EP1302630B1 - Dispositif pour déphaser les soupapes d'échange de gaz d'un moteur à combustion interne, notamment déphaseur à piston rotatif pour déphaser un arbre à cames relativement au vilebrequin - Google Patents

Dispositif pour déphaser les soupapes d'échange de gaz d'un moteur à combustion interne, notamment déphaseur à piston rotatif pour déphaser un arbre à cames relativement au vilebrequin Download PDF

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Publication number
EP1302630B1
EP1302630B1 EP02020920A EP02020920A EP1302630B1 EP 1302630 B1 EP1302630 B1 EP 1302630B1 EP 02020920 A EP02020920 A EP 02020920A EP 02020920 A EP02020920 A EP 02020920A EP 1302630 B1 EP1302630 B1 EP 1302630B1
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EP
European Patent Office
Prior art keywords
locking element
receptacle
drive wheel
pressure
internal combustion
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
EP02020920A
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German (de)
English (en)
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EP1302630A2 (fr
EP1302630A3 (fr
Inventor
Eduard Golovatai-Schmidt
Andreas Strauss
Jens Schäfer
Martin Dr. Scheidt
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IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
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Publication date
Application filed by Schaeffler KG filed Critical Schaeffler KG
Publication of EP1302630A2 publication Critical patent/EP1302630A2/fr
Publication of EP1302630A3 publication Critical patent/EP1302630A3/fr
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Publication of EP1302630B1 publication Critical patent/EP1302630B1/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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis

Definitions

  • the invention relates to a device for changing the timing of gas exchange valves of an internal combustion engine according to the preamble of forming features of claim 1, and it is particularly advantageous to rotary piston adjustment for rotational angle adjustment of a camshaft relative to a crankshaft realized.
  • valve timing control device which is attached to the drive end of a cylinder head mounted in an internal combustion engine camshaft and formed in principle as a function of various operating parameters of the internal combustion engine controllable hydraulic actuator.
  • This device consists essentially of a standing with a crankshaft of the internal combustion engine in drive connection drive wheel and a rotatably connected to a camshaft the internal combustion engine associated impeller, which are in drive connection with each other and transmit the torque of the crankshaft to the camshaft of the internal combustion engine.
  • the drive wheel has a hollow space formed by a hollow cylindrical peripheral wall and two side walls, in which two hydraulic working spaces are formed by two radial boundary walls extending to the longitudinal central axis of the device.
  • the impeller has at the periphery of its hub two radially extending into the working space wings, which divide the working spaces in each case an A-pressure chamber and a B-pressure chamber, which in case of selective or simultaneous pressurization with a hydraulic pressure means pivotal movement or fixation of the impeller relative to the drive wheel and thus cause the camshaft relative to the crankshaft.
  • the impeller when falling below a required for adjustment pressure fluid pressure, such as when switching off the engine by a separate locking element in a preferred base position within its adjustment range with the drive wheel mechanically coupled to, in particular when restarting the internal combustion engine to build up the required pressure medium pressure From the alternating torques of the camshaft resulting stop clatter of the impeller to avoid the boundary walls of the drive wheel.
  • This specifically designed as a stepped cylindrical locking pin locking element is arranged in a direction parallel to the longitudinal center axis of the device bore at the end of a blade of the impeller and displaceable by a spring element into a locking position within a receptacle in the camshaft side facing away from the drive wheel.
  • the formed with a larger diameter portion of the locking pin is formed by the inner wall of the bore in the wing and the formed with a smaller diameter portion of the locking pin, the locking side for exact position determination between the impeller and drive wheel is additionally conical, through an inserted into the bore guide bushing guided.
  • the inclusion of the locking pin is concretely incorporated as in the camshaft side facing away from the drive wheel elongated bore is formed, which extends in a direction transverse to the direction of rotation of the impeller and is connected via a groove with an A-pressure chamber of the device.
  • annular surface formed at the transition between the cylindrical portions of the locking pin is also connected via a radial bore to a B pressure chamber of the device so that both upon pressurization of the A pressure chambers of the device and upon pressurization of the B pressure chambers of the device, the locking pin is hydraulically actuated can be moved into a Entkoppelwolf within the bore in the wing of the impeller.
  • a disadvantage of this known device is that the arrangement of the locking pin in a hole at the end of a wing of the impeller requires a massive construction of the wing and thus limits the number of possible hydraulic working spaces in the device to a maximum of three to four when with Device a conventional adjustment angle of about 30 ° NW should be feasible.
  • the relatively large distance between the longitudinal axis of the bore in the impeller blade and the longitudinal center axis of the device is the cause that reduces the stiffness of the locked connection between the impeller and the drive wheel and that the locking pin is still subject to significant centrifugal forces in the engine operation related with the simultaneously increasing sensitivity to dirt of the lock by the rotationally attached at the end of the wings accumulating dirt particles in the hydraulic pressure medium, the function of the lock can adversely affect.
  • the embodiment of the lock with a stepped cylindrical locking pin which is connected to the annular surface formed between the cylindrical sections and with its locking-side annular surface to both the A-pressure chambers and the B-pressure chambers of the device, has proven to be disadvantageous, that a lock when stopping the engine is not possible because at least one of the two surfaces is still acted on the locking pin with the pressure of the pressure medium and thus holds the locking pin in its Entkoppelwolf in the bore in the wing of the impeller.
  • the device is not operable with a targeted locking and above all unsuitable for applications on SOHC engines or exhaust camshafts, in which a locking of the impeller or the camshaft in an "early" timing of the gas exchange valves of the internal combustion engine is necessary.
  • the locking side conical design of the locking pin with a constant cone angle has also in connection with its elongated receiving bore in the camshaft side facing away from the drive wheel has the disadvantage that in the locking high component loads on the impeller and the drive wheel of the device occur and that there is a danger in the unlocking in that there is a jamming of the locking pin in the receiving bore.
