JP2013160316A - Clutch, motor and vehicle door opening/closing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch capable of preventing deformation of a driven-side rotor when a power transmission member moves radially outward.SOLUTION: A clutch 50 includes a driving-side rotor 51 which is rotated integrally with a rotary shaft 20, and a driven-side rotor 56 which is rotated integrally with a worm shaft. Between the driving-side rotor 51 and the driven-side rotor 56 in a radial direction, a roller member 52 is disposed, which is moved between a disengagement position where the driving-side rotor 51 and the driven-side rotor 56 are not engaged in a rotating direction, and an engagement position where the driving-side rotor 51 and the driven-side rotor 56 are engaged in the rotating direction. In the clutch 50, when the rotary shaft 20 is not driven, the roller member 52 is disposed at the disengagement position and disconnects the rotary shaft 20 from the worm shaft, and when the rotary shaft 20 is driven, the roller member 52 is moved radially outward and disposed at the engagement position, and thereby connecting the rotary shaft 20 and the worm shaft. The clutch 50 includes a stopper face 62n which regulates a moving amount of the roller member 52 moving radially outward.

Description

  The present invention relates to a mechanical clutch that connects and disconnects a drive shaft and a driven shaft, a motor including the clutch, and a vehicle door opening and closing device including the motor.

  2. Description of the Related Art In recent years, some automobiles equipped with a sliding door that opens and closes an entrance / exit provided on the side of a vehicle body are equipped with a vehicle door opening / closing device that automatically opens and closes the sliding door by a driving force of a motor. In this vehicle door opening and closing device, it is required that the sliding door can be manually opened and closed. Therefore, for example, the vehicle door opening and closing device described in Patent Document 1 includes a mechanical clutch that enables automatic opening and closing and manual opening and closing in a motor serving as a drive source.

  The motor described in Patent Document 1 includes a motor main body having a drive shaft that is rotated, and a speed reduction unit that has a gear housing that houses a speed reduction mechanism that decelerates the rotation of the drive shaft and is connected to the motor main body. . The speed reduction mechanism has a driven shaft to which the rotation of the drive shaft is transmitted via a mechanical clutch housed in the gear housing, and is connected to the slide door side. The clutch includes a drive-side rotator that can rotate integrally with the drive shaft, and a bottomed tubular driven-side rotator that has a cylindrical side wall portion that can rotate integrally with the driven shaft. The drive-side rotator includes a substantially disc-shaped drive-side first rotator disposed on the inner side of the driven-side rotator so as to be coaxial with the driven-side rotator, and a shaft on the drive-side first rotator. A driving-side second rotating body that is arranged in a direction and is connected to the driving-side first rotating body so as to be relatively rotatable by a coil spring. The clutch also includes a roller member (power transmission member) for connecting the driving side rotating body and the driven side rotating body. The roller member is inserted in the axial direction into the cylindrical sandwiching portion interposed between the driving-side first rotating body and the side wall portion of the driven-side rotating body facing each other in the radial direction, and the driving-side second rotating body. A cylindrical urging portion; and a connecting portion that connects the axial end of the clamping portion and the axial end of the urging portion so that the central axes of the clamping portion and the urging portion are displaced from each other. It has a crank shape. The power transmission unit is biased radially inward by a compression coil spring that biases the biasing portion radially inward.

  When the motor main body is stopped, the roller member is urged radially inward by the compression coil spring, so that the driving-side rotating body and the driven-side rotating body are not engaged in the rotational direction. The drive shaft and the driven shaft are disconnected from each other. Therefore, even if the driven shaft rotates, the drive shaft is not rotated, so that it is possible to easily open and close the door manually.

  On the other hand, when the motor body is driven, the roller member circulates with the rotation of the driving side rotating body. When the centrifugal force at the time of rotation becomes larger than the urging force of the compression coil spring, the roller member is moved radially outward from the non-engagement position, and is sandwiched between the driving-side first rotating body and the driven-side rotating body. Is moved to an engaging position (clamping position). And since a drive side rotary body and a driven side rotary body are engaged in a rotation direction via a roller member, a driven side rotary body is rotated with a drive side rotary body. As a result, the driven shaft is rotated, and the slide door connected to the driven shaft is automatically opened and closed.

  If such a mechanical clutch is used, it is not necessary to carry out wiring for power feeding inside the motor as in the case of using an electromagnetic clutch, for example, and the internal structure of the motor becomes complicated. Is suppressed.

JP 2010-223375 A

  However, in the clutch described in Patent Document 1, when the motor main body is driven, a force directed radially outward, such as a centrifugal force, acts on the roller member. And the clamping part of the roller member was pressed from the inner side against the side wall part of the driven cylindrical part, and the driven side rotating body sometimes deformed toward the radially outer side. When the driven-side rotator is deformed radially outward, the driven-side rotator comes into contact with parts around the clutch (for example, a gear housing) of the motor, and the driven-side rotator may be worn.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a clutch capable of suppressing deformation of a driven-side rotating body due to a radially outward movement of a power transmission member, and a motor including the clutch. Another object of the present invention is to provide a vehicle door opening / closing device provided with the motor.

  In order to solve the above-described problem, the invention according to claim 1 is directed to a drive-side rotator provided so as to be integrally rotatable with the drive shaft, a driven-side rotator provided so as to be integrally rotatable with the driven shaft, and the radial direction. It is arranged between the driving side rotating body and the driven side rotating body and is provided so as to be able to rotate integrally with the driving side rotating body, and does not engage the driving side rotating body and the driven side rotating body in the rotation direction. A power transmission member that is moved between a non-engagement position and an engagement position that engages the drive-side rotator and the driven-side rotator in the rotation direction on the radially outer side than the non-engagement position; When the drive shaft is not driven, the power transmission member is disposed at the non-engagement position to disconnect the drive shaft and the driven shaft, while the drive-side rotating body is driven by the drive shaft. When rotating, the power transmission member moves radially outward A clutch that connects the drive shaft and the driven shaft by being arranged at the engagement position, and includes a stopper that restricts the amount of movement of the power transmission member radially outward. It is said.

  According to this configuration, the amount of movement of the power transmission member to the outside in the radial direction is regulated by the stopper. Accordingly, it is possible to reduce the radially outward force acting on the driven side rotating body from the power transmission member. As a result, it is possible to suppress deformation of the driven-side rotator due to the movement of the power transmission member radially outward.

  According to a second aspect of the present invention, in the clutch according to the first aspect, the driven rotary body includes a side wall portion that is formed in a cylindrical shape and that is radially opposed to the power transmission member disposed on the inner side. The inner peripheral surface of the side wall portion is formed on the inner peripheral surface of the side wall portion by providing the control convex portion protruding radially inward from the inner peripheral surface of the side wall portion and the control convex portion. A control recess that opens radially inward is formed, and the power transmission member is inserted into the control recess from the radially inner side when moving to the engagement position when the drive side rotating body is driven to rotate. The drive-side rotating body can be brought into contact with the control projection from the rotation direction and can be sandwiched between the control projection and the drive-side rotation body. By regulating the amount of movement outward in the direction, And as its gist to prevent contact with the bottom surface of the control recesses of the power transmitting member moved to Kigakarigo position.

  According to this configuration, the stopper prevents the power transmission member that has moved to the engagement position from coming into contact with the bottom surface of the control recess. It can be reduced more. As a result, it is possible to further suppress the deformation of the driven-side rotator due to the movement of the power transmission member outward in the radial direction.

  According to a third aspect of the present invention, in the clutch according to the first or second aspect, the stopper is formed on at least one of the components of the clutch other than the power transmission member, and is in a radial direction with respect to the power transmission member. The gist of the present invention is that it is a stopper surface that comes into contact with the power transmission member that has moved to the outside in the radial direction.

  According to this configuration, the stopper is a simple structure because it is a stopper surface formed on at least one of the components of the clutch other than the power transmission member. Then, the amount of movement of the power transmission member to the outside in the radial direction can be easily restricted simply by bringing the power transmission member into contact with the stopper surface having a simple structure.

  According to a fourth aspect of the present invention, in the clutch according to any one of the first to third aspects, the stopper is displaced in the axial direction with respect to the power transmission member moved to the engagement position. The gist is to restrict the amount of movement of the power transmission member in the radial direction by acting at a plurality of locations.

  According to this configuration, since the power transmission member that has moved to the engagement position can be prevented from being inclined with respect to the axial direction, the connection between the drive-side rotator and the driven-side rotator via the power transmission member is unstable. Can be suppressed. As a result, the rotational driving force can be stably transmitted from the driving side rotating body to the driven side rotating body via the power transmission member when the driving side rotating body is rotationally driven.

  The invention according to claim 5 includes a motor body having the drive shaft that is rotationally driven, and the driven shaft that is disposed coaxially with the drive shaft and rotated by a rotational driving force of the drive shaft, A speed reduction mechanism that decelerates and outputs the rotation of the drive shaft, a clutch according to any one of claims 1 to 4 disposed between the drive shaft and the driven shaft, and the motor body. The gist is that the motor is provided with a gear housing which is connected and accommodates the speed reduction mechanism and the clutch therein.

  According to this configuration, since the deformation of the driven-side rotating body due to the movement of the power transmission member radially outward is suppressed, the clutch comes into contact with the inner peripheral surface of the gear housing that houses the clutch. Is suppressed. Therefore, since the clutch is prevented from being slidably contacted with the inner peripheral surface of the gear housing, the life of the motor can be extended.

  The invention according to claim 6 is a vehicle door opening and closing device configured to open and close a door for opening and closing an opening provided in the vehicle by the driving force of the motor according to claim 5. When a command to automatically open / close is generated, the drive shaft is connected to the driven shaft by the clutch together with driving of the motor main body to automatically open / close the door, while the driven by the clutch when the motor main body is stopped. The gist of the invention is to provide a vehicle door opening and closing device characterized in that the shaft is disconnected from the drive shaft to reduce the operating load during manual opening and closing of the door.

  According to this configuration, since the motor used as the drive source has a long life, the frequency of maintenance such as motor replacement in the vehicle door opening and closing device can be reduced.

  ADVANTAGE OF THE INVENTION According to this invention, the clutch which can suppress a deformation | transformation of the driven side rotary body by the movement to the radial direction outer side of a power transmission member, the motor provided with this clutch, and the vehicle door opening / closing apparatus provided with this motor are provided. it can.

Sectional drawing of a motor with a clutch. The schematic block diagram of a sliding door opening / closing apparatus. Sectional drawing of the clutch of 1st Embodiment (CC sectional drawing in FIG. 8). The disassembled perspective view of the clutch of 1st Embodiment. The disassembled perspective view of the clutch of 1st Embodiment. (A) is a top view of the 2nd drive plate in 1st Embodiment, (b) is sectional drawing of the 2nd drive plate in 1st Embodiment. (A) is a top view of the roller member in 1st Embodiment, (b) is a side view of the roller member in 1st Embodiment. Sectional drawing (AA sectional drawing in FIG. 3) of the clutch of 1st Embodiment. Sectional drawing (BB sectional drawing in FIG. 3) of the clutch of 1st Embodiment. (A) And (b) is sectional drawing of the clutch of 1st Embodiment. (A) And (b) is sectional drawing of the clutch of 1st Embodiment. (A) And (b) is sectional drawing of the clutch of 1st Embodiment. (A) And (b) is sectional drawing of the clutch of 1st Embodiment. Sectional drawing of the clutch of 1st Embodiment. Sectional drawing of the clutch of 1st Embodiment. Sectional drawing of the clutch of 1st Embodiment. Sectional drawing of the clutch of 2nd Embodiment. The disassembled perspective view of the clutch of 2nd Embodiment. (A) is a top view of the 2nd drive plate in 2nd Embodiment, (b) is sectional drawing of the 2nd drive plate in 2nd Embodiment. (A) is a top view of the roller member in 2nd Embodiment, (b) is a side view of the roller member in 2nd Embodiment. (A) And (b) is a perspective view of the 2nd drive plate and roller member in 2nd Embodiment. (A) And (b) is a perspective view of the 2nd drive plate and roller member in 2nd Embodiment. Sectional drawing of the clutch of 2nd Embodiment. Sectional drawing of the clutch of 2nd Embodiment. Sectional drawing of the clutch of 2nd Embodiment.

(First embodiment)
A first embodiment of the present invention will be described below with reference to the drawings.
As shown in FIG. 2, the motor 11 of the present embodiment shown in FIG. 1 is used as a drive source for a slide door opening / closing device 1 mounted on an automobile. The slide door opening / closing device 1 is disposed in a slide door 3 that is slidable along the side surface of the vehicle body 2. The slide door 3 is supported by a connector 5 connected to a guide rail 4 provided on the vehicle body 2. The connector 5 moves along the guide rail 4 by winding and feeding out the wire cable 6 by driving the motor 11. The sliding door 3 opens and closes the entrance / exit 2a formed in the vehicle body 2 by the movement of the connector 5.

  As shown in FIG. 1, the motor 11 is a so-called geared motor including a motor body 12 and a speed reduction unit 13. The motor body 12 includes a yoke housing 14, a pair of magnets 15, an armature 16, a brush holder 17, and a pair of brushes 18.

  The yoke housing 14 has a bottomed cylindrical shape, and a pair of magnets 15 are fixed to the inner peripheral surface thereof. A bearing 19 is provided at the center of the bottom of the yoke housing 14, and the bearing 19 pivotally supports the base end portion of the rotating shaft 20 (drive shaft) of the armature 16 disposed inside the yoke housing 14. ing.

