JP2005069492A - Motor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch capable of reducing abnormal sound and vibration caused in each connection part and loss of driving force in each connection part even if a driving side rotary shaft and a driven side rotary shaft are in a non-coaxial condition. <P>SOLUTION: This clutch 30 transmits rotation to the driven side rotary shaft 23 from the driving side rotary shaft 13 by engaging or disengaging a driving side rotary body 33 fitted in and connected with the driving side rotary shaft 13 so as to rotate integrally and a driven side rotary body 32 arranged coaxially with the driving side rotary shaft 13 and fitted in and connected with the driven side rotary shaft 23 so as to rotate integrally for each other in the direction of rotation and prevents transmission of rotation to the driving side rotary shaft 13 from the driven side rotary shaft 23. The connection part of the driving side rotary body 33 and the driven side rotary body 32 and the connection part of the driving side rotary body 33 and the driving side rotary shaft 13 are set to enable relative inclination between the members to allow a non-coaxial condition of the driving side rotary shaft 13 and the driven side rotary shaft 23. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a motor including a clutch that prevents rotation of a driven side from being transmitted to a driving side.

  2. Description of the Related Art Conventionally, for example, a motor provided in a power window device is a regulator that reduces the rotational speed of a rotating shaft via a motor body having a rotating shaft and a worm shaft that is integrally formed with the rotating shaft or arranged on a concentric shaft. An output unit for transmitting to the (driven side) is provided. When the motor is driven, the rotation of the rotation shaft is transmitted to the output unit via the worm shaft. The rotation of the rotating shaft whose rotational speed is reduced in the output unit is converted into reciprocating motion by a regulator. Thus, the regulator opens and closes by moving the window glass up and down.

  In such a power window device, when the motor is not driven, the downward load applied to the window glass is converted into a rotational force by the regulator, and this rotational force is opposite to the original. It operates to rotate the rotating shaft of the motor body. Such rotation transmission may cause the window glass to be stolen by being opened by an external force.

  Therefore, in order to prevent this type of rotation transmission, a motor having a clutch for preventing the rotation on the driven side from being transmitted to the driving side is known. In such a motor, the rotation on the driving side is transmitted to the driven side by a clutch, while the rotation on the driven side is not transmitted to the driving side.

  By the way, this type of clutch transmits, for example, the rotation on the driving side to the driven side or is driven by the driving side rotating body and the driven side rotating body engaging / disengaging with each other in the rotational direction. Side rotation is not transmitted to the drive side. The drive-side rotating shaft is connected to such a drive-side rotating body, and the driven-side rotating shaft is connected to the driven-side rotating body, but the center axis of the driving-side rotating shaft matches that of the driven-side rotating shaft. It is desirable to be assembled (coaxially).

  This is because the structure of each coupling portion is not set so as to allow the driving-side rotating shaft and the driven-side rotating shaft to be in a non-coaxial state. The non-coaxial state is at least one of a state where the inclinations of the rotation center axes of the two rotation shafts do not coincide with each other and a state where the connecting portions of the two rotation shafts are displaced in the radial direction.

  However, due to the dimensional error of each rotating shaft, the bearing that supports the rotating shaft, and the housing that fixes the bearing, the center axes of the rotating shafts do not coincide with each other (non-coaxial state). In some cases, the driven-side rotating shaft presses a part of the driven-side rotating body in the radial direction, and the driven-side rotating body is bent by the pressing force. In such a case, when the rotating shaft and the rotating body are rotated, a large load is applied to each connecting portion in the radial direction, and a large noise or vibration is generated in the connecting portion, or a loss of driving force in the connecting portion is large. There were problems such as becoming.

  The present invention has been made in view of such circumstances, and its purpose is to generate abnormal noise and vibration generated from each connecting portion even when the driving side rotating shaft and the driven side rotating shaft are in a non-coaxial state, and the connecting portion. An object of the present invention is to provide a motor provided with a clutch that can reduce the loss of driving force in the motor.

  In order to achieve the above object, the invention according to claim 1 is directed to a rotating shaft in a motor including a motor body having a rotating shaft, and a speed reducing portion having a worm shaft arranged coaxially with the rotating shaft. A driving side rotating body provided between the worm shaft and connected to the rotating shaft so as to rotate together with the worm shaft, and a driven side rotating body connected to the worm shaft so as to rotate together with the worm shaft are mutually engaged in the rotation direction. Alternatively, in the motor having a clutch connected so as to transmit rotation from the rotating shaft to the worm shaft and to prevent rotation transmission from the worm shaft to the rotating shaft by being disengaged, the driven side rotating body Is arranged rotatably on the inner side of the outer ring, and a control surface is formed on the radially outer side of the driven-side rotator so that the distance from the inner peripheral surface of the outer ring changes in the rotational direction. Inner peripheral surface of the outer ring A sandwiched body is disposed between the worm shaft and the rotating body from the worm shaft by holding the sandwiched body between the control surface and the inner peripheral surface of the outer ring when the driven rotating body rotates. The rotation transmission to the shaft is prevented, and when the driving side rotating body rotates, the gripped body is disposed at a position where it is not sandwiched and the rotation is transmitted from the rotating shaft to the worm shaft, In order to allow a non-coaxial state between the rotating shaft and the worm shaft, at least of a connecting portion between the driving side rotating body and the driven side rotating body, and a connecting portion between the driving side rotating body and the rotating shaft. The gist is that the relative inclination between the members of one part is set to be possible.

  According to a second aspect of the present invention, in the motor according to the first aspect, the portion that allows the relative inclination between the members is a connecting portion between the driving side rotating body and the driven side rotating body. Yes, the rotating shaft and the driving side rotating body are connected by biasing the fitting convex portion of the rotating shaft to the side surface of the fitting concave portion of the driving side rotating body by the biasing means. Is the gist.

  According to a third aspect of the present invention, in the motor according to the first or second aspect, the speed reduction portion includes a gear housing, the gear housing has a clutch housing recess, and the outer ring The gist is that it is fixed to the clutch housing recess.

The gist of the invention described in claim 4 is the motor according to any one of claims 1 to 3, wherein the held object is a sphere.
(Function)
According to the invention described in each claim, the rotation is transmitted from the rotating shaft to the worm shaft by the clutch, and the rotation transmission from the worm shaft to the rotating shaft is prevented. The clutch includes at least one of a connecting portion between the driving side rotating body and the driven side rotating body and a connecting portion between the driving side rotating body and the rotating shaft so as to allow a non-coaxial state between the rotating shaft and the worm shaft. The relative inclination between the members of one part is set to be possible. And, when the portion where the relative inclination between the members can be set as one portion, the connecting portion of the rotating shaft and the worm shaft coincides in the radial direction, and the inclination of the rotation center axis of the both shafts does not coincide Even if it becomes, the big load of radial direction does not act on each connection part, The noise and vibration which generate | occur | produce from each connection part, and the loss of the driving force in a connection part become small. In addition, when two parts are set to allow relative inclination between members, the inclination of the rotation center axis of the rotating shaft and the worm shaft is different, and the connecting portion of both axes is displaced in the radial direction Even if it becomes, the big load of radial direction does not act on each connection part, The noise and vibration which generate | occur | produce from each connection part, and the loss of the driving force in a connection part become small. The clutch is provided between the rotating shaft of the motor main body and the worm shaft of the speed reducing unit. That is, since the clutch is provided at a location where the torque is small, the strength required for the clutch can be reduced and the clutch can be downsized. Further, during rotation of the driven side rotating body, the transmission of rotation from the worm shaft to the rotating shaft is prevented by holding the sandwiched body between the control surface of the driven side rotating body and the inner peripheral surface of the outer ring. Further, when the driving side rotating body rotates, the driven body is disposed at a position where the holding body is not held, and the rotation is transmitted from the rotating shaft to the worm shaft.

  According to the second aspect of the present invention, the clutch has a relative inclination between the members of the connecting portion of the driving side rotating body and the driven side rotating body so as to allow the non-coaxial state of the rotating shaft and the worm shaft. Is set to be possible. In such a case, even if the connecting portion of the rotating shaft and the worm shaft coincides in the radial direction and the inclination of the rotation center axis of the two shafts does not match, a large radial load is applied to each connecting portion. It does not act, and the noise and vibration which generate | occur | produce from each connection part and the loss of the driving force in a connection part become small.

