JP2010230153A - Clutch mechanism and motor with reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch mechanism and a motor with reduction gear, preventing rotation of a rotational shaft of an electric motor caused by an external force, without degrading output efficiency of the electric motor. <P>SOLUTION: A worm wheel 22, a drive plate 41, a clutch plate 42, a coil spring 43, and a casing 13 housing them are provided. Clutch engagement parts 55 engaged with each other are respectively disposed to the clutch plate 42 and the casing 13. The clutch plate 42 comes close to the worm wheel 22 to prevent the rotation of the drive plate 41, when the drive plate 41 is rotated before the worm wheel 22 is rotated. The clutch plate 42 is separated from the worm wheel 22 to rotate the drive plate 41 together with the worm wheel 22, when the worm wheel 22 is rotated before the drive plate 41 is rotated. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a clutch mechanism mounted on a vehicle or the like, and a motor with a speed reducer using the clutch mechanism.

  As a motor with a reduction gear mounted on a vehicle, for example, there is one used for a power window device of an automobile. In this type of motor with a speed reducer, a worm speed reducer and an electric motor are connected. The worm speed reducer includes a worm shaft coupled to the rotating shaft of the electric motor and a worm wheel meshed with the worm shaft. By connecting this worm wheel to the output shaft of the power window device, the window glass can be opened and closed.

  By the way, there is a case where a rotational force due to an external force such as the weight of the window glass or a vibration during traveling of the vehicle acts on the rotating shaft of the electric motor, and the window glass opens. Therefore, in order to maintain the stop position of the window glass, end spacers are provided at one end of the rotating shaft and one end of the worm shaft, and the rotating shaft with respect to the end spacer and the rotating resistance of the rotating shaft by external force are caused by the sliding resistance of the worm shaft. A technique for preventing this is disclosed (for example, see Patent Document 1).

JP 2007-232153 A

  However, in the above-described conventional technology, sliding resistance is generated on the rotating shaft with respect to the end spacer, which is excellent in preventing rotation of the rotating shaft due to external force, but the rotating shaft is rotated by an electric motor. In the case of trying to do so, sliding resistance is similarly generated. For this reason, there exists a subject that the output efficiency of an electric motor falls.

  Accordingly, the present invention has been made in view of the above-described circumstances, and a clutch mechanism that can prevent the rotation of the rotating shaft of the electric motor due to an external force and a deceleration without reducing the output efficiency of the electric motor A motor with a machine is provided.

In order to solve the above-mentioned problems, the invention described in claim 1 includes a drive rotator to which rotation of an electric motor is input, and a driven rotation that engages with the drive rotator and outputs the rotation of the electric motor. And the drive rotator and the driven rotator are provided so as to be close to and away from the drive rotator along the axial direction, and the drive rotator and the driven A clutch plate that can be engaged with the rotating body, an elastic member that is disposed between the driven rotating body and the clutch plate, and biases the clutch plate toward the driving rotating body, and the driving rotating body and the driven body A rotating body, a clutch plate, and a casing that accommodates an elastic member, and the clutch plate is close to the driving rotating body in the clutch plate and the casing. And when the driven rotating body rotates before the driving rotating body, the clutch plate is close to the driving rotating body, and the driving rotating body rotates. The clutch plate is separated from the drive rotator when the drive rotator rotates before the driven rotator, and the driven rotator rotates together with the drive rotator. It is characterized by being.
With this configuration, when the driven rotator on the output side tries to rotate before the drive rotator on the input side, the clutch plate and the casing are engaged with each other, and rotational force is applied to the drive rotator. It can be prevented from being transmitted. For this reason, rotation by the external force of a rotating shaft can be prevented and the fall of the output efficiency of an electric motor can be prevented, without providing sliding resistance to a rotating shaft like the past.
Moreover, since the elastic member can suppress the flutter of the clutch plate, the noise of the clutch mechanism can be reduced.

According to a second aspect of the present invention, a plurality of first convex portions are provided on either one of the opposing surfaces of the drive rotator and the driven rotator, and on the other side, the plurality of first convex portions and the periphery are provided. A plurality of first engaging portions capable of contacting in a direction are provided, and a plurality of second convex portions are provided on either one of the opposed surfaces of the drive rotating body and the clutch plate, and the plurality of second convex portions are provided on the other side. When a second engaging portion that can contact the second convex portion in the circumferential direction is provided, a plurality of through holes through which the first convex portion can be penetrated is formed in the clutch plate, and when the driving rotating body rotates, The second engaging portion and the second convex portion abut each other before the first engaging portion abuts on the first convex portion, and the second convex portion is caused by the second engaging portion. It is configured to be pushed up to the driven rotor side.
In this case, as in the invention described in claim 3, a plurality of first protrusions are provided on the surface of the driven rotor on the side of the drive rotor, and the plurality of through holes are formed in the clutch plate. While providing a plurality of second convex portions on the surface of the drive rotator, the plurality of first engagement portions are provided on a surface of the drive rotator on the side of the driven rotator, and the plurality of second engagement portions. May be provided.
With this configuration, it is possible to prevent the driven rotor from rotating due to an external force with a simple structure, and it is possible to easily transmit the rotational force generated by the electric motor to the driven rotor. For this reason, a clutch mechanism with reduced manufacturing costs can be provided.

According to a fourth aspect of the present invention, the first engagement portion and the second engagement portion are formed in a concave shape having a substantially U-shaped cross section, and the side wall of the second engagement portion An inclined wall portion is formed at the joint portion with the bottom wall so that the depth of the second engaging portion gradually becomes shallower toward the outer side in the circumferential direction, and an angle of the second convex portion is formed on the inclined wall portion. The second convex portion is configured to be pushed up toward the driven rotating body when the portion abuts.
With such a configuration, the structure of the clutch mechanism can be further simplified, so that the manufacturing cost can be further reduced.

According to a fifth aspect of the invention, the casing is provided with a support for rotatably supporting the drive rotator, and an insertion hole through which the support can be inserted is formed in the drive rotator. The clutch engagement portion is provided on each of the end surface on the clutch plate side and the portion of the clutch plate on the drive rotor side corresponding to the support column.
In this case, as in the invention described in claim 6, the clutch engaging portions may be provided on the inner peripheral surface of the casing and the outer peripheral edge of the clutch plate, respectively.
With this configuration, the clutch engagement portion can be provided in a simple structure and in a space-saving manner, so that the clutch mechanism can be downsized.

According to a seventh aspect of the present invention, the drive rotating body of the clutch mechanism according to any one of the first to sixth aspects is a worm wheel, the worm shaft meshing with the worm wheel, and the electric motor on the worm shaft. It was set as the motor with a reduction gear characterized by having connected.
By comprising in this way, the motor with a reduction gear which can prevent rotation of the rotating shaft of the electric motor by external force, without reducing the output efficiency of an electric motor can be provided.

The invention described in claim 8 is a clutch mechanism for connecting a rotating shaft of an electric motor provided with a brush holder and a speed reduction mechanism, a driving rotating body connected to the rotating shaft, and the driving rotating body, A driven rotor that engages and transmits the rotational force of the rotating shaft to the speed reduction mechanism; and is disposed between the drive rotor and the driven rotor, and is axially disposed with respect to the drive rotor. The drive rotator and the clutch plate that can be engaged with the driven rotator, and disposed between the driven rotator and the clutch plate. An elastic member that urges toward the drive rotator, the brush holder is provided with a storage portion that can store the drive rotator, and the periphery of the storage portion and the outer peripheral side of the clutch plate, A clutch engaging portion that is engageable with each other in a state in which the latch plate is close to the drive rotator is provided, and when the driven rotator rotates before the drive rotator, the clutch plate rotates the drive rotation. When the drive rotator is rotated before the driven rotator, the clutch plate is separated from the drive rotator, and the driven rotator is separated from the driven rotator. Is configured to rotate together with the driving rotating body.
By comprising in this way, the rotation by the external force of the rotating shaft of an electric motor can be prevented in the location closer to an electric motor than a speed reduction mechanism. For this reason, complication of the speed reduction mechanism can be prevented. Moreover, it becomes easy to transmit the rotational force of a rotating shaft to the speed reduction mechanism side, and it becomes possible to improve the output efficiency of an electric motor.

According to a ninth aspect of the present invention, a plurality of first convex portions are provided on the surface of the driven rotator on the side of the driving rotator, and a plurality of through holes that can penetrate the first convex portion are formed in the clutch plate. While providing a plurality of second protrusions on the surface of the drive rotator, the drive rotator is provided with a plurality of second engagement portions that can contact the second protrusions in the circumferential direction, When each of the second engaging portions is set to a first engaging portion that can contact with the first convex portion in the circumferential direction, and the drive rotating body rotates, the first engaging portion is The second engaging portion and the second convex portion are in contact with each other before contacting the one convex portion, and the second convex portion is pushed up to the driven rotor side by the second engaging portion. It is configured.
With this configuration, the structure of the clutch mechanism can be simplified while preventing the speed reduction mechanism from becoming complicated, and thus the manufacturing cost can be reduced.

