JP2003056602A - Rotary drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To avoid a damage of a motor, a reduction gear and the like by reverse input torque, to hold a mirror part in a specified position when the reverse input torque is small and to avoid damage to the mirror part when the reverse input torque is large. SOLUTION: A rotary drive device comprises the motor 3, a reverse input cutoff clutch 1, a regulating means 2 and a driven member 4 such as a mirror. The reverse input cutoff clutch 1 comprises an input outer ring 11 into which torque from the motor 3 is input, and an output inner ring 12 coupled to the driven member 4; and transmits input torque applied to the input outer ring 11 to the output inner ring 12, and under reverse input torque applied to the output inner ring 12, cuts off the transmission thereof to the input outer ring 11 and allows an idle rotation of the output inner ring 12. The regulating means 2 elastically regulates rotation of the output inner ring 12 in each predetermined specified position.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary drive device for moving a driven member between at least two specified positions by an input torque from a motor, and blocking transmission of a reverse input torque from the driven member to a motor. It is about.

[0002]

2. Description of the Related Art In recent years, vehicles such as automobiles are equipped with an electric retractable mirror that drives a door mirror by a motor and swings about 90 ° between a use position extended laterally of the vehicle and a folded storage position. There is more to do. As this electric retractable mirror, as shown in FIG.
When driven by 1, the mirror 42 can be moved lightly, and when an external force acts on the mirror 42, the clutch 43
There is known a drive mechanism in which the mirror 42 is firmly fixed to prevent the external force from acting on the motor 41 side by shutting off the external force (for example, JP-A-11-51092).

[0003]

However, when the above drive mechanism is actually used in an electric retractable mirror,
It is necessary to detect the rotation angle of the mirror, detect that the mirror has reached the use position or the storage position, and stop the motor. Therefore, a sensor that detects the rotation angle and a control system that processes the detection signal are separately required,
The structure becomes complicated. Further, in the drive mechanism described in the above publication, the mirror is completely fixed so as not to rotate even when a reverse input torque is applied to the mirror, but this cannot absorb the external force, resulting in damage to the mirror or the like. There is a risk.

An object of the present invention is to solve the above problems.

[0005]

A rotary drive device according to the present invention is a device for moving a driven member between at least two predetermined positions, and a motor and a torque from the motor are input. An input side member and an output side member connected to the driven member are provided, and while transmitting the input torque applied to the input side member to the output side member, the input side against the reverse input torque applied to the output side member. A reverse input cutoff clutch that cuts off the transmission to the member and allows the output side member to idle, and a restricting means that elastically restricts the rotation of the output side member at each specified position.

With such a configuration, the input torque applied from the motor to the input side member is transmitted to the output side member of the reverse input cutoff clutch, and the rotational torque of at least two (three or more) driven members is used. Move between specified positions. When the driven member reaches each specified position, the rotation of the output side member is elastically restricted by the restricting means, so that the driven member holds the position against the external force. On the other hand, when the external force becomes large and the reverse input torque exceeds the elastic rotation restriction force of the restriction means, the output side member starts to rotate against this rotation restriction force. Here, since the reverse input cutoff clutch has a structure that allows the output side member to idle with respect to the reverse input torque, the driven member can be freely rotated through the idle rotation of the output side member, and this free rotation causes the driven member to rotate. The applied external force can be absorbed. Further, since the reverse input cutoff clutch cuts off the transmission of the reverse input torque to the input side member, damage to the motor or the like due to a large reverse input torque can be avoided.

The reverse input cut-off clutch further holds a torque transmission member which can be engaged / disengaged with the input side member and the output side member in both forward and reverse rotation directions, and holds the torque transmission member, and through relative rotation with respect to the input side member. Engagement of torque transmission member
A retainer that controls disengagement, a first elastic member that connects the input side member and the retainer in the rotational direction, a stationary side member, and a sliding frictional resistance to the retainer against rotation of the retainer with respect to the stationary side member. It may be provided with a rotational resistance applying means for acting.

