WO2001011201A1 - Dispositif de reglage pour le reglage de la position de phase d'un arbre - Google Patents

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

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Publication number
WO2001011201A1
WO2001011201A1 PCT/EP1999/005677 EP9905677W WO0111201A1 WO 2001011201 A1 WO2001011201 A1 WO 2001011201A1 EP 9905677 W EP9905677 W EP 9905677W WO 0111201 A1 WO0111201 A1 WO 0111201A1
Authority
WO
WIPO (PCT)
Prior art keywords
stator
adjusting device
rotary piston
teeth
control valve
Prior art date
Application number
PCT/EP1999/005677
Other languages
German (de)
English (en)
Inventor
Hermann Härle
Siegfried A. Eisenmann
Original Assignee
Trochocentric (International) Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Trochocentric (International) Ag filed Critical Trochocentric (International) Ag
Priority to PCT/EP1999/005677 priority Critical patent/WO2001011201A1/fr
Priority to AU54202/99A priority patent/AU5420299A/en
Priority to ARP000103886A priority patent/AR024962A1/es
Publication of WO2001011201A1 publication Critical patent/WO2001011201A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—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
    • 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

  • Adjustment device for adjusting the phase position of a shaft
  • the invention relates to an adjusting device for adjusting the phase position of a driven shaft, in particular a camshaft.
  • the valves of internal combustion engines are actuated by means of a camshaft.
  • the camshafts are rotated by a drive shaft or by the crankshaft via a transmission device.
  • transmission devices with adjusters are used to adjust the phase position of the camshaft rotation alignment.
  • Such adjusters enable the control times of the intake and / or exhaust valves to be influenced as required, so that above all the so-called overlap of the valve lift curves can be changed.
  • this angle adjuster for the camshafts of the intake valves.
  • the camshafts of the exhaust valves are also rotated at the same time.
  • the adjuster is preferably located in the transmission path between the camshaft gear driven by a chain or a toothed belt and the camshaft.
  • the relative rotational position between the camshaft sprocket and the camshaft can be varied within a predetermined angular range.
  • a camshaft rotation range of 0 ° to 30 ° is preferably sufficient. In the case of four-stroke engines in which the camshaft rotates at half the speed of the crankshaft, this range corresponds to a crankshaft rotation range from 0 ° to 60 °. If both camshafts are adjustable at the same time, one speaks of a double variable camshaft control (double Vanos). It causes a fuller one Torque curve of the engine and optimizes the mixture preparation so that the
  • Pollutants in the exhaust gas can be reduced.
  • the task of the adjuster is to adjust the start and end of the valve lift from the “late” to the “early” and vice versa by means of the camshaft. This must be achievable over a wide engine speed range.
  • the adjustment should preferably take place continuously and automatically.
  • the advantages of correct adjustment are: more torque in the lower and middle 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 catalytic converter and lower raw emissions after a cold start, special functions for the mixture adjustment during warm-up, reduced fuel consumption and lower engine noise.
  • the invention particularly relates to adjusters which are actuated hydraulically. If necessary, the adjuster is fed by an additional hydraulic pump. Preferably, however, a supply by the lubricating oil pump of the engine should suffice, which is particularly cost-effective and economical.
  • a preferred adjuster should be able to set and hold any angle adjustment that is desirable in practice, regardless of the respective torque acting on the camshaft, in a sufficiently short time. To do this, his work capacity or adjustment capacity must be correspondingly large.
  • problems arise due to the low available oil pressure when the oil temperature is high and the engine and thus the pump speed is low. A high adjustment speed is desired.
  • the required feed pressure and / or feed flow should be as low as possible. At the same time, the construction dimensions should be so small that no further structural changes to the engine are necessary.
  • the adjuster should preferably find space radially within the camshaft sprocket and short axially.
  • a known adjuster uses an axially acting hydraulic piston for axial
  • the sleeve comprises an internal and an external helical toothing, the two toothings being designed with opposite pitch.
  • the external toothing of the sleeve engages in an internal toothing firmly connected to the camshaft sprocket and the internal toothing of the sleeve engages in a toothing connected to the camshaft.
  • Axial adjustment of the sleeve achieves an angular adjustment between the camshaft sprocket and the camshaft.
  • the adjustment range is limited due to the limited axial length. If the helix angle is increased, the working piston must be enlarged with the same transferable adjustment torque, which in turn leads to a larger piston diameter.
  • Another known adjuster is designed as a so-called wing adjuster.