According to a tenth aspect of the present invention, the second engagement portion is formed in a concave shape having a substantially U-shaped cross section, and the joint portion between the side wall and the bottom wall of the second engagement portion The inclined wall portion is formed so that the depth of the second engaging portion gradually decreases toward the outer side in the circumferential direction, and the corner portion of the second convex portion abuts on the inclined wall portion, thereby The second convex portion is configured to be pushed up to the driven rotating body side.
With such a configuration, the structure of the clutch mechanism can be further simplified, so that the manufacturing cost can be further reduced.

The invention described in claim 11 is a motor with a reduction gear comprising the clutch mechanism according to any one of claims 8 to 10, the electric motor coupled to the clutch mechanism by the clutch mechanism, and a reduction mechanism. The speed reduction mechanism includes a worm shaft and a worm wheel that meshes with the worm shaft, and the worm shaft and the driven rotating body are connected so as not to be relatively rotatable.
By comprising in this way, the motor with a reduction gear which can prevent rotation of the rotating shaft of the electric motor by external force, without reducing the output efficiency of an electric motor can be provided.

According to the present invention, when the driven rotator on the output side tries to rotate before the drive rotator on the input side, the clutch plate and the casing are engaged with each other, and the rotational force is transmitted to the drive rotator. Can be prevented. For this reason, rotation by the external force of a rotating shaft can be prevented and the fall of the output efficiency of an electric motor can be prevented, without providing sliding resistance to a rotating shaft like the past.
Moreover, since the elastic member can suppress the flutter of the clutch plate, the noise of the clutch mechanism can be reduced.
Further, the rotation of the driven rotator due to an external force can be prevented with a simple structure, and the rotational force generated by the electric motor can be easily transmitted to the driven rotator. For this reason, a clutch mechanism with reduced manufacturing costs can be provided.
And since a clutch engaging part can be provided in a simple structure and space-saving, size reduction of a clutch mechanism can be achieved.

It is a perspective view of the motor with a reduction gear in 1st embodiment of this invention. It is sectional drawing which follows the XX line of FIG. It is a disassembled perspective view of the clutch mechanism 4 in 1st embodiment of this invention. The drive plate in 1st embodiment of this invention is shown, (a) is the perspective view seen from the opposite side to a worm wheel, (b) is the perspective view seen from the worm wheel side. The clutch plate in 1st embodiment of this invention is shown, (a) is the perspective view seen from the drive plate side, (b) is the perspective view seen from the worm wheel side. The positional relationship of each part of the clutch mechanism in 1st embodiment of this invention is shown, (a) is a detailed drawing of the A section of FIG. 2, (b) is a detailed drawing of the B section of FIG. 2, (c) is FIG. FIG. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. The behavior of each part of the clutch mechanism in the first embodiment of the present invention is shown, (a) is an explanatory view of part A of FIG. 2, (b) is an explanatory view of part B of FIG. 2, (c) is an explanatory view of FIG. It is explanatory drawing of the C section. It is a disassembled perspective view of the clutch mechanism in 2nd embodiment of this invention. The clutch plate in 2nd embodiment of this invention is shown, (a) is the perspective view seen from the drive plate side, (b) is the perspective view seen from the worm wheel side. It is a perspective view of a clutch mechanism in a third embodiment of the present invention. It is sectional drawing which follows the YY line of FIG. It is a disassembled perspective view of the clutch mechanism in 3rd embodiment of this invention. The brush holder part in 3rd embodiment of this invention is shown, (a) is the perspective view seen from the armature core side, (b) is the perspective view seen from the worm shaft side. The joint motor in 3rd embodiment of this invention is shown, (a) is the perspective view seen from the armature core side, (b) is the perspective view seen from the worm shaft side. The joint frame in 3rd embodiment of this invention is shown, (a) is the perspective view seen from the joint motor side, (b) is the perspective view seen from the worm shaft side. The clutch plate in 3rd embodiment of this invention is shown, (a) is the perspective view seen from the joint motor side, (b) is the development view of the armature which is the perspective view seen from the joint frame side.

(First embodiment)
(Motor with reduction gear)
Next, a first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a perspective view of a motor 1 with a speed reducer. As shown in the figure, a motor 1 with a speed reducer is used for, for example, a power window device of a vehicle, and includes a worm speed reducer 2 and an electric motor 3 detachably provided thereto. The clutch mechanism 4 is built in the worm speed reducer 2.
For example, a DC motor with a brush is used as the electric motor 3, and a bottomed cylindrical yoke 5 in which a plurality of permanent magnets (not shown) are disposed, and a rotatable inside the yoke 5. The armature 6 provided is provided.

The yoke 5 is formed in a bottomed cylindrical shape, and is attached so that the opening side faces the worm speed reducer 2 side.
The armature 6 includes a rotating shaft 7 that is rotatably supported by the yoke 5, an armature core 8 that is fitted and fixed to the bottom surface of the yoke 5 of the rotating shaft 7, and an outer fitting on the yoke 5 opening side of the rotating shaft 7. And a commutator 9 which is fixed. The armature core 8 is formed with a plurality of slots (not shown) for winding windings.

(Worm reducer)
2 is a cross-sectional view taken along line XX of FIG.
As shown in FIGS. 1 and 2, the worm speed reducer 2 includes a brush holder portion 10 that receives the commutator 9 of the electric motor 3, a worm gear 11, and a gear housing portion 12 that houses the clutch mechanism 4. A resin casing 13 is provided.
The brush holder portion 10 is formed in a box shape having an opening on the electric motor 3 side, and comes into sliding contact with the commutator 9 to store a brush (not shown) for supplying electric power. Yes. The yoke 5 of the electric motor 3 is attached so as to close the opening of the brush holder portion 10.

  A connector 14 that can be connected to an external power source (not shown) is provided on the peripheral wall 10 a of the brush holder portion 10. The power supply terminal 15 of the connector 14 is electrically connected to a brush (not shown) housed in the brush holder portion 10, whereby the power of the external power supply can be supplied to the armature 6 of the electric motor 3. ing.

  The gear housing portion 12 of the casing 13 houses the worm shaft housing portion 16 that houses the worm shaft 21 that constitutes one of the worm gears 11, the worm wheel 22 that constitutes the other of the worm gear 11, and the clutch mechanism 4. The clutch housing portion 17 is integrally formed. The worm shaft storage portion 16 is formed in a bottomed cylindrical shape, and is provided with the opening facing the electric motor 3 side.

  One end of the worm shaft 21 housed in the worm shaft housing portion 16 is rotatably supported by the worm shaft housing portion 16. On the other hand, the other end is connected to the rotating shaft 7 of the electric motor 3 via a connecting member 18. That is, the rotary shaft 7 is configured to be detachably attached to the worm shaft 21 via the connecting member 18, and when the rotary shaft 7 is connected to the worm shaft 21, both of them rotate together. . The worm shaft storage portion 16 is provided with a steel ball (not shown) on one end side of the worm shaft 21, and the thrust load of the worm shaft 21 is received by this steel ball.

  The clutch housing portion 17 is formed in a bottomed cylindrical shape, and three bolt seats 24, 24, 24 projecting radially outward are provided on the outer peripheral surface. One of the three bolt seats 24, 24, 24 is provided on the worm shaft storage portion 16 side. Each bolt seat 24 is formed with a through hole 25. Each through hole 25 is provided with a bush 26.

Further, on the bottom surface 17a of the clutch housing portion 17, a support column 27 for projectingly supporting the worm wheel 22 so as to be rotatable is provided in a substantially radial center.
An insertion hole 28 is formed at the center in the radial direction of the column 27, and a center shaft 29 is inserted through an O-ring 58. The center shaft 29 is for rotatably supporting the clutch mechanism 4 and is inserted from the bottom surface 17a side of the clutch housing portion 17 toward the opening portion side. An outer flange portion 30 is formed on the proximal end side of the center shaft 29, and the axial positioning of the center shaft 29 is performed by the outer flange portion 30 coming into contact with the bottom surface 17 a of the clutch housing portion 17. .

(Clutch mechanism)
FIG. 3 is an exploded perspective view of the clutch mechanism 4.
As shown in FIGS. 2 and 3, the worm wheel 22 rotatably supported by the support column 27 of the clutch housing portion 17 is formed in a substantially disc shape with resin, and has a worm shaft on the outer peripheral surface. The tooth part 22a which meshes with 21 is formed. An insertion hole 35 for inserting the support column 27 is formed at the radial center of the worm wheel 22. In a state where the worm wheel 22 is inserted into the column 27, the end surface 27 a of the column 27 is exposed through the insertion hole 35 of the worm wheel 22.

  In the worm wheel 22, three first recesses 36, 36, 36 formed on the surface opposite to the bottom surface 17 a of the clutch housing portion 17 around the insertion hole 35 in a substantially fan shape in an axial plan view, And three 2nd recessed parts 37, 37, 37 are formed. The first concave portion 36 and the second concave portion 37 are arranged at equal intervals in the circumferential direction. That is, the first recesses 36 and the second recesses 37 are alternately arranged in the circumferential direction.

