EP1144811B1 - Dispositif pour actionner une soupape de changement des gaz - Google Patents

Dispositif pour actionner une soupape de changement des gaz Download PDF

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Publication number
EP1144811B1
EP1144811B1 EP00901531A EP00901531A EP1144811B1 EP 1144811 B1 EP1144811 B1 EP 1144811B1 EP 00901531 A EP00901531 A EP 00901531A EP 00901531 A EP00901531 A EP 00901531A EP 1144811 B1 EP1144811 B1 EP 1144811B1
Authority
EP
European Patent Office
Prior art keywords
valve
spring
accordance
force
gas exchange
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.)
Expired - Lifetime
Application number
EP00901531A
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German (de)
English (en)
Other versions
EP1144811A1 (fr
Inventor
Fritz Kreitmann
Hagen MÜLLER
Alexander Von Gaisberg
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.)
Daimler AG
Original Assignee
DaimlerChrysler AG
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
Priority claimed from DE19956136A external-priority patent/DE19956136A1/de
Application filed by DaimlerChrysler AG filed Critical DaimlerChrysler AG
Publication of EP1144811A1 publication Critical patent/EP1144811A1/fr
Application granted granted Critical
Publication of EP1144811B1 publication Critical patent/EP1144811B1/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
    • F01L1/20—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
    • 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

