JP4098695B2 - Valve timing adjustment device - Google Patents

Description

  The present invention relates to a valve timing adjusting device for an internal combustion engine (hereinafter referred to as an engine) that adjusts an opening / closing timing (hereinafter referred to as a valve timing) of at least one of an intake valve and an exhaust valve.

Conventionally, a valve timing adjusting device is provided in a transmission system that transmits drive torque of a drive shaft to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve in an engine, and the rotational phase of the driven shaft with respect to the drive shaft ( Hereinafter, the valve timing is adjusted by simply changing the rotation phase.
In the valve timing adjustment device disclosed in Patent Document 1, when the rotational phase is fixed by the foreign object biting in the assembly angle adjustment mechanism, the forward and reverse torques transmitted to the assembly angle adjustment mechanism are alternately applied by the electromagnetic brake. And the fixed state of the rotational phase is released.

JP 2003-227361 A

In the apparatus disclosed in Patent Document 1, it may be assumed that the planetary gear mechanism that transmits the torque generated by the electromagnetic brake to the assembly angle adjusting mechanism causes foreign matter to be caught and the rotational phase is fixed. However, the foreign matter caught between the gears of the planetary gear mechanism cannot be removed in a short time by simply generating torque in both forward and reverse directions. That is, in order to remove foreign matter, torque in both forward and reverse directions must be repeatedly generated for a long time, and during that time, valve timing cannot be adjusted.
An object of the present invention is to provide a valve timing adjusting device that removes foreign matter caught in a planetary gear mechanism of changing means for changing a rotation phase in a short time.

  According to the first aspect of the present invention, the detecting means detects the foreign object biting at the meshing position of the sun gear and the planetary gear of the planetary gear mechanism. The torque transmission means is configured such that when the detection means detects a foreign object biting, one of the teeth of the sun gear and the planetary gear at the meshing position is separated from the other tooth and is identical to the other tooth. Until the teeth on the pitch circle are engaged with each other, the control torque in the direction opposite to that before the detection of the engagement is transmitted to the gear mechanism. Since one tooth meshes with a tooth on the same pitch circle as the other tooth while being in sliding contact, the foreign matter caught between the one tooth and the other tooth is reliably removed. . In addition, foreign matter can be removed simply by generating a control torque in one direction, so that the time required for removing the foreign matter can be shortened. Therefore, the adjustment of the valve timing can be resumed immediately after the detection of the foreign object bite.

  According to the second aspect of the present invention, since the torque transmission means generates the control torque by the electric motor, the control torque can be accurately controlled. Therefore, it becomes easy to limit the amount of change in the rotational phase that is changed by the operation of the torque transmission means for removing foreign matter within a range that does not affect the operation of the engine.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 2 shows a valve timing adjusting apparatus 1 according to an embodiment of the present invention. The valve timing adjusting device 1 is provided in a transmission system that transmits a driving torque of a crankshaft as a driving shaft to a camshaft 2 as a driven shaft in a vehicle engine. The valve timing adjusting device 1 adjusts the valve timing of the intake valve or exhaust valve of the engine by changing the rotational phase of the camshaft 2 with respect to the crankshaft.
The valve timing adjustment device 1 includes a motion conversion mechanism 10, an electric motor 30, and a speed reduction mechanism 20.

First, the motion conversion mechanism 10 will be described. The motion conversion mechanism 10 includes a sprocket 11, an output shaft 16, arm members 28 and 29, a guide rotating body 25, a movable body 26, and the like. In FIG. 3 and FIG. 4 to be described later, hatching representing a cross section is omitted.
As shown in FIGS. 2 and 3, the sprocket 11 includes a support cylinder part 12, an input cylinder part 13 having a larger diameter than the support cylinder part 12, and a link part that connects the support cylinder part 12 and the input cylinder part 13 in a stepped manner. 14. The support cylinder portion 12 is supported by the outer peripheral wall of the output shaft 16 so as to be relatively rotatable around the rotation center line O. A chain belt is stretched around a plurality of teeth 13a formed on the input cylinder portion 13 and a plurality of teeth formed on the crankshaft. When the driving torque of the crankshaft is input to the input cylinder portion 13 through the chain belt, the sprocket 11 rotates around the rotation center line O in the clockwise direction in FIG. 3 while maintaining the rotational phase with respect to the crankshaft. That is, the sprocket 11 functions as a drive rotating body that rotates in synchronization with a crankshaft that is a drive shaft. The link part 14 is formed in a flat plate shape in which both plate surfaces are perpendicular to the parallel line of the rotation center line O.