  A flange-like flange portion 14b extending radially outward is formed in the opening portion 14a of the yoke housing 14. The flange portion 14b is connected and fixed to the gear housing 31 with a screw 21 in a state where the brush holder 17 is interposed between the flange portion 14b and an opening portion 31a of the gear housing 31 of the speed reduction portion 13 described later.

  The brush holder 17 substantially closes the opening 14 a of the yoke housing 14. The brush holder 17 includes, in the yoke housing 14, a bearing 22 that pivotally supports a tip side portion of the rotary shaft 20 and a pair of brushes 18 that are in sliding contact with a commutator 23 fixed to the rotary shaft 20. keeping. Further, in the brush holder 17, the connector portion 17 a protruding to the outside of the yoke housing 14 and the gear housing 31 is a portion to which a vehicle body side connector (not shown) extending from the vehicle body side is connected. A plurality of terminals 24 are exposed in the connection recess 17b of the connector portion 17a. These terminals 24 are inserted into the brush holder 17 and are electrically connected to a rotation sensor (a hall element 42 described later) provided in the motor 11, the brush 18, and the like. When the vehicle body side connector is connected to the connector portion 17a, the controller 25 and the motor 11 provided on the vehicle body side are electrically connected. As a result, power supply and output of sensor signals and the like can be performed between the motor 11 and the controller 25.

The speed reduction unit 13 includes a gear housing 31, a speed reduction mechanism 34 including a worm shaft 32 (driven shaft) and a worm wheel 33, an output shaft 35, and a clutch 50.
The gear housing 31 includes an opening 31a facing the opening 14a of the yoke housing 14, and the brush holder 17 is interposed between the openings 14a and 31a. The gear housing 31 is formed with a clutch housing portion 31b that is recessed from the opening 31a of the gear housing 31 in the axial direction. Further, the gear housing 31 accommodates a worm wheel 33 that is connected to the substantially cylindrical shaft accommodating cylinder portion 31c and extends in the axial direction from the bottom of the clutch accommodating portion 31b and accommodates the worm shaft 32, and is connected to the shaft accommodating cylinder portion 31c. A substantially circular wheel housing portion 31d is formed.

  Bearings 36 and 37 are disposed at both ends in the axial direction of the shaft accommodating cylinder portion 31c. The worm shaft 32 is coaxial with the rotary shaft 20 in a state where the tip end portion is supported by the bearing 37 (that is, the central axes of the rotary shaft 20 and the worm shaft 32 coincide with each other). As in the case of the shaft housing cylinder portion 31c. A worm portion 32 a having a screw tooth shape is formed at a substantially central portion in the axial direction of the worm shaft 32.

  A ring-shaped sensor magnet 41 magnetized in the circumferential direction between the worm portion 32 a and the portion supported by the bearing 37 in the worm shaft 32 is mounted so as to rotate integrally with the worm shaft 32. Has been. A hall element 42 that detects a change in the magnetic field associated with the rotation of the sensor magnet 41 is disposed in a portion of the shaft housing cylinder portion 31 c that faces the outer peripheral surface of the sensor magnet 41. The Hall element 42 is a signal for detecting rotation information such as the rotation speed and rotation speed of the worm shaft 32, and outputs a rotation detection signal that is a signal corresponding to a change in the magnetic field accompanying the rotation of the sensor magnet 41. . The controller 25 detects the opening / closing position and opening / closing speed of the slide door 3 based on the rotation detection signal.

  A disc-shaped worm wheel 33 that meshes with the worm portion 32a of the worm shaft 32 is rotatably accommodated in the wheel accommodating portion 31d. An output shaft 35 is fixed to the central portion of the worm wheel 33 in the radial direction so as to rotate integrally with the worm wheel 33. As shown in FIG. 2, a drive pulley (not shown) on which the wire cable 6 for opening and closing the slide door 3 is engaged is connected to the output shaft 35 so as to rotate integrally.

  As shown in FIG. 1, the clutch housing portion 31 b houses a mechanical clutch 50 that is disposed between the worm shaft 32 and the rotating shaft 20 and connects and disconnects the worm shaft 32 and the rotating shaft 20. Has been. As shown in FIG. 4, the clutch 50 includes a driving side rotating body 51, two roller members 52, two return springs 53, a holding case 54, two guide members 55, and a driven side rotating body 56.

The drive-side rotator 51 includes a first drive plate 61, a second drive plate 62 disposed so as to overlap the first drive plate 61, and two connecting springs 63.
The first drive plate 61 has a substantially disc shape, and has a cylindrical drive-side shaft coupling portion 61 a that protrudes in the axial direction at the center in the radial direction. A shaft coupling recess 61b is formed in the radial central portion of the drive side shaft coupling portion 61a (that is, the radial central portion of the first drive plate 61). The shaft coupling recess 61b extends along the axial direction from the axial end surface on the second driving plate 62 side in the driving side shaft coupling portion 61a toward the axial end surface on the driven side rotating body 56 side in the first driving plate 61. The shape seen from the axial direction forms a two-sided width shape. Then, as shown in FIG. 3, the tip of the rotating shaft 20 has a two-sided width shape corresponding to the shaft connecting recess 61b, and when the tip of the rotating shaft 20 is inserted into the shaft connecting recess 61b, The first drive plate 61 is engaged with the distal end portion of the rotation shaft 20 in the rotation direction, and can rotate integrally with the rotation shaft 20. In addition, the connected rotating shaft 20 and the first drive plate 61 are coaxial (the respective central axes coincide with each other).

  Further, a plate accommodating portion 61c protruding in the axial direction is formed at the radial center portion of the axial end surface of the first driving plate 61 opposite to the second driving plate 62 (that is, the driven side rotating body 56 side). Has been. The plate accommodating portion 61c has an annular shape. A disc-shaped thrust receiving plate 71 is accommodated in the plate accommodating portion 61c.

  As shown in FIGS. 4 and 8, two control grooves 61 d are formed on the outer peripheral edge portion of the first drive plate 61. The two control grooves 61d are formed at two locations in the first drive plate 61 that are equiangularly spaced in the circumferential direction (180 ° intervals in the present embodiment). Each control groove 61d is recessed radially outward from the outer peripheral edge of the first drive plate 61, thereby opening radially outward. Each control groove 61d is recessed in the axial direction from the second drive plate 62 side, and opens only on one side in the axial direction (that is, the second drive plate 62 side). In FIG. 6, the cross section of the first drive plate 61 is not hatched in order to prevent the drawing from being complicated.

  The central portion in the circumferential direction of each control groove 61d is a non-engaging recess 61e that is deeply recessed in the radial direction. The inner peripheral surface of the non-engaging recess 61e is parallel to the axial direction and curved in an arc shape. By forming the non-engaging recess 61e, a pair of engaging recesses 61f that are shallower in the radial direction than the non-engaging recess 61e are formed on both sides of each control groove 61d in the circumferential direction of the non-engaging recess 61e. Is formed. The inner peripheral surface of each engaging recess 61f is a wedge surface 61g that is parallel to the axial direction and curved in an arc shape. The curvature of each wedge surface 61g is equal to the curvature of the inner peripheral surface of the non-engaging recess 61e, and the center of curvature of each wedge surface 61g is more than the center of curvature of the inner peripheral surface of the non-engaging recess 61e. 61 is located radially outside. Further, when viewed from the axial direction of the first drive plate 61, each control groove 61d is axisymmetric with a straight line (not shown) extending in the radial direction passing through the center in the circumferential direction of each control groove 61d as an axis of symmetry. .

  Further, two pairs of return convex portions 61 h are formed to project from the end surface of the first drive plate 61 in the axial direction on the second drive plate 62 side. The two pairs of return convex portions 61h are two locations that are equiangularly spaced in the circumferential direction (180 ° intervals in the present embodiment) in the first drive plate 61, and are between the control grooves 61d that are adjacent in the circumferential direction. Each is formed at a position. The pair of return convex portions 61h are formed at a distance in the circumferential direction of the first drive plate 61 and have a substantially rectangular parallelepiped shape protruding in the axial direction.

  As shown in FIGS. 3 and 5, the second drive plate 62 has a disk shape. The second drive plate 62 includes a disc-shaped guide portion 62a and a substantially disc-shaped accommodation portion 62b that protrudes from the guide portion 62a toward the first drive plate 61 along the axial direction. The guide part 62a and the accommodating part 62b are formed coaxially. Further, the outer diameter of the guide portion 62 a is formed larger than the outer diameter of the first drive plate 61, and the outer diameter of the housing portion 62 b is formed substantially equal to the outer diameter of the first drive plate 61. An insertion hole 62c penetrating in the axial direction is formed in the radial center of the second drive plate 62. The insertion hole 62c has a circular shape when viewed from the axial direction, and the inner diameter thereof is set to be approximately equal to the outer diameter of the drive side shaft coupling portion 61a.

  As shown in FIGS. 5 and 8, a pair of spring accommodating portions 62e is formed on the outer peripheral side of the insertion hole 62c in the accommodating portion 62b. The two spring accommodating portions 62e are formed by recessing the accommodating portion 62b in the axial direction from the end surface in the axial direction on the first drive plate 61 side in the accommodating portion 62b. And each spring accommodating part 62e penetrates the accommodating part 62b in the axial direction, and is recessed in the axial direction to the axial end of the accommodating part 62b side in the guide part 62a. The pair of spring accommodating portions 62e extend along the circumferential direction of the clutch 50 (same as the rotation direction of the first drive plate 61 and the second drive plate 62) and have an arc shape surrounding the insertion hole 62c. There is no. Furthermore, the two spring accommodating portions 62e have a symmetrical shape with the insertion hole 62c interposed therebetween. The springs 62e receive the connecting springs 63, respectively. Each connection spring 63 is a compression coil spring.

  Further, a pair of return accommodating portions 62f are formed on both sides of each spring accommodating portion 62e in the circumferential direction. That is, two pairs of return accommodating portions 62f are formed in the accommodating portion 62b. The return accommodating portions 62f that form a pair on both sides in the circumferential direction of each spring accommodating portion 62e are formed by recessing the accommodating portion 62b in the axial direction from the axial end surface of the accommodating portion 62b on the first drive plate 61 side. ing. The radial width of each return accommodating portion 62f is narrower than the radial width of the spring accommodating portion 62e, and is substantially equal to the radial width of the return convex portion 61h. Further, the circumferential width of each return accommodating portion 62f is formed longer than the circumferential width of the return convex portion 61h. Further, the axial depth of each return accommodating portion 62f is formed to be equal to the axial depth of the spring accommodating portion 62e and substantially equal to the axial length of the return convex portion 61h. Moreover, the internal space of the spring accommodating part 62e and the internal space of the return accommodating part 62f of the both sides of the circumferential direction are connected.

  The accommodating portion 62b has two locations between the return accommodating portions 62f adjacent in the circumferential direction, and two locations that are equiangularly spaced in the circumferential direction (180 ° intervals in the present embodiment) in the accommodating portion 62b. Each of the guide recesses 62g is formed. Each guide recess 62g is formed by recessing the accommodating portion 62b along the radial direction from the outer peripheral edge of the accommodating portion 62b. Each guide recess 62g opens outward in the radial direction and penetrates the accommodating portion 62b in the axial direction. In the present embodiment, each guide recess 62g has a U shape whose shape viewed from the axial direction opens radially outward. Further, the circumferential width of each guide recess 62g is formed substantially equal to the circumferential width of the non-engaging recess 61e.

  The guide portion 62a is formed with insertion engaging portions 62h at two locations adjacent to the two guide recess portions 62g in the axial direction. The two insertion engaging portions 62h are formed at equal angular intervals in the circumferential direction (180 ° intervals in the present embodiment). Each insertion engagement portion 62h is formed by recessing the guide portion 62a in the axial direction from the end surface of the guide portion 62a opposite to the housing portion 62b in the axial direction. Further, as shown in FIGS. 6A and 6B, each insertion engaging portion 62h has a diameter larger than that of the guide recess 62g from a position adjacent to the radially inner end of the guide recess 62g in the axial direction. It has a groove shape extending along the radial direction to a position that is on the outer side in the direction (outer in the radial direction than the outer peripheral edge of the accommodating portion 62b). The circumferential width of each insertion engaging portion 62h is narrower than the circumferential width of the guide recess 62g. A portion of each insertion engagement portion 62h adjacent to the guide recess 62g in the axial direction penetrates the guide portion 62a in the axial direction and communicates with the guide recess 62g. A portion radially outward from the guide recess 62g in each insertion engagement portion 62h is a stopper recess 62k having a recess shape without penetrating the guide portion 62a in the axial direction. The bottom 62m of the stopper recess 62k closes the axial end on the accommodating portion 62b side at the radially outer end of the insertion engagement portion 62h. Further, the radially inner end face of the bottom 62m of the stopper recess 62k is a stopper face 62n having a planar shape parallel to the axial direction. When the second drive plate 62 is viewed from the axial direction, the stopper surface 62n is orthogonal to the center line L1 of the insertion engaging portion 62h extending in the radial direction through the center in the circumferential direction of the insertion engaging portion 62h.