Definitions

  • the invention relates to a device for actuating a Gas exchange valve according to the preamble of patent claim 1.
  • Electromagnetic actuators for actuating gas exchange valves usually have two solenoids, an opening magnet and a closing magnet, between the pole faces an armature arranged coaxially to a valve axis displaceable is.
  • the anchor acts directly or via an anchor tappet a valve stem of the gas exchange valve.
  • the principle of the mass oscillator is a preloaded spring mechanism on the anchor.
  • When not excited Magnets become the anchor through the valve springs in an equilibrium position held between the magnets.
  • the valve springs can work together on one side or each separately be arranged on both sides of the actuator.
  • the actuator is activated at startup, either the Closing magnet or the opening magnet for a short time overexcited or the armature with a start up routine at its resonant frequency stimulated to get out of equilibrium too become.
  • the closing magnet clamps in the opening direction acting valve spring further forward.
  • the closing magnet is turned off and the opening magnet is turned on.
  • the acting in the opening direction Valve spring accelerates the anchor over the equilibrium position out so that attracted by the opening magnet becomes.
  • the armature strikes the pole face of the opening magnet and is held by this.
  • the opening magnet is turned off and the closing magnet switched on.
  • the in closing direction acting valve spring accelerates the anchor over the equilibrium position out to the closing magnet.
  • the anchor is from the Attracted closing magnet, beats on the pole face of the Closing magnet on and is held by this.
  • Both Valve springs are biased so far that the anchor at de-energized solenoid to an approximately intermediate position between adjusts the pole faces of the solenoids and that simultaneously in or shortly before the closed position of the gas exchange valve a residual closing force from the lower valve spring acts on the gas exchange valve.
  • DE 19 647 305 C1 is an electromagnetic Actuator shown floating in a cylinder head is stored. He opens and closes a gas exchange valve, by moving its armature between two electromagnets is and thereby on a valve stem of the gas exchange valve acts.
  • a spring mechanism is between the actuator and the Valve disc arranged the gas exchange valve, wherein the upper opening spring on the actuator and the lower closing spring on the actuator Support cylinder head.
  • On the side facing away from the gas exchange valve Side is between one with the cylinder head connected cover plate and the actuator a clearance compensation element, which compensates for both positive and negative valve clearance.
  • the clearance compensation element has a piston in a cylinder on.
  • the piston separates a first, the gas exchange valve facing away, Internal combustion engine dependent controlled by a second, the gas exchange valve facing pressure chamber.
  • a check valve in the piston opens at overpressure in the first pressure chamber against the force of a retaining spring towards the second Pressure chamber.
  • the retaining spring is designed so that the check valve does not open when there is no game.
  • the gas exchange valve should always close safely. To this, too The clearance compensation element has the tendency to reach always to shorten slowly. This comes with a throttle point achieved by a defined play between the piston and the cylinder is formed. About the throttle point flows under load pressure medium from the second to the first pressure chamber. If the anchor no longer comes close enough to the closing magnet or creates a game between the anchor tappet and the Gas exchange valve, because the clearance compensation element too far must have a quick compensation in the opposite Direction, which with the opening Check valve is reached. The pressure in the second pressure chamber drops below that of the first pressure chamber, so that the check valve against the retaining spring opens and pressure medium from the first flows into the second pressure chamber until the game is balanced is. This process can be several working cycles of the valve take.
  • the iterative process with a fast and a slow one Compensation causes the gas exchange valve constantly moved in a range of optimal game setting. Becomes however, when the actuator is turned off, the armature will sag the valve springs to an equilibrium position between the magnets on. An average force of the valve springs acts via the actuator to the second pressure chamber. The pressure in the upper combustion engine-dependent controlled pressure chamber falls off and pressure medium flows through the throttle connections between the piston and the cylinder from the second pressure chamber. The Backlash element collapses and the actuator becomes upwards, shifted in the direction away from the gas exchange valve, whereby the equilibrium position of the valve springs adjusted becomes.
  • the piston is designed as an annular piston, is supported in the closing direction via a retaining ring on the valve stem and is slidably guided in the shell part, the same time serves as a cylinder of the second clearance compensation element.
  • the Ring piston separates a lower, on the gas exchange valve facing side pressure chamber from an upper, on the gas exchange valve side facing away from pantry.
  • the second clearance compensation element a Check valve on, over the pressure medium from the storage room via a breakthrough in the annular piston can flow to the pressure chamber.
  • the Check valve closes the breakthrough with a valve ball, with a preloaded helical compression spring in the direction Reservoir is pressed. Two more arranged in the pressure room Helical compression springs clamp the ring piston relative to Jacket part in front.
  • the safety valve is a check valve that has a second Breakthrough in the ring piston with a valve ball closes, the with a preloaded helical compression spring in the direction of the pressure chamber is pressed.
  • the helical compression spring is with regard to its biasing force designed so that the safety valve remains closed at forces that in a regular valve actuation occur. Should, however, in the valve operation due resonant vibrations or too high a lubricating oil pressure etc. inflating, i. a constant expansion of the second Compensatory elements would take place due to the constraint over the locking cam unacceptably high valve forces or pressures occur in the proposed embodiment can be reduced by opening the pressure relief valve. The same then applies if at a longer standstill of the internal combustion engine the first clearance compensation element empties has, and at the start before the second clearance compensation element the first clearance compensation element expands and thereby inadmissible high valve forces would arise.
  • the object of the invention is to provide a device for Actuation of gas exchange valves of an internal combustion engine with to create a compensation element that is characterized by an iterative Process with a fast and a slow compensation constantly is in a range of optimal setting, and this achieved as quickly as possible at the start of the engine.