  • An outer housing part is firmly connected to the camshaft sprocket and comprises radially inwardly projecting areas which divide an annular space into subspaces. From a shaft part fastened to the camshaft, vanes project radially outwards into a partial space. These wings lie laterally and radially on the outside close to the sub-area boundary, so that a rotary lobe system is created.
  • By supplying oil on one side of all vanes and draining oil on the other side of all vanes By supplying oil on one side of all vanes and draining oil on the other side of all vanes, a twist between the outer housing part and the shaft part can be achieved.
  • a transmission and adjustment torque is determined. The more Wings are arranged on the circumference, the higher the torque generated at a given oil pressure. At the same time, however, the maximum adjustment angle is reduced in the case of a larger number of leaves because the installation space is limited in the circumferential
  • the oil pressure of the lubricating oil pump is too low to generate a torque in the adjuster that is greater than the maximum camshaft torques.
  • the peaks of the camshaft torques adjust the rotational position of the adjuster until the wings rest on a partial area boundary. Because the camshaft torques oscillate between positive and negative maxima, if the oil pressure is too low, the adjuster is deflected alternately in both directions of rotation from a desired rotational position until the wing comes into contact. This leads to heavy wear and unpleasant noises.
  • a brake element is used, for example, which dampens the oscillating movements at low oil pressure.
  • an oil supply valve, a rotational position detection and a control are designed such that deviations from a desired position are corrected by a corresponding valve actuation.
  • the required oil pressure and, accordingly, the leakage-related oil consumption of this rotary lobe adjuster is high because the full pressure is also required to maintain a set rotational position or to transmit the camshaft torques.
  • high peak values occur in the working areas of the rotary lobe system. If the oil supply valve is closed, these high pinch pressures only interfere in such a way that correspondingly high leakage losses occur.
  • the invention has for its object to provide an adjusting device that makes any angle adjustment that is desirable in practice also possible with torques acting on the shaft, in particular with the torque curve transmitted from the valves to a camshaft. Its working capacity or its 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, a rotor or rotary piston, an output part and a commutator device, which connects rotating partial areas of the working space between the stator and rotor with high and low pressure.
  • the number of teeth of the internal teeth of the stator is preferably one greater than that of the external teeth of the rotary piston.
  • the individual components of a rotary piston machine can be manufactured with little effort, in particular by means of sintering.
  • the ring-shaped machine parts and the work space take up little space.
  • An adjuster according to the invention will preferably be arranged directly between the camshaft and the camshaft gear, the camshaft gear in particular being 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 rotary connections for supplying and discharging pressure fluid, in addition to the adjustment task required for camshafts, for example, it can be used in others Applications take on a drive task. That is, the one according to the invention
  • the adjuster can be used both as an alignment or positioning unit and as a movement unit on rotating shafts. In the most general case, the
  • Phase position and / or the rotational speed of a shaft which is from a drive shaft via a transmission device with at least one seated on a shaft
  • Transmission wheel is rotatable, the rotational position or speed of rotation
  • Fluid supply device with a control, a rotational position or
  • Rotational speed detection and at least one control valve used so that the
  • the control valve can be attached outside the adjustment device, but preferably as close as possible to the adjustment device in order to obtain short fluid lines from the control valve to the adjustment device.
  • the control valve is particularly preferably integrated directly into the adjusting device.
  • an integrated control element for the pressurized fluid is known for an axially acting hydraulic piston for adjusting a helically toothed sleeve.
  • the control valve can be integrated into one or more components of the adjusting device designed as a rotary piston machine by means of design measures.
  • the control valve is preferably seated in a central screw of the adjusting device, preferably in the axis of the camshaft.
  • the fluid is preferably fed to the control valve via the camshaft and further via various connecting channels in the individual elements of the adjusting device.
  • Rotating sections of the working space between the stator and rotor are connected with high and low pressure via grooves, which are connected or separated by means of a control piston.
  • the fluid flows out of that part of the work space that is connected to low pressure via the control valve.
  • the control piston is axially adjustable in order to separate or connect other grooves from each other.
