one Systems tracks.
  • FIGS. 3 and 4 show an arrangement of 2 rocker arms 20 and 21 for actuating two valves or slides 22 and 23, respectively.
  • FIG. 5 shows an arrangement for actuating two valves or slides by means of a common rocker arm 26. This enables two or more valves or slides to be actuated with a small valve distance.
  • Figure 6 shows a device for adjusting the equilibrium position of the vibrating system.
  • the position of the base point of the spring 13 is adjusted via two components 27 and 28 with wedge surfaces.
  • the component 27 is guided in a bore 29 of the housing 8.
  • Component 28 lies on the flat bottom 30 of the bore 29 and contains a radial threaded bore 31.
  • a bolt 32 is locked in the housing 8 by a stop 33 in its axial displacement and moves the component 28 in the direction of the longitudinal axis of the bolt when it rotates.
  • the device is self-locking.
  • FIG. 7 shows a device for adjusting the equilibrium position in accordance with the previously described type, but here a screw 34 with a wedge-shaped beveled surface 35 forms the counterpart to component 27.
  • the wedge surfaces are only opposite one another at a precisely defined position per revolution of the screw 34, so that the equilibrium position is set in discrete steps.
  • the device described is self-locking.
  • FIG. 8 shows a device for adjusting the equilibrium position, which is accessible in an axis parallel to the longitudinal axis 85 of the adjusting device.
  • a lever 36 rests on an abutment 37 and is positioned by an adjusting screw 38, which is supported in the housing 8.
  • the other end of the adjusting lever 36 acts on Fe via a guided pin 39 derunterlage 40.
  • the device described is self-locking if the thread pitch of the screw 38 is chosen accordingly.
  • FIG. 9 shows a further possible arrangement of a hydraulic compensating element 76 between the housing 8 and the magnet 2 of an electromagnetic actuating device assigned to the closed position.
  • the axially displaceable assembly consisting of the magnets 1 and 2 and the lifting ring 7, can establish the frictional connection between the armature 5, the rocker arm 10 and the valve by the force of a compression spring acting in the compensating element 76.
  • FIGS. 10 and 11 show further possible arrangements of the compensating element on the rocker arm 10.
  • FIG. 12 shows a possible arrangement of the actuating unit 43, transmission element 10 and control element 12, the force being transmitted via a push rod 44.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)
  • Servomotors (AREA)
  • Switches With Compound Operations (AREA)
  • Massaging Devices (AREA)
EP90110559A 1989-06-27 1990-06-05 Dispositif électromagnétique de positionnement Expired - Lifetime EP0405187B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90110559T ATE95277T1 (de) 1989-06-27 1990-06-05 Elektromagnetisch arbeitende stelleinrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3920931A DE3920931A1 (de) 1989-06-27 1989-06-27 Elektromagnetisch arbeitende stelleinrichtung
DE3920931 1989-06-27

Publications (2)

Publication Number Publication Date
EP0405187A1 true EP0405187A1 (fr) 1991-01-02
EP0405187B1 EP0405187B1 (fr) 1993-09-29

Family

ID=6383624

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90110559A Expired - Lifetime EP0405187B1 (fr) 1989-06-27 1990-06-05 Dispositif électromagnétique de positionnement

Country Status (4)

Country Link
US (1) US5117213A (fr)
EP (1) EP0405187B1 (fr)
AT (1) ATE95277T1 (fr)
DE (2) DE3920931A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996005415A1 (fr) * 1994-08-08 1996-02-22 Fev Motorentechnik Gmbh & Co. Kommanditgesellschaft Dispositif de frein moteur destine a un moteur de vehicule utilitaire
EP0799394A1 (fr) * 1994-04-28 1997-10-08 Aura Systems, Inc. Modele de soupapes echelonnees a actionnement electromagnetique
EP0867898A1 (fr) * 1997-03-24 1998-09-30 Binder Magnete GmbH Dispositif électromagnétique de positionnement
EP1087110A1 (fr) * 1999-09-23 2001-03-28 MAGNETI MARELLI S.p.A. Actionneur électromagnétique pour soupape de moteur à combustion interne
FR2989416A1 (fr) * 2012-04-16 2013-10-18 Valeo Sys Controle Moteur Sas Dispositif d'actionnement d'une soupape electronique

