JP2010014097A - Valve timing adjusting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing adjusting device easily securing retentivity of the valve timing. <P>SOLUTION: This valve timing adjusting device includes a peripheral surface part 20 of a driven rotary body 6, a first wedge surface part 21 for reducing an interval in the radial direction with the peripheral surface part 20 in the driven rotary body 6 to the ignition timing delay side, a second wedge surface part 22 for reducing an interval in the radial direction with the peripheral surface part 20 in the driven rotary body to the ignition timing advance side, a first rolling element 23 interposed between the peripheral surface part 20 and the first wedge surface part 21, a second rolling element 24 interposed between the peripheral surface part 20 and the second wedge surface part 22 on the ignition timing advance side more than the first rolling element 23, an elastic member 25 for energizing the first rolling element 23 to the ignition timing delay side and energizing the second rolling element 24 to the ignition timing advance side, a first actuator 30 for generating pressing force for pressing the first rolling element 23 to the ignition timing advance side by the driven rotary body 6, a second actuator 31 for generating pressing force for pressing the second rolling element 24 to the ignition timing delay side by the driven rotary body 6, and a control circuit 16 for controlling generation of the pressing force by the actuators 30 and 31. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a valve timing adjusting device that adjusts the valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine.

  Conventionally, a relative phase between a driving rotating body that rotates in conjunction with a crankshaft and a driven rotating body that rotates in conjunction with a camshaft is controlled by a phase control unit to realize valve timing according to the relative phase. Such a valve timing adjusting device is known. As a kind of such valve timing adjusting device, Patent Document 1 discloses a device in which a two-way clutch type phase control unit is provided in a rotation direction common to a driving rotating body and a driven rotating body.

  Specifically, in the phase control unit of Patent Document 1, the radial interval between the inner peripheral surface extending in the rotational direction of the drive rotator and the inner peripheral surface of the driven rotator is such that the driven rotator has a radial interval. A first roller that is biased toward the retarded side by a spring is interposed between the first inclined surface that shrinks toward the retarded side. Similarly, the inner peripheral surface of the drive rotator and a second inclined surface in which the radial distance between the inner periphery and the driven rotator decreases toward the advance side of the driven rotator with respect to the drive rotator. In between, the second roller urged toward the advance side by the spring is interposed. And the first torque that presses the inner race of the first roller and the driven rotor to the advance side by the first release projection and the release arm, or the second roller and the inner race is retarded by the second release projection and the release arm. The motor generator generates a second torque that presses the motor. Here, generation of torque by the motor generator is controlled by an electronic control unit.

  In the device of Patent Document 1 including such a phase control unit, when each roller is pressed against the inner peripheral surface and each inclined surface of the drive rotator by a spring to exert a wedge action, Thus, the driven rotor is locked on both the advance side and the retard side. As a result, the driven rotator is restricted from rotating relative to the drive rotator even when a variable torque that alternately biases the follower rotator toward the advance side and the retard side with respect to the drive rotator is transmitted from the camshaft. As a result, the valve timing is maintained.

  On the other hand, when the first roller is pressed to the advance side against the bias of the spring by the first release projection receiving the first torque from the motor generator according to the control of the electronic control unit under the valve timing holding state, Since the pressing of the first roller to the first inclined surface and the inner peripheral surface is relaxed, the lock on the advance side of the driven rotor is released. At this time, the inner race of the driven rotator is also pressed toward the advance side by the release arm that receives the first torque from the motor generator, so that the follower rotator receives the variable torque on the advance side to the drive rotator. Relative rotation to the advance side. As a result, the valve timing is advanced.

On the other hand, the second roller is pressed against the retarded side against the bias of the spring by the second release projection that receives the second torque from the motor generator according to the control of the electronic control unit while the valve timing is maintained. When this is done, the pressing of the second roller against the second inclined surface and the inner peripheral surface is eased, so that the retarded side lock of the driven rotor is released. At this time, the inner race of the driven rotator is also pressed to the retarded angle side by the release arm that receives the second torque from the motor generator, so that the driven rotator receives the fluctuation torque on the retarded angle side, Relative rotation to the retard side. As a result, the valve timing is retarded.
JP 2005-307818 A

  When the valve timing is maintained in the apparatus of Patent Document 1, the motor generator is controlled by the electronic control unit so that the release levers that form the release protrusions rotate at the same speed as the drive rotator. Alternatively, the second torque is generated. At this time, in order to prevent the lock of the driven rotor from being released on both the advance side and the retard side, the number of revolutions of the release lever and the drive rotor is adjusted with each release protrusion being separated from the roller to be pressed. Must match. However, since the rotational speed of the drive rotator fluctuates from moment to moment according to the operating state of the internal combustion engine, the motor control by the electronic control unit becomes complicated in order to match the rotation speed of the release lever and the drive rotator. In the worst case, there is a problem that the retention of the valve timing deteriorates.

  The present invention has been made in view of such a problem, and an object of the present invention is to provide a valve timing adjusting device that easily secures valve timing retention.

  The invention according to claim 1 controls the relative phase between the drive rotator that rotates in conjunction with the crankshaft, the driven rotator that rotates in conjunction with the camshaft, and the drive rotator and the driven rotator. A valve timing adjusting device for adjusting a valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine according to the relative phase, the phase control unit comprising: a drive rotor And a peripheral surface portion extending in a rotation direction common to the drive rotator and the driven rotator, and provided on the other rotator of the drive rotator and the driven rotator. A first wedge surface portion whose radial interval with the peripheral surface portion decreases toward the retarded angle side of the driven rotor relative to the drive rotor, and the same rotary body as the first wedge surface portion of the drive rotor and the driven rotor A second wedge surface portion whose radial distance from the circumferential surface portion decreases toward the advance side of the driven rotor relative to the drive rotor, and the first roller interposed between the circumferential surface portion and the first wedge surface portion. A moving body, a second rolling body interposed between the peripheral surface portion and the second wedge surface portion on the advance side with respect to the first rolling body, and interposed between the first rolling body and the second rolling body, An elastic member for urging one rolling element toward the retard side and urging the second rolling element toward the advance side, and a first wedge surface portion and a second wedge surface portion of the drive rotator and the driven rotator are provided. A first actuator that generates a first pressing force that pushes the first rolling element toward the advance side, and is built in the same rotating body as the first actuator among the driving rotating body and the driven rotating body; A second actuator for generating a second pressing force for pressing the two rolling elements toward the retard side, and a first actuator by the first actuator. And control means for controlling the generation of the second pushing force due to the generation, and second actuator pressing force, and having a.