  The output shaft 16 has a fixed portion 17 and a link portion 18. One end of the camshaft 2 is concentrically bolted to one end of the fixed portion 17, and the output shaft 16 rotates around the rotation center line O while maintaining a rotational phase with respect to the camshaft 2. That is, the output shaft 16 functions as a driven rotating body that rotates in synchronization with the camshaft 2 that is a driven shaft. Thereby, the rotation phase of the output shaft 16 with respect to the sprocket 11 is synchronized with the rotation phase of the camshaft 2 with respect to the crankshaft. Two link portions 18 are formed in a rectangular flat plate shape, and two of the two plate surfaces are arranged in a form perpendicular to the parallel line of the rotation center line O. Each link part 18 protrudes in the opposite direction from two places across the rotation center line O of the fixed part 17.

  The arm members 28 and 29 are connected to the link portion 18, the guide rotating body 25, the movable body 26, the planetary gear 22 of the speed reduction mechanism 20, and the transmission rotating body 24 by the cover 15 and the link portion 14 fixed to the input cylinder portion 13. It is pinched. The arm members 28 are formed in an oval flat plate shape, and two arm members 28 are arranged in a form in which both plate surfaces are perpendicular to the parallel line of the rotation center line O. One end portion of each arm member 28 is connected to a corresponding portion of the two portions sandwiching the rotation center line O of the link portion 14 via the shaft member 51, and forms a counter pair 80 with the link portion 14. The arm members 29 are formed in a C-shaped flat plate shape, and two arm members 29 are arranged in a form in which both plate surfaces are perpendicular to the parallel line of the rotation center line O. One end portion of each arm member 29 is connected to the corresponding link portion 18 via the shaft member 55 to form a counter pair 82 with the corresponding link portion 18. The other end of each arm member 29 is connected to the corresponding arm member 28 via the movable body 26 and forms a counter pair 84 with the corresponding arm member 28.

  As shown in FIGS. 2 and 4, the guide rotator 25 is formed in a circular flat plate shape, and both plate surfaces are arranged in a form perpendicular to the parallel line of the rotation center line O. The transmission rotator 24 is fitted and fixed to one plate surface side of the guide rotator 25, and the guide rotator 25 and the transmission rotator 24 can rotate integrally around the rotation center line O and are relative to the sprocket 11. It can be rotated. The other plate surface of the guide rotator 25 is in contact with each arm member 29 so as to be relatively slidable, and faces the plate surface of each arm member 28, each link portion 18, and link portion 14. Long holes 62 are formed at two locations across the rotation center line O of the guide rotator 25. Each elongated hole 62 opens on both plate surfaces of the guide rotator 25 and is disposed so as to be 180 ° rotationally symmetric with each other, and a guide passage 64 is formed on the inner peripheral side. The guide passages 64 formed by the long holes 62 are inclined with respect to the radial axis of the guide rotator 25 and extend linearly, and have a shape in which the radial distance from the rotation center line O changes.

  Two movable bodies 26 are provided corresponding to the long holes 62 and the guide passages 64 on the inner peripheral side thereof. Each movable body 26 is configured by combining a core member 70 and a shell member 72. The core member 70 is formed in a columnar shape and is sandwiched between the transmission rotating body 24 and the link portion 14. The shell member 72 is formed in a cylindrical shape concentrically fitted to the outer peripheral wall of one end portion of the core member 70, and is sandwiched between the transmission rotating body 24 and the arm member 29. As a result, the side walls 62 b and 62 c of the corresponding elongated holes 62 are fitted from both sides in the width direction of the guide passage 64 to the outer peripheral wall of the shell member 72 whose center line is parallel to the rotation center line O. The shell member 72 is rotatable relative to the elongated hole 62 and is slidable relative to the longitudinal direction of the guide passage 64. The outer peripheral wall of the core member 70 excluding the fitting end portion with the shell member 72 is fitted to the end portions of the corresponding arm members 28 and 29 so as to be relatively rotatable.

