EP1608852B1 - Dispositif d'actionnement variable des soupapes d'echange des gaz de moteurs a combustion interne et procede permettant de faire fonctionner un dispositif de ce type - Google Patents

Dispositif d'actionnement variable des soupapes d'echange des gaz de moteurs a combustion interne et procede permettant de faire fonctionner un dispositif de ce type Download PDF

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Publication number
EP1608852B1
EP1608852B1 EP04721188A EP04721188A EP1608852B1 EP 1608852 B1 EP1608852 B1 EP 1608852B1 EP 04721188 A EP04721188 A EP 04721188A EP 04721188 A EP04721188 A EP 04721188A EP 1608852 B1 EP1608852 B1 EP 1608852B1
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EP
European Patent Office
Prior art keywords
valves
displacement
cylinder
gas exchange
intermediate members
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
EP04721188A
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German (de)
English (en)
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EP1608852A1 (fr
Inventor
Helmut Schön
Gordon KÖHNE
Peter Kuhn
Frank Obrist
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.)
Thyssenkrupp Dynamic Components Teccenter AG
Original Assignee
ThyssenKrupp Presta TecCenter AG
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Publication date
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Publication of EP1608852A1 publication Critical patent/EP1608852A1/fr
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Publication of EP1608852B1 publication Critical patent/EP1608852B1/fr
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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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • 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
    • F01L13/0063—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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
    • F01L1/185—Overhead end-pivot rocking arms
    • 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
    • F01L13/0063—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements
    • F01L2303/01—Tools for producing, mounting or adjusting, e.g. some part of the distribution
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/06—Timing or lift different for valves of same cylinder
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/08—Timing or lift different for valves of different cylinders
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/13—Throttleless