  The first recess 36 is formed in a substantially U-shaped cross section, and has a bottom wall 36a and a side wall 36b. On the other hand, the second recess 37 is also formed in a substantially U-shaped cross section and has a bottom wall 37a and a side wall 37b. In the second recess 37, an inclined wall 37c is formed at a joint portion between the bottom wall 37a and the side wall 37b. By forming the inclined wall 37c, the depth of the second recess 37 is configured to gradually decrease from the center in the circumferential direction toward the outer side in the circumferential direction.

Here, the worm wheel 22 constitutes the other of the worm gear 11 and constitutes a part of the clutch mechanism 4.
That is, the clutch mechanism 4 is disposed between the worm wheel 22, the drive plate 41 disposed on the opposite side of the bottom surface 17 a of the clutch housing portion 17 of the worm wheel 22, and the worm wheel 22 and the drive plate 41. A clutch plate 42 and a coil spring 43 that is disposed between the drive plate 41 and the clutch plate 42 and biases the clutch plate 42 toward the worm wheel 22 are provided.

4A and 4B show the drive plate 41, where FIG. 4A is a perspective view seen from the side opposite to the worm wheel 22, and FIG. 4B is a perspective view seen from the worm wheel 22 side.
As shown in FIGS. 2, 3, 4 (a), and 4 (b), the drive plate 41 is made of resin and has a substantially disc-shaped plate body 44. A boss portion 45 is integrally formed on the surface 44a of the plate main body 44 opposite to the worm wheel 22 at the substantially radial center.
The boss portion 45 is formed in a columnar shape and protrudes along the axial direction. The outer peripheral surface of the boss portion 45 is splined.

  An insertion hole 46 through which the center shaft 29 can be inserted is formed at the center of the boss portion 45 in the radial direction, and the center shaft 29 is inserted therethrough. That is, the drive plate 41 is rotatably supported by the center shaft 29. Further, an O-ring groove 47 is formed on the peripheral surface of the insertion hole 46 on the end surface of the boss portion 45, and an O-ring 62 is attached thereto. Thereby, it is possible to prevent dust and water droplets from entering from the outside between the center shaft 29 and the drive plate 41.

On the other hand, on the surface 44b of the plate main body 44 on the worm wheel 22 side, a spring accommodating portion 49 that receives one end of the coil spring 43 is formed in the center in the radial direction. The spring accommodating portion 49 is in a state communicating with the insertion hole 46.
Further, on the surface 44b of the plate main body 44 on the worm wheel 22 side, three first convex portions 48 are provided at portions corresponding to the first concave portion 36 of the worm wheel 22. The first convex portion 48 has a substantially fan shape in the axial plan view and a quadrangular shape in the axial cross section so as to correspond to the shape of the first concave portion 36 in the axial plan view.

The circumferential width of the first convex portion 48 is set to be smaller than the circumferential width of the first concave portion 36 of the worm wheel 22, and the first convex portion 48 is inserted into the first concave portion 36. It has become. When the worm wheel 22 rotates, the side wall 36b of the first concave portion 36 and the circumferential side surface 48a of the first convex portion 48 abut on each other in the circumferential direction and rotate together in a state where they are engaged with each other (for details). Will be described later).
That is, in the clutch mechanism 4, the worm wheel 22 serves as a drive rotator to which the rotation of the rotation shaft 7 of the electric motor 3 is input via the worm shaft 21. On the other hand, the drive plate 41 has a role of a driven rotator that outputs the rotation of the worm wheel 22 as a drive rotator to the power window device.

5A and 5B show the clutch plate 42, where FIG. 5A is a perspective view seen from the drive plate 41 side, and FIG. 5B is a perspective view seen from the worm wheel 22 side.
As shown in FIGS. 2, 3, 5 (a), and 5 (b), the clutch plate 42 is made of resin and has a substantially disc-shaped plate body 51. The outer diameter of the plate body 51 is set so as to be inside the portion where the tooth portion 22a of the worm wheel 22 is formed. An insertion hole 33 for inserting the center shaft 29 is formed in the center of the plate body 51 in the radial direction, and the center shaft 29 is inserted therethrough. That is, the clutch plate 42 is rotatably supported on the center shaft 29.

In the plate body 51, three openings (through holes) 53 are formed at portions corresponding to the first convex portions 48 of the drive plate 41. The opening 53 is formed in a substantially fan shape in the axial plan view so as to correspond to the shape of the first convex portion 48 of the drive plate 41 in the axial plan view. The circumferential width of the opening 53 is set to be larger than the circumferential width of the first convex portion 48 of the drive plate 41.
The first protrusion 48 is penetrated through the opening 53. That is, the first convex portion 48 of the drive plate 41 is inserted into the first concave portion 36 of the worm wheel 22 through the opening 53 of the clutch plate 42.

  A spring accommodating portion 52 that receives the other end of the coil spring 43 is formed on the surface 51 a of the plate body 51 on the drive plate 41 side. The coil spring 43 is held in a compressed and deformed state by being housed in a spring housing portion 49 formed on the drive plate 41 and a spring housing portion 52 formed on the clutch plate 42 at both ends. . That is, the coil spring 43 is in a state of biasing the clutch plate 42 toward the worm wheel 22.

On the other hand, on the surface 51 b on the worm wheel 22 side of the plate body 51, three second convex portions 54 are provided at portions corresponding to the second concave portions 37 of the worm wheel 22. The second convex portion 54 has a substantially fan shape in the axial plan view and a quadrangular shape in the axial cross section so as to correspond to the shape of the second concave portion 37 in the axial plan view.
The circumferential width of the second convex portion 54 is set to be smaller than the circumferential width of the second concave portion 37 of the worm wheel 22. The second concave portion 37 is in a state where the second convex portion 54 is inserted. When the worm wheel 22 rotates, the side wall 37b and the inclined wall 37c of the second concave portion 37 and the circumferential side surface 54a of the second convex portion 54 are in contact with each other in the circumferential direction (details). Will be described later).

  Here, the end surface 27a of the column 27 integrally formed with the clutch housing portion 17 is exposed from the insertion hole 35 of the worm wheel 22 with the worm wheel 22 inserted. For this reason, the end surface 27 a of the support column 27 is in a state of being overlapped with the plate body 51 of the clutch plate 42. A clutch engaging portion 55 is formed at a portion corresponding to the column 27 of the plate body 51 that is superposed on each other and an end surface 27 a of the column 27.

  The clutch engaging portion 55 includes a plurality of engaging grooves 56 formed on the end surface 27 a of the support column 27, and engaging protrusions 57 formed in the plate body 51 and fitable in the engaging grooves 56. . The engagement grooves 56 and the engagement protrusions 57 are formed radially at equal intervals in the circumferential direction, and are set so that the width in the circumferential direction increases toward the outer side in the radial direction.

As shown in FIGS. 1 and 2, the clutch housing portion 17 is provided with a substantially annular bottom cover 63 that closes the opening portion 17b. The bottom cover 63 is for preventing intrusion of dust and water droplets into the clutch housing portion 17.
From the center of the bottom cover 63, the boss portion 45 of the drive plate 41 protrudes. Therefore, the worm wheel 22, the clutch plate 42, and the coil spring 43 are completely stored in the clutch storage portion 17.

A rubber seal member 64 is provided on the inner peripheral edge of the bottom cover 63 in order to enhance the internal sealing performance of the clutch housing portion 17.
On the other hand, a plurality of locking pieces 67 are provided on the outer peripheral edge of the bottom cover 63. The locking piece 67 is formed to be elastically deformable, and extends toward the bottom surface 17 a of the clutch housing portion 17 along the outer peripheral surface of the clutch housing portion 17.
Further, a locking projection 65 is formed on the outer peripheral surface of the clutch housing portion 17 at a portion corresponding to the locking piece 67. The bottom cover 63 is fixed by engaging the locking protrusion 65 and the locking piece 67.

  Such a clutch mechanism 4 is housed in the clutch housing portion 17 in the order of the worm wheel 22, the clutch plate 42, the coil spring 43, and the drive plate 41, and the center shaft 29 protrudes from the boss portion 45 of the drive plate 41. It has become. A C-type retaining ring 60 and a washer 59 are attached to the tip of the center shaft 29, thereby restricting the worm wheel 22, the clutch plate 42, the coil spring 43 and the drive plate 41 from coming off.

  Here, when the clutch mechanism 4 is assembled to the casing 13, a clearance K <b> 1 is formed between the clutch plate 42 and the drive plate 41. The clearance K1 can release the engaged state of the clutch engaging portion 55, that is, the engagement protrusion 57 formed on the clutch plate 42 from the engaging groove 56 formed on the column 27 of the clutch housing portion 17. It is set to a size that can be separated along the axial direction.

6 shows the positional relationship of each part of the clutch mechanism 4, (a) is a detailed view of the A part of FIG. 2, (b) is a detailed view of the B part of FIG. 2, and (c) is a detailed view of the C part of FIG. FIG.
As shown in FIGS. 6B and 6C, a clearance K2 is provided between the side wall 36b of the first concave portion 36 of the worm wheel 22 and the side surface 48a of the first convex portion 48 of the drive plate 41. Is formed. Further, a clearance K <b> 3 is formed between the side wall 37 b (slanted wall 37 c) of the second concave portion 37 of the worm wheel 22 and the side surface 54 a of the second convex portion 54 of the clutch plate 42. A clearance K4 is formed between the side surface 48a of the first convex portion 48 of the drive plate 41 and the opening 53 of the clutch plate 42.

