JP2018059622A - Clutch and motor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch capable of suppressing shortage of grease between an inner peripheral face of a clutch housing and a rolling element.SOLUTION: A driving-side rotor 42 transmits rotary driving force to a driven-side rotor 45. Rolling elements 44 disposed between the clutch housing 41 and the driven-side rotor 45 rotate around a rotation axis of the driving-side rotor 42 with the driving-side rotor 42 in rotation of the driving-side rotor 42, and held between the clutch housing 41 and the driven-side rotor 45 in non-rotation of the driving-side rotor 42 to prevent rotation of the driven-side rotor 45. A supporting member 43 holds the rolling elements 44 between the clutch housing 41 and the driven-side rotor 45, and rotated around the rotation axis of the driving-side rotor 42 with the driving-side rotor 42. An inner peripheral face 41 of the clutch housing 41 is coated with grease GR. Rotation of the rolling elements 44 around center axes L3 of the rolling elements 44 is restricted by the supporting member 43.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a clutch and a motor including the clutch.

  2. Description of the Related Art Conventionally, a motor used as a drive source for a power window device or the like mounted on a vehicle has a motor unit having a rotating shaft that is driven to rotate and a driven shaft that transmits the rotational driving force of the rotating shaft. And an output unit that outputs the rotational driving force transmitted to the motor. For example, as described in Patent Document 1, the rotating shaft and the driven shaft transmit the rotational driving force of the rotating shaft to the driven shaft while not transmitting the rotational force from the driven shaft side to the rotating shaft. It is connected via a clutch that operates on

  The clutch described in Patent Document 1 includes a drive-side rotator that rotates integrally with a rotation shaft, a driven-side rotator that can engage with the drive-side rotator in the rotation direction, and rotates integrally with the driven shaft, and a drive-side rotation. And a cylindrical clutch housing in which the body and the driven side rotating body are inserted. Further, between the inner peripheral surface of the clutch housing and the driven side rotator, the driven shaft is sandwiched between the inner peripheral surface of the clutch housing and the driven side rotator when the rotary shaft is not driven to rotate (becomes a wedge). A cylindrical rolling element that prevents rotation of the side rotating body (that is, rotation of the driven shaft) is interposed. The rolling element is held by a support member inserted inside the clutch housing such that the center axis thereof is parallel to the rotation axis of the drive side rotator. The support member rotates around the rotation axis of the driving side rotating body together with the driving side rotating body when the rotating shaft is driven to rotate. Therefore, at the time of rotational driving of the rotating shaft, the rolling element rotates with the driving side rotating body and the driven side rotating body around the rotation axis of the driving side rotating body along the inner peripheral surface of the clutch housing while being held by the support member. .

JP, 2006-40488, A

  By the way, between the inner peripheral surface of the clutch housing and the rolling element, the inner part of the clutch housing is prevented to prevent the rotating shaft from rotating from the driven shaft side when the rotating shaft (driving side rotating body) is not rotated. Grease is arranged to prevent the rolling element from slipping with respect to the inner circumferential surface of the clutch housing when the peripheral surface and the driven-side rotator sandwich the rolling element. However, when the rotating shaft is driven to rotate, the rolling element rotates around the rotation axis of the drive-side rotating body along the inner peripheral surface of the clutch housing while rotating around the central axis of the rolling element. Therefore, the grease between the inner peripheral surface of the clutch housing and the rolling element scatters as the rolling element rotates about the central axis, and the grease between the inner peripheral surface of the clutch housing and the rolling element is insufficient. There was a problem that sometimes. If the grease between the inner peripheral surface of the clutch housing and the rolling element is insufficient, it becomes difficult to hold the rolling element between the inner peripheral surface of the clutch housing and the driven-side rotating body when the rotary shaft is not rotated (wedges). It may be difficult to do).

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a clutch and a motor that can suppress the shortage of grease between the inner peripheral surface of the clutch housing and the rolling elements. It is to provide.

  A clutch that solves the above-described problems includes an annular clutch housing, a drive-side rotator that is rotationally driven, and a driven member that is at least partially disposed on the inner side of the clutch housing and to which rotational drive force is transmitted from the drive-side rotator. The rotating body is disposed between the side rotating body, the inner peripheral surface of the clutch housing and the driven side rotating body, and around the rotation axis of the driving side rotating body together with the driving side rotating body when the driving side rotating body is driven to rotate. A rolling element that rotates and prevents rotation of the driven-side rotating body by being sandwiched between an inner peripheral surface of the clutch housing and the driven-side rotating body when the driving-side rotating body is not rotated; A support member that holds the rolling element between an inner peripheral surface of the clutch housing and the driven-side rotating body and rotates around the rotational axis of the driving-side rotating body together with the driving-side rotating body; At least a grease disposed between an inner peripheral surface of the clutch housing and the rolling element, wherein the rolling element is rotated around the central axis of the rolling element by the support member. Limited.

  According to this configuration, the rolling element is restricted from rotating around the central axis of the rolling element by the support member. Therefore, even when the rolling element rotates around the rotation axis of the driving side rotating body together with the driving side rotating body at the time of rotational driving of the driving side rotating body, It rotates only within the allowable range. Therefore, since the scattering of the grease due to the rolling element rotating around the central axis of the rolling element is suppressed, it is possible to suppress the shortage of the grease between the inner peripheral surface of the clutch housing and the rolling element. .

  In the clutch, the support member has a facing portion that faces the rolling element in a rotation direction of the driving-side rotating body, and a center axis line of the rolling element is between the facing portion and the rolling element. An allowance gap for determining a rotation range of the rolling element is provided, and the rolling element abuts against the facing portion when the rolling element rotates about the center axis of the rolling element by an amount allowed by the allowance gap. It is preferred that the rotation of is prevented.

  According to this configuration, when the rolling element rotates around the central axis of the rolling element by an allowable gap provided between the rotating part of the driving side rotating body and the facing portion facing the rolling element, It abuts against the facing portion from the direction of rotation of the rolling element. As a result, the rolling element is prevented from further rotation around the central axis of the rolling element by the facing portion. Therefore, the scattering of grease due to the rolling element rotating around the central axis of the rolling element can be suppressed with a simple configuration. As a result, a shortage of grease between the inner peripheral surface of the clutch housing and the rolling elements can be easily suppressed.

  In addition, the rolling element can rotate around the central axis of the rolling element within a rotation range determined by providing an allowable gap between the rolling element and the facing portion. That is, the posture of the rolling element with respect to the inner peripheral surface of the clutch housing can be changed around the central axis of the rolling element. Then, the grease moves between the rolling element and the inner peripheral surface of the clutch housing as the rolling element rotates about the central axis of the rolling element within the rotation range. Grease can be supplied to the portion that contacts the surface.

  In the clutch, the facing portion is provided on both sides in the rotation direction of the driving side rotating body with respect to the rolling element, and the rolling element is centered on the rolling element by an amount allowed by the allowable gap. When rotating around the axis, it is preferable that the rolling element comes into contact with the facing portion on both sides in the rotation direction of the driving side rotating body.

  According to this configuration, when the rolling element rotates around the central axis of the rolling element by the amount allowed by the allowable gap, the rolling element comes into contact with the opposing portion on both sides in the rotational direction of the drive side rotating body. Therefore, the rolling element in contact with the facing portion can maintain the posture in contact with the facing portion more stably.

  In the clutch, it is preferable that the rolling element has a planar opposing surface facing the opposing part and the rotational direction of the driving side rotating body on both sides of the rolling body in the rotating direction of the driving side rotating body. .

  According to this configuration, it is easy to set an allowable gap provided between the rolling element and the facing portion. Moreover, since it is suppressed that the shape of a rolling element is complicated, the rolling element can be manufactured easily.

  In the clutch, the drive-side rotator includes a rolling element release portion that transmits a rotational driving force of the drive-side rotator to the opposing portion when the drive-side rotator is rotationally driven. When the rotational drive of the drive side rotator is started, the rolling member release portion is pressed in the rotation direction of the drive side rotator via the facing portion, whereby the inner peripheral surface of the clutch housing and the driven side rotator It is preferable that the opposed portion has a flat surface and a contact surface that can come into surface contact with the opposed surface in the rotation direction of the drive-side rotating body.

  According to this configuration, at the start of the rotational drive of the drive-side rotator, the rotational driving force of the drive-side rotator is transmitted from the rolling element release portion to the facing portion, and further transmitted from the facing portion to the rolling element. At this time, the facing portion to which the rotational driving force is transmitted from the driving side rotating body efficiently brings the rotational driving force to the rolling element by bringing the contact surface of the facing portion into surface contact with the facing surface of the rolling element. Can communicate. Therefore, it is possible to easily release the rolling element between the inner peripheral surface of the clutch housing and the driven side rotating body.

  In the clutch, the support member tends to rotate around a central axis of the rolling element when the driving-side rotating body is non-rotatingly driven, and a facing portion facing the rolling element in the rotation direction of the driving-side rotating body. It is preferable to have a contact portion that moves radially outward when the facing portion is pressed by the rolling element and contacts the inner peripheral surface of the clutch housing.

  According to this configuration, when the drive-side rotator is not rotated, the abutting portion moved radially outward by the facing portion pressed by the rolling element abuts on the inner peripheral surface of the clutch housing. Therefore, it is possible to suppress the rolling element from moving in the rotation direction of the drive side rotating body also by the frictional force generated between the contact portion and the inner peripheral surface of the clutch housing. Accordingly, the rolling element can be more easily sandwiched between the driven-side rotating body and the inner peripheral surface of the clutch housing, so that the rotation of the driven-side rotating body can be more easily prevented when the driving-side rotating body is not rotated.