  According to the fourth aspect of the present invention, since the to-be-held member is a sphere, it is not restricted by the to-be-held member that the driven side rotating body is inclined with respect to the outer ring or the elastic cam member.

  As described above in detail, according to the present invention, even if the driving side rotating shaft and the driven side rotating shaft are in a non-coaxial state, abnormal noise and vibration generated from each connecting portion, and driving force at the connecting portion are reduced. A motor provided with a clutch capable of reducing loss can be provided.

(First embodiment)
Hereinafter, a first embodiment in which the present invention is embodied in a power window device will be described with reference to FIGS.

  As shown in FIG. 7, the motor 1 of the power window device is fixed to the door 2. The motor 1 includes a motor main body 3 serving as a drive source and a speed reduction unit 4 that houses a speed reduction mechanism that decelerates the rotation of the motor main body 3. The forward / reverse rotation of the motor body 3 is transmitted to a gear 5 a fixed to the output shaft 5 of the speed reduction portion 4, and the gear 5 a meshes with a gear portion 6 a provided in a known X arm type regulator 6. Therefore, the regulator 6 opens and closes the window glass 7 based on the forward / reverse rotation of the gear 5a.

  As shown in FIG. 1, the motor body 3 includes a motor yoke housing 11, a plurality of magnets 12, a rotating shaft 13 as a driving side rotating shaft, an armature (armature) 14, a commutator (commutator) 15, and a resin cover 16. And a brush 17.

  The motor yoke housing 11 is formed in a substantially bottomed flat cylindrical shape. Then, two magnets 12 are fixed to the inner peripheral surface so as to face each other. A base end portion of the rotating shaft 13 is rotatably supported on the bottom portion of the motor yoke housing 11 along the central axis. A fitting convex portion 13a (see FIG. 2) having a hexagonal R-surface processed is formed at the tip of the rotating shaft 13. In addition, the fitting convex part 13a by which the hexagon R surface process was carried out is a thing of the shape which cannot be rotated and can be tilted in the state fitted by the recessed part of a hexagonal cross section.

  The armature 14 is fixed to an intermediate portion of the rotating shaft 13 corresponding to the position of the magnet 12. Further, a commutator 15 is fixed to the distal end side of the rotary shaft 13 with respect to the armature 14.

  The resin cover 16 is fixed to the opening of the motor yoke housing 11. The resin cover 16 includes a power supply portion (connector) (not shown) protruding outside the motor yoke housing 11. In addition, a brush 17 connected to the power feeding portion with a wiring (not shown) is disposed inside the motor yoke housing 11 of the resin cover 16. The resin cover 16 is provided with a bearing 18, and the tip end side of the rotary shaft 13 is rotatably supported by the bearing 18.

  Here, the brush 17 is disposed at a position corresponding to the commutator 15 and is in contact with the commutator 15. Accordingly, when a current is supplied from the external power source to the power feeding unit, a current is supplied to the coil conductor wound around the armature 14 via the brush 17 and the commutator 15, and the armature 14, that is, the rotating shaft 13 of the motor body 3. Is driven to rotate.

  The speed reduction unit 4 includes a gear housing 21, first and second bearings 22 a and 22 b, a worm shaft 23 as a driven side rotation shaft, a worm wheel 24, and an output shaft 5. The gear housing 21 is made of resin, and its opening (upper end in FIG. 1) is fixed to the motor yoke housing 11 and the resin cover 16.

  A clutch housing recess 25 is formed on the side of the opening (upper end in FIG. 1) of the gear housing 21. The gear housing 21 is formed with a worm shaft housing portion 26 extending from the bottom of the clutch housing recess 25 along the axial direction of the rotary shaft 13. Further, the gear housing 21 is formed with a wheel housing portion 27 that communicates with the worm shaft housing portion 26 in a direction orthogonal to the axis of the intermediate portion of the worm shaft housing portion 26 (right direction in FIG. 1). A bearing housing recess 28 is formed in the opening of the worm shaft housing 26.

  The first bearing 22 a is a substantially cylindrical slide bearing and is fitted in the recess 28 until it contacts the bottom surface of the bearing housing recess 28. Further, the second bearing 22b is fitted on the bottom side (lower side in FIG. 1) of the worm shaft housing portion 26.

  The worm shaft 23 is formed with a worm 29 at an intermediate portion thereof and is rotatably supported by the first and second bearings 22a and 22b at both ends thereof and accommodated in the worm shaft accommodating portion 26. At the end of the worm shaft 23 on the side of the motor body 3 (upper end in FIG. 1), an engaging recess 23a having a substantially square cross section is formed.

  The worm wheel 24 meshes with the worm 29 and is accommodated in the wheel accommodating portion 27 so as to be rotatable about the axis in the direction orthogonal to the worm shaft 23 (the direction orthogonal to the plane of FIG. 1). The output shaft 5 is coupled to the worm wheel 24 so as to rotate coaxially with the rotation of the worm wheel 24.

The rotary shaft 13 is connected to the worm shaft 23 via a clutch 30.
As shown in FIGS. 2 to 5, the clutch 30 includes an outer ring 31, a driven-side rotator 32, a drive-side rotator 33, a retainer 34, and steel balls as a plurality (three) of nipped members. A (sphere) 35 and a circlip 36 are provided.

The outer ring 31 is formed in a substantially cylindrical shape, and is press-fitted and fixed so as to come into contact with the bottom surface of the clutch housing recess 25 (the lower end surface in FIG. 1).
The driven-side rotator 32 has a disk part 32a, a columnar part 32b that protrudes upward (upward in FIG. 5) from the center part of the disk part 32a, and a substantially rectangular cross section that protrudes downward from the center part of the disk part 32a. And a fitting portion 32c. As shown in FIG. 5, the fitting portion 32 c is fitted into the engagement recess 23 a of the worm shaft 23 and is fixedly connected so as not to rotate. The driven-side rotating body 32 is disposed inside the outer ring 31.

  As shown in FIGS. 2 and 3, the disk portion 32 a has a plurality of (three) engaging grooves 37 formed at equal angular (120 °) intervals by cutting out a predetermined angle range from the outer peripheral side. Further, a control surface 38 is formed in the disk portion 32a by linearly cutting the outer periphery between the adjacent engaging grooves 37. The control surface 38 has a radial interval that changes in the rotational direction with respect to the inner peripheral surface 31 a of the outer ring 31.

  The drive-side rotator 33 includes a cylindrical portion 33a and an annular disc portion 33b extending radially outward from a lower end portion (lower end portion in FIG. 5) of the cylindrical portion 33a. The inner diameter of the lower end portion of the cylindrical portion 33a is set slightly larger than the outer diameter of the cylindrical portion 32b.

  A small-diameter portion 33c having a reduced inner diameter is formed on the upper end side of the cylindrical portion 33a. Further, a fitting recess 33d having a hexagonal section is formed in the upper end portion of the cylindrical portion 33a and is recessed in the axial direction and communicates with the inside of the lower end side of the cylindrical portion 33a through the inside of the small diameter portion 33c. Note that the size of the fitting recess 33d is set to a size that allows the fitting recess 13d to be fitted with the fitting protrusion 13a with almost no gap.

  A plurality (three) of lower engaging projections 39 projecting downward are formed at equiangular (120 °) intervals on the outer peripheral end of the disk portion 33b. The lower engagement protrusion 39 has a circumferential width set to a predetermined length shorter than the circumferential length of the engagement groove 37 (see FIG. 3). Further, a plurality (three) of upper engaging projections 40 projecting upward are formed at equiangular (120 °) intervals near the outer periphery of the disk portion 33b. Note that the lower engagement protrusion 39 and the upper engagement protrusion 40 of the present embodiment are disposed so as to be shifted by 60 °.

  The cylindrical portion 32 b of the driven side rotating body 32 is inserted into the cylindrical portion 33 a of the driving side rotating body 33, and the lower engagement protrusion 39 of the driving side rotating body 33 is engaged with the engaging groove 37 of the driven side rotating body 32. Has been inserted. Here, since the circumferential width of the lower engaging protrusion 39 is shorter than the circumferential length of the engaging groove 37, the driving side rotating body 33 is in a predetermined range with respect to the driven side rotating body 32 (with the protrusion 39. The engagement groove 37 is rotatable in the circumferential direction). Further, as shown in FIG. 5, the lower engagement protrusion 39 has a gap with the radially inner surface of the engagement groove 37 in a state where the central axes of the driven rotation body 32 and the drive rotation body 33 coincide with each other. Is set to Since the inner diameter of the cylindrical portion 33a is set to be slightly larger than the outer diameter of the cylindrical portion 32b, the driving side rotating body 33 can be tilted with respect to the driven side rotating body 32.

