EP2302177B1 - Dispositif de commande variable d'ouverture/fermeture de soupape - Google Patents

Dispositif de commande variable d'ouverture/fermeture de soupape Download PDF

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Publication number
EP2302177B1
EP2302177B1 EP10002953A EP10002953A EP2302177B1 EP 2302177 B1 EP2302177 B1 EP 2302177B1 EP 10002953 A EP10002953 A EP 10002953A EP 10002953 A EP10002953 A EP 10002953A EP 2302177 B1 EP2302177 B1 EP 2302177B1
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EP
European Patent Office
Prior art keywords
phase
rotational member
side rotational
biasing
control device
Prior art date
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Not-in-force
Application number
EP10002953A
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German (de)
English (en)
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EP2302177A1 (fr
Inventor
Masaki Kobayashi
Kenji Nonaka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
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Aisin Seiki Co Ltd
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Publication of EP2302177A1 publication Critical patent/EP2302177A1/fr
Application granted granted Critical
Publication of EP2302177B1 publication Critical patent/EP2302177B1/fr
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0478—Torque pulse compensated camshafts
    • 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
    • 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
    • F01L2001/34483—Phaser return springs

Definitions

  • Patent Document 1 paragraphs 0009 and 0029, Figs. 1 , 2 and 3
  • the valve opening/closing timing control device disclosed in Patent Document 1 includes a lock mechanism capable of locking a relative phase to an intermediate phase which is suitable for starting of an internal combustion engine, if necessary.
  • the lock mechanism has a lock groove formed in the driven side rotational member, and a lock pin movably supported by the driving side rotational member so as to be fitted into the lock groove.
  • the lock pin is biased by a spring in a direction of fitting the lock pin into the lock groove.
  • valve opening/closing timing control device is provided with a biasing mechanism, such as a torsion spring, for biasing the relative phase in a direction of the intermediate phase, as a means for suppressing a tendency in which the driven side rotational member is retarded with respect to the driving side rotational member by a reaction force of a cam received from a valve spring of the intake valve or the exhaust valve.
  • a biasing mechanism such as a torsion spring
  • US 23009/02355884 A1 discloses a valve opening/closing timing control device with a first torsional bias spring which urges the rotor toward an intermediate locking position from any position retarded of the locking position and a second torsional bias spring which urges the rotor in the advance direction over the full range of phaser authority to compensate for added camshaft torque loads imposed by non-valve actuating functions such as driving a mechanical fuel pump.
  • both of the first and second springs urge the rotor in the same direction or the advance direction.
  • the lock mechanism is not constituted of a lock groove formed on one rotational member and a lock pin supported by the other rotational member, but constituted of a biasing member interposed between the driving side rotational member and the driven side rotational member, it is mechanistically simple, and thus the valve opening/closing timing control device which is not susceptible to failure is obtained. In addition, it is possible to downsize the valve opening/closing timing control device.
  • the relative phase can be maintained reliably at the predetermined phase, for example, as compared with the above configuration in which one torsion spring (biasing member) is installed.
  • the aspect of this disclosure can be implemented by the biasing member of a simple configuration in which a spring such as a torsion spring or a spiral spring is disposed between the driving side rotational member and the driven side rotational member which are placed adjacent to each other, an assembling operation of the valve opening/closing timing control device is easily performed, and miniaturization can be easily performed.
  • a spring such as a torsion spring or a spiral spring
  • the relative phase can be maintained reliably at the predetermined phase, for example, as compared with the above configuration in which one torsion spring is installed.
  • Fig. 1 is a cross-sectional view illustrating an overall structure of a valve opening/closing timing control device according to a first embodiment
  • Figs. 5A and 5B are cross-sectional views taken along the line IIIa-IIIa and IIIb-IIIb in the state of Fig. 4 ;
  • Figs. 9A and 9B are views illustrating a valve opening/closing timing control device according to a second embodiment which correspond to Figs. 3A and 3B ;
  • Fig. 12 is an exploded perspective view of major parts of the valve opening/closing timing control device according to the second embodiment
  • the valve opening/closing timing control device includes a bush 18 fitted to the outer circumference of the camshaft 3 so as to relatively rotate with respect to the camshaft 3.