  The second drive plate 62 is formed with an insertion path 62p on the radially outer side of each spring accommodating portion 62e. Each insertion path 62p is linear along the radial direction from the center portion in the circumferential direction of each spring accommodating portion 62e to the outer peripheral surface of the second drive plate 62 (that is, the outer peripheral surface of the accommodating portion 62b and the outer peripheral surface of the guide portion 62a). It extends to. Further, as shown in FIG. 3, each insertion path 62 p opens to the first drive plate 61 side in the axial direction, and radially inside the spring accommodating portion 62 e and to the outer peripheral side of the second drive plate 62. It is open. Further, each insertion path 62p communicates with a spring accommodating portion 62e located on the radially inner side. In addition, the bottom surface of each insertion path 62p has a planar shape orthogonal to the axial direction, and is formed flush with the bottom surface of the spring accommodating portion 62e.

  As shown in FIGS. 3 to 5 and FIG. 8, the first drive plate 61 and the second drive plate 62 as described above are inserted with a pair of return convex portions 61h in a pair of return housing portions 62f. In addition, the drive side shaft coupling portion 61a is overlapped in the axial direction so as to be inserted into the insertion hole 62c. In the drive-side rotator 51, the first drive plate 61 and the second drive plate 62 are arranged on the same axis (so that their center axes coincide with each other). Further, the coupling springs 63 are arranged between the pair of return convex portions 61 h, whereby the first drive plate 61 and the second drive plate 62 are coupled in the rotational direction via the coupling springs 63. . The connection spring 63 is inserted into the spring accommodating portion 62e from the insertion path 62p in a state where the first drive plate 61 and the second drive plate 62 are overlapped. The first drive plate 61 and the second drive plate 62 can rotate relative to each other while resisting the urging force of the coupling spring 63 with the center axis of each other as the center of rotation. The first drive plate 61 and the second drive plate 62 are held at a predetermined relative rotational position by the urging force of the connection spring 63. In the present embodiment, the connection spring 63 has a relative rotational position between the first drive plate 61 and the second drive plate 62, a circumferential position of the control groove 61d (non-engaging recess 61e), and a circumferential direction of the guide recess 62g. The first drive plate 61 (returning convex portion 61h) is urged so as to be held at a neutral position where the position matches. Therefore, as shown in FIG. 6, when the rotary shaft 20 is not driven, when the drive side rotary body 51 is viewed from the axial direction, the circumferential center of the two control grooves 61 d and the circumferential direction of the two guide recesses 62 g are displayed. The center matches.

  As shown in FIG. 3, FIG. 4, FIG. 7 (a) and FIG. Similarly, a cam engaging portion 52c formed integrally with the connecting portion 52a and a roller member side stopper 52d extending from the cam engaging portion 52c are configured. Each roller member 52 has a crank shape.

  The connecting portion 52a has a plate shape in which the shape seen from the axial direction forms a track shape. The width of the connecting portion 52a in the short direction is formed to be substantially equal to the width in the circumferential direction of the guide recess 62g. The width in the longitudinal direction of the connecting portion 52a is formed to be substantially equal to the length in the radial direction of the guide recess 62g. Then, both end surfaces of the connecting portion 52a in the longitudinal direction have an arc shape having the same curvature as the inner peripheral surface of the non-engaging recess 61e. Further, the thickness of the connecting portion 52a is substantially equal to the axial width of the guide recess 62g (that is, the axial thickness of the accommodating portion 62b).

  The power transmission portion 52b is one end surface in the thickness direction (axial direction) of the connecting portion 52a, and one end portion in the longitudinal direction of the connecting portion 52a (end portion on the radially outer side when assembled as the clutch 50). It extends along the thickness direction (axial direction) of the connection part 52a from the part which becomes. The power transmission portion 52b has a cylindrical shape, and the axial length thereof is formed substantially equal to the axial length of the control groove 61d. In addition, the curvature of the cylindrical outer peripheral surface of the power transmission portion 52b is equal to the curvature of the inner peripheral surface of the non-engaging recess 61e and the wedge surface 61g.

  The cam engaging portion 52c is located on the other end surface (end surface 52f) in the thickness direction (axial direction) of the connecting portion 52a, on the other end in the longitudinal direction of the connecting portion 52a (inner side in the radial direction when assembled as the clutch 50) The end portion of the connecting portion 52a extends in the thickness direction (axial direction). The cam engagement portion 52c is formed in a columnar shape having a smaller diameter than the power transmission portion 52b, and the axial length thereof is longer than the axial thickness of the guide portion 62a. A flat biasing surface 52e is formed at the base end of the cam engagement portion 52c. The biasing surface 52e is parallel to the axial direction and faces one end side in the longitudinal direction of the connecting portion 52a (that is, the end portion side in the longitudinal direction on the side where the power transmission portion 52b is formed in the connecting portion 52a). Yes.

  The roller member side stopper 52d is orthogonal to the urging surface 52e from the axial end portion of the urging surface 52e on the connecting portion 52a side on the axial end surface 52f on the cam engaging portion 52c side of the linking portion 52a. It extends along the direction (same as the longitudinal direction of the connecting portion 52a). Accordingly, the roller member-side stopper 52d protrudes in the axial direction from the end surface 52f of the connecting portion 52a. The roller member-side stopper 52d has a thickness (axial thickness) substantially equal to the thickness (axial thickness) of the bottom 62m of the stopper recess 62k of the second drive plate 62. Further, the roller member side stopper surface 52g, which is the tip surface of the roller member side stopper 52d, is located at a position slightly shifted from the center in the longitudinal direction of the connecting portion 52a toward the power transmission portion 52b. The roller member-side stopper surface 52g has a planar shape parallel to the urging surface 52e.

  The two roller members 52 are connected to the two guide recesses 62g of the second drive plate 62 while the power transmission portions 52b are inserted into the two control grooves 61d of the first drive plate 61, respectively. It is assembled | attached with respect to the drive side rotary body 51 so that 52a may be inserted, respectively. Further, the two roller members 52 are arranged with respect to the drive-side rotating body 51 so that the cam engagement portions 52c are inserted into the two insertion engagement portions 62h of the second drive plate 62, respectively. In addition, as for the connection part 52a inserted in the guide recessed part 62g, the longitudinal direction corresponds with the radial direction, and the thickness direction corresponds with the axial direction. Further, in each roller member 52, the cam engaging portion 52c is positioned radially inward of the power transmission portion 52b, and the urging surface 52e faces the radially outer side. Further, the roller member-side stopper 52d of each roller member 52 opposes the bottom 62m of the stopper recess 62k of the insertion engaging portion 62h through which the roller member 52 is inserted, in the radial direction of the second drive plate 62. Accordingly, the roller member-side stopper surface 52g faces the stopper surface 62n located on the radially outer side of the roller member-side stopper surface 52g in the radial direction.

  Each roller member 52 slides the outer peripheral surface of the coupling portion 52a on the inner peripheral surface of the guide recess 62g, and simultaneously slides the outer peripheral surface of the cam engaging portion 52c on the inner peripheral surface of the insertion engaging portion 62h. It is possible to move in the radial direction with respect to the drive-side rotator 51. Therefore, the roller member 52 is guided in the radial movement by the guide recess 62g and the insertion engagement portion 62h, while the circumferential movement with respect to the second drive plate 62 is restricted by the guide recess 62g and the insertion engagement portion 62h. Is done. Further, the roller member 52 moving radially outward is restricted from moving further outward in the radial direction by the roller member side stopper surface 52g coming into contact with the bottom 62m of the stopper recess 62k. That is, the stopper surface 62n restricts the amount of movement of the roller member 52 outward in the radial direction. Further, each roller member 52 is engaged with the second drive plate 62 in the rotation direction by the coupling portion 52a being disposed in the guide recess 62g and the cam engagement portion 52c being inserted into the insertion engagement portion 62h. The second drive plate 62 can rotate integrally.

  Each insertion engagement portion 62h houses a return spring 53 at a position on the radially outer side of the cam engagement portion 52c. The return spring 53 of this embodiment is a compression coil spring. Each return spring 53 abuts against an urging surface 52e formed on the cam engaging portion 52c, and urges the roller member 52 radially inward along the radial direction.

  As shown in FIGS. 3, 5, and 9, the holding case 54 includes a disc-shaped cover part 54 a, an insertion part 54 b formed integrally with the cover part 54 a, and the cover part 54 a and the insertion part 54 b. And a pair of guide holding portions 54c formed integrally.

  The cover portion 54a has an outer diameter equal to the outer diameter of the guide portion 62a of the second drive plate 62. And the cylindrical insertion part 54b is formed in the center part of the radial direction of this cover part 54a. The insertion portion 54b extends along the axial direction from the axial end surface of the cover portion 54a on the second drive plate 62 side, and is formed coaxially with the cover portion 54a. The outer diameter of the insertion portion 54b is formed substantially equal to the inner diameter of the insertion hole 62c. Further, the insertion hole 54d formed in the central portion in the radial direction of the insertion portion 54b penetrates the insertion portion 54b and the cover portion 54a in the axial direction, and the inner diameter of the insertion hole 54d is equal to the outer diameter of the rotating shaft 20. It is formed approximately equally. The holding case 54 is inserted into the insertion hole 62c from the guide portion 62a side at the tip end portion of the insertion portion 54b (that is, the portion protruding in the axial direction from the guide holding portion 54c), whereby the drive side rotating body 51 is provided. With respect to each other, the center axis of each other is assembled so as to be able to rotate with each other. Further, the holding case 54 is coaxial with the drive-side rotator 51 (the center axes of the holding cases 54 coincide with each other).

  The pair of guide holding portions 54c are equiangularly spaced (180 ° intervals in this embodiment) in the circumferential direction on the outer peripheral surface of the insertion hole 54d on the axial end surface of the cover portion 54a on the second drive plate 62 side. The two portions extend radially outward along the radial direction, and then extend to both sides in the circumferential direction along the outer peripheral edge of the cover portion 54a. Each guide holding portion 54c is substantially T-shaped when viewed from the axial direction. By forming the guide holding portion 54c as described above, the holding case 54 is formed with holding recesses 54e at two locations between the two guide holding portions 54c and on both sides in the diameter direction of the insertion portion 54b. ing. Each holding recess 54e opens to the radially outer side and one side in the axial direction (second drive plate 62 side).

  A pair of regulating convex portions 54g is formed in the opening portion 54f that opens to the outside in the radial direction of each holding concave portion 54e. In each holding recess 54e, a pair of restricting projections 54g protrudes toward the inside of the guide recess 62g so as to narrow the circumferential width of the holding recess 54e. And the front-end | tip surface of the regulation convex part 54g which makes a pair is the guide surface 54h which makes mutually parallel in the circumferential direction. Each guide surface 54h is formed in parallel with an axial direction and in parallel with a straight line (not shown) passing through the center of the holding case 54 and passing through the center in the circumferential direction of the guide recess 62g.

  The guide members 55 are accommodated in the two holding recesses 54e, respectively. Each guide member 55 is a weight having a weight on which an inertial force acts. The axial thickness of each guide member 55 is formed to be equal to the axial width of the holding recess 54e. The end surface on the radially inner side of each guide member 55 is the inner surface 54m on the radially inner side of the holding recess 54e (that is, the outer peripheral surface of the insertion portion 54b and the portion extending in the radial direction of the cover portion 54a in the guide holding portion 54c). The shape corresponding to the surface composed of the side surfaces). Further, locking projections 55a are formed to project from both end faces of each guide member 55 in the circumferential direction. Each locking projection 55a is formed at the end on the inner surface 54m side of the holding recess 54e on both end surfaces in the circumferential direction of each guide member 55, and faces the regulation projection 54g. Further, both the circumferential end surfaces of each guide member 55 and the portions on the radially outer side (the opening 54 f side of the holding recess 54 e) than the locking projection 55 a are planar guided surfaces 55 b. Yes. The two guided surfaces 55b formed on each guide member 55 are parallel to the axial direction and parallel to each other. Further, in each guide member 55, the interval between the two guided surfaces 55b is formed substantially equal to the interval between the guide surfaces 54h forming a pair in each holding recess 54e. Further, the radially outer end surface 55c of each guide member 55 has an arc shape with the same curvature as the outer peripheral surface of the cover portion 54a.

  Such a guide member 55 is disposed between a pair of guide surfaces 54 h in the holding recess 54 e and is held by the holding case 54. Each guide member 55 is movable in the radial direction while bringing the guided surface 55b into sliding contact with the guide surface 54h. Accordingly, the guide member 55 is guided to move in the radial direction by the guide surface 54h, while the guide surface 54h restricts the movement in the circumferential direction with respect to the holding case 54. Furthermore, the guide member 55 can rotate integrally with the holding case 54 around the central axis of the holding case 54. In addition, each guide member 55 is disposed on the innermost radial direction within the moving range of the guide member 55 when the radially inner end surface is in contact with the inner side surface 54m of the holding recess 54e. Is the initial position. Each guide member 55 is movable outward in the radial direction until the locking projection 55a abuts on the regulation projection 54g. Each guide member 55 is arranged on the outermost radial direction within the movement range when the locking projection 55a is in contact with the regulation projection 54g. Each guide member 55 has the center of curvature of the radially outer end surface 55c coincides with the center of the holding case 54 when the locking projection 55a abuts on the regulation projection 54g.