  The retainer 34 has a small-diameter cylindrical portion 34a whose inner diameter is substantially equal to the outer diameter of the cylindrical portion 33a, an annular disk portion 34b that extends radially outward from a lower end portion (lower end portion in FIG. 5) of the small-diameter cylindrical portion 34a, A large-diameter cylindrical portion 34c extending downward from the outer edge of the disk portion 34b. The inner diameter of the large-diameter cylindrical portion 34c is set larger than the outer diameters of the disk portion 32a and the disk portion 33b.

  A plurality (three) of engagement holes 41 penetrating in the axial direction are formed in the disk portion 34b at equiangular (120 °) intervals. The engaging hole 41 has a circumferential length set to a predetermined length longer than the circumferential width of the upper engaging protrusion 40 (see FIG. 3).

  A plurality (three) of ball holding holes 42 penetrating in the radial direction are formed in the large-diameter cylindrical portion 34c at equiangular (120 °) intervals. Then, with the steel ball 35 fitted into each ball holding hole 42 from the radial direction, the cylindrical portion 33a is fitted into the small diameter cylindrical portion 34a, and the upper engaging projection 40 is fitted into the engaging hole 41. Has been. Each steel ball 35 is disposed between the inner peripheral surface 31 a of the outer ring 31 and the control surface 38 of the driven side rotating body 32. The circlip 36 is fitted to the upper end side of the cylindrical portion 33a, thereby preventing the small diameter cylindrical portion 34a from coming off. Here, since the length of the engagement hole 41 in the circumferential direction is longer than the width of the upper engagement protrusion 40 in the circumferential direction, the retainer 34 has a predetermined range (engagement hole 41 with respect to the drive-side rotator 33). And the protrusion 40).

  A ball 43 is inserted into the small-diameter portion 33c of the drive-side rotator 33 so as to contact the tip of the columnar portion 32b of the driven-side rotator 32, and the fitting convex portion 13a of the rotary shaft 13 is inserted into the fitting concave portion 33d. It is mated. Since the fitting convex portion 13 a is processed with a hexagonal R surface, the driving side rotating body 33 is not rotatable and tiltable with respect to the rotating shaft 13.

  In the clutch 30, when the drive side rotating body 33 (only the lower and upper engaging protrusions 39 and 40 are shown in FIG. 3) rotates in the direction of arrow A (counterclockwise direction) in FIG. Then, one side surface (counterclockwise surface) of the engagement groove 37 comes into contact with and presses one side surface (counterclockwise surface) of the lower engagement protrusion 39. At this time, one side surface (counterclockwise surface) of the engagement hole 41 is brought into contact with and pressed against one side surface (counterclockwise surface) of the upper engagement protrusion 40. On the other hand, when the drive-side rotator 33 rotates clockwise with the rotation of the rotating shaft 13, the other side surface (clockwise side surface) of the engagement groove 37 is the other side surface (clockwise side) of the lower engagement protrusion 39. The surface) and pressed. At this time, the other side surface (clockwise side surface) of the engagement hole 41 is brought into contact with and pressed against the other side surface (clockwise side surface) of the upper engagement protrusion 40. Therefore, at these times, the driven-side rotator 32 has a predetermined rotation angle with respect to the drive-side rotator 33, and the retainer 34 has a predetermined rotation angle with respect to the drive-side rotator 33. That is, the retainer 34 has a predetermined rotation angle with the driven-side rotator 32, and the steel ball 35 is disposed at a position corresponding to the substantially central portion of the control surface 38. Therefore, the driven side rotating body 32 is not prevented from rotating, and the driven side rotating body 32 rotates together with the drive side rotating body 33.

  On the other hand, when the driven rotary body 32 together with the worm shaft 23 rotates in the direction of arrow A (counterclockwise direction) as shown in FIG. 4, the steel ball 35 moves relative to the end side of the control surface 38. Then, the other side surface (clockwise side surface) of the engagement groove 37 abuts on the other side surface (clockwise side surface) of the lower engagement projection 39 and one side surface (counterclockwise direction) of the upper engagement projection 40. Before the side surface) comes into contact with one side surface (counterclockwise surface) of the engagement hole 41, that is, before the rotation of the driven side rotating body 32 is transmitted to the retainer 34 via the driving side rotating body 33. The steel ball 35 is sandwiched between the control surface 38 and the inner peripheral surface 31a of the outer ring 31 (becomes locked). Conversely, when the driven-side rotator 32 rotates in the clockwise direction, the steel ball 35 moves relative to the end side of the control surface 38 and the rotation of the driven-side rotator 32 causes the drive-side rotator 33 to rotate. The steel ball 35 is sandwiched between the control surface 38 and the inner peripheral surface 31 a of the outer ring 31 before being transmitted to the retainer 34. And since the outer ring | wheel 31 is fixed to the deceleration part 4 (clutch accommodation recessed part 25), the further rotation of the driven side rotary body 32 is blocked | prevented, and the drive side rotary body 33 is not rotated.

  In the motor 1, first, a clutch 30 is assembled to a gear housing 21 in which components such as a worm shaft 23 are assembled, and then a motor yoke housing 11 in which components such as an armature 14 and a resin cover 16 are assembled is used as a gear housing 21. It is assembled and completed. At this time, it is desirable that the rotation center axis of the worm shaft 23 and the rotation shaft 13 of the motor body 3 are assembled (coaxially) so that they coincide. However, when the rotation center axis of the worm shaft 23 does not coincide with that of the rotation shaft 13 due to dimensional errors of these components and the surrounding components related to the components (the rotation center axis of both the rotation shafts 13 and 23 does not match). In some cases, the inclinations do not match, or the connecting portions of the rotary shafts 13 and 23 are displaced in the radial direction.

  In such a case, the driven-side rotator 32 (worm shaft 23) can be tilted with respect to the driving-side rotator 33 without using the bending of the member, and the driving-side rotator 33 is tilted with respect to the rotating shaft 13. Since it is possible (see FIG. 6), a large radial load does not act on each connecting portion, and abnormal noise and vibration generated at the connecting portion and loss of driving force at the connecting portion are suppressed.

  In the motor 1 configured as described above, when the rotary shaft 13 of the motor body 3 is rotationally driven, the rotational force is transmitted to the worm shaft 23 via the clutch 30 and the worm shaft 23 rotates. Then, the worm wheel 24 is slower than the rotation speed of the worm shaft 23 and rotates with high torque. Then, with the rotation of the worm wheel 24, the output shaft 5 rotates, and the rotational force is transmitted to an external load (regulator 6).

  During such driving, if an overload is applied on the output shaft 5 side, the intermediate portion of the worm shaft 23 is perpendicular to the axis due to the rotational force transmitted from the rotary shaft 13 and the overload on the worm wheel 24 side (see FIG. 1 is rotated in a bent state under a large force in the direction indicated by the arrow X. At this time, as shown in FIG. 6, the end of the worm shaft 23 on the driven side rotating body 32 side is inclined and moved in the radial direction together with the rotating body 32, but the driven side rotating body 32 (worm shaft 23) can be tilted with respect to the drive-side rotator 33, and the drive-side rotator 33 can be tilted with respect to the rotating shaft 13, so that a large radial load does not act on each connecting portion, Abnormal noise and vibration generated at the connecting portion, and loss of driving force at the connecting portion are suppressed.

Next, the characteristic effects of the above embodiment will be described below.
(1) The driven-side rotator 32 (worm shaft 23) can be tilted with respect to the drive-side rotator 33, and the drive-side rotator 33 can be tilted with respect to the rotating shaft 13. Accordingly, even if the rotational axes 13 and 23 of the rotary shafts 13 and 23 are not aligned with each other or the connecting portions of the rotary shafts 13 and 23 are displaced in the radial direction (non-coaxial state), the clutch 30 A large radial load does not act on each connecting portion, and abnormal noise and vibration generated at the connecting portion and loss of driving force at the connecting portion are suppressed.