Definitions

  • the invention relates to a device for variable actuation of the gas exchange valves of internal combustion engines.
  • Such devices serve to make the control of gas exchange valves so that it is possible to operate reciprocating engines without the usual throttle.
  • Such a device is for example from the DE 101 23 186 A1 known.
  • a rotating cam first drives an intermediate member, which performs an oscillating, pure rotary motion and carries a control cam, which is composed of a latching area and a stroke area.
  • the control cam transmits the necessary for actuation of the valve lift curve on the role of a drag lever-like output member, which in turn actuates the valve.
  • the desired, different Ventilhubkurven be generated by the fact that the center of rotation of the intermediate member is displaced on a circular arc-shaped path which is concentric with the role of the driven member in its position with the valve closed.
  • the center of rotation is formed by a roller provided on the intermediate member, which is frictionally supported on a circular arc-shaped track in the housing, which is also concentric with the role of the output member, thus forming an equidistant to the path of the center of rotation and which is referred to as a backdrop.
  • the roller mounted on the intermediate member is supported on a cam whose angular position determines the position of the center of rotation on its arcuate path.
  • a fully variable valve train is described with a drive means, such as a cam, a arranged between the drive means and the gas exchange valve intermediate member which acts indirectly on the gas exchange valve and the valve is variable via the adjustment of an adjustable guide element.
  • the object underlying the present invention is to provide a device which avoids the disadvantages of the prior art and provides additional variabilities for mechanically fully variable valve controls.
  • the device according to the invention relates to a device for the variable actuation of gas exchange valves for internal combustion engines having a plurality of cylinders, in which one or more cams of a camshaft mounted in a housing, rotate depending on the engine speed.
  • the device comprises an intermediate member which can be actuated by these cams via a first cam joint and an output member.
  • the output member transmits the movement to the gas exchange valve.
  • the output member is connected to the intermediate member directly or via further intermediate links in connection.
  • the device further comprises at least one control cam. This control cam is located between the intermediate member or one of the further intermediate links and the output member. This control cam has a section in which no lifting movement for the gas exchange valve is transmitted via the output member.
  • This control cam has a further section in which a lifting movement for the gas exchange valve is transmitted via the output member.
  • the device offers the possibility of displacing the intermediate member or at least one of the further intermediate members along a displacement track. By this shift, the course of the lift curve of the gas exchange valves is changeable.
  • At least one displacement unit is provided, with which the displacement takes place to influence the stroke movement of at least one gas exchange valve. This shift takes place independently of the displacement of the intermediate links of other gas exchange valves by means of other displacement units.
  • the device further comprises a common adjusting shaft.
  • the adjusting shaft has for this purpose at least one cam per displacement unit. With the adjusting shaft, the intermediate members are substantially supported in the displacement direction.
  • the cam of at least one displacement unit has a trained as a detent portion. A rotation of the adjusting shaft in this section causes no change in the position of the guided on the displacement track intermediate links.
  • the cam of at least one other displacement unit has a corresponding portion without detent.
  • a rotation of the adjusting shaft in this section causes a change in the position of the guided on the displacement track other intermediate links.
  • the method claims describe methods for operating the device according to the invention.
  • the displacement of gear members, which cause the change of the valve lift curve is performed in separate units for each gas exchange valve or in separate units for a plurality of each adjacent gas exchange valves, these units are at least temporarily adjusted independently.
  • the position of the variable transmission member along the Verstellkurve is preferably determined by the direct or indirect contact with one or more cams, which are rotatably mounted on a common adjustment shaft.
  • the adjusting shaft or the adjusting axis can in turn be rotated or displaced by means of a suitable gear or a connecting element of an adjusting motor.
  • the adjustment can also be done by hydraulic elements.
  • the adjustment of the adjusting motor can also be done directly via a spindle provided with movement thread.
  • the device according to the invention including an adjusting motor or an adjusting device for each valve of an engine, can be provided separately, so that any combinations of valve strokes or opening angles of the individual valves of an engine are possible, including the switching off of individual cylinders.
  • two intake valves can be actuated by a cam via an intermediate member, which has a control cam for each valve. Since only one link and only one guide of the units is present, both valves are adjusted together and similar.
  • two different cams can be provided on the common intermediate member, with the result of different lifting curves on both valves despite common adjustment.
  • This variant opens up the possibility of opening only one of the two valves, especially in the lowest load range.
  • the particular advantage of this option is that in the lowest load range very small cross-sections must be released and they can be maintained more precisely if they are released only by a valve.
  • the possibilities of generating different valve lift curves for two intake or exhaust valves of a cylinder are inventively extended by the fact that two different cams and two intermediate links are used with different cams. Nevertheless, both valves can be adjusted together, since the two intermediate links can be stored in a common unit.
  • the common adjustment of the inlet and outlet valves of only one cylinder give long, easy adjustment rest periods. But it also allows an individual load control of the individual cylinders with an adjustment strategy according to the invention such that the torques of the individual cylinders are controlled for each load condition of the entire engine. This is essential, especially in the lower load range, for smooth engine operation, since the valve lifts normally do not match sufficiently due to tolerances.
