EP1078148B1 - Dispositif pour le reglage de la position de phase d'un arbre - Google Patents

Dispositif pour le reglage de la position de phase d'un arbre Download PDF

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Publication number
EP1078148B1
EP1078148B1 EP98929296A EP98929296A EP1078148B1 EP 1078148 B1 EP1078148 B1 EP 1078148B1 EP 98929296 A EP98929296 A EP 98929296A EP 98929296 A EP98929296 A EP 98929296A EP 1078148 B1 EP1078148 B1 EP 1078148B1
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EP
European Patent Office
Prior art keywords
stator
rotary piston
valve
adjusting device
channels
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
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EP98929296A
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German (de)
English (en)
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EP1078148A1 (fr
Inventor
Siegfried Eisenmann
Hermann Harle
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Trochocentric International AG
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Trochocentric International AG
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Publication of EP1078148A1 publication Critical patent/EP1078148A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear

Definitions

  • the invention relates to an adjusting device for adjusting the Phase position of a shaft, in particular a camshaft, according to the generic term of claim 1.
  • the valves of internal combustion engines are operated by camshafts.
  • the camshafts are from a drive shaft, or from the crankshaft, via a Transfer device set in rotary motion.
  • To the opening and Closing times of valves to the current output and / or To be able to adjust the speed of the engine are transmission devices with adjusters for adjusting the phase position of the camshaft rotation alignment used.
  • Such adjusters enable needs-based influencing the timing of the intake and / or exhaust valves, so that especially the so-called overlap of the valve lift curves can be changed.
  • the camshafts of the exhaust valves are also rotated.
  • the adjuster preferably sits between that of a chain or one Timing belt driven camshaft sprocket and the camshaft.
  • Corresponding the respective transmission device would, however, also be one another arrangement of the adjuster, for example between the drive shaft and the drive shaft gear.
  • the relative rotational position between the The camshaft sprocket and the camshaft are in a predetermined angular range variable.
  • a camshaft rotation range of 0 ° is preferably sufficient up to 30 °. In four-stroke engines where the camshaft is at half the speed the crankshaft rotates, this range corresponds to a crankshaft rotation range from 0 ° to 60 °. If both camshafts at the same time are adjustable, one speaks of a double variable camshaft control (Double vanos). It causes a fuller torque curve of the engine and optimizes the mixture preparation so that the pollutants in the exhaust gas be reduced.
  • Double vanos double variable camshaft control
  • the task of the adjuster is to determine the beginning and the end of the Valve stroke through the camshaft from “late” to “early” and vice versa adjust. This must be achievable over a wide engine speed range his.
  • the adjustment should preferably take place continuously and automatically.
  • the Advantages of correct adjustment are: more torque in the lower and medium speed range, less unburned residual gases at idle, Improved idling, lower pollutant emissions, internal exhaust gas recirculation even at low speed, faster warm-up of the catalyst and lower raw emissions after the cold start, special functions for the Mixture adjustment during warm-up, reduced fuel consumption and one lower engine noise.
  • the invention particularly relates to adjusters which are actuated hydraulically. If necessary, the adjuster is operated by an additional hydraulic pump fed. Preferably, however, a supply by the lubricating oil pump of the Motors are sufficient, which is particularly cost-effective and economical.
  • a preferred adjuster should have any desired angle adjustment regardless of the torque acting on the camshaft can set and hold for a sufficiently short time. To do this must be Work capacity or its adjustment performance must be correspondingly large. At a Feeding through the lubricating oil pump occurs at high oil temperature and even at low speed of the motor and thus the pump due to problems of the low available oil pressure. It will be high Adjustment speed desired. The required feed pressure and / or Feed flow should be as low as possible. At the same time, the building dimensions should be so small be that no further structural changes to the engine are necessary become.
  • the adjuster should preferably be located radially within the Find the camshaft sprocket and build it axially short.
  • a known adjuster uses an axially acting hydraulic piston axial adjustment of a sleeve.
  • the sleeve includes an internal and an external helical toothing, the two gears with opposite pitch are trained.
  • the external toothing of the sleeve engages with the Cam gear connected internal teeth and the internal teeth of the
  • the sleeve engages in a toothing connected to the camshaft.
  • Through a axial adjustment of the sleeve becomes an angle adjustment between the Camshaft gear and the camshaft achieved.
  • the adjustment range is because of the limited axial length. If the helix angle is increased, the working piston must have the same transferable torque be enlarged, which in turn leads to a larger piston diameter leads.
  • Another known adjuster is designed as a so-called wing adjuster.
  • An outer housing part is firmly connected to the camshaft sprocket and includes radially inwardly projecting areas that form an annulus into subspaces divide. Wings stand from a shaft part fastened to the camshaft radially outwards into a subspace. These wings are laterally and radially on the outside close to the subspace boundary, so that a rotary lobe system arises.
  • By adding oil to one side of all wings and that Draining oil on the other side of all wings can cause a twist can be achieved between the outer housing part and the shaft part.