In the above structure, when a rotational torque is input from the motor to the input side member of the reverse input cutoff clutch, the cage connected to the input side member via the first elastic member starts to rotate together with the input side member. . Since the sliding frictional resistance acts on the cage due to the action of the rotational resistance imparting means in association with the rotation, the cage receives the rotational resistance and rotates relative to the input side member to cause a rotation delay (at this time). , The first elastic member is elastically deformed). When the cage is delayed in rotation, the torque transmission member engages with both the input-side member and the output-side member, so that the rotational torque input to the input-side member is transmitted through the torque-transmission member to the output-side member. Be transmitted to.

On the other hand, with respect to the rotational torque (reverse input torque) input from the output side member, since the sliding frictional resistance from the rotational resistance applying means does not act on the retainer, it is held by the elastic action of the first elastic member. The vessel is centered. When the cage is centered in this way, the torque transmission member is disengaged from both the input side member and the output side member and can rotate, so that the output side member can idle. .

The above operation is realized by forming a wedge gap between the input side member and the output side member, and engaging or disengaging the engaging element as a torque transmitting member with respect to the wedge gap. can do. In this configuration, a cam surface for forming a wedge gap is provided on the output side member or the input side member (using a circular cross section such as a roller or a ball as an engaging element), for forming a wedge gap The configuration in which the cam surface of (1) is provided on the engaging element (a sprag or the like is used as the engaging element) is included.

The restricting means includes, for example, a concave engaging portion provided on one of the output side member and the stationary side member and a convex engaging portion provided on the other member, and includes a stationary side. Of the output side member by elastically engaging the concave engagement portion and the convex engagement portion at each prescribed position by arranging the engagement portion on the rotation locus of the rotation side engagement portion. Is regulated.

In this structure, when the output side member is rotated by the torque applied to the input side member, when the convex engaging portion and the concave engaging portion reach the opposing positions, both of them are elastic in the circumferential direction. Since they are engaged with each other, further rotation of the output side member can be restricted. On the other hand, when a large reverse input torque exceeding the rotation restriction force of the restriction means is applied to the output side member, the concave and convex engagement between the concave engagement portion and the convex engagement portion is released, and the output side member idles. .

This structure can be embodied by, for example, providing the concave engaging portion on the stationary member and the convex engaging portion on the output member via the second elastic member. In this case, the concave engaging portion and the convex engaging portion are engaged with each other by the elastic force of the second elastic member. If a reverse input torque that exceeds the torque reaction force due to this elastic force is applied to the output side member, the output side member can idle.

If the output side member and the stationary side member are opposed to each other in the axial direction, and the concave engaging portion and the convex engaging portion are provided at the opposing portions, the restricting means can be incorporated in the reverse input cutoff clutch. Therefore, the entire apparatus can be made compact.

At the time of engagement between the concave engagement portion and the convex engagement portion (not only immediately after engagement but also immediately before engagement), the drive current of the motor increases. Therefore, if the motor is stopped when the increase in the drive current is detected, the driven member can be accurately stopped at each specified position without using a sensor or the like.

The rotation resistance imparting means has a sliding member which is engageable with one of the retainer and the stationary member in the circumferential direction and slides with respect to the other. For example,
The sliding member may be slidable with respect to the stationary member in a state of being circumferentially engaged with the retainer.

As the driven member, for example, a mirror portion of a vehicle can be used. In this case, one of the two prescribed positions can be a use position in which the mirror portion is projected to the side of the vehicle, and the other can be a storage position in which the mirror portion is folded.

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to FIGS.
It will be described with reference to FIG.

FIG. 1 shows an embodiment of a rotary drive device according to the present invention. As shown in the figure, this rotation drive device is composed of a reverse input cutoff clutch 1, a regulating means 2 and a motor 3. Rotational torque from the motor 3 is transmitted to the mirror section 4 as a driven member via the reverse input cutoff clutch 1 and causes the mirror section 4 to swing in the forward and reverse directions about the swing axis O. The restricting means 2 holds the mirror section 4 at a predetermined storage position and use position.