  • the control piston can be controlled electromagnetically, pneumatically or hydraulically.
  • a rotary piston machine is now preferably provided, in which the rotation transmission from the rotary piston to the driven part takes place at a speed ratio of 1: 1.
  • the commutator control of the rotary piston machine then preferably comprises first and second radial fluid channels rotating with the driven part, in particular formed on the driven part, which are evenly distributed over the circumference and which interact with inner connection areas of radial stator channels distributed uniformly over the circumference.
  • the outer connection areas of the stator channels open into the working space between the teeth of the internal teeth of the stator.
  • the number of first or second fluid channels differs from the number of stator channels by one channel each, so that the inner connection areas of the stator channels are connected to first fluid channels in a first peripheral partial area and to second fluid channels in a second peripheral partial area.
  • the first fluid channels are via channels and bores on one fluid connection and the second fluid channels via a free space between the driven part and the rotary piston and other channels and bores on the other Fluid connection connected. High or low pressure is supplied to one or the other fluid connection via the control valve.
  • CH 676 490 In order to achieve a speed ratio of 1: 1 between the rotary piston and the driven part, a force transmission is formed between the rotary piston which is rotating about the axis of the driven part and the driven part.
  • the power or torque transmission can take place, for example, with a cardan shaft. That would lead to a large overall length.
  • Another transmission device mentioned in CH 676 490 comprises a coupling by means of bolts which are accommodated in suitable bores in one part and in bores with a diameter that is twice the eccentricity larger than the diameter in the other part. When transferring the rotation, the bolts roll along the edges of the larger bores. This bolt transmission also leads to an increased overall length in the axial direction.
  • a preferred solution according to CH 676 490 due to the smaller overall length comprises an internal toothing on the rotary piston and an external toothing on the driven part.
  • interacting teeth with tooth contours are provided in a driven part driven by the rotary piston, the axis of rotation of which can be stationary, which are adapted to the present eccentricity.
  • Such an oil pressure accumulator or oil reservoir could be provided outside the adjustment device or integrated into the adjustment device, in particular by a cutout in the camshaft or a sealing cover.
  • the temporarily stored oil pressure can also be used to adjust the adjustment device after a sudden breakdown of the engine oil pressure. This is e.g. B. advantageous if the engine was switched off in an uncontrolled manner, for example when the engine stalled, and there was no longer enough time to bring the phase shift of the camshaft back into the starting position for a restart. With the help of the stored oil pressure, the adjustment device can be moved back to the starting position before a new start.
  • the adjuster is preferably arranged on the camshaft, but possibly also on the drive shaft or on an additional transmission shaft instead.
  • the preferred adjusters work according to the orbit principle of the high-torque hydraulic motors known in high pressure hydraulics. This results in an extremely high work capacity.
  • the rotation position adjustment is infinitely variable and has no angular restriction. Because of the interlocking tooth shapes and the self-locking formed in preferred embodiments, no beating noises occur.
  • the adjusters according to the invention are easy to manufacture and require only a few parts. In the mentioned and described below using the examples
  • Embodiments with an output part, which can be rotated about a fixed axis at the rotational speed of the rotary piston, and in particular comprises a control part of the commutator device, are a solution that also serves as an advantageous, slow-running
  • Hydromotor can be used. It goes without saying that such a slow-running
  • Hydromotor can also be designed with a fixed output part and a rotating stator. In this case, rotating connections could then be dispensed with.
  • Slow-running hydraulic motors in particular arranged on shafts, can advantageously be used, for example, as drives in machine tools.
  • Fig. 1 shows a longitudinal section along the camshaft axis through a
  • FIG. 2 shows the cross section E-E according to FIG. 1
  • FIG. 3 shows the cross section D-D according to FIG. 1
  • FIG. 4 shows the cross section C-C according to FIG. 1
  • FIG. 5 is a view of the camshaft end with the adjuster according to FIG. 1st
  • Fig. 6 is a longitudinal section along the camshaft axis through one at the
  • Camshaft adjuster with integrated control valve.
  • Fig. 1 shows an adjuster 1, which is arranged at a free end of a camshaft 2.
  • the adjuster 1 is designed as a rotary piston machine and comprises at least one driven part 3, a rotary piston 4 and a stator 5.
  • An external toothing 6 of the stator 5 forms the camshaft gear 6 ', which is formed in one piece with the stator 5, but possibly also as a separate part against rotation could be attached to the stator 5.
