JP3845903B2 - Rotation transmission member joint device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a joint device for a rotary transmission member.
[0002]
[Prior art]
Conventionally, various types of joint devices for rotating power transmission members have been proposed. For example, Japanese Patent Application Laid-Open No. 7-26917 discloses a pair of meshes provided between a cam shaft side member and an output shaft side member. A tooth type electromagnetic clutch as a meshing means that is a member and that engages / disengages the two by engaging and releasing the engagement, and a camshaft side member by applying a torque in the braking direction as a phase change driving torque to the camshaft side member And an electromagnetic brake as drive means for changing the rotation angle phase between the output shaft side member and the output shaft side member is disclosed.
[0003]
[Problems to be solved by the invention]
By the way, a joint device for a rotary transmission member provided with such a tooth type electromagnetic clutch as a meshing means and an electromagnetic brake as a drive means is used, for example, a device for changing a rotational angle phase between a crankshaft and a camshaft of an engine. That is, when applied to a valve timing device, there are the following problems.
[0004]
That is, when the current rotation angle phase is changed to a predetermined target rotation angle phase, the engagement state of the tooth type electromagnetic clutch that holds the current rotation angle phase, that is, the tooth engagement state of the pair of engagement members is released. Release the coupled state between the crankshaft and the camshaft, and then actuate an electromagnetic brake to rotate the crankshaft and the camshaft relative to each other by the braking torque to change the rotational angle phase between them, Thereafter, the tooth type electromagnetic clutch is engaged again to maintain the changed rotational angle phase.
[0005]
Accordingly, in order to perform the rotational angle phase changing operation more quickly and improve the phase change responsiveness, it is necessary to quickly release the engagement of the tooth type electromagnetic clutch (that is, release the engagement of the tooth). . In this case, since the tooth of the tooth type electromagnetic clutch is tapered, the electromagnetic brake is operated in synchronization with the fastening release operation of the tooth type electromagnetic clutch, so that the braking torque of the electromagnetic brake A component force in the engagement release direction of the tooth type electromagnetic clutch is generated on the tooth surface of the tooth type electromagnetic clutch, and the release of the engagement is promoted (see FIG. 3).
[0006]
However, in the conventional joint device for rotary transmission members, when changing the rotation angle phase, the electromagnetic brake is operated in synchronization with the engagement release operation of the tooth electromagnetic clutch to promote the release release of the tooth electromagnetic clutch. Although it is configured, there is no effective control philosophy regarding the energization control for each solenoid coil of the tooth type electromagnetic clutch and the electromagnetic brake, and the energization amount of the solenoid coil of the tooth type electromagnetic clutch is simply used to release the engagement. Set to a value corresponding to the required driving force, and set the energization amount of the solenoid coil of the electromagnetic brake to a value corresponding to the braking torque required to change the predetermined amount of the rotation angle phase, and fasten them. Since it was applied continuously from the initial stage of the release operation, the engagement release operation of the tooth type electromagnetic clutch (ie, the tooth The engagement release operation) is relatively slow, and the engagement releasing action by the braking torque of the electromagnetic brake is also relatively small. As a result, as shown by the characteristic curve shown by the broken line in FIG. Even if the engagement release operation of the tooth type electromagnetic clutch is started at the set time, the engagement of the tooth type electromagnetic clutch is actually released from the set time of the target rotation angle phase, and the rotation angle phase is set by the braking torque of the electromagnetic brake. It takes a relatively long time (t) to start the change operation from the rotation angle phase before the change to the target rotation angle phase side. As a result, the responsiveness of the phase change becomes worse, and consequently the phase change. Longer transition periods will adversely affect engine operating characteristics.
[0007]
Accordingly, the present invention has been made for the purpose of enhancing the responsiveness in the rotational angle phase changing operation by performing the meshing release operation of the meshing means more quickly in the joint device of the rotational transmission member.
[0008]
[Means for Solving the Problems]
In the present invention, the following configuration is adopted as a specific means for solving such a problem.