  • the signals required for this adjustment strategy are also supplied by the rotary encoder of the crankshaft and assigned to the individual cylinders by the rotary encoder of the camshaft.
  • the displacement of gear members which causes the change of the valve lift, carried out by means of a common, rotatable adjusting with cams.
  • This offers at a largely independent adjustment of all or at least several inlet and outlet valves the ability to turn off by means of this continuous adjustment selected valves, so no longer open or at least set a smaller valve.
  • portions of the cams described the adjusting shaft are formed in the non-shutdown valves as a catch.
  • the latching area is a contour, which is formed from a concentric to the center of rotation of the adjusting circular arc.
  • valve lift of the displacement units controlled by the cams with locking is not changed within the effective range of the latching while the valve lift of the displacement units controlled by the cams without latching is changed. This change can be carried out until the valve or valves are completely closed. If all intake valves and / or exhaust valves of the same cylinder are activated in this way, the charge cycle for selected cylinders is suspended. Of course, the same function is achieved by using a straight guided wedge with corresponding cam contour. The latching area is then a contour which is formed from a direction parallel to the sliding direction of the drawing wedge.
  • Fig. 1 shows a camshaft 1, which carries a cam 2. This moves the roller 3 in the end region of the intermediate member 4.
  • the intermediate member 4 has a control cam 5, which is composed of a latching region 5a and a lifting portion 5b.
  • the intermediate member 4 is mounted on a pin 6, the axis 7 is guided on a circular arc-shaped Verstellkurve 8.
  • the center of the arcuate Verstellkurve 8 lies on the axis 9 of the roller 10 of the output member 11, which is supported via a hinge 12 in the housing, not shown, and the valve 13 is actuated. It is clear that an adjustment of the axis 7 on the Verstellkurve 8 in the direction of arrow 14 has a reduction of the opening angle and stroke of the valve 13 result.
  • Fig. 2 shows an embodiment in which the pin 6 and its axis 7 is guided by a pendulum support 15 positively on the circular arc-shaped Verstellkurve 8.
  • the adjusting shaft 17 carries cams 18, which via plunger 18 a the
  • Fig. 3 shows a cross section through an embodiment of the invention using a slide 34, which can be used separately for each valve or valve pair. Due to the separate application for individual valves, the longest possible rest periods or common resting phases result, so that an adjustment is easily possible only during the rest periods. For the inventive control of the individual cylinders, the separate arrangement is even necessary.
  • the bolt 6 is guided in this embodiment by the slide 34 positively in the housing, so that its axis 7 along the Verstellkurve 35, a straight line, is performed. This straight line approaches as a tangent to a circular arc about the axis 9 of the roller 10 of the stationary output member 11 only more or less good. In the figure, the deviation is exaggerated.
  • the clearance compensation element 31 must sink by a certain amount, which is indicated by the arrow 38 d.
  • Fig. 4 shows a perspective view of a due to the individual, each displacement unit associated adjusting shafts 17 not belonging to the claimed invention device using a slide 34 which is used separately for each valve pair of a cylinder.
  • the bolt 6 is guided in this embodiment by the slide 34 positively in the valve gear housing, not shown, so that its axis 7 along the Verstellkurve 35, a straight line is performed.
  • This straight line approximates a circular arc about the axis 9 of the roller 10 of the stationary output member 11 only more or less well. Due to the deviation of the straight Verstellkurve 35 of the circular arc shape, the clearance compensation element 31 must compensate for a certain amount.
  • An adjustment of the axis 7 on the Verstellkurve 35 is effected by a rotation of the cam 18 and the adjusting shaft 17.
  • a pair of valves by means of a cam 2 and an intermediate member 4, which in a slide 34 on a Bolt 6 is mounted, whose position in the valve train housing along a Verstellkurve 35 positively guided and positioned by means of an adjusting 17 via cams 18 is actuated.
  • the conditions in the other cylinders do not change.
  • a common adjusting position the displacement units of a cylinder group or a cylinder head.
  • Fig. 5 schematically shows the interaction of accelerator pedal 40, adjusting motors 23, rotation angle sensor 42 on the flywheel and rotation angle sensor 43 on the camshaft with the engine management 44.
  • the engine management system 44 evaluates the signals of the high-resolution rotation angle sensor 42 on the flywheel. These are assigned to the individual cylinders by means of the low-resolution angle of rotation sensor 43 on the camshaft or on another shaft running at half the crankshaft speed.
  • signals are sent to the individual adjusting motors 23 for leveling the torque peaks or the crankshaft speed, in which the valve strokes of the cylinders are corrected with smaller torques up and those of the cylinder with larger torques down.
  • an adjustment takes place, with or without compensation, during the common rest phases of the valves operated by an adjusting motor.
  • Their phase position takes the engine management 44 the sensor 43 on the camshaft.
  • Fig. 6 shows a schematic representation of a continuous adjusting shaft 45 of a 6-cylinder in-line engine, and in each case a section through one of two cams for the positioning of the displacement unit of a cylinder.
  • the adjusting shaft carries cams 46, 47 for positioning the displacement units for the six cylinders.
  • the cams 46 for the cylinders # 1, # 4 and # 5, and the cams 47 for the cylinders # 2, # 3 and # 6 are the same.
  • AA shows a cross section through the cam 46
  • BB shows a cross section through the cam 47.
  • the sector R of the cam 47 is formed by a center of rotation 48 of the adjusting 45 concentric circular arc 49, while in the corresponding sector of the cam 46, the Verstellnockenkurve continuously smaller distance to the center of rotation 48 leads.
  • Such a configuration of the cams 46 and 47 ensures that, when the adjusting shaft 45 is rotated about its center of rotation 48, the displacement units for the valves of the cylinders # 1, # 4 and # 5 are further displaced in the effective range of the sector R, while the displacement units for the valves of cylinders # 2, # 3 and # 6 remain at rest.
  • valve gear By appropriate design of the valve gear can be achieved in this way, for example, that the valves of the cylinder # 1, # 4 and # 5 in the subsequent effective range of the sector N remain permanently closed, while the valves of the cylinder # 2, # 3 and # 6 to do another stroke.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Claims (15)