  In the clutch, the rolling element is formed on the outer peripheral surface of the rolling element, the first arc-shaped arc surface that can contact the inner peripheral surface of the clutch housing, and the first rolling element when viewed from the central axis direction of the rolling element. A second arcuate surface that has an arc shape with a smaller curvature than that of the first arcuate surface and is capable of contacting the driven-side rotator, and when the drive-side rotator is not rotated, the first arcuate surface is Contacting the inner peripheral surface of the clutch housing, and the second arcuate surface contacting the driven-side rotating body and being sandwiched between the inner peripheral surface of the clutch housing and the driven-side rotating body. preferable.

  According to this configuration, the rolling element is restricted from rotating around the central axis of the rolling element by the support member. Therefore, the curvature of the part which can contact the inner peripheral surface of a clutch housing and the part which can contact a driven side rotary body can be varied in the outer peripheral surface of the said rolling element. When the curvature of the second arc surface is made smaller than the curvature of the first arc surface, the non-rotation of the drive-side rotator is less than when the entire outer peripheral surface of the rolling element has the curvature of the first arc surface. When the driven side rotating body is about to rotate during driving, the rolling body can be held between the driven side rotating body and the clutch housing at a stage where the rotational speed of the driven side rotating body is smaller. Therefore, when trying to rotate from the driven side rotating body side, the rolling body can be sandwiched between the driven side rotating body and the clutch housing at an earlier stage, so when the rotational drive of the driving side rotating body is stopped The rotation of the driven side rotating body can be quickly prevented.

  In the clutch, the rolling element can be slidably contacted with the inner peripheral surface of the clutch housing by rotating around the central axis of the rolling element within a range allowed by the support member on the outer peripheral surface of the rolling element. It is preferable to have a sliding contact range and a grease receiving recess that opens into the sliding contact range and stores the grease.

  According to this configuration, since the rolling element is restricted from rotating around the central axis of the rolling element by the support member, the rotation range around the central axis of the rolling element is determined. Therefore, the slidable contact range that can be slidably contacted with the inner peripheral surface of the clutch housing is determined on the outer peripheral surface of the rolling element. And since the grease accommodation recessed part provided in the rolling element is opening in this sliding contact range, the grease accommodated in the grease accommodation recessed part is pulled out toward the inner peripheral surface of a clutch housing with rotation of a rolling element. Thus, it is supplied between the rolling element and the inner peripheral surface of the clutch housing. Accordingly, it is possible to further suppress the shortage of grease between the inner peripheral surface of the clutch housing and the rolling elements.

  In the clutch, the support member has a facing portion facing the rolling element in the rotation direction of the driving side rotating body, and has a protruding piece extending toward the rolling element on a radially outer portion of the facing portion. It is preferable to provide a tip surface that intersects the rotational direction of the drive side rotating body at the tip of the protruding piece.

  According to this configuration, the protruding piece provided on the radially outer portion of the opposing portion of the support member is disposed between the inner peripheral surface of the clutch housing and the rolling element as the support member rotates together with the driving-side rotating body. Although it advances so that the arranged grease may be scraped, the tip of the projecting piece is provided with a tip surface that intersects the rotation direction of the drive side rotating body, thereby causing a grease flow toward the inner peripheral surface of the clutch housing. It becomes like this. That is, it is possible to obtain a situation in which grease is easily held between the inner peripheral surface of the clutch housing and the rolling elements.

  A motor that solves the above problems includes a motor unit having a rotary shaft that is driven to rotate, the clutch that has the drive-side rotary body that rotates integrally with the rotary shaft, and a driven shaft that rotates integrally with the driven-side rotary body. And an output unit for outputting the rotational driving force transmitted to the driven shaft.

  According to this configuration, the rotating shaft and the driven shaft are connected via the clutch in which the grease between the inner peripheral surface of the clutch housing and the rolling element is suppressed from being insufficient. Therefore, the rotation of the rotating shaft from the driven shaft side is further suppressed when the rotating shaft is not rotated.

  According to the clutch and motor of this invention, it can suppress that the grease between the inner peripheral surface of a clutch housing and a rolling element is insufficient.

Sectional drawing of the motor of embodiment. The partial expanded sectional view of the motor of an embodiment. The disassembled perspective view of the clutch in embodiment. (A) is a side view of the support member holding the rolling element in the clutch of the embodiment, (b) is a bottom view of the support member. The partial expanded sectional view of the clutch in embodiment (6a-6a sectional drawing in FIG. 2). (A) is sectional drawing (6a-6a sectional drawing in FIG. 2) of the clutch in embodiment, (b) is sectional drawing (6b-6b sectional drawing in FIG. 2) of the clutch in embodiment. (A) And (b) is sectional drawing for demonstrating operation | movement of the clutch in embodiment. (A) And (b) is sectional drawing for demonstrating operation | movement of the clutch in embodiment. (A) And (b) is sectional drawing for demonstrating operation | movement of the clutch in embodiment. (A) is a top view of the rolling element of another form, (b) is a front view of the rolling element. (A) is a top view of the rolling element of another form, (b) is a front view of the rolling element. (A) is a top view of the rolling element of another form, (b) is a front view of the rolling element. (A) is a top view of the rolling element of another form, (b) is a front view of the rolling element. (A) is a top view of the rolling element of another form, (b) is a front view of the rolling element. Sectional drawing of the clutch of another form. (A) And (b) is sectional drawing of the clutch of another form. The partial expanded sectional view of the clutch of another form.

Hereinafter, an embodiment of a motor provided with a clutch will be described.
A motor 10 according to this embodiment shown in FIG. 1 is provided in a power window device that lifts and lowers a window glass of a vehicle electrically. The motor 10 is configured by integrally assembling a motor unit 20 that generates rotational force and an output unit 30 that decelerates and outputs rotation output from the motor unit 20. In addition, the motor 10 includes a clutch 40 at a drive connection portion between the motor unit 20 and the output unit 30.

  The motor unit 20 of the present embodiment is a DC motor. A magnet 22 is fixed to an inner peripheral surface of a bottomed cylindrical yoke housing 21 (hereinafter referred to as a yoke 21) constituting the motor unit 20, and an armature 23 is disposed inside the magnet 22. . The armature 23 includes a rotating shaft 24 disposed at the center of the yoke 21. A base end portion (upper end portion in FIG. 1) of the rotating shaft 24 is supported by a bearing 25 provided at the center of the bottom of the yoke 21. A commutator 26 is fixed. Further, a connecting portion 24a having a two-sided width shape that is chamfered in parallel from a columnar shape is provided at the tip end portion (the lower end portion in FIG. 1) of the rotating shaft 24.

  A flange portion 21 a extending outward is formed in the opening portion of the yoke 21, and a brush holder 27 is fitted in the opening portion of the yoke 21. The brush holder 27 has a holder main body 27a having a shape for closing the opening of the yoke 21, and a connector part 27b protruding from the holder main body 27a to the outer side in the radial direction of the yoke 21 and connected to an external connector (not shown). The holder main body 27a holds a plurality of power supply brushes 28 that are electrically connected to the connector portion 27b by wires (not shown) and are in sliding contact with the commutator 26. The holder main body 27a holds a bearing 29 at a substantially central portion thereof, and the bearing 29 pivotally supports a portion of the rotating shaft 24 between the commutator 26 and the connecting portion 24a. When the external power supplied to the brush 28 via the connector portion 27b is supplied to the armature 23 via the commutator 26, the armature 23 (rotating shaft 24) is driven to rotate, that is, the motor portion 20 is It is designed to rotate.

  The output unit 30 is formed by housing a speed reduction mechanism 32 and the like in a resin gear housing 31. The gear housing 31 includes a fixing portion 31 a for fixing the gear housing 31 to the motor portion 20 at a portion (an upper end portion in FIG. 1) facing the motor portion 20 in the axial direction. The fixed portion 31 a has an outer shape similar to the outer shape of the flange portion 21 a of the yoke 21, and an accommodating recess 31 b that opens toward the inside of the yoke 21 is formed in the fixed portion 31 a. Then, in a state where a part of the holder main body 27a of the brush holder 27 is inserted into the housing recess 31b, the flange portion 21a that is in contact with the fixing portion 31a is fixed to the fixing portion 31a by the screw 33, whereby the gear The yoke 21 is fixed to the housing 31, and the motor unit 20 and the output unit 30 are integrated. The brush holder 27 is sandwiched between the yoke 21 and the fixed portion 31a.

  Further, the gear housing 31 is provided with a clutch housing recess 31c in the center of the bottom of the housing recess 31b in the axial direction, and extends from the center of the bottom of the clutch housing recess 31c along the direction of the central axis L1 of the rotary shaft 24. A worm shaft accommodating portion 31d is recessed. Further, the gear housing 31 is provided with a wheel housing portion 31e recessed on the side (right side in FIG. 1) of the worm shaft housing portion 31d. The wheel housing portion 31e and the worm shaft housing portion 31d are connected to each other at a substantially central portion in the axial direction (longitudinal direction) of the worm shaft housing portion 31d.

  A substantially cylindrical worm shaft 34 (driven shaft) is accommodated in the worm shaft accommodating portion 31d. The worm shaft 34 is made of a metal material, and a screw-like worm portion 34a is formed in the central portion in the axial direction. The worm shaft 34 is supported at both ends in the axial direction by a pair of bearings 35 and 36 disposed at both ends in the axial direction of the worm shaft housing portion 31d. The worm shaft 34 disposed in the worm shaft housing portion 31d is supported by bearings 35 and 36 so as to be disposed coaxially with the rotary shaft 24, that is, the central axis L1 of the rotary shaft 24 and the worm shaft 34. The central axis line L2 is arranged on the same straight line.