  The clearances K2, K3, and K4 are such that when the worm wheel 22 is rotated before the drive plate 41, the clutch plate 42 is moved before the first convex portion 48 of the drive plate 41 contacts the first concave portion 36. The corner 54 b of the second convex portion 54 is set so as to contact the inclined wall 37 c of the second concave portion 37. That is, when the worm wheel 22 rotates before the drive plate 41, the clutch plate 42 is pushed up, and the engaged state of the clutch engaging portion 55 is released.

  The clearances K2, K3, and K4 are such that the corner portion 54b of the second convex portion 54 of the clutch plate 42 contacts the inclined wall 37c of the second concave portion 37 when the drive plate 41 rotates before the worm wheel 22. Prior to this, the first convex portion 48 of the drive plate 41 is set to contact the first concave portion 36. In other words, when the drive plate 41 rotates before the worm wheel 22, the engagement state of the clutch engagement portion 55 is maintained.

This will be described in more detail with reference to FIGS.
Here, in the following description, the angle between the side surface 54a of the second convex portion 54 formed on the clutch plate 42 and the inclined wall 37c of the second concave portion 37 formed on the worm wheel 22 (second The circumferential play between the convex portion 54 and the second concave portion 37 is defined as θa.
Further, the angle between the side surface 57a of the engaging projection 57 formed on the clutch plate 42 and the side wall 56a of the engaging groove 56 formed on the support column 27 of the clutch housing portion 17 (engaged with the engaging projection 57). The backlash in the circumferential direction between the joint groove 56 is defined as θb.

Further, an angle between the side surface 48a of the first convex portion 48 formed on the drive plate 41 and the side wall 36b of the first concave portion 36 formed on the worm wheel 22 (the first convex portion 48 and the first concave portion). The circumferential backlash between the two and 36 is θx.
Then, the climbing angle of the clutch plate 42 by the inclined wall 37c of the second concave portion 37 (the release angle of the clutch engaging portion 55) is θy ′.
Further, an angle between the plate main body 44 of the drive plate 41 and the plate main body 51 of the clutch plate 42 is defined as θv.

Furthermore, an angle between one side surface 53a of the opening 53 formed in the plate body 51 of the clutch plate 42 and the side wall 36b of the first recess 36 formed in the worm wheel 22 is defined as θz.
When the angles θa to θz are set in this way, the angles θa to θz are
θx> θy (1)
θy = θa + θb + θy ′ (2)
θy ′ <θv (3)
θz> θy ′ (4)
Set to satisfy.

Here, the angle θb in the equation (2) is formed in the support column 27 of the clutch housing portion 17 with the angle between the circumferential side surfaces 57a and 57a of the engagement protrusion 57 formed on the clutch plate 42 being θ1. When the angle between the side walls 56a, 56a of the engaging groove 56 is θ2,
θb = (θ2−θ1) / 2 (5)
To be determined.

Further, the clutch plate 42 is moved until the engagement protrusion 57 formed on the clutch plate 42 is completely separated from the engagement groove 56 formed on the support column 27 of the clutch housing portion 17 and the clutch engagement portion 55 is released. When the rotation angle of the worm wheel 22 necessary to push up the angle is θy1, and the angle of the inclined wall 37c of the second recess 37 formed in the worm wheel 22 is θ, the angle θy ′ is
θy ′ = θy1 · tan θ (6)
To be determined. The angle θ of the inclined wall 37c of the second recess 37 is
θ = 45 °
Is set to

Here, the expressions (1) to (3), (5), and (6) are the conditions when the worm wheel 22 is rotated before the drive plate 41, that is, the electric motor 3 is rotated. Thus, the output condition is for output from the drive plate 41 to a power window device (not shown).
On the other hand, Expression (4) is a condition when the drive plate 41 is rotated ahead of the worm wheel 22, that is, a condition for preventing the reverse rotation of the drive plate 41 that can hold the stop position of the window glass, for example.

From these, the angle θz and the angle θx are θz> θy1 (7)
θx> θy1 (8)
By satisfy | filling, when the electric motor 3 is driven, the drive plate 41 can be rotated reliably. Further, the reverse rotation of the drive plate 41, that is, the rotation of the drive plate 41 can be reliably prevented by an external force.

(Function)
Next, the operation of the clutch mechanism 4 will be described with reference to FIGS.
7 to 20 show the behavior of each part of the clutch mechanism 4, wherein (a) in each figure is an explanatory diagram of part A in FIG. 2, (b) in each figure is an explanatory diagram of part B in FIG. (C) of FIG. 2 is an explanatory diagram of a portion C of FIG.
First, the case where the electric motor 3 is driven and the drive plate 41 is rotated will be described.
As shown in FIGS. 7A, 7B, and 7C, when the electric motor 3 is stopped, the clutch plate 42 is attached to the worm wheel 22 side by the coil spring 43. It is energized. For this reason, the engagement protrusions 57 of the clutch plate 42 are fitted in the plurality of engagement grooves 56 formed on the end surface 27a of the support column 27, and the clutch engagement portion 55 is engaged (FIG. 7). (See (a)).

Further, the second concave portion 37 of the worm wheel 22 is not in contact with the second convex portion 54 of the clutch plate 42 and is in a free state (see FIG. 7B).
Further, the first concave portion 36 of the worm wheel 22 is not in contact with the first convex portion 48 of the drive plate 41 and is in a free state. At this time, the first convex portion 48 of the drive plate 41 and the opening 53 of the clutch plate 42 are not in contact with each other and are in a free state (see FIG. 7C).

  As shown in FIG. 8A, FIG. 8B, and FIG. 8C, when the electric motor 3 is driven, the rotating shaft 7 and the worm shaft 21 rotate together to engage with the worm shaft 21. The wheel 22 rotates. Then, the inclined wall 37c of the second concave portion 37 formed on the worm wheel 22 comes into contact with the corner portion 54b of the second convex portion 54 of the clutch plate 42 (see FIG. 8B). At this time, the first concave portion 36 of the worm wheel 22 and the first convex portion 48 of the drive plate 41 are not in contact with each other (see FIG. 8C).

  If the worm wheel 22 continues to rotate in this state, the second recess 37 of the worm wheel 22 causes the clutch plate 42 to worm as shown in FIGS. 9 (a), 9 (b), and 9 (c). The wheel 22 is rotated in the same direction as the rotation direction. Then, the side surface 57 a of the engagement protrusion 57 formed on the clutch plate 42 and the side wall 56 a of the engagement groove 56 formed on the support column 27 of the clutch housing portion 17 come into contact with each other. That is, the second convex portion 54 of the clutch plate 42 is in contact with the inclined wall 37c of the second concave portion 37 of the worm wheel 22 at the corner portion 54b on the rear side in the rotational direction (left side in FIG. 9) (see FIG. 9B). ).

On the other hand, the engaging protrusion 57 of the clutch plate 42 has a side surface 57a in the front in the rotational direction that abuts against the side wall 56a of the engaging groove 56 of the support column 27 (see FIG. 9A).
For this reason, the rotation of the clutch plate 42 is restricted. At this time, the first concave portion 36 of the worm wheel 22 and the first convex portion 48 of the drive plate 41 are not yet in contact with each other (see FIG. 9C).

  As shown in FIGS. 10 (a), 10 (b), and 10 (c), when the rotation of the clutch plate 42 is restricted and the worm wheel 22 continues to rotate, The two convex portions 54 are pressed against the inclined wall 37 c of the second concave portion 37 of the support column 27. And the 2nd convex part 54 is pushed up toward the drive plate 41 side (upper side in FIG.10 (b)) along the inclined wall 37c. Then, the engagement protrusion 57 of the clutch plate 42 is separated from the engagement groove 56 of the column 27, and the engagement state of the clutch engagement portion 55 is released (see FIG. 10A).

Here, since the clutch plate 42 is urged toward the worm wheel 22 by the coil spring 43, when the urging force (spring force) of the coil spring 43 is F and the push-up force of the clutch plate 42 is F ′. The pushing force F ′ is
F <F '(9)
It is necessary to set to satisfy.

The pushing force F ′ is determined by the torque Tq of the worm wheel 22. That is, when the distance that the second convex portion 37 moves along the inclined wall 37c of the second concave portion 37 is r (see FIG. 10B), and the friction coefficient of the inclined wall 37c of the second concave portion 37 is μ. The torque Tq of the worm wheel 22 is
Tq = μ × F × cos θ × cos θ × r (10)
Determined by.
For this reason, it is necessary to determine the spring constant of the coil spring 43 and the output of the electric motor 3 so as to satisfy the expressions (9) and (10).

  As shown in FIGS. 10A and 10C, at the time when the engagement state of the clutch engaging portion 55 is released, the side surface 48a of the first convex portion 48 of the drive plate 41 and the worm wheel 22 are obtained. A slight gap S is formed between the first recess 36 and the side wall 36b.