  • the operating oil supplied from a hydraulic pump P to the supply oil passage 18a is supplied to a cylindrical space 2S of the inner rotor 2 by the oil passage system.
  • the fluid control valve mechanism V includes, as shown in Fig. 1 , a housing 28 integrally constituted of an operating oil control portion Va having a spool valve 22, and an operating oil supply/discharge portion Vb of a cylindrical shape to perform the distribution of the operating oil.
  • the spool valve 22 is slid by an electromagnetic solenoid 21 disposed on an upper end portion of the operating oil control portion Va in an upper and lower portion on the figure.
  • the operating oil supply/discharge portion Vb is rotatably inserted in the cylindrical space 2S of the inner rotor 2.
  • a main oil passage 23 penetrates into the center portion of the operating oil supply/discharge portion Vb to receive the operating oil from the above-described inner oil passage 2a, and a check valve C is provided in the main oil passage 23 to block flow of the fluid toward the cylindrical space 2S.
  • the spool valve 22 has a bottomed cylindrical shape.
  • the housing 28 is fixed to a front cover or the like of the engine, and the inner rotor 2 is rotatably supported by the operating oil supply/discharge part Vb.
  • a compression spring 29 is installed between the spool valve 22 and the bottom surface of the housing 28 to bias the spool valve 22 in an upward direction on the figure. If the solenoid 21 is energized in the state of Fig. 1 , an operation rod 30 protruding downward from the solenoid 21 moves the spool valve 22 to a downward position. If the energization is stopped, the operation rod 30 is retracted toward the solenoid 21 side, and the spool valve 22 is returned to an upward position shown in Fig. 1 by the biasing force of the compression spring 29 while following up with the movement of the rod 22.
  • control system of the valve opening/closing timing control device includes a crank angle sensor detecting the rotational angle of the crankshaft of the engine, a camshaft angle sensor detecting the rotational angle of the camshaft 3, and an ECU (not shown) controlling the fluid control valve mechanism V.
  • the ECU detects the relative phase of the outer rotor 1 and the inner rotor 2 from the detected result of the above-described crank angle sensor and camshaft angle sensor.
  • the distribution of the operating oil to each of the retarded angle chamber 11 and the advanced angle chamber 12 is performed by operating the fluid control valve mechanism V based on the information of the relative phase and the information of the driving state (e.g., revolutions of engine, temperature of cooling water or the like), thereby controlling the relative rotational phase of the outer rotor 1 and the inner rotor 2.
  • phase control is achieved between the most retarded angle phase (relative rotational phase in which the volume of the retarded angle chamber 11 is maximized) and the most advanced angle phase (relative rotational phase in which the volume of the advanced angle chamber 12 is maximized).
  • the ECU stops the distribution of the operating oil to the retarded angle chamber 11 and the advanced angle chamber 12 by the fluid control valve mechanism V, so that the vane 5 is not applied with the operating oil of any direction. Consequently, the engine stops in the state in which the relative phase of the outer rotor 1 and the inner rotor 2 is displaced at the start-up optimum phase suitable for next start-up by the above-described biasing operation of the spiral springs S1and S2.
  • the engine starts up reliably.
  • the ECU After the start-up of the engine, the ECU performs the distribution of the operating oil to each of the retarded angle chamber 11 and the advanced angle chamber 12 by the fluid control valve mechanism V to change the relative phase of the outer rotor 1 and the inner rotor 2, so that the control of the opening and closing timing of the intake valve and the exhaust valve is performed by the ECU.
  • the inner rotor 2 may reach the most retarded angle phase with respect to the outer rotor 1.
  • the ECU controls the phase of the inner rotor 2 with respect to the outer rotor 1 to move at the start-up optimum phase early.
  • the fluid control valve mechanism V discharges the operating oil from the retarded angle chamber 11 and supplies the operating oil to advanced angle chamber 12 by the control of the ECU, the inner rotor 2 with respect to the outer rotor 1 is moved in the direction of the start-up optimum phase.
