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EP1608851B1 - Dispositif de commande variable de soupapes d'echange des gaz pour moteurs a combustion interne et procede de fonctionnement d'un dispositif de ce type - Google Patents

Dispositif de commande variable de soupapes d'echange des gaz pour moteurs a combustion interne et procede de fonctionnement d'un dispositif de ce type Download PDF

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Publication number
EP1608851B1
EP1608851B1 EP04721181A EP04721181A EP1608851B1 EP 1608851 B1 EP1608851 B1 EP 1608851B1 EP 04721181 A EP04721181 A EP 04721181A EP 04721181 A EP04721181 A EP 04721181A EP 1608851 B1 EP1608851 B1 EP 1608851B1
Authority
EP
European Patent Office
Prior art keywords
cam
several
bolt
housing
valves
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
EP04721181A
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German (de)
English (en)
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EP1608851A1 (fr
Inventor
Helmut Schön
Kai-Uwe Keller
Peter Kuhn
Gordon KÖHNE
Frank Obrist
Christian Busch
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
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.)
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Publication date
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Publication of EP1608851A1 publication Critical patent/EP1608851A1/fr
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Publication of EP1608851B1 publication Critical patent/EP1608851B1/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
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • 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
    • F01L2800/13—Throttleless
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the invention relates to a device for the variable actuation of the gas exchange valves of internal combustion engines according to the preamble of claim 1.
  • 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 non-positively supported on a circular arc-shaped track in the housing, which is also concentric with the role of the output member, ie forms an equidistant to the orbit 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.
  • the mounted on the intermediate member role in the scenery only if the gas and inertial forces of the valve train are directed accordingly and the role actually supported on the backdrop. If this is not the case, which can happen at overspeed, for example, the traction is lost and there is a lifting, which can lead to noises and even damage when re-putting on.
  • there is the relatively difficult processing of the scenes as segments of an inner cylinder which can not be processed consistently and the insufficient hardness of common housing materials for the role-backdrop contact.
  • the assembly there is a disadvantage in that the control housing can not be completely pre-mounted on the cylinder head.
  • the DE 101 23 186 A1 is a valve drive device for variable stroke adjustment of a gas exchange valve of an internal combustion engine disclosed.
  • the pivot lever for adjusting the valve lift is adjusted by a cam of an adjusting device along a circular slide track.
  • a device for controlling the valve lift in internal combustion engines known.
  • an angle lever is adjusted via a formed on the angle lever circular toothing, which is in engagement with a likewise having a toothing control shaft. This solution is due to the working with gear adjustment manufacturing costly.
  • the object underlying the present invention is to develop a device for variable actuation of gas exchange valves for internal combustion engines according to the preamble of claim 1 such that a safe adjustment takes place along a Verstellkurve that comes close to a circular arc shape.
  • the centers of rotation of the intermediate links driven by the cam are guided according to the invention by positive guides, thus in a form-locking manner on the adjustment cam.
  • This ensures that the center of rotation of an intermediate link can not leave the Verstellkurve, so noises and damage that would be due to a leaving avoided.
  • This feature is preferably realized structurally in that one or more intermediate links are mounted on a cylindrical bolt, on whose axis the centers of rotation lie, and that the axis of the bolt is guided on the Verstellkurve inevitably. If the active surface on the output member, to which the control cam of the intermediate member transmits its movement, is circular cylindrical, thus e.g. is formed by a roller, is assumed to be a circular arc-shaped Verstellkurve whose center coincides with the center of the circular cylindrical active surface or the roller.
  • Such a Verstellkurve is realized by a presently not claimed proposal by pendulum supports, which are connected via their respective first joint with the cylinder head and the control housing and with their respective second joint with the bolt.
  • the axis common to the cylinder head side axis coincides with the axis of said, cylindrical active surfaces on the output member, the bolt-side joints with the Pin axis.
  • the bolt or its axis according to the invention will also be forcibly guided on the adjustment curve with four-bar linkages formed from pendulum supports.
  • the adjustment curve that can be realized in this way comes close to the circular arc shape and fulfills it exactly at the design point when the system lines meet at the center of the circular arc.
  • the deviations outside the design point are absorbed by hydraulic lash adjusters, which are to be provided on the drag lever-like or even straight driven members.
  • the claimed solution has the advantage that it can be used if between the output members of adjacent valves, be it designed like a drag lever or straight, not enough space for the above-mentioned, unclaimed solution is available.
  • the leadership of the bolt is provided by a linearly adjustable in the control housing slide.
  • a linearly adjustable in the control housing slide With this embodiment, further, special space requirements can be met. There are relatively large contact surfaces between slide and control housing to realize so that the strength properties of the housing material sufficient in any case.
  • the adjustment curve is a straight line whose deviations from the circular arc shape are also absorbed by the clearance compensation elements.
  • the position of the bolt or its axis on the respective Verstellkurve is preferably determined by the direct or indirect contact with one or more cams, which are rotatably mounted on one or more adjustment shafts.
  • the cams are mounted on an axially displaceable adjustment axis.
  • the adjustment or the adjustment can in turn be rotated or displaced by a suitable gear or a connecting element of an adjusting means, such as 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.