  • the increased space requirement and the relatively high production cost of the stepped locking pin is still to be mentioned as a disadvantage, since these are the cause of a limited applicability of the device in confined spaces in the engine compartment and relatively high production costs of the device.
  • the mechanical coupling is effected by a pin-like locking element movably arranged in an axial bore in the wheel hub of the impeller, which is movable by a spring element into a coupling position within a complementary receptacle in the side wall of the drive wheel.
  • the complementary recording of the locking element is disposed within the pressure medium guide to a volume-minimized A-pressure chamber of a hydraulic working space of the device, so that at the same time the recording of the locking element is pressurized at the start of the internal combustion engine by the pressurization of the A-pressure chambers of the hydraulic working chambers and this against the force its spring element hydraulically moved into its Entkoppelwolf in the axial bore in the wheel hub of the impeller.
  • the invention is therefore based on the object to design a device for changing the timing of gas exchange valves of an internal combustion engine, in particular rotary piston adjustment for rotational angle adjustment of a camshaft relative to a crankshaft, which between its impeller and its drive wheel a simple and inexpensive to produce lock with a has low space requirements, which is largely unaffected by centrifugal forces and insensitive to dirt and which is arranged or designed so that the locked connection between impeller and drive wheel has a high rigidity and that universal use of the device is also possible on SOHC engines or exhaust camshafts ,
  • the object is achieved in that the inclusion of the locking element in one of the side walls of the drive wheel has a quadrangular and formed in its surface by a defined all-sided game greater than the cross-sectional area of the locking element contour and is formed with an opening worm groove for supplying pressure medium, which is connected exclusively to a pressure-free in the locking position of the impeller A-pressure chamber of the device and via which the recording of the locking element can be acted upon only by pressurization of the A-pressure chambers with the pressure of the hydraulic pressure medium.
  • the object is achieved in that the locking element is formed with a chamfer and a rounding of its front edge and a hollow end, while in its rear end face a blind hole for fixing the an end of the preferably designed as a compression coil spring spring element whose other end is supported on an inserted into the axial bore and formed with a centering counter-holder with a Y-shaped profile cross-section, in which the longitudinal grooves formed between its profile legs are also provided for pressure fluid venting the axial bore.
  • the object is achieved in that the receptacle of the locking element is preferably incorporated in the camshaft side facing away from the drive wheel and positioned so that their square-shaped contour with mounted device below the radial end of one of the boundary walls the drive wheel is arranged, wherein its preferably with a quarter-circle course extending to the level of the stop surface of an adjacent boundary wall of the drive wheel worm groove is arranged opening from a lying in the direction of rotation of the impeller in the contour of the recording.
  • this object is achieved in a device according to the preamble of claim 1 such that the locking element is formed as uniform over its entire length locking pin and disposed in an axial bore in the wheel hub of the impeller whose longitudinal axis has a minimum possible distance from the longitudinal central axis of the device ,
  • the receptacle of the locking pin arranged in one of the sidewalls of the drive wheel has a quadrangular contour formed in its surface around a defined all-sided clearance greater than the cross-sectional area of the locking pin and is formed with an opening worm groove for supplying pressure medium is connected to a pressure-free in the locking position of the impeller A-pressure chamber of the device and thus causes the inclusion of the locking pin only when pressurized the pressure chambers of the device with the necessary for unlocking the locking pin pressure of the hydraulic pressure medium can be acted upon.
  • the locking pin is formed at its end facing the receiving end with a phase and a rounding of its front edge and a hollow end, while in its rear end face a blind hole for fixing the having an end of the spring element preferably designed as a compression coil spring.
  • the other end of the spring element is supported by a counter-holder inserted into the axial bore for the locking pin and formed with a centering tip, which preferably has a Y-shaped profile cross-section and in which the longitudinal grooves formed between its profile limbs simultaneously provide the pressure medium venting of the axial bore are.
  • the formation of the receiving end of the locking pin with the described defined contour serves to ensure that the entering during the unlocking process from a certain point torque load of the locking pin does not jamming of the same causes or allows a safe and accelerated unlocking of the locking pin.
  • the constantly increasing pressure of the hydraulic pressure means a relative rotation relative to the game inserted between the impeller and the drive wheel of the device and thereby exerts a shear force or torque on the locking pin occurring on the lateral surface of the locking pin contour edge of its recording.