  A disc-shaped worm wheel 37 that meshes with the worm portion 34a of the worm shaft 34 is rotatably accommodated in the wheel accommodating portion 31e. The worm wheel 37 and the worm shaft 34 constitute a speed reduction mechanism 32. That is, the speed reduction mechanism 32 of the present embodiment is a worm speed reduction mechanism (worm gear). In addition, an output shaft 38 that extends in the axial direction of the worm wheel 37 (in the direction perpendicular to the paper surface in FIG. 1) and rotates together with the worm wheel 37 is provided at the radial center of the worm wheel 37. A window glass of a vehicle is connected to the output shaft 38 via a window regulator (not shown).

Further, the clutch 40 that connects the rotating shaft 24 of the motor unit 20 and the worm shaft 34 of the output unit 30 is housed in the clutch housing recess 31c.
As shown in FIGS. 2 and 3, the clutch 40 includes a clutch housing 41, a driving side rotating body 42, a support member 43, a rolling element 44, and a driven side rotating body 45.

  The clutch housing 41 has a cylindrical shape, and a hook-shaped fixing flange portion 41 a extending radially outward is formed at one axial end portion of the clutch housing 41. The outer diameter of the cylindrical portion of the clutch housing 41 is formed substantially equal to the inner diameter of the clutch housing recess 31c, and the outer diameter of the fixed flange portion 41a is formed larger than the inner diameter of the clutch housing recess 31c. In addition, fixed recesses 41b are formed in the fixed flange portion 41a at four locations that are equiangularly spaced in the circumferential direction. Each fixing recess 41b penetrates the fixing flange portion 41a in the axial direction and opens radially outward.

  As shown in FIG. 2, the clutch housing 41 is inserted into the clutch housing recess 31c until the fixed flange portion 41a contacts the bottom surface of the housing recess 31b, and is fixed to the gear housing 31 at the fixed flange portion 41a. ing. Specifically, on the outer surface of the opening of the clutch housing recess 31c on the bottom surface of the housing recess 31b, four fixed projections 31f projecting in the axial direction are formed at equiangular intervals in the circumferential direction. These four fixed projections 31f are inserted in the axial direction with respect to the four fixed recesses 41b of the fixed flange portion 41a, and the tip portions of the respective fixed projections 31f are processed by heat caulking. Thereby, the clutch housing 41 is fixed to the gear housing 31 so as not to move in the axial direction and to rotate in the circumferential direction. The clutch housing 41 fixed to the gear housing 31 is arranged coaxially with the rotary shaft 24 and the worm shaft 34.

The drive-side rotator 42 has a substantially cylindrical shaft coupling portion 51. On the outer peripheral surface of the shaft connecting portion 51, a disc-shaped flange portion 52 that extends outward in the radial direction is integrally formed.
In the shaft coupling portion 51, a drive shaft insertion hole 53 extending along the axial direction is formed at the axial center of the axial end portion (upper end portion in FIG. 2) on the motor portion 20 side. The drive shaft insertion hole 53 has a two-sided width shape corresponding to the outer shape of the connecting portion 24 a of the rotating shaft 24. Then, when the connecting portion 24 a is press-fitted into the drive shaft insertion hole 53, the drive side rotating body 42 is connected to the rotary shaft 24 so as to be integrally rotatable. The rotating shaft 24 and the drive-side rotating body 42 connected to the rotating shaft 24 are coaxial (that is, their center axes are located on the same straight line).

  Further, in the shaft coupling portion 51, a driven shaft insertion hole 54 extending along the axial direction is formed at the axial center of the axial end portion (lower end portion in FIG. 2) on the output portion 30 side. The center axis of the driven shaft insertion hole 54 coincides with the center axis of the drive shaft insertion hole 53. In this embodiment, the drive shaft insertion hole 53 and the driven shaft insertion hole 54 communicate with each other.

  As shown in FIG. 6B, the inner peripheral surface of the driven shaft insertion hole 54 has a pair of drive side transmission surfaces 54a that are parallel to each other in a planar shape parallel to the axial direction. The shape of the driven shaft insertion hole 54 viewed from the axial direction is a substantially track shape (two directions parallel to the drive-side transmission surface 54a and the short-side direction perpendicular to the drive-side transmission surface 54a). (Width shape). Each drive-side transmission surface 54a is provided with two first elastic members 55 made of an elastic material such as a rubber material. Moreover, the 2nd elastic member 56 which consists of materials which have elasticity, such as a rubber material, is each provided in the both ends of the longitudinal direction of the driven shaft insertion hole 54 seeing axially. The first and second elastic members 55 and 56 slightly protrude inward from the inner peripheral surface of the driven shaft insertion hole 54.

  Further, as shown in FIGS. 3 and 6A, the drive-side rotating body 42 is released from a pair of rolling elements extending from the flange portion 52 to the output portion 30 side (downward in FIG. 3) in the axial direction. Part 57. The rolling element releasing portions 57 are provided on both sides in the longitudinal direction of the driven shaft insertion hole 54 as viewed in the axial direction. Further, the two rolling element releasing portions 57 are provided at positions that are separated from each other by 180 ° in the rotation direction and opposed in the radial direction. In addition, the both ends of the circumferential direction in each rolling element cancellation | release part 57 are comprised by the elastic part 58 which consists of materials which have elasticity, such as a rubber material. Each of the rolling element release portions 57 is disposed inside the clutch housing 41.

  As shown in FIGS. 2 and 3, the support member 43 holds the rolling element 44 between the clutch housing 41 and the driven side rotating body 45 that face each other in the radial direction. The support member 43 of this embodiment is made of resin.

  The support member 43 includes a ring portion 61 that forms an annular shape centering on the central axis L <b> 2 of the worm shaft 34. The outer diameter of the ring portion 61 is larger than the inner diameter of the clutch housing 41. The ring portion 61 is disposed on the motor portion 20 side (the upper side in FIG. 2) with respect to the fixed flange portion 41a of the clutch housing 41, and faces the fixed flange portion 41a in the axial direction. Further, an annular protrusion along the circumferential direction of the ring portion 61 is formed on the lower surface of the ring portion 61 (an end surface in the axial direction facing the fixed flange portion 41a), and the lower surface is in contact with the fixed flange portion 41a from the axial direction. Side protrusions 61a are formed. Further, an upper protrusion 61b that protrudes in the axial direction and abuts against the flange portion 52 of the drive side rotating body 42 from the axial direction is formed on the upper surface of the ring portion 61 (the end surface on the driving side rotating body 42 side).

  Rolling body holding portions that respectively hold the rolling elements 44 that form columnar shapes extending in the axial direction at two locations spaced apart in the circumferential direction on the inner peripheral side of the ring portion 61 (in this embodiment, two locations that are spaced by 180 °). 62 is formed.

Here, the rolling element 44 held by the rolling element holder 62 will be described in detail.
As shown in FIGS. 4A and 4B, each rolling element 44 is made of resin, and its central axis L3 is parallel to the central axis L1 of the rotating shaft 24 and the central axis L2 of the worm shaft 34. It is arranged to make. And as for each rolling element 44 of this embodiment, the shape seen from the axial direction has comprised the double-sided width shape. Therefore, each rolling element 44 has a shape having a longitudinal direction and a lateral direction when viewed from the axial direction. In the state shown in FIG. 4B, the radial direction of the clutch 40 is the longitudinal direction of the rolling element 44, and the circumferential direction of the clutch 40 is the short direction of the rolling element 44. Each rolling element 44 has first and second opposing surfaces 71a that are planar on both sides in the rotational direction X1 of the drive-side rotator 42 (the same as the circumferential direction of the clutch 40, hereinafter referred to as the rotational direction X1). , 71b. Furthermore, each rolling element 44 has first and second arcuate surfaces 72 a and 72 b on both sides in the radial direction of the clutch 40. The outer peripheral surface of each rolling element 44 of this embodiment is composed of these first and second opposing surfaces 71a and 71b and first and second arcuate surfaces 72a and 72b.

  As shown in FIG. 5, in each rolling element 44, the first and second opposing surfaces 71a and 71b are parallel to the central axis L3 and parallel to each other. In each rolling element 44, the first and second arcuate surfaces 72a and 72b have an arc shape with the center axis L3 as the center of curvature when viewed from the axial direction. Are equal. Further, the first and second arcuate surfaces 72a and 72b are formed parallel to the central axis L3 without being inclined. In each rolling element 44, the first arcuate surface 72a located radially outward is opposed to the cylindrical inner peripheral surface 41c of the clutch housing 41 in the radial direction and can contact the inner peripheral surface 41c. . On the other hand, in each rolling element 44, the second arcuate surface 72 b located on the radially inner side is opposed to the driven-side rotator 45 in the radial direction and can contact the driven-side rotator 45. In addition, the both end surfaces of the axial direction in each rolling element 44 have comprised the planar shape which makes a right angle with the 1st and 2nd opposing surfaces 71a and 71b (refer Fig.4 (a)).

  As shown in FIGS. 3, 4 (a), and 4 (b), each of the rolling element holding portions 62 has an axial support portion 63 that extends radially inward from the ring portion 61. The axial support part 63 faces the rolling element 44 in the axial direction. Moreover, each rolling element holding | maintenance part 62 is opposite to the ring part 61 along the axial direction (center axis line L1, L2 direction) from the both ends of the circumferential direction of the axial direction support part 63 (downward in Fig.4 (a)). And a pair of roller supports 64a and 64b (opposing portions). In each rolling element holding portion 62, paired roller supports 64a and 64b are positioned on both sides of the rolling element 44 in the rotation direction X1, and rotate the rolling element 44 so that the central axis L3 is parallel to the central axis L1. Holding from both sides in the direction X1. In addition, regarding the roller supports 64a and 64b forming a pair of the respective rolling element holding portions 62, the clutch 40 is viewed in the axial direction from the motor portion 20 side (that is, the state shown in FIG. The roller support positioned on the counterclockwise side is referred to as a first roller support 64a, and the roller support positioned on the clockwise side with respect to the rolling element 44 is referred to as a second roller support 64b.