  According to such an invention, the first rolling element is biased toward the retarded angle side of the elastic member with respect to the circumferential surface portion and the first wedge surface portion provided on one and the other of the driving rotating body and the driven rotating body. When pressed, the wedge action is exerted by the first wedge surface portion whose radial distance from the peripheral surface portion is reduced toward the retard side. As a result, the driven rotator is rotated to the first side (hereinafter simply referred to as “first side” in the solution section) of the advance side and the retard side with respect to the drive rotator. become unable. At the same time, when the second rolling element is pressed against the circumferential surface portion and the second wedge surface portion provided on one and the other of the driving rotating body and the driven rotating body by urging the elastic member toward the advance side, The wedge action is exhibited by the second wedge surface portion whose radial distance from the peripheral surface portion decreases toward the advance side. As a result, the driven rotator rotates relative to the drive rotator to the second side (hereinafter simply referred to as “second side” in the column of solution means) which is the other of the advance side and the retard side. become unable. In this way, when the driven rotator is locked on both the first side and the second side, the fluctuation torque that urges the driven rotator alternately to the advance side and the retard side with respect to the drive rotator is cam. Even when transmitted from the shaft, the valve timing is maintained.

  Further, under such a valve timing holding state, the first actuator built in the rotating body provided with each wedge surface portion presses the first rolling element toward the advance side against the bias of the elastic member. When the pressure is generated by the control of the control means, the pressing of the first rolling element against the peripheral surface portion and the first wedge surface portion is eased. As a result, since the lock on the first side of the driven rotator is released, the driven rotator rotates relative to the first side with respect to the drive rotator by receiving the fluctuation torque on the first side, Even if the fluctuation torque is received, the second side remains locked by the second rolling element, so that the relative rotation does not occur and the valve timing is changed to one side. On the other hand, the second actuator built in the rotating body provided with each wedge surface portion presses the second rolling element toward the retarded side against the bias of the elastic member under the valve timing holding state. When the pressure is generated, the pressing of the second rolling element against the peripheral surface portion and the second wedge surface portion is eased. As a result, since the lock on the second side of the driven rotator is released, the driven rotator rotates relative to the second side with respect to the drive rotator by receiving the fluctuation torque on the second side, Even if fluctuating torque is received, the first side remains locked by the first rolling element, so that the relative rotation does not occur and the valve timing is changed to the other side.

  In particular, according to the first aspect of the present invention, in order to lock the driven rotating body and maintain the valve timing, the first rolling body and the second rolling body are respectively pressed toward the advance side and the retard side. The generation of the first pressing force and the second pressing force may be stopped. According to this, since the control of the first actuator and the second actuator performed by the control means in order to maintain the valve timing is simple, that is, the generation and stop of the first pressing force and the second pressing force, respectively. It is possible to easily ensure the property.

  According to the second aspect of the present invention, a plurality of phase control units are arranged in the rotation direction common to the drive rotator and the driven rotator. According to this, since the driven rotator can be locked to the drive rotator at a plurality of locations in the rotation direction, the generation of the pressing force by each actuator built in one of the rotators is controlled by the control means. In combination with this, high valve timing retention can be ensured.

  According to a third aspect of the present invention, the first actuator and the second actuator are individual piezoelectric actuators that generate the first pressing force and the second pressing force by the extension of the piezoelectric element, respectively.

  In such an invention, the piezoelectric actuator as the first actuator is controlled by the control means to extend the piezoelectric element, so that the first pressing force for pressing the first rolling element toward the advance side can be generated quickly. it can. In addition, by controlling the piezoelectric actuator as the second actuator by the control means and extending the piezoelectric element, it is possible to quickly generate the second pressing force that presses the second rolling element toward the retard side. Moreover, the generation of the first pressing force and the second pressing force can be easily stopped by controlling the piezoelectric actuators as the respective actuators by the control means and contracting the individual piezoelectric elements together. According to the above, the retention of the valve timing can be easily ensured together with the adjustment response of the valve timing.

  According to the invention described in claim 4, the first actuator includes a first piston that contacts the first rolling element from the retard side, and a first drive source that reciprocates the first piston toward the advance side and the retard side. The second actuator has a second piston that contacts the second rolling element from the advance side, and a second drive source that reciprocates the second piston to the retard side and the advance side, Controls the reciprocating drive of the first piston by the first drive source and the reciprocating drive of the second piston by the second drive source.

  In such an invention, the first driving body is controlled by the control means, and the first piston contacting the first rolling element from the retard side is driven to the advance side, so that the first rolling element is moved to the advance side. It is possible to correctly generate the first pressing force for pressing to the right. The second driving source is controlled by the control means, and the second piston that contacts the second rolling element from the advance side is driven to the retard side, thereby pressing the second rolling body to the retard side. The double pressing force can be generated correctly. In addition, the first driving force and the second driving force are controlled by the control means to drive the first piston and the second piston to the retard side and the advance side, respectively. Generation can be easily stopped. According to the above, the retention property of the valve timing can be reliably ensured together with the adjustment response property of the valve timing.

  According to the invention described in claim 5, the first piston has a first holding surface portion that is formed in a circular arc shape along the outer peripheral surface of the first rolling element and holds the first rolling element from the retarded side, The second piston has a second holding surface portion that is formed in a circular arc shape along the outer peripheral surface of the second rolling element and holds the second rolling element from the advance side.

  In such an invention, when the first piston is driven to the advance side, the outer peripheral surface of the first rolling element is held in a surface contact state from the retard side by the arc-shaped first holding surface portion of the piston. Therefore, the first rolling element can be quickly pressed in the correct direction by the holding surface portion. Similarly, when the second piston is driven to the retard side, the outer peripheral surface of the second rolling element is held in a surface contact state from the advance side by the arc-shaped second holding surface portion of the piston. Therefore, the second rolling element can be quickly pressed in the correct direction by the holding surface portion. According to the above, it is possible to obtain adjustment responsiveness with high valve timing in a timely and reliable manner. Moreover, according to the surface contact action of each holding surface portion with respect to each rolling element, the surface pressure generated at the contact interface is reduced, so that the durability can be improved.

  According to the invention described in claim 6, the first actuator has a first cylinder chamber filled with the working fluid between the first piston and the first drive source, and the first piston advances in the first cylinder chamber. The cross-sectional area of the portion that reciprocally slides to the angle side and the retard angle side is smaller than the cross-sectional area of the portion that the first drive source reciprocates to the advance side and the retard side in the first cylinder chamber. Has a second cylinder chamber filled with the working fluid between the second piston and the second drive source, and the second piston chamber is a portion of the second cylinder chamber that reciprocally slides to the retard side and the advance side. The cross-sectional area is smaller than the cross-sectional area of the portion of the second cylinder chamber where the second drive source slides back and forth toward the retard side and the advance side.