  Each guide member 55 is formed with a cam groove 55d. As shown in FIG. 9, the cam groove 55 d has a groove shape extending substantially along the circumferential direction of the holding case 54 (or the second drive plate 62), and penetrates each guide member 55 in the axial direction. . Further, the cam groove 55d extends from the central portion in the circumferential direction (substantially the same as the longitudinal direction of the cam groove 55d) toward the radially outer side as it goes to both ends in the circumferential direction. Further, the width of the cam groove 55d (width in the short direction) is formed substantially equal to the outer diameter of the cam engaging portion 52c of the roller member 52. In the cam groove 55d of each guide member 55, the center in the circumferential direction (longitudinal direction) is the first guide portion P1, and both end portions in the circumferential direction (longitudinal direction) are the second guide portions P2. . The first guide portion P1 is located at the center of the guide member 55 in the circumferential direction. In a state where each guide member 55 is accommodated in the holding recess 54e, the first guide portion P1 is located on the innermost radial direction in the cam groove 55d, while the second guide portion P2 is located on the outermost radial direction in the cam groove 55d. Located in.

  Further, when viewed from the axial direction, the cam groove 55d of the present embodiment is formed in line symmetry with a straight line (not shown) extending in the radial direction passing through the first guide portion P1 as an axis of symmetry. Each cam groove 55d has an arc shape that swells radially outward from the first guide portion P1 to the second guide portion P2. And the shape which looked at the cam groove 55d from the axial direction has comprised the substantially V shape opened to a radial direction outer side. Furthermore, the cam groove 55d is provided with a pair of cam surfaces S facing in the radial direction (the short direction of the cam groove 55d). The cam surface S is an inner peripheral surface of the cam groove 55d and extends from the first guide portion P1 to the second guide portions P2 on both sides in the circumferential direction (longitudinal direction).

  As shown in FIGS. 3 and 9, the cam grooves 55d of the two guide members 55 respectively accommodated in the two holding recesses 54e are provided on the tip side portions of the cam engaging portions 52c of the two roller members 52, respectively. Has been inserted. By inserting the cam engagement portion 52c into the cam groove 55d, the roller member 52 is engaged with the cam groove 55d, and the movement along the longitudinal direction of the cam groove 55d with respect to the guide member 55 is guided. The movement of the cam groove 55d in the width direction is restricted. When the guide member 55 held by the holding case 54 and the drive-side rotator 51 are rotated relative to each other about the center axis of the drive-side rotator 51, the roller member 52 and the guide member 55 (cam groove 55d) are rotated. ) And relative rotation. Then, the roller member 52 is guided by the insertion engaging portion 62h in accordance with the radial position of the guide member 55 by the cam mechanism including the cam groove 55d and the cam engaging portion 52c, and the driving-side rotating body 51 in the radial direction. Is moved along. At this time, the roller member 52 is guided to move in the radial direction by the outer peripheral surface of the cam engaging portion 52c being in sliding contact with the cam surface S.

  As described above, the clutch 50 includes the cam groove 55d formed in the guide member 55 and the roller member 52 that engages with the cam groove 55d. As the guide member 55 and the drive-side rotator 51 rotate relative to each other, And a cam mechanism for guiding the movement of the roller member 52 in the radial direction by the cam groove 55d. As shown in FIGS. 8 and 9, with the guide member 55 arranged at the initial position, the cam engagement portion 52c is moved to the first guide of the cam groove 55d by the relative rotation of the drive side rotating body 51 and the guide member 55. When arranged in the part P1, the power transmission part 52b is arranged in the non-engaging recess 61e and arranged at the innermost radial direction within the radial movement range. The arrangement position of the roller member 52 at this time corresponds to a non-engaging position where the driving side rotating body 51 and a driven side rotating body 56 described later are not engaged in the rotation direction. That is, the initial position of the guide member 55 is a position where the roller member 52 can be disposed at the non-engagement position by the cam groove 55d. In the cam mechanism, the roller member 52 is disposed at the non-engagement position by disposing the cam engagement portion 52c in the first guide portion P1 of the cam groove 55d of the guide member 55 disposed at the initial position as described above. This is the initial state where the rotary shaft 20 and the worm shaft 32 are disconnected.

  On the other hand, as shown in FIG. 10B, with the guide member 55 disposed at the initial position, the cam engagement portion 52c is moved into the first position of the cam groove 55d by the relative rotation of the drive side rotating body 51 and the guide member 55. When arranged in the two guide portions P2, as shown in FIG. 10A, the power transmission portion 52b is arranged on the outermost radial direction within the radial movement range. At this time, a part of the power transmission part 52b protrudes radially outward from the outer peripheral surface of the first drive plate 61, and the arrangement position of the roller member 52 at this time depends on the drive-side rotating body 51 and that described later. This corresponds to an engagement position where the driven-side rotating body 56 is engaged in the rotation direction. The cam engaging portion 52c moves radially outward when moving from the first guide portion P1 to the second guide portion P2. Accordingly, the cam engagement portion 52c moves from the first guide portion P1 to the second guide portion P2 while contracting the return spring 53 in the radial direction against the urging force of the return spring 53. In the cam mechanism, the roller member 52 is disposed at the engagement position by disposing the cam engagement portion 52c in the second guide portion P2 of the cam groove 55d of the guide member 55 disposed at the initial position as described above. The state is a connected state in which the rotary shaft 20 and the worm shaft 32 are connected. In the connected cam mechanism, the return spring 53 urges the radially inner cam surface S radially inward through the cam engaging portion 52c of the roller member 52, Return to the initial state.

  The clutch 50 is constituted by a guide member 55 with which a roller member 52 is engaged, and the roller 50 is moved by the guide member 55 moved radially outward by the centrifugal force generated by rotating with the drive side rotating body 51. A holding mechanism for holding 52 in the engaged position is provided. The rotational force of the drive-side rotator 51 is transmitted from the roller member 52 urged radially inward by the return spring 53 to the guide member 55. In this holding mechanism, as shown in FIG. 10B, the state where the guide member 55 is disposed at the initial position is an initial state where the rotary shaft 20 and the worm shaft 32 are disconnected. Then, after the roller member 52 is moved to the second guide portion P2 by the cam mechanism and placed at the engagement position, the guide member 55 is guided to the drive side rotating body 51 while being moved radially outward by centrifugal force. When the member 55 is relatively rotated, the guide member 55 is rotated in the circumferential direction with respect to the roller member 52 as shown in FIG. At this time, although the cam engagement portion 52c moves from the second guide portion P2 to the first guide portion P1, the cam groove 55d is moved radially outward as the guide member 55 moves radially outward. The roller member 52 is maintained in a state of being disposed at the engagement position. In the holding mechanism, the guide member 55 is arranged at the outermost radial direction in the moving range as described above, and the cam engagement portion 52c is arranged at the first guide portion P1 of the cam groove 55d while the guide member 55 is arranged. A state in which the roller member 52 is held at the engagement position by 55 is a connection state in which the rotary shaft 20 and the worm shaft 32 are connected. The holding mechanism in the connected state is configured such that the return spring 53 biases the radially inner cam surface S radially inward along the radial direction via the cam engaging portion 52c of the roller member 52. Return to the initial state. In addition, since the radial movement of the guide member 55 is guided by the holding case 54, the holding mechanism functions well. Further, the guide member 55 receives the urging force of the return spring 53 when the drive side rotating body 51 is stopped, and moves radially inward while being guided by the holding case 54, so that the holding mechanism is returned to the initial state. It is done smoothly.

  As shown in FIG. 3, the driven side rotating body 56 includes a bottomed cylindrical driven cylindrical portion 56a and a driven side shaft connecting portion 56b formed integrally with the driven cylindrical portion 56a. As shown in FIG. 1, the driven-side rotating body 56 is accommodated in the clutch accommodating portion 31b so that the opening of the driven cylindrical portion 56a faces the motor main body 12 side.

  As shown in FIG. 3, the outer diameter of the driven cylindrical portion 56 a is equal to the outer diameters of the second drive plate 62 and the holding case 54. Further, the inner depth of the driven side rotating body 56 is substantially equal to the axial length of the first drive plate 61. As shown in FIG. 8, on the inner peripheral surface of the cylindrical side wall portion 56c of the driven cylindrical portion 56a, there are two circumferentially equiangular intervals (180 ° intervals in the present embodiment), radially inward. A protruding control projection 56d is formed. In the driven-side rotator 56, the inner diameter of the portion where the control convex portion 56 d is formed is slightly larger than the outer diameter of the first drive plate 61. And as shown in FIG. 3, the 1st drive plate 61 and the accommodating part 62b are accommodated in the inside of the driven cylindrical part 56a. The outer periphery of the first drive plate 61 accommodated in the driven cylindrical portion 56a faces the control convex portion 56d in the radial direction. Further, the power transmission portion 52 b of the roller member 52 is disposed between the first drive plate 61 and the side wall portion 56 c of the driven side rotating body 56 that are opposed in the radial direction. The drive-side rotator 51, the holding case 54, and the driven-side rotator 56 are arranged on the same axis (so that the central axes coincide). Further, the end of the side wall portion 56 c on the opening side of the driven cylindrical portion 56 a faces the outer peripheral edge portion of the guide portion 62 a of the second drive plate 62 in the axial direction.

  As shown in FIG. 8, by forming the control convex portion 56d on the inner peripheral surface of the side wall portion 56c, the control concave portion 56e is formed between the control convex portions 56d adjacent to each other in the circumferential direction inside the driven side rotating body 56. Is formed. The two control recesses 56e are formed at equal angular intervals in the circumferential direction (180 ° intervals in the present embodiment). The bottom surface 56f of the control recess 56e (that is, the inner peripheral surface of the side wall portion 56c) has an arc shape centered on the central axis (rotation axis) of the driven-side rotator 56. Further, as shown in FIG. 10A, the bottom surface 56f of the control recess 56e is more radial than the power transmission portion 52b when the roller member-side stopper surface 52g contacts the stopper surface 62n of the second drive plate 62. Located outside. The circumferential width of the control recess 56e is formed wider than the outer diameter of the power transmission portion 52b. In each control recess 56e, a pair of transmissions in which the inner side surfaces (the end surfaces in the circumferential direction of the control projection 56d) on both sides in the circumferential direction of the control recess 56e become wider in the circumferential direction toward the radially inner side. A surface 56g is formed. Each transmission surface 56g is formed in parallel with the axial direction.

  As shown in FIG. 3, a plate recess 56h that opens to the inside of the driven cylindrical portion 56a is formed in the center of the bottom of the driven cylindrical portion 56a. The plate recessed portion 56h is deeply recessed in the axial direction from the bottom of the driven cylindrical portion 56a in the axial direction to the driven side shaft coupling portion 56b. A disc-shaped thrust receiving plate 72 is accommodated in the bottom of the plate recess 56h. A thrust receiving ball 73 is accommodated in the plate recess 56h. The thrust receiving plate 73 and the thrust receiving plate 72 are in contact with the thrust receiving ball 73 from both sides in the axial direction. The thrust receiving plates 71 and 72 and the thrust receiving ball 73 both receive the thrust load of the rotating shaft 20.

  The driven side shaft coupling portion 56b extends along the axial direction from the center of the bottom of the driven cylindrical portion 56a and protrudes to the outside of the driven cylindrical portion 56a. Further, as shown in FIG. 1, the driven side shaft coupling portion 56 b has a cylindrical shape, and the outer diameter thereof is equal to the outer diameter of the worm side shaft coupling portion 32 b provided at the base end portion of the worm shaft 32. The size is assumed. In addition, the shaft connection recessed part 32c is formed in the base end surface (upper end surface in FIG. 1) of the worm side shaft connection part 32b in two places which become equiangular intervals (120 degree intervals) in the circumferential direction. FIG. 1 shows only one of the shaft coupling recesses 32c. Each of the shaft coupling recesses 32c is recessed along the axial direction of the worm shaft 32 from the base end surface of the worm side shaft coupling portion 32b, and on the base end side (upper side in FIG. 1) and radially outward of the worm shaft 32. It is open.

  As shown in FIG. 5, a shaft coupling convex portion 56k corresponding to the shaft coupling concave portion 32c (see FIG. 1) protrudes from the tip of the driven side shaft coupling portion 56b. The shaft coupling convex portion 56k is an outer peripheral edge at the tip of the driven side shaft coupling portion 56b, and projects in the axial direction from three locations that are equiangularly spaced in the circumferential direction (120 ° intervals in the present embodiment). In addition, each of the shaft coupling convex portions 56k has a circumferential width, a radial width, and an axial length that are equal to the circumferential width, the radial width, and the axial direction of the shaft coupling concave portion 32c (see FIG. 1). The depth of each is formed equal. As shown in FIGS. 1 and 3, by inserting the three shaft coupling convex portions 56k into the three shaft coupling concave portions 32c of the worm shaft 32, the driven side rotating body 56 and the worm shaft 32 are connected. It is engaged in the rotational direction and can rotate integrally. The driven-side shaft coupling portion 56b protrudes from the bottom of the clutch housing portion 31b into the shaft housing tube portion 31c and is pivotally supported by a bearing 36 disposed on one end side of the shaft housing tube portion 31c.