  Further, the support member 43 has a connecting portion 66 that connects the tip end portion of the first roller support 64a of one rolling element holding portion 62 and the tip end portion of the second roller support 64b of the other rolling element holding portion 62 to each other. . The connecting portion 66 has an arc shape centered on the central axes L1 and L2 when viewed in the axial direction. Further, a holding claw 67 protruding between the paired first and second roller supports 64a and 64b is provided at the tip of each roller support 64a and 64b. Each holding claw 67 abuts against one end surface of the rolling element 44 in the axial direction from the axial direction, and prevents the rolling element 44 from falling off from the rolling element holding part 62 in the axial direction.

  Further, as shown in FIGS. 4B and 5, in each rolling element holding portion 62, a pair of roller supports 64a and 64b are provided on the side surfaces facing each other in the rotational direction X1, respectively. It has contact surfaces 68a and 68b. The first contact surface 68a provided on the first roller support 64a has a planar shape parallel to the central axes L1 and L2, and is a rolling element disposed between the pair of roller supports 64a and 64b. 44 is opposed to the first opposing surface 71a. Similarly to the first contact surface 68a, the second contact surface 68b provided on the second roller support 64b has a planar shape that is parallel to the central axes L1 and L2, and forms a pair of rollers. It faces the second facing surface 71b of the rolling element 44 disposed between the supports 64a and 64b. And the 1st and 2nd opposing surfaces 71a and 71b which oppose the rotation direction X1 have comprised mutually parallel. The axial lengths of the first and second contact surfaces 68a and 68b are the axial lengths of the rolling elements 44 (the axial lengths of the first and second opposing surfaces 71a and 71b). Longer than. The radial width of the clutch 40 at the first and second contact surfaces 68a and 68b is equal to or greater than the radial width of the clutch 40 at the first and second opposing surfaces 71a and 71b. .

  Further, the maximum outer diameter (that is, the width in the longitudinal direction of the rolling element 44 when viewed in the axial direction) D1 of each rolling element 44 is the first contact surface 68a and the second contact surface in each rolling element holding portion 62. It is longer than the distance D2 between 68b. Further, the distance D2 in each rolling element holding portion 62 is a width D3 of each rolling element 44 in the rotation direction X1 (in this embodiment, the length between the first facing surface 71a and the second facing surface 71b). It is longer than the width in the short direction of the rolling element 44 when viewed in the axial direction. Therefore, the rotation range of the rolling element 44 around the central axis L3 is determined between the paired roller supports 64a and 64b and the rolling element 44 disposed between the paired roller supports 64a and 64b. An allowable gap G1 is provided. For these reasons, each rolling element 44 is restricted from rotating about the central axis L3 by the pair of roller supports 64a and 64b.

  As shown in FIG. 5, when the rolling element 44 rotates counterclockwise around the central axis L3 between the pair of roller supports 64a and 64b when viewed in the axial direction from the motor unit 20, the alternate long and short dash line As illustrated in FIG. 5, in the rolling element 44, the end portion on the first arcuate surface 72 a side of the first facing surface 71 a comes into contact with the first contact surface 68 a. Further, in the rolling element 44, the end portion of the second facing surface 71b on the second arcuate surface 72b side contacts the second contact surface 68b. On the other hand, when the rolling element 44 rotates clockwise around the central axis L3 between the pair of roller supports 64a and 64b as viewed in the axial direction from the motor unit 20 side, the same as shown by the two-dot chain line in FIG. In the rolling element 44, the end portion on the second arcuate surface 72b side of the first facing surface 71a contacts the first contact surface 68a. Further, in the rolling element 44, the end portion on the first arc surface 72a side of the second facing surface 71b contacts the second contact surface 68b. As described above, the rotation of the rolling element 44 around the central axis L3 is limited by the pair of roller supports 64a and 64b, so that the outer peripheral surface of the rolling element 44 can be brought into sliding contact with the inner peripheral surface 41c of the clutch housing 41. The sliding contact range A1 is determined.

  As shown in FIGS. 2 and 6 (a), the two rolling elements 44 are held at equal angular intervals (180 ° intervals in the present embodiment) in the rotation direction X1 by being held by the support member 43 having the above configuration. Is arranged. Further, since the roller supports 64 a and 64 b holding the rolling elements 44 are inserted and arranged inside the clutch housing 41, each rolling element 44 is radially connected to the clutch housing 41 inside the clutch housing 41. Opposite to. Further, the rolling element 44 has a portion corresponding to the sliding contact range A1 (see FIG. 5) in the first arc surface 72a between the pair of roller supports 64a and 64b, and the inner peripheral surface 41c of the clutch housing 41. Can be touched. The support member 43 can rotate relative to the clutch housing 41 in the rotation direction X1.

  Further, each rolling element release portion 57 of the drive side rotating body 42 is inserted inside the clutch housing 41 through the inner peripheral side of the ring portion 61 of the support member 43. Furthermore, each rolling element release part 57 is arrange | positioned between the two rolling element holding parts 62, respectively, and adjoins each rolling element holding part 62 in the circumferential direction. Therefore, both end portions (respective elastic portions 58) in the rotation direction X1 of each rolling element release portion 57 are the first roller support 64a of one rolling element holding portion 62 and the second roller support 64b of the other rolling element holding portion 62. And the rotation direction X1. The support member 43 and the drive-side rotator 42 can rotate relative to each other in the rotation direction X1, and when the drive-side rotator 42 rotates, each rolling element release portion 57 is a roller support positioned on the front side in the rotation direction. 64a and 64b are contacted.

  As shown in FIGS. 2 and 3, the driven-side rotator 45 is formed integrally with the base end portion (the upper end portion in FIG. 2) of the worm shaft 34, and is made of metal. The driven-side rotating body 45 includes a control unit 81 and a driven-side connecting unit 82 that are arranged in parallel in the axial direction. The driven side connecting portion 82 is provided on the base end side (the upper side in FIG. 2) of the control portion 81.

  The control unit 81 is formed integrally with the worm shaft 34 and has a column shape extending in the axial direction of the worm shaft 34. The central axis of the control unit 81 is coincident with the central axis L2 of the worm shaft 34, and is formed coaxially with the worm shaft 34. As shown in FIG. 6A, when viewed from the direction of the central axis L2, the control unit 81 has a point-symmetric shape with the central axis L2 of the worm shaft 34 as the center of symmetry.

  A pair of control surfaces 83 are formed on the outer peripheral surface of the control unit 81. Each control surface 83 is formed at two locations that are equiangularly spaced in the circumferential direction (180 ° intervals in the present embodiment) on the outer peripheral surface of the control unit 81. Each control surface 83 has a planar shape that is parallel to the axial direction and orthogonal to the radial direction of the driven-side rotator 45. Further, the pair of control surfaces 83 are parallel to each other, and the axial length of each control surface 83 is longer than the axial length of the rolling element 44.

  As shown in FIGS. 2 and 6B, the driven side connecting portion 82 has a column shape extending in the axial direction of the worm shaft 34. The center axis of the driven side connecting portion 82 coincides with the center axis L2 of the worm shaft 34, and is formed coaxially with the worm shaft 34. The driven side connecting portion 82 is formed to be slightly thinner than the driven shaft insertion hole 54. The driven side connecting portion 82 has a substantially elliptical cross-sectional shape orthogonal to the axial direction, and the cross-sectional shape is constant in the axial direction. In addition, when viewed in the axial direction, the longitudinal direction of the driven side connecting portion 82 is a direction parallel to the control surface 83, and the short direction of the driven side connecting portion 82 is a direction orthogonal to the control surface 83. (See also FIG. 6 (a)). As shown in FIG. 6B, when viewed from the direction of the central axis L2, the driven side connecting portion 82 has a point-symmetric shape with the central axis L2 of the worm shaft 34 as the center of symmetry.

  A pair of first driven side transmission surfaces 84 and a pair of second driven side transmission surfaces 85 are formed on the outer peripheral surface of the driven side coupling portion 82. Of the two first driven side transmission surfaces 84 forming a pair, one first driven side transmission surface 84 is formed 180 ° opposite to the other first driven side transmission surface 84. The two first driven side transmission surfaces 84 are each parallel to the axial direction and are parallel to each other. The interval between the two first driven side transmission surfaces 84 is formed to be equal to the interval between the pair of drive side transmission surfaces 54 a provided in the driven shaft insertion hole 54 of the driving side rotating body 42.

  The second driven side transmission surface 85 is formed between the two first driven side transmission surfaces 84, and one second driven side transmission surface 85 is in relation to the other second driven side transmission surface 85. It is formed on the opposite side of 180 °. The two second driven side transmission surfaces 85 each have a planar shape parallel to the axial direction and are parallel to each other. Further, the distance between the two second driven side transmission surfaces 85 is formed to be equal to the distance between the pair of drive side transmission surfaces 54 a provided in the driven shaft insertion hole 54 of the driving side rotating body 42. The first driven side transmission surface 84 and the second driven side transmission surface 85 are formed in the axial direction from one end to the other end of the driven side coupling portion 82 in the axial direction.

  As shown in FIG. 2, the driven side rotating body 45 as described above is inserted into the clutch housing 41 and the support member 43 from the side opposite to the driving side rotating body 42. The driven-side rotator 45 is disposed coaxially with the clutch housing 41, the drive-side rotator 42 and the support member 43.