  1. Dispositif pour l'actionnement de soupapes de changement des gaz d'un moteur à combustion interne à plusieurs cylindres, dans lequel une ou plusieurs cames (2) d'un arbre à cames (1), monté dans un carter, tournent en fonction de la vitesse de rotation dudit moteur,
    - avec un organe intermédiaire (4), qui peut être actionné au moyen de cette came (2) par l'intermédiaire d'une première courbe de liaison (K1), et
    - avec un organe de sortie (11), qui transmet le mouvement à la soupape de changement des gaz (13) et est en liaison avec l'organe intermédiaire (4), directement ou par l'intermédiaire d'autres organes intermédiaires, et
    - avec au moins une came de commande (5), entre l'organe intermédiaire (4), ou un autre organe intermédiaire (4), et l'organe de sortie (11), sachant que cette came de commande (5) est dotée d'une zone (5a) dans laquelle aucun mouvement de levée n'est transmis à la soupape de changement des gaz (13), par l'intermédiaire de l'organe de sortie (11), et d'une autre zone (5b), dans laquelle un mouvement de levée est transmis à la soupape de changement des gaz (13) par l'intermédiaire de l'organe de sortie (11), et
    - avec possibilité de déplacement de l'organe intermédiaire (4), ou d'au moins l'un des autres organes intermédiaires (4), le long d'un chemin de déplacement (8, 35), sachant que l'allure de la courbe de levée des soupapes de changement des gaz peut être modifiée par déplacement, caractérisé en ce que
    - au moins une unité de déplacement (15, 34) est prévue, au moyen de laquelle s'effectue le déplacement destiné à influencer la course de levée d'au moins une soupape de changement des gaz (13) indépendamment du déplacement des organes intermédiaires (4) des autres soupapes de changement des gaz (13) au moyen d'autres unités de déplacement (15, 34),
    - un arbre de réglage (45) commun est prévu, au moyen duquel la position, respectivement exigée, des organes intermédiaires (4), sur le chemin de déplacement (8, 35), peut être réglée pour une pluralité de soupapes de changement des gaz (13), directement ou indirectement, au moyen d'au moins une came par unité de déplacement, et les organes intermédiaires (4) peuvent venir en appui sensiblement dans la direction du déplacement,
    - une première came (47) d'au moins une unité de déplacement est dotée d'une zone d'arrêt (49), dans laquelle aucune variation de la position des organes intermédiaires (4) guidés sur le chemin de déplacement (8, 35) n'a lieu lors de la rotation de l'arbre de réglage (45),
    - et une deuxième came (46) d'au moins une autre unité de déplacement (15, 34) est dotée d'une zone correspondante, sans fonction d'arrêt, dans laquelle, lors de cette rotation de l'arbre de réglage (45), a lieu une modification de la position des autres organes intermédiaires (4) guidés sur le chemin de déplacement (8, 35).
  2. Dispositif selon la revendication 1, caractérisé en ce que la zone sans fonction d'arrêt de la deuxième came (46) présente un premier secteur (R), dans lequel la surface de came évolue en continu vers une moindre distance du centre de rotation (48) de l'arbre de réglage (45).
  3. Dispositif selon la revendication 2, caractérisé en ce que le contour de la deuxième came (46) présente un deuxième secteur (N), disposé dans le voisinage du premier secteur (R), dans lequel la surface de came est formée de sorte que les soupapes du cylindre, qui sont actionnées lors de l'activation de ce deuxième secteur (N), demeurent constamment fermées, tandis que le contour de la première came (47) présente un secteur correspondant (N), dans lequel la surface de came est formée de sorte que les soupapes du cylindre, qui sont actionnées lors de l'activation de ce secteur correspondant (N), exécutent encore une course de levée.
  4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce que plusieurs deuxièmes cames (46) identiques et plusieurs premières cames (47) identiques sont disposées sur l'arbre de réglage (45), sachant que les deuxièmes cames (46) et les premières cames (47) sont respectivement identiques en ce qui concerne leur position angulaire, c.-à-d. qu'elles ne sont pas contournées les unes part rapport aux autres
  5. Dispositif selon les revendications 1 à 4, caractérisé en ce que deux cames identiques et deux organes intermédiaires avec des cames de commande identiques sont utilisés pour les deux soupapes d'un cylindre.