As shown in FIGS. 11 (a), 11 (b), and 11 (c), when the worm wheel 22 is continuously rotated, the clutch engaging portion 55 is maintained in a released state. And the side wall 36b of the 1st recessed part 36 of the worm wheel 22 contact | abuts to the side surface 48a of the 1st convex part 48 of the drive plate 41 (refer FIG.11 (c)).
At this time, the clutch plate 42 rotates integrally with the worm wheel 22 while maintaining the state of being pushed up by the second recess 37 of the worm wheel 22. For this reason, the clutch plate 42 is not pushed down by the coil spring 43. Further, the first protrusion 48 of the drive plate 41 and the opening 53 of the clutch plate 42 do not come into contact with each other.

Subsequently, in such a state, the worm wheel 22 presses the drive plate 41 in the circumferential direction, and the worm wheel 22 and the drive plate 41 rotate together. Thereby, the rotation of the drive plate 41 is transmitted to the power window device or the like.
Note that the rotation angle of the rotating shaft 7 (armature 6) from when the electric motor 3 is driven to when the drive plate 41 rotates is such that the side surface 48a of the first convex portion 48 formed on the drive plate 41 and the worm wheel. 22 is θx, which is an angle between the first concave portion 36 and the side wall 36b of the first concave portion 36 (backlash in the circumferential direction between the first convex portion 48 and the first concave portion 36) (see FIG. 6C). ).

Next, the case where the electric motor 3 is stopped and, for example, the window glass (not shown) of the vehicle is stopped at a desired position will be described.
As shown in FIGS. 12 (a), 12 (b), and 12 (c), the worm wheel 22 is in a stopped state. For example, the weight of a wind glass (not shown) and vibration during vehicle travel are provided. When the drive plate 41 starts to rotate by an external force such as the above, the side surface 48a of the first convex portion 48 of the drive plate 41 contacts the side wall 36b of the first concave portion 36 of the worm wheel 22 (see FIG. 12C).
At this time, the drive plate 41 is still pushed up by the second recess 37 of the worm wheel 22, and the clutch engaging portion 55 is released (FIG. 12 (a), FIG. 12). (See (b)).

As shown in FIGS. 13 (a), 13 (b), and 13 (c), when the drive plate 41 continues to rotate, the drive plate 41 is integrated in a state of pressing the worm wheel 22 in the circumferential direction. Rotate. And the side surface 48a of the 1st convex part 48 contact | abuts to the side surface 53a of the opening part 53 of the clutch plate 42 (refer FIG.13 (c)).
Then, the drive plate 41 presses the clutch plate 42 and the worm wheel 22 in the circumferential direction, and the drive plate 41, the clutch plate 42, and the worm wheel 22 start to rotate integrally (FIG. 13A). FIG. 13 (b)).

  As shown in FIGS. 14 (a), 14 (b), and 14 (c), when the drive plate 41, the clutch plate 42, and the worm wheel 22 continue to rotate together, the clutch plate 42 is engaged. The protrusion 57 moves on the engagement groove 56 of the support column 27 formed in the clutch housing portion 17. Then, the clutch plate 42 is pushed down by the coil spring 43, and the engaging protrusion 57 is fitted into the engaging groove 56 (see FIG. 14A).

  As shown in FIG. 15A, FIG. 15B, and FIG. 15C, when the drive plate 41, the clutch plate 42, and the worm wheel 22 continue to rotate together, the clutch plate 42 The side surface 57a of the engagement protrusion 57 and the side wall 56a of the engagement groove 56 of the column 27 abut against each other. As a result, the clutch engaging portion 55 is completely engaged (see FIG. 15A).

  Then, since the rotation of the clutch plate 42 is restricted, the rotation of the drive plate 41 that has been rotated integrally with the clutch plate 42 is prevented. For this reason, the worm wheel 22 that has been rotated by being pressed by the drive plate 41 in the circumferential direction also stops. Thereby, when the drive plate 41 rotates before the worm wheel 22, the rotation (reverse rotation) of the drive plate 41 and the worm wheel 22 is prevented.

Next, the case where the drive plate 41 starts to rotate toward the opposite side to FIGS. 12 to 15 in a state where the electric motor 3 is stopped will be described.
16A, 16B, and 16C, the side surface 48a of the first convex portion 48 of the drive plate 41 is one side wall 36b of the first concave portion 36 of the worm wheel 22 (see FIG. 16). When the drive plate 41 starts to rotate toward the other side (to the right in FIG. 16C) when it is in contact with the left side in FIG. Is in a released state.

As shown in FIGS. 17A, 17B, and 17C, when the drive plate 41 continues to rotate, the first convex portion of the drive plate 41 is formed on the side surface 53a of the opening 53 of the clutch plate. The side surface 48a of 48 contacts (see FIG. 17C).
As shown in FIGS. 18 (a), 18 (b), and 18 (c), when the drive plate 41 continues to rotate, the drive plate 41 is integrated in a state of pressing the clutch plate 42 in the circumferential direction. Rotate. And the side surface 48a of the 1st convex part 48 contact | abuts to the side wall 36b of the 1st recessed part 36 of the worm wheel 22 (refer FIG.18 (c)).
Then, the drive plate 41 presses the clutch plate 42 and the worm wheel 22 in the circumferential direction, and the drive plate 41, the clutch plate 42, and the worm wheel 22 start to rotate together (FIG. 18A). FIG. 18B).

  As shown in FIGS. 19A, 19B, and 19C, when the drive plate 41, the clutch plate 42, and the worm wheel 22 continue to rotate together, the clutch plate 42 is engaged. The protrusion 57 moves from the released engagement groove 56 to the next adjacent engagement groove 56. Then, the clutch plate 42 is pushed down by the coil spring 43, and the engagement protrusion 57 is fitted into the engagement groove 56 (see FIG. 19A).

Here, it is desirable to set the angle (distance) between the engaging grooves 56 and 56 adjacent in the circumferential direction as small as possible. This is because the rotation angle when the drive plate 41 is rotated by an external force can be set small. However, when the clutch engaging portion 55 is released, the engaging protrusion 57 is positioned between the engaging groove 56 and the engaging groove 56 adjacent thereto. For this reason, the angle (distance) between the engaging grooves 56 and 56 needs to be set to a size that can maintain the released state of the clutch engaging portion 55.
In view of these, for example, when the angle θ2 between the side walls 56a, 56a of the engagement groove 56 formed in the support column 27 of the clutch housing portion 17 is set to about 4 °, the engagement groove 56, The angle θ2 ′ between 56 is set to about 3 °.

As shown in FIGS. 20A, 20B, and 20C, when the drive plate 41, the clutch plate 42, and the worm wheel 22 continue to rotate together, the clutch plate 42 The side surface 57a of the engagement protrusion 57 and the side wall 56a of the engagement groove 56 of the support column 27 are in contact with each other. As a result, the clutch engaging portion 55 is completely engaged (see FIG. 20A).
Then, since the rotation of the clutch plate 42 is restricted, the rotation of the drive plate 41 that has been rotated integrally with the clutch plate 42 is prevented. For this reason, the worm wheel 22 that has been rotated by being pressed by the drive plate 41 in the circumferential direction also stops. Thereby, when the drive plate 41 rotates before the worm wheel 22, the rotation (reverse rotation) of the drive plate 41 and the worm wheel 22 is prevented.

(effect)
Therefore, according to the above-described first embodiment, when the drive plate 41 on the output side tries to rotate before the worm wheel 22 on the input side, the engagement protrusion 57 of the clutch plate 42 and the clutch housing portion 17. It is possible to prevent the rotational force from being transmitted to the worm wheel 22 by engaging the engaging grooves 56 with each other. For this reason, rotation by the external force of the rotating shaft 7 can be prevented without imparting sliding resistance to the rotating shaft 7 as in the prior art, and a decrease in output efficiency of the electric motor 3 can be prevented.
Further, since the clutch plate 42 is biased toward the worm wheel 22 by the coil spring 43, even if the clearance K1 is formed between the clutch plate 42 and the drive plate 41, the fluttering of the clutch plate 42 is suppressed. Can do. For this reason, the noise of the clutch mechanism 4 can be reduced.

Furthermore, the drive plate 41 is provided with a plurality (three) of first convex portions 48, the clutch plate 42 is formed with an opening 53 through which the first convex portion 48 can pass, and a second convex portion 54 is provided. . On the other hand, a first recess 36 and a second recess 37 are formed in the worm wheel 22. In addition, a clutch engaging portion 55 is formed on each of the support column 27 formed on the clutch housing portion 17 and the clutch plate 42. The rotational force from the worm wheel 22 is smoothly transmitted to the drive plate 41 and the reverse rotation of the drive plate 41 is prevented. For this reason, the structure of the clutch mechanism 4 can be simplified and the manufacturing cost can be reduced.
Further, since the clutch engaging portion 55 is a simple structure constituted by the engaging protrusion 57 of the clutch plate 42 and the engaging groove 56 of the support column 27, the clutch engaging portion 55 can be disposed in a space-saving manner. The clutch mechanism 4 can be reduced in size.