  In the motion conversion mechanism 10 in which the elements 11, 16, 28, 29, 25, and 26 are linked in this way, the output shaft 16 rotates in the clockwise direction in FIGS. 3 and 4 as the crankshaft rotates. During this rotation, the motion conversion mechanism 10 converts the relative rotational motion of the guide rotor 25 with respect to the sprocket 11 into the motion of the movable body 26, and further converts the motion of the movable body 26 into the relative rotational motion of the output shaft 16 with respect to the sprocket 11. To do. By this conversion action, the rotational phase of the camshaft 2 with respect to the crankshaft (hereinafter referred to as the shaft phase) changes.

  Specifically, when the guide rotator 25 does not rotate relative to the sprocket 11, the movable body 26 rotates integrally with the guide rotator 25 without being guided through the guide passage 64. At this time, the positions of the turning pair 84 formed by the arm members 28 and 29, the turning pair 82 formed by the link portion 18 and the arm member 29, and the turning pair 80 formed by the link portion 14 and the arm member 28 are not changed. Thereby, the output shaft 16 rotates synchronously with the camshaft 2 while maintaining the rotational phase with respect to the sprocket 11, and the shaft phase is kept constant.

  When the guide rotator 25 rotates relative to the sprocket 11 in the advance angle direction X, the movable body 26 is guided along the guide passage 64 and is separated from the rotation center line O. At this time, the arm member 28 rotates around the center line of the shaft member 51 and the movable body 26 with respect to the link portion 14 and the arm member 29 respectively, and rotates around the position of the pair 84 according to the movement of the movable body 26. Move away from center line O. At the same time, the arm member 29 rotates relative to the link portion 18 around the center line of the shaft member 55, rotates around the position of the pair 82 according to the movement of the movable body 26, and retards the position of the pair 80. Move closer to Y. As a result, the output shaft 16 rotates relative to the sprocket 11 in the retarding direction Y, so that the shaft phase changes to the retarding side.

  When the guide rotator 25 rotates relative to the sprocket 11 in the retarding direction Y, the movable body 26 is guided through the guide passage 64 and approaches the rotation center line O. At this time, the arm member 28 rotates around the center line of the shaft member 51 and the movable body 26 with respect to the link portion 14 and the arm member 29 respectively, and rotates around the position of the pair 84 according to the movement of the movable body 26. Move closer to the center line O. At the same time, the arm member 29 rotates relative to the link portion 18 around the center line of the shaft member 55, rotates around the position of the pair 82 according to the movement of the movable body 26, and advances toward the position of the pair 80. Release to X. As a result, the output shaft 16 rotates relative to the sprocket 11 in the advance direction X, so that the shaft phase advances.

Next, the electric motor 30 will be described. As shown in FIGS. 2 and 5, the electric motor 30 includes a housing 31, a bearing 32, a rotating shaft 33, a stator 34, a control unit 38, and the like.
The housing 31 is fixed to the engine via a stay 35. Two housings 32 and a stator 34 are accommodated and fixed in the housing 31. The rotary shaft 33 is supported at two locations in the direction of the rotation center line O by each bearing 32 and can rotate around the rotation center line O. The rotary shaft 33 is connected and fixed to the eccentric shaft 19 via a shaft coupling 36, and rotates together with the eccentric shaft 19 in the clockwise direction in FIG. The rotating shaft 33 has a circular plate-like rotor portion 33b that protrudes radially outward from the main body 33a. A plurality of magnets 37 are embedded in the outer peripheral wall of the rotor portion 33b. The magnet 37 is made of a permanent stone such as a rare earth magnet, and is arranged around the rotation center line O at equal intervals.

The stator 34 is disposed on the outer peripheral side of the rotating shaft 33 and has a cylindrical main body 40, a core 41, and a coil 42. The core 41 is formed by laminating a plurality of iron pieces and protrudes from the inner peripheral wall of the main body 40 toward the rotating shaft 33 side. A plurality of cores 41 are arranged around the rotation center line O so as to be arranged at equal intervals. A coil 42 is wound around each core 41.
The control unit 38 is constituted by an electric circuit including a microcomputer, an energization driver, a sensor, and the like, and is connected to each coil 42 of the stator 34. In FIG. 2, the entire control unit 38 is shown to be installed in the housing 31. However, for example, the energization driver and sensor of the control unit 38 are installed in the housing 31, and the microcomputer of the control unit 38 is installed outside the housing 31. You may make it install in. The control unit 38 controls energization to each coil 42 by controlling the energization driver according to a control program stored in the memory of the microcomputer. A rotating magnetic field is formed on the outer peripheral side of the rotating shaft 33 by the energization of each controlled coil 42, and a control torque in the retarding direction Y or the leading angle direction X according to the direction of the rotating magnetic field is applied to the rotating shaft 33. .

