JP2002227616A - Valve timing controller of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To increase the mountability of a vehicle engine as well as the control speed of a valve timing by lessening the axially occupied space of imposing angle adjusting mechanism. SOLUTION: Three sliding grooves 11a, 11b, 11c are formed along the axial direction at one end face of a timing sprocket 2, and each second guide ball 21 of three movable operation members 14 is slidably engaged in the each sliding groove. Each movable operation member 14 is connected with a cam shaft 1 via a link arm 15 and a lever member 12. Each first guide ball 20 of the movable operation member is engaged in the spiral guide groove 30 with the determined radius formed on the inner end face of a guide plate 23 the movable operation member is displaced in the axial direction by means of the rotation of the guide plate 23. The axial displacement of the movable operation member controls the valve timing by relative rotation of the timing sprocket and the cam shaft 1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve timing control apparatus for an internal combustion engine that changes the opening / closing timing of an intake or exhaust engine valve of the internal combustion engine in accordance with an operating condition.

[0002]

2. Description of the Related Art As a conventional valve timing control device, for example, one disclosed in Japanese Patent Application Laid-Open No. Hei 10-153104 is known.

[0003] In brief, this valve timing control device comprises a timing pulley (a driving rotary member) that is rotationally driven by a crankshaft of an engine, and an outer periphery of a shaft member (a driven rotary member) integrally connected to a camshaft. The timing pulley and the shaft member are connected to each other via an assembly angle adjusting mechanism. The assembling angle adjusting mechanism is formed on a piston member (movable operating member) attached to the timing pulley so as to be axially displaceable while restricting relative rotation, and formed on an inner peripheral surface of the piston member and an outer peripheral surface of the shaft member. And a helical gear that meshes with each other. adjust.

[0004]

However, this conventional valve timing control device has a structure in which the piston member (movable operating member) of the assembly angle adjusting mechanism is operated to advance and retreat along the axial direction of the camshaft. Because
The space occupied by the mounting angle adjusting mechanism in the axial direction at the end of the camshaft is increased, and the shaft length of the engine is lengthened, which deteriorates the mountability of the vehicle. In particular, in order to change the operation position of the piston member by the electromagnet, the electromagnet must be disposed further axially outside the advance / retreat position of the piston member. It was not possible to mount the engine.

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a valve timing control device for an internal combustion engine that can reduce the space occupied in the axial direction of an assembly angle adjusting mechanism and improve the mountability on a vehicle.

[0006]

Means for Solving the Problems As means for solving the above-mentioned problems, the present invention according to the first aspect of the present invention is directed to a driving rotating body that is driven to rotate by a crankshaft of an engine and a coaxial with respect to the driving rotating body. A driven rotator provided rotatably relative to the upper rotator, and an assembling angle adjusting mechanism having a movable operation member movable in a radial direction of both rotators, and the assembling angle adjustment is performed according to an engine operating state. A valve timing control device for an internal combustion engine that variably controls a relative rotational phase of the two rotating bodies by operating a mechanism, wherein one of the driving rotating body and the driven rotating body has a radial direction of the two rotating bodies. The guide ball is a projection provided on the movable operation member on one of the driving rotating body and the driven rotating body, while guiding the movable operating member by the radial guiding section. A guide plate having a spiral guide groove that engages and the spiral guide groove,
A plurality of guide plates are formed on the inner end face of the guide plate, and the guide plate is rotated with respect to a driving rotator and a driven rotator to move the movable member through movement of a guide ball in the plurality of spiral guide grooves. The operation member is moved in the radial direction.

Accordingly, the movable operation member is moved along the radial direction of the driving rotary member and the driven rotary member, so that the space occupied by the movable operating member in the axial direction can be reduced.

In addition, the radial movement of the movable operation member is
Since the rotation is performed through the plurality of spiral guide grooves of the guide plate, it is possible to obtain a large relative rotation phase change with respect to a small relative rotation between the driving rotating body and the driven rotating body.

