WO2020059017A1 - Dispositif de réglage de diagramme de distribution - Google Patents

Dispositif de réglage de diagramme de distribution Download PDF

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Publication number
WO2020059017A1
WO2020059017A1 PCT/JP2018/034443 JP2018034443W WO2020059017A1 WO 2020059017 A1 WO2020059017 A1 WO 2020059017A1 JP 2018034443 W JP2018034443 W JP 2018034443W WO 2020059017 A1 WO2020059017 A1 WO 2020059017A1
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WO
WIPO (PCT)
Prior art keywords
holder
valve timing
rotor
vane
hydraulic chamber
Prior art date
Application number
PCT/JP2018/034443
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English (en)
Japanese (ja)
Inventor
卓大 松本
横山　雅之
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/034443 priority Critical patent/WO2020059017A1/fr
Priority to JP2020541469A priority patent/JP6786021B2/ja
Publication of WO2020059017A1 publication Critical patent/WO2020059017A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/356—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 making the angular relationship oscillate, e.g. non-homokinetic drive

Definitions

  • the present invention relates to a valve timing adjusting device for adjusting the opening / closing timing of a valve.
  • valve timing adjustment device that adjusts the opening / closing timing of at least one of an intake valve and an exhaust valve of an engine is known.
  • the inner rotor is locked with respect to the outer rotor by fitting an extending / retracting member supported so as to be able to extend and retract with respect to the outer rotor into a recess formed in the inner rotor.
  • the internal rotor is locked in one of three phases: an intermediate lock phase, a retard lock phase, and a most retard lock phase.
  • Patent Document 1 When the internal rotor is locked by the mechanism described in Patent Document 1, the lockable phase is limited according to the numbers of the retractable members and the concave portions. As described above, in Patent Document 1, there are three lockable phases: an intermediate lock phase, a retard lock phase, and a most retard lock phase. As described above, conventionally, it has not been possible to lock the rotor at an arbitrary phase.
  • the present invention has been made to solve the above-described problem, and has as its object to obtain a valve timing adjusting device capable of locking a rotor at an arbitrary phase.
  • a valve timing adjusting device includes a case in which a plurality of hydraulic chambers are formed, a rotor provided in the case, a camshaft being fixed and rotating relative to the case, and a rotor formed in the rotor.
  • a holder having two pins, a communication hole fixed between the two pins at the distal end surface, and communicating with the advance hydraulic chamber and the retard hydraulic chamber, and a communication groove communicating with the communication hole and the drain oil path; Installed in the communication hole of the holder Te are those comprising a coil spring for urging the two pins in the direction of the direction and the retarding hydraulic chamber of the advancing hydraulic chamber.
  • the rotor can be locked at an arbitrary phase.
  • FIG. 1A is a plan view of the valve timing adjusting device according to Embodiment 1.
  • FIG. 1B is an enlarged view of a portion A of FIG. 1A.
  • FIG. 2A is a plan view of the holder according to Embodiment 1.
  • FIG. 2B is a cross-sectional view based on the cutting line AA shown in FIG. 2A.
  • FIG. 3A is a diagram illustrating a state in which the lock is released and the rotor is rotated in the advance direction.
  • FIG. 3B is a diagram illustrating a state where the lock is released and the rotor is rotated in the retard direction.
  • 4A and 4B are diagrams for explaining the effect of the valve timing adjusting device according to the first embodiment.
  • FIG. 1B is an enlarged view of a portion A of FIG. 1A.
  • FIG. 2A is a plan view of the holder according to Embodiment 1.
  • FIG. FIG. 2B is a cross-sectional view based on the
  • FIG. 5 is a diagram showing a modified example of the holder according to the first embodiment.
  • FIG. 5 is a diagram showing a modified example of the holder according to the first embodiment.
  • FIG. 7A is a diagram showing a modified example of the holder according to the first embodiment.
  • FIG. 7B is an enlarged view of a portion B of FIG. 7A.
  • FIG. 8A is a top view illustrating an example of the coil spring according to Embodiment 1.
  • FIG. FIG. 8B is a view of the coil spring as viewed from arrow C.
  • FIG. 9A is a cross-sectional view based on the cutting line BB shown in FIG. 9B.