Next, the speed reduction mechanism 20 as a planetary gear mechanism will be described. As shown in FIGS. 2 and 6, the speed reduction mechanism 20 includes a sun gear 21, an eccentric shaft 19, a planetary gear 22, a bearing 23, a transmission rotating body 24, and the like.
The sun gear 21 is concentrically fixed to the inner peripheral wall of the input cylinder portion 13. The sun gear 21 is composed of an internal gear whose tooth tip curved surface is on the inner peripheral side of the tooth bottom curved surface. The sun gear 21 rotates integrally with the sprocket 11 around the rotation center line O in the clockwise direction of FIG.

The eccentric shaft 19 is arranged eccentrically with respect to the rotation center line O by being connected and fixed to the rotation shaft 33 of the electric motor 30. In FIG. 6, P represents the central axis of the eccentric shaft 19.
The planetary gear 22 is composed of an external gear whose tooth tip curved surface is on the outer peripheral side of the tooth bottom curved surface. The planetary gear 22 has a radius of curvature of the addendum curved surface that is smaller than the radius of curvature of the bottom curved surface of the sun gear 21, and the number of teeth of the planetary gear 22 is one less than the number of teeth of the sun gear 21. The planetary gear 22 meshes with the inner peripheral side of the sun gear 21 so as to be capable of planetary movement. A cylindrical hole 22 c is formed concentrically in the planetary gear 22, and one end portion of the eccentric shaft 19 is fitted to the cylindrical hole 22 c via a bearing 23 so as to be relatively rotatable. By this fitting, the eccentric shaft 19 and the rotation shaft 33 can rotate relative to the sprocket 11 in the advance angle direction X and the retard angle direction Y.

  The transmission rotating body 24 is formed in a circular flat plate shape, and both plate surfaces are arranged in a form perpendicular to the parallel line of the rotation center line O. Cylindrical engagement holes 24a are formed at a plurality of locations on the transmission rotator 24, and the engagement holes 24a are arranged around the rotation center line O at equal intervals. The planetary gear 22 disposed on the counter-rotating body side of the transmission rotating body 24 has an engaging protrusion 22d that protrudes in a columnar shape from a position facing each engaging hole 24a. The respective engagement protrusions 22d are arranged at equal intervals around the eccentric axis P of the eccentric shaft 19, and protrude into the opposing engagement holes 24a.

  In such a speed reduction mechanism 20, when no change occurs in the control torque transmitted from the rotary shaft 33 to the eccentric shaft 19, the planetary gear 22 maintains the meshing position with the sun gear 21 as the crankshaft rotates. The sprocket 11, the eccentric shaft 19, and the rotating shaft 33 rotate in the clockwise direction in FIG. 6. As a result, the engagement protrusion 22d presses the engagement hole 24a in the rotation direction, so that the transmission rotation body 24 together with the guide rotation body 25 is rotated around the rotation center line O while maintaining the rotation phase with respect to the sprocket 11. Rotate clockwise.

  When the control torque transmitted to the eccentric shaft 19 increases in the counterclockwise direction of FIG. 6, the planetary gear 22 rotates relative to the eccentric shaft 19 in the clockwise direction of FIG. The meshing position is changed. As a result, the force with which the engagement protrusion 22d presses the engagement hole 24a in the rotation direction increases, and thus the transmission rotation body 24 and the guide rotation body 25 rotate relative to the sprocket 11 in the advance angle direction X.

When the control torque transmitted to the eccentric shaft 19 increases in the clockwise direction in FIG. 6, the planetary gear 22 rotates relative to the eccentric shaft 19 in the counterclockwise direction in FIG. 6 due to the planetary movement of the planetary gear 22. The meshing position with the sun gear 21 is changed. As a result, the engaging protrusion 22d presses the engaging hole 24a in the counter-rotating direction, so that the transmission rotating body 24 and the guide rotating body 25 rotate relative to the sprocket 11 in the retarding direction Y.
As described above, in the present embodiment, the speed reduction mechanism 20 and the motion conversion mechanism 10 jointly constitute “changing means” described in the claims.

