JP2002227893A - Electromagnetic brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a stable braking force without being affected by fluctuation in an axial direction of a rotor. SOLUTION: A yoke 55 is arranged to an outer peripheral side of a cylinder part 26 of a guide plate 24 such that input and output ends 59a, 59b of a magnetism face to an outer peripheral surface of the cylinder part 26. Even when the guide plate 24 fluctuates in the axial direction, since a distance between the yoke 55 and the cylinder part 26 is not changed, the braking force does not fluctuate.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electromagnetic brake device for controlling rotation of a rotating body by applying a braking force to the rotating body.

[0002]

2. Description of the Related Art As a valve timing control device for an internal combustion engine, a device described in, for example, Japanese Patent Application Laid-Open No. 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 coaxially arranged on the side, and are connected to each other via an assembly angle operation mechanism. The assembling angle operating mechanism is formed on a piston member (movable operating member) attached to the timing pulley so as to be axially displaceable in a state where relative rotation is regulated, and 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.The piston member is appropriately advanced and retracted in the axial direction by a control mechanism having an electromagnetic brake and a return spring, so that the angle at which the timing pulley and the shaft member are assembled can be adjusted by the helical gear. Adjust through.

Further, the apparatus is provided with a drum as an intermediate rotating body which is rotatable relative to a timing pulley and a shaft member, and the relative rotation of the drum and the timing pulley is changed by an axial displacement of the piston member. A conversion mechanism including a helical gear mechanism for conversion is provided.
The return spring of the control mechanism urges the drum against the timing pulley in the speed increasing rotation direction, and the electromagnetic brake applies a braking force by the electromagnetic force to the front end surface of the drum in the axial direction. Causes the drum to rotate relative to the deceleration side. Therefore, when the energization of the electromagnetic brake is turned off, the assembly angle is changed to one of the retard side and the advance side by the force of the return spring, and when the energization is turned on, the assembly angle is changed by the braking force of the electromagnetic brake. The angle can be changed to the other side.

[0005]

The electromagnetic brake used in this valve timing control device is a rotating body (drum).
, The braking force becomes unstable due to the axial displacement of the rotating body, and it is difficult to obtain highly accurate braking. In other words, the rotation of the rotating body can be suppressed with a certain degree of accuracy in the radial direction by the support shaft, but it is difficult to suppress the deflection in the axial direction with a high accuracy. Then, when this axial deflection occurs in the rotating body, the air gap between the electromagnetic brake and the rotating body greatly changes, and the change in the air gap changes the magnetic flux and makes the braking force unstable.

In particular, when used in the valve timing control device as described above, the rotational axis tends to fluctuate in the axial direction due to engine vibration, reaction force from the camshaft, and the like, and the braking accuracy is reduced due to the axial fluctuation. It is feared that it will decrease.

Accordingly, an object of the present invention is to provide a brake device which is hardly affected by fluctuations in the axial direction of a rotating body and which can always obtain a stable braking force.

[0008]

According to the present invention, as a means for solving the above-mentioned problems, a yoke forming a path of a magnetic flux generated by a coil faces an end face serving as a magnetic input / output end to a rotating body made of a magnetic material. In the electromagnetic brake, which is arranged so as to brake the rotating body by a magnetic force acting on the rotating body from the end face of the yoke, the yoke is moved to the outer circumferential side of the rotating body such that the magnetic input / output end faces the outer circumferential surface of the rotating body. It was arranged in. Therefore, according to the present invention, even when the rotating body fluctuates in the axial direction, the distance between the magnetic input / output end of the yoke and the rotating body does not change.

The yoke may be constituted by a plurality of pieces divided in the circumferential direction, and the pieces may be brought into contact with and separated from the rotating body by turning on / off the energization of the coil. In this case, when the energization of the coil is turned on, each piece of the yoke comes into contact with the rotating body to eliminate the air gap, a large braking action by the electromagnetic force acts on the rotating body, and when the energization is turned off, The contact resistance of each piece does not act on the rotating body.

At this time, by providing an urging means for urging the pieces of the yoke so as to separate them radially outward with respect to the rotating body, each piece can be applied to the rotating body when the power is turned off. In this way, it is possible to reliably separate them.