  In such an invention, the first piston having the first cylinder chamber between the first drive source controlled by the control means has the first drive source due to the pressure transmission action of the working fluid filling the first cylinder chamber. It is driven to the advance side in accordance with the displacement to the advance side. At this time, the cross-sectional area of the portion where the first piston slides in the first cylinder chamber is smaller than the cross-sectional area of the portion where the first drive source slides. The driving speed of the piston can be relatively increased to increase the pressing speed of the first rolling element by the first piston. Similarly, the second piston having the second cylinder chamber between the second drive source controlled by the control means is retarded by the pressure transmission action of the working fluid filling the second cylinder chamber. It is driven to the retard side in accordance with the displacement to the side. At this time, the cross-sectional area of the portion where the second piston slides in the second cylinder chamber is smaller than the cross-sectional area of the portion where the second drive source slides. It is possible to increase the pressing speed of the second rolling element by the second piston by relatively increasing the driving amount of the piston. According to the above, it is possible to improve the valve timing adjustment responsiveness while using a small drive source for each actuator built in the drive rotator or the driven rotator.

  According to the seventh aspect of the present invention, of the driving rotating body and the driven rotating body, the first wedge surface portion and the second wedge surface portion are provided, and the rotating body incorporating the first actuator and the second actuator has a peripheral surface portion. It arrange | positions at the outer peripheral side of the rotary body provided. As described above, in the configuration in which each actuator is incorporated in the rotating body provided on the outer peripheral side of the rotating body provided with the peripheral surface portion and provided with the first wedge surface portion and the second wedge surface portion, these actuators are controlled by the control means. Therefore, it is possible to easily form a power feeding structure necessary for this.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description is abbreviate | omitted by attaching | subjecting the same code | symbol to the corresponding component in each embodiment.

(First embodiment)
FIG. 1 shows a valve timing adjusting apparatus 1 according to a first embodiment of the present invention. The valve timing adjusting device 1 is mounted on a vehicle and installed in a transmission system that transmits engine torque from a crankshaft (not shown) of an internal combustion engine to a camshaft 2. Here, the camshaft 2 shown in FIG. 1 opens and closes an intake valve (not shown) among the “valves” of the internal combustion engine by transmission of engine torque. Then, the valve timing of the intake valve is adjusted.

(Constitution)
The detailed configuration of the first embodiment will be described below. As shown in FIGS. 1 and 2, the valve timing adjusting device 1 includes a drive rotator 4, a driven rotator 6, and a phase control unit 8.

  The drive rotating body 4 is formed in a hollow case shape as a whole by attaching the cover 40 to the sprocket 42. The cover 40 is formed of a metal into a disk shape, and is disposed coaxially between the sprocket 42 and a power transmission base 10 described later. The sprocket 42 is formed of a metal in a cylindrical shape, and has a plurality of teeth 44 that protrude radially outward from the peripheral wall in the rotational direction. The sprocket 42 is linked to the crankshaft by an annular timing chain (not shown) being spanned between the teeth 44 and a plurality of teeth of the crankshaft. Therefore, when the engine torque is input from the crankshaft to the sprocket 42 through the timing chain, the drive rotator 4 rotates in the clockwise direction in FIG. 2 in conjunction with the crankshaft.

  The driven rotator 6 is formed in a disk shape from metal and is concentrically accommodated on the inner peripheral side of the sprocket 42 having a larger diameter than the rotator 6. The driven rotator 6 has a connecting portion 60 that is coaxially connected to the camshaft 2 by screwing. With this connection, the driven rotator 6 can rotate in the clockwise direction of FIG. 2 in conjunction with the camshaft 2 and is also referred to as an advance angle side (hereinafter simply referred to as “advance angle side”) with respect to the drive rotator 4. ) And the drive rotator 4 relative to the retard side (hereinafter also simply referred to as “retard side”).

  Thus, the variable torque acting on the camshaft 2 due to the spring reaction force from the intake valve or the like during operation of the internal combustion engine is transmitted to the driven rotor 6 connected to the camshaft 2. It has become. Here, as illustrated in FIG. 3A, the fluctuating torque includes a negative torque that biases the driven rotator 6 toward the advance side with respect to the drive rotator 4, and a driven rotator with respect to the drive rotator 4. 6 alternates with a positive torque that urges 6 toward the retard side. In particular, the fluctuation torque of the present embodiment shows a tendency that the peak torque T + of the positive torque is larger than the peak torque T− of the negative torque due to the friction between the camshaft 2 and its bearings, etc. The average torque Tave of the fluctuation torque is biased toward the positive torque side, that is, the retard side.

  As shown in FIG. 2, a plurality of (six in this embodiment) phase control units 8 are arranged side by side in the rotation direction common to the rotating bodies 4 and 6. As shown in FIGS. 1, 2, and 4, each phase control unit 8 shares a power transmission base 10, power transmission coils 11 and 12, power reception coils 13 and 14, and a control circuit unit 16 with each other, and a peripheral surface portion 20 and a wedge surface portion. 21, 22, rolling elements 23 and 34, elastic member 25, and actuators 30 and 31.

  As shown in FIGS. 1 and 4, the power transmission base 10 is formed in a disk shape from a metal, and is disposed coaxially with the rotating bodies 4 and 6 at a location apart from the cover 40 and is a chain case (not shown) of the internal combustion engine. ).

  The first power transmission coil 11 is formed in an annular shape as a whole by winding a metal wire. The 1st power transmission coil 11 is arrange | positioned coaxially with the rotary bodies 4 and 6, and is hold | maintained at the power transmission base 10 via the insulating material.

  The second power transmission coil 12 is formed in an annular shape having a smaller diameter than that of the first power transmission coil 11 as a whole by winding a metal conductive wire. The second power transmission coil 12 is disposed concentrically on the inner peripheral side of the first power transmission coil 11 and is held on the power transmission base 10 via an insulating material.

  The first power receiving coil 13 is formed in an annular shape having substantially the same diameter as that of the first power transmitting coil 11 as a whole by winding a metal conductive wire. The first power receiving coil 13 is coaxially disposed between the first power transmitting coil 11 and the driven rotor 6 and is held by the cover 40 so as to be integrally rotatable via an insulating material. The first power receiving coil 13 is electrically connected to a first actuator 30 described in detail later. Thereby, when the first power transmission coil 11 as the primary coil is energized, the first power reception coil 13 as the secondary coil is excited, and the first actuator 30 is energized by the induced voltage generated in the power reception coil 13. It is like that. That is, in the present embodiment, the first power transmission coil 11 and the first power reception coil 13 form a non-contact power feeding structure 17 for the first actuator 30.