  • the rotational phase of the most retarded angle phase in which the inner rotor 2 is disposed at the most retarded angle side, is referred to as the most retarded angle phase.
  • the time is needed until the relative rotational phase reaches the start-up optimum phase, so that the start-up of the engine is not smoothly performed.
  • the operating oil is cold at the time of stopping the engine in cold climates, the viscosity of the operating oil is high, and thus the distribution of the operating oil to each of the retarded angle chamber 11 and the advanced angle chamber 12 is not smoothly performed. For this reason, the start-up of the engine is not smoothly performed.
  • the spiral springs S1 and S2 are formed in a spiral shape from a strap of spring material, the thick (dimension of the rotational shaft in the direction of the core X) can be thinned as compared with one including a coil portion such as a torsion spring.
  • a coil portion such as a torsion spring.
  • each of the spiral springs S1 and S2 has a spiral spring body 30 in a spiral shape.
  • An end portion thereof in an inner diameter side is provided with an inner engaging portion 31 which is formed by bending the end portion in a radially inward direction and is engaged to the inner rotor 2.
  • An end portion thereof in an outer diameter side is provided with an outer engaging portion 32 which is formed by bending the end portion in a radially outward direction and is fixed to the outer rotor 1.
  • the outer circumference of an axial portion 10 of the inner rotor 2 is provided on one portion thereof with an engaging concave portion 10G which may be engaged to the inner engaging portion 31, so as to correspond to the shape of the spiral springs S1 and S2.
  • the inner surface of the front plate 6 connected to the outer rotor 1 is provided on one portion thereof with an engaging concave portion 6T which may be engaged to the outer engaging portion 32.
  • the inner engaging portion 31 is turned by predetermined turns against the biasing force of the spiral springs S1 and S2 which tend to be returned in a straight direction, in other words, in a direction of the spring body 30 which is curled in an inner diameter direction around the axis X, the inner engaging portion 31 is engaged and fixed to the engaging concave portion 10G.
  • the rotation operating direction of the inner engaging portion 31 at the time of performing the setting corresponds to a counterclockwise direction in the first spring S1, and corresponds to a clockwise direction in the second spiral spring S2, in Fig. 2 .
  • both ends of the spiral springs S1 and S2 are reliably fixed to each of the outer rotor 1 and the inner rotor 2 so as to prevent the relative movement therebetween, thereby achieving the configuration in which the inner engaging portion 31 of the first spiral spring S1 biases the inner rotor 2 toward the advanced angle side (clockwise direction in Fig. 2 ) and the inner engaging portion 31 of the second spiral spring S2 biases the inner rotor 2 toward the retarded angle side (counterclockwise direction in Fig. 2 ).
  • only one of the two spiral springs S1 and S2 may be disposed in the concave portion 6a formed in the front plate 6, and the other may be disposed in the concave portion formed in the rear plate 7. In this instance, the disc spacer 15 is not required.
  • the relative rotational phase is displaced to the intermediate control phase slightly closer to the retarded angle phase side rather than the start-up optimum phase.
  • the intermediate control phase is a phase suitable for improvement of the emission or torque-up at cold temperatures, and this phase is generally maintained during warm air driving.
  • Fig. 4 and Figs. 5A and 5B show the state of the most retarded angle phase exceeding the intermediate control phase.
  • the second embodiment includes two spiral springs S1 and S2 to bias a biasing force in a mutually reverse direction, as the maintenance mechanism M for maintaining the relative rotational phase of the outer rotor 1 and the inner rotor 2 at the start-up optimum phase suitable for the start-up of the engine, similar to the first embodiment.
  • the first feature of the configuration according to the second embodiment is that the width of the engaging concave portion 10G of the inner rotor 2 in a circumferential direction is sufficiently larger than the thickness of the inner engaging portion 31 of the spiral springs S1 and S2, as shown in Figs. 9A to 12 .
  • the respective inner engaging portions 31 engaged to the engaging concave portion 10G are movable along the circumferential direction in the engaging concave portion 10G.