  • the hollow design of the receiving side end face of the locking pin has proved to reduce the adhesion forces between the face of this end face and the stop surface in the receptacle of the locking pin to be advantageous and thereby contributes that only the adhesion forces between the resulting annular surface on the end face of the locking pin and the stop surface must be overcome in the recording, to a shortening of the unlocking at.
  • the pressure fluid venting takes place regardless of their execution advantageously always against the existing atmospheric pressure and is executable in the same way both chain-driven and belt-driven devices, the vented pressure medium in a chain drive is discharged directly into the cylinder head and belt drives via an additional flange seal on the camshaft-facing side wall of the device in a tank line in the camshaft.
  • the recording of the locking pin is also proposed with respect to the recording of the locking pin to incorporate this in the camshaft side facing away from the drive wheel and position such that the square-shaped contour is arranged at mounted device below the radial end of one of the boundary walls of the drive wheel and their with a quarter-circle course reaching up to the level of the stop surface of an adjacent boundary wall of the drive wheel worm groove opens from a direction of rotation of the impeller into the contour.
  • the side of the opening worm groove opposite side of the contour of the recording is additionally formed with a hardened inlet radius to facilitate the engagement of the locking pin in the recording, while the corners of the contour are rounded with a diameter of the locking pin adapted radius.
  • the reason of the recording also has two different depth levels, of which the upper level is formed as a stop surface for the receiving side end face of the locking pin.
  • the incorporated into the upper level lower level of the receiving ground has a transition to the inflowing worm groove and is provided for supplying the hydraulic pressure medium to the end face of the locking pin.
  • the entering worm groove preferably has a square or approximately square cross-section and is incorporated with a smaller depth than the receptacle in the side wall of the drive wheel.
  • other suitable cross-sections for the worm groove and / or an equal or uniform depth of the worm groove that merges into the lower plane of the receptacle are also conceivable here.
  • the as mentioned above in its surface by a defined game larger than the cross-sectional area of the locking pin formed contour of the recording serves, moreover, on the one hand the balance of the radial bearing clearance between the On the radial end faces of the boundary walls of the drive wheel mounted impeller and the drive wheel and on the other hand, the compensation of production-related position tolerances between the locking pin in the wheel hub of the impeller and its inclusion in the side wall of the drive wheel both in the radial and in the circumferential direction of the device.
  • it allows the enlarged trained recording to adjust during assembly of the device optimal clearance for the locking pin to avoid jamming of the locking pin in the recording.
  • the inventively designed device for changing the timing of gas exchange valves of an internal combustion engine, in particular rotary piston adjustment for rotational adjustment of a camshaft relative to a crankshaft thus has over the known from the prior art devices has the advantage that by the displacement of the locking of a wing of the impeller in the hub of the impeller or by the significant shortening of the distance between the longitudinal axis of the lock and the longitudinal center axis of the device on the one hand substantially increases the rigidity of the locked connection between the impeller and the drive wheel and on the other hand significantly reduces the forces acting on the locking pin during engine operation centrifugal forces become.
  • the inventively designed device has the advantage that the uniformly formed on its entire length locking pin is easy and inexpensive to produce and has a low space requirement, so that the manufacturing cost of the device are further reduced and the device even in confined spaces in the engine compartment is universally applicable.
  • the special design of the recording of the locking pin and standing with the recording operatively connected end face of the locking pin are the cause that no more component loads between the impeller and the drive wheel of the device occur during locking and that when unlocking a jamming of the locking pin in the Recording is no longer possible.
  • connection of the recording of the locking pin exclusively with one of the A-pressure chambers of the device has the particular advantage that a targeted locking of the device when stopping the engine is possible. Since when switching off the internal combustion engine and thus in de-energized control valve of the device, the pressure medium pressure applied to the B-pressure chambers of the device, the impeller is usually rotated under volume minimization of the respective A-pressure chambers of the device in the Necessary for the start of the engine base position in which the Locking pin then locks reliably.
  • the inventively designed device is thus both on intake camshafts with locking in “later "Timing of the gas exchange valves as well as exhaust camshafts and SOHC engines with locking in 'early' timing of the gas exchange valves used.
  • FIGS. 1 and 2 clearly shows a device 1 for changing the timing of gas exchange valves of an internal combustion engine, which is a rotary piston adjusting device for adjusting the rotational angle of a not shown Camshaft with respect to a likewise not shown crankshaft of an internal combustion engine is formed.