  (2) During driving, an overload is applied on the output shaft 5 side, and the intermediate portion of the worm shaft 23 is deflected by receiving a large force in the direction perpendicular to the axis (in the direction of the arrow X in FIG. 1), and the driven side of the worm shaft 23 As shown in FIG. 6, even if the end of the rotating body 32 tilts together with the rotating body 32 and moves in the radial direction, a large radial load does not act on each connecting portion of the clutch 30, Abnormal noise and vibration generated in the portion, and loss of driving force in the connecting portion are suppressed.

  (3) Since the pinched member disposed between the inner peripheral surface 31 a of the outer ring 31 and the control surface 38 of the driven-side rotating body 32 is a steel ball (sphere) 35, the driven-side rotating body 32 becomes the outer ring 31. The tilting with respect to the steel ball 35 is not restricted.

  (4) The clutch 30 is provided between the rotating shaft 13 of the motor body 3 as a driving source and the worm shaft 23 of the speed reducing unit 4. Thus, since the clutch 30 is provided in a location where torque is small, the strength required for the clutch 30 can be reduced, and the clutch 30 can be downsized.

(Second Embodiment)
A second embodiment in which the present invention is embodied in a power window device will be described below with reference to FIGS. Since the present embodiment has a configuration in which only the clutch 30 of the first embodiment is changed, the same components as those in the first embodiment are denoted by the same reference numerals and detailed description thereof is omitted. Some explanations are omitted.

  As shown in FIG. 8, the rotary shaft 13 is connected to the worm shaft 23 via a clutch 50. As shown in FIGS. 9 to 12, the clutch 50 includes a bearing 51, an elastic cam member 52, a driven side rotating body 53, a driving side rotating body 54, and a plurality (three) of nipped members. Steel balls (spheres) 55 are provided.

The bearing 51 is formed in a substantially cylindrical shape, and is press-fitted and fixed so as to come into contact with the bottom surface (the lower end surface in FIG. 8) of the clutch housing recess 25.
The elastic cam member 52 is made of a metal having elasticity, and has a cylindrical portion 52a having a circular outer periphery and an inner peripheral surface formed on the inner peripheral cam surface 56, and an upper end of the cylindrical portion 52a (the upper end in FIG. 12). And an annular flange portion 52b extending radially outward from the center. As shown in FIGS. 10 and 11, the inner peripheral cam surface 56 is a surface whose distance from the central axis changes in the circumferential direction. In the present embodiment, the innermost cam surface 56 is the farthest valley portion 56a. Are formed at equiangular (120 °) intervals, and the peak portions 56b having the closest distance are formed between the adjacent valley portions 56a. A plurality (three) of first engagement grooves 57 are formed at equiangular (120 °) intervals by cutting out a predetermined angle range from the outer peripheral side of the flange portion 52b. The elastic cam member 52 is rotatable with respect to the bearing 51 in a state in which the cylindrical portion 52a is fitted in the bearing 51 and no radially outward force is applied to the inner peripheral cam surface 56.

  The driven-side rotator 53 has a disk portion 53a, a columnar portion 53b that protrudes upward (upward in FIG. 12) from the center portion of the disk portion 53a, and a substantially square cross section that protrudes downward from the center portion of the disk portion 53a. And a fitting portion 53c. As shown in FIG. 12, the fitting portion 53 c is fitted into the engagement recess 23 a of the worm shaft 23 and is fixedly connected so as not to rotate. The driven-side rotator 53 is located inside the cylindrical portion 52 a of the elastic cam member 52. Be placed.

  As shown in FIGS. 10 and 11, a plurality of (three) second engagement grooves 58 are formed at equiangular (120 °) intervals by notching a predetermined angle range from the outer peripheral side, as shown in FIGS. 10 and 11. Yes. In the disk portion 53a, an arc-shaped ball holding groove 59 is formed on the outer peripheral side between the adjacent second engaging grooves 58 as viewed from the axial direction. Steel balls 55 are accommodated in the respective ball holding grooves 59 except for a part. Specifically, the steel ball 55 is formed to have a diameter slightly smaller than the radial gap when the inner wall surface of the ball holding groove 59 and the valley portion 56a of the inner peripheral cam surface 56 are linearly aligned in the radial direction. The inner wall surface of the holding groove 59 and the peak portion 56b of the inner peripheral cam surface 56 are formed to have a diameter slightly larger than the radial gap when linearly aligned in the radial direction. The steel ball 55 is held so as to be surrounded by the inner wall surface of the ball holding groove 59 and the surface of the valley portion 56a in a state where the ball holding groove 59 is in a position substantially corresponding to the valley portion 56a.

  The drive-side rotator 54 includes a cylindrical portion 54a and an annular disc portion 54b extending radially outward from a lower end portion (lower end portion in FIG. 12) of the cylindrical portion 54a. The inner diameter of the lower end portion of the cylindrical portion 54a is set slightly larger than the outer diameter of the column portion 53b. The outer diameter of the disk portion 54 b is set to be substantially the same as that of the flange portion 52 b of the elastic cam member 52.

  A small diameter portion 54c having a reduced inner diameter is formed on the upper end side of the cylindrical portion 54a. In addition, a fitting recess 54d having a hexagonal cross section is formed in the upper end portion of the cylindrical portion 54a and is recessed in the axial direction and communicates with the inside of the lower end side of the cylindrical portion 54a through the inside of the small diameter portion 54c. The size of the fitting recess 54d is set such that it can be fitted with the fitting protrusion 13a without any substantial gap.

  A plurality (three) of outer engaging projections 60 projecting downward are formed at equiangular (120 °) intervals on the outer peripheral end of the disk portion 54b. The outer engaging protrusion 60 has a circumferential width set to a predetermined length shorter than the circumferential length of the first engaging groove 57 (see FIG. 10). Further, a plurality (three) of inner engagement protrusions 61 projecting downward are formed at equiangular (120 °) intervals near the center of the disk portion 33b. The circumferential width of the inner engagement protrusion 61 is set to a predetermined length shorter than the circumferential length of the second engagement groove 58 (see FIG. 10). Further, a plurality (four) of holding holes 62 penetrating vertically are formed at equiangular (90 °) intervals near the outer periphery of the disk portion 54b. As shown in FIG. 12, each holding hole 62 is provided with a pressing ball 63 that can be projected and lowered downward, and is urged downward by a spring 64.

  The cylindrical portion 53 b of the driven side rotating body 53 is inserted into the cylindrical portion 54 a of the driving side rotating body 54, and the outer engaging protrusion 60 of the driving side rotating body 54 is inserted into the first engaging groove 57 of the elastic cam member 52. Further, the inner engagement protrusion 61 is inserted into the second engagement groove 58 of the driven side rotating body 53.

  Here, since the circumferential width of the outer engagement protrusion 60 is shorter than the circumferential length of the first engagement groove 57, the drive-side rotator 54 has a predetermined range (with respect to the protrusion 60 and the elastic cam member 52). The first engagement groove 57 can be rotated in the circumferential direction). Further, since the circumferential width of the inner engagement protrusion 61 is shorter than the circumferential length of the second engagement groove 58, the drive-side rotating body 54 has a predetermined range (with respect to the protrusion 61 and the driven-side rotating body 53). The second engagement groove 58 can be rotated in the circumferential direction). In addition, as shown in FIG. 12, the outer engagement protrusion 60 is spaced from the radially inner surface of the first engagement groove 57 in a state where the central axes of the driven-side rotator 53 and the drive-side rotator 54 coincide. The inner engagement protrusion 61 is set so as to have a gap with the radially inner surface of the second engagement groove 58 and the inner peripheral cam surface 56. Since the inner diameter of the cylindrical portion 54 a is set slightly larger than the outer diameter of the column portion 53 b, the driving side rotating body 54 can be tilted with respect to the driven side rotating body 53.

  A ball 65 is inserted into the small-diameter portion 54c of the driving side rotating body 54, and the fitting convex portion 13a of the rotating shaft 13 is fitted into the fitting concave portion 54d. Since the fitting convex portion 13a is processed with a hexagonal R surface, the drive-side rotating body 54 cannot rotate with respect to the rotating shaft 13 and can tilt.