[0009]
In the first invention of the present application, the first rotational transmission member and the second rotational transmission member, which are capable of transmitting rotational force to each other, are coaxially opposed to each other so as to be able to contact and separate from each other, and on the opposite end surface. The first rotation transmission is made up of a pair of meshing members each provided with a plurality of tapered teeth, receiving the driving force in the axial direction, and moving the pair of meshing members in the separating direction and releasing the meshing state. The engagement means configured to release the fastening between the member and the second rotation transmission member, and a predetermined drive torque is applied between the pair of engagement members of the engagement means to rotate them relative to each other. In a joint device for a rotary transmission member, comprising: a drive unit that changes a rotational angle phase between the rotary transmission member and the second rotary transmission member and whose drive torque value can be changed. Toru In the initial stage of the engagement release operation of the meshing means, an initial driving torque larger than the appropriate driving torque required for changing the predetermined amount of the rotation angle phase is applied for a predetermined period, and the driving torque is applied after the predetermined period has elapsed. Control is performed so that the driving torque is reduced to the appropriate driving torque.
[0010]
According to a second invention of the present application, in the joint device for a rotary transmission member according to the first invention, the drive means is constituted by an electromagnetic brake, and the drive torque is increased or decreased by controlling the amount of current supplied to the electromagnetic brake. It is characterized by that.
[0011]
According to a third invention of the present application, in the joint device for a rotary transmission member according to the first or second invention, the driving force in the fastening release direction of the meshing means is large at the initial stage of the releasing operation and small at the final stage. It is characterized by controlling as follows.
[0012]
According to a fourth invention of the present application, in the joint device for a rotary transmission member according to the third invention, the meshing means is constituted by an electromagnetic clutch that generates a driving force in a direction in which the pair of meshing members are separated by the magnetic force thereof. The driving force is increased or decreased by controlling the amount of current supplied to the electromagnetic clutch.
[0013]
【The invention's effect】
In the present invention, the following effects can be obtained by adopting such a configuration.
[0014]
(1) In the rotation transmission member coupling device according to the first and second inventions of the present application, the drive means is an appropriate drive torque required for changing the predetermined amount of the rotation angle phase in the initial stage of the engagement release operation of the meshing means. A larger initial driving torque is applied for a predetermined period, and after the predetermined period has elapsed, the driving torque is controlled to be reduced to the appropriate driving torque.
[0015]
Accordingly, the driving force in the fastening release direction of the meshing means generated on the tooth surface of the tapered tooth of the meshing means by the drive torque of the drive means is set to an initial drive torque that is greater than the appropriate drive torque. As a result, a larger value is obtained, and the engagement / disengagement action of the meshing means by the driving torque of the drive means is enhanced, and the engagement / release of the meshing means is accelerated accordingly, and as a result, the first rotation transmission member and the second rotation Responsiveness of the changing operation of the rotational angle phase with the transmission member is enhanced.
[0016]
Further, the drive means sets the drive torque to the initial drive torque for a predetermined time at the initial stage of the release of the engagement of the meshing means to promote the release of the engagement of the engagement means. The rotation angle phase of the first rotation transmission member and the second rotation transmission member is changed under the control of the rotation angle, so that the rotation angle phase change operation is properly performed to ensure the phase change accuracy, and for example, for a predetermined time Compared with the case where the initial driving torque is maintained even after the lapse of time, the power consumption in the solenoid coil is small, which is economical.
[0017]
(2) According to the joint device of the rotary transmission member according to the third and fourth inventions of the present application, the driving force of the engagement means in the fastening release direction is controlled to be large at the initial stage of the releasing operation and small at the final stage. Therefore, when a large driving force is applied at the initial stage of the fastening release that requires the most driving force for releasing the fastening, the fastening release speed of the meshing means is increased, and the first rotation transmission member and The responsiveness of the rotation angle phase changing operation with the second rotation transmission member is improved.
[0018]
In addition, since the driving force is set to be small at the end of the release of the fastening, the state is maintained after the fastening is released under this small driving force. It is.
[0019]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be specifically described based on preferred embodiments.
1. Description of structure FIG. 1 shows an engine valve timing control device as a preferred embodiment of a joint device for a rotational transmission member according to the present invention. In FIG. 1, reference numeral 1 denotes a cylinder head 9 side. The camshaft is rotatably supported by the motor (corresponding to the “first rotation transmission member” in the claims), 2 is the output shaft of the engine (not shown, but “second” in the claims) The pulley is driven via the timing belt 3 by a “rotational transmission member”, and the rotational angle phase difference between the cam shaft 1 and the pulley 2 (ie, the output shaft) is changed. The valve timing is changed.