The invention according to claim 2 is characterized in that the movable operation member is provided one for each of the spiral guide grooves.

According to the present invention, each movable operation member is provided, for example, in each of a plurality of spiral guide grooves having substantially the same shape, thereby sharing each component such as a link of each movable operation member. can do.

The invention according to claim 3 is characterized in that one end or the other end in the longitudinal direction of another spiral guide groove is disposed inside the one spiral guide groove.

According to the present invention, since the lengths of the spiral guide grooves can be made relatively long by overlapping the spiral guide grooves with each other, the relative rotation phase can be smoothly changed. Can control.

The invention according to a fourth aspect is characterized in that the curvatures of the plurality of spiral guide grooves are arbitrarily set.

The invention according to claim 5 is characterized in that the curvature of each spiral guide groove is partially changed at a predetermined position in the longitudinal direction.

The invention according to claim 6 is characterized in that both ends of the spiral guide groove in the longitudinal direction are configured as stoppers for regulating the maximum radial movement position of the movable operation member.

The invention according to claim 7 is characterized in that the bottom surfaces at both ends of the spiral guide groove are formed in a gentle rising taper shape.

According to the present invention, the guide plate and the driving rotator or driven rotator are connected via a spring member, and the guide plate is urged in one rotation direction by the spring member. An electromagnet faces the outer peripheral end surface of the guide plate, and imparts rotational resistance to the guide plate by the magnetic force of the electromagnet, thereby causing the guide plate to move in the other rotational direction against the spring force of the spring member. It is characterized by being biased.

[0018]

FIG. 1 shows an embodiment in which a valve timing control device for an internal combustion engine according to the present invention is applied to an intake valve side. Note that the present invention is not limited to the intake valve side, and can be similarly applied to the exhaust valve side.

The valve timing control apparatus includes a camshaft 1 rotatably supported by a cylinder head of an engine and having a cam (not shown) on an outer periphery for opening an intake valve, and a front end of the camshaft 1. A timing sprocket 3 rotatably mounted on a stepped-diameter cylindrical retainer 2 fixed to the engine, and rotationally driven by a crankshaft (not shown) of the engine; and front ends of the retainer 2 and the timing sprocket 3 Placed between clubs,
An assembling angle adjusting mechanism 4 for variably adjusting an assembling angle between the camshaft 1 and the timing sprocket 3, and a peripheral part of the assembling angle adjusting mechanism 4 which is mounted across the cylinder head 5 and a front end face of a rocker cover (not shown). A VTC cover 6 surrounding the area,
A controller 7 for controlling the assembly angle adjusting mechanism 4 in accordance with the operating state of the engine. In this embodiment, the driving rotator is constituted by the timing sprocket 3 and the driven rotator is constituted by the camshaft 1 and the retainer 2.
It is constituted by.

As shown in FIG. 1, the timing sprocket 3 has a disk-shaped base 3a through which the retainer 2 is inserted at the center, an outer peripheral portion of the base 3a, and an axial protrusion from the side of the base 3a. Each tooth 9a provided on the projected portion 8
The other end of the drive and driven tune, one end of which is wound around the drive sprocket of the crankshaft (not shown) and the driven sprocket of the exhaust side camshaft, respectively, is wound around each tooth 9a, 9b. It has become. In addition, a disc-shaped protruding wall 10 is integrally formed at the front end of the base 3a, and the protruding wall 10 has a radial guide portion on its end face, as shown in FIGS. Sliding groove 1
1a, 11b and 11c are formed along the radial direction. The sliding grooves 11 a, 11 b, 11 c are formed in a substantially arc shape in cross section, and are radially arranged at a position of about 120 degrees in the circumferential direction with respect to each other. And each sliding groove 11
The movable operation member 14 is guided in the radial direction by a, 11b, and 11c.