  In the clutch 50, when the driving side rotating body 54 (only the outer and inner engaging protrusions 60 and 61 are shown in FIG. 3) rotates in the direction of arrow B (clockwise direction) in FIG. One side surface (clockwise side surface) of the two engagement grooves 58 is in contact with and pressed against one side surface (clockwise side surface) of the inner engagement protrusion 61. At this time, one side surface (clockwise surface) of the first engagement groove 57 contacts and is pressed against one side surface (clockwise side surface) of the outer engagement protrusion 60. On the contrary, when the driving side rotating body 54 rotates counterclockwise with the rotation of the rotating shaft 13, the other side surface (counterclockwise side surface) of the second engagement groove 58 is the other side surface of the inner engagement protrusion 61 ( It is in contact with and pressed against the counterclockwise surface. At this time, the other side surface (counterclockwise surface) of the first engagement groove 57 is brought into contact with and pressed against the other side surface (counterclockwise surface) of the outer engagement protrusion 60. Therefore, at these times, the driven-side rotator 53 has a predetermined rotation angle with respect to the drive-side rotator 54, and the elastic cam member 52 has a predetermined rotation angle with respect to the drive-side rotator 54. . That is, the elastic cam member 52 has a predetermined rotation angle with the driven side rotating body 53, and the steel ball 55 is disposed at a position corresponding to the valley portion 56 a of the inner peripheral cam surface 56. Therefore, the driven side rotating body 53 is not prevented from rotating, and the driven side rotating body 53 rotates together with the drive side rotating body 54.

  On the other hand, when the driven-side rotator 53 rotates together with the worm shaft 23 in the arrow B direction (clockwise direction) as shown in FIG. 11, the steel ball 55 relatively moves toward the peak portion 56 b of the inner peripheral cam surface 56. The other side surface (counterclockwise surface) of the second engagement groove 58 is in contact with the other side surface (counterclockwise surface) of the inner engagement protrusion 61 and one side surface (outer engagement protrusion 60). The elastic cam member 52 is rotated before the rotation of the driven-side rotator 53 via the drive-side rotator 54 before the (clockwise-side surface) contacts one side surface (clockwise-side surface) of the first engagement groove 57. Before being transmitted to the steel ball 55, the steel ball 55 is sandwiched between the inner wall surface of the ball holding groove 59 and the mountain portion 56b of the inner circumferential cam surface 56 (becomes locked). Conversely, when the driven-side rotator 53 rotates in the counterclockwise direction, the steel ball 55 moves in the same manner toward the peak portion 56b of the inner peripheral cam surface 56, and the rotation of the driven-side rotator 53 causes the drive side to rotate. Before being transmitted to the elastic cam member 52 via the rotating body 54, the steel ball 55 is sandwiched between the inner wall surface of the ball holding groove 59 and the peak portion 56 b of the inner peripheral cam surface 56. At this time, the cylindrical portion 52 a of the elastic cam member 52 is bent in the same direction when a radially outward force is applied to the inner peripheral cam surface 56, and is held between the steel ball 55 and the bearing 51. Since the bearing 51 is fixed to the speed reduction unit 4 (clutch housing recess 25), further rotation of the driven-side rotator 53 is prevented, and the drive-side rotator 54 is not rotated.

  In the motor 1, first, the clutch 50 is assembled to the gear housing 21 in which components such as the worm shaft 23 are assembled, and then the motor yoke housing 11 in which components such as the armature 14 and the resin cover 16 are assembled is used as the gear housing 21. It is assembled and completed. At this time, it is desirable that the rotation center axis of the worm shaft 23 and the rotation shaft 13 of the motor body 3 are assembled (coaxially) so that they coincide. However, when the rotation center axis of the worm shaft 23 does not coincide with that of the rotation shaft 13 due to dimensional errors of these components and the surrounding components related to the components (the rotation center axis of both the rotation shafts 13 and 23 does not match). In some cases, the inclinations do not match, or the connecting portions of the rotary shafts 13 and 23 are displaced in the radial direction.

  In such a case, the driven-side rotator 53 (worm shaft 23) can be tilted with respect to the drive-side rotator 54 without using the bending of the member, and the drive-side rotator 54 is tilted with respect to the rotating shaft 13. Since it is possible (refer to FIG. 13), a large radial load does not act on each connecting portion, and abnormal noise and vibration generated at the connecting portion and loss of driving force at the connecting portion are suppressed.

  In the motor 1 configured as described above, when the rotary shaft 13 of the motor body 3 is driven to rotate, the rotational force is transmitted to the worm shaft 23 via the clutch 50, and the worm shaft 23 rotates. Then, the worm wheel 24 is slower than the rotation speed of the worm shaft 23 and rotates with high torque. Then, with the rotation of the worm wheel 24, the output shaft 5 rotates, and the rotational force is transmitted to an external load (regulator 6).

  During such driving, if an overload is applied on the output shaft 5 side, the intermediate portion of the worm shaft 23 is perpendicular to the axis due to the rotational force transmitted from the rotary shaft 13 and the overload on the worm wheel 24 side (see FIG. 8 is rotated in a bent state under a large force in the direction indicated by the arrow Y. At this time, as shown in FIG. 13, the end of the worm shaft 23 on the driven-side rotator 53 side is inclined together with the rotator 53 and moves in the radial direction. 23) can be tilted with respect to the drive-side rotator 54, and the drive-side rotator 54 can be tilted with respect to the rotating shaft 13, so that a large radial load does not act on each connecting portion. Abnormal noise and vibration generated at the connecting portion, and loss of driving force at the connecting portion are suppressed.

Next, the characteristic effects of the above embodiment will be described below.
(1) The driven-side rotating body 53 (worm shaft 23) can be tilted with respect to the driving-side rotating body 54, the driving-side rotating body 54 can be tilted with respect to the rotating shaft 13, and the driving-side rotating body 54 can be It can be tilted with respect to the driven side rotating body 53 (worm shaft 23). Accordingly, even when the rotation center axes of the rotary shafts 13 and 23 are not aligned with each other or the connecting portions of the rotary shafts 13 and 23 are displaced in the radial direction (non-coaxial state), the clutch 50 A large radial load does not act on each connecting portion, and abnormal noise and vibration generated at the connecting portion and loss of driving force at the connecting portion are suppressed.

  (2) During driving, an overload is applied on the output shaft 5 side, and the intermediate portion of the worm shaft 23 is deflected by receiving a large force in the direction perpendicular to the axis (in the direction of the arrow Y in FIG. 8), and the driven side of the worm shaft 23 As shown in FIG. 13, even if the end of the rotating body 53 is tilted together with the rotating body 53 and moves in the radial direction, a large radial load does not act on each connecting portion of the clutch 50, Abnormal noise and vibration generated in the portion, and loss of driving force in the connecting portion are suppressed.

  (3) Since the supported member disposed between the inner peripheral cam surface 56 of the elastic cam member 52 and the inner wall surface of the ball holding groove 59 of the driven side rotating body 53 is a steel ball (sphere) 55, the driven side Inclination of the rotating body 53 with respect to the elastic cam member 52 is not restricted by the steel ball 55.

  (4) The clutch 50 is provided between the rotating shaft 13 of the motor body 3 as a driving source and the worm shaft 23 of the speed reducing unit 4. Thus, since the clutch 50 is provided in a location where the torque is small, the strength required for the clutch 50 can be reduced, and the clutch 50 can be downsized.

  (5) The disk portion 54b of the driving side rotating body 54 is provided with four pressing balls 63 that abut against the flange portion 52b of the elastic cam member 52 and urge the disk portion 54b toward the rotating shaft 13 at equal angular intervals. It has been. Therefore, the drive-side rotator 54 is prevented from freely tilting with respect to the rotating shaft 13 and the driven-side rotator 53. As a result, the generation of abnormal noise and vibration at the connecting portion is suppressed.

The above embodiment may be modified as follows.
In the above embodiments, both members are connected by fitting the fitting convex portion 13a of the rotating shaft 13 into the fitting concave portions 33d and 54d of the drive side rotating bodies 33 and 54. Then, the fitting convex portion 13a may be urged by the urging means to the side surfaces of the fitting concave portions 33d and 54d to connect both members. If it does in this way, shakiness of fitting convex part 13a and fitting concave parts 33d and 54d will be controlled. Therefore, in addition to the effects of the above-described embodiment, the generation of abnormal noise and vibration at the connecting portion between the rotating shaft 13 and the driving side rotating body is suppressed.