  6. Dispositif selon les revendications 1 à 4, caractérisé en ce que deux cames différentes et deux organes intermédiaires avec des cames de commande différentes sont utilisés pour les deux soupapes d'un cylindre.
  7. Dispositif selon les revendications 1 à 4, caractérisé en ce que deux cames identiques et deux organes intermédiaires avec des cames de commande différentes sont utilisés pour les deux soupapes d'un cylindre.
  8. Dispositif selon les revendications 1 à 4, caractérisé en ce que deux cames différentes et deux organes intermédiaires avec des cames de commande identiques sont utilisés pour les deux soupapes d'un cylindre.
  9. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce qu'un organe intermédiaire commun avec deux cames de commande identiques est utilisé pour les soupapes d'entrée et de sortie d'un cylindre.
  10. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce qu'un organe intermédiaire commun avec deux cames de commande différentes est utilisé pour les soupapes.
  11. Dispositif selon l'une ou plusieurs des revendications 1 à 10, caractérisé en ce qu'un réglage est effectué jusqu'au maintien constant à l'état fermé d'au moins une soupape.
  12. Dispositif selon l'une ou plusieurs des revendications 1 à 11, caractérisé en ce que toutes les soupapes d'entrée et de sortie d'un cylindre sont groupées dans une unité de déplacement (15, 34).
  13. Procédé pour l'exploitation d'un moteur à combustion interne à plusieurs cylindres en utilisant un ou plusieurs dispositif/s selon l'une ou plusieurs des revendications 1 à 12, caractérisé en ce que, quand l'état de charge désiré de la totalité du moteur est atteint,
    a) des signaux d'angle de rotation du vilebrequin sont évalués avec un premier détecteur d'angle de rotation (42) sur la roue volante pour la détection d'uniformités de rotation du vilebrequin et / ou des pointes de couple de rotation sont saisies et évaluées par un management du moteur (44),
    b) ceux-ci sont associés aux différents cylindres, à l'aide d'un deuxième détecteur d'angle de rotation (43), disposé sur l'arbre à cames ou sur un autre arbre, qui tourne a la demi vitesse de rotation de l'arbre à cames,
    c) avec ces informations, sont générés des signaux, qui sont lancés à différents servomoteurs (23) pour l'égalisation des pointes de couple de rotation et / ou de la vitesse de rotation de l'arbre à cames, les courses de levées des soupapes des cylindres à couples de rotation plus petits étant corrigées vers le haut et celles des cylindres à couples de rotation plus élevés étant corrigées vers le bas.
  14. Procédé pour l'exploitation d'un moteur à combustion interne à plusieurs cylindres en utilisant un ou plusieurs dispositif/s selon l'une ou plusieurs des revendications 1 à 12, caractérisé en ce que
    a) à chaque cylindre sont associés un dispositif séparé et un servomoteur (23) pour l'actionnement dudit dispositif,
    b) la position de phase des phases de repos des différentes soupapes, commandées par un servomoteur (23), est déterminée, et
    c) les mouvements de déplacement de chacun des dispositifs sont effectués pendant les phases de repos communes des soupapes commandées par le servomoteur respectif (23).
  15. Procédé selon la revendication 14, caractérisé en ce que la position de phase des phases de repos des différentes soupapes, commandées par un servomoteur (23), sont déterminées par un management du moteur (44), à partir d'un signal d'un détecteur d'angle de rotation (43), agencé sur l'arbre à cames.
EP04721188A 2003-03-24 2004-03-17 Dispositif d'actionnement variable des soupapes d'echange des gaz de moteurs a combustion interne et procede permettant de faire fonctionner un dispositif de ce type Expired - Lifetime EP1608852B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10312958A DE10312958B4 (de) 2003-03-24 2003-03-24 Vorrichtung zur vairablen Betätigung der Gaswechselventile von Verbrennungsmotoren und Verfahren zum Betreiben einer derartigen Vorrichtung
DE10312958 2003-03-24
PCT/EP2004/002740 WO2004085802A1 (fr) 2003-03-24 2004-03-17 Dispositif d'actionnement variable des soupapes d'echange des gaz de moteurs a combustion interne et procede permettant de faire fonctionner un dispositif de ce type