  • the object is achieved by the features of the claim 1 solved, while advantageous embodiments and developments the invention are taken from the dependent claims can.
  • the compensation element retains at standstill the internal combustion engine his attitude at. This can be done happen that when stopping the engine, the compensation element mechanically, electrically or hydraulically blocked becomes.
  • a simple possibility is that the Outflow via the throttle point by means of a valve controllable is.
  • the valve may conveniently be a solenoid valve, in the de-energized state, the flow through the throttle point closes. It may depend on suitable operating parameters the internal combustion engine are driven, so that a drain from the pressure chamber only at certain periods of the actuation cycle the gas exchange valve is possible. Otherwise, will achieved in that the compensation element at standstill of Internal combustion engine is hydraulically blocked and thus its Retains setting.
  • the valve can be upstream or downstream of the throttle point to be ordered. If the throttle point by a Throttle gap formed between the piston and the cylinder, the valve is conveniently in a drain or return line arranged between the throttle gap and a the sealing ring surrounding the piston opens into the working cylinder.
  • An embodiment of the invention is based on the knowledge, that in devices for actuating gas exchange valves, the acting force on a compensating element during work cycles cyclically between a maximum and a minimum Value fluctuates, due to inertia forces, Pressure fluctuations in the cylinder head and in particular in devices, the at least one acting on the gas exchange valve Have valve spring, as well as by changing the clamping force over a work cycle.
  • These fluctuations only while the work games are being performed by the invention used, during the work cycles a defined leakage too reach and thus the tendency that the compensation element always slowly shortened or extended in special arrangements and that the compensation element at standstill of the internal combustion engine his attitude completely or at least almost unchanged.
  • a slow compensation of a desired iterative process in one direction is conveniently achieved with a high pressure valve.
  • About the high pressure valve flows during the work cycles throttled from a certain amount of pressure fluid by this cyclically opens at a defined force on the compensation element and closes at a defined force, the forces each greater than an average force and less than or equal to a maximum force the compensation element are.
  • a quick equalization of the iterative process in the opposite direction is achieved with a check valve. If the internal combustion engine is switched off, no cyclic fluctuations of the force occur on the compensation element.
  • the defined opening force of the high pressure valve in the region of a maximum force is not achieved or maintained only briefly in certain devices, for example in a device with a valve spring acting in the closing direction, in which the gas exchange valve stops in the open position. If the force acting on the compensating element at standstill of the internal combustion engine is less than the opening force, the high-pressure valve remains closed. Pressure fluid can not flow out of the pressure chamber sealed to the outside, whereby the compensating element retains its setting. If the acting force is greater than the opening force, only a small amount of pressure fluid flows until the closing force is reached and the high-pressure valve is closed. The adjustment of the compensation element is only slightly changed.
  • Electromagnetic gas exchange valve controls have an actuator, the one Opening magnet and a closing magnet has, between whose pole faces an armature is arranged coaxially displaceable and acts on a valve stem of the gas exchange valve. Further acts on the gas exchange valve, a spring mechanism with at least one acting in the opening direction and at least one in Closing direction biased valve spring.
  • the compensation element may be a clearance compensation element, a compensation element, adjustable with a valve spring preload is or another compensation element that is in the power flow an actuating element arranged on a gas exchange valve is.
  • An electromagnetic actuator 20 is in a recess 75th a cylinder head 25 is inserted, with a not closer shown cylinder head cover 26 is closed.
  • the actuator 20 actuates a gas exchange valve 7, with its valve stem 24 by means of a valve guide 27 in the cylinder head 25 is performed.
  • the actuator 20 has two solenoids, and although an upper closing magnet 22 and a lower opening magnet 21. Between the pole faces of the solenoids 21st and 22, an armature 23 moves over an armature tappet 28 acts on the valve stem 24 of the gas exchange valve 7.
  • a spring housing 29 is provided, in which a spring mechanism, consisting of two valve springs 10 and 11, is housed.
  • the upper valve spring 10 acts with one end on one with the Gas exchange valve 7 moved spring plate 30 in the opening direction 18 and is supported by the other end of the opening magnet 21 off.
  • the lower valve spring 11 acts with one end on a with the gas exchange valve 7 moving spring plate 31 in the closing direction 17 and is based on a spring rest at the other end 19 off.
  • the illustrations show the actuator 20 in the closed position, in which the closing magnet 22 is energized and the armature 23rd rests against the pole face of the closing magnet 22. simultaneously the gas exchange valve 7 is closed by its valve plate 32 is seated on a valve seat ring 33 in the cylinder head 25th is recessed and forms the opening of a gas exchange channel 34. If the closing magnet 22 is de-energized and the opening magnet 21 energized, the gas exchange valve 7 opens until the Anchor 23 abuts the pole face of the opening magnet 21. In order to the maximum opening stroke has been reached.
  • the compensation element 3 is over a cup 35 supplied with pressurized oil between the compensation element 3 and the armature plunger 28 is arranged with his side cheeks 36, the compensation element 3 partially surrounds and outward in an oil pressure fed, cylinder head fixed Guide 37 is guided over sliding friction.
  • the guide 37 is formed by a separate component 38.
  • the Component 38 is inserted in the cylinder head 25 and is supported via a collar 39 in the closing direction 17 on the opening magnet 21st and in the opening direction 18 at a step 40 in the cylinder head 25th from.
  • the component 38 has at its outer periphery a Pressure chamber 41, via which it via a channel 42 with a pressure connection 43 is connected. From the pressure chamber 41, a channel 44 leads to the guide 37 and opens into an annular groove 45. Shortly before and in the closed position of the gas exchange valve 7 is a forming Interior 46 between the cup 35 and the compensation element 3 via a channel 47 in the cup 35 with the Ring groove 45 connected.
  • the interior 46 is outwardly over a Seal 48 between the compensating element 3 and the cup 35th sealed.