  In addition, the driven-side rotator 56 and the drive-side rotator 51 constitute a clamping mechanism that clamps the roller member 52 disposed at the engagement position. In this clamping mechanism, as shown in FIG. 8 or FIG. 10A, the power transmission portion 52b of the roller member 52 is formed by the wedge surface 61g of the driving side rotating body 51 and the transmission surface 56g of the driven side rotating body 56. The state in which the rotating shaft 20 and the worm shaft 32 are disconnected is a state in which the rotating shaft 20 and the worm shaft 32 are disconnected. On the other hand, as shown in FIG. 11A, in the clamping mechanism, the state where the power transmission portion 52b of the roller member 52 arranged at the engagement position is sandwiched between the wedge surface 61g and the transmission surface 56g is the rotation axis. 20 and the worm shaft 32 are connected. In this connected state, the first drive plate 61 is rotated relative to the second drive plate 62 while contracting the connection spring 63 against the urging force of the connection spring 63. Then, the clamping mechanism in the connected state is returned to the initial state by the urging force of the connecting spring 63. More specifically, the first drive plate rotates relative to the second drive plate 62 by the urging force of the connecting spring 63 that urges the return convex portion 61h (in FIG. 11A or counterclockwise in FIG. 12A). The first drive plate 61 and the second drive plate 62 are returned to the neutral position. Then, the wedge surface 61g is separated from the transmission surface 56g, and the holding of the power transmission unit 52b by the wedge surface 61g and the transmission surface 56g is released. That is, the clamping mechanism is returned to the initial state.

Next, the operation of the motor 11 of this embodiment will be described focusing on the operation of the clutch 50.
When the rotary shaft 20 is not rotationally driven as when the motor body 12 is stopped, as shown in FIGS. 8 and 9, the relative rotational position of the first drive plate 61 and the second drive plate 62 is By the urging force of the connecting spring 63 that urges the return convex portion 61h, the circumferential position of the two control grooves 61d and the circumferential position of the two guide concave portions 62g are maintained at a neutral position. Each guide member 55 is disposed at the initial position by the urging force of the return spring 53 transmitted through the cam engaging portion 52c because no centrifugal force is applied. Further, the cam engaging portion 52c is maintained in the state of being disposed in the first guide portion P1 by the urging force of the return spring 53, and the power transmission portion 52b is disengaged by the urging force of the return spring 53. It is maintained in a state of being placed inside. Therefore, the roller member 52 is located at the innermost radial position within the radial movement range, and is disposed at a non-engagement position where the roller member 52 does not engage with the driven side rotating body 56 in the rotational direction. Therefore, the cam mechanism, the holding mechanism, and the clamping mechanism are in an initial state, and the clutch 50 disconnects the rotating shaft 20 and the worm shaft 32.

  In this state, as shown in FIGS. 1 and 2, when the output shaft 35 is rotated from the slide door 3 side so as to manually open or close the slide door 3, the output shaft 35 is rotated. Thus, the worm shaft 32 is rotated. As shown in FIG. 8, when the rotary shaft 20 is not rotationally driven, the roller member 52 is disposed at the non-engagement position, so the driven-side rotator 56 does not engage with the roller member 52 in the rotation direction. The rotating shaft 20 and the worm shaft 32 are in a disconnected state. Therefore, the driven-side rotator 56 idles with respect to the drive-side rotator 51 as the worm shaft 32 rotates. Therefore, rotation from the output shaft 35 side becomes easy. Therefore, it is possible to easily open and close the slide door 3 manually without requiring a large operating force.

  Then, as shown in FIGS. 1 to 3, when a command to automatically open or close the slide door 3 is generated, the motor body 12 is driven by the controller 25 and the rotary shaft 20 is driven to rotate. The drive side rotating body 51 connected to the rotating shaft 20 starts to rotate. As shown in FIG. 6, at the start of the rotational drive of the drive-side rotator 51, the first drive plate 61 and the second drive plate 62 rotate almost integrally (with almost no relative rotation). Since the rotational driving force of the second drive plate 62 is transmitted from the inner peripheral surface of the insertion engaging portion 62h to the cam engaging portion 52c, the roller member 52 also has the center axis of the driving side rotating body 51 as the center of rotation. It rotates integrally with the drive side rotator 51. On the other hand, the rotation position of the guide member 55 and the holding case 54 that holds the guide member 55 is maintained by the inertial force that acts on the guide member 55 when the drive-side rotating body 51 starts to rotate. As a result, as shown in FIGS. 10A and 10B, the drive side rotating body 51 rotates relative to the guide member 55 and the holding case 54 at the start of the rotation drive. Then, a difference in rotation angle is generated between the guide member 55 held by the holding case 54 and the driving side rotating body 51. Then, since the cam engaging portion 52c is rotated in the circumferential direction of the holding case 54 with respect to the cam groove 55d, the cam mechanism is operated and the cam engaging portion 52c is guided to the cam surface S of the cam groove 55d. However, the first guide portion P1 is moved toward the second guide portion P2 on the front side in the rotation direction of the drive side rotating body 51. At this time, as shown in FIG. 14, the cam engagement portion 52 c is pressed against the cam surface S on the radially inner side while contracting the return spring 53 in the radial direction against the urging force of the return spring 53. The first guide portion P1 is moved to the second guide portion P2 while being moved outward in the direction. Then, due to the action of the cam surface S on the radially inner side in the cam groove 55d (that is, the cam surface S on which the roller member 52 is pressed in the radial direction by the return spring 53), the roller member 52 becomes unrelated to the radially inner side. It is moved from the mating position to the engagement position on the radially outer side. As shown in FIG. 10B, the guide member 55 held by the holding case 54 is maintained at its rotational position by the inertial force at the start of the rotation drive of the drive side rotator 51. Centrifugal force is not acting on the guide member 55. Therefore, when the cam engagement portion 52c moves relatively from the first guide portion P1 to the second guide portion P2 at the start of the rotational drive of the drive side rotator 51, the guide member 55 is disposed at the initial position. ing.

  As shown in FIGS. 10A and 15, the roller member 52 that has moved to the engagement position (that is, the roller member 52 in which the cam engagement portion 52c has been moved to the second guide portion P2) is a roller member side stopper. The roller member side stopper surface 52g of 52d contacts the stopper surface 62n of the second drive plate 62. The roller member 52 with the roller member-side stopper surface 52g in contact with the stopper surface 62n is prevented from further outward movement in the radial direction by the stopper surface 62n. The power transmission portion 52b of the roller member 52 is inserted into the control recess 56e from the inside in the radial direction when the roller member 52 is moved to the engaging position, but the stopper surface 62n contacts the roller member-side stopper surface 52g. This prevents the roller member 52 from moving outward in the radial direction before the power transmission portion 52b contacts the bottom surface 56f of the control recess 56e. Therefore, the power transmission portion 52b is not in contact with the bottom surface 56f of the control recess 56e. That is, the stopper surface 62n regulates the amount of movement of the roller member 52 outward in the radial direction so that the power transmission portion 52b of the roller member 52 moved to the engagement position comes into contact with the bottom surface 56f of the control recess 56e. Stop.

  Then, as shown in FIGS. 11A and 11B, the power transmission portion 52b of the roller member 52 disposed at the engagement position is moved into the control recess 56e as the drive side rotating body 51 rotates. Thus, it contacts the transmission surface 56g on the front side in the rotational direction of the drive side rotating body 51. Thereby, the rotational driving force of the rotating shaft 20 is transmitted in the order of the first driving plate 61, the connecting spring 63, the second driving plate 62, and the roller member 52, and further, the driven side rotation from the power transmission portion 52b of the roller member 52. It can be transmitted to the body 56.

  Further, at the start of the rotational drive of the drive side rotator 51, the slide door 3 connected to the driven side rotator 56 is stopped, so that a large load acts on the driven side rotator 56. Therefore, when the power transmission portion 52 b of the roller member 52 arranged at the engagement position contacts the front transmission surface 56 g in the rotation direction of the driving side rotating body 51, the roller member is caused by the reaction force received from the driven side rotating body 56. 52 is decelerated. And the 2nd drive plate 62 engaged with the roller member 52 in the cam engaging part 52c is also decelerated. On the other hand, as shown in FIG. 12A, the first drive plate 61 rotates in advance with respect to the second drive plate 62 while contracting the connection spring 63 against the urging force of the connection spring 63. That is, the first drive plate 61 rotates relative to the second drive plate 62. Accordingly, the first drive plate 61 rotates relative to the power transmission portion 52b of the roller member 52 that rotates integrally with the second drive plate 62, and the first drive plate 61 out of the pair of engaging recesses 61f of each control groove 61d. The power transmission portion 52b is disposed in the engagement concave portion 61f on the rear side in the rotational direction of the rotation, and the wedge surface 61g of the engagement concave portion 61f contacts the power transmission portion 52b from the rotational direction. And the power transmission part 52b is clamped by the wedge surface 61g and the transmission surface 56g. As a result, the rotational driving force of the rotary shaft 20 is transmitted from the first drive plate 61 to the driven-side rotator 56 via the power transmission portion 52b of the roller member 52 without passing through the connection spring 63 and the second drive plate 62. Then, the driven side rotator 56 starts to rotate.

  Further, as shown in FIGS. 11B and 12B, after the cam engagement portion 52c is disposed in the second guide portion P2, the roller that rotates together with the drive-side rotator 51 that has started to rotate. The guide member 55 to which the urging force of the return spring 53 is transmitted from the member 52 also starts to rotate with the drive side rotating body 51. When the rotation speed of the guide member 55 is increased during the rotation of the drive-side rotator 51, the inertial force acting on the guide member 55 is reduced as the rotation speed is increased. As the inertial force acting on the guide member 55 becomes smaller, the guide member 55 rotates together with the holding case 54 on the driving side by the action of the urging force of the return spring 53 transmitted through the cam engagement portion 52c. It rotates relative to the body 51 in the same direction as the driving side rotating body 51. Along with the relative rotation of the guide member 55 with respect to the drive-side rotator 51, the cam groove 55d of the guide member 55 held by the holding case 54 rotates in the circumferential direction of the holding case 54 with respect to the cam engaging portion 52c. Therefore, the cam engagement portion 52c is relatively moved from the second guide portion P2 to the first guide portion P1. At the same time, as the rotational speed of the guide member 55 increases, the centrifugal force acting on the guide member 55 gradually increases. Therefore, the guide member 55 is moved radially outward while being guided by the guide surface 54h. The Accordingly, since the radial position of the cam engagement portion 52c is maintained without changing in the radial direction, the roller member 52 is held at the engagement position by the guide member 55 (that is, the holding mechanism is in a connected state). .

  As shown in FIG. 16, when the driving side rotating body 51 rotates, a centrifugal force corresponding to the rotational speed of the driving side rotating body 51 acts on the roller member 52 that rotates together with the driving side rotating body 51. The centrifugal force tries to move the roller member 52 outward in the radial direction. When the roller member-side stopper surface 52g comes into contact with the stopper surface 62n, the amount of movement of the roller member 52 outward in the radial direction is the stopper surface. It is regulated by 62n. Accordingly, the roller member 52 is held at the engagement position without the power transmission portion 52b contacting the bottom surface 56f of the control recess 56e.

  Then, after the driven-side rotator 56 starts to rotate, as shown in FIG. 12A, when the load acting on the driven-side rotator 56 is larger than the urging force of the coupling spring 63, the first drive is performed. The plate 61 is rotated in the rotation direction of the first drive plate 61 with respect to the second drive plate 62 while contracting the connection spring 63 against the urging force of the connection spring 63. As a result, of the pair of wedge surfaces 61g of each control groove 61d, the wedge surface 61g on the rear side in the rotational direction of the first drive plate 61 contacts the outer peripheral surface of the power transmission unit 52b from the rotational direction, and the wedge surface 61g. And the transmission surface 56g sandwich the power transmission unit 52b (that is, the clamping mechanism is in a connected state). Then, the rotational driving force of the rotary shaft 20 is transmitted from the first drive plate 61 to the driven side rotating body 56 via the roller member 52. As a result, since the driven-side rotator 56 is rotated, the worm shaft 32 connected to the driven-side rotator 56 is rotated. And the rotational force decelerated by the worm part 32a and the worm wheel 33 is output from the output shaft 35, and the sliding door 3 is automatically opened or closed.

  On the other hand, as shown in FIGS. 13A and 13B, when the load acting on the driven-side rotator 56 is equal to or less than the urging force of the coupling spring 63, the first drive plate 61 and the second drive The plate 62 rotates integrally with the plate 62 while being held at the neutral position by the urging force of the coupling spring 63. Accordingly, the rotational driving force of the rotating shaft 20 is transmitted in the order of the first driving plate 61, the coupling spring 63, the second driving plate 62, the roller member 52, and the driven side rotating body 56. As a result, since the driven-side rotator 56 is rotated, the worm shaft 32 connected to the driven-side rotator 56 is rotated. And the rotational force decelerated by the worm part 32a and the worm wheel 33 is output from the output shaft 35, and the sliding door 3 is automatically opened or closed.

  When the motor main body 12 is stopped, the rotation speed of the rotating shaft 20 decreases. Then, as shown in FIG. 12A, when the motor main body 12 is stopped when the load acting on the driven side rotating body 56 is larger than the urging force of the connecting spring 63, The connection spring 63 that biases the return convex portion 61h rotates the first drive plate 61 in the direction opposite to the immediately preceding rotation direction. As a result, the first drive plate 61 is rotated relative to the second drive plate 62, and thus the holding of the power transmission portion 52b by the transmission surface 56g and the wedge surface 61g is released (that is, the holding mechanism is in the initial state). To return). Further, due to the urging force of the connecting spring 63, the relative rotational position of the first drive plate 61 and the second drive plate 62 matches the circumferential position of the two control grooves 61d and the circumferential position of the two guide recesses 62g. Return to the neutral position.