  • FIG. 9B is a plan view showing a cutting line BB.
  • FIG. 9C is a cross-sectional view based on the section line CC shown in FIG. 9D.
  • FIG. 9D is a plan view showing a cutting line CC.
  • FIG. 1A is a plan view of a valve timing adjustment device 100 according to Embodiment 1.
  • the valve timing adjusting device 100 adjusts the opening / closing timing of at least one of an intake valve and an exhaust valve of an engine (not shown).
  • the valve timing adjusting device 100 includes a case 1, a rotor 2, vanes 3A to 3C, a coil spring 4, and pins 5A and 5B.
  • the case 1 has a plurality of shoes 1A to 1C protruding toward the center.
  • a plurality of hydraulic chambers 1E to 1G are formed inside the case 1 by the plurality of shoes 1A to 1C.
  • FIG. 1A shows a case where the case 1 has three shoes 1A to 1C and three hydraulic chambers 1E to 1G.
  • a sprocket 10 is formed on an outer peripheral surface of the case 1 to receive a driving force from a crankshaft of an engine (not shown).
  • the rotor 2 is provided in the case 1.
  • the rotor 2 has a plurality of vanes 3A to 3C protruding toward the outer periphery.
  • FIG. 1A shows a case where three vanes 3A to 3C are formed.
  • the vanes 3A to 3C correspond one-to-one to the hydraulic chambers 1E to 1G, and partition each of the hydraulic chambers 1E to 1G into an advance hydraulic chamber and a retard hydraulic chamber. That is, the hydraulic chamber 1E is partitioned into the advance hydraulic chamber 11E and the retard hydraulic chamber 12E. Similarly, the hydraulic chambers 1F, 1G are partitioned into advance hydraulic chambers 11F, 11G and retard hydraulic chambers 12F, 12G.
  • the clockwise direction is the advance direction
  • the counterclockwise direction is the retard direction.
  • a camshaft (not shown) is fixed to the rotor 2, and the camshaft and the rotor 2 rotate integrally.
  • An axis X in FIG. 1A indicates a rotor rotation axis that is a rotation axis when the rotor 2 rotates integrally with the camshaft.
  • Case 1 is also arranged to rotate about axis X as a rotation axis. The rotor 2 rotates integrally with the camshaft, while rotating relative to the case 1 by receiving hydraulic pressure.
  • the camshaft fixed to the rotor 2 is a camshaft on the intake side or the exhaust side of the engine. Further, the number of hydraulic chambers formed inside the case 1 and the number of vanes formed in the rotor 2 are not limited to those shown.
  • FIG. 1B is an enlarged view of a portion A of FIG. 1A.
  • the vane 3A which is the first vane, has a front end surface 3a facing the inner peripheral surface 1a of the case 1 with a gap.
  • the vanes 3B and 3C other than the vane 3A as shown in FIG. 1A, there is no gap as much as between the front end surface 3a of the vane 3A and the inner peripheral surface 1a.
  • a gap that does not hinder relative rotation with respect to the inner peripheral surface 1 is maintained with respect to the inner peripheral surface 1a.
  • the vane 3A which is the first vane, has a concave holder insertion portion 3b formed on the flat distal end surface 3a and a groove-shaped drain oil passage 3c extending radially inward from the holder insertion portion 3b of the distal end surface 3a.
  • the drain oil passage 3c is connected to the outside of the valve timing adjusting device 100, and when the engine oil is supplied into the advance hydraulic chamber 11E or the retard hydraulic chamber 12E and the pin 5A or the pin 5B is released, It becomes a passage for the engine oil or air at the back of the pin 5A or 5B to escape to the outside.
  • a coil spring 4 is provided between the distal end surface 3a and the inner peripheral surface 1a.
  • the coil spring 4 is held by a holder 6 made of resin or the like.
  • the holder 6 is fixed to the distal end surface 3a by inserting one end of the holder 6 into a concave holder insertion portion 3b formed on the distal end surface 3a.
  • FIG. 2A is a plan view of the holder 6 according to the first embodiment.
  • FIG. 2B is a cross-sectional view based on the cutting line AA shown in FIG. 2A.
  • the holder 6 has a communication hole 6a that penetrates the advance hydraulic chamber 11E and the retard hydraulic chamber 12E.
  • the coil spring 4 is installed in the communication hole 6a.
  • the holder 6 is formed with a communication groove 6b for connecting the communication hole 6a to the drain oil passage 3c of the vane 3A.
  • the columnar pin 5A is provided on the leading end face 3a on the advance hydraulic chamber 11E side of the coil spring 4.
  • the columnar pin 5B is provided on the distal end face 3a on the side of the retard hydraulic chamber 12E of the coil spring 4.