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US5548263A (en) * 1992-10-05 1996-08-20 Aura Systems, Inc. Electromagnetically actuated valve
US5339777A (en) * 1993-08-16 1994-08-23 Caterpillar Inc. Electrohydraulic device for actuating a control element
US5608369A (en) * 1995-07-25 1997-03-04 Outboard Marine Corporation Magnetic gap construction
DE19647305C1 (de) * 1996-11-15 1998-02-05 Daimler Benz Ag Vorrichtung zur elektromagnetischen Betätigung eines Gaswechselventils
EP0970295B1 (fr) * 1997-03-24 2001-06-20 LSP Innovative Automotive Systems GmbH Dispositif d'entrainement electromagnetique
JP3831104B2 (ja) * 1997-05-13 2006-10-11 株式会社日立製作所 吸排気弁の電磁駆動装置
DE19737967A1 (de) 1997-08-30 1999-03-04 Telefunken Microelectron Vorrichtung zum Betätigen eines Gaswechselventils mit einem elektromagnetischen Aktuator
US6116570A (en) * 1998-03-30 2000-09-12 Siemens Automotive Corporation Electromagnetic actuator with internal oil system and improved hydraulic lash adjuster
DE19835402C1 (de) * 1998-08-05 2000-02-10 Meta Motoren Energietech Elektromagnetisch arbeitende Vorrichtung zum Betätigen eines Ventils
US6763790B2 (en) * 1998-09-09 2004-07-20 International Engine Intellectual Property Company, Llc Poppet valve actuator
US6786186B2 (en) * 1998-09-09 2004-09-07 International Engine Intellectual Property Company, Llc Unit trigger actuator
JP3835024B2 (ja) * 1998-11-19 2006-10-18 トヨタ自動車株式会社 内燃機関の電磁駆動装置
DE19858758C1 (de) * 1998-12-18 2000-09-07 Siemens Ag Vorrichtung und Verfahren zur Hubübertragung
JP3872230B2 (ja) 1999-05-07 2007-01-24 株式会社日立製作所 吸排気弁の電磁駆動装置
DE19927823B4 (de) * 1999-06-18 2004-08-12 Daimlerchrysler Ag Elektromagnetischer Aktuator und Verfahren zur Justierung des elektromagnetischen Aktuators
DE19944698C2 (de) * 1999-09-18 2003-03-06 Daimler Chrysler Ag Hubkolbenbrennkraftmaschine
DE10005247C1 (de) * 2000-02-05 2001-02-15 Daimler Chrysler Ag Vorrichtung zum Betätigen eines Gaswechselventils einer Brennkraftmaschine
US6570474B2 (en) 2000-02-22 2003-05-27 Siemens Automotive Corporation Magnetostrictive electronic valve timing actuator
DE10010048C5 (de) * 2000-03-02 2005-12-22 Daimlerchrysler Ag Vorrichtung zum Betätigen eines Gaswechselventils mit einem elektromagnetischen Aktuator
DE10051076C2 (de) 2000-10-14 2003-12-18 Daimler Chrysler Ag Verfahren zur Herstellung eines elektromagnetischen Aktuators
EP1375844A4 (fr) * 2001-03-29 2011-04-06 Isuzu Motors Ltd Dispositif de commande de soupape de moteur a combustion interne
DE10120401A1 (de) * 2001-04-25 2002-10-31 Daimler Chrysler Ag Vorrichtung zur Betätigung eines Gaswechselventils
DE10248330A1 (de) * 2002-10-17 2004-04-29 Bayerische Motoren Werke Ag Elektromagnetische Ventiltriebvorrichtung mit einstellbarer Neutralstellung
DE20305920U1 (de) * 2003-04-11 2003-08-14 Trw Deutschland Gmbh Vorrichtung zur nockenwellenlosen Betätigung eines Gaswechselventils
US6889636B2 (en) * 2003-09-03 2005-05-10 David S. W. Yang Two-cycle engine
FR2860032B1 (fr) * 2003-09-24 2007-07-20 Peugeot Citroen Automobiles Sa Dispositif de commande de soupape pour moteur a combustion interne et moteur a combustion interne comprenant un tel dispositif
FR2873232B1 (fr) * 2004-07-16 2008-10-03 Peugeot Citroen Automobiles Sa Dispositif de commande electromagnetique fonctionnant en basculement
US7347172B2 (en) * 2005-05-10 2008-03-25 International Engine Intellectual Property Company, Llc Hydraulic valve actuation system with valve lash adjustment
US8327474B2 (en) * 2008-12-23 2012-12-11 Van Zeeland Anthony J Magnetic drain stopper assembly