  14 (a), (b), and FIG. 15 show portions (the upper ends of the cylindrical portions 33a and 54a) connected to the rotary shaft 13 of the drive-side rotators 33 and 54 of the above embodiments. You may change to A fitting recess 71a having a substantially hexagonal cross section that is recessed in the axial direction is formed at the upper end of the cylindrical portion 71 of the drive-side rotator. The fitting recess 71a does not communicate with the small diameter portion unlike the above embodiments. An opening 71b that opens outward in the radial direction and extends in the axial direction is formed in a part of the side surface of the fitting recess 71a. As shown in FIG. 14B, the opening 71b is formed at a position corresponding to one corner having a substantially hexagonal cross section.

  The cylindrical portion 71 is assembled with a circlip 72, a coil spring 73, and a biasing member 74 that constitute biasing means. The circlip 72 is fitted to the outer periphery below the fitting recess 71 a of the cylindrical portion 71. The coil spring 73 is externally fitted to the cylindrical portion 71 so that the lower end thereof is in contact with the circlip 72.

  The urging member 74 includes a cylindrical portion 74a, an annular extending portion 74b that extends radially outward from the upper end thereof, and a protruding portion 74c that protrudes radially inward from a part of the upper end of the cylindrical portion 74a. The urging member 74 is configured such that the cylindrical portion 74a can move up and down relative to the cylindrical portion 71 so that the lower surface of the extending portion 74b is in contact with the upper end of the coil spring 73 and the protruding portion 74c is fitted into the opening 71b. It is fitted. Therefore, the biasing member 74 is biased upward by the coil spring 73.

  A circlip 75 is fitted to the outer periphery near the upper end of the cylindrical portion 71 to prevent the biasing member 74 from coming off. A V-shaped groove 74d extending in the vertical direction is formed at the tip of the protruding portion 74c. The bottom of the V-shaped groove 74d is inclined so that the distance from the central axis of the cylindrical portion 74a is closer toward the lower side. As shown in FIG. 14 (b), the V-shaped groove 74d forms a substantially hexagonal cross section together with the fitting recess 71a, but protrudes greatly into the fitting recess 71a toward the lower side.

  A ball holding hole 71c is formed in the bottom of the fitting recess 71a, and the ball 76 is accommodated in the hole 71c except for a part thereof. The fitting concave portion 71 a is fitted with the fitting convex portion 13 a of the rotating shaft 13, and the end thereof is in contact with the ball 76.

  Here, one corner of the fitting convex portion 13a is fitted into the V-shaped groove 74d. And, since the V-shaped groove 74d is inclined so as to protrude downward, and the biasing member 74 is biased upward, the fitting convex portion 13a is The biasing member 74 is biased obliquely upward. And the fitting convex part 13a is urged | biased by the side surface of the fitting recessed part 71a by this axial orthogonal direction component, and the rattling of the fitting convex part 13a and the fitting recessed part 71a is suppressed. Therefore, in addition to the effects of the above-described embodiment, the generation of abnormal noise and vibration at the connecting portion between the rotating shaft 13 and the driving side rotating body is suppressed.

  16 (a), (b), and FIG. 17 show the portions (the upper ends of the cylindrical portions 33a and 54a) connected to the rotary shaft 13 of the drive-side rotators 33 and 54 in the above embodiments. You may change to Note that this another example is only partially different from the other examples shown in FIGS. 14A, 14B, and 15, and therefore, the same components are denoted by the same reference numerals, and the description thereof is partially described. Omitted, only different parts will be described in detail. As shown in FIG. 16B, unlike the opening 71b shown in FIG. 14B, the opening 71d of the cylindrical portion 71 is formed at a position corresponding to one plane having a substantially hexagonal cross section. A V-shaped groove 74d shown in FIG. 14B is not formed at the tip of the projecting portion 74c, and the tapered surface 74e is inclined so that the distance from the central axis of the cylindrical portion 74a becomes closer toward the lower side. Is formed.

  One straight line portion of the fitting convex portion 13a comes into contact with the tapered surface 74e. Since the taper surface 74e is inclined so as to protrude downward, and the biasing member 74 is biased upward, the fitting convex portion 13a is attached. The biasing member 74 is biased upward. And the fitting convex part 13a is urged | biased by the side surface of the fitting recessed part 71a by this axial orthogonal direction component, and the rattling of the fitting convex part 13a and the fitting recessed part 71a is suppressed. Therefore, in addition to the effects of the above-described embodiment, the generation of abnormal noise and vibration at the connecting portion between the rotating shaft 13 and the driving side rotating body is suppressed.

  18 (a), (b), and FIG. 19 show a portion (the upper end portion of the cylindrical portions 33a, 54a) connected to the rotary shaft 13 of the drive side rotators 33, 54 of the above embodiments. You may change to A fitting recess 81a having a substantially hexagonal cross section that is recessed in the axial direction is formed at the upper end of the cylindrical portion 81 of the drive-side rotator. The fitting recess 81a does not communicate with the small diameter portion unlike the above embodiments. An opening 81b that opens radially outward is formed in a part of the side surface of the fitting recess 81a. The opening 81b extends from the upper end of the cylindrical portion 81 downward in the axial direction and extends from the lower end in the counterclockwise direction. As shown in FIG. 19, a guide groove 81c twisted in the counterclockwise direction from the upper end to the lower side is formed on the outer peripheral surface of the cylindrical portion 81 opposite to the opening 81b.

  The cylindrical portion 81 is assembled with a circlip 82, a coil spring 83, a biasing member 84, and a ball 85 that constitute biasing means. The circlip 82 is fitted to the outer periphery below the fitting recess 81 a of the cylindrical portion 81. The coil spring 83 is externally fitted to the cylindrical portion 81 so that the lower end thereof is in contact with the circlip 82.

  The urging member 84 includes a cylindrical portion 84a and a protruding portion 84b that protrudes radially inward from a part of the upper end thereof. A holding recess 84c that is recessed radially outward is formed on the inner periphery of the cylindrical portion 84a. The holding recess 84c is formed on the opposite side of the protruding portion 84b. The urging member 84 is configured such that the ball 85 is substantially accommodated in the holding recess 84c, the protruding portion of the ball 85 is fitted into the guide groove 81c, the lower surface of the cylindrical portion 84a is in contact with the upper end of the coil spring 83, and The cylindrical portion 84a is externally fitted to the cylindrical portion 81 so as to be vertically movable so that the protruding portion 84b is fitted to the opening 81b. Therefore, the biasing member 84 is biased upward by the coil spring 83. The cylindrical portion 81 rotates clockwise when the ball 85 is guided by the guide groove 81c.

  A circlip 86 is fitted to the outer periphery near the upper end of the cylindrical portion 81 to prevent the biasing member 84 from coming off. A V-shaped groove 84d extending in the vertical direction is formed at the tip of the protruding portion 84b. As shown in FIG. 18B, the V-shaped groove 84d forms a substantially hexagonal cross section together with the fitting recess 81a. However, the position of the V-shaped groove 84d in the clockwise direction as the urging member 84 moves upward. Rotate.

  A ball holding hole 81d is formed at the bottom of the fitting recess 81a, and the ball 87 is accommodated in the hole 81d except for a part thereof. The fitting concave portion 81 a is fitted with the fitting convex portion 13 a of the rotating shaft 13, and its end is in contact with the ball 87.

  Here, one corner of the fitting protrusion 13a is fitted into the V-shaped groove 84d. Since the V-shaped groove 84d rotates in the clockwise direction with the upward movement of the biasing member 84 and the biasing member 84 is biased upward, the fitting convex portion 13a is fitted. The urging member 84 urges the recess 81a in the clockwise direction. Therefore, the fitting convex part 13a is urged | biased by the side surface of the fitting recessed part 81a, and the rattling of the fitting convex part 13a and the fitting recessed part 81a is suppressed. Therefore, in addition to the effects of the above-described embodiment, the generation of abnormal noise and vibration at the connecting portion between the rotating shaft 13 and the driving side rotating body is suppressed.