  • This device 1 is attached to the drive-side end of a camshaft mounted in the cylinder head of the engine and designed in principle as a hydraulic actuator, which in dependence on various operating parameters of the internal combustion engine by the in FIG. 1 33 is controlled hydraulic valve.
  • the device 1 consists essentially of a standing with the crankshaft of the engine drivingly connected drive wheel 2 and a rotatably connected to the camshaft of the engine impeller 3, wherein the impeller 3 is pivotally mounted in the drive wheel 2 and with this in drive connection stands.
  • the drive wheel 2 in this case has a cavity formed by a hollow cylindrical peripheral wall 4 and two side walls 5, 6, in which five equally circumferentially distributed hydraulic working chambers 9 are formed by five directed to the longitudinal center axis of the device 1 radial boundary walls.
  • the impeller 3 of the device 1 accordingly has on the circumference of its hub 10 five uniformly circumferentially distributed and each radially into a working space 9 of the drive wheel 2 extending wings 11, which divide the working spaces 9 in each case an A-pressure chamber 12 and a B-pressure chamber 13 that cause a pivotal movement or fixation of the impeller 3 with respect to the drive wheel 2 and thus a rotational angle adjustment or hydraulic clamping of the camshaft relative to the crankshaft with selective or simultaneous pressurization with a hydraulic pressure means.
  • the device 1 to avoid a resulting from the alternating torques of the camshaft stop clatter of the impeller 3 at start of the internal combustion engine has a separate locking element 14, with the impeller 3 falls below a required for adjustment pressure medium pressure in a preferred base position within its adjustment range with the Drive wheel 2 is mechanically coupled.
  • This locking element 14 is in arranged parallel to the longitudinal center axis of the device 1 bore in the impeller 3 and displaceable by a spring element 15 in a locking position within a receptacle 16 in the side wall 5 of the drive wheel 2.
  • FIGS. 1 to 3 is in this respect still be removed that the locking element 14 is formed according to the invention as uniform over its entire length locking pin, which is arranged in a continuous axial bore 17 in the hub 10 of the impeller 3.
  • the longitudinal axis of this axial bore 17 has the smallest possible distance from the longitudinal central axis of the device 1, in order to minimize the centrifugal force influences on the locking element 14 that arise during engine operation.
  • the locking element 14, as shown FIG. 3 emerges on the receiving side formed with a phase 19 and a rounding 20 of its front edge, which accelerate the axial movement of the locking element 14 in its unlocked position while avoiding it in jamming.
  • Adhesion forces of the locking element 14 in the receptacle 16 are additionally avoided by the hollow formation of the front end 21 of the locking element 14, which is also visible in FIG. 3.
  • the locking element 14 On its rear end face 22, however, the locking element 14 has a blind bore 23 in which, as well as from FIG. 3 can be removed, which is fixed one end of the compression spring designed as a spring element 15.
  • the other end of this spring element 15 is supported on an inserted into the axial bore 17 and formed with a centering tip 24 abutment 15, which has a Y-shaped profile cross-section and in which the longitudinal grooves formed between its profile legs 26 at the same time for pressure fluid venting the axial bore 17 are provided.
  • recognizable receptacle 16 of the locking element 14 further has according to the invention a quadrangular and in its surface by a defined all-sided game greater than the cross-sectional area of the locking member 14 formed contour and is formed with an opening worm groove 18, which only with an unpressurized in locking position A-pressure chamber 12 of the device 1 is connected. This ensures that the receptacle 16 of the locking element 14 is acted upon only upon pressurization of the A-pressure chambers 12 of the device 1 via the worm groove 18 with the pressure of the hydraulic pressure medium and thus the locking member 14 is moved to its unlocked position.
  • FIG. 4 It can be seen that the receptacle 16 of the locking element 14 is incorporated into the side wall 5 of the drive wheel 2 facing away from the camshaft and is positioned such that its quadrangular contour is arranged below the radial end face 27 of a limiting wall 7 of the drive wheel 2, indicated by dashed lines in the drawing.
  • the worm groove 18 has a quarter-circle course up to the level of the stop surface 28 of an adjacent boundary wall 8, also shown in phantom, and opens into the contour of the receptacle 16 from a side lying in the direction of rotation of the impeller 3.
  • the side of the worm groove 18 opposite side of the contour of the receptacle 16, however, as the magnifications of FIGS.
  • FIGS. 5 and 6 show, formed with a hardened inlet radius 29, which facilitates the engagement of the locking element 14 in the receptacle 16.
  • the unspecified corners of the contour with a diameter of the locking pin 14 corresponding radius are rounded and that the bottom of the receptacle 16 has two different depths levels 30, 31.
  • the upper level 30 is formed as a stop surface of the locking pin 14 in the receptacle 16, while the incorporated into the upper level 30 lower level 31 has a transition 32 to the opening worm groove 18 and is provided for supplying the hydraulic pressure medium to the end 21 of the locking element 14 ,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (4)