[0020]
At the tip of the camshaft 1, an internal gear 5 which is one of constituent members of a planetary gear mechanism 4 described later and a hollow shaft member 11 having a predetermined axial length are arranged coaxially, The members 5 and 11 are coupled and fixed to the cam shaft 1 by a coupling bolt 12 so as to rotate integrally with the cam shaft 1.
[0021]
The pulley 2 is rotatably supported on the cylinder head 9 side via a bearing 33, and a planetary gear mechanism 4 is disposed on the inner side in the radial direction. The planetary gear mechanism 4 includes a plurality of pinion gears 7, 7, supported by a carrier 6 integrally formed with the internal gear 5, a sun gear 8 formed on one end side of a cylindrical member 17 to be described later, and the pulley 2.・ ・ Consists of
[0022]
A spiral spring 10 is arranged on one side of the planetary gear mechanism 4 in the axial direction, with one end fixed to the pulley 2 side and the other end fixed to a cylindrical member 17 side to be described later. ing. The spiral spring 10 is set in a winding direction in relation to an electromagnetic brake 21 described later, which will be described later.
[0023]
The tubular member 17 is integrally coupled to the flange member 18 and is rotatably supported on the hollow shaft member 11 side via a bearing 31. Further, the flange member 18 corresponds to “one engagement member” in the claims, and the outer peripheral portion of one side surface 18a thereof is a contact surface with respect to an electromagnetic brake 21 described later, while the diameter thereof A plurality of teeth 20A, 20A,... Are provided so as to be positioned on a pitch circle having a predetermined diameter at the middle position in the direction.
[0024]
On the other hand, a tooth type electromagnetic clutch 14 is disposed near the tip of the hollow shaft member 11. The electromagnetic clutch 14 corresponds to “meshing means” in claims, and includes a slider 15 and a bearing support member 13 described below. The slider 15 corresponds to “the other meshing member” in the claims, and the tooth 20A, 20A,... On the flange member 18 side is formed on the outer peripheral portion of the surface facing the flange member 18. Are substantially disc-shaped with teeth 20B, 20B,... Facing each other, and are splined to the hollow shaft member 11 so as to be movable in the axial direction. Further, the bearing support member 13 is non-rotatably attached to the end of the hollow shaft member 11 so as to be close to and opposed to the slider 15, and the slider 15 is always attached to the flange between the slider 15. A wave ring 19 that presses and biases toward the member 18 is disposed.
[0025]
Accordingly, in the electromagnetic clutch 14, the slider 15 is pressed and urged toward the flange member 18 by the wave ring 19, and the teeth 20B, 20B,... On the slider 15 side are each tooth 20A on the flange member 18 side. , 20A,... Are engaged with each other, and in this engaged state, the relative rotation of the slider 15 and the flange member 18 is restricted, and the rotational angle phase between the cam shaft 1 and the pulley 2 is Will be retained.
[0026]
On the other hand, on the back side of the slider 15, the solenoid coil 16 is disposed close to the slider 15 while being fixed to the casing 26 side. The solenoid coil 16 separates the slider 15 from the flange member 18 side by a magnetic attractive force to release the meshing state of the teeth 20A, 20A,... 20B, 20B,. 14 is released, and the energization control is performed by a VVT controller 35 that operates in response to a control signal from the ECU 36. The energization control of the electromagnetic clutch 14 will be described later.
[0027]
Further, an electromagnetic brake 21 including a solenoid coil 22 and a contact 23 that is movable in the axial direction by receiving the magnetic force of the solenoid coil 22 is disposed at a radially outer position of the solenoid coil 16. . The electromagnetic brake 21 constitutes “driving means” in the scope of claims, and energizes the solenoid coil 22 to excite the contact 23 so that one end side of the contact 23 is connected to the electromagnetic brake 21. A predetermined braking torque is applied to the flange member 18 by pressing against the side surface 18 a of the flange member 18. The energization control to the solenoid coil 22 of the electromagnetic brake 21 is performed by a VVT controller 35 that operates in response to a control signal from the ECU 36. This 21 energization control will be described later.