  • the inner peripheral surface 1a is a curved surface having a circular cross section.
  • the distal end surface 3a has a flat surface facing the inner peripheral surface 1a.
  • the pins 5A and 5B are provided in a space between the inner peripheral surface 1a and the distal end surface 3a.
  • the space in which the pin 5A is provided is such that the radial distance between the inner peripheral surface 1a and the distal end surface 3a is smaller than the diameter of the pin 5A as it approaches the right side in FIG. It is a large space.
  • the distance in the radial direction between the inner peripheral surface 1a and the distal end surface 3a is specifically illustrated as distances d1 and d2 in FIG. 1B.
  • the space in which the pin 5B is provided is such that the radial distance between the inner peripheral surface 1a and the distal end surface 3a is smaller than the diameter of the pin 5B as the distance to the left in FIG. Therefore, the space becomes larger than the diameter.
  • the pin 5A is urged by the coil spring 4 toward the left in FIG. 1B, that is, in the direction of the advance hydraulic chamber 11E.
  • the pin 5A is urged toward the side where the radial distance between the inner peripheral surface 1a and the distal end surface 3a is smaller than the diameter of the pin 5A, and becomes pinched between the case 1 and the vane 3A.
  • the pin 5B is urged by the coil spring 4 to the right in FIG. 1B, that is, in the direction of the retard hydraulic chamber 12E.
  • the pin 5B is urged toward the side where the radial distance between the inner peripheral surface 1a and the distal end surface 3a is smaller than the diameter of the pin 5B, and is in a state of being sandwiched between the case 1 and the vane 3A. .
  • the pin 5 ⁇ / b> A acts as a stopper to prevent the rotor 2 from rotating in the advance direction with respect to the case 1.
  • the pin 5B acts as a stopper, and the rotor 2 rotates in the retard direction with respect to the case 1. prevent.
  • the rotor 2 is locked to the case 1 by the action of the pin 5A against the external force in the advance direction, and the rotor 2 is locked to the case 1 by the action of the pin 5B against the external force in the retard direction. Locked.
  • FIG. 3A shows a state where the lock is released and the rotor 2 is rotated in the advance direction.
  • the pin 5A is pushed out in the advance direction while compressing the coil spring 4 by the oil pressure P1 of the engine oil. That is, the pin 5A is pushed out to the side where the radial distance between the inner peripheral surface 1a and the distal end surface 3a is larger than the diameter of the pin 5A.
  • the pin 5A is released from the state sandwiched between the case 1 and the vane 3A, and does not function as a stopper.
  • the pin 5B slides in the retard direction.
  • the pin 5B also comes out of the state sandwiched between the case 1 and the vane 3A, and does not function as a stopper. Therefore, the rotor 2 can rotate in the advance angle direction with respect to the case 1.
  • FIG. 3B shows a state where the lock is released and the rotor 2 is rotated in the retard direction.
  • the pin 5B is pushed out in the retard direction while compressing the coil spring 4 by the oil pressure P2 of the engine oil. That is, the pin 5B is pushed out to the side where the radial distance between the inner peripheral surface 1a and the distal end surface 3a is larger than the diameter of the pin 5B.
  • the pin 5B is released from the state sandwiched between the case 1 and the vane 3A, and does not function as a stopper.
  • the engine oil between the pin 5A and the holder 6 flows from the communication hole 6a and the communication groove 6b to the drain oil passage 3c. Flow in. Therefore, the pin 5A receives the oil pressure P1 and is smoothly pushed out in the advance direction. Similarly, the engine oil between the pin 5B and the holder 6 also flows into the drain oil passage 3c from the communication hole 6a and the communication groove 6b, so that the pin 5B receives the oil pressure P2 and is smoothly pushed out in the retard direction. It is.
  • valve timing adjusting device 100 After the supplied engine oil is discharged to the outside of the valve timing adjusting device 100 after the rotor 2 rotates relative to the case 1 as shown in FIGS. 3A and 3B, the pins 5A and 5B It is urged to be sandwiched between the case 1 and the vane 3A as shown in FIG. 1B. Therefore, the rotor 2 is locked at the phase after the rotation. As described above, the valve timing adjusting device 100 can lock the rotor 2 at an arbitrary phase. Since the rotor 2 can be locked at an arbitrary phase, locking at an ideal phase for the engine becomes possible.