As shown in FIGS. 1 and 2, the assembling angle adjusting mechanism 4 is axially coupled to the end of the retainer 2 and radiates to the outer periphery corresponding to the sliding grooves 11a, 11b and 11c. A lever member 12 having three arm portions 13, 13, 13 extending in the direction, and the respective sliding grooves 11a, 11
b, 11c, three movable operating members slidably engaged with each other, one end of which is integrally connected to the base end of each movable operating member 14, and the other end of which is connected to each of the arms. Part 13
Linear link arm 15, 1 connected to the tip of
5, 15 and the movable operation members 14
Operating mechanism 16 that moves forward and backward based on a control signal from
And is mainly constituted by

The lever member 12 has a cylindrical base end 12a.
Each of the arm portions 13 is protruded at an angular position of about 120 degrees in the circumferential direction, and one end of the base 12a is fitted to the tip of the retainer 2, and the camshaft is 1 are fixed together in the axial direction. The lever member 12 is connected to each arm 1
A slit 13a is formed substantially at the center of the slot 3, and the other end of each link arm 16 is rotatably connected to each other through each pin 18, 18, 18 in each slit 13a. A positioning pin 19 is fitted to the lever member 12 and the camshaft 1.
Thus, accurate positioning of both is performed.

Each movable operation member 14 is shown in FIGS.
As shown in FIG. 5, substantially annular sliding portions 14b and 14c, which are back to back, are slidably housed in the hollow interior of the cylindrical portion 14a, and are formed on the outer surfaces of the sliding portions 14b and 14c. Each of the sliding grooves 11a,
A first guide ball 20 and a second guide ball 21 which are projections which roll by engaging with spiral guide grooves 30, 30 and 30 of a guide plate 23 which will be described later.
Are held so that they can roll freely. The two sliding portions 14b, 14c are connected to the respective guide grooves 20, 21 by the spring force of the respective coil springs 22 interposed therebetween, and the respective sliding grooves 11a, 11b, 11c to the respective spiral guide grooves. It is urged in 30 directions.

Therefore, when each movable operating member 14 is displaced in the radial direction along each of the sliding grooves 11a, 11b, 11c, the timing sprocket 3 and the camshaft 1 are moved by each link arm 15 by the action of each link arm 15. Are relatively rotated by an angle corresponding to the displacement of.

On the other hand, as shown in FIGS. 1 and 4, the operating mechanism 16 is disposed opposite to the protruding wall 10 of the timing sprocket 3 with each movable operating member 14 interposed therebetween. A substantially disk-shaped guide plate 23 for radially displacing the
3, a metal annular wall 25 fixed to the front end portion by bolts 24, and a spiral spring 26 radially expandable and contractible in an annular gap C between the annular wall 25 and the guide plate 23. And an electromagnet 2 for urging the guide plate 23 in the other rotation direction (the direction opposite to the rotation direction of the timing sprocket 3) by applying a magnetic force to the annular wall 25.
8 is provided.

The guide plate 23 is shown in FIGS.
As shown in FIG. 2, a cylindrical support portion 12b integrally extending forward of the cylindrical base portion 12a of the lever portion 12 is inserted through the central insertion hole 23a with a predetermined clearance, and is projected from the other end surface. The cylindrical part 23b and the cylindrical support part 12
In addition to being rotatably supported by a ball bearing 29 provided on the outer periphery of b, three spiral guide grooves 30, 30, 30 are formed on one end surface thereof. The guide plate 23 has a ring member 31 screwed to the outer periphery of the distal end of the cylindrical support portion 12b.
Nine inner races are positioned in the axial direction by pressing them in the axial direction.