  • a particularly advantageous in terms of space and variety of parts variant of the three embodiments is to simultaneously form the bolt on which the intermediate members are mounted as adjusting by provided with cams, rotatably mounted in the pendulum supports, the four-bar linkage or the slide and an adjusting means ,
  • an adjusting motor for example, an adjusting motor, according to the desired Ventilhubkurve is rotated.
  • sliders must be provided for the cams made of a material of increased strength in the control housing. Since the adjusting motor will usually be arranged fixed to the housing, but the bolt or the control shaft but displaced parallel to itself during the adjustment, must be arranged between the two a connecting element, which allows this shift.
  • This can be a PTO shaft, a Schmidt clutch, an Oldham clutch or even a gear or chain transmission depending on space requirements. With hydraulic actuation also offers a lever mechanism.
  • the device according to the invention can be provided separately for each valve of an engine, including an adjusting motor or an adjusting device, so that any desired combinations of valve lifts or opening angles the individual valves of an engine are possible, including the shutdown 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 bolt 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 very small cross-sections have to be released in the lowest load range and can be adhered to more precisely if they are only released 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 mounted on a common bolt.
  • an adjustment is provided according to the invention essentially during the common rest periods of all valves to be adjusted together. These are derived from the signal of the crankshaft and the camshaft and are getting shorter, the more valves are adjusted together. Their number is therefore limited.
  • 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 largely independent adjustment of the inlet and outlet valves offers the possibility to switch off selected valves by means of a continuous adjusting shaft, that is to say no longer open or at least to set a smaller valve lift.
  • 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.
  • the inventive solution was advantageous found an exact, low-wear adjustment for gas exchange valves, which also works with great accuracy.
  • 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 unclaimed solution in which the bolt 6 and its axis 7 is guided by a pendulum support 15 positively on the circular arc-shaped Verstellkurve 8.
  • the cylinder-head-side joint 16 of the pendulum support 15 or its axis coincides with the axis 9 of the roller 10 of the output member 11 together.
  • the adjusting shaft 17 carries cams 18 which determine the position of the bolt 6 and its axis 7 on the Verstellkurve 8 via plunger 18 a.
  • An adjustment of the axis 7 on the Verstellkurve 8, as shown by the directional arrow 14, is caused by a rotation of the cam 18 and the adjusting shaft 17 corresponding to the direction arrow 14a.
  • the adjusting movement described has a reduction of stroke and opening angle of the valve 13 result.
  • Fig. 3 shows a perspective view of the unclaimed solution similar Fig. 2 with pendulum support 15 for intake valve 19 and exhaust valve 20 of a cylinder, picked out from a number of cylinders or valves.
  • pendulum support 15 for intake valve 19 and exhaust valve 20 of a cylinder, picked out from a number of cylinders or valves.
  • the cylinder head side hinge 16 of the pendulum support 15 whose axis coincides with the axis 9 of the rollers 10 of the output members 11, so that the pin 6 is forcibly guided on a circular arc-shaped adjustment curve.
  • Bolt 6 Unlike the embodiment according to Fig. 2 takes over here Bolt 6 at the same time the function of the adjusting shaft. He wears the cams 18, which are supported on mounted in the housing, hardened sliders 21 and is rotatable in the pendulum support.
  • a connecting element of the bolt 6 is connected to the housing-fixed adjusting motor 23.
  • a propeller shaft 22 serves as a connecting element.
  • This embodiment offers considerable advantages in terms of variety of parts, but also space in the area of the actual valve control.
  • other connecting elements such as Schmitt couplings, Oldham couplings, toothed and chain drive come into question, a certain flexibility for the accommodation of the adjusting motor 23 is given.
  • Fig. 4 shows an embodiment of the invention for a valve or cylinder arrangement as in Fig. 3 in cross section.
  • the pin 6 is positively guided by four-bar linkages (24, 25, 26, 27) on a Verstellkurve 28, which comes close to a circular arc shape.
  • the bolt 6 could take over the function of an adjusting, as in Fig. 3 shown. But it can also, as shown, a separate adjusting 17 are used with cams 18.
  • the embodiment shown is particularly suitable for pre-assembly of valves including springs, levers and clearance compensation elements in the cylinder head as a lower housing part and a complete pre-assembly of all other parts in the control housing as the upper part.
  • the bearing blocks 32 for the joints 24 and 26 can be screwed in the same plane as the cover 33 of the camshaft bearing.
  • Fig. 5 shows a perspective view of the device according to the invention Fig. 4 , It can be better seen inlet valve 19 and exhaust valve 20 of the cylinder picked out, as well as the direct actuation of the bolt 6 by the cams 18. It can be clearly seen that not only the bolt 6 and the camshaft 1 in the upper housing part, the control housing can be pre-assembled, but also the adjusting shaft 17th
  • Fig. 6 shows a cross section through an unclaimed solution using a slide 34, which can be used separately for each valve or valve pair. Due to the separate application, the longest possible resting periods or common resting phases result, so that an adjustment is easily possible only during the rest periods. For the 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 approximates a circular arc about the axis 9 of the roller 10 of the stationary output member 11 only more or less well. In the Fig. 6 the deviation is exaggerated.
  • Fig. 7 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 will with the help of the low-resolution rotation angle sensor 43 on the camshaft or at another, running at half crankshaft speed shaft, the individual cylinders.
  • signals are sent to the individual servomotors 23 for leveling the torque peaks or the crankshaft speed, in which the valve strokes of the cylinders are corrected upwards with smaller torques and those of the cylinders with larger torques downwards.
  • an adjustment takes place, with or without compensation, during the common rest phases of the valves operated by an adjusting motor. Its phase position takes the engine management 44 the sensor 43 on the camshaft by the way.