  In the first embodiment described above, the clutch engaging portion 55 is constituted by the engaging groove 56 formed in the support column 27 of the clutch housing portion 17 and the engaging protrusion 57 formed in the clutch plate 42. explained. However, the present invention is not limited to this, and the engaging protrusion 57 may be formed on the support column 27 while the engaging groove 56 may be formed on the clutch plate 42.

(Second embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the same aspect as 1st embodiment, and description is abbreviate | omitted (same also about the following embodiment).
FIG. 21 is an exploded perspective view of the clutch mechanism 74 of the second embodiment, FIG. 22 shows the clutch plate 82, (a) is a perspective view seen from the drive plate 41 side, and (b) is from the worm wheel 22 side. It is the seen perspective view.
In the second embodiment, the electric motor 3 is detachably provided on the worm reducer 72, the clutch mechanism 74 is internally provided on the worm reducer 72, and the casing 73 of the worm reducer 72 is a worm reducer 72. The shaft housing portion 16 and the clutch housing portion 77 are integrally formed. The clutch housing portion 77 is formed in a bottomed cylindrical shape, and the opening 77b is closed by the bottom cover 63. The clutch mechanism 74 is disposed between the worm wheel 22, the drive plate 41 disposed on the opposite side of the bottom surface 77 a of the clutch housing portion 77 of the worm wheel 22, and the worm wheel 22 and the drive plate 41. The clutch plate 82 is disposed between the drive plate 41 and the clutch plate 82. The basic structure of such that it includes a coil spring 43 that urges the worm wheel 22 side is the same as the first embodiment described above.

  Here, in the clutch housing portion 77 of the second embodiment, a clutch engaging portion 55 is formed at a portion corresponding to the end surface 27a of the support column 27 protruding substantially in the center in the radial direction and the support column 27 of the clutch plate 82. However, a new clutch engaging portion 75 is formed on the inner peripheral surface 77 c of the clutch housing portion 77 and the outer peripheral edge of the clutch plate 82.

As shown in FIGS. 21, 22 (a) and 22 (b), the clutch plate 82 has a plate body 83 formed in a substantially disc shape. The outer diameter of the plate body 83 is set so as to substantially match the diameter of the inner peripheral surface 77 c of the clutch housing portion 77.
On the other hand, the inner peripheral surface 77c of the clutch housing portion 77 is formed with a reduced diameter portion 76 in which the bottom surface 77a side is reduced in diameter by a step from the opening 77b.
The position of the stepped surface 76 a of the reduced diameter portion 76 is set to a position that can contact the outer peripheral edge of the plate main body 83 in a state where the clutch plate 82 is set in the clutch housing portion 77. That is, the plate main body 83 is in a state of being overlaid with the support column 27 of the clutch housing portion 77 and is overlaid with the stepped surface 76 a of the reduced diameter portion 76 of the clutch housing portion 77.

A clutch engaging portion 75 is formed on the stepped surface 76 a of the reduced diameter portion 76 and the outer peripheral edge of the plate body 83. The clutch engaging portion 75 is formed on a plurality of engaging grooves 78 formed on the stepped surface 76 a of the reduced diameter portion 76 and an outer peripheral edge of the plate body 83, and an engaging protrusion 79 that can be fitted into the engaging groove 78. It consists of and.
Therefore, according to the second embodiment described above, the same effects as those of the first embodiment described above can be achieved. Further, by using the clutch mechanism 4 described above and the clutch mechanism 74 of the second embodiment properly, variations can be increased according to the layout of the clutch mechanism, the specifications of the motor 1 with a reduction gear, and the like. It becomes possible to meet the demand.

In the first embodiment and the second embodiment described above, the case where the first concave portion 36 is formed in the worm wheel 22 while the first convex portion 48 is formed in the drive plate 41 has been described. However, the present invention is not limited to this, and the first concave portion 36 may be formed in the drive plate 41 while the first convex portion 48 is formed in the worm wheel 22.
Further, the case where the second concave portion 37 is formed in the worm wheel 22 and the second convex portion 54 is formed in the clutch plate 42 has been described. However, the present invention is not limited to this, and the second convex portion 54 may be formed on the worm wheel 22 while the second concave portion 37 may be formed on the clutch plate 42.

  Furthermore, in the second embodiment described above, the clutch engaging portion 75 is engaged with the engaging groove 78 formed in the stepped surface 76a of the inner peripheral surface 77c of the clutch housing portion 77 and the outer peripheral edge of the clutch plate 42. The case where it comprises the joint protrusion 79 was demonstrated. However, the present invention is not limited to this, and the engaging protrusion 79 may be formed on the stepped surface 76 a of the clutch housing portion 77, while the engaging groove 78 may be formed on the outer peripheral edge of the clutch plate 42.

(Third embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS.
FIG. 23 is a perspective view of the clutch mechanism 94 of the third embodiment, and FIG. 24 is a cross-sectional view taken along line YY of FIG.
In the third embodiment, the point that the electric motor 3 is detachably provided on the worm reduction gear 92 is the same as in the first embodiment described above.

  Here, as shown in FIGS. 23 and 24, the worm reduction gear 92 has a separate structure in which the brush holder portion 100 that receives the commutator 9 of the electric motor 3 and the gear storage portion (not shown) that stores the worm gear 11 are separated. It has become. Only the worm gear 11, that is, the worm shaft 21 constituting one of the worm gears 11, and the worm wheel (not shown) constituting the other are accommodated in the gear housing not shown. A clutch mechanism 94 is provided between the rotating shaft 7 and the worm shaft 21 that protrude toward the worm gear 11 via the brush holder portion 100.

FIG. 25 is an exploded perspective view of the clutch mechanism 94.
As shown in FIGS. 24 and 25, the clutch mechanism 94 includes a joint motor 102 fixed to the worm shaft 21 side end of the rotating shaft 7 and a joint frame fixed to the rotating shaft 7 side end of the worm shaft 21. 103, the clutch plate 104 disposed between the joint motor 102 and the joint frame 103, and the clutch plate 104 disposed between the joint frame 103 and the clutch plate 104 to urge the clutch plate 104 toward the brush holder portion 100. A coil spring 105 is provided.

26A and 26B show the brush holder unit 100, where FIG. 26A is a perspective view seen from the armature core 8 side, and FIG. 26B is a perspective view seen from the worm shaft 21 side.
26A and 26B, the brush holder portion 100 is formed in a box shape having an opening on the electric motor 3 side, and the yoke 5 of the electric motor 3 is a brush. The holder 100 is attached so as to close the opening.
A brush holder body 107 is provided inside the brush holder portion 100. The brush holder body 107 is provided with a brush 106 that can be protruded and projected toward the center in the radial direction. The brush 106 is in sliding contact with the commutator 9 and supplies electric power.

  A pigtail 108 for supplying power to the brush 106 is wired on the peripheral wall 100 a of the brush holder unit 100, and one end thereof is connected to the brush 106. In addition, a terminal 109 is provided on the peripheral wall 100 a of the brush holder portion 100, and the other end of the pigtail 108 is connected to the terminal 109. Terminal 109 is electrically connected to a connector (not shown) provided in a gear housing (not shown). As a result, the power of the external power source can be supplied to the armature 6 of the electric motor 3.

Further, on the bottom surface 100b of the brush holder portion 100, a sliding bearing 111 for rotatably supporting one end side of the rotating shaft 7 is provided at the substantially center in the radial direction (see FIG. 24). Further, a cylindrical joint housing portion 110 is integrally formed on the bottom surface 100 b of the brush holder portion 100.
The joint housing part 110 is formed so as to surround the periphery of the slide bearing 111, and protrudes toward the joint motor 102 side (toward the left side in FIG. 26B). A joint motor 102 is accommodated in the joint accommodating portion 110.

27A and 27B show the joint motor 102, where FIG. 27A is a perspective view seen from the armature core 8 side, and FIG. 27B is a perspective view seen from the worm shaft 21 side.
As shown in FIGS. 24, 25, 27 (a), and 27 (b), the joint motor 102 is made of resin and has a substantially disc-shaped main body 112. A square hole 113 is formed in most of the center of the main body 112 in the radial direction.
On the other hand, a two-side chamfered portion 114 is formed at the end of the rotating shaft 7 on the worm shaft 21 side (see FIG. 25), and the two-sided chamfered portion 114 is inserted into the square hole 113 of the main body portion 112. It has become. Thereby, the rotating shaft 7 and the joint motor 102 are connected so as not to be relatively rotatable and movable in the axial direction.

  On the outer peripheral surface of the main body portion 112, there are provided three protruding portions 115 that are substantially fan-shaped in an axial plan view toward the outer side in the radial direction. And these protrusion part 115 is arrange | positioned at equal intervals in the circumferential direction. The diameter of the rotation trajectory of each protrusion 115 is set to be slightly smaller than the inner diameter of the joint storage portion 110. In addition, on the surface of each protrusion 115 on the clutch plate 104 side, a concave portion 116 having a substantially fan shape in an axial plan view is formed so as to correspond to the shape of the protrusion 115 in a plan view.