Further, the yoke may be attached to the base member via a displacement absorbing mechanism for absorbing displacement in the radial direction. In this case, when the base member is attached to the installation member of the rotating body, the positional displacement of the yoke and the rotating body in the radial direction due to each assembly error between the base member and the yoke, and the installation member and the rotating body is absorbed, thereby facilitating the installation work. It is possible to do.

Further, a lubricating oil supply structure may be provided between the yoke and the rotating body. In this case, the heat generated in the yoke can be cooled by the lubricating oil.
When the yoke is brought into contact with the rotating body, the sliding resistance can be reduced.

As a structure for supplying the lubricating oil, the rotating body may be provided with a lubricating oil passage extending from the radially inner side to the inner peripheral surface of the yoke. At this time, the lubricating oil is efficiently supplied between the yoke and the rotating body by the centrifugal force acting on the rotating body.

Further, if auxiliary equipment is arranged inside the rotating body, the space inside the rotating body can be effectively used, and the size of the apparatus can be reduced.

Further, the yoke may be formed in an annular shape, and the rotating body may be supported on the inner peripheral surface. In this case, a dedicated bearing for bearing the rotating body can be eliminated or reduced, and the manufacturing cost can be reduced.

Further, the magnetic input / output ends of the yoke are arranged so as to face the outer peripheral surface of the rotating body on both sides in the axial direction, and the magnetic input / output ends are extended inward in the axial direction so as to approach each other. Is also good. In this case, it is possible to increase the area of the magnetic input / output end facing the outer peripheral surface of the rotating body,
It is possible to secure a larger braking force.

In the electromagnetic brake according to the present invention, a driving rotating body that is driven to rotate by a crankshaft of an internal combustion engine and a driven rotating body that is a separate member connected to the camshaft or the shaft are connected via an assembling angle operating mechanism. In the valve timing control device for an internal combustion engine, which is coaxially coupled and variably controls the rotational phases of the crankshaft and the camshaft by operating the assembly angle operating mechanism according to the engine operating condition, the assembly angle operating mechanism is operated. It can be used for applying a braking force to the intermediate rotating body for causing the rotation. In this case, since the electromagnetic brake is hardly affected by the axial vibration of the engine or the like, stable valve timing control can be realized.

In this case, the valve timing control device can reduce the operating resistance of the movable operation member by connecting the intermediate rotating body to the movable operation member of the assembly angle operation mechanism via a ball. Therefore, a reliable braking action can be applied to the intermediate rotating body only by the electromagnetic force without using a friction material.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS First, a first embodiment shown in FIGS. 1 to 7 will be described. In this embodiment, the electromagnetic brake 50 according to the present invention is applied to a valve timing control device for an internal combustion engine. Although the valve timing control device of this embodiment is applied to the intake valve side of the internal combustion engine, it can also be applied to the exhaust valve side.

The valve timing control device includes a camshaft 1 (a driven rotary member) rotatably supported by a cylinder head of an engine and having a cam (not shown) for driving an intake valve on the outer periphery thereof. A disk-shaped drive plate 2 (drive rotator) rotatably assembled and disposed at the front end of the shaft 1, and is formed on the outer periphery of the drive plate 2 and is rotationally driven by a crankshaft (not shown) of the engine. A timing sprocket 3, an assembling angle operating mechanism 4 arranged on the front end side of the camshaft 1 and the driving plate 2 for operating an assembling angle of the shaft 1 and the driving plate 2, and an assembling angle operating mechanism 4 An actuating device 15 for driving operation, and a VT attached to the block of the engine and surrounding the drive plate 2, the assembling angle operating mechanism 4, and the front surface and peripheral region of the actuating device 15
C cover 6 (a base member on which the electromagnetic brake 50 according to the present invention is mounted) and the operating device 1 according to the operating condition of the engine
And a controller 7 for controlling the controller 5.

A spacer 8 having a locking flange 8a is integrally attached to the front end of the camshaft 1. The driving plate 2 is restricted in axial displacement by the locking flange 8a. It is rotatably arranged around the spacer 8.