Each of the spiral guide grooves 30 is formed in a spiral shape in the same direction from the outer end 30a provided at a position of about 120 degrees in the circumferential direction of the guide plate 23 toward the center. The inner end portions 30b on the center side are arranged near the insertion holes 23a at the center of the guide plate 23, and are set to the same length. The spiral guide grooves 30 are arranged close to the inner and outer peripheries of each other, and the adjacent ones are located between the respective inner and outer ends 30a and 30b. , 30b are located.
The curvature of each spiral guide groove 30 is arbitrarily set, and in this embodiment, the curvature is set to be uniform from the outer end 30a to the inner end 30b. Further, as shown in FIG. 5, each of the inner and outer ends 30a, 30b has a bottom surface 30c. 30d is formed in a tapered shape so as to gradually increase from the bottom surface on the center side toward each edge side, thereby exhibiting a stopper function.

Therefore, when the guide plate 23 rotates in the opposite direction to the timing sprocket 3 in a state where the first guide ball 20 of each movable operation member 14 is engaged with the spiral guide groove 30, each movable operation member 14 At this time, it is configured to move radially inward along the spiral shape of each spiral guide groove 30 of the guide plate 23.

As shown in FIG. 1, one end 26a of the spiral spring 26 has a cylindrical portion 2 of the guide plate 23.
3b, while the other end 26b is bolted in the axial direction from the outer peripheral side of the timing sprocket 3.
It is fixed to the fixed locking member 32 by a bolt 33.

The electromagnet 28 is mounted on the VTC cover 6 so as to face the outer end face of the annular wall 25 in the axial direction, and is energized or deenergized by a control signal from the controller 7. It is designed to be de-energized. The controller 7 detects a current engine operating state based on an engine speed by a crank angle sensor, an engine load by an air flow meter or the like, and information signals from various sensors such as a water temperature sensor and a throttle valve opening sensor. It has become.

In the following, the operation of the present embodiment will be described. First, at the time of starting the engine and idling, the energization of the electromagnet 28 is turned off by a control signal from the controller 7, and as a result, the guide plate 23 The timing sprocket 3 is urged in the same direction as the rotation of the timing sprocket 3 only by the spring force 26. Thereby, the guide plate 23
The guide balls 20 of the movable operation member 14 are pressed against the outer end portions 30a of the spiral guide grooves 30, and further rotation is regulated, and the initial position is maintained. Accordingly, each movable operation member 14 is in a state of being maximally displaced radially outward as shown in FIGS. 1 and 2, and a cam connected to each movable operation member 14 via the link arm 15 and the lever member 12. The shaft 1 is maintained at the most retarded angle with respect to the timing sprocket 3.

Therefore, at this time, the rotational phase of the crankshaft and the camshaft 1 is controlled to the most retarded side,
Stabilization of engine rotation and improvement of fuel efficiency can be achieved.

Further, when the engine shifts to the normal operation, the energization of the electromagnet 28 is turned on by a control signal from the controller 7, and the electromagnet 28 generates a magnetic force for imparting rotational resistance to the guide plate 23. This allows
The rotation of the guide plate 23, which rotates following the timing sprocket 3 via the spiral spring 26, is hindered. This guide plate 23 resists the spring force of the spiral spring 26 and biases the rotation of the timing sprocket 3 in the direction opposite to the rotation of the timing sprocket 3. Then, the guide ball 20 of each movable operation member 14 is pressed against the inner end portion 30b of each spiral guide groove 30 and is relatively rotated with respect to the timing sprocket 3 until it is regulated.

At this time, in each of the movable operation members 14, the first guide balls 20 roll along the groove surfaces of the spiral guide grooves 30, and the second guide balls 21 on the opposite side are used for both sliding. It moves straight radially inward along the grooves 11a, 11b, 11c. Then, when the connection point (each pin 18) on the base end side of the link arm 15 moves radially inward as the movable operation member 14 moves radially inward,
The distal end of the link arm 15 also attempts to move following the movement. At this time, the proximal end of the link arm 15 is
Since the lever member 12 is connected to each arm portion 13 of the lever member 12, the lever member 12 moves in an arc while rotating the lever member 12. As a result, the angle at which the timing sprocket 3 and the camshaft 1 are assembled is adjusted and changed to the most advanced state.

Therefore, at this time, the rotational phase of the crankshaft and the camshaft 1 is controlled to the most advanced side, and the output of the engine can be increased.