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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)

Claims (19)

  1. Dispositif pour l'actionnement variable de soupapes de cylindre pour des moteurs à combustion interne, qui présente les caractéristiques suivantes:
    a) une ou plusieurs cames (2) d'un arbre à cames (1), monté dans un carter, tourne / tournent en fonction de la vitesse de rotation du moteur,
    b) la came (2) entraîne un organe intermédiaire (4), qui est monté sur un tourillon (6) avec un axe (7) et exécute un pur mouvement de rotation oscillant autour de l'axe (7),
    c) le tourillon (6) de l'organe intermédiaire (4) peut être déplacé, guidé réciproquement et parallèlement à lui-même, dans le carter, le long d'une courbe de réglage (28),
    d) l'organe intermédiaire (4) présente une courbe de commande (5) avec une zone d'arrêt (5a) et une zone de course (5b) et actionne, par l'intermédiaire de cette courbe de commande (5), un organe d'entraînement (11), qui, de son côté, actionne au moins une soupape (13),
    caractérisé en ce que,
    pour le guidage forcé du tourillon (6), est prévu un quadrilatère articulé relié à la culasse ou au carter et présentant des premiers (24, 26) et des deuxièmes (25, 27) points d'articulation, dans laquelle les deux premiers points d'articulation (24, 26) sont disposés fixement et à une première distance l'un de l'autre, et chacun des deux deuxièmes points d'articulation (25, 27) est agencé en pivotement autour de l'un des premiers points d'articulation (24, 26), la distance entre les deuxièmes points d'articulation (25, 27) étant plus petite que la première distance entre les deux premiers points d'articulation (24, 26), de sorte que le tourillon (6) se trouve guidé sur une courbe de réglage (28) à peu près en forme d'arc de cercle.
  2. Dispositif selon la revendication 1, caractérisé en ce qu'un élément hydraulique de compensation de jeu (31) est agencé sur l'organe d'entraînement (11).
  3. Dispositif selon revendication 1 ou 2, caractérisé en ce que la position du tourillon (6), respectivement de son axe (7), est réglée, directement ou indirectement sur la courbe de réglage (8, 28, 35) au moyen d'au moins un disque à came (18) ou d'une came, et que le tourillon (6), respectivement son axe (7), s'appuie sensiblement dans la direction tangentielle de la courbe de réglage (8, 28, 35) par rapport au carter.
  4. Dispositif selon revendication 1 ou 2, caractérisé en ce qu'une unité hydraulique établit directement ou indirectement la position chaque fois exigée du tourillon (6), respectivement de son axe (7), sur la courbe de réglage (8, 28, 35), et soutient celui-ci dans la direction tangentielle de la courbe de réglage (8, 28, 35), par rapport au carter.
  5. Dispositif selon la revendication 3, caractérisé en ce que les disques à came devant pivoter (18) sont disposées sur un arbre de réglage (17) qui est ajusté par l'intermédiaire d'un servomoteur (23) et, si nécessaire, d'une transmission.
  6. Moteur à combustion interne comprenant au moins un dispositif selon l'une ou plusieurs des revendications 1 à 5, l'un des dispositifs étant séparément associé à chaque soupape du moteur.
  7. Moteur à combustion interne comprenant au moins un dispositif selon l'une ou plusieurs des revendications 1 à 5, un dispositif étant séparément associé chaque fois à deux soupapes parallèles, voisines, d'un cylindre.
  8. Dispositif selon la revendication 7, caractérisé par un organe intermédiaire (4) commun, avec deux courbes de commande différentes pour les deux soupapes.
  9. Dispositif selon la revendication 7, caractérisé par deux cames (2) différentes et deux organes intermédiaires (4), avec différentes courbes de commande pour les deux soupapes.
  10. Dispositif selon l'une ou plusieurs des revendications 1 à 9, caractérisé en ce que les organes de transmission sont configurés de sorte qu'il existe au moins une position de réglage de l'organe intermédiaire (4) déplaçable, dans laquelle au moins une soupape (13) reste fermée pendant la rotation des cames (2).
  11. Dispositif selon l'une ou plusieurs des revendications 1 à 10, caractérisé par l'actionnement commun, groupé des soupapes de plusieurs cylindres et par un tourillon (6) commun, continu pour tous les organes intermédiaires (4) de ces soupapes.
  12. Dispositif selon l'une ou plusieurs des revendications 3 à 11, caractérisé en ce que le boulon (6) peut tourner librement sur le côté de son guidage, en ce qu'il porte, relié, solidaire en rotation, l'un ou plusieurs des disques à came (18), et en ce qu'il peut être pivoté par un moteur de réglage (23), par l'intermédiaire d'un élément de liaison approprié, et que les disques à cames (18) s'appuient par rapport au boîtier.