  Further, when the rotational speed of the drive-side rotator 51 decreases, the rotational speed of the guide member 55 and the driven-side rotator 56 that have been rotated by the rotational drive force transmitted from the drive-side rotator 51 via the roller member 52 is also increased. descend. Then, since the centrifugal force acting on the guide member 55 is reduced, the guide member 55 is moved radially inward by the urging force of the return spring 53 (that is, the holding mechanism returns to the initial state). As shown in FIGS. 8 and 9, the roller member 52 in which the cam engagement portion 52 c is inserted into the cam groove 55 d of the guide member 55 is moved radially inward together with the guide member 55. At this time, the cam engaging portion 52c is positioned in the first guide portion P1 in the cam groove 55d. Accordingly, the roller member 52 is moved from the engagement position to the non-engagement position. As a result, the rotation direction engagement between the driving side rotating body 51 and the driven side rotating body 56 is released, and the rotating shaft 20 and the worm shaft 32 are disconnected.

  13A and 13B, when the motor main body 12 is stopped, the load acting on the driven side rotating body 56 is smaller than the urging force of the coupling spring 63. In such a case, when the centrifugal force acting on the guide member 55 decreases as the rotational speed of the drive-side rotator 51 decreases, the guide member 55 is moved radially inward by the urging force of the return spring 53 ( That is, the holding mechanism is returned to the initial state). As shown in FIGS. 8 and 9, the roller member 52 is moved radially inward together with the guide member 55. At this time, since the cam engagement portion 52c is located at the first guide portion P1 in the cam groove 55d, the roller member 52 is moved from the engagement position to the non-engagement position. As a result, the rotation direction engagement between the driving side rotating body 51 and the driven side rotating body 56 is released, and the rotating shaft 20 and the worm shaft 32 are disconnected.

  10 (a) to 13 (a) show the clutch 50 when the driving side rotating body 51 (rotating shaft 20) is rotated clockwise in the drawing. However, the clutch 50 connects the rotary shaft 20 and the worm shaft 32 in the same manner when the rotary shaft 20 is rotated counterclockwise in FIGS. 10 (a) to 13 (a).

As described above, the first embodiment has the following effects.
(1) The amount of movement of the roller member 52 outward in the radial direction is regulated by the stopper surface 62n. Accordingly, it is possible to reduce the radially outward force that acts on the driven-side rotator 56 from the roller member 52. As a result, deformation of the driven-side rotator 56 due to the movement of the roller member 52 radially outward can be suppressed.

  (2) The stopper surface 62n regulates the amount of movement of the roller member 52 radially outward so that the power transmission portion 52b of the roller member 52 moved to the engagement position contacts the bottom surface 56f of the control recess 56e. To prevent. Accordingly, it is possible to further reduce the radially outward force that acts on the driven-side rotator 56 from the roller member 52. As a result, the deformation of the driven side rotating body 56 due to the movement of the roller member 52 radially outward can be further suppressed.

  (3) The stopper surface 62n has a simple structure because it is a flat surface formed on the second drive plate 62, which is a component of the clutch 50. Then, the amount of movement of the roller member 52 to the outside in the radial direction can be easily regulated only by bringing the roller member-side stopper 52d of the roller member 52 into contact with the stopper surface 62n having a simple structure. Further, the amount of movement of the roller member 52 to the radially outer side can be regulated without complicating the structure of the clutch 50 or increasing the size of the clutch 50.

  (4) Since the clutch 50 provided in the motor 11 suppresses deformation of the driven side rotating body 56 due to the movement of the roller member 52 radially outward, the inner periphery of the gear housing 31 in which the clutch 50 is accommodated. It is suppressed that the driven-side rotator 56 of the clutch 50 contacts the surface (specifically, the inner peripheral surface of the clutch housing portion 31b). Therefore, since the driven-side rotating body 56 is prevented from being slidably contacted with the inner peripheral surface of the gear housing 31, the life of the motor 11 can be extended.

  (5) Since the motor 11 used as a drive source of the sliding door opening / closing device 1 has a longer life due to the provision of the clutch 50, the sliding door opening / closing device 1 performs maintenance such as replacement of the motor 11. The frequency can be lowered.

(Second Embodiment)
Hereinafter, a second embodiment of the present invention will be described with reference to the drawings. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  A clutch 90 of the third embodiment shown in FIG. 17 is provided in the motor 11 instead of the clutch 50 of the first embodiment. Compared with the clutch 50, the clutch 90 includes a second drive plate 92 instead of the second drive plate 62 and a roller member 93 instead of the roller member 52.

  As shown in FIGS. 18, 19 (a), and 19 (b), the second drive plate 92 constitutes the drive side rotating body 51 together with the first drive plate 61 and the connecting spring 63. The second drive plate 92 has two locations between the two spring accommodating portions 62e, and two locations that are equiangularly spaced in the circumferential direction (180 ° intervals in the present embodiment) in the second drive plate 92. In addition, restricting recesses 92a are respectively formed. Each regulating recess 92a is recessed from the end surface of the second drive plate 92 on the first drive plate 61 side (that is, the end surface in the axial direction opposite to the guide portion 62a in the housing portion 62b) in the axial direction. It is formed. Specifically, each regulating recess 92a is formed by recessing the guide portion 62a in the axial direction by more than half in the axial direction. Each regulating recess 92a has a substantially square shape when viewed from the axial direction. A pair of inner side surfaces 92b on both sides in the circumferential direction of each regulating recess 92a are spaced apart from each other in the circumferential direction and have a planar shape parallel to the axial direction. Further, the two inner side surfaces 92b that form a pair are parallel to the center line L2 on both sides of the center line L2 of the restriction recess 92a that extends in the radial direction through the center in the circumferential direction of the restriction recess 92a. The distance between the pair of inner side surfaces 92 b is substantially equal to the diameter of the power transmission portion 52 b of the roller member 93.

  The second drive plate 92 is formed with insertion guide holes 92c penetrating the second drive plate 92 in the axial direction at two locations on the inner side in the radial direction of each regulating recess 92a. The insertion guide hole 92c has a substantially long hole shape extending in the radial direction along the center line L2 of the restriction recess 92a. And the edge part of the radial direction outer side of each insertion guide hole 92c is formed so that it may overlap with the control recessed part 92a located in the radial direction outer side. That is, the radially outer end of the insertion guide hole 92c is formed on the bottom 92d of the restriction recess 92a located on the radially outer side, while the radially inner end of the insertion guide hole 92c is the restriction recess. It is located radially inward of 92a. The circumferential width of each insertion guide hole 92 c is substantially equal to the diameter of the cam engaging portion 52 c of the roller member 93.

  Of the inner circumferential surface of each insertion guide hole 92c, the inner side surface of the radially outer end of each insertion guide hole 92c is a first stopper surface 92e. The first stopper surface 92e has a planar shape parallel to the axial direction, and is perpendicular to the center line L2 of the regulating recess 92a when the second drive plate 92 is viewed from the axial direction.

  The second drive plate 92 is formed with stopper recesses 92f at two locations on the radially inner side of the restricting recesses 92a. Each stopper recess 92f is formed by recessing the receiving portion 62b in the axial direction from the end surface of the receiving portion 62b opposite to the guide portion 62a in the axial direction. Each regulating recess 92a has a substantially square shape when viewed from the axial direction, and is wider than the regulating recess 92a in the circumferential direction. Further, when the second drive plate 92 is viewed from the axial direction, the radially inner end of each restricting recess 92a is formed at the bottom of the stopper recess 92f located on the radially inner side of each restricting recess 92a. Furthermore, the axial depth of each stopper recess 92f is shallower than the axial depth of the restriction recess 92a, and the axial position of the bottom surface 92g of each stopper recess 92f is less than the bottom 92d of the restriction recess 92a. It is close to the end face in the axial direction on the opposite side to the guide part 62a in the accommodating part 62b. And the bottom face 92g of each stopper recessed part 92f has comprised the planar shape orthogonal to an axial direction.

  A pair of second stopper surfaces 92k is formed on the inner surface of the radially outer end of each stopper recess 92f in the inner peripheral surface of each stopper recess 92f. The paired second stopper surfaces 92k are respectively provided on both sides of the restricting recess 92a located on the radially outer side of each stopper recess 92f. In addition, the pair of second stopper surfaces 92k is located on the radially inner side with respect to the first stopper surface 92e located therebetween. Each second stopper surface 92k is formed in a plane parallel to the axial direction, and is formed so as to be perpendicular to the center line L2 of the restricting recess 92a when the second drive plate 92 is viewed from the axial direction. . Each second stopper surface 92k is formed at a position shifted in the axial direction with respect to the first stopper surface 92e. Specifically, each second stopper surface 92k is formed at a position closer to the accommodating portion 62b than the first stopper surface 92e in the axial direction.

  In the second drive plate 92, a pair of return accommodating portions 92m are formed on both sides of each spring accommodating portion 62e in the circumferential direction. That is, the second drive plate 92 has two pairs of return accommodating portions 92m. The return accommodating portions 92m that form a pair on both sides in the circumferential direction of each spring accommodating portion 62e are formed by recessing the second drive plate 92 in the axial direction from the axial end surface of the accommodating portion 62b on the first drive plate 61 side. Has been. The pair of return accommodating portions 92m extend in the circumferential direction from the circumferential end of the spring accommodating portion 62e to the stopper recess 92f adjacent to the spring accommodating portion 62e in the circumferential direction, and the second drive plate It is formed in an arc shape centering on the central axis (rotation axis) of 92. The radial width of each return accommodating portion 92m is smaller than the radial width of the spring accommodating portion 62e, and is substantially equal to the radial width of the return convex portion 61h. Further, the axial depth of each return accommodating portion 92m is formed to be equal to the axial depth of the spring accommodating portion 62e and substantially equal to the axial length of the return convex portion 61h. The axial depth of each return accommodating portion 92m is deeper than the axial depth of the stopper recess 92f. Moreover, the internal space of the spring accommodating part 62e and the internal space of the return accommodating part 92m of the both sides of the circumferential direction are connected.

  In the second drive plate 92, insertion paths 92n and 92p are formed on the radially outer sides of the spring accommodating portions 62e, respectively. Each insertion path 92n, 92p opens to the first drive plate 61 side, and from the central portion in the circumferential direction of each spring accommodating portion 62e to the outer peripheral surface of the second drive plate 92 (that is, the outer peripheral surface of the accommodating portion 62b and the guide portion 62a). A concave shape extending to the outer peripheral surface).

  One insertion path 92n (the insertion path on the left side in FIG. 19 (a)) extends in the circumferential direction from the opening on the outer peripheral side of the insertion path 92n toward the position that is substantially the center in the radial direction of the insertion path 92n. After the width becomes narrower, the width in the circumferential direction becomes wider from the position toward the opening on the inner circumference side of the insertion path 92n. The inner diameter of the portion having the narrowest circumferential width in the insertion path 92 n is formed to be substantially equal to the outer diameter of the connection spring 63. The other insertion path 92p has a circumferential width that is substantially equal to the outer diameter of the coupling spring 63 and is curved with respect to the radial direction.

  As shown in FIGS. 17, 18, 19A and 19B, the second drive plate 92 and the first drive plate 61 as described above are paired in the return accommodating portion 92m that makes a pair. Each of the return convex portions 61h is inserted and overlapped in the axial direction so that the drive side shaft connecting portion 61a is inserted into the insertion hole 62c. In the drive-side rotator 51, the first drive plate 61 and the second drive plate 92 are arranged coaxially (so that their center axes coincide with each other). In addition, the connection spring 63 is disposed between the pair of return convex portions 61 h, whereby the first drive plate 61 and the second drive plate 92 are connected in the rotational direction via the connection spring 63. . The connection spring 63 is inserted into the spring accommodating portion 62e from the insertion paths 92n and 92p in a state where the first drive plate 61 and the second drive plate 92 are overlapped. The first drive plate 61 and the second drive plate 92 can rotate relative to each other while resisting the urging force of the coupling spring 63 with the center axis of each other as the center of rotation. The first drive plate 61 and the second drive plate 92 are held at a predetermined relative rotational position by the urging force of the connection spring 63. In the present embodiment, the coupling spring 63 determines the relative rotational position of the first drive plate 61 and the second drive plate 92, the circumferential position of the control groove 61d (non-engaging recess 61e), and the insertion guide hole 92c (restriction). The first drive plate 61 (returning convex portion 61h) is biased so as to be held at a neutral position where the circumferential position of the concave portion 92a) coincides.

  As shown in FIGS. 20A and 20B, the roller member 93 includes a connecting portion 52a, a power transmission portion 52b, and a cam engaging portion 52c, like the roller member 52 of the first embodiment. I have.