  Next, the characteristic operation of the valve timing adjusting apparatus 1 that deals with the foreign matter biting in the speed reduction mechanism 20 will be described with reference to the flowchart of FIG. This operation is periodically started when the ignition switch of the vehicle is turned on, and is forcibly terminated when the ignition switch is turned off.

In step S1, the control unit 38 initializes the counter N set in the microcomputer.
In step S <b> 2, energization of the coil 42 is controlled by the control unit 38 for a predetermined time, and a one-way control torque necessary for setting the shaft phase to the current target phase is applied to the rotating shaft 33.

In step S <b> 3, it is detected whether or not a foreign object has occurred in the speed reduction mechanism 20. Specifically, in the speed reduction mechanism 20, as shown in FIG. 1 (A), there is a possibility that foreign matter 100 such as dust is caught between the teeth 21a of the sun gear 21 and the teeth 22a of the planetary gear 22 at the meshing position. is there. When such foreign matter 100 is caught, the control torque and the load current of the coil 42 necessary for setting the shaft phase as the target phase increase, and the rotational speed of the rotary shaft 33 decreases. Therefore, in the present embodiment, the control unit 38 monitors at least one physical quantity of the load current of the coil 42 and the rotational speed of the rotary shaft 33, and the gears 21, 22 are changed based on the change state such as the change amount and change rate of the physical quantity. The biting of the foreign material 100 at the meshing position is indirectly detected. For the load current of the coil 42 and the rotational speed of the rotary shaft 33, the detection result by the sensor of the control unit 38 is used.
If no foreign object biting is detected in step S3, the operation is terminated. If foreign object biting is detected, the process proceeds to step S4.

In step S4, the control unit 38 counts up the counter N. In subsequent step S5, the control unit 38 determines whether or not the counter N has reached the set value N ₀ . The set value N ₀ can be set as appropriate, and is set to 10, for example.
If in step S5 the counter N is found not reached the set value N ₀ proceeds to step S6, if the counter N is determined to have reached the set value N _0, the process proceeds to step S7.

  In step S6, foreign matter removal control by the control unit 38 is performed. Specifically, in the speed reduction mechanism 20, as shown in FIG. 1 (A), the planetary gear 22 in which the teeth 22a are engaged with the teeth 21a of the sun gear 21 with the foreign object 100 interposed therebetween is caused to make a planetary movement in the opposite direction to that before the engagement. Thus, the meshing positions of the gears 21 and 22 can be changed. Assuming that the foreign object 100 is attached to the sun gear 21 side, when the planetary gear 22 advances in planetary motion, it adjoins the teeth 22a of the planetary gear 22 on the same pitch circle as shown in FIG. The teeth 21a of the sun gear 21 engage with the adjacent teeth 22b while sliding. Therefore, the foreign material 100 adhering to the tooth 21a is surely scraped off by the tooth 22b slidingly contacting the tooth 21a. On the other hand, when it is assumed that the foreign object 100 is attached to the planetary gear 22 side, when the planetary movement of the planetary gear 22 progresses, as shown in FIG. Thus, the teeth 22a of the planetary gear 22 mesh with the adjacent adjacent teeth 21b while sliding. Therefore, the foreign material 100 adhering to the teeth 22a is surely scraped off by the teeth 21b slidingly contacting the teeth 22a. As described above, in the present embodiment, one of the teeth 21a and 22a at the meshing position at the start of execution of step S6 is separated from the other tooth and meshes with the adjacent tooth of the other tooth, so that the latest step S2 A control torque opposite to that at the time of execution is applied to the rotating shaft 33. As a result, the planetary gear 22 performs planetary movement in the opposite direction to that in the recent execution of step S2, and the foreign matter 100 is removed by the above-described principle. After completion of execution of step S6, the process returns to step S2.

On the other hand, in step S7, it is determined that the valve timing adjusting device 1 cannot be normally operated due to the foreign matter in the deceleration mechanism 20, and the energization from the control unit 38 to all the coils 42 is stopped. At the same time, the occurrence of an abnormality in the valve timing adjusting device 1 is warned by, for example, a vehicle indicator, and the operation is terminated.
As described above, in the present embodiment, the control unit 38 constitutes the “detection means” in the claims, and the control unit 38 and the electric motor 30 together constitute the “torque transmission means” in the claims. Yes.