The reverse input cutoff clutch 1 is shown in FIGS.
As shown in FIG. 1, an input outer ring 11 as an input side member, an output inner ring 12 as an output side member, a roller 13 as a torque transmission member, a retainer 14 for holding the roller 13, and a first elasticity for positioning the retainer 14. Centering spring 15 as a member, first and second side plates 1 as stationary members
6a, 16b, and a slide spring 17 as a rotation resistance imparting means for exerting a sliding frictional resistance on the cage with respect to the rotation of the cage 14 is provided. The input torque from the motor 3 is input to the input outer ring 11, passes through the roller 13, and is output from the output inner ring 12. As shown in FIG. 1, the output inner ring 1
The rotation axis of the mirror unit 4 is connected to 2.

In the following description, the right side of the drawing of FIG. 2 is referred to as "one end side" and the left side of the drawing is referred to as "the other end side" for convenience of description.

A tooth portion 11 is provided on the outer periphery of one end of the input outer ring 11.
b is formed. As shown in FIG. 1, this tooth portion 11
Reference character b constitutes a reduction mechanism 6 by meshing with a drive gear 5 attached to the output shaft of the motor 3. The deceleration mechanism 6 is not limited to the one shown in the figure, and any configuration can be adopted. The tooth portion 11b can be directly formed on the outer circumference of the input outer ring 11 made of a metal material such as hardened steel, or can be formed on another member and fixed to the outer circumference of the input outer ring 11. In this case, for example, the tooth portion 11b is made of resin, the input outer ring 11 is made of a metal material such as hardened steel, and these are press-fitted, concave and convex fitting,
Alternatively, it is conceivable that they are integrated by means such as insert molding.

As shown in FIGS. 4 (a) and 4 (b), a collar portion 11c protruding toward the inner diameter side is formed on the inner circumference of one end portion of the input outer ring 11. The flange portion 11c has a notch portion 11d formed at one location in the circumferential direction over the entire length in the axial direction.

The output inner ring 12 is disposed on the inner diameter side of the input outer ring 11, as shown in FIGS. The output inner ring 12 has a cylindrical portion 12 facing the inner peripheral surface of the input outer ring 11.
It is provided with a and a shaft portion 12b extending in the axial direction. In the present embodiment, the outer circumference of the cylindrical portion 12a is formed into a cylindrical surface shape.

As shown in FIG. 5, the inner peripheral surface of the input outer ring 11 and the outer peripheral surface of the cylindrical portion 12a of the output inner ring 12 are formed with a wedge gap s1 which is symmetrically reduced in both forward and reverse rotational directions. A plurality of cam surfaces 11a (the same number as the number of rollers 13) are formed at equal intervals in the circumferential direction. The wedge gap s1 has a circumferential center c1 larger than the diameter of the roller 13,
The clearance is symmetrically reduced from the center c1 in the circumferential direction in both the forward and reverse rotation directions. The roller 13 has a wedge gap s1
When the roller 13 is located at the center c1 in the circumferential direction, the roller 13 can rotate in the wedge gap s1.

The cage 14 has a cylindrical shape, and in a state in which the rollers 13 are held in a plurality of pockets 14a formed at equal intervals in the circumferential direction, the inner circumference of the input outer race 11 and the outer circumference of the cylindrical portion 12a of the output inner race 12 are retained. It is arranged between. As shown in FIG.
An axial notch 14b for accommodating the centering spring 15 is formed on an end face on one axial side of the retainer 14, and a notch part extending on the circumferential direction is formed on the end face on the other axial end. 14c is formed. In the illustrated example, the notch 1
4b and 14c are at 180 ° opposite positions in the radial direction.
The other end of the cage 14 in the axial direction protrudes from the end surface of the input outer ring 11 on the other end side, and a notch 14c extending in the circumferential direction is formed on the protruding portion.