  • By an integration of the product of radius and working pressure over the A transmission and adjustment torque is determined for the wing surfaces. The more The wings are arranged around the circumference, the higher that is given Oil pressure generated torque. At the same time, however, with a larger number Wing the maximum adjustment angle is reduced, because yes the installation space in Circumferential direction is limited.
  • the oil pressure of the lubricating oil pump is too low to torque in the adjuster generate that is greater than the maximum camshaft torques.
  • the Tips of the camshaft torques adjust the rotational position of the adjuster until the wings touch a subspace boundary. Because the camshaft torques oscillate between positive and negative maxima, the If the oil pressure is too low, adjuster away from a desired rotational position alternately deflected in both directions of rotation until the wings touch. This leads to excessive wear and unpleasant noises.
  • a braking element is used, for example, that dampens the oscillating movements at low oil pressure.
  • an oil supply valve To adjust and hold the rotary position is an oil supply valve, one Rotational position detection and a control designed so that deviations from a target position can be corrected by an appropriate valve actuation.
  • the required oil pressure and accordingly the leakage-related oil consumption this rotary lobe adjuster is high because the full pressure also holds a set twist position or for transmitting the camshaft torques is needed.
  • Corresponding to that in both directions of rotation occurring maximum camshaft torques occur in the Working areas of the rotary lobe system have high peak values. If the oil supply valve is closed, these high pinch pressures only interfere in the Way that correspondingly high leakage losses occur.
  • Open valve can change the oil into the wrong during torque peaks Flow in the direction because, especially at low engine speeds, the Actuation oil pressure is lower than the pinch pressure. In this way the Adjustment speed and positioning accuracy reduced, so that at such engines the oil pump must be dimensioned much larger. This leads to higher ones, especially at high engine speeds Energy losses.
  • the invention is based on the object of finding an adjuster, each desirable angular adjustment even with torques acting on the shaft, especially in the one transmitted from the valves to a camshaft Torque curve, makes adjustable. His work ability or his Adjustment performance should be as large as possible even at low actuation fluid pressure. At the same time, the construction dimensions and the manufacturing effort should be small.
  • Such Machines include at least one stator, one rotor or rotary piston, an output part and a valve device, the rotating portions of the Working space between stator and rotor connects with high and low pressure.
  • the number of teeth on the internal teeth of the stator is preferably one than that of the external toothing of the rotary piston.
  • the individual components a rotary piston machine can be done with little effort, in particular by means of sintered.
  • the ring-shaped machine parts and the work area take up little space.
  • An adjuster according to the invention is preferred be placed directly between the camshaft and the camshaft sprocket, wherein the camshaft gear is in particular formed directly on the stator, so that only an extremely small additional installation space is required.
  • the rotary position adjuster as a rotary piston machine or hydraulic motor with two ring-shaped rotary connections for starting and closing Discharge of pressure fluid can, for example, in addition to Camshafts require adjustment tasks in other applications Take over the drive task. That is the adjuster according to the invention both as an alignment or positioning unit and as a movement unit rotating shafts can be used.
  • the Phase position and / or the rotational speed of a width that of a Drive shaft via a transmission device with at least one on one Shaft-mounted transmission wheel is rotatable, the rotational position or Speed of rotation of the transmission wheel relative to the shaft with pressurized fluid, the can be fed in and out via two ring-shaped rotary connections.
  • Actuation is a fluid supply device with a controller, a Rotational position or rotational speed detection and at least one Control valve inserted so that the setting of a target rotational position or - Speed, or acceleration by a corresponding Valve actuation can be achieved.
  • a rotary piston machine in which the rotation transmission from Rotary piston on the driven part with the speed ratio 1: 1.
  • the Valve device of the rotary piston machine then preferably includes the Output part rotating, in particular formed thereon, first and second, evenly distributed over the circumference.
  • radial valve channels with inner Connection areas of radial, evenly distributed over the circumference, Interact stator channels.
  • the outer connection areas of the Stator channels open between the teeth of the internal teeth of the stator the workspace.
  • the number of first and second valve channels differs differ from the number of stator channels by one channel, so that the inner Connection areas of the stator channels in a first circumferential partial area first valve channels and in a second circumferential section with second Valve channels are connected.
  • the first valve channels are via an inner one Ring channel in the output part to the one ring-shaped rotary connection and the second valve channels via a space between the output part and the Rotary pistons and an outer connecting channel in the stripping section to the others circular rotary connector connected.
  • CH 676 490 the force or Torque transmission, for example with a cardan shaft. This would lead to a large overall length in the axial direction.
  • Another, in the transmission device mentioned in CH 676 490 comprises a coupling by means of bolts, which in one part have matching bores and in the other part in bores with twice the eccentricity larger diameter than that Bolt diameters are added. The bolts roll during rotation transmission along the boundary surfaces of the larger holes. This too Bolt transmission leads to an increased overall length in the axial direction.