  • the second feature of the configuration according to the second embodiment is that the front plate 6 is provided with first restriction piece 33A in a standing manner which can abut against the inner engaging portion 31 of the first spiral spring S1, and the front plate 6 is provided with second restriction piece 33B in a standing manner which can abut against the inner engaging portion 31 of the second spiral spring S2.
  • the first restriction piece 33A restricts the displacement of the inner engaging portion 31 of the first spiral spring S1 in the direction of the advanced angle region B
  • the second restriction piece 33B restricts the displacement of the inner engaging portion 31 of the second spiral spring S2 in the direction of the retarded angle region A.
  • the first spiral spring S1 operates to bias the rotational phase of the inner rotor 2 with respect to the outer rotor 1 in the direction of the start-up optimum phase in the retarded angle region A from the most retarded angle phase to the first predetermined phase (corresponding to the start-up optimum phase) defined by the first restriction piece 33A.
  • the second spiral spring S2 operates to bias the rotational phase of the inner rotor 2 with respect to the outer rotor 1 in the direction of the start-up optimum phase in the advanced angle region B from the most advanced angle phase to the second predetermined phase (corresponding to the start-up optimum phase) defined by the second restriction piece 33B.
  • a third embodiment employs not the spiral spring, but two torsion springs S1 and S2 as a biasing member for maintaining the relative phase at the start-up optimum phase, as shown in Fig. 13 and Figs. 14A and 14B .
  • the first torsion spring S1 biasing the relative phase toward the advanced angle side is received in the concave portion 6a of the front plate 6, while the second torsion spring S2 biasing the relative phase toward the retarded angle side is received in a concave portion 7a of the rear plate 7.
  • Figs. 14A and 14B show the state of the respective torsion springs S1 and S2 at the start-up optimum phase.
  • the outer engaging portions 32 of the torsion springs S1 and S2 are engaged to the engaging concave portion 6T in a relatively non-movable manner in the inner surface of the front plate 6 which is connected to the outer rotor 1.
  • the inner engaging portions 31 of the torsion springs S1 and S2 are engaged to the engaging concave portion 10G with a wide width in a relatively movable manner, the width of the engaging concave portion being cut sufficiently rather than an outer diameter of the inner engaging portion 31.
  • the biasing operation position to the inner rotor 2 by the inner engaging portion 31 of the respective torsion springs S1 and S2 is limited to each position of the first and second restriction pieces 33A and 33B, if the distribution of the operating oil to each of the retarded angle chamber 11 and the advanced angle chamber 12 is stopped, in a case where the balance of the biasing force of the respective torsion springs S1 and S2 is lost from an original state due to long-term use, the rotational phase is not deviated by the collapse in the balance, and can be maintained at the start-up optimum phase with high accuracy.
  • the position of the first restriction piece 33A corresponds to the first predetermined phase
  • the position of the second restriction piece 33B corresponds to the second predetermined phase.
  • a fourth embodiment employs single torsion spring S having an inner engaging portion 31 which is engaged to the engaging concave portion 10G of the inner rotor 2 and an outer engaging portion 32 which is engaged to the engaging concave portion 6T of the outer rotor 1, as a biasing member for maintaining the relative phase at the start-up optimum phase, as shown in Fig. 15 .
  • the relative phase is displaced at the start-up optimum phase by the biasing force of the torsion spring S, and is maintained at this phase.
  • the displacement operation from the start-up optimum phase to the retarded angle side by the operating oil is performed, with being accompanied by deformation in which the inner engaging portion 31 of the torsion spring S relatively rotates in a counterclockwise direction with respect to the outer engaging portion 32, when seen at plane view in Fig. 15 , that is, the diameter of the torsion spring S is decreased.
  • a fifth embodiment employs the engaging concave portion 10 of the inner rotor 2 extended long in a circumferential direction and single torsion spring S fitted to the cylindrical operating oil supply/discharge portion Vb, as a biasing member for maintaining the relative phase at the start-up optimum phase.