The centering spring 15 is shown in FIG.
As shown in (b), it is composed of a leaf spring bent in a substantially U shape. As shown in FIGS. 2 and 3, the centering spring 15 is U-shaped after the notch portion 11d of the input outer ring 11 and the notch portion 14b of the retainer 14 have been phase-aligned in the circumferential direction in advance. Both the notches 1 with the direction of expansion and contraction of both ends oriented in the circumferential direction and with the U-shaped bottom portion 15a at the back
It is fitted to 1d and 14b. This centering spring 15
Has a function of elastically connecting the retainer 14 and the input outer ring 11 in the rotational direction, and the roller 13 accommodated in the pocket 14a of the retainer 14 causes the wedge center s1 of the wedge gap s1 in the circumferential direction.
It has a function of positioning (centering) the cage 14 with respect to the input outer ring 11 so as to be positioned at. FIG. 5 shows a state in which the cage 14 is centered by the centering spring 15. In this state, the circumferential center of the pocket 14a of the cage 14 and the circumferential center of the cam surface 11a of the input outer ring 11 are aligned. Incidentally, the roller 13 is located at the circumferential center c1 of the wedge gap s1.

The first side plate 16a and the second side plate 16b are
It is a member that does not rotate (a member that does not rotate) and is formed by pressing a metal plate or a resin molded product. As shown in FIG. 2, the side plates 16a and 16b are provided between the constituent elements of the clutch (input outer ring 11, output inner ring 12, roller 1).
3, cage 14, centering spring 15, sliding spring 1
7) is housed and is integrated by fastening means such as bolting.

The first side plate 16a has a retainer 14 at its inner diameter.
Portion 16a1 accommodating the other end of the roller and the sliding spring 17
And a receiving portion 16a2 extending from the other end of the cylindrical portion 16a1 toward the inner diameter side. The receiving portion 16a2 axially faces the end surface of the cylindrical portion 12a of the output inner ring 12, and the inner surface of the receiving portion 16a2 is pressed against the end surface of the cylindrical portion 12a. The second side plate 16b has an input outer ring 1 on the inner diameter side.
A cylindrical portion 16b1 accommodating 1 and a support portion 16b2 arranged on the inner diameter side thereof are formed. The shaft portion 12b of the output inner ring 12 is inserted into the inner periphery of the support portion 16b2, and the support portion 16b2 functions as a bearing portion (slide bearing) that rotatably supports the shaft portion 12b in the radial direction. A part of the cylindrical portion 16b1 of the second side plate 16b is cut off, and the tooth portion 11b of the input outer ring 11 is cut off at this cut portion.
Mesh with the drive gear 5 shown in FIG.

The sliding spring 17 is a sliding member that slides on the first side plate 16a, and is formed as an end ring-shaped spring material in this embodiment. This sliding spring 17 is shown in FIG.
, The ring-shaped sliding portion 17a and the sliding portion 17
It is provided with engaging portions 17b and 17c in which both ends of a are bent to the inner diameter side. The sliding portion 17a is slightly reduced in diameter and is pushed into the inner peripheral surface of the cylindrical portion 16a1 of the first side plate 16a, and elastically adheres to the inner peripheral surface of the cylindrical portion 16a1. Engaging part 17
Both b and 17c are inserted into the circumferential notch 14c on the other end side of the retainer 14, and in this state, the engaging portion 1
The circumferential distance between 7b and 17c is smaller than the circumferential length of the cutout portion 14c.

The operation of the reverse input cutoff clutch 1 will be described below.

In the initial state before the rotational torque is input to the input outer ring 11, the retainer 14 is centered by the centering spring 15 as shown in FIG. Therefore, the roller 1 accommodated in the pocket 14 a of the cage 14 is
3 is a circumferential center c1 of the wedge gap s1 between the cam surface 11a of the input outer ring 11 and the cylindrical portion 12a of the output inner ring 12.
Is located in.

When, for example, a rotational torque in the clockwise direction in the figure is input to the input outer ring 11 from the motor 3, the cage 14 connected to the input outer ring 11 by the centering spring 15 starts rotating together with the input outer ring 11. And the cage 14
Is rotated by a predetermined angle, as shown in FIG.
End face 14 on the rear side in the rotation direction that defines the notch 14c
d is in contact with the engaging portion 17c on the rear side of the sliding spring 17 in the rotational direction.