  • FIG. 4A and 4B are diagrams for explaining another effect of the valve timing adjustment device 100.
  • FIG. 4A is applied to the rotor 2 from the camshaft.
  • the cam reaction force F1 and the cam reaction force F2 are forces in directions opposite to each other, and are forces alternately applied to the rotor 2 such as first the cam reaction force F1, then the cam reaction force F2, and then the cam reaction force F1. .
  • the cam reaction force F2 acts on the rotor 2 as a force to return the rotation of the rotor 2.
  • FIGS. 5, 6, and 7A are views showing a modified example of the holder 6 in the first embodiment.
  • two surfaces of the holder 6 where the two pins 5A and 5B are in contact have a V-shaped concave surface portion 6c.
  • the two surfaces of the holder 6 where the two pins 5A and 5B are in contact may have a curved concave portion 6d having a smaller radius of curvature than the pins 5A and 5B.
  • the peripheral surface of the pin 5A comes into contact with the concave portions 6c and 6d of the holder 6 at the time of unlocking, thereby suppressing the flow of engine oil into the communication hole 6a.
  • the effect of reducing the consumption of engine oil can also be obtained by suppressing the inflow of engine oil into the communication hole 6a by contacting the peripheral surfaces of the pins 5B with the concave portions 6c and 6d of the holder 6.
  • FIG. 7B is an enlarged view of a portion B in FIG. 7A. 7A and 7B, the holder 6 has two ribs 6e on the vane 3A side.
  • One rib 6e has a shape protruding from the surface of the holder 6 on the vane 3A side to the pin 5A side from the surface in contact with the pin 5A.
  • the other rib 6e has a shape protruding from the surface in contact with the pin 5B toward the pin 5B on the vane 3A side of the holder 6.
  • Two rib insertion portions 3d which are spaces into which the two ribs 6e are inserted, are formed in the holder insertion portion 3b.
  • the engine oil supplied to the advance hydraulic chamber 11E flows into the drain oil passage 3c through the flow path R1 shown in FIG. 7B, and is discharged out of the valve timing adjustment device 100. Will be lost.
  • the rib 6e receives the oil pressure P3 of the engine oil flowing into the gap between the holder insertion portion 3b and the holder 6, so that the bottom surface of the holder 6 becomes the bottom surface of the holder insertion portion 3b. 3e, the flow path R1 is connected to the drain oil path 3c. Therefore, it is possible to prevent the engine oil in the advance hydraulic chamber 11 from flowing into the drain oil passage 3c. Therefore, the effect of reducing the consumption of engine oil is obtained. Further, the presence of the rib 6e can prevent the engine oil supplied to the retard hydraulic chamber 12E from flowing into the drain oil passage 3c.
  • FIG. 8A is a top view showing an example of the coil spring 4 according to the first embodiment.
  • FIG. 8A not the end faces of the pins 5A and 5B but the peripheral faces are visible.
  • FIG. 8B is a view of the coil spring 4 as viewed from an arrow C.
  • the coil spring 4 may have a coil wound in a circular shape or an elliptical shape as shown in FIGS. 8A and 8B.
  • the coil spring 4 in which the coil is wound in an elliptical shape can uniformly apply the urging force F11 to a wide area of the pins 5A and 5B, so that the pins 5A and 5B can be prevented from tilting.
  • the pins 5A and 5B do not tilt, so that only one end of the pins 5A and 5B is sandwiched between the case 1 and the vane 3A. Can be prevented. Therefore, the entire region from one end to the other end of the pins 5A and 5B can be shifted to a state sandwiched between the case 1 and the vane 3A, that is, a stable locked state, and an effect of improving the locking performance can be obtained.
  • FIG. 9A is a cross-sectional view based on the cutting line BB shown in FIG. 9B.
  • the thickness of the holder 6 and the thickness of the vane 3A are both the thickness t1.
  • FIG. 9C is a cross-sectional view based on the section line CC shown in FIG. 9D.
  • the thickness t2 of the holder 6 is smaller than the thickness t1 of the vane 3A.
  • the engine oil supplied to the advance hydraulic chamber 11E passes through the flow passage R2 shown in FIGS. 9C and 9D and the drain oil passage 3c. Will flow into.
  • the thickness of the holder 6 and the thickness of the vane 3A become the same thickness t1, the occurrence of the flow path R2 can be prevented, and the consumption of engine oil Can be obtained.
  • “same” here includes not only a case where the thickness is strictly the same, but also a case where it can be said that the thickness is substantially the same, such as a case where the thickness is shifted by a tolerance.
  • FIG. 9A shows a case where the thickness of the holder 6, the thickness of the vane 3A, and the length of the pins 5A and 5B are all t1.
  • the length t1 of the pins 5A and 5B is the axial length of the pins 5A and 5B.
  • the valve timing adjusting device 100 includes the case 1, the rotor 2, the vanes 3A, the pins 5A and 5B, the holder 6, and the coil spring 4.
  • the vane 3A is one of a plurality of vanes 3A to 3C formed on the rotor 2, and the flat tip surface 3a faces the inner peripheral surface 1a of the case 1 with a gap and has a diameter from the tip surface 3a. It has a drain oil passage 3c extending inward in the direction.
  • the pins 5A and 5B are cylinders provided in the gap between the distal end surface 3a and the inner peripheral surface 1a and having a diameter larger than the distance d1 between both ends of the distal end surface 3a and the inner peripheral surface 1a.
  • the holder 6 is fixed between the pin 5A and the pin 5B on the distal end surface 3a, and has a communication hole 6a for communicating the advance hydraulic chamber 11E and the retard hydraulic chamber 12E, and a communication hole 6a and the drain oil passage 3c. It has a communication groove 6b for communication.
  • the coil spring 4 is installed in the communication hole 6a of the holder 6 and urges the pins 5A and 5B in the direction of the advance hydraulic chamber 11E and in the direction of the retard hydraulic chamber 12E. With this configuration, the valve timing adjustment device 100 can lock the rotor 2 at an arbitrary phase. Further, since the communication hole 6a of the holder 6 stabilizes the posture of the coil spring 4, the coil spring 4 can urge the pins 5A and 5B with a stable posture and load, which leads to an improvement in the accuracy of the lock function.
  • the communication hole 6a and the communication groove 6b can be manufactured by molding. According to this configuration, since no machining is required to manufacture the holder 6, the cost can be reduced.
  • the two surfaces of the holder 6 with which the pins 5A and 5B are in contact may have a shape having a concave portion 6c or a concave portion 6d.
  • this shape at the time of unlocking, the peripheral surfaces of the pins 5A and 5B abut against the concave portion 6c or the concave portion 6d to suppress the flow of engine oil into the communication hole 6a. Therefore, the concave portion 6c or the concave portion 6d can prevent the engine oil from flowing out to the drain oil passage 3c through the communication hole 6a, and the effect of reducing the consumption of the engine oil can be obtained.
  • the holder 6 has a rib 6e protruding outward on the vane 3A side.
  • the vane 3A has a holder insertion portion 3b into which the rib 6e and the vane 3A side of the holder 6 are inserted.
  • the coil spring 4 may have a coil wound in an elliptical shape.
  • the elliptical coil spring 4 can prevent the pins 5A and 5B from being tilted, so that a stable locked state can be realized.
  • the holder 6 and the vane 3A have the same length in the axis X direction. Thus, it is possible to prevent the engine oil from flowing into the drain oil passage 3c, and to obtain an effect of reducing the consumption of the engine oil.
  • the axial length between the pins 5A and 5B is the same as the axial length of the vane 3A.
  • the length of the holder 6 in the direction of the axis X, the length of the vane 3A in the direction of the axis X, and the length of the pins 5A and 5B in the axial direction are all the same, the consumption of engine oil is significantly reduced.
  • one of the vanes 3A to 3C is provided with one lock mechanism including the coil spring 4, the pins 5A and 5B, and the holder 6 for the vane 3A.
  • a lock mechanism may be provided for each of two or more of the vanes 3A to 3C.
  • valve timing adjusting device can lock the rotor at an arbitrary phase, and thus is suitable for being mounted on a vehicle requiring high performance.
  • 1 Case 1A 1C Shoe, 1E ⁇ 11G Hydraulic chamber, 1a Inner peripheral surface, 2 Rotor, 3A ⁇ 3C Vane, 3a tip surface, 3b Holder insertion part, 3c Drain oil passage, 3d Rib insertion part (holder insertion part) 3e bottom, 4 coil spring, 5A, 5B pin, 6 holder, 6a communication hole, 6b communication groove, 6c, 6d concave surface, 6e rib, 10 sprocket, 11E-11G advance hydraulic chamber, 12E-12G retard hydraulic Chamber, 20 ° rotor, 100 ° valve timing adjustment device.