  • a part of working chambers 7 between the stator 5 and the rotary piston 4 is selectively supplied with pressurized fluid, in particular oil under pressure, and fluid is discharged from another part of working chambers 7.
  • the working chambers 7 form between a stator internal toothing 5a and a circular piston external toothing 4a.
  • the number of teeth of the stator internal teeth 5a is preferably twelve and that of the rotary piston external teeth 4a is eleven.
  • the rotary movement of the rotary piston arises from the expansion of the working chambers 7 of one circumferential half due to the fluid supply and the corresponding reduction in size of the working chambers 7 of the other circumferential half.
  • a commutator control is provided in order to control the fluid supply or to connect the working chambers 7 with high or low pressure in such a way that the desired rotary piston movement occurs.
  • the commutator control comprises a channel system which rotates with the speed of the rotary piston 4 (FIG. 3) and a channel system which is fixedly connected to the stator 5 (FIG. 4). Because the rotating channel system of the embodiment shown is formed on the driven part 3, according to FIG. 2 the driven part 3 is preferably set in rotation by the interaction of an external gear toothing 3a and a circular piston internal toothing 4b. The rotation transmission from the rotary piston 4 to the driven part 3 takes place with the speed ratio 1: 1, for which purpose the number of teeth of the driven external gear 3a corresponds to that of the rotary piston internal gear 4b. In addition, in the embodiment shown, the number of teeth of the external piston teeth 4a is the same as that of the internal piston teeth 4b.
  • the commutator control includes first radial fluid channels 8 and second radial fluid channels 9 rotating with the output part 3, preferably formed thereon, which are evenly distributed over the circumference and which interact with inner connection areas 10 of radial stator channels 11 evenly distributed over the circumference, whose outer connection areas 12 open into the working chambers between the teeth of the internal toothing 5a of the stator 5.
  • the number of first and second fluid channels 8, 9 differs from the number of stator channels 11 by one channel each, so that the inner connection areas 10 of the stator channels 11 are in a first circumferential partial area with first fluid channels 8 and in a second peripheral section with second
  • Fluid channels 9 are connected.
  • the inner and outer connection regions 10 and 12 of the stator channels 11 are connected as bores by a stator 5
  • the stator channels 11 are preferably formed as depressions in the outer stator cover 20.
  • the first fluid channels 8 connect via an inner ring channel 13 in the driven part 3 and in the camshaft 2, and at least one first radial bore 15a to an annular first rotary connection 14a.
  • the second fluid channels 9 connect via a free space 16 between the driven part 3 and the rotary piston 4, an outer connecting channel 17 in the driven part 3 and a radial bore 15b in the camshaft 2 to a second annular rotary connection 14b.
  • annular grooves 18 are formed for receiving sealing elements.
  • An external control valve 41 connects either the first rotary connection 14a or the second rotary connection 14b with high or low pressure. Accordingly, the other rotary connection is subjected to low or high pressure.
  • the rotary connection 14a is connected, for example, to high pressure
  • the oil presses into the first fluid channels 8 via the radial bore 15a and the inner ring channel 13 connected to the working chambers 7 of this peripheral portion.
  • the other part of the working chambers 7 is connected to the low pressure side.
  • the inner connection areas 10 are at least partially overlapping with the second fluid channels 9. From the working chambers in this area, the oil runs through the outer connection areas 12 through the stator channels 11 via the inner connection areas 10 into second fluid channels 9. From there the oil reaches a free space 16 between the driven part 3 and the rotary piston 4. This free space 16 is connected to the rotary connection 14b via an outer connecting channel 17, through which the oil flows out.
  • the stator housing comprises the outer stator cover 20, the control disk
  • the stator housing is held together by screws 22.
  • the rotary piston 4 is in axial contact with the inside of the control disk 19 and the inner stator cover 21 in sliding contact.
  • the stator housing is rotatably held in the axial direction on the driven part 3.
  • the driven part 3 is connected to the camshaft 2 in a rotationally fixed manner, an axially arranged central screw 23, which is screwed to the camshaft 2, preferably extending through a driven end part 24 and the driven part 3.
  • the inner ring channel 13 is formed between the central screw 23 and the driven part 3.
  • the stator housing is rotatably held in an annular groove between the driven end part 24 and the driven part 3 and is sealed off from the outside by means of a sealing unit 25.
  • a guide ring 26 is inserted between the driven part 3 and the camshaft end.