When the input outer ring 11 is further rotated, the sliding spring 17 rotates together with the end surface 14d of the cage 14 engaged with the engaging portion 17c of the sliding spring 17. At this time, the sliding spring 17 has the cylindrical portion 16a1 of the first side plate 16a.
Sliding and rotating on the inner circumference receives sliding frictional resistance from the stationary side. This sliding frictional resistance is transmitted to the cage 14 via the engaging portion 17c, and serves as a rotational resistance of the cage 14. Here, if the rotational resistance (torque) of the cage 14 caused by the sliding frictional resistance of the sliding spring 17 is set to be larger than the elastic force (spring torque) of the centering spring 15 in advance, the centering spring 15 will be elastically deformed. As a result, the cage 14 causes a rotation delay with respect to the input outer ring 11.

Due to the rotation delay of the cage 14, as shown in FIG. 9, the roller 13 held in the pocket 14a has the cam surface 11a of the input outer ring 11 and the cylindrical portion 12 of the output inner ring 12.
It is in a state of being caught in the wedge gap s1 between the outer peripheral surface of a. As a result, the rotational torque input to the input outer ring 11 is transmitted to the output inner ring 12 via the roller 13. When the counterclockwise rotation torque is input to the input outer ring 11, the output inner ring 12 rotates counterclockwise by the opposite operation.

When the input outer ring 11 stops, the restoring force of the centering spring 15 causes the roller 13 to separate from the wedge gap s1 and is centered at the circumferential center c1 of the wedge gap s1. The meshing force (residual torque) that acts on the roller 13 is large, and the roller 1 does not rotate even after the input outer ring 11 is stopped.
If 3 remains caught in the wedge gap s1,
By applying a counterclockwise (reverse rotation to the input rotation torque) rotational torque to the input outer ring 11 (by rotating the input outer ring 11 in the reverse direction), the roller 13 is wedged into the wedge gap s.
It can be detached from 1.

On the other hand, when reverse input torque is applied to the output inner ring 12 from the mirror portion 4, the sliding friction resistance of the sliding spring 17 does not occur, and the centering spring 15 acts so that the cage 14 is in the centering state (see FIG. 5)). In this centering state, the roller 13 is located at the center of the wedge gap s1 in the circumferential direction, so that the roller 13 can rotate. From the above, it becomes possible to idle the output inner ring 12 to interrupt the transmission of the reverse input torque to the input side.

The regulating means 2 elastically engages the concave engaging portion 21 provided on one of the stationary side member or the output inner ring 12 and the convex engaging portion 22 provided on the other side. The mirror unit 4 is held in the storage position and the use position.

In FIG. 2, the first side plate 1 as a stationary member.
The case where the concave engaging portion 21 is formed in the receiving portion 16a2 of the 6a and the convex engaging portion 22 is formed in the cylindrical portion 12a of the output inner race 12 facing the receiving portion 16a2 is illustrated. Concave engagement portion 21
Is formed, for example, by recessing the inner surface of the receiving portion 16a2 of the first side plate 16a, and the formation position is
There are four locations that are evenly spaced 90 ° in the circumferential direction (Fig. 10
(See (a)). The convex engagement portion 22 is formed of, for example, a steel ball, and is housed in an axial hole 23 formed in the end surface of the cylindrical portion 12a of the output inner ring 12 via a second elastic member 24 such as a coil spring. In this embodiment, the convex engaging portion 22 is
Similar to the concave engaging portions 21, they are equally distributed in the circumferential direction by 90 °.
It is formed in four places. The convex engaging portion 22 is constantly pressed by the elastic force of the elastic member 24 toward the end surface of the receiving portion 16a2, and the concave engaging portions 21 are arranged on the rotation locus of the convex engaging portion 22. ing. Therefore, the convex engaging portion 22
Slides or rolls on the inner surface of the receiving portion 16a2 as the output inner ring 12 rotates, and protrudes when it faces the concave engaging portion 21 and elastically engages with the concave engaging portion 21.