The control of the rotational phase of the crankshaft and the camshaft 1 is not limited to switching between two positions on the retard side and the advance side, but can be continuously performed at an arbitrary rotational phase by appropriately adjusting the magnetic force generated by the electromagnet 28. It is also possible to control it.

As described above, the movable operation member 14 is displaced in the radial direction of the timing sprocket 3 along each of the sliding grooves 11a, 11b, 11c, and the displacement of the movable operation member 14 in the radial direction is reduced. Since the rotation is converted into relative rotation between the timing sprocket 3 and the camshaft 1 through a link mechanism using the link arm 15 and the lever member 12, a reliable phase is obtained by a compact structure that does not occupy a large space in the axial direction. Control can be performed.

The radial operation of each movable operation member 14 is also performed by engaging each spiral guide groove 30 of the guide plate 23 with the first guide ball 20 of the movable operation member 14. These operating mechanisms do not significantly increase the space occupied in the axial direction.

In the case of this device, the spiral spring 26 is employed as a spring member for connecting the timing sprocket 3 and the guide plate 23, and the spiral spring 2
6 is arranged between the guide plate 23 and the annular wall 25, so that the spring member does not increase the axial length of the device.

Therefore, from these facts, the electromagnet 28
The shaft length of the entire apparatus including the above is greatly reduced as compared with the conventional apparatus, and the mountability of the engine on the vehicle is reliably improved.

In addition, in this device, the spiral guide groove 30 of the guide plate 23 and the first guide ball 20 of the movable operation member 14 are engaged to rotate the guide plate 23 in the radial direction of the movable operation member 14. , The outer end 30a of the spiral guide groove 30
By setting the curvature of the circular arc portion from the inner end portion 30b to the inner end portion 30b to be small, the relative rotation change can be increased with respect to a small relative rotation amount between the timing sprocket 3 and the camshaft 1. As a result, the outer diameter of the device can be made sufficiently small, and the size of the entire device can be reduced in combination with the downsizing in the axial direction.

Further, as described above, the spiral guide groove 3
By setting the curvature of the arc portion from the outer end portion 30a to the inner end portion 30b to be small, it is possible to avoid a problem that the guide plate 23 is rotated by a load input from the movable operation member 14 side. That is, for example, the problem that the guide plate 23 rotates and fluctuates due to the fluctuation torque input to the camshaft 1 due to the spring force of the valve spring of the intake valve during the operation of the engine,
The control of the valve timing is also completed promptly.

Further, since the shape of each of the spiral guide grooves 30 is set to be the same, and one movable operation member 14 is provided for each of the spiral guide grooves 30, the shape and size of the movable operation member 14 are set. Sasato link arm 15
Can be all the same in length. For this reason, each component can be shared, and the manufacturing cost can be reduced.

Furthermore, since the curvature of the arc portion of the spiral guide groove 30 can be set arbitrarily,
For example, if the curvature is adjusted to the valve lift condition of the intake valve, it is possible to increase the speed of the relative rotation phase conversion regardless of the relative rotation speed between the timing sprocket 3 and the camshaft 1. As a result, the engine performance can be improved.

Since the inner and outer ends 30a and 30b of the spiral guide groove 30 function as stoppers for restricting the maximum rotation of the guide plate 23, there is no need to provide a separate stopper mechanism. As a result, an increase in the number of parts can be suppressed, so that the efficiency of manufacturing operation can be improved and a rise in cost can be suppressed.

Further, since the bottom surfaces 30c and 30d of the inner and outer ends 30a and 30b are formed in a tapered shape, a damper effect is exerted by frictional resistance with the first guide ball 20 in the rotation end region of the guide plate 23. As a result, an abrupt rotation stop action is avoided, and a smooth stop action is obtained. Further, since all of the inner and outer ends 30a and 30b are formed in a tapered shape, the load at the time of stopping received from each of the first guide balls 20 is dispersed, and from this point, a smooth stopping action is further promoted. it can.