  • the adjuster is preferred for adjusting the camshaft phase position on the camshaft, but possibly on the drive or on one additional transmission shaft arranged.
  • the preferred adjusters work according to the orbit principle in the High-pressure hydraulics known high-torque hydraulic motors. This results in an extremely high work capacity.
  • the rotational position is adjusted stepless and has no angle restriction. Because of the interlocking Tooth shapes, and the trained in the preferred designs Self-locking, no beating noises occur.
  • they are adjusters according to the invention are simple to manufacture and require only a few Parts.
  • the adjuster 1 shows an adjuster 1, which is attached to a free end of a camshaft 2 is arranged.
  • the adjuster 1 is designed as a rotary piston machine and includes at least one driven part 3, a rotary piston 4 and one Stator 5.
  • An external toothing 6 of the stator 5 forms the camshaft gear 6 ', which could possibly also be attached to the stator 5 as a separate part.
  • By rotating the rotary piston 4 by one Camshaft axis 2a rotating eccentric axis is a twist between Stator 5 and stripping section 3 achieved.
  • a part of working chambers 7 between the stator 5 and the rotary piston 4 selectively fed pressurized fluid or oil under pressure and out another part of working chambers 7 fluid can be drained.
  • the Working chambers 7 are formed according to FIG. 2 between a stator internal toothing 5a and a circular piston external toothing 4a.
  • The is preferably Number of teeth of the stator internal teeth 5a twelve and those of the rotary piston external teeth 4a eleven.
  • the rotary motion of the rotary piston is caused by the fluid supply-related expansion of the working chambers 7 of the one Half of the circumference and the corresponding reduction in the size of the working chambers 7 other half of the circumference.
  • To control the fluid supply or the To connect working chambers 7 so rotating with high or low pressure that the desired rotary piston movement is a valve device intended.
  • the valve device comprises a rotating with the speed of the rotary piston 4 (FIG. 3) and a channel system that is firmly connected to the stator 5 (FIG. 4). Because the rotating channel system of the illustrated embodiment on the driven part 3 2, the driven part 3 is preferably by the Interaction of an external output gear 3a and a rotary piston internal gear 4b rotated. The rotary transmission from the rotary piston 4 on the output part 3 takes place with the speed ratio 1: 1, which is why Number of teeth of the output external gear 3a with that of the rotary piston internal gear 4b matches. It is also shown in the Embodiment also the number of teeth of the circular piston outer toothing 4a same size as that of the circular piston internal teeth 4b.
  • the valve device comprises with the driven part 3 rotating, preferably formed thereon, first 8 and second 9, radial evenly distributed over the circumference Valve channels, with inner connection areas 10 of radial, even Distributed over the circumference, stator channels 11 cooperate, the outer Connection areas 12 between the teeth of the internal teeth 5a of the stator 5 open into the working chambers.
  • the number of the first or second Valve channels 8, 9 differ from the number of stator channels 11 by a channel so that the inner connection regions 10 of the stator channels 11 in a first peripheral portion with first valve channels 8 and in a second Circumferential portion are connected to second valve channels 9.
  • the inner ones and outer connection areas 10 and 12 of the stator channels 11 are bores by a control disk 19 firmly connected to the stator 5 educated.
  • the stator channels 11 are preferably as recesses in the outside Stator cover 20 formed.
  • the first valve channels 8 close via an inner ring channel 13 in the Output part 3 and in the camshaft 2, and at least one first Radial bore 15a to an annular first rotary connection 14a.
  • the second valve channels 9 close via a space 16 between the Output part 3 and the rotary piston 4, an outer connecting channel 17 in Output part 3 and a radial bore 15b in the camshaft 2 to a second annular rotary connector 14b.
  • ring grooves 18 for receiving Sealing elements formed.
  • the stator housing includes the outer stator cover 20 Control disc 19, the stator 5 and an inner stator cover 21st
  • the stator housing is held together by screws 22.
  • the rotary piston 4 is in the axial direction with the inside of the control disc 19 and the inside Stator cover 21 in sliding contact.
  • the stator housing is in Axial direction rotatably held on abrasion part 3.
  • the driven part 3 is non-rotatable connected to the camshaft 2, preferably one on the Camshaft 2 screwed, axially arranged screw part 23 through a Output end part 24 and the output part 3 extends. Between the Screw part 23 and the driven part 3, the inner ring channel 13 is formed.
  • the stator housing is in an annular groove between the driven end part 24 and the driven part 3 rotatably and by means of a sealing unit 25th sealed to the outside.
  • a guide ring 26 between the Output part and the camshaft end inserted.
  • a Range of rotation limitation formed between the Output end part 24 and the outer stator cover 20 a Range of rotation limitation formed. This includes, for example, two radially outwardly projecting end part abutment surfaces 27 each one Stator stop surface 28 is assigned so that the adjustment only within a predetermined range of rotation angle is possible.
  • the stator 5 with the internal toothing and / or the rotary piston 4 and / or the Output part 3 and / or the stator cover 20, 21 are preferably in powder metallurgical process. If necessary, a rotary piston 4 used from plastic. To reduce the weight are in Rotary piston 4 optionally formed axial cavities 29.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Golf Clubs (AREA)
  • Vehicle Body Suspensions (AREA)
  • Control Of Position Or Direction (AREA)
  • Heat Treatment Of Articles (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (13)