On the front surface (left surface in FIG. 1) of the drive plate 2, three radial guides 10 composed of a pair of parallel guide walls 9a and 9b as shown in FIGS. It is attached at equal intervals and substantially along the radial direction of the plate 2, and between the guide walls 9 a and 9 b of each of the radial guides 10, an assembling angle operating mechanism 4 described later is provided.
Of movable operation members 11 are slidably assembled.

The assembling angle operating mechanism 4 has three levers 12 which are arranged at equal intervals in the circumferential direction and extend in the radial direction, and the bolts 18 are attached to the shaft center of the camshaft 1 together with the spacer 8. A fixed lever shaft 13;
A movable member 11 having a substantially square shape slidably engaged with each radial guide 10;
And an arcuate link arm 14 for pivotally connecting the movable operation members 11 one by one.
In the figure, reference numeral 16 denotes a base end of each link arm 14 and the lever 12.
Reference numeral 17 denotes a pin for connecting the distal end of each link arm 14 and the movable operation member 11.

When each movable operation member 11 is guided substantially radially by the radial guide 10 as described above, each link 12 of the link arm 14 and the lever shaft 13 is moved.
When each movable operation member 11 is displaced along the radial guide 10 by receiving an external force, the driving plate 2 (timing sprocket) is linked by the link arm 14 and the lever 12. 3) and the camshaft 1 relatively rotates by a direction and an angle corresponding to the displacement of the movable operation member 11.

At predetermined positions on the front side of each movable operation member 11, hemispherical concave portions 21 and 21A are provided in a radial direction, and each of the concave portions 21 and 21A has a ball 22 as a rolling member. , 22A are rotatably accommodated and held so that approximately half of them protrude forward.

The operating device 15 has a guide plate 24 (an intermediate rotating body in the present invention) rotatably supported via a bearing 23 on a spacer ring 19 attached to the front end of the lever shaft 13. Plate 2
When the drive plate 2 and the drive plate 2 rotate relative to each other, an operation conversion mechanism 40 for radially operating the movable operation member 11 in a direction and an amount corresponding to the relative rotation direction and the rotation angle, and a spring for initial position biasing 25 and an acceleration / deceleration mechanism 41 for increasing / decelerating the rotation of the guide plate 24 by the electromagnetic brake 50 according to the present invention.

The operation conversion mechanism 40 is provided with the movable operation member 1.
1 and the guide plate 24. The guide plate 24 has a spiral groove 28 having a substantially semicircular cross section on the rear surface side, and the spheres 22 and 22A held by the movable operation members 11 are engaged with the spiral groove 28. I have. The spiral of the spiral groove 28 is formed as shown in FIG.
The spiral groove 28 is shown only at the center line. The guide plate 24 is delayed with respect to the drive plate 2 while the ball 22 of the movable operation member 11 is engaged with the spiral groove 28 because the diameter of the drive plate 2 is gradually reduced along the rotation direction R of the drive plate 2. In this case, the movable operation member 11 moves radially inward along the spiral shape of the spiral groove 28 at this time. Conversely, when the guide plate 24 relatively rotates in the advance direction from this state, the movable operation member 11 moves radially outward along the spiral shape of the spiral groove 28.

The spring 25 is provided with a guide plate 24.
Are housed inside a cylindrical portion 26 projecting from the front end of the cylindrical portion. The diameter of the cylindrical portion 26 is reduced in a stepped manner with respect to the disk-shaped portion in which the spiral groove 28 is formed. The inner end of the spring 25 is connected to the camshaft 1.
Is inserted and locked on the outer surface of a spacer ring 19 integrally connected with the lever shaft 13, and the outer end is locked on the cylindrical portion 26 of the guide plate 24 by a pin 53. The biasing force of the mainspring 25 causes the rotation of the guide plate 24 to rotate relative to the lever shaft 13 (camshaft 1).
It acts to advance in the direction (increase the speed).