  • the armature 23 with its armature plunger 28, the compensation element 3 and the gas exchange valve 7 can be rotationally symmetrical to be built in. Through the annular groove 45 is safe provided that the cup 35 regardless of the orientation the assembly is supplied with oil.
  • the pressure oil is then, if required, via a recess 49 on an inner cover page 67 of the cup 35 is supplied to the compensating element 3.
  • the feeder of pressurized oil over cups 35 is a mature and so with a few problems afflicted technology. It is possible, however Also, the pressure oil with or without cup 35 directly on the side a correspondingly executed compensation element or over the Supply armature plunger 28.
  • the Total length of the armature plunger 28, the compensation element 3 and be readjusted according to the valve stem 24.
  • a floating actuator 20 may be the lash adjuster basically also on the gas exchange valve 7 facing away Side of the closing magnet 22 and / or on the gas exchange valve 7 facing side of the opening magnet 21 is arranged his.
  • the occurring disturbance variables and a resulting clearance compensation through the compensation element 3, may cause the determined by the valve springs 10, 11 equilibrium position not with an energetic middle position between the pole faces matches or does not have a predetermined position and that one on the gas exchange valve 7 in the closed position acting residual closing force of the lower valve spring 11 changed becomes.
  • the device has a Compensation element 4, with which the spring support 19 of in Closing direction 17 acting valve spring 11 is displaceable and the acting in the closed position of the gas exchange valve 7 Residual clamping force constant and also to individual operating states is adjustable.
  • Fig. 2 shows a schematic diagram of the compensating element 3.
  • the Compensation element 3 has a by a piston 12 and a working cylinder 50 formed pressure chamber 1, with a Seal 14 between the piston 12 and the cylinder 50 after is sealed on the outside.
  • On the piston 12 of the anchor tappet acts 28 with a force 68 in the opening direction 18 and on the cylinder 50, the valve stem 24 acts with a force 69 in the closing direction 17th
  • the closing magnet 22 de-energized and energized the opening magnet 21, the Anchor 23 acts on the valve stem 24 in the opening direction 18th and thereby biases the valve spring acting in the closing direction 17 11 further ahead.
  • the force acting on the compensating element 3 force rises to a maximum value of 54.
  • Fig. 4 is about a Working cycle 62, a pressure 61 in the pressure chamber 1 is applied.
  • On designed as a high-pressure valve 5 valve of the compensating element 3 opens at a defined pressure in the pressure chamber 1 or at a defined force 8, which by a safety value 55 is greater than an average force 53 and less than one maximum force 54.
  • the high pressure valve 5, preferably as Conventional check valve is running controls the Flow through a throttle 52, in the flow direction before or can be arranged behind the high pressure valve 5. So can with the valve open 5 throttled a small amount of pressure medium drain, without a pressure curve 51 in the pressure chamber 1 is significantly affected.
  • the opening magnet 21 de-energized and the closing magnet 22 energized.
  • the in the opening direction 18 acting valve spring 10 is further biased and the valve spring 11 acting in the closing direction 17 is relaxed.
  • the force acting on the compensating element 3 force drops to a minimum value of 56, the so-called residual closing force.
  • the high pressure valve 5 closes at a defined Force 9, which is less than the maximum force 54 and around the safety value 55 is greater than the average force 53.
  • the residual closing force 56 opens Check valve 57 at a defined force 58, the smaller is as the average force 53.
  • Pressure medium can from the pressure port 43 flow into the pressure chamber 1, whereby the compensation element 3 stretch and balanced positive game can be.
  • the gas exchange valve 7 If the gas exchange valve 7 is opened again, closes the check valve 57 at a defined force 59, which is larger than the remaining closing force 56 and smaller than that mean force is 53.
  • a defined force 59 Over a wide range of the opening stroke and the closing stroke of the gas exchange valve 7 is the high pressure valve 5 and the check valve 57 tightly closed, in which the movement of the gas exchange valve 7 is not affected becomes.
  • the opening force 58 and the closing force 59 of the check valve 57 and the opening force 8 and the closing force 9 of the high pressure valve 5 same size. In principle, however, the opening forces be executed by the closing forces of different sizes.
  • a solenoid valve 70th trained valve can be used.
  • Fig. 3 shows a variant with such a solenoid valve 70.
  • a solenoid valve 70 forms a piston 73 with its collar 72 at its periphery to the working cylinder 50th towards a throttle gap 71 which outwardly through the seal 14th is sealed.
  • a reflux channel 74 in the working cylinder 50.
  • the pressure medium is in a Pressure sump, e.g. a lubricating oil sump, or in a pantry passed, from which the pressure chamber 1 is fed.
  • the solenoid valve 70 is dependent on suitable operating parameters arbitrarily controllable, so that the drain over the throttle gap 71 in time to certain phases of the duty cycle can be limited.
  • solenoid valve 70 When de-energized solenoid valve 70 is the drain blocked from the pressure chamber 1, so that the compensation element 3 is hydraulically blocked and thus during the Standstill of the internal combustion engine maintains its attitude.
  • the solenoid valve 70 can also be used in a corresponding manner Compensation device 4 used in place of a high pressure valve 6 become.
  • Fig. 5 shows an enlarged section of the compensating element 4 of Fig. 1.
  • the compensating element 4 has a through a piston 13 and a working cylinder 60 formed pressure chamber 2, with four seals 15, 16, 65, 66 between the Piston 13 and the cylinder 60 is sealed. Furthermore owns the compensation element 4, a high-pressure valve 6 and a check valve 64.
  • the spring seat 19 and the piston 13 are made in one piece, saving additional components can be.
  • the spring seat 19 and the piston 13 is U-shaped trained and is thus easily and well managed.
  • the force acting on the compensating element 4 force of the valve spring 11 fluctuates during the working cycles of the gas exchange valve 7 between a maximum force and a minimum force as on the compensating element 3. Will the gas exchange valve 7 opened, the force increases to a maximum value.
  • the High pressure valve opens at a defined force, the smaller is greater than the maximum force and a safety value is acting as a mean on the compensating element 4 Force. Pressure medium can thereby via the high pressure valve 6 and throttled via a high pressure valve 6 downstream throttle 63 flow away. If the gas exchange valve 7 is closed, the force on the compensating element decreases to a minimum Value off.
  • the high pressure valve 6 closes at a defined Force that is greater than the mean by a safety value Force.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)