With the above structure, when the mirror portion 4 is opened from the accommodation position to the use position or when the mirror portion 4 is closed from the use position to the accommodation position, the concave engagement portion 21 and the convex engagement portion 21 are projected when the mirror portion 4 is rotated by about 90 °. Since the groove-shaped engaging portion 22 elastically engages, the mirror portion 4 can be held at each position. As described above, the mirror unit 4 includes the reverse input cut-off clutch 1 that idles the output inner ring 12 against the reverse input torque.
Since there is a possibility that the mirror portion 4 may rotate due to the vibration of the vehicle body or the wind pressure during traveling, the rotation drive device according to the present invention has the regulation means 2 because The mirror portion 4 can be reliably fixed to each prescribed position against this type of external force.

When the concave engaging portion 21 and the convex engaging portion 22 face each other while the motor 3 is being driven, the convex engaging portion 22 falls into the concave engaging portion 21 and the rotation angle is determined by the engagement of both. However, at this time, since the drive current of the motor 3 increases due to the increase in torque, by detecting this, the mirror unit 4
It is possible to detect that the vehicle has reached the storage position or the use position and stop the motor based on this information. Therefore, the rotation angle can be detected without separately installing a rotation angle detection mechanism having a sensor or the like, and a low-cost electric retractable mirror having a compact structure can be provided.

When the mirror portion 4 comes into contact with a pedestrian, an obstacle, or the like and a large reverse input torque exceeding the spring sliding torque of the second elastic member 24 is applied to the output inner ring 12, the convex engagement portion is provided. 22 passes over the step of the concave engaging portion 21 and is separated from the concave engaging portion 21. After the separation, the output inner ring 12 idles and absorbs the external force, so that the damage to the mirror portion 4 can be avoided. At this time, the reverse input torque is not transmitted to the motor 3, the speed reducing mechanism 6, etc., so that damage to these mechanisms can be prevented.

The concave engaging portion 21 is formed by partially recessing the inner side surface as described above, and as shown in FIGS. 10 (a) and 10 (b), an annular protruding portion 26a is formed on the inner side surface. It can also be configured by In this case, the increase of the motor current value starts before the engagement of both the engaging portions 21 and 22. Therefore, by stopping the motor at the time when the current value exceeds the peak value and begins to decrease, the both engaging portions are stopped. 21 and 22 can be engaged reliably. 11 (a) and (b),
This is an example in which the concave engaging portion 21 is configured by forming two rows of linear protruding portions 26b orthogonal to the rotation direction of the convex engaging portion 21.

In this embodiment, the concave engaging portion 21 is provided on the first side plate 16a on the stationary side, and the convex engaging portion 22 is provided on the output inner ring 12 on the rotating side. The portion 21 may be provided on the rotating side member (for example, the output inner ring 12) and the convex engagement portion 22 may be provided on the stationary side member (for example, the first side plate 16a). Further, although four concave engaging portions 21 and four convex engaging portions 22 are formed, if either one is formed at two positions 90 ° apart, it suffices if the other is formed at at least one place. .

In the above description, the mirror portion of the electric retractable mirror of the automobile is exemplified as the driven member, but any member can be used as the driven member as long as the driven member is positioned at two or more positions. can do. The prescribed positions for positioning the driven member are not limited to two positions, but may be three or more positions. In that case, it is necessary to increase or decrease the number of engaging points of the concave engaging portion 21 and the convex engaging portion 22 according to the positioning position.

[0046]

As described above, according to the present invention, the reverse input cutoff clutch transmits the input torque from the motor to the driven member, while the reverse input torque applied to the output member is applied to the input member. Cut off the transmission of. Therefore, the input side (motor, speed reducer, etc.) of the output side member is not reversely driven by the reverse input torque, and damage to them can be avoided. When the reverse input torque is small, the driven member is held at the specified position, while when the reverse input torque is large, the output side member is idled to absorb the impact due to the external force. It is possible to avoid damage to the driven member.

[Brief description of drawings]

FIG. 1 is a sectional view of a rotation drive device according to the present invention.