The electromagnetic brake 50 has a substantially annular magnetic generating portion including a coil 54 and a yoke 55, and is attached to a VTC cover so as to surround the outer surface of the cylindrical portion 26 of the guide plate 24. The electromagnetic brake 50 functions to apply a braking force to the cylindrical portion 26 by the magnetic force generated by the coil 54, thereby decelerating the guide plate 24. Therefore, the acceleration / deceleration mechanism 41 increases the speed of the guide plate 24 in the initial state where the electromagnetic brake 53 does not generate a magnetic force, and conversely decelerates the guide plate 24 when the magnetic force is generated.

Here, as shown in FIGS. 6 and 7, the yoke 55 is composed of substantially semicircular pieces 55a and 55b which are divided into two along the circumferential direction. As shown in FIG. 5, the two pieces 55a and 55b are each pivotally mounted at one end thereof to the back surface of the VTC cover 6 by a pivot pin 56. In addition, both pieces 55a, 55
At the other end of b, a spring 57 is provided as urging means for urging the other ends in the separating direction. Since one end of each piece 55a, 55b is pivotally connected to the VTC cover 6, at this time, the spring 57
a, 55b are urged radially outward. In addition, both pieces 5
As shown in FIG. 7, the inner peripheral surfaces of 5a and 55b are formed in a substantially elliptical shape slightly longer in the left-right direction in the figure.

On the back surface of the VTC cover 6, arc-shaped stopper claws 58a, 58b abutting on the outer peripheral surfaces of the pieces 55a, 55b are provided so as to project therefrom.
Excessive displacement radially outward of the stopper pawls 58a, 58
b.

In this embodiment, the yoke 55
Divided pieces 55a, 55b, a pivot pin 56 for swingably supporting these pieces, and both pieces 55a, 55
The spring 57 that urges b toward the open side constitutes a position shift absorbing mechanism. That is, when assembling this device, the guide plate 24 is attached to the camshaft 1 side, and the yoke 5
5 is attached to the VTC cover 6 by the pivot pin 56, and then the pieces 55a and 55b of the yoke 55 are arranged on the outer peripheral side of the cylindrical portion 26 of the guide plate 24.
The VTC cover 6 is attached to the engine block. At this time, even if there is an assembling error between the yoke 55 and the guide plate 24, the error is compensated by expanding the pieces 55a and 55b by the spring 57. , Each piece 55a,
It can be absorbed by the elliptical shape of the inner surface of 55b (see FIG. 6). Therefore, since the yoke 55 and the guide plate 24 are not caught, the VTC cover 6 can be easily assembled to the engine block.

The yoke 55 is, as shown in FIG.
The magnetic input / output ends 59a and 59b arranged on both sides in the axial direction face the outer peripheral surface of the cylindrical portion 26 of the guide plate 24. The magnetic input / output end 59 of the yoke 55
Reference numerals a and 59b extend in a direction approaching each other on a surface facing the cylindrical portion 26, and are generally formed in a substantially C-shaped cross section. Therefore, the area of the magnetic input / output ends 59a and 59b is ensured to be sufficiently large, and the magnetic force does not decrease even if the cylindrical portion 26 is slightly displaced in the axial direction.

Each piece 55a, 55b of the yoke 55 is
Since a magnetic action acts between the cylindrical portion 26 by energization,
At this time, each piece 55a, 55b moves in the approaching direction against the force of the spring 57, and each inner peripheral surface contacts the outer peripheral surface of the cylindrical portion 26 as shown in FIG. Therefore, the magnetic flux flowing into the cylindrical portion 26 from each of the pieces 55a and 55b by this contact increases, and a large braking action can be obtained.

A lubricating oil passage 60 is formed in the guide plate 24 from the radially inner side toward the outer peripheral surface of the cylindrical portion 26. This passage 60 is formed by the yoke 55 and the cylindrical portion 2.
The lubricating oil is supplied to the contact portion 6 at this time. In this supply, the centrifugal force due to the rotation of the guide plate 24 acts on the lubricating oil. Is supplied to the inner peripheral side of.

By the way, a driving torque is transmitted from the driving plate 2 to the camshaft 1 via the movable operation member 11, the link arm 14, and the lever 12, and the engine valve is transmitted from the camshaft 1 to the movable operation member 11. The torque (alternating torque) of the camshaft 1 due to the reaction force (reaction force due to the spring force of the valve spring) from the end of each lever 12 of the lever shaft 13 via the link arm 14 14 is input as a force in the direction connecting the pivot points at both ends.