  20 (a), (b), and FIG. 21 show portions (upper end portions of the cylindrical portions 33a and 54a) connected to the rotary shaft 13 of the drive-side rotators 33 and 54 in the above embodiments. You may change to A fitting recess 91a having a substantially hexagonal cross section that is recessed in the axial direction is formed at the upper end of the cylindrical portion 91 of the drive-side rotator. Note that the fitting recess 91a does not communicate with the small diameter portion unlike the above embodiments. An opening 91b that opens radially outward and extends in the axial direction is formed in a part of the side surface of the fitting recess 91a. The opening 91b is formed at a position corresponding to one corner having a substantially hexagonal cross section. An accommodation recess 91c extending from the fitting recess 91a to the lower side is provided on the lower side of the opening 91b of the cylindrical portion 91 from the outer peripheral side. A through hole 91d that penetrates to the opposite side of the cylindrical portion 91 is formed below the accommodation recess 91c. A stepped portion 91e having an enlarged diameter is formed on the terminal side of the through hole 91d (the left side in FIG. 20A).

  A leaf spring 92 that constitutes an urging means is fixed to the cylindrical portion 91. More specifically, as shown in FIG. 20A, a bent portion 92a bent in a cross-sectional shape is formed on the upper portion of the leaf spring 92. The lower part of the leaf spring 92 is housed and fixed in the housing recess 91c by a rivet 93 that penetrates the through hole 91d and is caulked by the stepped portion 91e. And the bending part 92a of the leaf | plate spring 92 protrudes in the said fitting recessed part 91a inside the top part. A fitting hole 92b that penetrates in the thickness direction of the leaf spring 92 is formed at the center in the width direction of the top of the bent portion 92a. The fitting hole 92b is formed in the fitting recess 91a as shown in FIG. The width becomes wider toward the inner side.

  A ball holding hole 91f is formed at the bottom of the fitting recess 91a, and the ball 94 is accommodated in the hole 91f except for a part thereof. The fitting concave portion 91 a is fitted with the fitting convex portion 13 a of the rotating shaft 13, and its end is in contact with the ball 94.

  Here, the top of the bent portion 92a is disposed above the central portion in the axial direction of the fitting convex portion 13a. One corner of the fitting convex portion 13a is fitted into the fitting hole 92b. And this fitting convex part 13a is urged | biased by the bending part 92a of the leaf | plate spring 92 in an axis orthogonal direction. Therefore, the fitting convex part 13a is urged | biased by the side surface of the fitting recessed part 91a, and the rattling of the fitting convex part 13a and the fitting recessed part 91a is suppressed. Therefore, in addition to the effects of the above-described embodiment, the generation of abnormal noise and vibration at the connecting portion between the rotating shaft 13 and the driving side rotating body is suppressed. In addition, since the top of the bent portion 92a is disposed above the central portion in the axial direction of the fitting convex portion 13a, the fitting convex portion 13a is difficult to come off from the fitting concave portion 91a.

  The upper end portions (fitting recesses 33d and 54d) of the cylindrical portions 33a and 54a of the drive-side rotators 33 and 54 of the above embodiments and the rotation shaft 13 (fitting protrusions 13a) are shown in FIG. , (B) may be changed as shown in FIG. A fitting recess 101a that is recessed in the axial direction is formed at the upper end of the cylindrical portion 101 of the drive-side rotator. The fitting recess 101a does not communicate with the small diameter portion unlike the above embodiments. The fitting recess 101a has a key groove 101b extending radially outward at a predetermined angle (120 °) interval. On the upper end side of the cylindrical portion 101, a pair of through holes 101c extending in the radial direction of the cylindrical portion 101 from the fitting recess 101a to the outer periphery of the cylindrical portion 101 are formed. As shown in FIG. 22B, the pair of through holes 101c communicate with one key groove 101b from both circumferential wall surfaces of the key groove 101b. A ball holding hole 101d is formed at the bottom of the fitting recess 101a, and the ball 102 is accommodated in the hole 101d except for a part thereof.

  The cylindrical portion 101 is assembled with a circlip 103, a coil spring 104, a cylindrical member 105, and a pair of balls 106 constituting urging means. The circlip 103 is fitted to the outer periphery below the fitting recess 101a of the cylindrical portion 101. The coil spring 104 is externally fitted to the cylindrical portion 101 so that the lower end thereof is in contact with the circlip 103. A tapered portion 105 a that increases in diameter toward the upper end is formed on the inner periphery of the upper end of the cylindrical member 105. The cylindrical member 105 is externally fitted to the cylindrical portion 101 so that its lower surface is in contact with the upper end of the coil spring 104 and can be moved up and down. A circlip 107 is fitted to the outer periphery near the upper end of the cylindrical portion 101 to prevent the cylindrical member 105 from coming off. In this state, the coil spring 104 is compressed, and the cylindrical member 105 is urged upward by the coil spring 104.

  The rotating shaft 108 has a fitting convex portion 108a at the tip. The fitting convex portion 108a has a key 108b extending radially outward at a predetermined angle (120 °) interval. The fitting convex portion 108 a is fitted into the fitting concave portion 101 a, and its end is in contact with the ball 102. Here, the fitting convex portion 108a is set to have a backlash with the fitting concave portion 101a. Therefore, the rotating shaft 108 can be tilted with respect to the driving side rotating body (cylindrical portion 101).

  Balls 106 are accommodated in the pair of through holes 101c, respectively. The pair of balls 106 are in contact with the tapered portion 105 a of the cylindrical member 105. Here, since the cylindrical member 105 is urged upward, the balls 106 are respectively urged radially inward. The pair of balls 106 are in contact with the key 108b so as to sandwich the key 108b of the fitting convex portion 108a and press radially inward. Therefore, the fitting convex portion 108a is biased to the side surface of the fitting concave portion 101a, and rattling between the fitting convex portion 108a and the fitting concave portion 101a is suppressed. Therefore, in addition to the effect similar to the effect of the said embodiment, generation | occurrence | production of the noise and vibration in the connection part of the rotating shaft 108 and a drive side rotary body are suppressed.

  In each of the above embodiments, the rotary shafts 13 and 108 can be tilted with respect to the drive side rotary bodies 33 and 54, and the drive side rotary bodies 33 and 54 are driven side rotary bodies 32 and 53 (worm shaft 23). However, it may be set so that a member connected only to one of the connecting portions can be tilted. Even in this case, when the connecting portions of the rotary shafts 13 and 108 and the worm shaft 23 coincide with each other in the radial direction, and the inclinations of the rotation center axes of the rotary shafts 13 and 108 and the worm shaft 23 do not match, the clutch A large load in the radial direction does not act on each of the connecting portions, and abnormal noise and vibration generated at the connecting portions and loss of driving force at the connecting portions are suppressed. Further, the rotary shafts 13 and 108 and the drive side rotary bodies 33 and 54 cannot be tilted, and the drive side rotary bodies 33 and 54 and the driven side rotary bodies 32 and 53 cannot be tilted. , 53 can be tilted with respect to the worm shaft 23, the same effect can be obtained. In this case, the connecting portion between the driven side rotating bodies 32 and 53 and the worm shaft 23 needs to have the same configuration as the connecting portion between the rotating shafts 13 and 108 and the driving side rotating bodies 33 and 54 described above. .

  A connecting portion between the rotating shafts 13 and 108 and the driving side rotating bodies 33 and 54, a connecting portion between the driving side rotating bodies 33 and 54 and the driven side rotating bodies 32 and 53, and a driven side rotating bodies 32 and 53 and the worm shaft. As long as the members connected to at least two of the connecting portions to 23 are set to be tiltable, any combination may be used. Even in this case, the inclinations of the rotation center axes of the rotary shafts 13 and 108 and the worm shaft 23 do not coincide with each other, and the connecting portions of the rotary shafts 13 and 108 and the worm shaft 23 are displaced in the radial direction. In addition, a large radial load does not act on each coupling portion of the clutch, and abnormal noise and vibration generated at the coupling portion and loss of driving force at the coupling portion are suppressed.

  In each of the above embodiments, the held members are steel balls (spheres) 35 and 55, but may be changed to other held members as long as the surface to be held is a spherical surface. Even if it does in this way, it will not be controlled by the pinched member that the driven side rotation bodies 32 and 53 incline with respect to the outer ring | wheel 31 (elastic cam member 52).

  In each of the above embodiments, the fitting concave portions 33d and 54d are formed on the driving side rotating bodies 33 and 54, and the fitting convex portion 13a is formed on the rotating shaft 13, but conversely the driving side rotating bodies 33 and 54 A fitting convex part may be formed and a fitting concave part may be formed in the rotating shaft 13.