Claims (11)

  1. Dispositif pour actionner une soupape d'échange des gaz pour un moteur à combustion interne, comportant au moins un élément de compensation qui comprend une chambre sous pression formée par un piston et par un cylindre de travail, laquelle communique avec un réservoir via un clapet anti-retour, et comportant un emplacement d'étranglement via lequel un fluide sous pression peut s'écouler hors de la chambre sous pression pendant les cycles de travail, caractérisé en ce que l'élément de compensation (3, 4) conserve sensiblement son réglage lors d'un arrêt du moteur à combustion interne.
  2. Dispositif selon la revendication 1, caractérisé en ce que l'écoulement est susceptible d'être commandé via l'emplacement d'étranglement (52, 63, 71) au moyen d'une valve (5, 6, 70).
  3. Dispositif selon la revendication 2, caractérisé en ce qu'il est prévu à titre de valve (70) une valve magnétique qui obture le passage à travers l'emplacement d'étranglement (52, 63, 71) dans l'état sans courant.
  4. Dispositif selon la revendication 2, caractérisé en ce que l'élément de compensation (3, 4) est agencé dans le flux de force d'un élément d'actionnement (20) sur la soupape d'échange des gaz (7) et la chambre sous pression (1, 2) est étanchée vers l'extérieur, et en ce que l'élément de compensation (3, 4) comprend comme valve une valve à haute pression (5, 6) via laquelle le fluide sous pression s'écoule de façon étranglée pendant les cycles de travail normaux de la soupape d'échange des gaz (7) du fait que la valve à haute pression (5, 6) s'ouvre cycliquement à une force définie (8) sur l'élément de compensation (3, 4) et se ferme à une force définie (9) qui est supérieure à une force moyenne (53) et légèrement inférieure ou égale à une force maximale (54) sur l'élément de compensation (3, 4).
  5. Dispositif selon l'une des revendications précédentes, caractérisé en ce qu'au moins un ressort de soupape (10, 11) agit sur la soupape d'échange des gaz (7).
  6. Dispositif selon l'une des revendications 2 à 5, caractérisé en ce que la chambre sous pression (1, 2) est étanchée vers le côté du piston (12, 13) par des joints (14, 15, 16, 65, 66) entre le piston (12, 13) et le cylindre (50, 60).
  7. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que la valve à haute pression (5, 6) est une valve à bille faisant office de clapet anti-retour.
  8. Dispositif selon l'une des revendications précédentes, caractérisé en ce que l'élément de compensation (3) est un élément de rattrapage de jeu.
  9. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que le dispositif comprend au moins un ressort de soupape (11) qui agit en direction de fermeture (17) sur la soupape d'échange des gaz (7) et qui prend appui en direction d'ouverture (18) sur un appui de ressort (19), l'appui de ressort (19) étant déplaçable avec l'élément de compensation (4) et la précontrainte du ressort de soupape (11) étant ainsi réglable.
  10. Dispositif selon la revendication 6, caractérisé en ce que l'appui de ressort (19) est réalisé d'un seul tenant avec un piston (13) de l'élément de compensation (4).
  11. Dispositif selon l'une des revendications précédentes, caractérisé en ce que la soupape d'échange des gaz (7) est actionnée au moyen d'un actionneur électromagnétique (20) qui possède un aimant d'ouverture (21) et un aimant de fermeture (22) entre les surfaces polaires desquels est agencé un induit (23) mobile coaxialement à la soupape d'échange des gaz (7) et agissant sur une tige de soupape (24), et comportant un mécanisme à ressort qui comprend un ressort de soupape précontraint (10) agissant en direction d'ouverture (18) et un ressort de soupape précontraint (11) agissant en direction de fermeture (17).
EP00901531A 1999-01-13 2000-01-12 Dispositif pour actionner une soupape de changement des gaz Expired - Lifetime EP1144811B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19900951 1999-01-13
DE19900951 1999-01-13
DE19956136A DE19956136A1 (de) 1999-01-13 1999-11-23 Vorrichtung zum Betätigen eines Gaswechselventils
DE19956136 1999-11-23
PCT/EP2000/000156 WO2000042298A1 (fr) 1999-01-13 2000-01-12 Dispositif pour actionner une soupape de changement des gaz