  The second power receiving coil 14 is formed in an annular shape having substantially the same diameter as that of the second power transmitting coil 12 as a whole, that is, a smaller diameter than the first power receiving coil 13 by winding a metal wire. The second power receiving coil 14 is arranged concentrically on the inner peripheral side of the first power receiving coil 13 and is held by the cover 40 so as to be integrally rotatable via an insulating material. The second power receiving coil 14 is electrically connected to a second actuator 31 described in detail later. Thereby, when the second power transmission coil 12 as the primary coil is energized, the second power reception coil 14 as the secondary coil is excited, and the second actuator 31 is energized by the induced voltage generated in the power reception coil 14. It is like that. That is, in the present embodiment, the second power transmission coil 12 and the second power reception coil 14 form a non-contact power feeding structure 18 for the second actuator 31.

  The control circuit unit 16 as “control means” is configured by, for example, a power supply driver and a control microcomputer thereof, and is arranged in the vicinity of the power transmission base 10 or in a position away from the power transmission base 10, and the power transmission coil 11, 12 is electrically connected. The control circuit unit 16 controls the operation of the first actuator 30 through the first power receiving coil 13 by energizing the first power transmitting coil 11, and via the second power receiving coil 14 by energizing the second power transmitting coil 12. Then, the operation of the second actuator 31 is controlled.

  As shown in FIG. 2, the configurations of the elements 20 to 25, 30, and 31 individually included in each phase control unit 8 are not substantially different between the units 8. Therefore, in the following, a detailed configuration will be described focusing on 20 to 25, 30, and 31 of the one-phase control unit 8.

  As shown in FIGS. 2 and 4, the peripheral surface portion 20 is formed in a circular arc surface concentric with the rotating body 6 from a part of the outer peripheral surface of the driven rotating body 6 extending in the rotation direction. Thereby, the peripheral surface part 20 of the one-phase control unit 8 is connected to the peripheral surface part 20 of the phase control unit 8 adjacent to the rotation direction in the rotation direction.

  The first wedge surface portion 21 is formed on a portion of the inner peripheral surface of the sprocket 42 of the drive rotator 4 disposed on the outer peripheral side of the driven rotator 6 so as to face the peripheral surface portion 20 of the same phase control unit 8. . The first wedge surface portion 21 of the present embodiment has a curved surface shape in which the distance from the rotation center of the drive rotator 4 decreases toward the retard side. As a result, the first wedge surface portion 21 has a shape in which the radial interval with respect to the peripheral surface portion 20 of the same phase control unit 8 is reduced toward the retard side.

  The second wedge surface portion 22 is formed on the inner peripheral surface of the sprocket 42 at a portion facing the peripheral surface portion 20 of the unit 8 on the advance side of the first wedge surface portion 21 of the same phase control unit 8. . The second wedge surface portion 22 of the present embodiment is smoothly connected to the first wedge surface portion 21 of the same phase control unit 8 and has a curved surface shape in which the distance from the rotation center of the drive rotator 4 decreases toward the advance side. Presents. Thus, the second wedge surface portion 22 has a shape in which the radial interval with respect to the peripheral surface portion 20 of the same phase control unit 8 is reduced toward the advance side.

  The first rolling element 23 is a roller formed of a metal in a columnar shape and is eccentric with respect to the rotation center of the rotating bodies 4 and 6, and the peripheral surface portion 20 and the first wedge surface portion 21 of the same phase control unit 8. Intervened in between.

  The second rolling element 24 is a roller formed of a metal in a cylindrical shape, is eccentric with respect to the rotation center of the rotating bodies 4 and 6, and is more advanced than the first rolling element 23 of the same phase control unit 8. It is interposed between the peripheral surface portion 20 and the second wedge surface portion 22 of the same phase control unit 8 so as to be positioned.

  The elastic member 25 is a compression coil spring in which a metal wire is wound in a rectangular ring shape, for example, and is interposed between the rolling elements 23 and 24 of the same phase control unit 8. The elastic member 25 urges the first rolling element 23 to the retard side and compresses the second rolling element 23 to the retard side by the compression to the advance side by the first rolling element 23 or the compression to the retard side by the second rolling element 24. A restoring force that urges 24 toward the advance side is generated.

  As shown in FIGS. 1 and 2, the first actuator 30 is a piezoelectric actuator as a kind of linear motion actuator, and is built in the drive rotator 4 provided with the wedge surface portions 21 and 22. The first actuator 30 of this embodiment is a combination of a first drive source 32 and a first piston 33.

  The first drive source 32 is a piezoelectric element made of, for example, stacked PZT or the like, and is supported by the sprocket 42 of the drive rotator 4 on the retard side with respect to the first rolling element 23 of the same phase control unit 8. The first drive source 32 is arranged so that the expansion and contraction direction is substantially along the rotation direction of the rotating bodies 4 and 6, and the retard side end thereof is fixed to the sprocket 42. Thereby, the advance side end of the first drive source 32 is a displacement end 32a (see FIG. 5) capable of reciprocating displacement. The first drive source 32 is electrically connected to the first power receiving coil 13, and expands and contracts depending on the presence / absence of energization through the power receiving coil 13. Specifically, the first drive source 32 expands by energization to displace the displacement end 32a to the advance side, while contracting by energization stop to displace the displacement end 32a to the retard side.

  As shown in FIG. 2, the first piston 33 is formed of a metal in a columnar shape, is retarded from the first rolling element 23 of the same phase control unit 8, and is advanced from the first drive source 32 of the unit 8. Are supported by the sprocket 42. The first piston 33 is disposed so as to be reciprocally driven in an axial direction substantially along the rotational direction of the rotating bodies 4 and 6, and is sandwiched between the first rolling element 23 and the first drive source 32 of the same phase control unit 8. Has been.

  Therefore, as shown in FIG. 6, when the first piston 33 is driven to the advance side by the displacement end 32 a of the first drive source 32 that is displaced to the advance side, the first piston 33 resists the bias of the elastic member 25. A first pressing force that presses the rolling element 23 toward the advance side is generated. Here, the end face on the advance side that contacts the first rolling element 23 from the retard side in the first piston 33 is an arcuate surface that is eccentric with respect to the rotation center of the rotating bodies 4 and 6 and that is recessed toward the retard side. The first holding surface portion 33a is formed, and particularly in the present embodiment, an arcuate surface shape along the outer peripheral surface of the first rolling element 23 is exhibited. Accordingly, the first holding surface portion 33a of the first piston 33 can hold the first rolling element 23 in a surface contact state from the retarded angle side and correctly press the rolling element 23 toward the advanced angle side.

  On the other hand, as shown in FIG. 5, when the displacement end 32 a of the first drive source 32 is displaced to the retard side, the first piston 33 is moved by the first rolling element 23 that receives the bias of the elastic member 25. The first rolling element 23 and the first piston 33 are driven to the retarded angle side by being pressed against.

  As shown in FIGS. 1 and 2, the second actuator 31 is a separate piezoelectric actuator from the first actuator 30 of the same phase control unit 8, and is built in the drive rotator 4 together with the first actuator 30. The first actuator 30 of this embodiment is a combination of a second drive source 34 and a second piston 35.