  • a rotational range limitation is preferably formed between the driven end part 24 and the outer stator closure cover 20. This includes, for example, two radially outwardly projecting end stop faces 27, each of which a stator stop face 28 is assigned such that the adjustment is only possible within a predetermined range of rotation angles.
  • the arrangement of the rotation range limitation on the outer stator closure cover 20 shows with a simple visual check in which rotational position the camshaft 2 is located.
  • the stator 5 with the internal toothing and / or the rotary piston 4 and / or the driven part 3 and / or the stator sealing covers 20, 21 are preferably produced in the powder metallurgical process. If necessary, a rotary piston 4 made of plastic is used. To reduce the weight, axial cavities 29 are optionally formed in the rotary piston 4.
  • Figure 6 shows the structural design of the adjustment device with an integrated control valve. The control valve 41 is seated in the central screw 23 which is screwed into the camshaft 2. The principle of phasing also corresponds to that described above in this embodiment. With the exception of the arrangement of the control valve in the camshaft, more precisely in an extension of the camshaft, there are only a few design differences from the exemplary embodiment in FIG. In the exemplary embodiment in FIG.
  • the inner cover 21 is also the camshaft sprocket with external teeth 6 '.
  • Components having the same function as the components of the first exemplary embodiment are provided with the same reference symbols in the second exemplary embodiment.
  • the oil supply to the control valve 41 takes place through the camshaft 2, preferably via a central outer bore 40 in the camshaft 2. From there, the oil passes through a first oil feed bore 30 in the camshaft 2, a second oil feed bore 31 in the driven part 3 and a third oil feed bore 32 in the central screw 23 into the control valve 41.
  • the oil flows out on the low-pressure side either via first oil discharge holes 33 or via a second oil discharge hole 34, which each also contains two radial holes 34a and 34c to an oil outlet 56. Alternatively, the high and Low pressure pages can be exchanged.
  • a control piston 38 is used in the control valve 41 to connect the working chambers in the respective peripheral partial areas with either high or low pressure.
  • the control piston 38 is moved back and forth in its axial position by an electromagnet 39 in a manner known in valve technology. It is controlled by a central motor control and is preferably arranged in a machine-fixed manner.
  • the oil flow through the control valve 41 will now be described.
  • the control piston 38 lies in a central bore 52 which is in the central screw 23 on the Camshaft 2 opposite side is executed.
  • this bore 52 there are grooves 42,
  • the grooves 43 and 45 correspond to the fluid connections from FIG. 1.
  • Surfaces 47, 48 projecting radially inwards arise between the grooves,
  • the control piston 38 has three recesses, so that radially outwardly projecting sealing surfaces 53, 54 and 55 are formed. The tolerance between the
  • Fluid from the high pressure side passes from the outer bore 40 of the camshaft 2 through the bores 30, 31 and 32 into the groove 44. This is connected to either the first fluid channels 8 or the second fluid channels 9, depending on the position of the control piston 38.
  • groove 44 is connected to the first fluid channels 8.
  • the sealing surface 53 lies against the surface 47 and thus seals groove 42 from groove 43.
  • the surface 49 and the sealing surface 54 seal the grooves 44 and 45 from one another. High-pressure oil thus flows via the recess between the sealing surfaces 53 and 54 in the control piston 38 from the groove 44 into the groove 43 and from there via the first oil bore 35 into the first fluid channels 8.
  • the pressure oil flows in via the commutator control in the manner described above a part of the working chambers 7.
  • the oil on the low-pressure side flows from the other working chambers 7 via the commutator control and the second fluid channels 9 into the free space 16.
  • the pressure fluid flows through the bores 37, 36 into the groove 45. This is over another depression between the sealing surfaces 54 and 55 in the control piston 38 is connected to the groove 46.
  • the oil flows to the oil drain 56 via the first oil drain holes 33.
  • the control piston 38 is additionally guided between the surface 51 and the sealing surface 55.
  • the control piston 38 When the desired angular adjustment of the camshaft has been reached, the control piston 38 is moved into a middle position in which all the grooves 42, 43, 44, 45, 46 are separated from one another. The set position is held without oil pressure due to the self-locking of the teeth. If the adjusting device is to be moved back to its starting position, the control piston 38 is steered into a right position. In this position, the control piston 38 seals the groove 43 from the groove 44 and the groove 45 from the groove 46. Fluid on the high-pressure side now flows from groove 44 into groove 45 and from there further to the second fluid channels 9. Conversely, the first fluid channels 8 are connected to the low-pressure side, that is to say the fluid outlet.
  • a sealing unit 25 is provided between the outer stator closure cover 20 and the central screw 23.