Publications (2)

Publication Number Publication Date
EP1608852A1 EP1608852A1 (fr) 2005-12-28
EP1608852B1 true EP1608852B1 (fr) 2011-08-31

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EP04721188A Expired - Lifetime EP1608852B1 (fr) 2003-03-24 2004-03-17 Dispositif d'actionnement variable des soupapes d'echange des gaz de moteurs a combustion interne et procede permettant de faire fonctionner un dispositif de ce type

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US (1) US7302922B2 (fr)
EP (1) EP1608852B1 (fr)
JP (1) JP2006521491A (fr)
KR (1) KR101059407B1 (fr)
CN (1) CN100404802C (fr)
AT (1) ATE522704T1 (fr)
DE (1) DE10312958B4 (fr)
WO (1) WO2004085802A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10312961C5 (de) * 2003-03-24 2009-01-29 Thyssenkrupp Presta Teccenter Ag Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren
EP2472075B1 (fr) * 2009-08-24 2014-09-17 Yamaha Hatsudoki Kabushiki Kaisha Dispositif de soupape variable, moteur comportant ce dispositif et véhicule à selle
AT516669B1 (de) * 2014-11-24 2016-08-15 Ge Jenbacher Gmbh & Co Og Verfahren zur Steuerung einer Brennkraftmaschine
DE102015104633A1 (de) * 2015-03-26 2016-09-29 Pierburg Gmbh Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung
DE102015118884A1 (de) * 2015-11-04 2017-05-04 Pierburg Gmbh Mechanisch steuerbarer Ventiltrieb
DE102016205805A1 (de) * 2016-04-07 2017-10-12 Bayerische Motoren Werke Aktiengesellschaft Ventiltrieb sowie Motorbaugruppe

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JPS62113807A (ja) * 1985-11-12 1987-05-25 Nissan Motor Co Ltd 内燃機関の吸排気弁リフト制御装置
WO1993008377A1 (fr) * 1991-10-25 1993-04-29 Peter Kuhn Systeme de commande des soupapes de moteurs a combustion interne a l'aide de cames rotatives
DE4135257C2 (de) * 1991-10-25 1998-09-03 Peter Prof Dr Ing Kuhn Vorrichtung zur Betätigung der Ventile in Verbrennungsmotoren mittels umlaufender Nocken
US5365895A (en) * 1991-12-03 1994-11-22 Motive Holdings Limited Variable valve lift mechanism for internal combustion engine
EP0717174A1 (fr) * 1994-12-12 1996-06-19 Isuzu Motors Limited Système de commande de soupape pour moteur à combustion interne
JPH08165910A (ja) * 1994-12-12 1996-06-25 Isuzu Motors Ltd 内燃機関の動弁装置
DE19532334A1 (de) * 1995-09-01 1997-03-06 Bayerische Motoren Werke Ag Variabler Ventiltrieb, insbesondere für Brennkraftmaschinen
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JP3933335B2 (ja) * 1999-01-26 2007-06-20 株式会社日立製作所 内燃機関の可変動弁装置
JP3790379B2 (ja) * 1999-02-05 2006-06-28 株式会社日立製作所 内燃機関の可変動弁装置
DE10066056B4 (de) * 2000-07-18 2006-02-02 Thyssenkrupp Automotive Ag Hubventilsteuerung für Kraftmaschinen
DE10052811A1 (de) * 2000-10-25 2002-05-08 Ina Schaeffler Kg Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine
DE10100173A1 (de) * 2001-01-04 2002-07-11 Fev Motorentech Gmbh Vollvariabler mechanischer Ventiltrieb für eine Kolbenbrennkraftmaschine
DE10123186A1 (de) * 2001-05-12 2002-11-14 Bayerische Motoren Werke Ag Ventiltrieb-Vorrichtung zur variablen Hubverstellung eines Gaswechselventils einer Brennkraftmaschine
DE10136612A1 (de) * 2001-07-17 2003-02-06 Herbert Naumann Variable Hubventilsteuerungen
DE10164493B4 (de) 2001-12-29 2010-04-08 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Vorrichtung zur variablen Betätigung der Ladungswechselventile in Hubkolbenmotoren

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Publication number Publication date
WO2004085802A1 (fr) 2004-10-07
KR101059407B1 (ko) 2011-08-29
DE10312958B4 (de) 2005-03-10
CN100404802C (zh) 2008-07-23
ATE522704T1 (de) 2011-09-15
US20070000461A1 (en) 2007-01-04
CN1764771A (zh) 2006-04-26
EP1608852A1 (fr) 2005-12-28
KR20050109599A (ko) 2005-11-21
US7302922B2 (en) 2007-12-04
DE10312958A1 (de) 2004-10-21
JP2006521491A (ja) 2006-09-21

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