  The second drive source 34 is a piezoelectric element similar to the first drive source 33, and is supported by the sprocket 42 of the drive rotating body 4 on the advance side of the second rolling element 24 of the same phase control unit 8. The second drive source 34 is arranged such that the expansion / contraction direction is substantially along the rotation direction of the rotating bodies 4 and 6, and the advance side end thereof is fixed to the sprocket 42. Thereby, the retard side end of the second drive source 34 is a displacement end 34a (see FIG. 5) that can be reciprocally displaced. The second drive source 34 is electrically connected to the second power receiving coil 14, and expands and contracts depending on the presence / absence of energization through the power receiving coil 14. Specifically, the second drive source 34 expands by energization and displaces the displacement end 34a to the retarded angle side, and contracts by energization stop to displace the displacement end 34a to the advance angle side.

  As shown in FIG. 2, the second piston 35 is formed of a metal in a columnar shape, and is advanced from the second rolling element 24 of the same phase control unit 8 and retarded from the second drive source 34 of the unit 8. Are supported by the sprocket 42. The second piston 35 is disposed so as to be reciprocally driven in an axial direction substantially along the rotational direction of the rotating bodies 4 and 6, and is sandwiched between the second rolling element 24 and the second driving source 34 of the same phase control unit 8. Has been.

  Therefore, as shown in FIG. 7, when the second piston 35 is driven to the retarded angle side by the displacement end 34 a of the second drive source 34 that is displaced to the retarded angle side, the second member 35 resists the bias of the elastic member 25. A second pressing force is generated that presses the two rolling elements 24 toward the retard side. Here, in the second piston 35, an end surface on the retarded side that contacts the second rolling element 24 from the advance side is an arc surface that is eccentric with respect to the rotation center of the rotating bodies 4 and 6 and is recessed toward the advance side. The second holding surface portion 35a is formed, and in this embodiment, an arcuate surface along the outer peripheral surface of the second rolling element 24 is exhibited. As a result, the second holding surface portion 35a of the second piston 35 can hold the second rolling element 24 in a surface contact state from the advance side and correctly press the rolling element 24 to the retard side.

  On the other hand, as shown in FIG. 5, when the displacement end 34 a of the second drive source 34 is displaced to the advance side, the second piston 35 is moved by the second rolling element 24 that is biased by the elastic member 25. The second rolling element 24 and the second piston 35 are driven to the advance angle side by being pressed against.

  In each control unit 8 having the above configuration, when the first drive source 32 is energized through the first power receiving coil 13 by energization from the control circuit unit 16 to the first power transmission coil 11, The first piston 33 is driven to the advance side by extension, and the first pressing force acts on the first rolling element 23. On the other hand, when energization from the control circuit unit 16 to the first power transmission coil 11 is stopped, and energization to the first drive source 32 via the first power reception coil 13 is also stopped, the drive source 32 The first piston 33 is driven to the retard side together with the first rolling element 23 by the contraction.

  Further, in each control unit 8, when the second drive source 34 is energized through the second power receiving coil 14 by energization from the control circuit unit 16 to the second power transmission coil 12, the second drive source 34 is expanded by the extension of the drive source 34. The piston 35 is driven to the retard side, and the second pressing force acts on the second rolling element 24. In contrast, when the energization from the control circuit unit 16 to the second power transmission coil 12 is stopped, and the energization to the second drive source 34 via the second power receiving coil 14 is also stopped, the drive source 34 By contraction, the second piston 35 is driven together with the second rolling element 24 to the advance side.

  As described above, in the present embodiment, the first and second pushes for pressing the rolling elements 23 and 24 by the reciprocating drive of the pistons 33 and 35 by the drive sources 32 and 34 by energizing and stopping the power transmission coils 11 and 12 are performed. The generation of pressure can be controlled.

(Operation)
Next, the valve timing adjustment operation of the first embodiment will be described. During the operation of the internal combustion engine, the control circuit unit 16 controls the generation of the first and second pressing forces based on the rotation angles of the crankshaft and the camshaft. As a result, the valve timing is adjusted to a timing according to the relative phase between the rotating bodies 4 and 6. The detailed contents of the valve timing adjustment operation will be described below.

(Retention processing)
In the internal combustion engine, when an operation condition indicating a stable operation state such as an accelerator holding state is established, the control circuit unit 16 executes a holding process. Specifically, in the holding process, both the first and second pressing forces are lost in each phase control unit 8 by stopping both energization of the power transmission coils 11 and 12.

  In each phase control unit 8 at the time of such holding processing, the first rolling element 23 is driven to the retard side together with the first piston 33 under the bias of the elastic member 25. It is pressed against the wedge surface portion 21 and the peripheral surface portion 20. Here, in each phase control unit 8 in which the radial interval between the first wedge surface portion 21 and the peripheral surface portion 20 is reduced toward the retarded angle side, the first rolling element with respect to each of the surface portions 21 and 20. Since 23 is pressed toward the retard side, the wedge action is exhibited. Therefore, when the retarded positive torque of the variable torque acts on the driven rotor 6, the relative displacement of the first rolling element 23 toward the advance side with respect to the peripheral surface portion 20 is restricted by the wedge action. Thus, the locking of the driven rotor 6 with respect to the drive rotor 4 is realized on the retard side.

  Further, in each phase control unit 8 at the time of holding processing, the second rolling element 24 is driven to the advance side together with the second piston 35 under the bias of the elastic member 25, so that the second rolling element 24 as shown in FIG. It is pressed against the wedge surface portion 22 and the peripheral surface portion 20. Here, in each phase control unit 8 in which the radial interval between the second wedge surface portion 22 and the peripheral surface portion 20 is reduced toward the advance side, the second rolling element is provided with respect to each of the surface portions 22 and 20. Since 24 is pressed toward the advance side, the wedge action is exhibited. Therefore, when the negative torque on the advance side of the variable torque acts on the driven rotor 6, the relative displacement of the second rolling element 24 toward the retard side with respect to the peripheral surface portion 20 is restricted by the wedge action. Thus, the locking of the driven rotor 6 with respect to the drive rotor 4 is also realized on the advance side.

  As described above, when the holding process is performed, the driven rotating body 6 is restricted from rotating relative to the retarded angle side and the advanced angle side with respect to the drive rotating body 4, so that the relative phase between the rotating bodies 4 and 6, As a result, the valve timing is reliably maintained.