  • Both ends 31a and 31b of the torsion spring S are extended outwardly in a radial direction, and the torsion spring S is fitted into the engaging concave portion 10 in a state in which both ends 31a and 31b are close to each other against the biasing force of the torsion spring S.
  • the front plate 6 is provided with a pair of restriction pieces 34A and 34B in a standing manner which abut against or are adjacent to the outside of the torsion spring S in the vicinity of both ends 31a and 31b.
  • both ends 31a and 31b of the torsion spring S are simultaneously pushed by both ends 10a and 10b of the engaging concave portion 10 and the pair of the restriction pieces 34A and 34B, thereby biasing the relative phase at the start-up optimum phase.
  • the displacement operation is performed by pushing the other end portion 31a of the torsion spring S in a counterclockwise direction with one end surface 10a of the engaging concave portion 10G of the inner rotor 2, with one end portion 31b of the torsion spring S being pushed by the restriction piece 34B.
  • the embodiments disclosed here can be used in the whole valve opening/closing timing control devices capable of setting the opening and closing timing of any one of an intake valve and an exhaust valve of an engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (9)

  1. Dispositif de commande variable d'ouverture/-
    fermeture de soupapes, comprenant :
    un élément rotatif côté menant (1) qui peut tourner en synchronisme avec un vilebrequin d'un moteur à combustion interne ;
    un élément rotatif côté mené (2) aménagé coaxialement avec l'élément rotatif côté menant et qui est susceptible de tourner en synchronisme avec un arbre à cames qui ouvre et ferme l'une quelconque des soupapes d'admission et d'échappement du moteur à combustion interne ;
    une chambre d'angle retardé (11) et une chambre d'angle avancé (12) formées par l'élément rotatif côté menant et l'élément rotatif côté mené, dans lequel la chambre d'angle retardé déplace une phase relative de l'élément rotatif côté mené vers l'élément rotatif côté menant dans une direction d'angle retardé lorsque son volume est augmenté et la chambre d'angle avancé déplace la phase relative dans une direction d'angle avancé lorsque son volume est augmenté ; et
    un mécanisme de maintien (M) maintenant la phase relative à une phase prédéterminée entre une phase d'angle le plus avancé et une phase d'angle le plus retardé, caractérisé en ce que :
    le mécanisme de maintien (M) comprend un premier élément de sollicitation (S1) et un second élément de sollicitation (S2),
    le premier élément de sollicitation (S1) presse la phase relative de l'angle de phase le plus retardé à la phase prédéterminée et ne presse pas la phase relative de la phase prédéterminée à la phase d'angle le plus avancé, et
    le second élément de polarisation (S2) presse la phase relative de la phase d'angle le plus avancé à la phase prédéterminée et ne presse pas la phase relative de la phase prédéterminée à la phase d'angle le plus retardé.
  2. Dispositif de commande variable d'ouverture/- fermeture de soupapes selon la revendication 1, dans lequel une plaque avant (6) et une plaque arrière (7) sont fixées à l'élément rotatif côté menant (1), et
    le premier élément de sollicitation (S1) et le second élément de sollicitation (S2) sont tous deux disposés entre l'élément rotatif côté mené (2) et la plaque avant ou entre l'élément rotatif côté mené et la plaque arrière.
  3. Dispositif de commande variable d'ouverture/- fermeture de soupapes selon la revendication 1, dans lequel une plaque avant (6) et une plaque arrière (7) sont fixées à l'élément de rotation côté menant,
    le premier élément de sollicitation (S1) est disposé entre l'élément de rotation côté mené (2) et la plaque avant ou entre l'élément rotatif côté mené et la plaque arrière, et
    le second élément de sollicitation (S2) est disposé entre l'élément rotatif côté mené et la plaque avant ou entre l'élément rotatif côté mené et la plaque arrière.