  A first roller member side stopper surface 93a that is parallel to the axial direction of the cam engaging portion 52c is formed on the outer peripheral surface of the cam engaging portion 52c. In addition, the outer diameter of the cam engaging portion 52c is reduced by forming a pair of protruding portions 93b between the cylindrical outer peripheral surface of the cam engaging portion 52c and the first roller member side stopper surface 93a. The first roller member side stopper surface 93a is formed on the outer peripheral surface of the cam engaging portion 52c. The first roller member side stopper surface 93a faces one end in the longitudinal direction of the connecting portion 52a on the side where the power transmission portion 52b is formed, and is formed in parallel with the short direction of the connecting portion 52a. . Further, the width of the first roller member side stopper surface 93a is formed to be equal to the diameter of the cam engaging portion 52c. Further, the first roller member side stopper surface 93a extends along the axial direction of the first roller member side stopper surface 93a from the base end of the cam engaging portion 52c to the substantially central portion of the cam engaging portion 52c. The first stopper surface 92e is longer in the axial direction than the axial length. Further, when the roller member 93 is viewed from the axial direction of the cam engaging portion 52c, the first roller member side stopper surface 93a is tangent to the cylindrical outer peripheral surface of the cam engaging portion 52c. Further, when the roller member 93 is viewed from the direction that is the diameter direction of the cam engaging portion 52c and the short side direction of the connecting portion 52a so that the first roller member side stopper surface 93a looks linear (that is, FIG. 20 (b)), the first roller member side stopper surface 93a and the cylindrical outer peripheral surface of the cam engagement portion 52c are connected in the axial direction without any step.

  A pair of roller member side stoppers 93c are formed integrally with the roller member 93 at both ends of the connecting portion 52a in the short direction of the connecting portion 52a on the side where the cam engaging portion 52c is formed. Yes. The pair of roller member side stoppers 93c protrude from both ends in the short direction of the connecting portion 52a at one end in the longitudinal direction of the connecting portion 52a, and each roller member side stopper 93c has a substantially rectangular parallelepiped shape. And the length of the longitudinal direction of the connection part 52a in each roller member side stopper 93c is formed shorter than the diameter of the cam engaging part 52c. Further, the width in the short direction of the connecting portion 52a at the portion of the roller member 93 where the pair of roller member side stoppers 93c are formed is substantially equal to the width in the circumferential direction of the stopper recess 92f (see FIG. 19A). Is formed. Further, each roller member side stopper 93c is arranged in the axial direction of the cam engaging portion 52c from the axial end surface of the connecting portion 52a on the power transmission portion 52b side in the axial direction of the cam engaging portion 52c. It extends over the base end of the cam engaging portion 52c beyond the end face of the cam. Accordingly, the two roller member side stoppers 93c that form a pair are provided on both sides of the cam engaging portion 52c in the diametrical direction at the base end portion of the cam engaging portion 52c.

  In addition, a second roller member-side stopper surface 93d is formed on an end surface on the power transmission portion 52b side of both end surfaces in the longitudinal direction of the connecting portion 52a in each roller member-side stopper 93c. Each of the second roller member side stopper surfaces 93d has a planar shape parallel to the axial direction of the cam engaging portion 52c and is formed in parallel with the first roller member side stopper surface 93a. Further, the two second roller member side stopper surfaces 93d have the same position in the longitudinal direction of the connecting portion 52a (formed at a position in the same plane) and are connected more than the first roller member side stopper surface 93a. It is located on the end portion side of the cam engaging portion 52c side in the portion 52a. And a pair of 2nd roller member side stopper surface 93d has shifted | deviated to the axial direction of the cam engaging part 52c with respect to the 1st roller member side stopper surface 93a.

  As shown in FIGS. 17, 18, 21 (a) and 21 (b), the two roller members 93 as described above have the power transmission portion 52 b in the two control grooves 61 d of the first drive plate 61. While being inserted respectively, it is assembled | attached with respect to the drive side rotary body 51 so that the cam engaging part 52c may be inserted in the two insertion guide holes 92c of the 2nd drive plate 92, respectively. Further, since the two roller members 93 are assembled to the drive side rotating body 51 such that the cam engaging portion 52c is positioned radially inward with respect to the power transmission portion 52b, the first roller member side stopper The surface 93a faces outward in the radial direction, and the first stopper surface 92e of the second drive plate 92 and the axial one end of the cam engaging portion 52c on the first roller member side stopper surface 93a are in the radial direction. Opposite to. Further, the two roller members 93 are arranged with respect to the drive side rotating body 51 so that the connecting portions 52a are respectively inserted into the portions formed in the accommodating portions 62b of the two restricting concave portions 92a of the second drive plate 92. ing. The connecting portion 52a inserted into the restricting recess 92a has a longitudinal direction that coincides with the radial direction of the second drive plate 92, and a thickness direction that coincides with the axial direction. Further, the two roller members 93 are arranged with respect to the drive-side rotating body 51 such that the pair of roller member-side stoppers 93c are respectively inserted into the two stopper recesses 92f of the second drive plate 92, and each stopper recess 92f. The pair of second stopper surfaces 92k and the pair of second roller member side stopper surfaces 93d face each other in the radial direction of the second drive plate 92. Further, the power transmission portion 52 b of each roller member 93 is disposed on the radially inner side of the side wall portion 56 c of the driven side rotating body 56. Accordingly, each power transmission part 52 b is disposed between the side wall part 56 c and the first drive plate 61 in the radial direction.

  Further, each roller member 93 is urged radially inward by the return spring 53 housed in the regulating recess 92a on the radially outer side than the cam engaging portion 52c. That is, the roller member 93 is urged radially inward by the return spring 53. Each roller member 93 slides the outer peripheral surface of the cam engaging portion 52c on the inner peripheral surface of the insertion guide hole 92c at the same time that the outer peripheral surface of the connecting portion 52a is slidably brought into contact with the pair of inner side surfaces 92b of the restricting recess 92a. It is possible to move in the radial direction with respect to the drive side rotating body 51 while making contact. Therefore, the roller member 93 is guided in the radial movement by the restriction recess 92a and the insertion guide hole 92c, while the circumferential movement with respect to the second drive plate 92 is restricted by the restriction recess 92a and the insertion guide hole 92c. . Further, the roller member 93 that moves radially outward is restricted from further outward movement in the radial direction by the first roller member-side stopper surface 93a coming into contact with the first stopper surface 92e. Further, the roller member 93 that moves radially outward is restricted from further outward movement in the radial direction when the pair of second roller member side stopper surfaces 93d abut against the second stopper surface 92k. When the first roller member side stopper surface 93a is in contact with the first stopper surface 92e, or when the second roller member side stopper surface 93d is in contact with the second stopper surface 92k, the power transmission unit 52b is The control recess 56e is located radially inward of the bottom surface 56f and does not contact the bottom surface 56f.

  The clutch 90 of the second embodiment as described above connects / disconnects the rotary shaft 20 and the worm shaft 32 in the same manner as the clutch 50 of the first embodiment when the motor 11 is driven / stopped. Hereinafter, the operation of the clutch 90 of the second embodiment different from that of the clutch 50 of the first embodiment will be described.

  When the motor main body 12 is driven, the rotary shaft 20 is driven to rotate, and the drive-side rotator 51 connected to the rotary shaft 20 starts to rotate. As shown in FIGS. 18 and 19A, at the start of the rotational drive of the drive-side rotator 51, the first drive plate 61 and the second drive plate 92 are substantially integrated (with almost no relative rotation). )Rotate. Since the rotational driving force of the second drive plate 92 is transmitted from the inner peripheral surface of the insertion guide hole 92c to the cam engaging portion 52c, the roller member 93 is also the same with the central axis of the drive side rotating body 51 as the rotation center. It rotates integrally with the drive side rotating body 51. On the other hand, the rotation position of the guide member 55 and the holding case 54 that holds the guide member 55 is maintained by the inertial force that acts on the guide member 55 when the drive-side rotating body 51 starts to rotate. As a result, the drive-side rotator 51 rotates relative to the guide member 55 and the holding case 54 at the start of the rotation drive, and the guide-side rotator 51 and the drive-side rotator 51 are held by the holding case 54. A difference in rotation angle occurs between them. Then, since the cam engaging portion 52c is rotated in the circumferential direction of the holding case 54 with respect to the cam groove 55d, the cam mechanism is operated and the cam engaging portion 52c is guided to the cam surface S of the cam groove 55d. However, the first guide portion P1 is moved toward the second guide portion P2 on the front side in the rotation direction of the drive side rotating body 51. At this time, as shown in FIG. 23, the cam engagement portion 52c is pressed against the cam surface S on the radially inner side while contracting the return spring 53 in the radial direction against the urging force of the return spring 53. The first guide part P1 is moved to the second guide part P2 (see FIG. 10B) while being moved outward in the direction. Then, due to the action of the cam surface S on the radially inner side in the cam groove 55d (that is, the cam surface S on which the roller member 93 is pressed in the radial direction by the return spring 53), the roller member 52 becomes unrelated to the radially inner side. It is moved from the mating position to the engagement position on the radially outer side. In addition, since the rotation position of the guide member 55 held by the holding case 54 is maintained by the inertial force when the drive side rotating body 51 starts to rotate, centrifugal force acts on the guide member 55. Not done. Therefore, when the cam engagement portion 52c moves relatively from the first guide portion P1 to the second guide portion P2 at the start of the rotational drive of the drive side rotator 51, the guide member 55 is disposed at the initial position. ing.

  Further, the roller member 93 is urged radially inward by a return spring 53 at a portion that is closer to the power transmission portion 52b than a portion of the cam engagement portion 52c that is inserted into the cam groove 55d. Accordingly, in the roller member 93, a drag force directed radially outward from the radially inner cam surface S of the cam groove 55d acts on the axial end on the distal end side of the cam engaging portion 52c. The force toward the radially outer side does not act on the axial end portion on the distal end side of the portion 52b. As a result, at the start of the rotational drive of the drive-side rotator 51, the roller member 93 moves to the engagement position in a state where the distal end is slightly inclined with respect to the proximal end of the cam engagement portion 52c so as to be positioned radially outward. Is done. Then, as shown in FIG. 24, the roller member 93 moved to the engagement position in an inclined state has the cam engagement portion 52c out of the first roller member side stopper surface 93a and the second roller member side stopper surface 93d. The first roller member-side stopper surface 93a closer to the tip is in contact with the first stopper surface 92e of the second drive plate 92. The roller member 93 whose first roller member side stopper surface 93a is in contact with the first stopper surface 92e is prevented from further outward movement in the radial direction by the first stopper surface 92e. The power transmission portion 52b of the roller member 93 is inserted into the control recess 56e from the inside in the radial direction when the roller member 93 is moved to the engagement position. The first stopper surface 92e is the first roller member-side stopper surface. By abutting on 93a, the roller member 93 is prevented from moving outward in the radial direction before the power transmission portion 52b abuts on the bottom surface 56f of the control recess 56e. Therefore, the power transmission portion 52b is not in contact with the bottom surface 56f of the control recess 56e. That is, the first stopper surface 92e restricts the amount of movement of the roller member 93 radially outward, so that the power transmission portion 52b of the roller member 93 moved to the engagement position contacts the bottom surface 56f of the control recess 56e. Stop that. Further, in this state, the roller member 93 is slightly inclined so that the distal end is positioned radially outside the base end of the cam engagement portion 52c, and therefore the second roller member side stopper surface 93d. Is not in contact with the second stopper surface 92k.

  Then, along with the rotation of the driving side rotating body 51, the power transmission portion 52b of the roller member 93 disposed at the engagement position is transmitted in the control recess 56e on the front transmission surface 56g in the rotational direction of the driving side rotating body 51. (See FIG. 11A). Thereby, the rotational driving force of the rotating shaft 20 is transmitted in the order of the first driving plate 61, the connecting spring 63, the second driving plate 92, and the roller member 93, and further, the driven side rotation from the power transmission portion 52b of the roller member 93. It can be transmitted to the body 56.

  The guide member 55 to which the urging force of the return spring 53 is transmitted from the roller member 93 that rotates together with the drive-side rotator 51 that has started to rotate after the cam engaging portion 52c is disposed in the second guide portion P2 is also provided. It starts to rotate with the drive side rotating body 51. When the rotation speed of the guide member 55 is increased during the rotation of the drive-side rotator 51, the inertial force acting on the guide member 55 is reduced as the rotation speed is increased. As the inertial force acting on the guide member 55 becomes smaller, the guide member 55 rotates together with the holding case 54 on the driving side by the action of the urging force of the return spring 53 transmitted through the cam engagement portion 52c. It rotates relative to the body 51 in the same direction as the driving side rotating body 51. Along with the relative rotation of the guide member 55 with respect to the drive-side rotator 51, the cam groove 55d of the guide member 55 held by the holding case 54 rotates in the circumferential direction of the holding case 54 with respect to the cam engaging portion 52c. Therefore, the cam engagement portion 52c is relatively moved from the second guide portion P2 to the first guide portion P1. At the same time, as the rotational speed of the guide member 55 increases, the centrifugal force acting on the guide member 55 gradually increases. Therefore, the guide member 55 is moved radially outward while being guided by the guide surface 54h. The Accordingly, since the radial position of the cam engagement portion 52c is maintained without changing in the radial direction, the roller member 93 is held at the engagement position by the guide member 55.

  Further, when the driving side rotating body 51 rotates, a centrifugal force corresponding to the rotational speed of the driving side rotating body 51 acts on the roller member 93 that rotates together with the driving side rotating body 51. Centrifugal force tends to move the roller member 93 radially outward. When the first roller member-side stopper surface 93a comes into contact with the first stopper surface 92e, the roller member 93 moves outward in the radial direction. It is regulated by the first stopper surface 92e. Therefore, the roller member 93 is held at the engagement position without the power transmission portion 52b contacting the bottom surface 56f of the control recess 56e.