(Retard processing)
When an operation condition representing a light load normal operation state or the like is satisfied in the internal combustion engine in which the valve timing is maintained, the control circuit unit 16 executes a retardation process. Specifically, in the retard processing, the first pressing force is generated from the first actuator 30 in each phase control unit 8 by only energizing the first power transmission coil 11 while energization of the second power transmission coil 12 is stopped. Let

  In each phase control unit 8 at the time of execution of the retardation processing, the first rolling element 23 receives the first pressing force from the first piston 33, thereby resisting the urging of the elastic member 25 as shown in FIG. Pressed toward the advance side. Here, in each phase control unit 8 in which the radial interval between the first wedge surface portion 21 and the peripheral surface portion 20 is reduced toward the retard side, the first rolling element 23 is connected to the first wedge surface portion 21 and the peripheral surface portion 20. The position is shifted toward the advance side relative to the surface portion 20. As a result, in each phase control unit 8, the pressing of the first rolling element 23 against the first wedge surface portion 21 and the peripheral surface portion 20 is alleviated, so that the retarded side lock of the driven rotating body 6 is released. In each phase control unit 8, the second rolling element 24 is pressed toward the advance side via the elastic member 25 by the displaced first rolling element 23, whereby the second wedge surface portion 22 and the peripheral surface portion 20. Therefore, the lock on the advance side of the driven rotor 6 is maintained.

  As described above, when the retarding process is executed, the driven rotating body 6 rotates relative to the driving rotating body 4 toward the retarding side by applying a retarding-side positive torque among the variable torques as shown in FIG. To do. On the other hand, as shown in FIG. 3, the driven rotator 6 is restrained from rotating relative to the drive rotator 4 relative to the drive rotator 4 by the lock on the advance side, even if it receives a negative torque on the advance side of the variable torque. The Therefore, the relative rotation to the retard angle side and the relative rotation restriction to the advance angle side are repeated according to the alternation of the varying torque, so that the relative phase between the rotating bodies 4 and 6 and the valve timing can be surely retarded. It will be done.

(Advance processing)
In the internal combustion engine in which the valve timing is maintained, when an operating condition indicating an accelerator off state, a low / medium speed / high load operating state, or the like is satisfied, the control circuit unit 16 executes an advance angle process. Specifically, in the advance processing, the second pressing force is generated from the second actuator 31 in each phase control unit 8 by only energizing the second power transmission coil 12 while energization of the first power transmission coil 11 is stopped. Let

  In each phase control unit 8 at the time of execution of such advance processing, the second rolling element 24 receives the second pressing force from the second piston 35 and resists the biasing of the elastic member 25 as shown in FIG. It is pushed toward the retard side. Here, in each phase control unit 8 in which the radial interval between the second wedge surface portion 22 and the peripheral surface portion 20 is reduced toward the advance side, the second rolling element 24 is connected to the second wedge surface portion 22 and the peripheral surface portion. The position is shifted toward the retard side relative to the surface portion 20. As a result, in each phase control unit 8, the pressing of the second rolling element 24 against the second wedge surface portion 22 and the peripheral surface portion 20 is eased, so that the lock on the advance side of the driven rotating body 6 is released. Further, in each phase control unit 8, the first rolling element 23 is pressed toward the retarded side via the elastic member 25 by the displaced second rolling element 24, whereby the first wedge surface portion 21 and the peripheral surface portion 20. Thus, the retarded side lock of the driven rotor 6 is maintained.

  As described above, at the time of execution of the advance angle processing, the driven rotation body 6 rotates relative to the drive rotation body 4 toward the advance angle side due to the negative torque on the advance angle side of the variable torque acting. On the other hand, even if the driven rotor 6 receives a retarded positive torque among the fluctuation torques, the relative rotation of the driven rotor 4 to the retarded side is restricted by the retarded side lock. Therefore, the relative rotation to the advance side and the relative rotation restriction to the retard side are repeated according to the alternating of the varying torque, so that the relative phase between the rotating bodies 4 and 6 and thus the valve timing is reliably advanced. It will be done.

  According to the first embodiment described so far, in each phase control unit 8 at the time of holding processing, the drive sources 32 and 34 composed of individual piezoelectric elements are simply processed by stopping energization of the power transmission coils 11 and 12. The first and second pressing forces by the pistons 33 and 35 can be eliminated by contracting. Further, in each phase control unit 8 at the time of holding processing, the elastic member 25 between the rolling elements 23 and 24 and the driven rotor 6 do not substantially constitute a spring mass system, so that negative torque and positive torque are generated by the driven rotor. 6, the rolling elements 23, 24 are prevented from vibrating away from the first wedge surface portion 21, the second wedge surface portion 22, and the peripheral surface portion 20, and the holding state is maintained. Can be kept stable. Further, according to these, the retention of the valve timing can be easily secured with power saving.

  Furthermore, in each phase control unit 8 at the time of execution of the retard processing, the first piston 33 is driven quickly by extending the first drive source 32 made of a piezoelectric element in response to energization to the first power transmission coil 11. Thus, the generation speed of the first pressing force with respect to the first rolling element 23 can be increased. In addition, at this time, the first rolling element 23 can be pushed while being brought into surface contact with the first holding surface portion 33a of the first piston 33, so that the first pressing force from the holding surface portion 33a to the first rolling element 23 can be pushed. The transmission efficiency can be increased and the first rolling element can be pushed stably in a certain direction. According to these, when the valve timing is retarded, high adjustment responsiveness can be obtained in a timely and reliable manner.

  Similarly, in each phase control unit 8 at the time of execution of the advance angle processing, the second piston 35 is quickly moved by extending the second drive source 34 made of a piezoelectric element in response to energization to the second power transmission coil 13. And the generation speed of the second pressing force against the second rolling element 24 can be increased. In addition, at this time, since the second rolling element 24 can be pushed while being brought into surface contact with the second holding surface part 35a of the second piston 35, the second pressing force from the holding surface part 35a to the second rolling element 24 can be pushed. The second rolling element can be pushed stably in a certain direction. According to these, even when the valve timing is advanced, high adjustment responsiveness can be obtained in a timely and reliable manner.

  In addition to the above, according to the first embodiment, when the rolling elements 23 and 24 are pressed in the surface contact state by the holding surface portions 33a and 35a of the pistons 33 and 35 in each phase control unit 8, the surface pressure at the pressing interface is small. Therefore, the durability of the pistons 33 and 35 is improved. In each phase control unit 8, the drive rotor 4 incorporating the actuators 30 and 31 is arranged on the outermost periphery of the apparatus 1 as shown in FIGS. This makes it easy to form the power feeding structures 17 and 18.

(Second embodiment)
As shown in FIG. 8, the second embodiment of the present invention is a modification of the first embodiment. In each phase control unit 108 of the second embodiment, the first actuator 130 is formed by combining the first cylinder chamber 136 in addition to the first drive source 132 and the first piston 133.