  13. Dispositif selon la revendication 12, caractérisé en ce que les disques à cames (18) prennent appui sur des coulisseaux (21) en matière de dureté surélevée, qui sont prévus dans le carter.
  14. Moteur à combustion interne comprenant plusieurs dispositifs selon l'une ou plusieurs des revendications 1 à 5 ou 8 à 13, caractérisé par un arbre de réglage (17) commun, qui présente au moins un disque à came (18) pour chaque dispositif, et le disque à came (18) pour au moins un dispositif présente une section dans laquelle la position de ce dispositif ne subit aucune modification lors de la rotation de l'arbre de réglage (17), et le disque à came (18) pour au moins un autre dispositif provoque une modification de la position de cet autre dispositif, pendant cette rotation de l'arbre de réglage (17).
  15. Moteur à combustion interne comprenant plusieurs dispositifs selon l'une ou plusieurs des revendications 1 à 5 ou 8 à 13, caractérisé par un arbre de réglage (17) commun, qui présente au moins une came (18) pour chaque dispositif et le contour de la came, pour au moins un dispositif, présente une section dans laquelle, lors du déplacement de l'arbre de réglage (17), la position de ce dispositif ne subit aucune modification, et le contour de la came, pour au moins un autre dispositif, provoque une modification de la position de cet autre dispositif, pendant cette rotation de l'arbre de réglage (17).
  16. Procédé pour l'exploitation d'un moteur à combustion interne à plusieurs cylindres, en utilisant un ou plusieurs dispositifs selon l'une ou plusieurs des revendications 1 à 5 ou 8 à 13, caractérisé en ce que, après qu'un état de charge désiré ait été atteint pour la totalité du moteur,
    a) des signaux d'angle de rotation du vilebrequin sont reçus par un premier détecteur d'angle de rotation (42) sur le volant moteur et sont évalués par un système de gestion du moteur (44) pour détecter des uniformités de rotation du vilebrequin et / ou des pointes de couple de rotation,
    b) celle-ci sont associées aux différentes cylindres, au moyen d'un deuxième détecteur d'angle de rotation (43), disposé sur l'arbre à cames ou sur un autre arbre tournant avec une demi vitesse de rotation du vilebrequin,
    c) à partir de ces informations sont générés des signaux, qui parviennent à différents entraînements pour l'écrêtement des pointes de couple de rotation et / ou des vitesses de rotation du vilebrequin, l'écrêtement étant atteint en ce que les courses des soupapes des cylindres à faibles couples de rotation sont corrigées vers le haut et celles des cylindres aux couples de rotation plus élevés sont corrigées vers le bas.
  17. Procédé pour l'exploitation d'un moteur à combustion interne à plusieurs cylindres, en utilisant un ou plusieurs dispositifs selon l'une ou plusieurs des revendications 1 à 5 ou 8 à 13, caractérisé en ce que,
    a) à chaque cylindre, sont associés un dispositif séparé et un entraînement pour l'actionnement du dispositif,
    b) la position de phase des phases de repos de chacune des soupapes commandées par un entraînement est déterminée, et
    c) les mouvements de réglage des dispositifs respectifs ont lieu pendant les phases de repos communes des soupapes desservies par l'entraînement respectif.
  18. Procédé selon la revendication 17, caractérisé en ce que la position de phase des phases de repos de chacune des soupapes commandées par un entraînement est déterminée par un système de gestion du moteur (44), à partir du signal d'un détecteur d'angle de rotation (43), disposé sur l'arbre à cames.
  19. Dispositif selon la revendication 1, caractérisé en ce que les points d'articulation (24, 25, 26, 27) sont disposés les uns par rapport aux autres de sorte que, au point d'orientation, les droites (29, 30), reliant chacune deux points d'articulation (24, 25, 26, 27), se coupent au point central d'un rouleau (10) prévu sur l'organe d'entraînement (11).
EP04721181A 2003-03-24 2004-03-17 Dispositif de commande variable de soupapes d'echange des gaz pour moteurs a combustion interne et procede de fonctionnement d'un dispositif de ce type Expired - Lifetime EP1608851B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10312959A DE10312959B4 (de) 2003-03-24 2003-03-24 Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren
DE10312959 2003-03-24
PCT/EP2004/002743 WO2004085804A1 (fr) 2003-03-24 2004-03-17 Dispositif de commande variable de soupapes d'echange des gaz pour moteurs a combustion interne et procede de fonctionnement d'un dispositif de ce type