  4. Dispositif de commande variable d'ouverture/- fermeture de soupapes selon la revendication 1, dans lequel :
    la chambre d'angle retardé (11) et la chambre d'angle avancé (12) sont comprises dans un mécanisme convertisseur de phase déplaçant une phase relative entre l'élément rotatif côté menant et l'élément rotatif côté mené jusqu'à un côté de phase d'angle avancé ou un côté de phase d'angle retardé en distribuant un fluide opératoire à chacun des deux types de chambres, dont le volume est modifié de manière complémentaire par une cloison mobile ; et
    dans lequel :
    l'élément de sollicitation (S1, S2) presse la phase relative vers une phase prédéterminée convenant au démarrage du moteur à combustion interne, sauf pour une phase d'angle le plus avancé et une phase d'angle le plus retardé.
  5. Dispositif de commande variable d'ouverture/- fermeture de soupapes selon la revendication 4, dans lequel l'élément de sollicitation comprend un premier élément de sollicitation (S1) pour presser la phase relative dans un certain sens de la phase d'angle avancé et un second élément de sollicitation (S2) pour presser la phase relative dans un sens de la phase d'angle retardé, et
    le dispositif de commande variable d'ouverture/- fermeture de soupapes comprend en outre une première portion de restriction (33A) pour définir la force de sollicitation du premier élément de sollicitation entre la phase prédéterminée et la phase d'angle le plus retardé, et une seconde portion de restriction (33B) pour définir la force de sollicitation du second élément de sollicitation entre la phase prédéterminée et l'angle de phase le plus avancée.
  6. Dispositif de commande variable d'ouverture/- fermeture de soupapes selon la revendication 4 ou 5, dans lequel l'élément de sollicitation (S1, S2) présente la force de sollicitation à l'encontre d'une force de déplacement agissant sur l'élément rotatif côté mené (2) sur la base de la fluctuation du couple de torsion de l'arbre à cames.
  7. Dispositif de commande variable d'ouverture/- fermeture de soupapes selon l'une quelconque des revendications 4 à 6, dans lequel l'élément de sollicitation est un ressort (S1, S2) placé entre l'élément rotatif côté menant (1) et l'élément rotatif côté mené (2).
  8. Dispositif de commande variable d'ouverture/- fermeture de soupapes selon l'une quelconque des revendications 4 à 7, dans lequel une plaque avant et une plaque arrière (7) sont fixées à l'élément rotatif côté menant (1), et
    le premier élément de sollicitation (S1) et le second élément de sollicitation (S2) sont tous deux disposés entre l'élément rotatif côté mené (2) et la plaque avant ou entre l'élément rotatif côté mené et la plaque arrière.
  9. Dispositif de commande variable d'ouverture/- fermeture de soupapes selon l'une quelconque des revendications 4 à 8, dans lequel une plaque avant (6) et une plaque arrière (7) sont fixées à l'élément rotatif côté menant (1),
    le premier élément de sollicitation (S1) est disposé entre l'élément rotatif côté mené (2) et la plaque avant ou entre l'élément rotatif côté mené et la plaque arrière, et
    le second élément de sollicitation (S2) est disposé entre l'élément rotatif côté mené et la plaque avant ou entre l'élément rotatif côté mené et la plaque arrière.
EP10002953A 2009-09-25 2010-03-19 Dispositif de commande variable d'ouverture/fermeture de soupape Not-in-force EP2302177B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009220652A JP5382440B2 (ja) 2009-09-25 2009-09-25 弁開閉時期制御装置

Publications (2)

Publication Number Publication Date
EP2302177A1 EP2302177A1 (fr) 2011-03-30
EP2302177B1 true EP2302177B1 (fr) 2012-10-31

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EP10002953A Not-in-force EP2302177B1 (fr) 2009-09-25 2010-03-19 Dispositif de commande variable d'ouverture/fermeture de soupape

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US (1) US20110073055A1 (fr)
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JP5382086B2 (ja) * 2011-10-25 2014-01-08 株式会社デンソー 液圧式バルブタイミング調整装置
DE102012200683B4 (de) * 2012-01-18 2017-01-26 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
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JP5382440B2 (ja) 2014-01-08
US20110073055A1 (en) 2011-03-31
EP2302177A1 (fr) 2011-03-30
CN102032009A (zh) 2011-04-27

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