Abstract

L'invention concerne un dispositif de réglage (1) pour le réglage de la position de phase d'un arbre commandé (2) avec du fluide de pression, l'arbre commandé étant mis en rotation par un arbre de commande et le dispositif de réglage étant une machine à piston rotatif travaillant selon le principe de l'orbite. Le dispositif de réglage selon l'invention comprend au moins une roue de transmission (6') entraînant l'arbre commandé (2), un stator (5) à denture intérieure (5a), un piston rotatif annulaire (4) à denture extérieure (4a) s'engrenant dans la denture intérieure (5a) du stator (5), un élément de sortie (3) mis en rotation par le piston rotatif (4), une soupape de commande (41) intégrée dans le dispositif de réglage (1), le réglage d'une position angulaire de consigne de l'arbre commandé (2) étant obtenu par un actionnement correspondant de la soupape de commande, ainsi qu'une commande de collecteur (8-12) qui, pour commander le mouvement du piston rotatif, relie des zones partielles rotatives d'une chambre de travail (7) située entre le stator (5) et le piston rotatif (4) à la pression haute ou basse du fluide.
PCT/EP1999/005677 1999-08-05 1999-08-05 Dispositif de reglage pour le reglage de la position de phase d'un arbre WO2001011201A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/EP1999/005677 WO2001011201A1 (fr) 1999-08-05 1999-08-05 Dispositif de reglage pour le reglage de la position de phase d'un arbre
AU54202/99A AU5420299A (en) 1999-08-05 1999-08-05 Adjusting device for adjusting the phase position of a shaft
ARP000103886A AR024962A1 (es) 1999-08-05 2000-07-27 Dispositivo de variacion para variar la sincronizacion de un eje accionado

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP1999/005677 WO2001011201A1 (fr) 1999-08-05 1999-08-05 Dispositif de reglage pour le reglage de la position de phase d'un arbre

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WO2001011201A1 true WO2001011201A1 (fr) 2001-02-15

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PCT/EP1999/005677 WO2001011201A1 (fr) 1999-08-05 1999-08-05 Dispositif de reglage pour le reglage de la position de phase d'un arbre

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AR (1) AR024962A1 (fr)
AU (1) AU5420299A (fr)
WO (1) WO2001011201A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004020794A1 (fr) * 2002-08-09 2004-03-11 Aft Atlas Fahrzeugtechnik Gmbh Dispositif de commande pour ajuster l'angle de rotation d'un arbre a cames
DE102004025215A1 (de) * 2004-05-22 2005-12-08 Ina-Schaeffler Kg Nockenwellenversteller
US7380529B2 (en) 2003-11-10 2008-06-03 Aft Atlas Fahrzeugtechnik Gmbh Method for adjusting an angle of rotation, and phase displacement device for carrying out said method

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3937644A1 (de) * 1989-11-11 1991-05-16 Bayerische Motoren Werke Ag Vorrichtung zur hydraulischen drehwinkelverstellung einer welle relativ zu einem antriebsrad, insbesondere nockenwelle fuer brennkraftmaschinen
EP0532214A1 (fr) * 1991-09-02 1993-03-17 Toyota Jidosha Kabushiki Kaisha Dispositif variateur de calage de soupapes pour moteur à combustion interne

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3937644A1 (de) * 1989-11-11 1991-05-16 Bayerische Motoren Werke Ag Vorrichtung zur hydraulischen drehwinkelverstellung einer welle relativ zu einem antriebsrad, insbesondere nockenwelle fuer brennkraftmaschinen
EP0532214A1 (fr) * 1991-09-02 1993-03-17 Toyota Jidosha Kabushiki Kaisha Dispositif variateur de calage de soupapes pour moteur à combustion interne

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004020794A1 (fr) * 2002-08-09 2004-03-11 Aft Atlas Fahrzeugtechnik Gmbh Dispositif de commande pour ajuster l'angle de rotation d'un arbre a cames
US6997151B2 (en) 2002-08-09 2006-02-14 Ina-Schaeffler Kg Control device for adjusting the angle of rotation of a camshaft
US7380529B2 (en) 2003-11-10 2008-06-03 Aft Atlas Fahrzeugtechnik Gmbh Method for adjusting an angle of rotation, and phase displacement device for carrying out said method
DE102004025215A1 (de) * 2004-05-22 2005-12-08 Ina-Schaeffler Kg Nockenwellenversteller

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AR024962A1 (es) 2002-10-30
AU5420299A (en) 2001-03-05

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