[0028]
The operational relationship between the electromagnetic brake 21 and the spiral spring 10 is as follows. That is, in this embodiment, by applying a braking torque to the flange member 18 by the electromagnetic brake 21, the rotation angle phase of the cam shaft 1 is changed to the rotation angle of the pulley 2 via the planetary gear mechanism 4. In addition to being delayed with respect to the phase (that is, the retarding operation of the rotation angle phase), the spiral spring 10 is wound up with the relative rotation of the camshaft 1 and the pulley 2 to store the spring force. On the other hand, when the acceleration torque is applied to the flange member 18 by the spring force in the restoring direction of the spiral spring 10, the rotational angle phase of the cam shaft 1 is changed to that of the pulley 2 via the planetary gear mechanism 4. The rotation angle phase is advanced (that is, the advance operation of the rotation angle phase).
[0029]
Description of basic operation The basic operation of the valve timing control apparatus having the above- described configuration will be described as follows.
[0030]
A: Holding operation of rotation angle phase The rotation angle phase between the camshaft 1 and the pulley 2 is held by the electromagnetic clutch 14. That is, the solenoid coil 16 is de-energized, the slider 15 is pressed against the flange member 18 by the urging force of the wave ring 19, and the teeth 20A, 20A,. 20B, 20B,... Are engaged with each other to bring the slider 15 and the flange member 18 into a coupled state, and the relative rotation between the slider 15 and the flange member 18 is restricted. Then, the planetary gear mechanism 4 is in a locked state, and torque from the pulley 2 is transmitted from the carrier 6 → the pinion gear 7 → the internal gear 5 → the cam shaft 1, and the pulley 2 and the cam shaft 1 rotate at a predetermined rotation. It will rotate integrally while maintaining the angular phase.
[0031]
B: Retardation operation of rotation angle phase Retardation operation of rotation angle phase is started by first releasing the holding state of the rotation angle phase by the electromagnetic clutch 14. That is, the solenoid coil 16 is energized, and the slider 15 is pulled away from the flange member 18 by a magnetic attraction force, and the teeth 20A, 20A,... 20B, 20B, and the teeth 20A, 20A,. .. Are disengaged and the engaged state of the electromagnetic clutch 14 is released. Thereafter, a predetermined braking torque is applied to the flange member 18 by the electromagnetic brake 21 to slow down the rotation of the flange member 18 relative to the rotation of the slider 15. Then, the cam shaft 1 that rotates integrally with the slider 15 and the internal gear 5 of the planetary gear mechanism 4 rotate faster than the sun gear 8 of the planetary gear mechanism 4 that rotates integrally with the flange member 18. Is rotated with respect to the rotation angle phase of the pulley 2.
[0032]
In this case, with the relative rotation between the pulley 2 and the cylindrical member 17, the spiral spring 10 is wound up and stores a spring force.
[0033]
When the retard amount of the cam shaft 1 reaches a target value, the energization to the electromagnetic brake 21 is stopped to release the braking torque, and the energization to the solenoid coil 16 is stopped to stop the slider of the electromagnetic clutch 14. 15 is urged toward the flange member 18 by the spring force of the wave ring 19, and the teeth 20A, 20A,... And 20B, 20B,. The rotation angle phase with the flange member 18, that is, the rotation angle phase between the cam shaft 1 and the pulley 2 is maintained.
[0034]
C: Advance operation The advance operation is performed by energizing the solenoid coil 16 and pulling the slider 15 away from the flange member 18 by the magnetic attraction force to release the engaged state of the electromagnetic clutch 14. That is, when the electromagnetic clutch 14 is released from the engaged state (the rotational angle phase is maintained), the flange member 18 receives the acceleration torque due to the spring force in the restoring direction of the spiral spring 10 and the flange member 18 is moved against the slider 15. Rotate fast. Then, the camshaft 1 that rotates integrally with the slider 15 and the internal gear 5 of the planetary gear mechanism 4 rotate slower than the sun gear 8 of the planetary gear mechanism 4 that rotates integrally with the flange member 18. Is rotated with respect to the rotation angle phase of the pulley 2.
[0035]
When the advance amount of the cam shaft 1 reaches a target value, the energization to the solenoid coil 16 is stopped, and the slider 15 of the electromagnetic clutch 14 is biased toward the flange member 18 by the spring force of the wave ring 19, The teeth 20A, 20A,... And 20B, 2B,... Are brought into a fastening state, and the rotational angle phase between the slider 15 and the flange member 18, that is, the cam shaft 1 and the pulley 2 are set. Rotation angle phase is maintained.