If the curvature of each of the inner and outer ends 30a and 30b is set to, for example, a curvature substantially equal to the outer peripheral edge of the guide plate 23, that is, if the curvature is partially set to be small, a stable stopper function is exhibited. be able to.

Further, in this device, since the rotation of the guide plate 23 with respect to the timing sprocket 3 is controlled by the spring force of the spiral spring 26 and the magnetic force of the electromagnet 28, the control is performed using the oil pressure of the oil pump. It is not necessary to be affected by the engine operating speed as compared with the case. Therefore, the valve timing control can be completed quickly regardless of the operating state of the engine. Further, since the spring force of the spiral spring 26 is set in a direction to control the valve timing to the retard side, even if the electromagnet 28 breaks down, the start of the engine is guaranteed.

The number of movable operation members 14 is arbitrary as long as it is two or more. However, if a plurality of movable operation members 14 are provided as in this embodiment, the stress applied to one movable operation member 14 is reduced. The durability of the device is improved.

The present invention is not limited to the configuration of the above embodiment. For example, the number of spiral guide grooves 30 can be further increased, and the curvature thereof can be changed in the middle. is there. As described above, by changing the curvature in the middle, the operation of the movable operation member 14 can be stably held at the changed position. For example, if the curvature is changed in accordance with a steady operation region such as an engine middle rotation middle load, etc. Thus, stable control of the valve timing at this time can be performed.

Further, the rotation urging means of the guide plate 23 may be constituted by, for example, another electromagnet instead of the spiral spring 26.

[0052]

As described above, the invention according to claim 1 is
Since the movable operation member of the mounting angle adjusting mechanism is installed so that the moving direction thereof is along the radial direction of the driving rotary member and the driven rotary member, the space occupied by the mounting angle adjusting mechanism in the engine axial direction is reduced, and as a result, In addition, vehicle mountability is improved.

Moreover, the movement of the movable operation member in the radial direction is
Since the rotation is performed through a plurality of spiral guide grooves of the guide plate, by reducing the curvature of the spiral guide groove, a large relative rotation phase change is obtained with respect to a small relative rotation between the driving rotating body and the driven rotating body. Can be obtained.

According to the second aspect of the present invention, each movable operation member is provided, for example, for each of a plurality of spiral guide grooves having substantially the same shape, so that each of the movable operation members such as a link of each movable operation member is provided. Components can be shared. As a result, manufacturing costs can be reduced.

According to the third aspect of the present invention, the spiral guide grooves overlap each other,
Since the length of each spiral guide groove can be made relatively long, it is possible to control the relative rotation phase to change smoothly.

According to the fourth aspect of the present invention, the curvature of the plurality of spiral guide grooves is set arbitrarily,
It is possible to freely set the valve timing according to the specifications and characteristics of the engine or the operating state.

According to the fifth aspect of the present invention, since the movable operation member 14 can be stably stopped at a portion where the curvature is partially changed, stable valve timing control in a desired operation region can be obtained. Can be

According to the sixth aspect of the present invention, since both ends of the spiral guide groove are formed as stoppers, it is not necessary to separately provide a stopper mechanism, and an increase in the number of parts is prevented, thereby reducing the manufacturing work efficiency. Improvement and cost reduction can be achieved.

According to the seventh aspect of the invention, the damper effect due to the frictional resistance with the movable operation member in the rotation end region of the guide plate is exerted, so that a rapid rotation stop operation is avoided, and a smooth stop operation is achieved. Is obtained.

When all of the inner and outer ends are formed in a tapered shape, the load at the time of stopping received from each movable operation member is dispersed, and from this point, a smooth stopping action can be further promoted.

According to the eighth aspect of the present invention, the rotation of the rotating guide plate can be reliably controlled by a simple structure using the spring member and the electromagnet.
Unlike the case where a hydraulic pump or the like that rotates by the power of the engine is used, the rotation phase of the crankshaft and the camshaft can always be quickly changed regardless of the engine operating speed or the like.