  Further, as shown in FIG. 6B, the driven side connecting portion 82 is loosely fitted in the driven shaft insertion hole 54 that can rotate integrally with the driving side rotating body 42. The first and second elastic members 55 and 56 are interposed between the outer peripheral surface of the driven side connecting portion 82 loosely fitted in the driven shaft insertion hole 54 and the inner peripheral surface of the driven shaft insertion hole 54. Specifically, the pair of second elastic members 56 are in contact with both ends in the longitudinal direction of the driven side connecting portion 82 when viewed in the axial direction. The four first elastic members 55 are respectively interposed between the two first driven side transmission surfaces 84 and the two second driven side transmission surfaces 85 and the drive side transmission surface 54a.

  When the driving side rotating body 42 rotates around the central axis with respect to the driven side rotating body 45, the driving side transmission surface 54a elastically deforms the first elastic member 55 and the first and second driven side transmission surfaces. It abuts on either one of 84 and 85 in the rotational direction. As a result, the drive-side rotator 42 and the driven-side rotator 45 are engaged in the rotation direction, and the rotational driving force of the drive-side rotator 42 is transmitted to the driven-side rotator 45.

  Further, as shown in FIG. 6A, the control unit 81 of the driven side rotator 45 is arranged such that the rolling elements 44 are interposed between the control surfaces 83 and the inner peripheral surface 41 c of the clutch housing 41. It is inserted inside the support member 43 and faces the clutch housing 41 and the rolling elements 44 in the radial direction. That is, the support member 43 holds the rolling element 44 between the inner peripheral surface 41 c of the clutch housing 41 and each control surface 83 of the driven side rotating body 45.

  The distance between each control surface 83 and the inner peripheral surface 41 c of the clutch housing 41 (interval in the direction orthogonal to the control surface 83) changes in the rotation direction of the driven-side rotator 45. In the present embodiment, the distance between the control surface 83 and the inner peripheral surface 41c of the clutch housing 41 is the longest at the center in the circumferential direction of each control surface 83, and from the center in the circumferential direction of each control surface 83 to the circumferential direction. It gradually shortens as it goes to both ends. Further, the distance between the center in the circumferential direction of each control surface 83 and the inner peripheral surface 41c of the clutch housing 41 is longer than the maximum outer diameter D1 (see FIG. 5) of the rolling element 44 and each control surface 83. The distance between the circumferential end of the rolling housing 44 and the inner peripheral surface 41 c of the clutch housing 41 is shorter than the maximum outer diameter D <b> 1 of the rolling element 44.

  As shown in FIG. 5, in the clutch 40 of the present embodiment, grease GR is applied to the inner peripheral surface 41 c of the clutch housing 41. The grease GR is disposed so as to be filled also in the space between the inner peripheral surface 41 c of the clutch housing 41 and the first arc surface 72 a of the rolling element 44. The grease GR has an effect of increasing the sliding friction between the inner peripheral surface 41c of the clutch housing 41 and the rolling element 44 when the rotating shaft 24 is not rotated (that is, when the driving side rotating body 42 is not rotated). There is. In the drawings other than FIG. 5, the illustration of the grease GR is omitted.

Next, the operation of the motor 10 configured as described above will be described together with its operation, focusing on the operation of the clutch 40.
As shown in FIG. 2 and FIG. 7A, when the motor unit 20 is driven by energizing the motor unit 20, the drive side rotating body 42 rotates together with the rotating shaft 24. That is, the driving side rotating body 42 is rotationally driven. 7A and 7B illustrate a case where the drive side rotating body 42 is rotationally driven in the first direction R1. And as shown to Fig.7 (a), with the rotation of 1st direction R1 of the drive side rotary body 42, the circumferential direction of the rotation direction front side in each rolling element cancellation | release part 57 of the drive side rotary body 42 The end portion (elastic portion 58) contacts the first roller support 64a of each rolling element holding portion 62 in the rotational direction, and presses the first roller support 64a and the rolling element 44 in the first direction R1. As a result, each rolling element 44 is arranged at the center in the circumferential direction of each control surface 83 of the driven-side rotating body 45. That is, the rolling element 44 is not clamped between the control surface 83 and the clutch housing 41 (that is, does not hinder the rotation of the driven side rotating body 45), and is unlocked.

  In the unlocked state, as shown in FIG. 7B, each drive-side transmission surface 54 a of the drive-side rotating body 42 is first connected to each second driven-side transmission surface 85 of the driven-side coupling portion 82. By abutting from the direction R1, the driving side rotating body 42 and the driven side rotating body 45 are coupled to the rotation direction X1 so as to be integrally rotatable. Thereby, the rotational driving force of the driving side rotating body 42 (rotating shaft 24) is transmitted to the driven side rotating body 45 (worm shaft 34), and the rotating shaft 24 and the worm shaft 34 are integrally rotated in the first direction R1. .

  At this time, as shown in FIGS. 5 and 7A, in the support member 43 and each rolling element 44, each first roller support 64a is pushed by each rolling element release portion 57 in the first direction R1. As a result, the drive-side rotator 42 and the driven-side rotator 45 rotate around the rotation axis of the drive-side rotator 42 (same as the central axis L1). Each rolling element 44 has a central axis L3 in a direction opposite to the rotation direction of the support member 43 between the roller supports 64a and 64b that make a pair by a frictional force between the inner surface 41c of the clutch housing 41. Try to rotate around. When each rolling element 44 rotates around its central axis L3 by an amount allowed by the allowance gap G1 between the roller supports 64a and 64b that hold the respective rolling elements 44, roller supports on both sides in the rotational direction X1 of each rolling element 44 Abuts on 64a and 64b. In the present embodiment, when the drive-side rotator 42 rotates in the first direction R1, each rolling element 44 has an end portion on the first arcuate surface 72a side of the first facing surface 71a at the first contact surface. 68a, and the end of the second opposing surface 71b on the second arcuate surface 72b side contacts the second contact surface 68b. Thereby, the rotation of each rolling element 44 around the central axis L <b> 3 is limited by the support member 43. Therefore, even if each rolling element 44 rotates around the rotation axis of the driving side rotating body 42 together with the driving side rotating body 42 when the driving side rotating body 42 is driven to rotate, the center axis L3 of each rolling element 44 is provided. It rotates only within the range allowed by the support member 43.

  Then, the rotation of the worm shaft 34 in the first direction R <b> 1 is transmitted to the output shaft 38 while being decelerated between the worm wheel 37 and output from the output shaft 38. Then, the window glass of the vehicle is raised and lowered via a window regulator (not shown) according to the rotation direction of the output shaft 38. When the energization of the motor unit 20 is stopped, the rotational drive of the rotary shaft 24, that is, the rotational drive of the drive side rotating body 42 is stopped.

  As shown in FIGS. 8A and 8B, when the driving of the motor unit 20 is stopped, that is, when the rotating shaft 24 (driving side rotating body 42) is not rotated, the load side (this embodiment) is used. Then, when a load is applied to the output shaft 38 from the side of the window regulator), the driven side rotating body 45 tends to rotate due to the load. 8A and 8B illustrate a case where the driven-side rotator 45 attempts to rotate in the second direction R2. Then, each control surface 83 of the driven side rotating body 45 presses the rolling element 44 disposed between each control surface 83 and the inner peripheral surface 41 c of the clutch housing 41 to the outer peripheral side. The rolling element 44 pushed by the control surface 83 has the first arc surface 72a abutting against the inner peripheral surface 41c of the clutch housing 41 between the pair of roller supports 64a and 64b, and the control surface 83 has the same control surface. The second arcuate surface 72b comes into contact with a portion closer to the end in the circumferential direction (the end on the rear side in the second direction R2 in the control surface 83) than the center in the circumferential direction of 83. Each rolling element 44 is sandwiched between a portion of the control surface 83 near the rear end in the second direction R <b> 2 and the inner peripheral surface 41 c of the clutch housing 41. Thereby, the rolling element 44 becomes a wedge, and the rotation (rotation in the second direction R2) of the driven side rotating body 45 is blocked (that is, the rotation of the worm shaft 34 is locked). Therefore, the output shaft 38 is prevented from rotating when the rotary shaft 24 (drive-side rotator 42) is not rotated. In the state (state shown in FIG. 8A) in which the driven-side rotator 45 is disposed at the lock position (position where the rolling element 44 is sandwiched between the driven housing 45 and the clutch housing 41), the state shown in FIG. As described above, each second driven side transmission surface 85 of the driven side connecting portion 82 does not come into contact with each driving side transmission surface 54a of the driving side rotating body 42 in the rotational direction (second direction R2).

  Incidentally, even when the driven-side rotating body 45 tries to rotate in the first direction R1 when the motor unit 20 (driving-side rotating body 42) is not driven, the rotation of the driven-side rotating body 45 is similarly prevented. The That is, each rolling element 44 is sandwiched between a portion of the control surface 83 near the rear end in the first direction R1 and the inner peripheral surface 41c of the clutch housing 41, whereby each rolling element 44 is As a wedge, rotation of the driven-side rotator 45 (rotation in the first direction R1) is blocked (that is, rotation of the worm shaft 34 is locked).