  The first cylinder chamber 136 is formed in the sprocket 42 of the drive rotating body 4 on the retard angle side of the first wedge surface portion 21 of the same phase control unit 108, and the stepped area is reduced by one step as the advance angle side. It has a cylindrical hole shape. The first cylinder chamber 136 is filled with an incompressible fluid such as oil injected therein as a working fluid.

  In the first cylinder chamber 136, a displacement end 132 a having a cross-sectional shape substantially equal to the chamber portion 136 a in the first drive source 132 is slidable in the axial direction in the input chamber portion 136 a that has a larger cross-sectional area. It is inserted. Here, the first drive source 132 of this embodiment is configured by mounting a plate-like movable member on the piezoelectric element 132b corresponding to the first drive source 32 of the first embodiment, and the displacement end 132a is moved by the movable member. Is formed.

  In the output chamber 136b, which has a smaller cross-sectional area in the first cylinder chamber 136, a retarded side end 133a having a transverse cross section substantially the same as the chamber 136b in the first piston 133 can be reciprocally slid in the axial direction. Is inserted. Here, the first piston 133 of the present embodiment has a protrusion protruding from the main body portion 133b corresponding to the first piston 33 of the first embodiment to the opposite side of the first rolling element 23, and the protrusion As a result, a retard side end 133a is formed.

  In the second embodiment having such a configuration, the displacement end 132a of the first drive source 132 is reciprocally displaced toward the advance side and the retard side by the pressure transmission action of the working fluid filling the first cylinder chamber 136. Thus, the first piston 133 is reciprocated to the advance side and the retard side. Here, as shown in FIG. 8, the cross-sectional area of the output chamber 136 b on which the retard side end 133 a of the first piston 133 on the side opposite to the first rolling element 23 slides is the displacement of the first drive source 132. It is smaller than the cross-sectional area of the input chamber 136a on which the end 132a slides. Therefore, the drive amount Y1 of the first piston 133 relative to the displacement amount X1 of the displacement end 132a is relatively increased by the ratio A1 / B1 of the transverse area A1 of the input chamber portion 136a and the transverse area B1 of the output chamber portion 136b. Will be. Therefore, in each phase control unit 108 at the time of execution of the retard processing, the pressing speed of the first rolling element 23 by the first piston 133 can be increased even with the relatively small first drive source 132. .

  Now, in each phase control unit 108 of 2nd embodiment, the 2nd actuator 131 also combines the 2nd drive source 134, the 2nd piston 135, and the 2nd cylinder chamber 137 according to the 1st actuator 130 mentioned above. Become.

  The second cylinder chamber 137 is formed in the sprocket 42 of the drive rotor 4 on the advance side with respect to the second wedge surface portion 22 of the same phase control unit 108, and the stepped area is reduced by one step toward the retard side. It has a cylindrical hole shape. The second cylinder chamber 137 is filled with the same working fluid as the first cylinder chamber 136.

  In the second cylinder chamber 137, the input chamber portion 137a, which has a larger cross-sectional area, has a displacement end 134a having a cross-sectional shape substantially equal to that of the chamber portion 137a in the second drive source 134 so as to be slidable in the axial direction. It is inserted. Here, the second drive source 134 of this embodiment is configured by mounting a plate-like movable member on a piezoelectric element 134b corresponding to the second drive source 34 of the first embodiment, and the displacement end 134a is moved by the movable member. Is formed.

  In the second cylinder chamber 137, the output chamber portion 137b on the side having a smaller cross-sectional area has an advance side end 135a having a cross-sectional shape substantially equal to that of the chamber portion 137b in the second piston 135, which can slide back and forth in the axial direction. Is inserted. Here, the second piston 135 of the present embodiment has a protruding portion protruding from the main body portion 135b corresponding to the second piston 35 of the first embodiment to the side opposite to the second rolling element 24, and the protruding portion. As a result, an advance side end 135a is formed.

  In the second embodiment having such a configuration, the displacement end 134a of the second drive source 134 is reciprocally displaced toward the retard side and the advance side by the pressure transmission action of the working fluid filling the second cylinder chamber 137. Thus, the second piston 135 is reciprocated to the retard side and the advance side. Here, as shown in FIG. 8, the cross-sectional area of the output chamber portion 137 b on which the advance side end 135 a of the second piston 135 on the side opposite to the second rolling element 24 slides is the displacement of the second drive source 134. It is smaller than the cross-sectional area of the input chamber portion 137a on which the end 134a slides. Therefore, the driving amount Y2 of the second piston 135 is relatively increased by the ratio A2 / B2 of the transverse area A2 of the input chamber portion 137a and the transverse area B2 of the output chamber portion 137b with respect to the displacement amount X2 of the displacement end 134a. Will be. Therefore, in each phase control unit 108 at the time of execution of the advance angle processing, the pressing speed of the second rolling element 24 by the second piston 135 can be increased even with the relatively small second drive source 134. . The cross-sectional area ratio A2 / B2 can be appropriately set to an equal value or a different value with respect to the cross-sectional area ratio A1 / B1 in the case of the first actuator 130.

  According to the second embodiment described so far, the adjustment at the time of retarding and advancing the valve timing while miniaturizing the drive rotating body 4 incorporating a plurality of sets of the actuators 130 and 131 at the outermost periphery of the apparatus 2. Responsiveness can be improved.

(Other embodiments)
Although a plurality of embodiments of the present invention have been described above, the present invention is not construed as being limited to these embodiments, and can be applied to various embodiments without departing from the scope of the present invention. .

  Specifically, only one phase control unit 8 may be provided in the rotation direction common to the rotating bodies 4 and 6. Further, with respect to the phase control unit 8, the peripheral surface portion 20 is provided in the drive rotator 4, and the wedge surface portions 21 and 22 are provided in the driven rotator 6, and the actuators 30, 31, 130, 131 are incorporated in the rotator 6. May be. In this case, as the advance processing, a first pressing force is generated from the first actuators 30 and 130 built in the driven rotor 6, and the first rolling element 23 with respect to the first wedge surface portion 21 and the peripheral surface portion 20 is generated. By relaxing the pressing, the lock on the advance side of the driven rotor 6 is released. Similarly, as the retarding process, a second pressing force is generated from the second actuators 31 and 131 built in the driven rotor 6 to press the second rolling element 24 against the second wedge surface portion 22 and the peripheral surface portion 20. By relaxing, the retarded side lock of the driven rotor 6 is released.

  The actuators 30 and 31 may be configured by only the drive sources 32 and 34, and the rolling elements 23 and 24 may be pressed by the displacement ends 32 a and 34 a of the drive sources 32 and 34. Further, the drive sources 32, 34, 132, and 134 constituting the actuators 30, 31, 130, and 131 are, for example, linear actuators that use linear solenoids in addition to linear actuators that use piezoelectric elements. Also good. Furthermore, the holding surface portions 33a and 35a of the pistons 33, 35, 133, and 135 constituting the actuators 30, 31, 130, and 131 may be formed in a flat surface shape, for example. In addition, the rolling elements 23 and 24 may be formed in a spherical shape, for example.