  1. Dispositif de réglage (1) pour régler la position de phase d'un arbre, en particulier d'un arbre à cames (2), susceptible d'être mis en rotation depuis un arbre d'entraínement, en particulier un arbre de vilebrequin, par l'intermédiaire d'un dispositif de transmission comportant au moins une roue de transmission (6') montée sur un arbre, le dispositif de réglage rendant réglable la position en rotation de la roue de transmission (6') par rapport à l'arbre (2), en utilisant un fluide sous pression qui peut être amené et évacué par deux raccordements rotatifs (14a, 14b) en forme d'anneaux, et un dispositif d'alimentation en fluide muni d'une commande, d'une détection de position en rotation et d'au moins une soupape de commande, permettant d'obtenir le réglage d'une position en rotation de consigne au moyen d'un actionnement correspondant d'une soupape, caractérisé en ce que le dispositif de réglage (1) est une machine à piston circulaire fonctionnant selon le principe orbital, comprenant un stator (5) avec une denture intérieure (5a), un piston circulaire (14) en forme d'anneau avec une denture extérieure (4a) s'engrenant dans la denture intérieure du stator (5a), une partie menée (3) susceptible d'être mise en rotation par le piston circulaire (4), et un dispositif à soupape (8 à 12) permettant, pour la commande du mouvement du piston circulaire, de relier des zones partielles rotatives de l'enceinte de travail (7) entre le stator (5) et le piston circulaire (4), à une haute pression ou à une basse pression du dispositif d'alimentation en fluide.
  2. Dispositif de réglage (1) selon la revendication 1, caractérisé en ce que le nombre de dents de la denture intérieure du stator (5a) est, de un, supérieur à celui de la denture extérieure du piston circulaire (4a).
  3. Dispositif de réglage selon la revendication 1 ou 2, caractérisé en ce que la transmission rotative du piston circulaire (4) à la partie menée (3) s'effectue dans le rapport de vitesse de rotation 1 : 1, et le dispositif à soupape (8 à 12) comprend des premiers et deuxièmes canaux à soupape (8, 9) radiaux, répartis régulièrement sur la périphérie, tournant avec la partie menée (3), réalisés de préférence sur celle-ci, les canaux de soupape (8, 9) radiaux coopérant avec des zones de raccordement intérieures (10) de canaux de stator radiaux (11) répartis régulièrement sur la périphérie, dont des zones de raccordement (12) extérieures débouchent entre les dents de la denture intérieure du stator (5a) dans l'enceinte de travail (7), le nombre des premiers, respectivement deuxièmes canaux de soupape (8, 9) étant différent du nombre des canaux de stator (11), la différence étant de un canal, de manière que les zones de raccordement intérieures (10) des canaux de stator (11), dans une première zone partielle périphérique, soient reliées à des premiers canaux de soupape (8) et, dans une deuxième zone partielle périphérique, soient reliées à des deuxièmes canaux de soupape (9).
  4. Dispositif de réglage selon la revendication 3, caractérisé en ce que les premiers canaux de soupape (8) raccordent, par l'intermédiaire d'un canal annulaire intérieur (13) ménagé dans la partie menée (3), à un premier raccordement rotatif (14b) en forme d'anneau, et les deuxièmes canaux de soupape (9) raccordent, par l'intermédiaire d'un espace libre (16), entre la partie menée (3) et le piston circulaire (4), et un canal de liaison extérieur (17), ménagé dans la partie menée (3), à l'autre raccordement rotatif (14a) en forme d'anneau.