  In addition, as shown in FIGS. 2, 9A and 9B, when the driving side rotating body 42 rotates in the second direction R2 together with the rotating shaft 24 by driving the motor unit 20, Although the rotation directions of the members are opposite to each other, the clutch 40 connects the rotary shaft 24 and the worm shaft 34 in the same operation as when the driving side rotating body 42 rotates in the first direction R1 (see FIG. 7). To do. That is, with the rotation of the driving side rotating body 42 in the second direction R2, the circumferential end (elastic portion 58) on the front side in the rotating direction of each rolling element release portion 57 of the driving side rotating body 42 is The second roller support 64b of the rolling element holding part 62 is brought into contact with the second roller support 64b in the rotational direction, and the second roller support 64b and the rolling element 44 are pressed in the second direction R2. As a result, each rolling element 44 is arranged at the center in the circumferential direction of each control surface 83 of the driven-side rotator 45, and is brought into an unlocked state that is not sandwiched between the control surface 83 and the clutch housing 41. In the unlocked state, each drive-side transmission surface 54a of the drive-side rotator 42 comes into contact with each first driven-side transmission surface 84 of the driven-side coupling portion 82 from the second direction R2, thereby driving-side rotator. The rotational driving force of 42 (rotating shaft 24) is transmitted to the driven side rotating body 45 (worm shaft 34), and the rotating shaft 24 and the worm shaft 34 rotate integrally in the second direction R2.

  At this time, as shown in FIGS. 5 and 9A, in the support member 43 and each rolling element 44, each second roller support 64b is pushed by each rolling element release portion 57 in the second direction R2. As a result, the drive-side rotator 42 and the driven-side rotator 45 rotate around the rotation axis of the drive-side rotator 42. Each rolling element 44 has a central axis L3 in a direction opposite to the rotation direction of the support member 43 between the roller supports 64a and 64b that make a pair by a frictional force between the inner surface 41c of the clutch housing 41. Try to rotate around. When each rolling element 44 rotates around its central axis L3 by an amount allowed by the allowance gap G1 between the roller supports 64a and 64b that hold the respective rolling elements 44, roller supports on both sides in the rotational direction X1 of each rolling element 44 Abuts on 64a and 64b. In the present embodiment, when the driving side rotating body 42 rotates in the second direction R2, each rolling element 44 has an end portion on the second arcuate surface 72b side of the first facing surface 71a at the first contact surface. 68a, and the end of the second facing surface 71b on the first arc surface 72a side contacts the second contact surface 68b. Thereby, the rotation of each rolling element 44 around the central axis L <b> 3 is limited by the support member 43. Therefore, even if each rolling element 44 rotates around the rotation axis of the driving side rotating body 42 together with the driving side rotating body 42 when the driving side rotating body 42 is driven to rotate, the center axis L3 of each rolling element 44 is provided. It rotates only within the range allowed by the support member 43.

  When the rotation of the worm shaft 34 in the second direction R2 is transmitted to the output shaft 38 and output from the output shaft 38, the window of the vehicle is passed through a window regulator (not shown) according to the rotation direction of the output shaft 38. The glass is raised and lowered. When the energization of the motor unit 20 is stopped, the rotational drive of the rotary shaft 24, that is, the rotational drive of the drive side rotating body 42 is stopped. After the driving of the motor unit 20 is stopped, as described above, the rolling element 44 serves as a wedge to prevent the rotation of the driven side rotating body 45 (that is, the rotation of the worm shaft 34 is locked). The shaft 38 is prevented from being rotated (see FIG. 8A).

Next, characteristic effects of the present embodiment will be described.
(1) The rotation of each rolling element 44 around the central axis L <b> 3 of each rolling element 44 is limited by the support member 43. Therefore, even if each rolling element 44 rotates around the rotation axis of the driving side rotating body 42 together with the driving side rotating body 42 when the driving side rotating body 42 is driven to rotate, the center axis L3 of each rolling element 44 is provided. It rotates only within the range allowed by the support member 43. Accordingly, since the grease GR is prevented from being scattered due to the rotation of each rolling element 44 around its central axis L3, the grease GR between the inner peripheral surface 41c of the clutch housing 41 and each rolling element 44 is insufficient. Can be suppressed. As a result, when the rotational drive of the drive side rotator 42 is stopped, each rolling element 44 is less likely to become a wedge between the inner peripheral surface 41 c of the clutch housing 41 and the control surface 83 of the driven side rotator 45. This can be suppressed.

  (2) When each rolling element 44 rotates around the central axis L3 of each rolling element 44 by an allowable gap G1 provided between each rolling element 44 and the roller supports 64a and 64b facing each other in the rotation direction X1. The roller supports 64a and 64b come into contact with each rolling element 44 in the rotational direction. Thereby, each rolling element 44 is prevented from further rotation around the central axis L3 of each rolling element 44 by the roller supports 64a and 64b. Therefore, the scattering of the grease GR due to the rotation of each rolling element 44 around the central axis L3 of each rolling element 44 can be suppressed with a simple configuration. As a result, the shortage of the grease GR between the inner peripheral surface 41c of the clutch housing 41 and each rolling element 44 can be easily suppressed.

  Further, each rolling element 44 rotates around the central axis L3 of each rolling element 44 within a rotation range determined by providing an allowable gap G1 between each rolling element 44 and the roller supports 64a and 64b. be able to. That is, the posture of each rolling element 44 with respect to the inner peripheral surface 41c of the clutch housing 41 can be changed around the central axis L3. Since the grease GR is moved between each rolling element 44 and the inner peripheral surface 41c of the clutch housing 41 as the rolling element 44 rotates around the central axis L3 within the rotation range, each rolling element 44 is moved. In this case, the grease GR can be supplied to the portion in contact with the inner peripheral surface 41c of the clutch housing 41. Accordingly, it is possible to further suppress the shortage of the grease GR between the inner peripheral surface 41c of the clutch housing 41 and each rolling element 44.

  (3) When each rolling element 44 rotates about the center axis L3 of each rolling element 44 by the amount allowed by the permissible gap G1, it contacts the roller supports 64a and 64b on both sides in the rotational direction X1 of each rolling element 44, respectively. Touch. Therefore, the rolling element 44 that contacts the roller supports 64a and 64b can more stably maintain the posture that contacts the roller supports 64a and 64b. As a result, it is possible to suppress the generation of noise in the clutch 40 when the drive side rotating body 42 is driven to rotate.

  (4) Each rolling element 44 has roller support 64a, 64b and planar first and second opposing surfaces 71a, 71b facing the rotation direction X1 on both sides in the rotation direction X1 of each rolling element 44. Therefore, it becomes easy to set the allowable gap G1 provided between each rolling element 44 and the roller supports 64a and 64b holding each rolling element 44. Moreover, since it is suppressed that the shape of each rolling element 44 is complicated, each rolling element 44 can be manufactured easily.

  (5) At the start of the rotational drive of the drive-side rotator 42, the rotational drive force of the drive-side rotator 42 is transmitted from the rolling element release portion 57 to the roller supports 64a and 64b, and further from the roller supports 64a and 64b to the rolling elements 44. Is transmitted to. At this time, the roller supports 64a and 64b to which the rotational driving force is transmitted from the drive-side rotating body 42 have the first contact surface 68a or the second contact surface 68b on the first facing surface 71a of the rolling element 44 or By making surface contact with the second facing surface 71 b, the rotational driving force can be efficiently transmitted to the rolling elements 44. Therefore, it is possible to easily release the rolling element 44 between the inner peripheral surface 41 c of the clutch housing 41 and the driven side rotating body 45.

  (6) In the motor 10, the rotary shaft 24 and the worm shaft 34 are connected via the clutch 40 in which the grease GR between the inner peripheral surface 41c of the clutch housing 41 and each rolling element 44 is suppressed from being insufficient. It is connected. Therefore, when the rotation shaft 24 is not rotated, the rotation shaft 24 is further suppressed from rotating from the worm shaft 34 side.

In addition, you may change the said embodiment as follows.
The rolling element 44 may have a grease accommodating recess that opens to the sliding contact range A1 on the outer peripheral surface of the rolling element 44 and accommodates the grease GR. In addition, the grease accommodating recess is formed so that the outer peripheral surface of the rolling element 44 remains in the sliding contact range A1, and is not formed over the entire sliding contact range A1.

  For example, the rolling element 44 shown in FIGS. 10A and 10B has a grease accommodating recess 75 at one end in the axial direction of the rolling element 44 (the end on the base end side of the roller supports 64a and 64b). . The grease accommodating recess 75 opens to one side of the rolling element 44 in the axial direction and radially outward of the rolling element 44 (on the clutch housing 41 side). In addition, in FIG.10 (b), the dot is attached | subjected to the sliding contact range A1.

  Further, for example, the rolling element 44 shown in FIGS. 11A and 11B has a grease containing recess 76 at the other end in the axial direction of the rolling element 44 (the end on the tip side of the roller supports 64a and 64b). Have. The grease accommodating recess 76 is open to the other side in the axial direction of the rolling element 44 and the radially outer side (clutch housing 41 side) of the rolling element 44.

And as shown to Fig.12 (a) and FIG.12 (b), the rolling element 44 may have the grease accommodating recessed parts 75 and 76 in the both ends of an axial direction.
Further, for example, the rolling elements 44 shown in FIGS. 13A and 13B have a grease accommodating recess 77 in the central portion in the axial direction. The grease accommodating recess 77 is recessed in the radial direction of the first arcuate surface 72a from a portion corresponding to the sliding contact range A1 in the first arcuate surface 72a of the rolling element 44.

  14 (a) and 14 (b), the rolling element 44 has grease accommodating recesses 75 and 76 at both axial end portions, and further has a grease accommodating recess at the axial central portion. 77 may be included.

  In the examples shown in FIGS. 10 to 14, the grease receiving recesses 75, 76, 77 are all rectangular when viewed from the radial direction of the first arcuate surface 72 a, but the present invention is not limited to this. A circular shape, a polygonal shape, or the like may be used. Moreover, the rolling element 44 may include four or more grease-accommodating recesses that open to the sliding contact range A1.