Even if the electromagnet is arranged on an extension of the camshaft in the axial direction, since the movable direction of the movable operation member is radial, the overall axial length does not increase so much. This makes it possible to mount it on a vehicle for which it is difficult to secure the axial length.

[Brief description of the drawings]

FIG. 1 is a sectional view taken along line AA of FIG. 2 showing an embodiment of the present invention.

FIG. 2 is an exemplary sectional view of the embodiment, taken along line BB of FIG. 1;

FIG. 3 is a sectional view taken along the line CC of FIG. 1;

FIG. 4 is a sectional view taken along the line DD of FIG. 1;

FIG. 5 is a sectional view taken along the line EE in FIG. 4;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Camshaft (driven rotary body) 3 ... Timing sprocket (drive rotary body) 4 ... Assembly angle adjustment mechanism 11a, 11b, 11c ... Sliding groove (radial guide part) 14 ... Movable operating member 15 ... Link arm ( 20) 21 guide ball 23 guide plate 26 spiral spring (spring member) 28 electromagnet 30 spiral guide groove

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3G018 BA32 CA12 DA29 DA36 DA71 DA85 EA02 EA11 EA12 EA16 EA17 EA21 EA31 EA32 GA04 GA14

Claims (8)

[Claims] 1. A driving rotating body that is driven to rotate by a crankshaft of an engine, a driven rotating body that is provided coaxially and relatively rotatable with respect to the driving rotating body, and is movable along a radial direction of both rotating bodies. Valve timing control for an internal combustion engine, comprising: an assembly angle adjustment mechanism having a movable operating member that performs a variable control of the relative rotational phase of the two rotating bodies by operating the assembly angle adjustment mechanism according to the engine operating state. An apparatus, wherein one of the driving rotator and the driven rotator is provided with a radial guide portion along a radial direction of the both rotators, and the movable operation member is guided by the radial guide portion, A guide plate having a spiral guide groove into which the protrusion of the movable operation member is engaged is provided on one of the drive rotary body and the driven rotary body, and the spiral guide groove is provided with the guide. The guide plate is formed in a plurality of rows on the inner end face, and the guide plate is rotated with respect to the driving rotary body and the driven rotary body, so that a movable operation is performed through the movement of the protrusion in the plurality of spiral guide grooves. A valve timing control device for an internal combustion engine, wherein a member is moved in a radial direction. 2. The valve timing control device for an internal combustion engine according to claim 1, wherein one of said movable operation members is provided for each of said spiral guide grooves. 3. The internal combustion engine according to claim 1, wherein one end or the other end in the longitudinal direction of another spiral guide groove is disposed inside the one spiral guide groove. Engine valve timing control device. 4. The valve timing control device for an internal combustion engine according to claim 1, wherein the curvatures of the plurality of spiral guide grooves are arbitrarily set. 5. The valve timing control device for an internal combustion engine according to claim 1, wherein the curvature of each spiral guide groove is partially changed at a predetermined position in a longitudinal direction. . 6. The device according to claim 1, wherein both ends of the spiral guide groove in the longitudinal direction are configured as stoppers for regulating a maximum radial movement position of the movable operation member.
6. The valve timing control device for an internal combustion engine according to any one of claims 1 to 5. 7. The valve timing control device for an internal combustion engine according to claim 6, wherein the bottom surfaces at both ends of the spiral guide groove are formed in a gentle rising taper shape. 8. The guide plate and the driving rotator or the driven rotator are connected via a spring member, and the spring member urges the guide plate in one rotation direction, and simultaneously connects an electromagnet to the guide plate. The guide plate is biased in the other rotational direction against the spring force of the spring member by facing the outer peripheral side end surface and imparting rotational resistance to the guide plate by the magnetic force of the electromagnet. The valve timing control device for an internal combustion engine according to claim 7, wherein