  5. Dispositif de réglage selon la revendication 3 ou 4, caractérisé en ce que les zones de raccordement intérieures et extérieures (10, 12) des canaux de stator (11) sont réalisées dans un disque de commande (19) relié rigidement au stator (5), et les canaux de stator (11) sont réalisés de préférence sous forme de cavités ménagées dans le couvercle de fermeture de stator (20).
  6. Dispositif de réglage selon l'une des revendications 1 à 5, caractérisé en ce qu'une denture extérieure de la partie menée (3a) s'engrène dans une denture intérieure du piston circulaire (4b), sachant que, de préférence, les nombres de dents et/ou les formes de dents sont choisis telle que la liaison rotative entre la partie menée (3) et le stator (5) soit autobloquante, de manière que toute position de rotation, également en cas d'absence de fluide sous pression et de couples élevés entre le stator (5) et la partie menée (3), soit maintenue fermement, essentiellement par une liaison à ajustement de forme.
  7. Dispositif de réglage selon la revendication 6, caractérisé en ce que les deux dentures du piston circulaire (4a, 4b) ont les mêmes nombres de dents, ce nombre de dents étant de préférence de onze, et en particulier le nombre de dents de la denture intérieure du stator (5a) étant de douze.
  8. Dispositif de réglage selon l'une des revendications 1 à 7, caractérisé en ce que des cavités (29) axiales sont formées dans le piston circulaire (5), dans le but de diminuer le poids.
  9. Dispositif de réglage selon l'une des revendications 1 à 8, caractérisé en ce que la partie stator, portant la denture intérieure (5a) et/ou le piston circulaire (4) et/ou la partie menée (3) et/ou le couvercle de fermeture de stator (20, 21), sont fabriqués par un procédé faisant appel à la métallurgie des poudres.
  10. Dispositif de réglage selon l'une des revendications 1 à 9, caractérisé en ce que le piston circulaire (4) est fabriqué en matière synthétique.
  11. Dispositif de réglage selon l'une des revendications 1 à 10, caractérisé en ce que la partie menée (3) est susceptible d'être reliée de façon assujettie en rotation à l'arbre à cames (2), sachant que, de préférence, une partie filetée (23) disposée axialement, bloquée par vissage sur l'arbre à cames (2), s'étend à travers une partie menée de fermeture (24) et la partie menée (3), le stator (5), en particulier, étant maintenu dans une gorge annulaire entre la partie menée de fermeture (24) et la partie menée (3) et est formé, le cas échéant, de quatre parties maintenues assemblées à l'aide de vis, précisément un premier et un deuxième couvercle de fermeture de stator (20, 21), un disque de commande (19) et une partie de denture (5).
  12. Dispositif de réglage selon la revendication 11, caractérisé en ce qu'entre la partie menée de fermeture (24) et le couvercle de fermeture de stator (20) est réalisée une limitation de plage de rotation, de préférence sous la forme de deux faces de butée de partie de fermeture (27), faisant saillie radialement vers l'extérieur, à chacune desquelles est associée une face de butée de stator (28), de manière que le réglage ne soit possible que dans les limites d'une plage d'angle de rotation prédéterminée.
  13. Dispositif de réglage selon l'une des revendications 1 à 12, caractérisé en ce que la roue de transmission (6') est fixée au stator (5), en particulier cependant est réalisée directement sur celui-ci, la roue de transmission (6') comprenant de préférence une denture pour chaíne ou pour courroie crantée.
EP98929296A 1998-05-12 1998-05-12 Dispositif pour le reglage de la position de phase d'un arbre Expired - Lifetime EP1078148B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP1998/002759 WO1999058821A1 (fr) 1998-05-12 1998-05-12 Dispositif pour le reglage de la position de phase d'un arbre