Each movable operation member 11 is provided with a radial guide 10
However, the balls 22, 22A held so as to protrude to the front side are engaged with the spiral grooves 28 of the guide plate 24. The force input from the section through the link arm 14 is applied to the guide wall 9a of the radial guide 10,
9b and the spiral groove 28 of the guide plate 24.

Therefore, the force input from the link arm 14 to the movable operation member 11 is divided into two component forces orthogonal to each other, and these component forces are separated by the wall of the spiral groove 28 and the guide walls 9a and 9b. Since the movable operation member 11 is received in a direction substantially orthogonal to the operation direction, the operation of the movable operation member 11 is reliably prevented.

Incidentally, reference numeral 61 in FIG. 1 denotes a disc spring for urging the guide plate 24 in the direction of the ball 22.

Hereinafter, the operation of the present embodiment will be described.

At the time of starting the engine and idling, the power supply to the electromagnetic brake 50 is turned off by a control signal from the controller 7, and the pieces 55a, 55 of the yoke 55 are turned off.
As shown in FIG. 6, b is expanded by the force of the spring 57 and is not in contact with the guide plate 24.
For this reason, at this time, the guide plate 24 is urged toward the speed increasing side by the mainspring spring 25, and the movable operation member 11 of the assembly angle operation mechanism 4 is maintained at the radially outer end.

Accordingly, at this time, the drive plate 2 and the camshaft 1 are maintained at the most retarded angle of assembling.
The rotational phase of the crankshaft and the camshaft 1 is controlled to the most retarded side, thereby stabilizing the engine rotation and improving fuel efficiency.

When the engine shifts to the normal operation from this state, and the energization of the electromagnetic brake 50 is turned on by a control signal from the controller 7, the respective pieces 55a and 55b of the yoke 55 are turned on as shown in FIG. Guide plate 24
At this time, the braking force by the magnetic force acts on the cylindrical portion 26 at this time. As a result, the guide plate 24 is decelerated, the movable operation member 11 of the assembly angle operation mechanism 4 is displaced radially inward by the guide action of the spiral groove 28 and the spheres 22 and 22A, and the drive plate 2 and the camshaft 1 are moved to the maximum. The angle is changed to the advanced angle.

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 is increased.

The electromagnetic brake 5 used in this embodiment
0, the distance between the yoke 55 and the cylindrical portion 26 does not change due to the axial change of the guide plate 24 because the yoke 55 is arranged on the outer peripheral side of the cylindrical portion 26, and the braking force is always stable. Can be obtained.

The yoke 55 has a two-part structure, and each piece 55a, 55b is in contact with the outer peripheral surface of the cylindrical portion 26 during braking, so that the number of coil turns and power consumption increase. A relatively large braking force can be obtained without the need. Further, since the two pieces 55a and 55b always come into uniform contact from both sides of the cylindrical part 26, the cylindrical part 2
There is also an advantage that the magnetic force acting on 6 is less likely to be biased.

Further, in this embodiment, since the lubricating oil is supplied to the contact portion between the yoke 55 and the cylindrical portion 26, the contact friction between the yoke 55 and the cylindrical portion 26 can be reduced, and the yoke 55 The part can be efficiently cooled by the lubricating oil.

In this embodiment, the cylindrical portion 26 is protruded from the guide plate 24, and the electromagnetic brake 50 is disposed on the outer peripheral side of the cylindrical portion 26, while the mainspring spring is disposed on the inner peripheral side of the cylindrical portion 26. Since 25 is arranged, the limited space inside the device can be effectively used, and the size of the entire device can be reduced.

The embodiment of the present invention is not limited to the one described above. For example, in the above description, the yoke 55 is constituted by the two divided pieces 55a and 55b, but as shown in FIG. It may be integrally formed in an annular shape from the beginning. In the case of the embodiment shown in FIG.
The gap between the cylindrical portion 26 and the yoke 155 is almost eliminated, and the yoke 155 is rigidly attached to the VTC cover 6. In this case, the yoke 155 can be used as a bearing for guiding the rotation of the guide plate 24. . Therefore, the exclusive bearing can be eliminated, or the number can be reduced.