  In each of the above embodiments, the fitting recesses 33d and 54d are hexagonal in cross section, and the fitting projection 13a is hexagonal R-face processed. Then, the number of both corners may be changed as appropriate. For example, the fitting concave portions 33d and 54d may be octagonal in cross section, and the fitting convex portion 13a may be processed into an octagonal R surface.

  In each of the above embodiments, the clutches 30 and 50 are provided between the rotary shafts 13 and 108 and the worm shaft 23. However, the clutches 30 and 50 may be provided at other positions. For example, the output shaft 5 may be divided into two and a clutch may be provided between the shafts.

In the above embodiments, the clutches 30 and 50 provided in the motor 1 are used. However, clutches used in other devices may be used.
Technical ideas other than those described in the claims that can be grasped from the above embodiment will be described below together with the effects thereof.

  The portion that allows the relative inclination between the members is a connecting portion between the driving side rotating body and the driven side rotating body. In this way, even if the connecting portions of the drive-side rotating shaft and the driven-side rotating shaft coincide with each other in the radial direction and the inclinations of the rotation center axes of the both rotating shafts do not coincide with each other, A large load does not act, and noise and vibration generated from each connecting portion, and loss of driving force at the connecting portion are reduced.

  The portion that allows the relative inclination between the members to be set is a connection portion between the driving side rotating body and the driving side rotating shaft. In this way, even if the connecting portions of the drive-side rotating shaft and the driven-side rotating shaft coincide with each other in the radial direction and the inclinations of the rotation center axes of the both rotating shafts do not coincide with each other, A large load does not act, and noise and vibration generated from each connecting portion and loss of driving force at the connecting portion are reduced.

  The portion that allows the relative inclination between the members is a connecting portion between the driven side rotating body and the driven side rotating shaft. In this way, even if the connecting portions of the drive-side rotating shaft and the driven-side rotating shaft coincide with each other in the radial direction and the inclinations of the rotation center axes of the both rotating shafts do not coincide with each other, A large load does not act, and noise and vibration generated from each connecting portion and loss of driving force at the connecting portion are reduced.

  The portion that allows the relative inclination between the members to be set includes a connecting portion between the driving side rotating body and the driven side rotating body, a connecting portion between the driving side rotating body and the driving side rotating shaft, and These are at least two of the connecting portions of the driven side rotating body and the driven side rotating shaft. In this way, even if the inclinations of the rotation center axis lines of the driving side rotating shaft and the driven side rotating shaft are different and the connecting portions of both rotating shafts are displaced in the radial direction, each connecting portion has a large radial direction. The load does not act, and the noise and vibration generated from each connecting portion and the loss of driving force at the connecting portion are reduced.

  -The to-be-held member has a spherical surface, and the spherical surface is held and held. In this case, the surface with which the sandwiched body comes into contact is a spherical surface, and therefore the tilting of the driven side rotating body with respect to the outer ring or the elastic body is not restricted by the sandwiched body.

  The driving-side rotating body and the driving-side rotating shaft each include a fitting recess having a key groove extending radially outward on one of them, and having a key extending radially outward on the other, the fitting The fitting convex part fitted to a recessed part was provided, and the said fitting convex part was formed so that it might have the said fitting recessed part and backlash. If it does in this way, it will become possible for a drive side rotary body and a drive side rotating shaft to incline.

The urging means is a leaf spring and acts so that the fitting convex portion does not come out of the fitting concave portion. If it does in this way, it will become difficult to remove a fitting convex part from a fitting concave part.
The portion that allows the relative inclination between the members is allowed to be in a non-coaxial state without using the bending of the members. In this way, a large radial load does not act on the connecting portion, and noise and vibration generated from the connecting portion and loss of driving force at the connecting portion are reduced.

FIG. 3 is a cross-sectional view of a main part of the motor according to the first embodiment. The disassembled perspective view of the clutch of 1st Embodiment. Explanatory drawing for demonstrating the clutch of 1st Embodiment. Explanatory drawing for demonstrating the clutch of 1st Embodiment. Explanatory drawing for demonstrating the clutch of 1st Embodiment. Explanatory drawing for demonstrating the clutch of 1st Embodiment. The model explanatory drawing for demonstrating a power window apparatus. Sectional drawing of the principal part of the motor of 2nd Embodiment. The disassembled perspective view of the clutch of 2nd Embodiment. Explanatory drawing for demonstrating the clutch of 2nd Embodiment. Explanatory drawing for demonstrating the clutch of 2nd Embodiment. Explanatory drawing for demonstrating the clutch of 2nd Embodiment. Explanatory drawing for demonstrating the clutch of 2nd Embodiment. (A) Explanatory drawing for demonstrating the clutch of another example. (B) CC sectional drawing of (a). The principal part disassembled perspective view of the clutch of another example. (A) Explanatory drawing for demonstrating the clutch of another example. (B) DD sectional drawing of (a). The principal part disassembled perspective view of the clutch of another example. (A) Explanatory drawing for demonstrating the clutch of another example. (B) EE sectional drawing of (a). The principal part disassembled perspective view of the clutch of another example. (A) Explanatory drawing for demonstrating the clutch of another example. (B) FF sectional drawing of (a). The principal part disassembled perspective view of the clutch of another example. (A) Explanatory drawing for demonstrating the clutch of another example. (B) GG sectional drawing of (a). The principal part disassembled perspective view of the clutch of another example.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 3 ... Motor main body, 4 ... Deceleration part, 13, 108 ... Rotary shaft, 23 ... Worm shaft, 24 ... Worm wheel, 31 ... Outer ring, 32, 53 ... Driven side rotary body, 33, 54 ... Drive side rotary body, 35 , 55 ... Steel balls, 38 ... Control surface, 51 ... Bearing, 52 ... Elastic cam member, 56 ... Inner peripheral cam surface, 72, 82 ... Circlip, 73, 83 ... Coil spring, 74, 84 ... Biasing member, 85 ... ball, 92 ... leaf spring.

Claims (4)

The rotating shaft (13) in a motor comprising a motor body (3) having a rotating shaft (13) and a speed reducing portion (4) having a worm shaft (23) arranged coaxially with the rotating shaft (13). And a drive-side rotating body (33) provided between the worm shaft (23) and connected to the rotating shaft (13) so as to be integrally rotatable, and a follower connected to the worm shaft (23) so as to be integrally rotatable. The side rotating bodies (32) are engaged or disengaged with each other in the rotational direction, thereby transmitting rotation from the rotating shaft (13) to the worm shaft (23) and rotating from the worm shaft (23). In a motor with a clutch coupled to prevent rotation transmission to the shaft (13),
The driven-side rotator (32) is rotatably disposed inside the outer ring (31),
On the radially outer side of the driven-side rotator (32), a control surface (38) is formed in which the distance from the inner peripheral surface (31a) of the outer ring (31) changes in the rotational direction,
A sandwiched body (35) is disposed between the control surface (38) and the inner peripheral surface (31a) of the outer ring (31),
During the rotation of the driven side rotating body (32), the pinched body (35) is sandwiched between the control surface (38) and the inner peripheral surface (38) of the outer ring (31), whereby the worm shaft ( 23) to prevent rotation transmission from the rotating shaft (13),
At the time of rotation of the driving side rotating body (33), the clamped body (35) is arranged at a position where it is not pinched and the rotation is transmitted from the rotating shaft (13) to the worm shaft (23). And
A connecting portion of the driving side rotating body (33) and the driven side rotating body (32) and the driving side rotation so as to allow a non-coaxial state of the rotating shaft (13) and the worm shaft (23). A motor characterized in that a relative inclination between members of at least one portion of a connecting portion between the body (33) and the rotating shaft (13) is set to be possible. The motor according to claim 1,
The portion for setting the relative inclination between the members is a connecting portion between the driving side rotating body (33) and the driven side rotating body (32),
By urging the fitting convex part (13a) of the rotating shaft (13) to the side surface of the fitting concave part (33d) of the driving side rotating body (33) by the urging means, the rotating shaft (13). And a drive-side rotator (33) connected to each other. In the motor according to claim 1 or 2,
The speed reduction part (4) includes a gear housing (21), the gear housing (21) is formed with a clutch housing recess (25), and the outer ring (31) is formed in the clutch housing recess (25). A motor characterized by being fixed. In the motor according to any one of claims 1 to 3,
The said pinched body (35) is a sphere, The motor characterized by the above-mentioned.

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