[0036]
As described above, the operations described in A to C are the basic operations of the valve timing control device.
[0037]
Energization control when changing rotation angle phase By the way, in the valve timing control device of this embodiment, the advance and retard are performed by the basic operation as described above. By applying the present invention to the energization control of the motor 14 and the electromagnetic brake 21, the rotation angle phase can be changed more quickly after the setting of the target rotation angle phase as shown by the characteristic curve L shown in FIG. Therefore, the phase change operation with high responsiveness is realized, so that the good operating characteristics of the engine can be maintained.
[0038]
This energization control will be described by taking as an example a case where the rotation angle phase is changed from the current rotation angle phase to the target rotation angle phase as indicated by the characteristic curve L shown by the solid line in FIG. First, the basic idea of control in this embodiment is based on the operating characteristics of the electromagnetic clutch 14. That is, the electromagnetic clutch 14 starts the engagement release operation simultaneously with the transition to the phase change operation as shown in FIG. 5C, but the teeth 20A, 20A,..., 20B, 20B,. but is the engagement releasing operation of the operation start time (time t ₁₎ is not intended to be immediately disengaged, the complete over operation start time (time t ₁₎ from the predetermined time (time t ₃ -t ₁₎ Yes, and in that case, the tooth mesh release operation requires the greatest driving force in the initial stage of the release operation.
[0039]
In consideration of the operating characteristics of the electromagnetic clutch 14, the initial operation of releasing the engagement is performed by temporarily applying the largest driving force in the releasing direction to the electromagnetic clutch 14 in the initial stage of the releasing operation of the electromagnetic clutch 14. It is performed quickly, and thereafter, it returns to an appropriate driving force to continue the release of the fastening and keep the fastening released state. In the initial stage of releasing the engagement of the electromagnetic clutch 14, not only the driving force due to the electromagnetic force of the solenoid coil 16 for releasing the engagement of the electromagnetic clutch 14 but also the drive torque for generating the phase change is originally generated. The electromagnetic force of the solenoid coil 22 of the electromagnetic brake 21 is also used as the driving force, and a larger driving force by the electromagnetic clutch 14 and the electromagnetic brake 21 is applied.
[0040]
In the energization control based on such a basic idea, first, energization of the electromagnetic clutch 14 is performed for a predetermined time (time t ₁ ) from the output time (time t ₁ ) of the phase change command, as shown in FIG. _2- Set the energization amount to the maximum value (100%) for the time t ₁ ), apply a larger driving force for releasing the engagement, and set the energization amount to the proper value required for the original engagement release after the predetermined time has elapsed. Switching to the energization amount (A%) is held until the phase change is completed.
[0041]
The energization control of the electromagnetic brake 21 is essentially necessary to change the current rotation angle phase to the target rotation angle phase during the period from when the phase change command is output until the phase change is completed. It is only necessary to apply a large driving torque (that is, an appropriate torque). However, in this embodiment, as shown in FIG. 6B, the torque is larger than the appropriate torque by a predetermined time (time t ₂ −t ₁ ) from the output time (time t ₁ ) of the phase change command. The energization amount is set to a maximum value (100%) in order to apply the initial drive torque, and after the predetermined time has elapsed, this is returned to the appropriate torque, and this appropriate torque is maintained until the phase change is completed. As described above, as shown in FIG. 2, the electromagnetic clutch 14 is applied with the driving torque (braking torque) by the electromagnetic brake 21 from the initial stage of the release operation of the electromagnetic clutch 14. , 20A,... And a flange member 18 provided with the teeth 20B, 20B,... And a solenoid coil 16 that drives the slider 15 in the meshing release direction. 20A,..., 20B, 20B,... Each have a tapered shape, and the electromagnetic brakes are formed by the tapered shape of each tooth 20A, 20A,..., 20B, 20B,. Since the driving force Fr acts in the direction of releasing the electromagnetic clutch 14 by the driving torque F applied by the motor 21, the electromagnetic brake 21 The driving force Fr caused by the driving torque is to utilize the unfastening of the electromagnetic clutch 14.