  The recess 116 is open to the clutch plate 104 side and the radially outer side, and is formed to connect the bottom wall 116a, the pair of side walls 116b and 116b, and the bottom wall 116a and the side wall 116b. And an inclined wall 116c. Due to the inclined wall 116c, the axial depth of the recess 116 gradually becomes shallower toward the outer side in the circumferential direction.

FIG. 28 shows the joint frame 103, (a) is a perspective view seen from the joint motor 102 side, and (b) is a perspective view seen from the worm shaft 21 side.
As shown in FIGS. 24, 25, 28 (a), and 28 (b), the joint frame 103 is made of resin and has a main body 117 formed in a substantially disc shape. ing. The outer diameter of the main body 117 is set so as to substantially coincide with the diameter of the rotation locus of the protrusion 115 formed on the joint motor 102.

  An insertion hole 118 through which the end of the worm shaft 21 on the side of the rotating shaft 7 can be inserted is formed in the center of the main body 117 in the radial direction. Spline processing is applied to the inner peripheral surface of the insertion hole 118. On the other hand, the outer peripheral surface is splined at the end of the worm shaft 21 on the rotating shaft 7, so that the joint frame 103 and the worm shaft 21 are spline-fitted with each other.

  Further, the inner flange portion 121 is formed on the joint motor 102 side of the insertion hole 118 so as to be flush with the surface 117 a of the main body portion 117 on the joint motor 102 side. Furthermore, an annular portion 122 formed so as to surround the inner flange portion 121 is provided on the surface 117 a of the main body portion 117. The inner flange portion 121 and the annular portion 122 function as a spring accommodating portion 123 that receives one end of the coil spring 105.

  On a surface 117a on the joint motor 102 side of the main body 117, three axially fan-shaped convex portions 119 protrude from the outer peripheral side along the axial direction. These convex portions 119 are arranged at equal intervals in the circumferential direction so as to correspond between the protruding portions 115 formed in the joint motor 102. Furthermore, the axial length of the convex portion 119 is set to a length that can be interposed between the protruding portions 115 formed in the joint motor 102 when the joint frame 103 is set.

  Since the protrusions 119 are interposed between the protrusions 115 formed on the joint motor 102, when the joint motor 102 rotates, the side surface 115 a of the protrusion 115 contacts the side surface 119 a of the protrusion 119 of the joint frame 103. Touch. Then, the joint motor 102 and the joint frame 103 rotate together. Thereby, the rotational force of the rotating shaft 7 is transmitted to the worm shaft 21.

  That is, in the clutch mechanism 94, the joint motor 102 has a role of a driving rotating body to which the rotation of the rotating shaft 7 of the electric motor 3 is input. On the other hand, the joint frame 103 has a role of a driven rotating body that outputs the rotation of the joint motor 102 that is a driving rotating body to the worm shaft 21. Further, between the projecting portions 115 of the joint motor 102 has a function as an engaging portion 120 that engages with the convex portion 119 of the corresponding joint frame 103.

29A and 29B show the clutch plate 104, where FIG. 29A is a perspective view seen from the joint motor 102 side, and FIG. 29B is a perspective view seen from the joint frame 103 side.
As shown in FIGS. 24, 25, 29 (a), and 29 (b), the clutch plate 104 is made of resin and has a plate body 124 formed in a substantially disc shape. ing. The outer diameter of the plate body 124 is set so as to substantially match the outer diameter of the joint housing part 110 provided in the brush holder part 100. An insertion hole 125 for inserting the rotary shaft 7 is formed in the center of the plate body 124 in the radial direction, and the rotary shaft 7 is inserted through the hole 125. That is, the clutch plate 104 is rotatably supported on the rotating shaft 7.

  In the plate body 124, three openings (through holes) 126 are formed at portions corresponding to the convex portions 119 of the joint frame 103. The opening 126 is formed in a substantially fan shape in an axial plan view so as to correspond to the cross-sectional shape of the convex portion 119 of the joint frame 103. The circumferential width of the opening 126 is set to be larger than the circumferential width of the convex portion 119 of the joint frame 103. The first protrusion 48 is penetrated through the opening 126. That is, the convex portion 119 of the joint frame 103 is in a state of being interposed in the engaging portion 120 of the joint motor 102 via the opening 126 of the clutch plate 104.

  A spring accommodating portion 127 that receives the other end of the coil spring 105 is formed on the surface 124 a on the joint frame 103 side of the plate main body 124. The coil spring 105 is held in a state of being compressed and deformed by being housed in a spring housing portion 123 provided at both ends of the joint frame 103 and a spring housing portion 127 formed in the clutch plate 104. . That is, the coil spring 105 biases the clutch plate 104 toward the joint motor 102 side.

  On the other hand, on the surface 124 b on the joint motor 102 side of the plate body 124, three convex portions 128 are provided at portions corresponding to the concave portions 116 formed in the protruding portion 115 of the joint motor 102. The convex portion 128 has a substantially fan shape in the axial plan view and a quadrangular shape in the axial cross section so as to correspond to the shape of the concave portion 116 in the axial plan view.

  The circumferential width of the convex portion 128 is set to be smaller than the circumferential width of the concave portion 116 of the joint motor 102, and the convex portion 128 is inserted into the concave portion 116. When the joint motor 102 rotates, the side wall 116b and the inclined wall 116c of the concave portion 116 and the side surface 128a in the circumferential direction of the convex portion 128 come into contact with each other in the circumferential direction.

Here, the joint motor 102 is housed in the joint housing part 110 provided in the brush holder part 100, while the outer diameter of the plate body 124 of the clutch plate 104 substantially matches the outer diameter of the joint housing part 110. Therefore, the peripheral edge of the joint housing part 110 and the outer peripheral edge of the plate main body 124 of the clutch plate 104 are overlapped with each other. Clutch engaging portions 130 are formed on the peripheral edge of the joint storage portion 110 and the outer peripheral edge of the plate body 124 that are overlapped with each other.
The clutch engaging portion 130 includes a plurality of engaging grooves 131 formed on the peripheral edge of the joint housing portion 110 and a plurality of engaging protrusions 132 formed on the outer peripheral edge of the plate main body 124 and capable of fitting into the engaging grooves 131. It consists of and. The engagement grooves 131 and the engagement protrusions 132 are formed at equal intervals in the circumferential direction.

As shown in FIGS. 23 to 24, the clutch mechanism 94 is attached to the brush holder unit 100 in the order of the joint motor 102, the clutch plate 104, the coil spring 105, and the joint frame 103. The end surface and the end surface of the worm shaft 21 face each other.
Here, a steel ball 135 is provided between the end face of the rotating shaft 7 and the worm shaft 21. With the steel balls 135, thrust loads generated on the rotary shaft 7 and the worm shaft 21 are received from each other. Further, a concave portion 136 having a substantially conical section is formed on the end surface of the worm shaft 21 on the rotating shaft 7 side, and a steel ball 135 is set therein. Thereby, the movement of the steel ball 135 is regulated.

  Further, when the clutch mechanism 94 is assembled, a clearance K5 is formed between the clutch plate 104 and the main body 117 of the joint frame 103 (see FIG. 24). The clearance K5 can release the engagement state of the clutch engagement portion 130, that is, the engagement protrusion formed on the clutch plate 104 from the engagement groove 131 formed on the joint housing portion 110 of the brush holder portion 100. 132 is set to a size that can be separated along the axial direction.

  Then, by driving the electric motor 3, when the joint motor 102 rotates before the joint frame 103, the side surface 115 a of the projecting portion 115 of the joint motor 102 contacts the side surface 119 a of the convex portion 119 of the joint frame 103. Prior to this, the inclined wall 116c of the concave portion 116 of the joint motor 102 comes into contact with the corner portion 128b (see FIG. 29) of the convex portion 128 of the clutch plate 42. Therefore, in a state where the clutch plate 42 is pushed up and the clutch engaging portion 130 is released, the side surface 115a of the projecting portion 115 of the joint motor 102 abuts on the side surface 119a of the convex portion 119 of the joint frame 103, and Rotational force is transmitted to.

  On the other hand, when the joint frame 103 rotates before the joint motor 102 due to an external force, the clutch plate is moved before the side surface 119a of the convex portion 119 of the joint frame 103 contacts the side surface 115a of the protruding portion 115 of the joint motor 102. 42 abuts on the circumferential side surface 126 a of the opening 126 formed in the plate 42. For this reason, since the engaged state of the clutch engaging part 130 is maintained, the reverse rotation of the joint frame 103 is prevented.

That is, the engaging portion 120 provided between the projecting portions 115 of the joint motor 102 in the third embodiment corresponds to the first recess 36 (see FIG. 6) of the worm wheel 22 of the first embodiment described above. ing. Further, the recess 116 of the joint motor 102 corresponds to the second recess 37 (see FIG. 6) of the worm wheel 22 of the first embodiment described above.
Furthermore, the convex portion 119 of the joint frame 103 corresponds to the first convex portion 48 (see FIG. 6) of the drive plate 41 of the first embodiment described above.