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

Abstract

L'invention fait intervenir des broches (5A, 5B) qui sont des colonnes positionnées dans l'écartement entre une surface circonférentielle intérieure (1a) et une surface (3a) d'extrémité de bout d'une palette (3A), et présentent un diamètre plus grand que la distance entre la surface circonférentielle intérieure (1a) et chacune des deux extrémités de la surface (3a) d'extrémité de bout. Un support (6) est fixé entre la broche (5A) et la broche (5B) sur la surface (3a) d'extrémité de bout, et présente un trou (6a) de raccordement qui relie une chambre hydraulique (11E) d'angle d'avance et une chambre hydraulique (12E) d'angle de retard entre elles. Un ressort hélicoïdal (4) est placé dans le trou (6a) de raccordement du support (6), et sollicite les broches (5A, 5B) dans la direction de la chambre hydraulique (11E) d'angle d'avance et la direction de la chambre hydraulique (12E) d'angle de retard.
PCT/JP2018/034443 2018-09-18 2018-09-18 Dispositif de réglage de diagramme de distribution WO2020059017A1 (fr)

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Application Number Priority Date Filing Date Title
PCT/JP2018/034443 WO2020059017A1 (fr) 2018-09-18 2018-09-18 Dispositif de réglage de diagramme de distribution
JP2020541469A JP6786021B2 (ja) 2018-09-18 2018-09-18 バルブタイミング調整装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/034443 WO2020059017A1 (fr) 2018-09-18 2018-09-18 Dispositif de réglage de diagramme de distribution

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000068547A1 (fr) * 1999-05-11 2000-11-16 INA Wälzlager Schaeffler oHG Dispositif de reglage de l'angle de rotation d'un arbre a cames par rapport au vilebrequin d'un moteur a combustion interne a piston
WO2001066915A2 (fr) * 2000-03-08 2001-09-13 Stiwa-Fertigungstechnik Sticht Gesellschaft M.B.H. Dispositif de reglage et de fixation pour un arbre a cames
JP2002227619A (ja) * 2001-02-01 2002-08-14 Nippon Soken Inc バルブタイミング調整装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000068547A1 (fr) * 1999-05-11 2000-11-16 INA Wälzlager Schaeffler oHG Dispositif de reglage de l'angle de rotation d'un arbre a cames par rapport au vilebrequin d'un moteur a combustion interne a piston
WO2001066915A2 (fr) * 2000-03-08 2001-09-13 Stiwa-Fertigungstechnik Sticht Gesellschaft M.B.H. Dispositif de reglage et de fixation pour un arbre a cames
JP2002227619A (ja) * 2001-02-01 2002-08-14 Nippon Soken Inc バルブタイミング調整装置

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JP6786021B2 (ja) 2020-11-18

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