  Then, after the driven-side rotator 56 starts to rotate, when the load acting on the driven-side rotator 56 is greater than the urging force of the coupling spring 63, the first drive plate 61 is subjected to the urging force of the coupling spring 63. The connection spring 63 is contracted against the rotation of the first drive plate 61 with respect to the second drive plate 92. As a result, of the pair of wedge surfaces 61g of each control groove 61d, the wedge surface 61g on the rear side in the rotational direction of the first drive plate 61 comes into contact with the outer peripheral surface of the power transmission portion 52b from the rotational direction, and the wedge surface 61g. And the transmission surface 56g sandwich the power transmission portion 52b. When the wedge surface 61g comes into contact with the power transmission unit 52b, the power transmission unit 52b receives a force directed radially outward from the wedge surface 61g, and is thus pressed radially outward by the wedge surface 61g. Then, the roller member 93 that has been slightly inclined so that the distal end is located radially outside the base end of the cam engagement portion 52c is shown in FIGS. 25, 22 (a), and 22 (b). As shown, the power transmission portion 52b is pushed radially outward by the wedge surface 61g and slightly moves radially outward. As a result, the cam engagement portion 52c and the power transmission portion 52b are arranged in parallel to the central axis of the driven-side rotating body 56, and the pair of second roller member side stopper surfaces 93d is a pair of second stopper surfaces. Each abuts on 92k. As a result, the amount of movement of the roller member 93 outward in the radial direction is restricted not only by the first stopper surface 92e but also by the second stopper surface 92k. Then, the rotational driving force of the rotating shaft 20 is transmitted from the first driving plate 61 to the driven side rotating body 56 via the roller member 93. As a result, since the driven-side rotator 56 is rotated, the worm shaft 32 connected to the driven-side rotator 56 is rotated.

  On the other hand, when the load acting on the driven-side rotator 56 is equal to or less than the biasing force of the connection spring 63, the first drive plate 61 and the second drive plate 92 are held in the neutral position by the biasing force of the connection spring 63. Rotate integrally in the applied state. Accordingly, the rotational driving force of the rotating shaft 20 is transmitted in the order of the first driving plate 61, the connecting spring 63, the second driving plate 92, the roller member 93, and the driven side rotating body 56. As a result, since the driven-side rotator 56 is rotated, the worm shaft 32 connected to the driven-side rotator 56 is rotated. In this case, the amount of movement of the roller member 93 outward in the radial direction is regulated by the first stopper surface 92e.

As described above, the second embodiment has the following effects in addition to the effects (1) to (5) of the first embodiment.
(6) The first stopper surface 92e and the second stopper surface 92k are brought into contact with the roller member 52 at two positions where the first stopper surface 92e and the second stopper surface 92k are displaced in the axial direction, thereby restricting the amount of movement of the roller member 52 outward in the radial direction. Therefore, since it can suppress that the roller member 52 which moved to the engagement position inclines with respect to an axial direction, the connection of the drive side rotary body 51 and the driven side rotary body 56 via the roller member 52 becomes unstable. This can be suppressed. As a result, when the drive side rotator 51 is rotationally driven, the rotational drive force can be stably transmitted from the drive side rotator 51 to the driven side rotator 56 via the roller member 52.

  (7) When the roller member 93 is viewed from a direction that is the diameter direction of the cam engaging portion 52c and the short side direction of the connecting portion 52a so that the first roller member side stopper surface 93a looks linear (that is, In the state shown in FIG. 20B, the first roller member side stopper surface 93a and the cylindrical outer peripheral surface of the cam engaging portion 52c are connected in the axial direction without any step. Further, the first roller member side stopper surface 93a is formed longer in the axial direction than the first stopper surface 92e. Therefore, even when the roller member 93 is inclined with respect to the axial direction of the second drive plate 92 or is shaken in the axial direction inside the clutch 50, the first stopper surface 92e causes the roller member 93 to move. The amount of movement outward in the radial direction can be restricted.

Each embodiment of the present invention may be modified as follows.
In each of the above embodiments, the present invention has been described by taking the slide door opening / closing device 1 for automatically opening / closing the slide door 3 that opens / closes the entrance / exit 2a provided on the side of the vehicle body 2 as an example. However, the present invention may be applied to a device that opens and closes a door other than the slide door 3 as long as the door is automatically opened and closed using the motor 11 as a drive source. For example, the present invention may be applied to a back door opening and closing device that automatically opens and closes a back door that opens and closes an opening provided in the rear portion of the vehicle by the driving force of the motor 11. The motor 11 of each of the above embodiments is not limited to a door opening / closing device, and transmits the rotational driving force of the rotary shaft 20 to a load connected to the output shaft 35, while allowing the output shaft 35 to rotate from the load side. It may be used in a device that does.

  In the above embodiments, the clutches 50 and 90 are provided in the motor 11. However, the clutches 50 and 90 may be used in addition to the motor 11 to operate so as to connect / disconnect the drive shaft and the driven shaft arranged coaxially.

  In the second embodiment, the second driving plate 92 is formed so that the first stopper surface 92e and the second stopper surface 92k are displaced in the axial direction. However, the second drive plate 92 may be formed with a stopper surface against which the roller member 52 that has moved outward in the radial direction comes into contact at three or more positions shifted in the axial direction. Even if it does in this way, the effect similar to (6) of the said 2nd Embodiment can be acquired.

  In the first embodiment, as a stopper for restricting the movement amount of the roller member 52 to the outer side in the radial direction, the stopper surface 62n with which the roller member 52 that is opposed to the roller member 52 in the radial direction and moves outward in the radial direction abuts. Are formed on the second drive plate 62. Similarly, in the second embodiment, as a stopper for restricting the movement amount of the roller member 93 to the outer side in the radial direction, the roller member 93 that is opposed to the roller member 93 in the radial direction and has moved to the outer side in the radial direction abuts. A first stopper surface 92e and a second stopper surface 92k are formed on the second drive plate 92. However, the stoppers that restrict the amount of movement of the roller members 52 and 93 outward in the radial direction are not limited to the planar stopper surface 62n, the first stopper surface 92e, and the second stopper surface 92k. For example, the amount of movement of the roller member 52 to the outer side in the radial direction may be restricted by acting on the roller members 52 and 93 from the inner side in the radial direction.

  In the first embodiment, the second drive plate 62 is formed with a stopper surface 62n as a stopper that restricts the amount of movement of the roller member 52 outward in the radial direction. However, the stopper that restricts the amount of movement of the roller member 52 radially outward may be formed on the components of the clutch 50 other than the second drive plate 62 (except for the roller member 52). Similarly, in the second embodiment, the stopper that restricts the amount of movement of the roller member 93 radially outward is formed on the components of the clutch 90 other than the second drive plate 92 (except for the roller member 93). May be.

  In the first embodiment, the stopper surface 62n restricts the movement amount of the roller member 52 to the outer side in the radial direction, thereby making contact with the bottom surface 56f of the control recess 56e of the roller member 52 moved to the engagement position. Stop. However, the stopper surface 62n does not necessarily need to prevent the contact of the control recess 56e of the roller member 52 moved to the engagement position with the bottom surface 56f. Even in this case, the stopper surface 62n restricts the amount of movement of the roller member 52 outward in the radial direction, so that it is possible to reduce the radially outward force that acts on the driven side rotating body 56 from the roller member 52. . As a result, deformation of the driven-side rotator 56 due to the movement of the roller member 52 radially outward can be suppressed. Similarly, in the clutch 90 of the second embodiment, the first stopper surface 92e and the second stopper surface 92k do not necessarily prevent the contact of the roller member 93 moved to the engagement position with the bottom surface 56f of the control recess 56e. May be. Also in this case, the first stopper surface 92e and the second stopper surface 92k restrict the movement amount of the roller member 93 to the radially outer side, so that the roller member 93 acts on the driven side rotating body 56 to the radially outer side. The power to go can be reduced. As a result, deformation of the driven-side rotator 56 due to the movement of the roller member 93 radially outward can be suppressed.

The roller members 52 and 93 are not limited to the shapes of the above embodiments. For example, the roller members 52 and 93 may have a simple column shape or the like.
-The cam part which is a site | part which guides the movement of the roller members 52 and 93 between a non-engagement position and an engagement position in the guide member 55 is not restricted to the groove-shaped cam groove 55d. For example, the roller members 52 and 93 are moved between the non-engagement position and the engagement position by the cam protrusion portion that is formed so as to protrude from the guide member 55 in the axial direction and is engaged with the cam engagement portion 52c. You may make it guide.

  In the clutches 50 and 90 of each of the above embodiments, when the driving side rotating body 51 starts to rotate, the roller member 52 is moved radially outward by the action of the cam groove 55d and disposed at the engagement position. However, the clutch members 50 and 90 are moved outward in the radial direction by the centrifugal force acting on the roller member 52 that rotates integrally with the drive-side rotator 51 when the drive-side rotator 51 starts to rotate. It may be arranged at the engagement position.

  In the clutch 50 of the first embodiment, the roller member 52, the return spring 53, the control groove 61d, the guide recess 62g, the insertion engagement portion 62h, the connection spring 63, the guide member 55 having the cam groove 55d, and the control projection 56d. The number of control recesses 56e may be changed as appropriate. It is sufficient that at least one of these configurations is provided in the clutch 50. In the clutch 90 of the second embodiment, the roller member 93, the return spring 53, the control groove 61d, the restriction recess 92a, the insertion guide hole 92c, the connection spring 63, the guide member 55 having the cam groove 55d, and the control protrusion 56d. The number of control recesses 56e may be changed as appropriate. It is sufficient that at least one of these configurations is provided in the clutch 90.

  In each of the above embodiments, the first drive plate 61 is formed separately from the rotary shaft 20, but may be formed integrally. In each of the above-described embodiments, the driven-side rotator 56 is formed separately from the worm shaft 32, but may be formed integrally.

  DESCRIPTION OF SYMBOLS 1 ... Sliding door opening / closing apparatus as a vehicle door opening / closing apparatus, 2 ... Vehicle body as vehicle, 2a ... Entrance / exit as opening, 11 ... Motor, 12 ... Motor main body, 20 ... Rotating shaft as drive shaft, 31 ... Gear housing 32: Worm shaft as driven shaft 34: Reduction mechanism 50, 90 ... Clutch 51: Drive-side rotator 52, 93 ... Roller member as power transmission member 56 ... Drive-side rotator 56c ... side wall part, 56d ... control convex part, 56e ... control concave part, 56f ... bottom face of control concave part, 62n ... stopper surface as a stopper, 92e ... first stopper surface as a stopper, 92k ... second stopper surface as a stopper.

Claims (6)

A drive-side rotator provided so as to be integrally rotatable with the drive shaft;
A driven side rotating body provided to be rotatable integrally with the driven shaft;
It is arranged between the driving side rotating body and the driven side rotating body in the radial direction and is provided so as to be able to rotate integrally with the driving side rotating body. The driving side rotating body and the driven side rotating body are rotated in the rotation direction. Is moved between a non-engagement position that does not engage with and an engagement position that engages the drive-side rotator and the driven-side rotator in the rotational direction on the radially outer side of the non-engagement position. A power transmission member,
When the drive shaft is not driven, the power transmission member is disposed at the non-engagement position and disconnects the drive shaft and the driven shaft, while the drive side rotary body is driven to rotate by driving the drive shaft. A clutch that connects the drive shaft and the driven shaft by moving the power transmission member radially outward and being disposed at the engagement position;
A clutch provided with a stopper for restricting the amount of movement of the power transmission member radially outward. The clutch according to claim 1, wherein
The driven-side rotator includes a side wall portion that is formed in a cylindrical shape and that is radially opposed to the power transmission member disposed inside thereof, and an inner peripheral surface of the side wall portion is provided on an inner peripheral surface of the side wall portion. A control convex portion protruding radially inward from the control convex portion and a control concave portion that is formed on the inner peripheral surface of the side wall portion and opened radially inward by providing the control convex portion,
When the power transmission member moves radially outward to the engagement position during rotational driving of the drive side rotator, the power transmission member is inserted into the control recess from the inside in the radial direction, and the control protrusion from the rotational direction of the drive side rotator. It can be held between the control convex part and the driving side rotating body in contact with the part,
The stopper restricts the amount of movement of the power transmission member radially outward to prevent the power transmission member moved to the engagement position from contacting the bottom surface of the control recess. clutch. In the clutch according to claim 1 or 2,
The stopper is a stopper surface that is formed on at least one of the components of the clutch other than the power transmission member and is in contact with the power transmission member that faces the power transmission member in the radial direction and moves radially outward. Clutch characterized by. The clutch according to any one of claims 1 to 3,
The stopper acts on the power transmission member moved to the engagement position at a plurality of positions shifted in the axial direction to restrict the amount of movement of the power transmission member in the radially outer direction. . A motor body having the drive shaft that is rotationally driven;
A reduction mechanism that is arranged coaxially with the drive shaft and has the driven shaft that is rotated by a rotational driving force of the drive shaft, and that decelerates and outputs the rotation of the drive shaft;
The clutch according to any one of claims 1 to 4, wherein the clutch is disposed between the drive shaft and the driven shaft.
A gear housing connected to the motor body and housing the speed reduction mechanism and the clutch inside;
A motor comprising: A vehicle door opening and closing device configured to open and close a door that opens and closes an opening provided in a vehicle by a driving force of a motor according to claim 5,
When a command to automatically open and close the door is generated, the drive shaft is connected to the driven shaft by the clutch and the door is automatically opened and closed while the motor main body is driven. Thus, the driven shaft is disconnected from the drive shaft to reduce the operating load when the door is manually opened and closed.