FIG. 2 is a cross-sectional view of the reverse input cutoff clutch, which is taken along line B- in FIG.
The B section is shown.

3 is a cross-sectional view of the reverse input cutoff clutch, taken along line A- in FIG.
A cross section is shown.

FIG. 4A is a front view of the input outer ring viewed from the direction A in FIG. 4B, and FIG. 4B is a sectional view taken along line BB in FIG. 4A.

FIG. 5 is a partial enlarged cross-sectional view showing an operation (a neutral state) of the reverse input cutoff clutch.

6A is a sectional view of a cage, FIG. 6B is a plan view of the same, FIG. 6C is a sectional view taken along line CC of FIG. 6A, and FIG. It is the front view seen from the D direction in the inside.

FIG. 7A is a sectional view of a centering spring,
FIG. 6B is a plan view of the same.

FIG. 8 is a partial enlarged cross-sectional view showing the operation (sliding spring) of the reverse input cutoff clutch.

FIG. 9: Operation of reverse input cutoff clutch (torque transmission state)
It is a partial expanded sectional view showing.

10A is a plan view showing an embodiment of a concave engaging portion, and FIG. 10B is a sectional view taken along line AA in FIG. 10A.

11A is a plan view showing an embodiment of a concave engaging portion, and FIG. 11B is a sectional view taken along line AA in FIG. 11A.

FIG. 12 is a perspective view showing an example of an electric retractable mirror.

[Explanation of symbols]

1 Reverse input cutoff clutch 2 regulation means 3 motor 4 mirror section 6 Reduction mechanism 11 Input side member (input outer ring) 12 Output side member (output inner ring) 13 Torque transmission member (roller) 14 cage 15 First elastic member (centering spring) 16a Stationary member (first side plate) 16b Stationary member (second side plate) 17 Rotational resistance applying means (sliding spring) 21 concave engagement part 22 Convex engagement part 24 Second elastic member

Claims (8)

[Claims] 1. A device for moving a driven member between at least two predetermined positions, which is a motor, an input member to which torque from the motor is input, and an output member connected to the driven member. While transmitting the input torque applied to the input side member to the output side member, the reverse input torque applied to the output side member is blocked from being transmitted to the input side member, and the output side member A rotary drive device comprising: a reverse input cut-off clutch that allows idling; and a restriction unit that elastically restricts rotation of an output-side member at each specified position. 2. A reverse input cutoff clutch further holds a torque transmission member capable of engaging and disengaging with the input side member and the output side member in both forward and reverse rotation directions, and holding the torque transmission member, and relative to the input side member. A retainer that controls engagement / disengagement of the torque transmission member through rotation, a first elastic member that connects the input side member and the retainer in a rotation direction, a stationary side member, and rotation of the retainer with respect to the stationary side member. The rotation drive device according to claim 1, further comprising: a rotation resistance applying unit that applies a sliding friction resistance to the cage. 3. The stationary side includes a concave engagement portion provided on one of the output side member and the stationary side member, and a convex engagement portion provided on the other member. Of the output side member by elastically engaging the concave engagement portion and the convex engagement portion at each prescribed position by arranging the engagement portion on the rotation locus of the rotation side engagement portion. Claim 1 which regulates
Alternatively, the rotation drive device according to the item 2. 4. The rotary drive device according to claim 3, wherein the output side member and the stationary side member are axially opposed to each other, and a concave engagement portion and a convex engagement portion are disposed in the opposed portion. 5. With the engagement of the concave engaging portion and the convex engaging portion,
4. The rotary drive device according to claim 3, wherein the motor is stopped when the drive current of the motor increases. 6. The rotation resistance imparting means has a sliding member which is engageable with one of the retainer and the stationary member in the circumferential direction and which slides with respect to the other. The rotary drive device described above. 7. The rotary drive device according to claim 6, wherein the sliding member slides with respect to the stationary member in a state of being engaged with the retainer in the circumferential direction. 8. The rotary drive device according to claim 1, wherein the driven member is a mirror portion of a vehicle.