Publications (2)

Publication Number Publication Date
EP1144811A1 EP1144811A1 (fr) 2001-10-17
EP1144811B1 true EP1144811B1 (fr) 2003-05-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP00901531A Expired - Lifetime EP1144811B1 (fr) 1999-01-13 2000-01-12 Dispositif pour actionner une soupape de changement des gaz

Country Status (5)

Country Link
US (1) US6481395B2 (fr)
EP (1) EP1144811B1 (fr)
JP (1) JP2002535530A (fr)
ES (1) ES2197067T3 (fr)
WO (1) WO2000042298A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19927823B4 (de) * 1999-06-18 2004-08-12 Daimlerchrysler Ag Elektromagnetischer Aktuator und Verfahren zur Justierung des elektromagnetischen Aktuators
DE10051076C2 (de) 2000-10-14 2003-12-18 Daimler Chrysler Ag Verfahren zur Herstellung eines elektromagnetischen Aktuators
AT500679B8 (de) * 2004-06-16 2007-02-15 Ge Jenbacher Gmbh & Co Ohg Ventilantrieb
US20090266319A1 (en) * 2008-04-28 2009-10-29 James Douglas Ervin System and method for providing hydraulic valve lash compensation for electrically actuated internal combustion engine poppet valves

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4392462A (en) * 1980-12-22 1983-07-12 Stanadyne, Inc. Inverted bucket tappet with seal
US4515343A (en) * 1983-03-28 1985-05-07 Fev Forschungsgesellschaft fur Energietechnik und ver Brennungsmotoren mbH Arrangement for electromagnetically operated actuators
DE4109666A1 (de) 1991-03-23 1992-09-24 Audi Ag Hydraulisches ventilspiel-ausgleichselement
JP3106890B2 (ja) * 1995-01-11 2000-11-06 トヨタ自動車株式会社 内燃機関の弁駆動装置
JPH08284620A (ja) * 1995-04-17 1996-10-29 Mitsubishi Motors Corp ラッシュアジャスタ及びラッシュアジャスタを備えた内燃機関
DE19647305C1 (de) 1996-11-15 1998-02-05 Daimler Benz Ag Vorrichtung zur elektromagnetischen Betätigung eines Gaswechselventils
DE19723785A1 (de) * 1997-06-06 1998-12-10 Daimler Benz Ag Vorrichtung zum Spielausgleich eines elektromagnetischen Ventils
DE19826832A1 (de) * 1998-06-16 1999-12-23 Fev Motorentech Gmbh Elektromagnetischer Aktuator für ein Gaswechselventil mit integriertem Ventilspielausgleich

Also Published As

Publication number Publication date
EP1144811A1 (fr) 2001-10-17
JP2002535530A (ja) 2002-10-22
US6481395B2 (en) 2002-11-19
US20020017254A1 (en) 2002-02-14
WO2000042298A1 (fr) 2000-07-20
ES2197067T3 (es) 2004-01-01

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