  1. Dispositif pour faire varier les durées de réglage de soupapes d'échange de gaz d'un moteur à combustion interne, en particulier dispositif de réglage à piston rotatif pour le réglage de l'angle de rotation d'un arbre à cames par rapport à un vilebrequin, comprenant les caractéristiques suivantes :
    - le dispositif (1) est fixé à l'extrémité côté entraînement d'un arbre à cames monté dans la culasse du moteur à combustion interne, et est réalisé en principe sous forme d'entraînement de réglage hydraulique commandable en fonction de différents paramètres de fonctionnement du moteur à combustion interne,
    - le dispositif (1) se compose essentiellement d'une roue d'entraînement (2) en liaison d'entraînement avec un vilebrequin du moteur à combustion interne, et d'un rotor (3) connecté de manière solidaire en rotation à un arbre à cames du moteur à combustion interne,
    - la roue d'entraînement (2) présente une cavité formée par une paroi périphérique cylindrique creuse (4) et deux parois latérales (5, 6), dans laquelle au moins une chambre de travail hydraulique (9) est formée par au moins deux parois de limitation radiales (7, 8),
    - le rotor (3) présente, à la périphérie de son moyeu (10), au moins une pale (11) s'étendant radialement dans une chambre de travail (9) de la roue d'entraînement (2), laquelle divise celle-ci en une chambre de pression A (12) et une chambre de pression B (13),
    - les chambres de pression (12, 13) provoquent, lors de la sollicitation en pression sélective ou simultanée avec un fluide hydraulique sous pression, un mouvement de pivotement ou une fixation du rotor (3) par rapport à la roue d'entraînement (2) et donc de l'arbre à cames par rapport au vilebrequin,
    - le rotor (3), si la pression de fluide sous pression nécessaire au réglage n'est pas suffisante, peut être accouplé mécaniquement à la roue d'entraînement (2) par un élément de verrouillage séparé (14) dans une position de base préférée à l'intérieur de sa plage de réglage,
    - l'élément de verrouillage (14) est disposé dans un alésage dans le rotor (3) qui est parallèle à l'axe médian longitudinal du dispositif (1) et peut être déplacé par un élément de ressort (15) dans une position de verrouillage à l'intérieur d'un logement (16) dans l'une des parois latérales (5, 6) de la roue d'entraînement (2),
    - le logement (16) de l'élément de verrouillage (14) est connecté à au moins une chambre de pression (12 ou 13) à l'intérieur du dispositif (1), de sorte que dans le cas d'une sollicitation en pression de cette chambre de pression (12 ou 13), l'élément de verrouillage (14) puisse être déplacé hydrauliquement dans une position de déverrouillage à l'intérieur de l'alésage dans le rotor (3),
    - l'élément de verrouillage (14) étant réalisé en tant que broche de verrouillage uniformément cylindrique sur toute sa longueur, et étant disposé dans un alésage axial (17) dans le moyeu (10) du rotor (3), dont l'axe longitudinal présente un espacement aussi faible que possible de l'axe médian longitudinal du dispositif (1),
    caractérisé en ce que
    - le logement (16) de l'élément de verrouillage (14) présente, dans l'une des parois latérales (5, 6) du rotor (2), un contour quadrilatéral dont la surface est plus grande, dans la mesure d'un jeu circonférentiel défini, que la surface en section transversale de l'élément de verrouillage (14), et est réalisé avec une rainure débouchant en forme de ver (18) pour l'alimentation en fluide sous pression,
    - la rainure est connectée exclusivement à une chambre de pression A (12) sans pression du dispositif (1) dans la position de verrouillage du rotor (3) et par le biais de laquelle le logement (16) de l'élément de verrouillage (14) ne peut être sollicité que lors de la sollicitation en pression de la chambre de pression A (12) avec la pression du fluide hydraulique sous pression.
  2. Dispositif selon le préambule de la revendication 1, caractérisé en ce que
    - l'élément de verrouillage (14) est réalisé avec un biseau (19) et un arrondi (20) de son arête frontale ainsi qu'avec un côté frontal creux (21), tandis qu'il présente dans son côté frontal arrière (22) un alésage de base (23) pour la fixation de l'une des extrémités de l'élément de ressort (15) réalisé de préférence sous forme de ressort de compression à boudin,
    - l'autre extrémité de l'élément de ressort s'appuie sur une contre-fixation (25) insérée dans l'alésage axial (17) et réalisée avec une pointe de centrage (24), ayant une section transversale profilée en forme de Y, les rainures longitudinales (26) formées entre ses branches profilées étant en même temps prévues pour l'évacuation du fluide sous pression de l'alésage axial (17).
  3. Dispositif selon le préambule de la revendication 1, caractérisé en ce que
    - le logement (16) de l'élément de verrouillage (14) est incorporé de préférence dans la paroi latérale (5) de la roue d'entraînement (2) opposée à l'arbre à cames et est positionné de telle sorte que son contour quadrilatéral soit disposé sous le côté frontal radial (27) de l'une des parois de limitation (7 ou 8) de la roue d'entraînement (2) lorsque le dispositif (1) est monté,
    - sa rainure en forme de ver (18) s'étendant de préférence avec une allure en forme de quart de cercle jusqu'à la hauteur de la surface de butée (28) d'une paroi de limitation adjacente (8 ou 7) de la roue d'entraînement (2) étant disposée depuis un côté situé dans la direction de rotation du rotor (3) en débouchant dans le contour du logement (16).
  4. Dispositif selon la revendication 3, caractérisé en ce que
    - le côté du contour du logement (16) opposé au côté avec la rainure en forme de ver (18) est réalisé avec un rayon d'entrée (29) durci en surface, tandis que les coins du contour sont arrondis avec un rayon adapté à l'élément de verrouillage (14) et la base du logement (16) présente deux plans à des profondeurs différentes (30, 31),
    - dont le plan supérieur (30) est réalisé sous forme de surface de butée de l'élément de verrouillage (14) tandis que le plan inférieur (31) incorporé dans le plan supérieur (30) présente une transition (32) pour la rainure débouchant en forme de ver (18) et est prévu pour introduire le fluide hydraulique sous pression vers le côté frontal (21) de l'élément de verrouillage (14).
EP02020920A 2001-10-15 2002-09-19 Dispositif pour déphaser les soupapes d'échange de gaz d'un moteur à combustion interne, notamment déphaseur à piston rotatif pour déphaser un arbre à cames relativement au vilebrequin Expired - Lifetime EP1302630B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10150856 2001-10-15
DE10150856A DE10150856B4 (de) 2001-10-15 2001-10-15 Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Rotationskolben-Verstelleinrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle

Publications (3)

Publication Number Publication Date
EP1302630A2 EP1302630A2 (fr) 2003-04-16
EP1302630A3 EP1302630A3 (fr) 2003-11-26
EP1302630B1 true EP1302630B1 (fr) 2009-05-06

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Application Number Title Priority Date Filing Date
EP02020920A Expired - Lifetime EP1302630B1 (fr) 2001-10-15 2002-09-19 Dispositif pour déphaser les soupapes d'échange de gaz d'un moteur à combustion interne, notamment déphaseur à piston rotatif pour déphaser un arbre à cames relativement au vilebrequin

Country Status (5)

Country Link
US (1) US6805080B2 (fr)
EP (1) EP1302630B1 (fr)
JP (1) JP2003120231A (fr)
DE (2) DE10150856B4 (fr)
ES (1) ES2324598T3 (fr)

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DE10354586A1 (de) * 2003-11-21 2005-06-16 Ina-Schaeffler Kg Hydraulischer Nockenwellenversteller und Verfahren zum Betreiben desselben
DE10355502A1 (de) * 2003-11-27 2005-06-23 Ina-Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Rotationskolben-Verstelleinrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
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CN106460580B (zh) * 2014-03-20 2019-08-20 吉凯恩粉末冶金工程有限公司 具有锁定盘的可变凸轮轴调节器、锁定盘及用于制造其的方法

Also Published As

Publication number Publication date
ES2324598T3 (es) 2009-08-11
DE10150856A1 (de) 2003-04-24
US6805080B2 (en) 2004-10-19
EP1302630A2 (fr) 2003-04-16
EP1302630A3 (fr) 2003-11-26
DE10150856B4 (de) 2005-08-11
JP2003120231A (ja) 2003-04-23
US20030084863A1 (en) 2003-05-08
DE50213520D1 (de) 2009-06-18

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