Publications (2)

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EP1078148A1 EP1078148A1 (fr) 2001-02-28
EP1078148B1 true EP1078148B1 (fr) 2003-05-14

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EP98929296A Expired - Lifetime EP1078148B1 (fr) 1998-05-12 1998-05-12 Dispositif pour le reglage de la position de phase d'un arbre

Country Status (13)

Country Link
US (1) US6386165B1 (fr)
EP (1) EP1078148B1 (fr)
JP (1) JP2002514705A (fr)
KR (1) KR20010043542A (fr)
CN (1) CN1292845A (fr)
AT (1) ATE240452T1 (fr)
AU (1) AU7911398A (fr)
BR (1) BR9815968A (fr)
CA (1) CA2330144A1 (fr)
DE (1) DE59808397D1 (fr)
HU (1) HUP0101674A3 (fr)
SK (1) SK16982000A3 (fr)
WO (1) WO1999058821A1 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001088344A1 (fr) * 2000-05-13 2001-11-22 Krupp Presta Ag Dispositif de reglage pour ajuster la position angulaire d'un arbre
DE10027857A1 (de) * 2000-06-06 2001-12-20 Trochocentric International Ag Getriebe mit Federglied
JP3546002B2 (ja) * 2000-08-29 2004-07-21 株式会社日立ユニシアオートモティブ バルブタイミング制御装置の製造方法
DE10351223B4 (de) * 2003-10-28 2010-02-18 Hydraulik-Ring Gmbh Nockenwellenverstelleinrichtung für Fahrzeuge, vorzugsweise für Kraftfahrzeuge
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KR20010043542A (ko) 2001-05-25
CA2330144A1 (fr) 1999-11-18
SK16982000A3 (sk) 2001-04-09
EP1078148A1 (fr) 2001-02-28
WO1999058821A1 (fr) 1999-11-18
US6386165B1 (en) 2002-05-14
AU7911398A (en) 1999-11-29
CN1292845A (zh) 2001-04-25
JP2002514705A (ja) 2002-05-21
ATE240452T1 (de) 2003-05-15
DE59808397D1 (de) 2003-06-18
HUP0101674A2 (hu) 2001-08-28
BR9815968A (pt) 2001-10-23
HUP0101674A3 (en) 2002-01-28

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