[0050]

As described above, according to the present invention, even when the rotating body fluctuates in the axial direction, the distance between the yoke and the rotating body does not change, so that the braking force is always stable regardless of the axial fluctuation. Can be obtained.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

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

FIG. 3 is a sectional view similar to FIG. 2, showing an operating state of the embodiment.

FIG. 4 is a view taken in the direction of arrow B in FIG. 1 showing the same embodiment;

FIG. 5 is a perspective view showing the same embodiment.

FIG. 6 is a sectional view of the same embodiment, taken along line AA of FIG. 1;

FIG. 7 is a sectional view similar to FIG. 6, showing an operation state of the embodiment.

FIG. 8 is a sectional view showing another embodiment of the present invention and corresponding to FIG. 6;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Cam shaft 2 ... Drive plate 4 ... Assembling angle operation mechanism 11 ... Movable operation member 22, 22A ... Ball 24 ... Guide plate (intermediate rotating body) 50 ... Electromagnetic brake 54 ... Coil 55, 155 ... Yoke 55a, 55b ... Piece 57: Spring (biasing means) 59a, 59b: Magnetic input / output end 60: Lubricating oil passage

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3G018 CA12 DA05 DA36 DA39 DA83 FA07 FA21 GA02 3J058 AA03 AA06 AA29 CB01 CC12 DE19 FA01

Claims (11)

[Claims] A yoke forming a path of a magnetic flux generated by a coil is disposed with an end face serving as a magnetic input / output end facing a rotating body made of a magnetic material, and the rotating body is formed by a magnetic force acting on the rotating body from the end face of the yoke. An electromagnetic brake, wherein the yoke is disposed on an outer peripheral side of a rotating body such that a magnetic input / output end faces an outer peripheral surface of the rotating body. 2. The electromagnetic brake according to claim 1, wherein the yoke is constituted by a plurality of pieces divided in a circumferential direction, and the pieces are brought into contact with and separated from the rotating body by turning on / off the energization of the coil. apparatus. 3. The electromagnetic brake device according to claim 2, further comprising: urging means for urging each piece of the yoke to separate radially outward with respect to the rotating body. 4. The electromagnetic brake device according to claim 1, wherein the yoke is attached to the base member through a displacement absorbing mechanism that absorbs a radial displacement of the yoke. . 5. The electromagnetic brake device according to claim 1, wherein a lubricating oil supply structure is provided between the yoke and the rotating body. 6. The electromagnetic brake device according to claim 5, wherein a lubricating oil passage extending from a radially inner side to an inner peripheral surface of the yoke is provided in the rotating body. 7. The electromagnetic brake device according to claim 1, wherein an auxiliary device is disposed inside the rotating body. 8. The yoke is formed in an annular shape, and a rotating body is supported on an inner peripheral surface of the yoke.
The electromagnetic brake device according to any one of claims 1 to 7. 9. The magnetic input / output end of the yoke is disposed so as to face the outer peripheral surface of the rotating body on both axial sides, and the magnetic input / output ends are extended toward the inside in the axial direction. The electromagnetic brake device according to any one of claims 1 to 8, wherein: 10. A driving rotary body that is driven to rotate by a crankshaft of an internal combustion engine, and a driven rotary body that is a separate member connected to the camshaft or the shaft, are coaxially connected via an assembly angle operating mechanism. Used in a valve timing control device of an internal combustion engine that variably controls the rotational phase of a crankshaft and a camshaft by operating an assembly angle operation mechanism according to an engine operating condition, and for operating the assembly angle operation mechanism. An electromagnetic brake for applying a braking force to an intermediate rotating body, wherein a yoke forming a magnetic flux passage is arranged on an outer peripheral side of the rotating body such that a magnetic input / output end faces an outer peripheral surface of the rotating body. Brake device. 11. The electromagnetic brake device according to claim 10, wherein the intermediate rotating body is linked to a movable operating member of the assembly angle operating mechanism via a ball.