  In addition to the device that adjusts the valve timing of the intake valve, the present invention provides a device that adjusts the valve timing of the exhaust valve as a “valve”, and a device that adjusts the valve timing of both the intake valve and the exhaust valve. Can also be applied.

It is sectional drawing which shows the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: It is the II sectional view taken on the line of FIG. It is the II-II sectional view taken on the line of FIG. It is a characteristic view (a), (b) for demonstrating the action | operation of the valve timing adjustment apparatus by 1st embodiment of this invention. It is the IV-IV sectional view taken on the line of FIG. It is a cross-sectional schematic diagram which shows the characteristic part of the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: It corresponds to the principal part enlarged view of FIG. It is a cross-sectional schematic diagram for demonstrating the action | operation of the valve timing adjustment apparatus shown in FIG. It is a cross-sectional schematic diagram for demonstrating the action | operation of the valve timing adjustment apparatus shown in FIG. It is a cross-sectional schematic diagram which shows the characteristic part of the valve timing adjustment apparatus by 2nd embodiment of this invention, Comprising: It respond | corresponds to FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Valve timing adjustment apparatus, 2 Cam shaft, 4 Drive rotary body, 6 Driven rotary body, 8 Phase control unit, 10 Power transmission base, 11 1st power transmission coil, 12 2nd power transmission coil, 13 1st power receiving coil, 14 2nd Power receiving coil, 16 control circuit portion (control means), 17, 18 power feeding structure, 20 peripheral surface portion, 21 first wedge surface portion, 22 second wedge surface portion, 23 first rolling element, 24 second rolling element, 25 elastic member, 30 1st actuator, 31 2nd actuator, 32 1st drive source, 32a Displacement end, 33 1st piston, 33a 1st holding surface part, 34 2nd drive source, 34a Displacement end, 35 2nd piston, 35a 2nd holding Face part, 40 cover, 42 sprocket, 108 phase control unit, 130 first actuator, 131 second actuator, 132 first Power source, 132a displacement end, 132b piezoelectric element, 133 first piston, 133a retarded side end, 133b main body, 134 second drive source, 134a displacement end, 134b piezoelectric element, 135 second piston, 135a advance side end , 135b body portion, 136 first cylinder chamber, 136a input chamber portion, 136b output chamber portion, 137 second cylinder chamber, 137a input chamber portion, 137b output chamber portion

Claims (7)

A drive rotator that rotates in conjunction with a crankshaft, a driven rotator that rotates in conjunction with a camshaft, and a phase control unit that controls the relative phase between the drive rotator and the driven rotator, A valve timing adjusting device for adjusting a valve timing of a valve that opens and closes the camshaft by torque transmission from the crankshaft in an internal combustion engine, according to the relative phase,
The phase control unit includes:
A peripheral surface portion provided in one of the drive rotator and the driven rotator and extending in a rotation direction common to the drive rotator and the driven rotator;
A first wedge surface portion that is provided on the other rotating body of the driving rotating body and the driven rotating body, and whose radial distance from the peripheral surface portion decreases toward the retarded angle side of the driven rotating body with respect to the driving rotating body. When,
Of the drive rotator and the driven rotator, provided on the same rotator as the first wedge surface portion, the radial distance from the peripheral surface portion is reduced toward the advance side of the driven rotator with respect to the drive rotator. A second wedge surface portion,
A first rolling element interposed between the peripheral surface portion and the first wedge surface portion;
A second rolling element interposed between the peripheral surface portion and the second wedge surface portion on the advance side with respect to the first rolling element;
An elastic member interposed between the first rolling element and the second rolling element, for urging the first rolling element toward the retard side and urging the second rolling element toward the advance side; ,
Of the drive rotator and the driven rotator, a first pressing force that is built in the rotator provided with the first wedge surface portion and the second wedge surface portion and presses the first rolling element toward the advance side. A generated first actuator;
A second actuator that is built in the same rotary body as the first actuator among the drive rotary body and the driven rotary body, and generates a second pressing force that presses the second rolling body toward the retarding angle;
Control means for controlling the generation of the first pressing force by the first actuator and the generation of the second pressing force by the second actuator;
A valve timing adjusting device characterized by comprising:   2. The valve timing adjusting device according to claim 1, wherein a plurality of the phase control units are arranged in a rotation direction common to the driving rotating body and the driven rotating body.   The said 1st actuator and said 2nd actuator are the separate piezoelectric actuators which generate | occur | produce said 1st pressing force and said 2nd pressing force, respectively by expansion | extension of a piezoelectric element, The Claim 1 or 2 characterized by the above-mentioned. Valve timing adjustment device. The first actuator has a first piston that contacts the first rolling element from the retard side, and a first drive source that reciprocates the first piston to the advance side and the retard side,
The second actuator has a second piston that contacts the second rolling element from the advance side, and a second drive source that reciprocates the second piston to the retard side and the advance side,
The said control means controls the reciprocating drive of the said 1st piston by the said 1st drive source, and the reciprocating drive of the said 2nd piston by the said 2nd drive source, The any one of Claims 1-3 characterized by the above-mentioned. The valve timing adjusting device according to 1. The first piston has a first holding surface portion that is formed in a circular arc shape along the outer peripheral surface of the first rolling element and holds the first rolling element from the retarded angle side,
The said 2nd piston is formed in the circular arc surface shape along the outer peripheral surface of a said 2nd rolling element, and has a 2nd holding surface part which hold | maintains a said 2nd rolling element from the said advance angle side. The valve timing adjusting device according to 1. The first actuator has a first cylinder chamber filled with a working fluid between the first piston and the first drive source, and in the first cylinder chamber, the first piston is on the advance side and the first drive source. The cross-sectional area of the portion that reciprocally slides to the retard side is smaller than the cross-sectional area of the portion that the first drive source reciprocates to the advance side and the retard side in the first cylinder chamber,
The second actuator has a second cylinder chamber filled with a working fluid between the second piston and the second drive source, and in the second cylinder chamber, the second piston is on the retard side and the second drive source. The cross-sectional area of the portion reciprocally sliding to the advance side is smaller than the cross-sectional area of the portion of the second cylinder chamber reciprocatingly sliding to the retard side and the advance side in the second cylinder chamber. The valve timing adjusting device according to claim 4 or 5.   Of the driving rotating body and the driven rotating body, the first wedge surface portion and the second wedge surface portion are provided, and the rotating body incorporating the first actuator and the second actuator is provided with the peripheral surface portion. It arrange | positions at the outer peripheral side of a body, The valve timing adjustment apparatus as described in any one of Claims 1-6 characterized by the above-mentioned.

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