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EP1608851A1 EP1608851A1 (fr) 2005-12-28
EP1608851B1 true EP1608851B1 (fr) 2008-10-01

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US (1) US7296546B2 (fr)
EP (1) EP1608851B1 (fr)
AT (1) ATE409801T1 (fr)
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WO (1) WO2004085804A1 (fr)

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DE102005040959A1 (de) * 2005-08-30 2007-03-08 Bayerische Motoren Werke Ag Hubvariabler Ventiltrieb für eine Brennkraftmaschine
US7363893B2 (en) * 2005-12-05 2008-04-29 Delphi Technologies, Inc. System for variable valvetrain actuation
DE102006022481A1 (de) 2006-05-13 2007-11-15 Bayerische Motoren Werke Ag Zylinderkopf für eine Brennkraftmaschine mit einem hubvariablen Ventiltrieb
JP4766007B2 (ja) * 2007-06-14 2011-09-07 トヨタ自動車株式会社 可変動弁装置
US9133735B2 (en) 2013-03-15 2015-09-15 Kohler Co. Variable valve timing apparatus and internal combustion engine incorporating the same
DE102016205805A1 (de) * 2016-04-07 2017-10-12 Bayerische Motoren Werke Aktiengesellschaft Ventiltrieb sowie Motorbaugruppe
CN108068370B (zh) * 2017-11-09 2024-01-16 特乐斯特机械(上海)有限公司 一种轮胎生产线胎侧带自动过料分料对中装置

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Also Published As

Publication number Publication date
US20060260574A1 (en) 2006-11-23
DE10312959A1 (de) 2004-11-18
ATE409801T1 (de) 2008-10-15
DE502004008152D1 (de) 2008-11-13
DE10312959B4 (de) 2006-10-05
EP1608851A1 (fr) 2005-12-28
WO2004085804A1 (fr) 2004-10-07
US7296546B2 (en) 2007-11-20

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