  And the convex part 128 of the clutch plate 104 is corresponded to the 2nd convex part 54 (refer FIG. 6) of the clutch plate 42 of above-mentioned 1st embodiment. The opening 126 of the clutch plate 104 corresponds to the opening 53 of the clutch plate 42 of the first embodiment described above. Further, the joint housing part 110 provided in the brush holder part 100 and the clutch engaging part 130 formed on the plate body 124 of the clutch plate 104 are the clutch engaging part 55 (FIG. 6) of the first embodiment described above. Equivalent to the reference).

  Therefore, according to the third embodiment described above, in addition to the same effects as those of the first embodiment described above, it is possible to prevent reverse rotation due to the external force of the rotating shaft 7 at a location closer to the electric motor 3 than the worm reducer 92. it can. For this reason, complication of the worm reduction gear 92 can be prevented. Moreover, it becomes easy to transmit the rotational force of the rotating shaft 7 to the worm reducer 92 side, and the output efficiency of the electric motor 3 can be improved.

  In the above-described third embodiment, the clutch engaging portion 130 includes the engaging groove 131 formed in the joint housing portion 110 of the brush holder portion 100, and the engaging protrusion 132 formed on the outer peripheral edge of the clutch plate 104. The case where it was configured with was explained. However, the present invention is not limited to this, and the engagement protrusions 132 may be formed on the joint housing portion 110 of the brush holder portion 100, while the engagement grooves 131 may be formed on the outer peripheral edge of the clutch plate 104.

The present invention is not limited to the above-described embodiment, and includes various modifications made to the above-described embodiment without departing from the spirit of the present invention.
Furthermore, in the above-described embodiment, the case where the motor 1 with a reduction gear is used for a power window device of a vehicle, for example, has been described. However, the present invention is not limited to this, and can be used for various devices.

  In the first embodiment and the second embodiment described above, the coil spring 43 is used as an elastic member that biases the clutch plates 42 and 82 toward the worm wheel 22 side. In the third embodiment described above, the clutch plate The case where the coil spring 105 is used as an elastic member that biases the 104 toward the joint motor 102 has been described. However, any elastic member may be used as long as it is compressed and deformed. For example, a leaf spring or the like may be used instead of the coil springs 43 and 105.

1 Motor with reducer 2,92 Worm reducer (deceleration mechanism)
3 Electric motor 4, 94 Clutch mechanism 13 Casing 21 Worm shaft 22 Worm wheel (drive rotating body)
27 Column 27a End surface 35 Insertion hole 36 First recess (first engagement portion)
36a, 37a, 116a Bottom wall 36b, 37b, 116b Side wall 37 Second recess (second engaging portion)
37c, 116c Slanted wall 41 Drive plate (driven rotor)
42, 82, 104 Clutch plates 43, 105 Coil spring (elastic member)
44 Plate body 44a, 44b Surface 48 First convex part 53, 126 Opening (through hole)
54 2nd convex part 54a, 128a Side surface 54b, 128b Corner | angular part 55,75,130 Clutch engaging part 56,131 Engaging groove | channel 57,132 Engaging protrusion 100 Brush holder part (brush holder)
102 Joint motor (drive rotating body)
103 Joint frame (driven rotor)
110 Joint storage (storage)
115 Projection 116 Recess (Second Engagement Section)
119 Convex part (first convex part)
120 engaging portion (first engaging portion)
124 Plate body 124a Surface 128 Convex part (second convex part)

Claims (11)

A drive rotator to which the rotation of the electric motor is input;
A driven rotator that engages with the drive rotator and outputs the rotation of the electric motor;
It is disposed between the drive rotator and the driven rotator and is provided so as to be close to and away from the drive rotator along the axial direction. The drive rotator and the driven rotator An engageable clutch plate;
An elastic member that is disposed between the driven rotor and the clutch plate and biases the clutch plate toward the drive rotor;
These drive rotator, driven rotator, clutch plate, and a casing that houses the elastic member,
The clutch plate and the casing are each provided with a clutch engaging portion that can be engaged with each other in a state where the clutch plate is close to the drive rotating body,
When the driven rotator rotates before the drive rotator, the clutch plate is close to the drive rotator, the rotation of the drive rotator is prevented,
When the drive rotator rotates before the driven rotator, the clutch plate is separated from the drive rotator, and the driven rotator rotates with the drive rotator. A featured clutch mechanism. A plurality of first convex portions are provided on either one of the opposing surfaces of the drive rotator and the driven rotator, and a plurality of first convex portions that can contact the plurality of first convex portions in the circumferential direction are provided on the other side. One engaging part,
A plurality of second protrusions are provided on either one of the opposing surfaces of the drive rotator and the clutch plate, and the other is a second engagement capable of contacting the plurality of second protrusions in the circumferential direction. Set up a section,
Forming a plurality of through-holes through which the first convex portion can penetrate the clutch plate;
When the driving rotating body rotates, the second engaging portion and the second protruding portion come into contact with each other before the first engaging portion comes into contact with the first protruding portion. The clutch mechanism according to claim 1, wherein the clutch mechanism is configured to be pushed up to the driven rotor by the second engagement portion. A plurality of first protrusions are provided on the surface of the driven rotator on the drive rotator side,
While forming the plurality of through holes in the clutch plate and providing a plurality of second convex portions on the surface of the drive rotor,
3. The device according to claim 1, wherein the plurality of first engagement portions and the plurality of second engagement portions are provided on a surface of the drive rotation body on the driven rotation body side. Clutch mechanism. The first engagement portion and the second engagement portion are formed in a concave shape having a substantially U-shaped cross section,
A slant wall portion is formed at the joint portion between the side wall and the bottom wall of the second engagement portion so that the depth of the second engagement portion gradually becomes shallower toward the outer side in the circumferential direction,
4. The structure according to claim 2, wherein the second convex portion is configured to be pushed up toward the driven rotor when the corner portion of the second convex portion abuts against the inclined wall portion. The clutch mechanism described in 1. The casing is provided with a support for rotatably supporting the drive rotator, and an insertion hole through which the support can be inserted is formed in the drive rotator.
2. The clutch engaging portion is provided on an end surface of the support column on the side of the clutch plate and on a portion of the clutch plate on the side of the drive rotator corresponding to the support column, respectively. The clutch mechanism according to claim 4.   The clutch mechanism according to any one of claims 1 to 4, wherein the clutch engaging portion is provided on each of an inner peripheral surface of the casing and an outer peripheral edge of the clutch plate. The drive rotating body of the clutch mechanism according to any one of claims 1 to 6 is a worm wheel,
A worm shaft meshing with the worm wheel, and a motor with a reduction gear, wherein the electric motor is connected to the worm shaft. A clutch mechanism for connecting a rotating shaft of an electric motor provided with a brush holder and a speed reduction mechanism,
A drive rotator coupled to the rotating shaft;
A driven rotor that engages with the drive rotor and transmits the rotational force of the rotating shaft to the speed reduction mechanism;
It is disposed between the drive rotator and the driven rotator and is provided so as to be close to and away from the drive rotator along the axial direction. The drive rotator and the driven rotator An engageable clutch plate;
An elastic member that is disposed between the driven rotor and the clutch plate and biases the clutch plate toward the drive rotor;
The brush holder is provided with a storage portion that can store the drive rotating body,
Clutch engagement portions that can be engaged with each other in a state where the clutch plate is close to the drive rotating body are provided on the periphery of the storage portion and the outer peripheral side of the clutch plate,
When the driven rotator rotates before the drive rotator, the clutch plate is close to the drive rotator, the rotation of the drive rotator is prevented,
When the drive rotator rotates before the driven rotator, the clutch plate is separated from the drive rotator, and the driven rotator rotates with the drive rotator. A featured clutch mechanism. A plurality of first protrusions are provided on the surface of the driven rotator on the drive rotator side,
While forming a plurality of through holes that can penetrate the first convex portion in the clutch plate, and providing a plurality of second convex portions on the surface of the drive rotor,
The drive rotator is provided with a plurality of second engaging portions that can contact the second convex portion in the circumferential direction, and between the second engaging portions in the circumferential direction, respectively. Set to the first engaging part that can contact,
When the drive rotating body rotates, the second engaging portion and the second protruding portion come into contact with each other before the first engaging portion comes into contact with the first protruding portion. 9. The clutch mechanism according to claim 8, wherein the clutch mechanism is configured to be pushed up toward the driven rotor by the second engagement portion. The second engaging portion is formed in a concave shape having a substantially U-shaped cross section,
A slant wall portion is formed at the joint portion between the side wall and the bottom wall of the second engagement portion so that the depth of the second engagement portion gradually becomes shallower toward the outer side in the circumferential direction,
10. The clutch according to claim 9, wherein the second convex portion is configured to be pushed up toward the driven rotor when the corner portion of the second convex portion abuts against the inclined wall portion. mechanism. The clutch mechanism according to any one of claims 8 to 10,
A motor with a reduction gear including the electric motor and the reduction mechanism coupled to each other by the clutch mechanism,
The speed reduction mechanism includes a worm shaft and a worm wheel meshing with the worm shaft,
A motor with a speed reducer, wherein the worm shaft and the driven rotor are connected so as not to be relatively rotatable.

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