  According to the valve timing adjusting apparatus 1 described above, it is possible to engage at the meshing positions of the gears 21 and 22 only by applying to the rotating shaft 33 a control torque in the direction opposite to that at the time of execution of step S2 before the detection of the foreign object engagement. It is possible to reliably remove the foreign matter. Therefore, since the time required for removing the foreign matter can be shortened, the adjustment of the valve timing can be resumed promptly after detecting the foreign matter biting in step S3.

  Moreover, according to the valve timing adjusting device 1, since the control torque is generated by the electric motor 30, the control torque can be accurately controlled. Therefore, it becomes easy to limit the amount of change in the shaft phase that is changed by the execution of step S6 for removing foreign matter to a range that does not affect the operation of the engine, for example, 6 ° CA (Crank Angle).

Instead of the electric motor 30 described above, an electromagnetic brake is used that has a brake member and a solenoid that are rotated by transmitting the driving torque of the crankshaft and uses the braking torque generated in the brake member magnetically attracted by the solenoid as a control torque. May be.
Moreover, in the above-mentioned embodiment, the number of teeth of the planetary gear 22 is reduced by one from the number of teeth of the sun gear 21, and one of the teeth of the gears 21 and 22 meshing with a foreign object sandwiched from the other tooth. A control torque opposite to that before detecting the foreign object is applied to the rotating shaft 33 until it is engaged with a tooth that is separated from the other tooth and adjacent to the tooth on the same pitch circle, that is, one tooth away from the other tooth. Like to do. On the other hand, the number of teeth of the planetary gear 22 is reduced by N (N is a positive integer equal to or greater than 2) less than the number of teeth of the sun gear 21, and one of the teeth of the gears 21 and 22 meshing with a foreign object interposed therebetween. Until the tooth is separated from the other tooth and meshes with a tooth that is N pitches away from the other tooth on the same pitch circle as the other tooth, a control torque in the direction opposite to that before detection of foreign object biting is applied to the rotary shaft 33. You may make it give to.

It is a schematic diagram for demonstrating the action | operation of one Embodiment of this invention. It is a figure which shows one Embodiment of this invention, Comprising: It is the II-II sectional view taken on the line of FIG. It is a figure which shows one Embodiment of this invention, Comprising: It is the III-III sectional view taken on the line of FIG. It is a figure which shows one Embodiment of this invention, Comprising: It is the IV-IV sectional view taken on the line of FIG. It is a figure which shows one Embodiment of this invention, Comprising: It is the VV sectional view taken on the line of FIG. It is a figure which shows one Embodiment of this invention, Comprising: It is the VI-VI sectional view taken on the line of FIG. It is a flowchart for demonstrating the action | operation of one Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Valve timing adjustment apparatus, 2 Camshaft (driven shaft), 10 Motion conversion mechanism (change means), 20 Reduction mechanism (planetary gear mechanism, change means), 21 Sun gear, 21a, 21b Sun gear tooth, 22 Planetary gear , 22a, 22b, planetary gear teeth, 30 motor (torque transmission means), 38 control unit (detection means, torque transmission means), 42 coil, 100 foreign matter

Claims (2)

A valve timing adjusting device that is provided in a transmission system that transmits a driving torque of a drive shaft to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve in an internal combustion engine, and adjusts the opening / closing timing of the at least one valve. There,
Change means for changing a rotational phase of the driven shaft with respect to the drive shaft using a control torque transmitted to the planetary gear mechanism, the planetary gear having a planetary gear mechanism in which the planetary gear meshes with the sun gear so as to be capable of planetary movement; ,
Detecting means for detecting the intrusion of foreign matter at the meshing position of the sun gear and the planetary gear;
When the detection means detects the intrusion of foreign matter, one of the teeth of the sun gear and the planetary gear at the meshing position is separated from the other tooth and has the same pitch circle as the other tooth. Torque transmission means for transmitting the control torque in the opposite direction to that before detection of biting to the planetary gear mechanism until it meshes with the upper teeth;
A valve timing adjusting device comprising: 2. The valve timing adjusting device according to claim 1, wherein the torque transmission means generates the control torque by an electric motor.

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