[0042]
By performing energization control of the electromagnetic clutch 14 and the electromagnetic brake 21 in this way, a large driving force is applied in the direction of releasing the engagement by the solenoid coil 16 of the electromagnetic clutch 14 at the initial stage of releasing the engagement of the electromagnetic clutch 14. The electromagnetic brake 21 exerts a large driving force (Fr) in the direction of releasing the electromagnetic clutch as a component of the driving torque, and the synergistic action of the two keeps the initial speed of the releasing operation of the electromagnetic clutch 14 high. As a result, as shown by the solid line in FIG. 5, the phase change is completed earlier than the output of the phase change command, and the responsiveness of the rotation angle phase changing operation is enhanced. The period of the transient state of the rotational angle phase is shortened by the increase in the responsiveness of the rotational angle phase changing operation, and as a result, good operating characteristics of the engine are maintained.
[0043]
Further, in both the electromagnetic clutch 14 and the electromagnetic brake 21, the energization amount to the solenoid coil is changed to the energization amount necessary for releasing the original engagement or the energization amount necessary for the original phase change after the predetermined time has elapsed. In addition, since this is maintained, for example, the energization amount to each of the solenoid coils 16 and 22 can be reduced as compared with a case where a large energization amount at the initial phase change is maintained even after a predetermined time has passed. In particular, it is suitable for a battery with a limited battery capacity such as an automobile engine.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a specific structure of a joint device for a rotary transmission member according to a preferred embodiment of the present invention.
FIG. 2 is a structural conceptual diagram of the electromagnetic clutch shown in FIG.
FIG. 3 is an explanatory diagram of an acting force in the tooth portion shown in FIG. 2;
FIG. 4 is an explanatory diagram of a relative relationship between an energization amount characteristic of the electromagnetic clutch and the electromagnetic clutch and a tooth meshing state at the time of phase change.
FIG. 5 is an explanatory diagram of control characteristics of a rotation angle phase when the joint device for a rotation transmission member shown in FIG. 1 is applied to a valve timing control device.
[Explanation of symbols]
1 is a cam shaft, 2 is a pulley, 3 is a timing belt, 4 is a planetary gear mechanism, 5 is an internal gear, 6 is a carrier, 7 is a pinion gear, 8 is a sun gear, 9 is a cylinder head, 10 is a spiral spring, 11 is Hollow shaft member, 12 coupling bolt, 13 bearing support member, 14 electromagnetic clutch, 15 slider, 16 solenoid coil, 17 cylindrical member, 18 flange member, 19 wave ring, 20A and 20B are tooth , 21 is an electromagnetic brake, 22 is a solenoid coil, 23 is a contact, 25 is a casing, 26 is a casing, 27 is an end plate, 31 to 33 are bearings, 35 is a VVT controller, and 36 is an ECU.

Claims (4)

Between the first rotation transmission member and the second rotation transmission member that are capable of transmitting rotational force to each other, they are concentrically opposed to each other and provided with a plurality of tapered teeth on the opposite end surfaces. The pair of meshing members receive the driving force in the axial direction thereof, the pair of meshing members move in the separating direction, and the meshing state is released, so that the first rotation transmission member and the second rotation transmission member are Meshing means configured to release the fastening of
A predetermined drive torque is applied between the pair of meshing members of the meshing means to rotate them relative to each other, thereby changing the rotation angle phase between the first rotation transmission member and the second rotation transmission member. A joint device for a rotary transmission member comprising a drive means capable of changing a drive torque value,
The initial driving torque larger than the appropriate driving torque required for changing the predetermined amount of the rotation angle phase is applied for a predetermined period at the initial stage of the engagement release operation of the engagement means. After the elapse of time, the rotation transmission member coupling device is controlled so as to reduce the driving torque to the appropriate driving torque. In claim 1,
The joint device for a rotary transmission member, wherein the drive means is constituted by an electromagnetic brake, and the drive torque is controlled to increase or decrease by controlling an energization amount to the electromagnetic brake. In claim 1 or 2,
A joint device for a rotary transmission member, wherein the driving force of the meshing means in the fastening release direction is controlled to be large at the initial stage of the releasing operation and small at the final stage. In claim 3,
The meshing means is constituted by an electromagnetic clutch that generates a driving force in a direction to separate the pair of meshing members by the magnetic force, and the driving force is increased or decreased by controlling the amount of current supplied to the electromagnetic clutch . Rotating transmission member joint device.

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