  In this way, the grease receiving recesses 75, 76, 77 provided in the rolling element 44 are opened in a sliding contact range A 1 that can be slidably contacted with the inner peripheral surface 41 c of the clutch housing 41. Therefore, the grease GR accommodated in the grease accommodating recesses 75, 76, 77 is pulled out toward the inner peripheral surface 41 c of the clutch housing 41 along with the rotation of the rolling element 44, and the inner periphery of the rolling element 44 and the clutch housing 41. Supplied between the surface 41c. Accordingly, it is possible to further suppress the shortage of the grease GR between the inner peripheral surface 41c of the clutch housing 41 and the rolling element 44. As a result, when the rotational drive of the driving side rotating body 42 is stopped, the rolling element 44 is less likely to become a wedge between the inner peripheral surface 41c of the clutch housing 41 and the control surface 83 of the driven side rotating body 45. Can be further suppressed.

  The rolling element 44 is restricted by the support member 43 from rotating around the central axis L3 of the rolling element 44. Therefore, in the outer peripheral surface of the rolling element 44, the curvature of the portion that can contact the inner peripheral surface 41c of the clutch housing 41 and the portion that can contact the control surface 83 of the driven-side rotating body 45 can be made different. So, in the said embodiment, although the 1st circular arc surface 72a and the 2nd circular arc surface 72b are the same curvature in each rolling element 44, a different curvature may be sufficient.

  For example, as shown in FIG. 15, the second arcuate surface 72 c that contacts the control surface 83 of the driven-side rotator 45 is more curved than the first arcuate surface 72 a that contacts the inner peripheral surface 41 c of the clutch housing 41. It is good also as a small circular arc shape. In this way, the wedge angle θ1 when the inner peripheral surface 41c of the clutch housing 41 and the control surface 83 of the driven side rotating body 45 sandwich the rolling element 44 as a wedge is set, and the entire outer peripheral surface of the rolling element 44 is the first. It can be made smaller than the case of the curvature of the circular arc surface 72a (that is, in the case of a cylindrical shape). Then, when the rotational driving of the driving side rotating body 42 is stopped, the angle at which the driven side rotating body 45 rotates until the rolling element 44 is sandwiched between the inner peripheral surface 41 c of the clutch housing 41 and the control surface 83. Is smaller than the case where the entire outer peripheral surface of the rolling element 44 has the curvature of the first arc surface 72a. Therefore, when the driven-side rotating body 45 tries to rotate when the driving-side rotating body 42 is not driven to rotate, the driven-side rotating body 44 rotates as compared with the case where the entire outer peripheral surface of the rolling body 44 has the curvature of the first arcuate surface 72a. When the rotational speed of the body 45 is smaller, the rolling element 44 can be held between the driven side rotating body 45 and the clutch housing 41. Therefore, when the rotating body 45 is to be rotated from the driven side rotating body 45 side, the rolling body 44 can be held between the driven side rotating body 45 and the clutch housing 41 at an earlier stage. When the motor is stopped, the rotation of the driven-side rotator 45 can be quickly prevented.

  As shown in FIGS. 16 (a) and 16 (b), the support member 43 is provided with a roller support 64a by the rolling element 44 that tries to rotate around the central axis L3 when the driving side rotating body 42 is not rotated. , 64b may be provided so as to have a contact portion 69 that is moved radially outward by being pressed and contacts the inner peripheral surface 41c of the clutch housing 41. More specifically, in the support member 43, on both sides of the rolling element holding portion 62 in the circumferential direction (rotation direction X1), the contact portion protruding radially outward (clutch housing 41 side) from the radially outer side surface of the coupling portion 66 is provided. A contact portion 69 is provided. When the rolling element 44 is not sandwiched between the inner peripheral surface 41c of the clutch housing 41 and the control surface 83 of the driven side rotating body 45 (for example, in the state shown in FIG. 16A), the abutting portion 69 is provided. The clutch housing 41 is positioned away from the inner peripheral surface 41c. Then, as shown in FIG. 16B, when the driven side rotating body 45 tries to rotate when the driving side rotating body 42 is not rotated, the rolling body 44 is sandwiched between the driven side rotating body 45 and the clutch housing 41. In the meantime, the rolling element 44 is rotated around its central axis L3 by the frictional force with the driven side rotating body 45. FIG. 16B illustrates a state in which the driven side rotating body 45 is about to rotate in the second direction R2. Then, since the maximum outer diameter D1 of the rolling element 44 is longer than the distance D2 between the roller supports 64a and 64b, the rolling element 44 rotates around the central axis L3 to rotate the roller supports 64a and 64b from the rotational direction around the central axis L3. After the contact, the roller supports 64a and 64b are further pressed away from each other. The paired roller supports 64a and 64b move outward in the radial direction by moving in a direction away from each other. That is, the roller supports 64a and 64b are moved radially outward by being pressed by the rolling elements 44 rotated around the central axis L3. Then, the support member 43 is elastically deformed, and the connecting portion 66 provided integrally with the roller supports 64a and 64b is moved outward in the radial direction. As a result, the contact portion 69 is moved outward in the radial direction, and the clutch housing. 41 abuts against the inner peripheral surface 41c of 41. Therefore, it is possible to suppress the rolling element 44 from moving in the rotation direction X1 of the driving side rotating body 42 even by the frictional force generated between the contact portion 69 and the inner peripheral surface 41c of the clutch housing 41. Accordingly, since the rolling element 44 is more easily sandwiched between the driven side rotating body 45 and the inner peripheral surface 41 c of the clutch housing 41, the rotation of the driven side rotating body 45 is further increased when the driving side rotating body 42 is not rotated. It becomes easy to stop. Even when the load applied to the output shaft 38 becomes larger, in addition to the frictional force between the rolling element 44 and the inner peripheral surface 41 c of the clutch housing 41, the abutting portion 69 and the inner periphery of the clutch housing 41 are also provided. Since the frictional force with the surface 41 c acts so as to prevent the driven side rotating body 45 from rotating, it is easy to prevent the driven side rotating body 45 from rotating.

  In addition, when the holding of the rolling element 44 by the inner peripheral surface 41c of the clutch housing 41 and the driven side rotating body 45 is released at the start of the rotational driving of the driving side rotating body 42, the support member 43 returns to the original shape. The contact portion 69 is separated from the inner peripheral surface 41 c of the clutch housing 41.

  In the example shown in FIGS. 16A and 16B, the contact portion 69 has a shape protruding radially outward from the connecting portion 66 of the support member 43, but the shape of the contact portion 69 is Not limited to this. The contact portion moves outward in the radial direction when the roller supports 64a and 64b are moved outward in the radial direction by the rolling element 44 about to rotate around the central axis L3 when the drive side rotating body 42 is not rotated. As long as it is in contact with the inner peripheral surface 41 c of the clutch housing 41. For example, you may comprise so that the outer peripheral surface of the connection part 66, the radial direction outer side surface of roller support 64a, 64b, etc. may become a contact part.

  In the above embodiment, the portions of the roller supports 64a and 64b with which the rolling elements 44 that rotate about the central axis L3 abut are the flat first and second abutting surfaces 68a and 68b. However, the first and second contact surfaces 68a and 68b with which the rolling element 44 rotated around the central axis L3 contacts may not necessarily be planar. For example, the first and second contact surfaces 68a and 68b may have an arc shape when viewed from the axial direction.

  In the above embodiment, the rolling element 44 has the planar first and second opposing surfaces 71a and 71b on both sides in the rotational direction X1. However, the first and second opposing surfaces 71a and 71b, which are portions that contact the roller supports 64a and 64b when the rolling member 44 rotates around the central axis L3 in the rolling member 44, are not necessarily flat. Also good. That is, the rolling element 44 does not necessarily have a two-plane width shape. The rolling element 44 may be any shape as long as the shape seen from the axial direction has a longitudinal direction and a lateral direction, and has a column shape extending in the axial direction. For example, the rolling element 44 may have first and second opposing surfaces 71a and 71b whose arc viewed from the axial direction has an arc shape (however, the rolling element 44 is not cylindrical). . Further, for example, the rolling element 44 may have an elliptical shape when viewed from the axial direction.

  In the above embodiment, when the rolling element 44 rotates about the central axis L3 of the rolling element 44 by the amount permitted by the allowable gap G1, the rolling element 44 contacts the roller supports 64a and 64b on both sides in the rotation direction X1 of the rolling element 44. Touch. However, when the rolling element 44 rotates around the central axis L3 of the rolling element 44 by an amount permitted by the allowable gap G1, the rolling element 44 contacts the roller support 64a or the roller support 64b only on one side in the rotational direction X1 of the rolling element 44. It may be in contact. In this case, the rolling element 44 is formed in, for example, a shape in which a part of the outer periphery of the cylinder is planar (substantially D shape in the axial direction).

  In the above-described embodiment, the rotation range around the central axis L <b> 3 of the rolling element 44 is limited by providing the permissible gap G <b> 1 between the paired roller supports 64 a and 64 b and the rolling element 44. However, if the rotation of the rolling element 44 around the central axis L3 is limited, the permissible gap G1 is not necessarily provided between the roller supports 64a and 64b and the rolling element 44. For example, the first opposing surface 71a of the rolling element 44 and the first abutting surface 68a of the roller support 64a are always in contact with each other, and the second opposing surface 71b of the rolling element 44 and the second opposing surface of the roller support 64b are in contact with each other. It is good also as a structure which always contact | abutted with the contact surface 68b. If it does in this way, rotation around the central axis L3 is restricted by roller supports 64a and 64b so that it may not rotate about the central axis L3. Even in this case, since the scattering of the grease GR due to the rotation of the rolling element 44 around the central axis L3 is suppressed, the grease GR between the inner peripheral surface 41c of the clutch housing 41 and each rolling element 44 is reduced. The shortage can be suppressed.