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FR1233442A (fr) * 1959-08-26 1960-10-12 Procédé de commande des soupapes des moteurs à explosion
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FR2504189A1 (fr) * 1981-04-16 1982-10-22 Maschf Augsburg Nuernberg Ag Dispositif hydraulique pour la commande des soupapes de circulation de gaz
GB2097084A (en) * 1981-04-16 1982-10-27 Maschf Augsburg Nuernberg Ag Hydraulic device for actuating gas change
EP0244878A2 (fr) * 1985-02-11 1987-11-11 INTERATOM Gesellschaft mit beschränkter Haftung Commande électromagnétique-hydraulique de soupapes des moteurs à combustion interne
EP0245614A1 (fr) * 1986-05-16 1987-11-19 Dr.Ing.h.c. F. Porsche Aktiengesellschaft Dispositif de commande de soupape pour un moteur à combustion interne à piston alternatif
US4777915A (en) * 1986-12-22 1988-10-18 General Motors Corporation Variable lift electromagnetic valve actuator system
US4831973A (en) * 1988-02-08 1989-05-23 Magnavox Government And Industrial Electronics Company Repulsion actuated potential energy driven valve mechanism

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0799394A1 (fr) * 1994-04-28 1997-10-08 Aura Systems, Inc. Modele de soupapes echelonnees a actionnement electromagnetique
EP0799394A4 (fr) * 1994-04-28 1997-10-08
WO1996005415A1 (fr) * 1994-08-08 1996-02-22 Fev Motorentechnik Gmbh & Co. Kommanditgesellschaft Dispositif de frein moteur destine a un moteur de vehicule utilitaire
US5730102A (en) * 1994-08-08 1998-03-24 Fev Motorentechnik Gmbh & Co. Kommanditgesellschaft Engine brake device for a commercial vehicle
EP0867898A1 (fr) * 1997-03-24 1998-09-30 Binder Magnete GmbH Dispositif électromagnétique de positionnement
EP1087110A1 (fr) * 1999-09-23 2001-03-28 MAGNETI MARELLI S.p.A. Actionneur électromagnétique pour soupape de moteur à combustion interne
US6427650B1 (en) 1999-09-23 2002-08-06 MAGNETI MARELLI S.p.A. Electromagnetic actuator for the control of the valves of an internal combustion engine
FR2989416A1 (fr) * 2012-04-16 2013-10-18 Valeo Sys Controle Moteur Sas Dispositif d'actionnement d'une soupape electronique

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ATE95277T1 (de) 1993-10-15
DE59002881D1 (de) 1993-11-04
DE3920931A1 (de) 1991-01-03
EP0405187B1 (fr) 1993-09-29
US5117213A (en) 1992-05-26

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