  The roller supports 64a and 64b may be changed as shown in FIG. The radially outer portions of the paired roller supports 64a and 64b face each other across the rolling element 44 along the inner peripheral surface 41c of the clutch housing 41 (along the rotational direction X1 of the drive side rotating body 42). Each of the protruding pieces 64x is provided with a protruding piece 64x that restricts the movement of the rolling element 44 to the radially outer side. In the above-described embodiment shown in FIG. 5 and the like, the tip of each protruding piece 64x has an acute-angled protrusion shape. However, in the example shown in FIG. 17, a tip surface 64y is provided at the tip of each protruding piece 64x. ing. Each distal end surface 64y is parallel to one plane parallel to each other, specifically, to a radial straight line connecting the central axis L1 of the rotating shaft 24 (the central axis L2 of the worm shaft 34) and the central axis L3 of the rolling element 44. It is a plane.

  The operation of the roller supports 64a and 64b will be described as a representative case where the driving side rotating body 42 and the support member 43 are rotated in the first direction R1 by driving the motor unit 20. The first roller support 64a rotated around in the same direction. At that time, the protruding piece 64x of the roller support 64a advances so as to scrape the grease GR, but the grease GR moves toward the inner peripheral surface 41c of the clutch housing 41 at the tip surface 64y provided at the tip of the protruding piece 64x. A flow occurs (in FIG. 17, an arrow α). As a result, the grease GR is easily held between the inner peripheral surface 41 c of the clutch housing 41 and the first arc surface 72 a of the rolling element 44.

  Further, if the gap G2 between the protruding piece 64x and the first arcuate surface 72a of the rolling element 44 is set to be small due to the provision of the tip face 64y at the tip of the protruding piece 64x, the grease to the gap G2 is set. It is possible to suppress the escape of GR. This also promotes the flow of the grease GR toward the inner peripheral surface 41 c of the clutch housing 41 described above, and the relationship between the inner peripheral surface 41 c of the clutch housing 41 and the first circular arc surface 72 a of the rolling element 44. This contributes to a situation in which the grease GR is easily held in between.

  In addition, the shape and direction of the front end surface 64y of each protrusion piece 64x are examples, and may be changed as appropriate. For example, the tip surface 64y may not be a single plane. Further, the tip surface 64y may be a surface that intersects the rotational direction X1 of the drive-side rotating body 42 that can cause the flow of the grease GR described above even if it is not a surface parallel to the above-described radial straight line. That's fine.

  In the above embodiment, the grease GR is applied to the inner peripheral surface 41 c of the clutch housing 41. However, as long as the grease GR is disposed at least between the inner peripheral surface 41c of the clutch housing 41 and the rolling element 44, the position of the grease GR is not limited to the position of the above embodiment.

  The shapes of the clutch housing 41, the driving side rotating body 42, the support member 43, the rolling element 44, and the driven side rotating body 45 constituting the clutch 40 are not necessarily the shapes of the above-described embodiments. For example, the driving side rotating body 42 may be formed integrally with the rotating shaft 24. Further, for example, the driven-side rotator 45 may be provided separately from the worm shaft 34 and assembled so as to be rotatable integrally with the worm shaft 34. Further, the number of rolling elements 44 is not limited to two, and it is sufficient that at least one rolling element 44 is disposed between the inner peripheral surface 41 c of the clutch housing 41 and the driven side rotating body 45.

  In the above embodiment, the speed reduction mechanism 32 included in the output unit 30 includes the worm shaft 34 and the worm wheel 37, but the number of gears included in the speed reduction mechanism 32 may be changed as appropriate. Further, the speed reduction mechanism 32 may not necessarily be a worm speed reduction mechanism as long as it has a driven shaft connected to the rotation shaft 24 via the clutch 40. Further, the output unit 30 does not necessarily include the speed reduction mechanism 32 as long as it has a driven shaft connected to the rotation shaft 24 via the clutch 40 and can output the rotation transmitted from the rotation shaft 24. Also good.

In the above embodiment, the motor 10 is used as a drive source for the power window device, but may be used as a drive source for other devices.
In the above embodiment, the clutch 40 is provided in the motor 10 and connects the rotary shaft 24 and the worm shaft 34 of the speed reduction mechanism 32. However, the clutch 40 may be provided in a device other than the motor 10 and connect a rotating shaft that is rotationally driven to a driven shaft that is transmitted with the rotational driving force of the rotating shaft.

DESCRIPTION OF SYMBOLS 10 ... Motor, 20 ... Motor part, 24 ... Rotating shaft, 30 ... Output part, 34 ... Worm shaft as driven shaft, 40 ... Clutch, 41 ... Clutch housing, 41c ... Inner peripheral surface, 42 ... Drive side rotating body, DESCRIPTION OF SYMBOLS 43 ... Support member, 44 ... Rolling body, 45 ... Driven side rotating body, 57 ... Rolling body cancellation | release part, 64a, 64b ... Roller support as an opposing part, 64x ... Projection piece, 64y ... Tip surface, 68a ... Contact surface First contact surface as 68b ... Second contact surface as contact surface, 69 ... Contact portion, 71a ... First opposing surface as opposing surface, 71b ... Second as opposing surface Opposing surface, 72a ... first arc surface, 72b, 72c ... second arc surface, 75, 76, 77 ... grease housing recess, A1 ... sliding contact range, G1 ... allowance gap, GR ... grease, L3 ... rolling element Center axis line, X1.

Claims (10)

An annular clutch housing;
A drive-side rotating body that is rotationally driven;
A driven-side rotator at least a part of which is disposed inside the clutch housing and to which a rotational driving force is transmitted from the drive-side rotator;
It is disposed between the inner peripheral surface of the clutch housing and the driven-side rotator, and rotates around the rotational axis of the drive-side rotator together with the drive-side rotator when the drive-side rotator is driven to rotate. A rolling element that prevents rotation of the driven-side rotating body by being sandwiched between an inner peripheral surface of the clutch housing and the driven-side rotating body during non-rotating driving of the side rotating body;
A support member that holds the rolling element between an inner peripheral surface of the clutch housing and the driven-side rotator, and rotates around the rotation axis of the drive-side rotator together with the drive-side rotator;
Grease disposed at least between the inner peripheral surface of the clutch housing and the rolling element;
A clutch with
The clutch is characterized in that the rolling element is restricted from rotating around the central axis of the rolling element by the support member. The clutch according to claim 1, wherein
The support member has a facing portion facing the rolling element in the rotation direction of the driving side rotating body,
Between the facing portion and the rolling element, an allowable gap for determining a rotation range of the rolling element around a central axis of the rolling element is provided,
The clutch is characterized in that when the rolling element rotates around the central axis of the rolling element by an amount allowed by the allowable gap, the rolling element abuts against the opposing portion and is prevented from further rotation. The clutch according to claim 2,
The opposing portions are provided on both sides of the rotation direction of the driving side rotating body with respect to the rolling element,
When the rolling element rotates about the center axis of the rolling element by an amount allowed by the allowable gap, the rolling element comes into contact with the facing portion on both sides in the rotation direction of the driving-side rotating element. clutch. The clutch according to claim 3,
The said rolling element has a planar opposing surface which opposes the said opposing part and the rotation direction of the said drive side rotary body in the both sides of the rotation direction of the said drive side rotary body in the said rolling element. The clutch according to claim 4,
The drive-side rotator has a rolling element release portion that transmits the rotational driving force of the drive-side rotator to the facing portion when the drive-side rotator is rotationally driven.
The rolling element is pressed in the rotation direction of the driving-side rotating body by the rolling-element releasing portion via the facing portion at the start of rotational driving of the driving-side rotating body, whereby the inner peripheral surface of the clutch housing And the driven side rotating body is released,
The clutch is characterized in that the facing portion has a planar shape and has a contact surface that can come into surface contact with the facing surface in the rotational direction of the drive side rotating body. The clutch according to any one of claims 1 to 5,
The support member includes a facing portion that faces the rolling element in the rotation direction of the driving side rotating body, and the rolling element that is about to rotate around the central axis of the rolling element when the driving side rotating body is not rotated. And a contact portion that moves radially outward when the facing portion is pressed and contacts the inner peripheral surface of the clutch housing. The clutch according to any one of claims 1 to 6,
The rolling element has an arcuate first arcuate surface that can contact the inner circumferential surface of the clutch housing, an outer peripheral surface of the rolling element, and the first arcuate surface as viewed from the central axis direction of the rolling element. And a second arcuate surface that is in contact with the driven-side rotating body, and when the driving-side rotating body is not driven to rotate, the first arcuate surface of the clutch housing The clutch is in contact with an inner peripheral surface, and the second arcuate surface is in contact with the driven-side rotating body and is sandwiched between the inner peripheral surface of the clutch housing and the driven-side rotating body. . The clutch according to any one of claims 1 to 7,
The rolling element is slidably contactable with the inner peripheral surface of the clutch housing by rotating around the central axis of the rolling element within a range allowed by the support member on the outer peripheral surface of the rolling element. And a grease containing recess that opens to the sliding contact range and accommodates the grease. The clutch according to any one of claims 1 to 8,
The support member has a facing portion facing the rolling element in the rotation direction of the driving side rotating body, and has a protruding piece extending toward the rolling element on a radially outer portion of the facing portion, and the protruding piece A clutch characterized in that a front end surface intersecting with a rotation direction of the driving side rotating body is provided at a front end portion of the clutch. A motor unit having a rotary shaft that is driven to rotate;
The clutch according to any one of claims 1 to 9, comprising the driving side rotating body that rotates integrally with the rotating shaft.
An output unit that has a driven shaft that rotates integrally with the driven-side rotator, and that outputs a rotational driving force transmitted to the driven shaft;
A motor comprising: