JP6740078B2 - Clutch mechanism and drain valve drive - Google Patents

Description

The present invention relates to a clutch mechanism that connects and disconnects the transmission of rotational torque from a rotor to a transmission train wheel and a drain valve drive device that transmits a driving force from the transmission train wheel to a drain valve drive member.

2. Description of the Related Art As a drain valve driving device for driving a drain valve of a washing machine or the like, there is a drain valve driving device provided with a transmission wheel train and a clutch mechanism between a motor as a drive source and a drain valve driving member connected to the drain valve. Patent Document 1 discloses a drain valve drive device of this type. The drain valve driving device of Patent Document 1 includes a transmission wheel train (drive wheel train) that transmits the driving force of the motor to the output shaft, and a clutch mechanism that disconnects the transmission of the rotational torque from the motor to the transmission wheel train. The clutch mechanism includes a clutch pawl formed on the rotor and a pinion (clutch pinion) formed with a clutch pawl facing the clutch pawl. A compression coil spring is arranged between the pinion and the rotor. When the pinion is pushed down to the rotor side by the clutch lever, the clutch pawls are engaged with each other and the clutch is engaged. When the clutch lever retracts from above the pinion, the clutch pawl is released by the urging force of the compression coil spring, and the clutch is disengaged.

JP 2002-242951A

In the drain valve driving device of Patent Document 1, the pinion-side clutch claw and the rotor-side clutch claw are opposed to each other. However, when the pinion is pushed down in the state where they are in the same rotation position, the tips of the clutch claws are moved to each other. Will interfere. In order to avoid such a situation, it is necessary to position and assemble the pinion at a rotational position where the tips of the clutch claws do not interfere with each other. As a positioning mechanism for positioning the pinion, an engaging portion protruding from the rotating body located on the outer peripheral side of the pinion toward the outer peripheral surface of the pinion is provided, and this engaging portion is engaged with the outer peripheral surface of the pinion. It is possible to use a configuration in which the pinion is indirectly positioned and assembled by engaging with the portion and restricting the rotation of the rotating body.

When adopting such a positioning mechanism, a gear that meshes with the pinion can be used as the rotating body that restricts the rotation of the pinion. However, when an engaging portion that projects from the rotating body located on the outer peripheral side of the pinion toward the outer peripheral surface of the pinion is provided, this engaging portion overlaps with the tooth portion of the pinion when viewed in the axial direction. After positioning and assembling, when the pinion moves in the axial direction by the biasing force of the compression coil spring, the rotating body also moves in the axial direction by the pinion. Therefore, there is a problem that the assembly position of the rotating body is displaced. For example, when the rotating body is integrally formed with the gear, the gear and the other gear are disengaged from each other.

In view of such a point, an object of the present invention is to realize a clutch mechanism in which a rotating body used as a positioning mechanism for positioning a rotor pinion is not moved in the axial direction by the rotor pinion.

In order to solve the above problems, the present invention is a clutch mechanism for connecting and disconnecting the rotation torque transmission from a rotor to a transmission train wheel, the first clutch being formed on a rotor pinion arranged coaxially with the rotor. A pawl, a second clutch pawl formed on the rotor, an urging member for urging the rotor pinion in a clutch disengagement direction in which the first clutch pawl separates from the second clutch pawl, and a reverse clutch disengagement direction. Clutch switching member for moving the rotor pinion in the positive clutch connecting direction, and a positioning mechanism for positioning the rotor pinion at a normal position which is a rotational position where the circumferential positions of the first clutch pawl and the second clutch pawl are different. And the positioning mechanism restricts rotation of the rotating body, which has an engaged portion formed on the rotor pinion, an rotator including an engaging portion that engages with the engaged portion, and A rotation restricting mechanism, the rotating body includes a relief portion provided at an angular position different from that of the engagement portion, and the rotor pinion is movable in the axial direction through the relief portion. And

According to the present invention, the rotor pinion having the clutch pawl can be positioned by the rotating body at a position where the tip of the clutch pawl does not collide. Further, since the rotating body includes the escape portion formed at an angle position different from that of the engaging portion, from the rotating position where the engaging portion engages with the rotor pinion to the rotating position where the escape portion is located on the rotor pinion side. It is possible to rotate up to. At the rotational position where the escape portion is located on the rotor pinion side, the rotor pinion can be moved in the axial direction through the escape portion. In other words, since the rotating body does not regulate the movement of the rotor pinion in the axial direction, even if the rotor pinion moves in the axial direction by the biasing member, the rotating body is not moved in the axial direction by the rotor pinion. Therefore, it is possible to reduce the risk that the rotating body is moved after the rotor pinion is assembled and the positioning of the members is lost.

In the present invention, the number of the first clutch pawls and the number of the second clutch pawls are the same, and the regular position is a position where the first clutch pawls and the second clutch pawls are alternately arranged in the circumferential direction. Is. With this configuration, since all the clutch claws are engaged, the pressing force applied to the clutch claws can be dispersed. Therefore, durability can be improved.

In the present invention, the engaging portion includes a positioning protrusion that protrudes radially outward from an outer peripheral edge of the rotating body, and the engaged portion has an outer periphery of a protruding portion that protrudes from an axial end surface of the rotor pinion. It is a positioning recess that opens in the surface, and it is preferable that the rotation locus of the positioning protrusion and the rotation locus of the positioning recess overlap each other. With this configuration, the positioning protrusion can be reliably engaged with the positioning recess, and the engagement is unlikely to come off. Therefore, the rotor pinion can be accurately positioned.

In the present invention, the outer peripheral surface of the protrusion preferably has the same diameter as the root circle of the rotor pinion. With this configuration, it is possible to avoid the interference between the gear that meshes with the rotor pinion and the protrusion.

In the present invention, it is desirable that the engaging portion is provided at at least two angular positions. With this configuration, the engaging portion and the engaged portion can be easily engaged with each other, so that there is less possibility that an erroneous assembled state will occur.

In the present invention, it is preferable that the rotating body includes a gear that constitutes the transmission train wheel, and that the gear mesh with the rotor pinion. With this configuration, the rotor pinion can be positioned using the gear of the transmission train wheel that meshes with the rotor pinion.

In the present invention, it is preferable that the relief portion has a shape that is located radially inward of the outer peripheral surface of the tooth portion of the gear. For example, it is preferable that the relief portion has a planar shape that substantially matches the tooth portion of the gear when viewed in the axial direction of the rotating body. With this configuration, at the rotational position where the relief portion faces the rotor pinion side, the tooth portion of the rotor pinion can be moved to the relief portion along the tooth groove of the gear provided on the rotating body. Therefore, the rotor does not move in the axial direction by the teeth of the rotor pinion.

In the present invention, it is preferable that the engagement portion includes an edge portion that covers a tooth groove of the gear in the axial direction, and the positioning protrusion protrudes radially outward from the edge portion. With this configuration, it is possible to form the positioning protrusion that protrudes toward the outer peripheral side from the tip circle on the rotating body.

In the present invention, the rotation restricting mechanism includes n rotation restricting surfaces formed on the rotating body, and when the number of teeth of the rotor pinion is N1 and the number of teeth of the gear is N2, N2=N1 It is desirable to satisfy the relational expression of ×n. With this configuration, the positional relationship between the angular position of the rotation restriction surface provided on the input gear and the angular positions of the engaged portion and the first clutch pawl provided on the rotor pinion during one rotation of the input gear. There is no deviation. Therefore, by restricting the rotation of the input gear, the rotor pinion can be positioned at the regular position, so that the interference between the first clutch pawl and the second clutch pawl can be avoided.

In the present invention, the rotation restriction mechanism includes a rotation restriction protrusion formed on the clutch switching member, and when the clutch switching member moves in a direction that moves the rotor pinion in the clutch connecting direction, the rotation restriction surface. It is desirable that the rotation restricting protrusion be moved to a position opposed to. With this configuration, rotation restriction can be performed using the clutch switching member. Therefore, the rotation restricting operation can be performed in conjunction with the clutch connecting operation. Further, since it is not necessary to separately provide a rotation restricting member, it is advantageous in simplifying and downsizing the clutch mechanism.

In the present invention, it is preferable that the clutch switching member is a clutch switching lever that rotates in association with rotation of the transmission train wheel. With this configuration, the clutch engagement/disengagement operation and the rotation restriction operation can be performed in conjunction with the rotation of the transmission train wheel. Moreover, the clutch engagement/disengagement operation and the rotation restriction operation can be performed in conjunction with each other by a simple mechanism.

Further, in order to solve the above problems, the drain valve driving device of the present invention is based on the above-mentioned clutch mechanism, a motor including the rotor, the transmission train wheel, and the rotation of an output gear of the transmission train wheel. And a driven drain valve driving member.

According to the present invention, the transmission of the rotational torque from the motor of the drain valve drive device to the transmission train wheel is interrupted by the clutch mechanism. The clutch mechanism is assembled so that the clutch pawls do not interfere with each other, and a reliable clutch disengagement operation can be performed. Therefore, the operation of the drain valve driving device can be stabilized.

According to the clutch mechanism of the present invention, the rotor pinion having the clutch pawl can be positioned by the rotating body at a position where the tip of the clutch pawl does not collide. Further, since the rotating body includes the escape portion formed at an angle position different from that of the engaging portion, from the rotating position where the engaging portion engages with the rotor pinion to the rotating position where the escape portion is located on the rotor pinion side. It is possible to rotate up to. At the rotational position where the escape portion is located on the rotor pinion side, the rotating body does not restrict the movement of the rotor pinion in the axial direction. It cannot be moved in any direction. Therefore, it is possible to reduce the risk that the rotating body is moved after the rotor pinion is assembled and the positioning of the members is lost.

It is a perspective view of a drain valve drive device to which the present invention is applied. It is an exploded perspective view of a drain valve drive device to which the present invention is applied. It is a top view of the drain valve drive which removed the pulley and the 2nd case. FIG. 7 is a development view of a train wheel showing a cross section connecting the shafts of the gears of the gear unit. It is explanatory drawing of a motor, a transmission train wheel, a 1st clutch mechanism, and a rotation control mechanism. It is operation|movement explanatory drawing (top view) of a 1st clutch mechanism and a rotation control mechanism. It is operation|movement explanatory drawing (side view) of a 1st clutch mechanism and a rotation control mechanism. It is operation|movement explanatory drawing (perspective view) of a positioning mechanism. It is operation|movement explanatory drawing (plan view) of a positioning mechanism. It is the perspective view which looked at a rotor and the 2nd clutch mechanism from the +Z direction side. FIG. 6 is a perspective view of the rotor and the second clutch mechanism as seen from the −Z direction side. It is a cross-sectional perspective view of a rotor and an induction ring. It is an exploded perspective view of a rotor and an induction ring. It is explanatory drawing of a fan gear and a torsion coil spring. It is an exploded perspective view of a motor and a 2nd clutch mechanism. It is a perspective view and a top view of a reverse rotation prevention mechanism.

(overall structure)
Hereinafter, a drain valve drive device according to an embodiment of the present invention will be described with reference to the drawings. 1 is a perspective view of a drain valve driving device 1 to which the present invention is applied, and FIG. 2 is an exploded perspective view of the drain valve driving device 1 to which the present invention is applied. The drain valve driving device 1 includes a wire 10 that is a drain valve driving member for driving a drain valve (not shown), a pulley 11 to which one end of the wire 10 is fixed, and a pulley 11 that rotates to wind the wire 10. The geared motor 2 for feeding is provided. The geared motor 2 includes a case 20 that rotatably holds the pulley 11, a gear unit 30 and a motor 40 that are housed in the case 20.

As shown in FIG. 2, in the case 20, a circular opening 12 is formed on the surface to which the pulley 11 is attached. A serration portion 13 a formed on the output shaft 13 of the gear unit 30 is arranged in the opening 12. The pulley 11 is assembled so as to rotate integrally with the output shaft 13 via the serration portion 13 a, and is fixed to the output shaft 13 by a fixing screw 14. The case 20 is formed with an annular rib 15 that surrounds the pulley 11 and a substantially rectangular outer peripheral rib 16 that surrounds the annular rib 15. The annular rib 15 is connected to the outer peripheral rib 16 by a radial rib. The drain valve driving device 1 is fixed to a device body such as a washing machine via a bracket 3 (see FIG. 4) fixed to the case 20. The bracket 3 is attached so as to contact the upper end surfaces of the annular rib 15 and the outer peripheral rib 16 and cover the pulley 11.

A concave portion 17 is formed on the inner peripheral surface of the annular rib 15 over a predetermined angle range, and a convex portion 18 formed on the outer peripheral surface of the pulley 11 is arranged in the concave portion 17. The angular range in which the pulley 11 rotates is restricted by the concave portion 17 and the convex portion 18. Further, the annular rib 15 is formed with an opening 19 which is partially cut away in the circumferential direction. The wire 10 is pulled out from the opening 19 to the outer peripheral side.

The drainage valve driving device 1 keeps the pulley 11 in the winding position by continuing to energize the motor 40 that is the drive source while the wire 10 is wound around the pulley 11 by a predetermined amount. As a result, the valve body of the drainage valve connected to the wire 10 is held at a position away from the drainage port. Further, the drain valve driving device 1 stops the energization of the motor 40 and releases the holding state of the pulley 11. Thereby, the wire 10 can be pulled out by the external force. For example, when the wire 10 is pulled out by an urging force such as a spring force connected to the valve body of the drainage valve, the drainage port is closed by the valve body.

In the present specification, the rotation axis direction of the pulley 11 is referred to as a third direction Z, and is orthogonal to the third direction Z 2
The directions are a first direction X and a second direction Y. The first direction X is a direction in which the wire 10 is pulled out. Further, one side of the first direction X is +X direction, the other side is −X direction, one side of the second direction Y is +Y direction, the other side is −Y direction, and one side of the third direction Z is +Z direction. , And the other side is the −Z direction. The drain valve drive device is arranged in a posture in which the +Z direction faces upward and the −Z direction faces downward, but it may be arranged in other postures. For example, it may be arranged such that the −Z direction faces upward and the +Z direction faces downward. In addition, in the present specification, the CW direction and the CCW direction are the CW direction and the CCW direction when viewed from the +Z direction side.

(Case)
The case 20 is divided into two in the third direction Z. The case 20 includes a first case 21 located on the −Z direction side and a second case 22 located on the +Z direction side. The gear unit 30 and the motor 40 are arranged between the first case 21 and the second case 22. A terminal accommodating portion 23 in which terminals for supplying power to the motor 40 are arranged is formed on the side surface of the case 20.

FIG. 3 is a plan view of the drain valve driving device 1 with the pulley 11 and the second case 22 removed. 4 is a development view of a train wheel showing a cross section connecting the shafts of the gears of the gear unit 30, and is a cross sectional view taken along the line AA of FIG. In FIGS. 3 and 4, the axes of the gears of the gear unit 30 (rotation center axis lines) are indicated by symbols B, C, D, E, F, G, H, J, and O. These axes are oriented in the third direction Z. The gear unit 30 includes a transmission train wheel 50 that transmits the rotation of the motor 40 to the output shaft 13, a first clutch mechanism 60 that disconnects the transmission of the rotational torque from the motor 40 to the transmission train wheel 50, and a transmission train wheel 50. Includes a second clutch mechanism 80 that switches between a state in which the rotational torque is transmitted and a state in which the rotational torque is not transmitted, and a reverse rotation prevention mechanism 90 that regulates the rotation direction of the motor 40.

The first clutch mechanism 60 includes a rotation restricting mechanism 70 that restricts rotation of the gears of the transmission train wheel 50. The rotation restricting mechanism 70 restricts the rotation of the transmission train wheel 50 and holds the wire 10 when an external load is applied to the wire 10. The second clutch mechanism 80 also includes a train wheel (a lock gear 84 and a speed increasing gear 85 described later) that mesh with the gears of the transmission train wheel 50, and a rotation restricting device 80A that restricts the rotation of the train wheel.

(motor)
As shown in FIG. 4, the motor 40 is arranged at the bottom of the first case 21, and the gear unit 30 is arranged on the +Z direction side of the motor 40. The motor 40 is an AC synchronous motor. The motor 40 is wound around a cup-shaped motor case 41, a support plate 42 attached to the end of the motor case 41 on the +Z direction side, a bobbin 43 arranged inside the motor case 41, and a bobbin 43. The stator coil 44 and the rotor 45 arranged on the inner peripheral side of the bobbin 43 are provided. The rotation center axis of the rotor 45 is the O axis. A through hole in which the rotor 45 is arranged is formed in the support plate 42. Further, the −Z direction end of the fixed shaft that rotatably supports the gears that form the transmission train 50 is press-fitted into the support plate 42. The +Z direction end of the fixed shaft is fixed to the second case 22 by press fitting or the like.

The rotor 45 includes a substantially cylindrical magnet 451 and a shaft portion 452 arranged on the inner peripheral side of the magnet 451. The rotor 45 is formed by insert-molding a magnet 451 made of a ferrite magnet or the like on the end portion of the shaft portion 452 in the −Z direction. An annular recess is provided between the magnet 451 and the shaft 452, and a guide ring 46, which will be described later, is disposed therein. The shaft portion 452 projects toward the +Z direction side of the guide ring 46, and a rotor gear 47 is formed on the outer peripheral surface thereof. The rotor gear 47 is a gear that transmits the rotation of the rotor 45 to the second clutch mechanism 80, as described later. A fixed shaft 453 that rotatably supports the rotor 45 is arranged at the center of the rotor 45. The fixed shaft 453 extends in the third direction Z. One end of the fixed shaft 453 is fixed to the motor case 41 by press fitting or the like, and the other end of the fixed shaft 453 is fixed to the second case 22 by press fitting or the like.

The motor case 41 and the support plate 42 are magnetic plates. The support plate 42 is formed with pole teeth bent in the −Z direction and extending from the edge of the through hole in which the rotor 45 is arranged. Further, the motor case 41 has pole teeth formed by cutting and raising the bottom of the motor case 41 and bending it in the +Z direction. The pole teeth provided on the support plate 42 and the pole teeth cut and raised from the motor case 41 are alternately arranged in the circumferential direction and face the outer peripheral surface of the magnet 451 in the radial direction. That is, the motor case 41 and the support plate 42 also serve as the stator core.

FIG. 5 is an explanatory view of the motor 40, the transmission train wheel 50, the first clutch mechanism 60, and the rotation restricting mechanism 70. FIG. 5A is an exploded perspective view seen from the +Z direction side, and FIG. 6] is a perspective view of the clutch switching lever 64 seen from the −Z direction side. A part of the outer peripheral surface of the motor case 41 is cut out in the circumferential direction, and the terminal block 48 formed on the bobbin 43 is arranged therein. A terminal 49 to which a wire for supplying power to the stator coil 44 is connected is attached to the terminal block 48. The wiring connected to the terminal 49 is taken out from the terminal accommodating portion 23 (see FIGS. 2 and 3) formed in the case 20.

(Transmission train)
The transmission train wheel 50 transmits the driving force of the motor 40 to the output shaft 13 that rotates the pulley 11. The transmission train wheel 50 includes a rotor pinion 51, a planetary gear mechanism 52, a reduction gear 53, and an output gear 54. The rotation center axis of the rotor pinion 51 is the O axis, the rotation center axis of the planetary gear mechanism 52 is the D axis, the rotation center axis of the reduction gear 53 is the C axis, and the rotation center axis of the output gear 54 is the B axis. Is. The transmission train wheel 50 transmits the driving force of the motor 40 in this order. The output shaft 13 is arranged at the center of rotation of the output gear 54 and rotates integrally with the output gear 54. Therefore, the wire 10, which is the drain valve driving member, is driven based on the rotation of the output gear 54.

The rotor pinion 51 is made of resin, and is supported by the fixed shaft 453 of the rotor 45 so as to be rotatable and movable in the axial direction (that is, the third direction Z). A first clutch mechanism 60 is provided between the rotor pinion 51 and the rotor 45. A state in which the rotor pinion 51 rotates integrally with the rotor 45 (clutch connected state) and a state in which the rotor pinion 51 does not rotate integrally with the rotor 45 (clutch disengaged state) by switching the connection/disconnection state of the first clutch mechanism 60. Is switched to.

As shown in FIG. 4, the planetary gear mechanism 52 includes a first rotating body 522 formed with a sun gear 521, a second rotating body 524 formed with an internal gear 523, a sun gear 521 and an internal gear 523. A plurality of planetary gears 525 that mesh with and a third rotating body 526 that rotatably holds the plurality of planetary gears 525 are provided. The first rotating body 522 includes a large-diameter gear portion 527 that meshes with the rotor pinion 51. That is, the large diameter gear portion 527 is an input gear to which the rotation of the rotor pinion 51 is input. Further, a large-diameter gear portion 528 that meshes with the speed increasing gear 85 of the second clutch mechanism 80 is formed on the outer peripheral surface of the second rotating body 524. As described later, the second clutch mechanism 80 is switched between a locked state in which the rotation of the speed increasing gear 85 is restricted and a idling state in which the speed increasing gear 85 idles. When the drain valve driving device 1 is activated, the second clutch mechanism 80 is locked and the rotation of the second rotating body 524 is restricted by the speed increasing gear 85.

When the rotation of the second rotating body 524 is restricted, the third rotating body 526, which is a planet carrier, rotates based on the rotation of the sun gear 521. A small-diameter gear portion 529 that meshes with the large-diameter gear portion 531 of the reduction gear 53 is formed at the −Z direction end of the third rotating body 526. That is, the planetary gear mechanism 52 is configured to transmit the rotational torque to the reduction gear 53 when the rotation of the second rotating body 524 is restricted via the speed increasing gear 85 of the second clutch mechanism 80. on the other hand,
When the speed increasing gear 85 of the second clutch mechanism 80 is switched to the idling state, even if the planetary gear 525 tries to revolve, the second rotating body 524 formed with the internal gear 523 idles, so that the planetary carrier is a planet carrier. The third rotating body 526 does not rotate. Therefore, the rotation torque is not transmitted to the reduction gear 53.

The reduction gear 53 includes a large diameter gear portion 531 that meshes with the small diameter gear portion 529 of the third rotating body 526 and a small diameter gear portion 532 that meshes with the output gear 54, and is rotatably supported by the fixed shaft 533. The reduction gear 53 reduces the rotation output from the planetary gear mechanism 52 and transmits it to the output gear 54.

(First clutch mechanism)
As shown in FIG. 5A, the first clutch mechanism 60 includes a first clutch pawl 61 formed on an end surface of the rotor pinion 51 in the −Z direction and a second clutch formed on the shaft portion 452 of the rotor 45. The claw 62, the coil spring 63 (see FIG. 7, FIG. 8) that is a biasing member that biases the rotor pinion 51 in the direction away from the shaft portion 452 (+Z direction in this embodiment), and the rotor pinion 51 A fan-shaped clutch switching lever 64, which is a clutch switching member that is pushed down to the portion 452 side (-Z direction) to switch the engagement/disengagement of the first clutch mechanism 60, is provided. The clutch switching lever 64 is arranged on the +Z direction side of the reduction gear 53 and is rotatably supported by the fixed shaft 533.

As shown in FIG. 5B, the clutch switching lever 64 is provided with a cam pin 65 and an inclined cam 67 that project in the −Z direction. The cam pin 65 is formed on the edge of the clutch switching lever 64 on the output gear 54 side, and is inserted into the cam groove 66 formed on the end surface of the output gear 54 in the +Z direction. The inclined cam 67 is a cam portion that moves the rotor pinion 51 in the −Z direction, and includes an inclined surface that extends in the circumferential direction.

6 and 7 are operation explanatory views of the first clutch mechanism and the rotation restricting mechanism. 6 is a plan view seen from the +Z direction side, and FIG. 7 is a side view. As shown in FIG. 6, the clutch switching lever 64 has a clutch disengagement position 64A (see FIG. 6C) rotated to the planetary gear mechanism 52 side and a clutch connection position 64B rotated to the output gear 54 side (FIG. 6( Rotate between a)). When the clutch switching lever 64 is located at the clutch disengagement position 64A as shown in FIG. 6(c), the first clutch mechanism 60 has the first clutch pawl 61 and the second clutch pawl 61 as shown in FIG. 7(b). The clutch 62 is separated from the clutch 62.

When the clutch switching lever 64 rotates from the clutch disengagement position 64A to the output gear 54 side (CCW direction), the inclined surface of the inclined cam 67 pushes down the rotor pinion 51 to the shaft portion 452 side (−Z direction side). When the clutch switching lever 64 moves to the clutch engagement position 64B as shown in FIG. 6A, the rotor pinion 51 has the first clutch pawl 61 and the second clutch pawl 62 as shown in FIG. 7A. Moves to the connecting position 51B where is engaged. As a result, the first clutch mechanism 60 is switched to the clutch connection state in which the rotor pinion 51 rotates integrally with the shaft portion 452.

When the clutch switching lever 64 rotates from the clutch connecting position 64B to the planetary gear mechanism 52 side (CW direction), the inclined cam 67 retreats from the position where it overlaps with the rotor pinion 51. Move in the direction. As a result, as shown in FIG. 7B, the rotor pinion 51 moves to the separated position 51C where the engagement between the first clutch claw 61 and the second clutch claw 62 is released. As a result, the first clutch mechanism 60 switches to the clutch disengaged state.

The clutch switching lever 64 rotates in conjunction with the rotation of the output gear 54. That is, the clutch switching lever 64 rotates to the output gear 54 side via the cam pin 65 and the cam groove 66 in conjunction with the rotation of the output gear 54 in the CW direction. As a result, the clutch connection operation is performed. Further, when the output gear 54 rotates in the CCW direction, the projection 55 protruding from the output gear 54 in the +Z direction presses the clutch switching lever 64 to rotate it toward the planetary gear mechanism 52 side. As a result, the clutch disengagement operation is started.

Here, in the clutch disengagement operation, the clutch switching lever 64 is pushed by the protrusion 55 in the section from the clutch connecting position 64B shown in FIG. 6A to the intermediate position 64C shown in FIG. 6B. Although rotating by pressure, the section from the intermediate position 64C shown in FIG. 6B to the clutch disengagement position 64A shown in FIG. 6C is tilted by the force of the rotor pinion 51 being pushed up by the coil spring 63. By pressing the slope of 67, the clutch switching lever 64 rotates.

The drain valve driving device 1 rotates the output gear 54 in the rotation direction when winding the wire 10 (that is, the CCW direction) to start drainage, but the position of the protrusion 55 of the output gear 54 is determined by the output gear 54. When it reaches a predetermined rotation position, the clutch switching lever 64 is pressed to rotate to the planetary gear mechanism 52 side (CW direction). Therefore, when the pulley 11 is rotated to a position near one end of the rotation range defined by the recess 17, the above-mentioned clutch disengagement operation is performed. As a result, the driving force of the motor 40 is not transmitted to the rotor pinion 51, and the operation of the transmission train wheel 50 is stopped. Therefore, excessive rotation of the pulley 11 can be prevented, and excessive winding of the wire 10 can be prevented.

(Rotation control mechanism)
As shown in FIG. 5A, the first rotating body 522 of the planetary gear mechanism 52 is provided with a protruding portion 71 that protrudes in the +Z direction from the +Z direction end surface of the large diameter gear portion 527 that is the input gear. There is. The protruding portion 71 includes a plurality of rotation restricting portions 72 that protrude in the radial direction. The plurality of rotation restricting portions 72 are arranged at equal angular intervals. A rotation restricting surface 73 facing one side in the circumferential direction (CW direction) is formed in each rotation restricting portion 72.

As shown in FIG. 5B, a rotation restricting protrusion 74 protruding in the −Z direction is formed on the edge of the clutch switching lever 64 on the planetary gear mechanism 52 side. The rotation restricting projection 74 is movable to a position where it can contact the rotation restricting surface 73 and a position retracted from the rotation restricting surface 73. As described above, when the winding operation of the wire 10 is performed and the clutch switching lever 64 rotates toward the planetary gear mechanism 52 side (CW direction) to move the rotor pinion 51 in the clutch disengagement direction (+Z direction), the clutch The rotation restricting protrusions 74 formed on the switching lever 64 enter between the rotation restricting portions 72 adjacent in the circumferential direction. As a result, a state in which the rotation restricting protrusion 74 and the rotation restricting surface 73 face each other in the circumferential direction is formed, and the rotation restricting protrusion 74 restricts the rotation of the first rotating body 522 (see FIG. 6C).

As shown in FIG. 6C, the rotation restricting protrusion 74 moves along the arc-shaped movement locus B1 around the fixed shaft 533 by the rotation of the clutch switching lever 64. The rotation restricting surface 73 has an arc shape with the same radius as the movement locus B1 of the rotation restricting protrusion 74. When the rotation restriction of the first rotating body 522 is released, the clutch switching lever 64 rotates toward the output gear 54 side (CCW direction) with the rotation restriction protrusion 74 abutting on the rotation restriction surface 73. At this time, since the rotation restricting surface 73 is substantially coincident with the movement locus B1, the force in the direction of pressing the rotation restricting surface 73 is not applied from the rotation restricting protrusion 74 to the rotation restricting surface 73. Therefore, when the rotation restriction of the first rotating body 522 is released, the rotation restricting protrusion 74 does not press the first rotating body 522 to force the rotation.

When the clutch engagement operation is performed, the rotation restricting mechanism 70 first engages at least a part of the first clutch pawl 61 and the second clutch pawl 62, and then the rotation restricting protrusion 74 rotates the first rotating body 522. It is configured to be released from regulation. That is, when the clutch switching lever 64 moves from the clutch disengagement position 64A (see FIG. 6(c)) to a predetermined rotation position on the way to the output gear 54 side (CCW direction), it is pushed down by the inclined cam 67. The tip of the first clutch pawl 61 moves to a position on the −Z direction side of the tip of the second clutch pawl 62, and a state is formed in which the tips of the first clutch pawl 61 and the second clutch pawl 62 are engaged with each other. It Then, when the clutch switching lever 64 further rotates in the CCW direction from this state, the rotation restricting protrusion 74 is completely retracted from between the rotation restricting portions 72, and the rotation restricting protrusion 74 moves to a position not facing the rotation restricting surface 73. .. When the clutch connecting operation is performed in this order, the rotational position of the rotor pinion 51 is displaced before the first clutch pawl 61 and the second clutch pawl 62 are engaged during the clutch connecting operation, and as a result, It can be avoided that the tips of the first clutch claw 61 and the second clutch claw 62 collide with each other to hinder the clutch connecting operation.

The rotation restricting mechanism 70 restricts the rotation of the first rotating body 522 at the rotation position where the rotation restricting surface 73 formed on any one of the plurality of rotation restricting portions 72 contacts the rotation restricting protrusion 74. Here, when the rotation position where the rotation of the first rotating body 522 is restricted by the rotation restricting protrusion 74 is the lock position 522A (see FIG. 6C), the rotation restricting portion 72 that contacts the rotation restricting protrusion 74 in the present embodiment. Since a plurality of (4 places) are provided, there are a plurality of (4 places) lock positions 522A.

In the planetary gear mechanism 52, since the rotation of the second rotating body 524 is restricted by the speed increasing gear 85 when the drain valve driving device 1 is activated as described above, the rotation restricting mechanism 70 restricts the rotation of the first rotating body 522. Then, the rotation of the third rotating body 526 that meshes with the reduction gear 53 is also restricted, and the locked state is achieved. Therefore, even if an external force is applied to the wire 10 and a rotational torque is applied to the transmission train wheel 50 from the output shaft 13 side, the rotational torque is not transmitted, and a load for holding the pulley 11 at a position where the wire 10 is wound by a predetermined amount. A holding state is formed. Specifically, when an external force pulling out the wire 10 is applied in a state where the wire 10 is wound by a predetermined amount, a rotational torque in the CW direction is applied to the first rotating body 522. At this time, the rotation restricting protrusion 74 contacts the rotation restricting surface 73 to restrict the rotation of the first rotating body 522 in the CW direction.

When the wire 10 is pulled out by switching to a load release state in which the wire 10 can be pulled out by an external force, the rotation restricting mechanism 70 causes the clutch switching lever 64 to move to the output gear 54 side (CCW direction) as the output gear 54 rotates. When rotated, the rotation restricting protrusion 74 retracts from between the rotation restricting portions 72. As a result, the rotation restriction mechanism 70 releases the rotation restriction of the first rotating body 522. At this time, the clutch connection operation of the first clutch mechanism 60 is performed by the rotation of the clutch switching lever 64. That is, before the operation of releasing the rotation restriction of the first rotating body 522 and the clutch connecting operation are performed, the first rotating body 522 is positioned at the lock position 522A.

(Positioning mechanism)
In the first clutch mechanism 60, the first clutch pawl 61 and the second clutch pawl 62 are circumferentially arranged to avoid interference between the pawl tips of the first clutch pawl 61 and the second clutch pawl 62 during the clutch engagement operation. The rotor pinion 51 is positioned and assembled in the rotation direction so that the rotor pinion 51 has a positional relationship in which the rotor pinion 51 is alternately arranged in the direction. Hereinafter, the rotational position of the rotor pinion 51 in which the first clutch pawl 61 and the second clutch pawl 62 are alternately arranged in the circumferential direction will be referred to as a normal position 51A (see FIG. 7). In the present embodiment, since the number of the first clutch pawls 61 is 4, there are four regular positions 51A. Although the number of the first clutch claws 61 and the number of the second clutch claws 62 are the same in this embodiment, they may not be the same. Further, in the regular position 51A, the positions of the first clutch claw 61 and the second clutch claw 62 in the circumferential direction may be different, and the first clutch claw 61 and the second clutch claw 62 are alternately arranged in the circumferential direction. It does not have to be the position. For example, at least one first clutch pawl 61 may be arranged at a position adjacent to the second clutch pawl 62 in the circumferential direction.

The second clutch pawl 62 is formed on the shaft portion 452 of the rotor 45. The rotor 45 is arranged at a magnetically stable position when the motor 40 is in the non-excited state. In this embodiment, the second clutch pawl 62 is positioned by arranging the rotor 45 at a magnetically stable position. Therefore, it is not necessary to position the second clutch pawl 62 by mechanical positioning means. When the rotor 45 is positioned at a magnetically stable position, the second clutch pawl 62 is positioned at a position corresponding to the magnetized pattern of the magnet 451. The normal position 51A of the rotor pinion 51 is a position where the second clutch claws 62 and the first clutch claws 61 are alternately arranged in the circumferential direction when the rotor 45 is positioned at a magnetically stable position. By setting such a position as the regular position 51A, when the rotor pinion 51 is assembled, the second clutch claw 62 is moved by the first clutch claw 61 and the rotor 45 is moved from a magnetically stable position. Can be avoided. Therefore, it is possible to avoid assembling the first clutch mechanism 60 in a state where it is displaced from the magnetically stable position.

The first clutch mechanism 60 includes a positioning mechanism 60A. The positioning mechanism 60A positions the rotor pinion 51 at the regular position 51A when the rotor pinion 51 is assembled. In this embodiment, there are four regular positions 51A, but the positioning mechanism 60A positions the rotor pinion 51 at either of the two positions. The positioning mechanism 60A indirectly regulates the rotation of the rotor pinion 51 via the first rotating body 522 having the large-diameter gear portion 527 that meshes with the rotor pinion 51. Therefore, the positioning mechanism 60A includes a positioning recess 68 formed in the rotor pinion 51, a first rotating body 522 having a positioning protrusion 69, and a rotation restricting mechanism 70 that restricts the rotational position of the first rotating body 522. ..

8 and 9 are operation explanatory views of the positioning mechanism 60A. FIG. 8 is a perspective view of the positioning mechanism 60A, and FIG. 9 is a plan view seen from the positioning mechanism 60A+Z direction. 8A and 9A show a state in which the rotor pinion 51 is positioned and incorporated. Further, FIGS. 8B and 9B show a state in which the rotor pinion 51 is rotated to a position where it meshes with the escape portion 692. As shown in FIG. 8, the rotor pinion 51 includes a gear portion 510 that meshes with the large-diameter gear portion 527 of the first rotating body 522, a protrusion portion 511 that protrudes in the +Z direction from an end surface of the gear portion 510 in the +Z direction, and a protrusion portion 511. The shaft portion 512 is provided so as to project in the +Z direction from the center of the portion 511. The shaft portion 512 is a portion that is pressed by the tilt cam 67 of the clutch switching lever 64 during the clutch connecting operation by the above-described first clutch mechanism 60. The outer peripheral surface of the protruding portion 511 has substantially the same diameter as the root circle of the gear portion 510. The outer peripheral surface of the protruding portion 511 may be located on the inner peripheral side of the root circle of the gear portion 510. However, it is necessary that the rotation locus of the outer peripheral surface of the protrusion 511 and the rotation locus of the tip of the positioning protrusion 69 overlap each other.

The positioning recess 68 is formed on the outer peripheral surface of the protrusion 511 and opens toward the outer peripheral side. The rotation locus of the positioning recess 68 overlaps the rotation locus of the positioning protrusion 69. A plurality of positioning recesses 68 are provided and are formed at angular positions corresponding to the first clutch pawls 61. In the present embodiment, the first clutch pawls 61 are provided at four locations at equal angular intervals. Further, the positioning recesses 68 are provided at two positions separated by 180 degrees.

The positioning protrusions 69 are provided at the end of the first rotary body 522 in the +Z direction, and are arranged at equal angular intervals over the entire circumference of the first rotary body 522. At the +Z direction end of the first rotary body 522, an edge portion 691 extending in the circumferential direction over an angular range of two tooth spaces of a large diameter gear portion 527 formed on the outer peripheral surface of the first rotary body 522. Are formed. A plurality of edge portions 691 are arranged on the outer peripheral edge of the first rotating body 522 at equal angular intervals. The positioning protrusion 69 projects outward from the center of the edge portion 691 in the circumferential direction. Therefore, the tip of the positioning protrusion 69 projects further toward the outer peripheral side than the tooth tips of the large diameter gear portion 527 and is at the same angular position as the tooth tips of the large diameter gear portion 527. Further, the two tooth spaces located on both sides in the circumferential direction of the positioning protrusion 69 overlap the edge portion 691 in the axial direction (third direction Z).

The rotor pinion 51 and the first rotating body 522 are assembled so that the positioning recess 68 and the positioning protrusion 69 are in a positional relationship of engaging with each other. Then, in the positional relationship in which the positioning recess 68 and the positioning projection 69 are engaged, the rotor pinion 51 is located at the regular position 51A that can bring the first clutch mechanism 60 into the clutch connected state. The positional relationship in which the positioning recess 68 and the positioning projection 69 engage is a positional relationship in which the positioning projection 69 faces the direction of the rotation center of the rotor pinion 51 and the positioning recess 68 faces the direction of the rotation center of the first rotating body 522. is there. The rotor pinion 51 has two such rotational positions. Then, these two rotational positions coincide with two of the four regular positions 51A.

Further, the rotor pinion 51 and the large-diameter gear portion 527 mesh with each other and rotate. Therefore, the number of the positioning projections 69 and the rotor pinion are set so that the number of teeth of the rotor pinion 51 corresponding to the angular spacing of the positioning recesses 68 is equal to the number of teeth of the large diameter gear portion 527 corresponding to the angular spacing of the positioning projections 69. The number of teeth of 51 and the number of teeth of the large-diameter gear portion 527 are determined. In this embodiment, the number of teeth N1 of the rotor pinion 51 is 12, the number of positioning recesses 68 is two, and the number of teeth N2 of the large diameter gear portion 527 is 48. Therefore, the positioning protrusions 69 are provided at eight places.

The rotation restricting mechanism 70 restricts the rotation of the first rotating body 522 when the rotating position of the first rotating body 522 is the lock position 522A (see FIG. 6C and FIG. 8A). The positioning mechanism 60A has a direction in which the positioning protrusion 69 can be engaged with the positioning recess 68 when the first rotating body 522 is positioned at the lock position 522A by the rotation restricting mechanism 70, that is, a direction of the rotation center of the rotor pinion 51. Is configured to face. In order to realize such an arrangement, the number of positioning protrusions 69 needs to be an integral multiple of the number of rotation restricting portions 72. In the present embodiment, the number of the positioning recesses 68 is 8 and the number of the rotation restricting portions 72 is 4, so that at the lock position 522A, one of the positioning protrusions 69 always projects toward the rotation center of the rotor pinion 51. To do.

With the above configuration, the positioning mechanism 60A can engage the positioning recess 68 and the positioning protrusion 69 to determine the rotational positions of the first rotating body 522 and the rotor pinion 51 and assemble them, and as a result, the first rotating body. When 522 is positioned at the lock position 522A, the rotor pinion 51 is positioned at the regular position 51A. In the present embodiment, there are four lock positions 522A, and the four lock positions 522A correspond to the regular positions 51A of the rotor pinion 51, respectively. Therefore, during the clutch engagement operation, the rotation restricting mechanism 70 positions the first rotating body 522 at the lock position 522A, and as a result, the rotor pinion 51 is positioned at the regular position 51A. Therefore, the clutch connecting operation is performed in a state where the claw tips of the first clutch claw 61 and the second clutch claw 62 do not interfere with each other.

In order to ensure that the rotor pinion 51 is positioned at the regular position 51A at the lock position 522A, the number of teeth N1 of the rotor pinion 51 and the number of teeth N2 of the large diameter gear portion 527 are the same as above. No need. For example, as long as the relational expression of N2=N1×n (n: the number of rotation restricting portions 72) is satisfied, the configuration may be different from the above. If this relational expression is satisfied, the angular position of the rotation restricting portion 72 provided on the first rotating body 522 and the first clutch pawl provided on the rotor pinion 51 during one rotation of the first rotating body 522. The positional relationship with the angular position of 61 does not shift. Therefore, by restricting the rotation of the first rotating body 522, the rotor pinion 51 can be positioned at the regular position 51A, and the interference between the first clutch pawl 61 and the second clutch pawl 62 can be avoided.

In the present embodiment, the positioning mechanism 60A has two positioning recesses 68 formed in the rotor pinion 51, and the positioning projections 69 and the positioning recesses 68 engage with each other at two of the four regular positions 51A. The number of positioning recesses 68 may be one or four. That is, the positioning recesses 68 may be positioned and number so that the rotor pinion 51 can be positioned in at least one of the four regular positions 51A. Further, the lock position 522A by the rotation restricting mechanism 70 may be a position and number corresponding to at least one of the four regular positions 51A.

For example, the rotation restricting portion 72 can be provided at two locations and the lock position 522A can be provided at two locations. As described above, in the positioning mechanism 60A of the present embodiment, the positioning protrusion 69 and the positioning recess 68 are engaged with each other at two of the four regular positions 51A. Therefore, when the lock position 522A is set to two places, when the first rotating body 522 is positioned at the lock position 522A, the positioning protrusion 69 and the positioning recess 68 engage with each other, and the rotor pinion 51 moves to the regular position 51A. It can be configured to be positioned.

(Escape part)
On the outer peripheral surface of the first rotating body 522, a clearance portion 692 is provided between the edge portions 691 adjacent to each other in the circumferential direction. The rotor pinion 51 can move in the axial direction (third direction Z) through the escape portion 692. That is, the escape portion 692 is a portion that does not regulate the movement of the rotor pinion 51 in the axial direction (third direction Z), and is arranged at an angular position different from that of the positioning protrusion 69. Specifically, the relief portion 692 is a region in which the tooth groove of the large-diameter gear portion 527 extends to the end surface of the first rotating body 522 in the +Z direction. In other words, the planar shape of the first rotating body 522 when viewed in the axial direction (third direction Z) is substantially the same as the tooth portion of the large diameter gear portion 527. The relief portion 692 may have any shape as long as it does not have a portion that overlaps with the tooth groove of the large diameter gear portion 527 in the axial direction, and does not have to have a shape that substantially matches the planar shape of the tooth portion of the large diameter gear portion 527. Good. For example, any shape may be used as long as it is located radially inward of the surface of the tooth portion of the large-diameter gear portion 527.

In this embodiment, four tooth spaces are formed in each relief portion 692. Here, the function of the escape portion 692 will be described. Since the positioning mechanism 60A is provided with the edge portions 691 on both sides in the circumferential direction of the positioning protrusion 69, in the positioning state shown in FIGS. 8A and 9A, the tooth portion and the edge portion of the rotor pinion 51. 691 overlap with each other in the third direction Z. Therefore, in this state, when the rotor pinion 51 moves in the +Z direction by the urging force of the coil spring 63, the teeth of the rotor pinion 51 are caught by the edge portion 691 and the first rotating body 522 moves in the +Z direction. As a result, the gears of the planetary gear mechanism 52 may be disengaged.

Therefore, when the rotor pinion 51 is assembled, the rotor pinion 51 is rotated by a predetermined amount after the positioning state shown in FIGS. 8A and 9A is formed. As a result, as shown in FIG. 9B, it is possible to form a state in which the escape portion 692 faces the rotor pinion 51. In the clearance portion 692, the tooth groove of the large-diameter gear portion 527 extends to the end surface of the first rotating body 522 in the +Z direction. Therefore, even if the rotor pinion 51 moves in the +Z direction by the urging force of the coil spring 63, the tooth portion of the rotor pinion 51 does not press the first rotating body 522 in the axial direction to move it, and FIG. ), only the rotor pinion 51 moves in the +Z direction. Therefore, after the rotor pinion 51 is assembled, it is possible to prevent the first rotating body 522 from moving in the +Z direction via the rotor pinion 51 and disengagement of the gears of the planetary gear mechanism 52.

In the present embodiment, since the escape portions 692 are provided one by one between the positioning protrusions 69 that are adjacent in the circumferential direction, a total of eight escape portions 692 are provided. However, the relief portion 692 may be provided in at least one place. At least one relief part 6
If there is 92, it is possible to rotate the first rotating body 522 until the escape portion 692 is directed to the rotor pinion 51, and it is possible to form a state in which the tooth portion of the rotor pinion 51 does not overlap the edge portion 691 in the axial direction. Therefore, the rotor pinion 51 can move in the axial direction (third direction Z) through the relief portion 692, and the tooth portion of the rotor pinion 51 can avoid moving by pressing the first rotating body 522.

(Second clutch mechanism)
10 and 11 are perspective views of the rotor 45 and the second clutch mechanism 80, FIG. 10 is a perspective view seen from the +Z direction side, and FIG. 11 is a perspective view seen from the −Z direction side. As shown in FIGS. 3, 10 and 11, the second clutch mechanism 80 includes a planetary gear mechanism 81, a fan gear 82 and a lock lever 83, a lock gear 84, a speed increasing gear 85, and a torsion coil spring 86. Prepare The second clutch mechanism 80 drives the lock lever 83 based on the rotation of the motor 40 to switch between a state in which the rotations of the lock gear 84 and the speed increasing gear 85 are restricted and a state in which they are not restricted. As a result, a state in which the rotational torque is transmitted from the planetary gear mechanism 52 meshing with the speed increasing gear 85 to the reduction gear 53 is switched to a state in which the rotational torque is not transmitted. Therefore, the transmission train wheel 50 can switch between a state in which the driving force is transmitted and a state in which the driving force is not transmitted.

The second clutch mechanism 80 includes a rotation restricting device 80A that restricts the rotation of the lock gear 84 and the speed increasing gear 85. The rotation restricting device 80A includes the guide ring 46, the planetary gear mechanism 81, the fan gear 82, the lock lever 83, and the torsion coil spring 86. In the rotation restricting device 80A, the lock lever 83 is a rotation restricting member that restricts the rotation of the lock gear 84 that is a rotating body, and the fan gear 82 is a rotation restricting member drive gear that rotates the lock lever 83. As shown in FIGS. 3 and 4, the rotation center axis of the planetary gear mechanism 81 is the J axis, the rotation center axis of the fan gear 82 is the H axis, and the rotation center axis of the lock lever 83 is the G axis. The rotation center axis of the lock gear 84 is the F axis, and the rotation center axis of the speed increasing gear 85 is the E axis.

As shown in FIG. 4, the planetary gear mechanism 81 includes a first rotating body 812 formed with a sun gear 811, a second rotating body 814 formed with an internal gear 813, a sun gear 811 and an internal gear 813. A plurality of planetary gears 815 meshing with the plurality of planetary gears 815 and a third rotating body 816 that rotatably holds the plurality of planetary gears 815 are provided. The first rotating body 812 includes a large-diameter gear portion 817 that meshes with the rotor gear 47 formed on the shaft portion 452 of the rotor 45. Further, on the outer peripheral surface of the second rotating body 814, a large-diameter gear portion 818 that meshes with a guide ring gear 464 formed on the guide ring 46 arranged on the outer peripheral side of the shaft portion 452 is formed. A small-diameter gear portion 819 that meshes with the fan tooth portion 823 of the fan gear 82 is provided at the −Z direction end of the third rotating body 816.

The guide ring 46 is arranged between the magnet 451 and the shaft portion 452 as described above. The guide ring 46 includes a cylindrical metal part 461 made of a non-magnetic metal such as aluminum or copper, and a resin part 462 provided on the inner peripheral side of the metal part 461. The guide ring 46 is manufactured by insert-molding the metal part 461 in resin. Bearing portions 465 and 466 are formed on the inner peripheral surface of the guide ring 46, and are rotatably supported by the shaft portion 452 by the bearing portions 465 and 466.

The guide ring 46 includes a flange portion 463 protruding to the outer peripheral side and a guide ring gear 464 provided on the +Z direction side of the flange portion 463. The collar portion 463 is formed by overlapping the metal portion 461 and the resin portion 462 (see FIG. 12), and the guide ring gear 464 is formed only by the resin portion 462. As will be described later, the guide ring gear 464 has the same diameter as the rotor gear 47 formed on the shaft portion 452. When the motor 40 is driven and the rotor 45 rotates, an eddy current is generated between the magnet 451 and the metal portion 461, a magnetic flux is generated by the eddy current, and a braking force that prevents relative rotation of the metal portion 461 with respect to the magnet 451 is generated. .. The induction ring 46 and the rotor 45 are
This braking force (brake force by eddy current) is coupled so as to rotate together.

As shown in FIGS. 10 and 11, when the rotor 45 rotates in the forward rotation direction (CW direction), the rotation of the rotor 45 is input to the first rotating body 812 that meshes with the rotor gear 47. The rotation direction of the first rotating body 812 is the CCW direction. At this time, when the braking force due to the eddy current acts on the induction ring 46, the second rotating body 814 meshing with the guiding ring 46 does not rotate, and the third rotating body 816, which is a planet carrier, rotates the same as the first rotating body 812. Rotate in the direction (CCW direction). As a result, the fan gear 82 rotates in the CW direction. The fan gear 82 is biased in the CCW direction by a torsion coil spring 86 that is a biasing member. Therefore, the fan gear 82 rotates against the biasing force of the torsion coil spring 86.

The fan gear 82 is rotatably supported by a fixed shaft 821, and the lock lever 83 is rotatably supported by a fixed shaft 831. The lock lever 83 is attached so as to rotate in the direction opposite to the fan gear 82 (CCW direction) in conjunction with the rotation of the fan gear 82 in the CW direction. Specifically, as will be described later, the engagement pin 835 formed on the lock lever 83 is engaged with the engagement recess 828 formed on the fan gear 82.

The lock gear 84 includes a large diameter portion 842 in which a plurality of protrusions 841 are formed on the outer peripheral surface at equal angular intervals, and a small diameter gear portion 843 having a diameter smaller than that of the large diameter portion 842. When the fan gear 82 rotates in the CW direction, the lock lever 83 rotates in the CCW direction and comes into contact with the outer peripheral surface of the large diameter portion 842 of the lock gear 84. As a result, the lock lever 83 and the protrusion 841 are engaged with each other, and the rotation of the lock gear 84 is restricted. When the rotation is restricted, the tip end of the first arm portion 833, which will be described later, formed on the lock lever 83 and the protrusion 841 come into contact with the outer peripheral surface of the lock gear 84 in the tangential direction.

The second clutch mechanism 80 restricts the rotation of the speed increasing gear 85 by the lock lever 83 restricting the rotation of the lock gear 84. The speed increasing gear 85 includes a large diameter gear portion 851 and a small diameter gear portion 852, and the large diameter gear portion 851 meshes with the small diameter gear portion 843 of the lock gear 84. On the other hand, the small diameter gear portion 852 of the speed increasing gear 85 meshes with the large diameter gear portion 528 formed on the second rotating body 524. As described above, when the rotation of the second rotary body 524 is restricted via the speed increasing gear 85, the transmission train wheel 50 is in a state in which the rotational torque is transmitted from the planetary gear mechanism 52 to the reduction gear 53. That is, by setting the lock gear 84 in the locked state, the transmission wheel train 50 including the gear (large diameter gear portion 851) that meshes with the wheel train including the lock gear 84 (the lock gear 84, the speed increasing gear 85) generates the driving force. Switch to the state of transmission.

Further, in the second clutch mechanism 80, when the lock lever 83 engages with the protrusion 841 of the lock gear 84, the rotation of the lock lever 83 and the fan gear 82 is restricted, and the third rotating body 816 meshed with the fan gear 82. Rotation is restricted. In the planetary gear mechanism 81, when the rotation of the third rotating body 816, which is a planet carrier, is restricted, the second rotating body 814 formed with the internal gear 813 is rotated. At this time, the rotation direction of the second rotating body 814 is opposite to the rotation direction (CCW direction) of the first rotating body 812 to which the rotation of the rotor 45 is input (CW direction). As a result, the guide ring 46 meshing with the second rotating body 814 rotates in the direction opposite to the rotation direction of the rotor 45 (CCW direction), so that the relative rotation speed of the rotor 45 and the guide ring 46 increases.

In the second clutch mechanism 80, when a rotational force is applied to the lock gear 84 from the speed increasing gear 85 side by an external force or the like due to a braking force due to an eddy current generated between the metal portion 461 of the induction ring 46 and the magnet 451, The rotational force holds the lock gear 84 and the lock lever 83 so that they are not disengaged from each other. Since the braking force due to the eddy current generated between the metal portion 461 of the induction ring 46 and the magnet 451 has a magnitude corresponding to the relative rotation speed of the metal portion 461 and the magnet 451, the second rotating body of the planetary gear mechanism 81. 814 is the first rotating body 81
When the eddy current is amplified and the braking force is amplified by rotating in the direction opposite to 2, the holding force for holding the lock gear 84 increases. Therefore, the locked state in which the rotation of the lock lever 83 is restricted can be reliably maintained.

When the motor 40 is de-energized while the lock gear 84 is locked by the lock lever 83, the second clutch mechanism 80 releases the lock state of the lock gear 84 and switches to the idling state. That is, when the rotation of the rotor 45 stops, in the planetary gear mechanism 81, the rotation of the first rotating body 812 that meshes with the rotor gear 47 stops, and the second rotating body 814 that meshes with the guide ring gear 464 becomes idle. As a result, the third rotating body 816 cannot hold the fan gear 82 against the urging force of the torsion coil spring 86, and the fan gear 82 rotates in the urging direction of the torsion coil spring 86. The rotation of the fan gear 82 causes the lock lever 83 to separate from the lock gear 84, so that the locked state of the lock gear 84 is released. As a result, the second clutch mechanism 80 switches to a state in which the lock gear 84 and the speed increasing gear 85 idle.

When the speed increasing gear 85 of the second clutch mechanism 80 is switched to the idling state, in the transmission train wheel 50, the second rotating body 524 of the planetary gear mechanism 52 is switched to the idling state. In this state, when the external load applied to the wire 10 is transmitted from the output gear 54 side to the transmission train wheel 50, the second rotating body 524 idles as the third rotating body 526 that meshes with the reduction gear 53 rotates. .. Therefore, the load holding state of the wire 10 is released, and the wire 10 can be paid out by an external load.

(Structure of rotor and induction ring)
12 is a sectional perspective view of the rotor 45 and the guide ring 46, and FIG. 13 is an exploded perspective view of the rotor 45 and the guide ring 46. Here, detailed configurations of the rotor 45 and the guide ring 46 will be described with reference to FIGS. 12 and 13. As described above, the rotor 45 is formed by insert-molding the magnet 451 made of a ferrite magnet or the like on the end portion of the shaft portion 452 in the −Z direction. The shaft portion 452 is divided into a first shaft portion 452A in which the rotor gear 47 is formed and a second shaft portion 452B in which the magnet 451 is insert-molded. The first shaft portion 452A includes a first central shaft portion 454 into which the fixed shaft 453 is inserted, and a tubular portion 455 that surrounds the outer peripheral side of the first central shaft portion 454. The tubular portion 455 and the first central shaft portion 454 extend from the lower end surface of the rotor gear 47 toward the −Z direction side. Protrusions 455a are formed at the lower end of the tubular portion 455 at two locations on the opposite side with respect to the central axis of the tubular portion 455. The second shaft portion 452B includes a substantially disc-shaped insert portion 456 and a second central shaft portion 457 that projects from the center of the insert portion 456 in the +Z direction. An annular convex portion 451a is formed on the lower end of the magnet 451 so as to project inward, and the annular convex portion 451a is inserted into the outer peripheral edge of the insert portion 456. The insert portion 456 has recesses 456a formed at two locations on the opposite side with respect to the second central shaft portion 457.

When the induction ring 46 is assembled to the rotor 45, the inner peripheral side of the magnet 451 fixed to the second shaft portion 452B with the first shaft portion 452A and the second shaft portion 452B separated as shown in FIG. The guide ring 46 is dropped into. Then, the tubular portion 455 of the first shaft portion 452A is dropped to the inner peripheral side of the guide ring 46. As a result, the rotor gear 47 having the same diameter as the guide ring gear 464 is arranged on the +Z direction side of the guide ring gear 464. When the first shaft portion 452A is dropped toward the inner peripheral side of the guide ring 46, the protrusion 455a of the first shaft portion 452A is inserted into the recess 456a of the second shaft portion 452B. As a result, the first shaft portion 452A is prevented from rotating with respect to the second shaft portion 452B, so that the first shaft portion 452A and the second shaft portion 452B are assembled so as to rotate integrally.

As described above, in the present embodiment, the first shaft portion 452A in which the rotor gear 47 is formed and the second shaft portion 452B in which the magnet 451 is insert-molded are separated, so that the rotor gear 47 is disposed on the inner peripheral side of the guide ring 46. There is no need to pass it. Therefore, it is not necessary to make the outer diameter of the rotor gear 47 smaller than the inner diameter of the guide ring 46, so that the root circle of the guide ring gear 464 can be made smaller than the outer diameter of the rotor gear 47. Therefore, in order to secure the gear ratio (reduction ratio) with the gear that meshes with the guide ring gear 464 (in the present embodiment, the large diameter gear portion 818 of the second rotating body 814), the large diameter gear portion 818 is enlarged. You don't have to. Therefore, it is not necessary to secure a space for disposing the large gear. Although the guide ring gear 464 has the same diameter as the rotor gear 47 in the present embodiment, the guide ring gear 464 does not have to have the same diameter as the rotor gear 47.

In addition, as shown in FIG. 12, positioning of the first shaft portion 452A in the axial direction (third direction Z) is performed by setting the tip surface 454a of the first central shaft portion 454 and the tip surface 457a of the second central shaft portion 457. Are brought into contact with each other. The tip end surfaces 454a and 457a of the first central shaft portion 454 and the second central shaft portion 457 abut at substantially the center of the shaft portion 452 in the axial direction. Since the detent of the first shaft portion 452A and the positioning in the axial direction are different from each other (the first central shaft portion 454 and the tubular portion 455), the first shaft portion 452A and the second shaft portion 452B can be accurately assembled. You can

(Holding structure of torsion coil spring)
As described above, in the lock lever 83 and the fan gear 82, the engagement pin 835 formed in the lock lever 83 is engaged with the engagement recess 828 formed in the fan gear 82, and they rotate in conjunction with each other. It is assembled as follows. Further, the fan gear 82 is biased in the CCW direction by the torsion coil spring 86. The fan gear 82 of the present embodiment includes a coil spring holding portion 824 capable of holding the torsion coil spring 86 so as not to fall off.

As shown in FIG. 11, the lock lever 83 includes a shaft portion 832 (second shaft portion) attached to the fixed shaft 831 and a first arm portion 833 and a second arm portion 834 projecting from the shaft portion 832 to the outer peripheral side. Prepare The first arm portion 833 and the second arm portion 834 are formed at different angular positions. The first arm portion 833 extends toward the lock gear 84, and the tip of the first arm portion 833 engages with the protrusion 841 of the lock gear 84 to restrict the rotation of the lock gear 84. The second arm portion 834 extends toward the fan gear 82 side, and an engagement pin 835 is formed at the tip of the second arm portion 834.

14 is an explanatory view of the fan gear 82 and the torsion coil spring 86, FIG. 14A is a perspective view showing a state in which the torsion coil spring 86 is removed from the fan gear 82, and FIG. 14B is a fan. It is the top view which looked at gear 82 from the +Z direction. The fan gear 82 includes a shaft portion 822 (first shaft portion) attached to the fixed shaft 821, and a fan tooth portion 823 formed at an end portion of the shaft portion 822 in the −Z direction. The shaft portion 822 includes a central portion 825 that linearly extends in the third direction Z, and a cylindrical portion 826 that surrounds the outer peripheral side of the portion of the central portion 825 on the −Z direction side. The +Z direction end of the cylindrical portion 826 is connected to the central portion 825. A projecting portion 827 that projects to the outer peripheral side is formed at the end of the cylindrical portion 826 in the +Z direction. The protrusion 827 is formed with an engagement recess 828 that is open to the outer peripheral side.

A notch 826a is formed in the cylindrical portion 826 by cutting out a part in the circumferential direction. The notch 826a includes a narrow opening groove connected to the edge of the cylindrical portion 826 in the −Z direction, and a wide portion in which the width is stepwise expanded to one side in the circumferential direction on the +Z direction side of the opening groove. By expanding the circumferential width of the notch 826a in a stepwise manner, an arm portion 829 is formed that extends in an arc shape in the circumferential direction along the edge on the −Z direction side of the cylindrical portion 826. The coil spring holding portion 824 is configured by the −Z direction side end portion of the central portion 825 and the arm portion 829.

The torsion coil spring 86 includes a coil portion 861 formed by winding a wire into a coil shape, and two spring legs 862 and 863 protruding from the coil portion 861 to the outer peripheral side. As shown in FIG. 11, the coil portion 861 is attached to the end portion of the center portion 825 of the fan gear 82 in the −Z direction. At this time, the spring leg 862 protruding from the +Z direction side end of the coil portion 861 is inserted into the notch 826a. The notch 826a extends from the edge of the cylindrical portion 826 in the −Z direction to at least the +Z direction side of the arm portion 829 (that is, the engagement position of the spring foot 862 with the arm portion 829). The position of the torsion coil spring 86 in the third direction Z is regulated by the other spring leg 863 coming into contact with the −Z direction end surface 826b (see FIG. 14A) of the cylindrical portion 826. When the coil portion 861 is rotated in the circumferential direction in this state, the state in which the spring leg 862 is engaged with the arm portion 829 is formed.

The position of the torsion coil spring 86 in the third direction Z is determined by the −Z direction end surface 826b of the cylindrical portion 826 with which the spring foot 863 abuts and the +Z direction end surface 826c of the arm portion 829 with which the spring foot 862 engages (FIG. 14). (See (a)). Therefore, these end surfaces 826b and 826c function as position restricting portions that restrict the position of the torsion coil spring 86 in the third direction Z. Further, the −Z direction side end of the central portion 825 inserted into the inner peripheral side of the coil part 861 is located at a position projecting to the −Z direction side more than the −Z direction side end face 826b of the cylindrical portion 826. Therefore, when the fan gear 82 is assembled so that the −Z direction end of the central portion 825 comes into contact with the support plate 42, a gap for disposing the spring foot 863 in the gap between the support plate 42 and the end surface 826b of the cylindrical portion 826. Is formed.

As shown in FIG. 11, one spring leg 862 of the torsion coil spring 86 abuts on the inner edge 826d (see FIG. 14A) of the wide portion of the notch 826a formed in the cylindrical portion 826. As a result, the biasing force of the torsion coil spring 86 acts on the fan gear 82. The other spring leg 863 abuts on the fixed shaft 831 arranged at the rotation center of the lock lever 83. The shaft portion 832 of the lock lever 83 is formed with a notch 836 that is notched on the side where the spring foot 863 is arranged. The spring leg 863 abuts on the outer peripheral surface of the fixed shaft 831 exposed to the outside through the notch 836. In this embodiment, the fixed shaft 831 with which the spring foot 863 abuts is a metal shaft. The fixed shaft 831 does not have to be made of metal.

FIG. 15 is an exploded perspective view of the motor 40 and the second clutch mechanism 80. When assembling the second clutch mechanism 80, as shown in FIG. 15, the rotor 45 to which the guide ring 46 is attached is attached to the center of the support plate 42, and the speed increasing gear 85 is attached. Note that the order of assembling the speed increasing gear 85 does not have to be before assembling the fan gear 82 and the lock lever 83, and may be before assembling the lock gear 84.

Then, the torsion coil spring 86 and the fan gear 82 are attached to the fixed shaft 821. At this time, as shown in FIG. 15, the torsion coil spring 86 is assembled to the coil spring holding portion 824 of the fan gear 82, and is assembled to the fixed shaft 821 in this state. As a result, the torsion coil spring 86 is assembled without dropping from the fan gear 82. At this time, the −Z direction side spring leg 863 of the torsion coil spring 86 is brought into contact with the fixed shaft 831 from the side opposite to the fan tooth portion 823. Then, the lock lever 83 is attached to the fixed shaft 831. At this time, the engagement pin 835 of the lock lever 83 is engaged with the engagement recess 828 of the fan gear 82. After that, the planetary gear mechanism 81 is assembled, and finally the lock gear 84 is assembled.

In the present embodiment, the lock lever 83, which is separate from the fan gear 82, is used as the rotation restricting member that restricts the rotation of the lock gear 84, and the lock lever 83 is moved in the CCW direction based on the rotation of the fan gear 82 in the CW direction. The lock lever 83 and the fan gear 82 may be integrally rotated. For example, the fan gear 82 may be provided with an arm portion that abuts the lock gear 84 and can engage with the protruding portion 841. However, in this case, it is necessary to separately provide a portion for contacting the spring foot 863. Alternatively, another rotation transmission member may be interposed between the fan gear 82 and the lock lever 83. Further, as the rotation restricting member, one that engages with the lock gear 84 by an operation other than rotation may be used. For example, a member that moves in the axial direction based on the rotation of the fan gear 82 to restrict the rotation of the lock gear 84 may be provided.

Further, in the present embodiment, the large-diameter gear portion 817 of the first rotating body 812 in which the sun gear 811 is formed and the rotor gear 47 mesh with each other, and the large-diameter gear portion of the second rotating body 814 in which the internal gear 813 is formed. Although the 818 meshes with the guide ring gear 464, the large diameter gear part 817 of the first rotating body 812 meshes with the guide ring gear 464 and the large diameter gear part 818 of the second rotating body 814 meshes with the rotor gear 47. You may. Even with such a configuration, since the relative rotation speed of the guide ring 46 and the rotor 45 increases when the lock state of the lock gear 84 is formed, the holding force for holding the lock gear 84 can be increased. ..

(Reverse rotation prevention mechanism 90)
16A is a perspective view of the reverse rotation preventing mechanism 90, and FIG. 16B is a plan view of the reverse rotation preventing mechanism 90. The reverse rotation preventing mechanism 90 includes a reverse rotation preventing protrusion 91 formed on the shaft portion 452 of the rotor 45, and a reverse rotation preventing lever 92 attached to an upper portion of the planetary gear mechanism 81. The reverse rotation preventing lever 92 is bent in the −Z direction from the disk portion 93 that abuts on the end surface of the first rotating body 812 of the planetary gear mechanism 81 in the +Z direction and a part of the outer peripheral edge of the disk portion 93 in the circumferential direction. The bent portion 94 and the arm portion 95 extending from the end portion of the bent portion 94 in the −Z direction toward the outer peripheral side are provided.

As described above, the shaft portion 452 of the rotor 45 is formed with the second clutch pawl 62 that meshes with the first clutch pawl 61 of the rotor pinion 51, and the reverse rotation preventing protrusion 91 is arranged on the outer peripheral side of the second clutch pawl 62. ing. The reverse rotation preventing projections 91 are convex portions that project from the end surface of the shaft portion 452 in the +Z direction, and are arranged at equal angular intervals in the circumferential direction. The reverse rotation preventing projection 91 has an arc shape and includes an end surface 96 facing the circumferential direction. The second clutch pawl 62 is arranged on the inner peripheral side of the reverse rotation prevention protrusion 91. Further, a part of the second clutch claw 62 is arranged at an angular position where the reverse rotation preventing projection 91 is not provided.

The reverse rotation prevention lever 92 and the planetary gear mechanism 81 are rotatably supported by the same fixed shaft 97. The reverse rotation preventing lever 92 rotates together with the first rotating body 812 of the planetary gear mechanism 81 by the viscosity of grease and the leaf spring 98 arranged above the reverse rotation preventing lever 92. Therefore, when the rotor 45 starts rotating, the reverse rotation preventing lever 92 rotates together with the first rotating body 812 meshing with the rotor gear 47. When the rotation direction of the rotor 45 is a predetermined forward rotation direction (CW direction), the reverse rotation prevention lever 92 rotates in the reverse direction (CCW direction), so that the arm portion 95 does not interfere with the reverse rotation prevention protrusion 91. On the other hand, when the rotation direction of the rotor 45 is the reverse rotation direction (CCW direction), the reverse rotation prevention lever 92 rotates in the CW direction, so the tip of the arm portion 95 enters between the reverse rotation prevention protrusions 91 that are adjacent in the circumferential direction. As a result, the circumferential end surface 96 of the reverse rotation preventing projection 91 and the tip of the arm portion 95 of the reverse rotation preventing lever 92 collide. Due to the impact at the time of this collision, the rotation direction of the rotor 45 that has been reversed is corrected to the normal rotation direction (CW direction).

Since the second clutch pawl 62 is arranged at an angular position between the reverse rotation preventing protrusions 91 adjacent to each other in the circumferential direction, the arm portion 95 of the reverse rotation preventing lever 92 collides with the second clutch pawl 62, and the reverse rotation preventing protrusion 91 is formed. It does not enter the inner circumference side. Therefore, at the time of reverse rotation, the circumferential end surface 96 of the reverse rotation prevention protrusion 91 and the tip end of the arm portion 95 can surely collide with each other. When the end surface 96 of the reverse rotation preventing projection 91 collides with the tip of the arm portion 95, the arm portion 95 receives a radial impact force, but the arm portion 95 is supported from the inner peripheral side by the planetary gear mechanism 81. .. Therefore, the reverse rotation prevention lever 92 is less likely to be deformed by the impact force.

(Operation at startup)
The operation at the time of starting the drainage valve drive device 1 will be described. At the time of start-up, it is assumed that the wire 10 is pulled out to the position where the drain valve is closed. When power supply to the motor 40 is started in this state, the rotor 45 starts rotating. At this time, the rotation of the rotor 45 in the reverse rotation direction is restricted by the reverse rotation prevention mechanism 90 described above, so that the rotor 45 rotates in the normal rotation direction.

Next, the rotation of the rotor 45 in the forward direction causes the rotation restricting device 80A of the second clutch mechanism 80 to switch to a state in which the lock gear 84 is locked. First, due to the output rotation of the planetary gear mechanism 81, the fan gear 82 rotates against the urging force of the torsion coil spring 86, the lock lever 83 contacts the lock gear 84 and engages with the protrusion 841, and the lock gear 84 is locked. To lock. As a result, the transmission train wheel 50 is switched to a state in which the rotational torque is transmitted. That is, in the transmission train wheel 50, the rotation of the second rotating body 524 of the planetary gear mechanism 52 is restricted by the speed increasing gear 85 of the second clutch mechanism 80, and the rotation of the rotor pinion 51 is reduced from the planetary gear mechanism 52 to the reduction gear 53. To the state of being transmitted to. Therefore, the winding operation of the wire 10 is performed by the rotation of the rotor 45 in the normal direction.

When the lock lever 83 contacts the lock gear 84 and the lock gear 84 is locked, the second clutch mechanism 80 causes the planetary gear mechanism 81 to rotate the guide ring 46 in the direction opposite to the rotation direction of the rotor 45. As a result, the relative rotation speed of the rotor 45 and the guide ring 46 is increased, the braking force due to the eddy current generated between the guide ring 46 and the magnet 451 is amplified, and the holding force for holding the lock gear 84 is increased. ..

(Operation at the end of wire winding)
In the drain valve driving device 1, when the winding of the wire 10 is completed, the clutch switching lever 64 of the first clutch mechanism 60 rotates to perform the clutch disengagement operation, and the rotation of the rotor 45 is not input to the transmission train wheel 50. Therefore, the wire 10 is not wound more than the predetermined winding amount. Further, since the rotation restricting protrusion 74 of the rotation restricting mechanism 70 restricts the rotation of the first rotating body 522 of the planetary gear mechanism 52 by the rotation of the clutch switching lever 64, the planetary gear mechanism 52 enters the locked state and the transmission train wheel 50. Cannot transmit the rotating torque. Therefore, even if an external force pulling out the wire 10 is applied, the wire 10 is in a load holding state in which it does not move. As a result, the drain valve is held in the open state.

(Operation when the load is released)
The drain valve driving device 1 shifts to a load release state in which the wire 10 can be pulled out by an external force when the motor 40 is de-energized in the load holding state. When the power supply to the motor 40 is cut off, the rotation of the rotor 45 stops. In the second clutch mechanism 80, the fan gear 82 returns to the biasing direction of the torsion coil spring 86 when the rotation of the rotor 45 is stopped, so that the lock lever 83 and the lock gear 84 are disengaged from each other and locked by the rotation restricting device 80A. The rotation restriction of the gear 84 is released. As a result, the transmission train wheel 50 is switched to a state in which the rotational torque is not transmitted. That is, in the planetary gear mechanism 52 of the transmission train wheel 50, the rotation restriction of the second rotating body 524 is released, so that the planetary gear mechanism 52 is unlocked. As a result, the transmission train wheel 50 enters a load released state in which the transmission train wheel 50 can idle. In this state, when an external force in the pulling-out direction of the wire 10 is applied, the transmission train wheel 50 idles and the wire 10 is pulled out. A brake rubber 87 is incorporated in the lock gear 84. The brake rubber 87 expands by the centrifugal force when the wire 10 is pulled out by an external force, and generates a frictional force with the lock gear 84. As a result, the drawing speed when the wire 10 is drawn is reduced. Therefore, it is possible to reduce the risk of damage caused by the wire 10 being suddenly pulled out.

When the wire 10 is pulled out to a predetermined position before reaching the maximum pull-out position, the clutch engagement operation starts based on the rotation of the output gear 54 in the CW direction. That is, the clutch groove 66 formed in the output gear 54 and the cam pin 65 provided in the clutch switching lever 64 cause the clutch switching lever 64 to rotate toward the output gear 54 and the clutch connecting operation is performed. This returns to the state in which the rotation of the rotor 45 is input to the transmission train wheel 50. Further, the rotation of the clutch switching lever 64 causes the rotation restricting mechanism 70 to rotate the first rotating body 52 of the planetary gear mechanism 52.
2 is unlocked. Therefore, the transmission train wheel 50 returns to a state in which the rotational torque can be transmitted.

(Main effects of the present invention)
As described above, the drain valve drive device 1 of the present embodiment includes the first clutch mechanism 60 that continuously disconnects the transmission of the rotational torque from the rotor 45 to the transmission train wheel 50, and the first clutch mechanism 60 is the first clutch mechanism 60. A positioning mechanism 60A for positioning the rotor pinion 51 is provided at the regular position 51A, which is a rotational position where the circumferential positions of the first clutch pawl 61 and the second clutch pawl 62 are different. Then, the positioning mechanism 60A indirectly positions the rotor pinion 51 by using the first rotating body 522 including the positioning protrusion 69 that is an engaging portion. Therefore, the rotor pinion 51 is provided with a positioning recess 68 that is an engaged portion, and is provided with a rotation restricting mechanism 70 that restricts the rotation of the first rotating body 522.

The first clutch mechanism 60 can assemble the rotor pinion 51 so that the clutch claws do not interfere with each other by engaging the positioning protrusion 69 with the positioning recess 6. Therefore, a reliable clutch engagement/disengagement operation can be performed, and the operation of the drain valve drive device 1 can be stabilized.

In this embodiment, when the rotor pinion 51 is pushed up in the +Z direction by the coil spring 63, the rotor pinion 51 does not hit the positioning protrusion 69 and the first rotating body 522 is pushed up in the same direction (+Z direction). ing. Specifically, the first rotating body 522 includes a relief portion 692 provided at an angular position different from that of the positioning protrusion 69, and the movement of the rotor pinion 51 in the axial direction (third direction Z) can be performed through the relief portion 692. It is possible.

Therefore, after the positioning protrusion 69 and the positioning recess 68 are engaged with each other to assemble the rotor pinion 51 at the regular position 51A, the first rotating body 522 and the rotor pinion 51 up to the rotational position where the escape portion 692 is located on the rotor pinion 51 side. Can be rotated. Accordingly, even if the rotor pinion 51 moves in the +Z direction by the biasing force of the coil spring 63, the rotor pinion 51 can be prevented from hitting the first rotating body 522. Therefore, it is possible to reduce the risk that the first rotating body 522 is moved in the +Z direction together with the rotor pinion 51 after the rotor pinion 51 is assembled, and the positioning of the member is lost. For example, it is possible to reduce the risk of disengagement of the gears that form the planetary gear mechanism 52 that includes the first rotating body 522.

The positioning mechanism 60A of this embodiment includes a positioning protrusion 69 that projects radially outward from the outer peripheral edge of the first rotating body 522, and the rotation locus of this positioning protrusion 69 and the rotation locus of the positioning recess 68 overlap each other. There is. Therefore, the positioning protrusion 69 can be reliably engaged with the positioning recess 68, and the engagement is unlikely to come off, so that the rotor pinion 51 can be accurately positioned.

In the present embodiment, the outer peripheral surface of the protrusion 511 in which the positioning recess 68 is formed is a cylindrical surface having the same diameter as the root circle of the gear portion 510 of the rotor pinion 51. Therefore, when the rotor pinion 51 moves in the −Z direction, it is possible to prevent the tooth portion of the large-diameter gear portion 527 that meshes with the gear portion 510 of the rotor pinion 51 from interfering with the protruding portion 511.

The positioning protrusion 69 of this embodiment is provided at at least two angular positions. Therefore, since it can be easily adjusted to the rotational position that engages with the positioning recess 68, there is little risk of being assembled in an incorrect assembly state.

In the present embodiment, the first rotating body 522 includes the large-diameter gear portion 527 provided in the planetary gear mechanism 52 that forms the transmission train wheel 50, and the large-diameter gear portion 527 meshes with the gear portion 510 of the rotor pinion 51. .. Therefore, since the rotor pinion 51 can be positioned by utilizing the large diameter gear portion 527 to which the rotation of the rotor pinion 51 is transmitted, it is not necessary to provide a rotating body separately from the transmission train wheel 50.

The escape portion 692 of the present embodiment has a shape that does not have a portion that overlaps with the tooth groove of the large diameter gear portion 527 when viewed in the third direction Z. Specifically, the clearance portion 692 has a planar shape when viewed in the axial direction (third direction Z) of the first rotating body 522 in a part of the large diameter gear portion 527 in the circumferential direction (for four tooth grooves and 3 teeth). Therefore, at the rotational position where the escape portion 692 faces the rotor pinion 51 side, it is possible to move the gear portion 510 of the rotor pinion 51 to the escape portion 692 along the tooth groove of the large diameter gear portion 527. Therefore, the first rotating body 522 is not moved in the axis +Z direction by the gear portion 510 of the rotor pinion 51.

The first rotating body 522 of the present embodiment is provided with an edge portion 691 that covers the tooth groove of the large-diameter gear portion 527 in the axial direction (third direction Z), and the positioning protrusion 69 is arranged from the center of the edge portion 691 in the circumferential direction. It projects radially outward. By providing such an edge portion 691, it is possible to form the positioning protrusion 69 on the first rotating body 522 so as to protrude from the tip circle of the large diameter gear portion 527 to the outer peripheral side.

In the positioning mechanism 60A of the present embodiment, the number of teeth N1 of the rotor pinion 51 and the number of teeth N2 of the large diameter gear portion 527 satisfy the relational expression N2=N1×n (n: number of rotation restricting portions 72). If this relational expression is satisfied, the angular position of the rotation restricting portion 72 provided on the first rotating body 522 and the positioning recess 68 provided on the rotor pinion 51 while the first rotating body 522 makes one rotation. The positional relationship with the angular position of the first clutch pawl 61 does not shift. Therefore, by restricting the rotation of the first rotating body 522, the rotor pinion 51 can be positioned at the regular position 51A, and the interference between the first clutch pawl 61 and the second clutch pawl 62 can be avoided.

In the present embodiment, the rotation restricting mechanism 70 that restricts the rotation of the first rotating body 522 uses the clutch switching lever 64 of the first clutch mechanism 60 to move the rotor pinion 51 in the clutch connecting direction (−Z direction). Rotation is regulated in conjunction with the operation. Therefore, it is not necessary to separately provide a rotation restricting member, which is advantageous in simplifying and downsizing the first clutch mechanism 60. Further, the clutch engagement/disengagement operation, the rotation restriction operation of the rotor pinion 51, and the rotation restriction release operation can be performed in conjunction with each other.

DESCRIPTION OF SYMBOLS 1... Drain valve drive device, 2... Geared motor, 3... Bracket, 10... Wire, 11... Pulley, 12... Opening, 13... Output shaft, 13a... Serration part, 14... Fixing screw, 15... Annular rib, 16... Outer peripheral ribs, 17... Recesses, 18... Projections, 19... Openings, 20... Case, 21... First case, 22... Second case, 23... Terminal accommodating section, 30... Gear unit, 40... Motor, 41... Motor case, 42... Support plate, 43... Bobbin, 44... Stator coil, 45... Rotor, 46... Induction ring, 47... Rotor gear, 48... Terminal block, 49... Terminal, 50... Transmission wheel train, 51... Rotor pinion, 51A... Regular position, 51B... Coupling position, 51C... Separation position, 52... Planetary gear mechanism, 53... Reduction gear, 54... Output gear, 55... Projection, 60... First clutch mechanism, 60A... Positioning mechanism, 61... 1 clutch claw, 62... second clutch claw, 63... coil spring, 64... clutch switching lever, 64A... clutch disengagement position, 64B... clutch connection position, 64C... midway position, 65... cam pin, 66... cam groove, 67... Inclined cam, 68... Positioning recess, 69... Positioning protrusion, 70... Rotation restricting mechanism, 71... Projection part, 72... Rotation restricting portion, 73... Rotation restricting surface, 74... Rotation restricting protrusion, 80... Second clutch mechanism, 80A ... Rotation regulating device, 81... Planetary gear mechanism, 82... Fan gear, 83... Lock lever, 84... Lock gear, 85... Accelerating gear, 86... Torsion coil spring, 87... Brake rubber, 90... Reverse rotation preventing mechanism, 91 ... reverse rotation prevention protrusion, 92... reverse rotation prevention lever, 93... disk portion, 94... bent portion, 9
5... Arm part, 96... End face, 97... Fixed shaft, 98... Leaf spring, 451... Magnet, 451a... Annular convex part, 452... Shaft part, 452A... 1st shaft part, 452B... 2nd shaft part, 453... Fixed shaft, 454... First central shaft portion, 454a... Tip surface, 455... Cylindrical portion, 455a... Projection, 456... Insert portion, 456a... Recessed portion, 457... Second central shaft portion, 457a... Tip surface, 461... Metal part, 462... Resin part, 463... Collar part, 464... Induction ring gear, 465... Bearing part, 510... Gear part, 511... Projection part, 512... Shaft part, 521... Sun gear, 522... First rotating body 522A... Lock position, 523... Internal gear, 524... Second rotating body, 525... Planetary gear, 526... Third rotating body, 527... Large diameter gear section, 528... Large diameter gear section, 529... Small diameter gear section 531... Large diameter gear portion, 532... Small diameter gear portion, 533... Fixed shaft, 691... Edge portion, 692... Relief portion, 811... Sun gear, 812... First rotating body, 813... Internal gear, 814... 2 rotors, 815... Planetary gear, 816... 3rd rotor, 817... Large diameter gear part, 818... Large diameter gear part, 819... Small diameter gear part, 821... Fixed shaft, 822... Shaft part (1st shaft part) ), 823... Fan-shaped portion, 824... Coil spring holding portion, 825... Center portion, 826... Cylindrical portion, 826a... Notch, 826b... End face (position regulating portion), 826c... End face (position regulating portion), 826d... Inner edge, 827... Projection part, 828... Engagement recessed part, 829... Arm part, 831... Fixed shaft, 832... Shaft part (2nd shaft part), 833... 1st arm part, 834... 2nd arm part, 835... Engagement pin, 836... Notch, 841... Projection portion, 842... Large diameter portion, 843... Small diameter gear portion, 851... Large diameter gear portion, 852... Small diameter gear portion, 861... Coil portion, 862, 863... Spring foot , B1... Movement locus, X... first direction, Y... second direction, Z... third direction

Claims (13)

A clutch mechanism that connects and disconnects the transmission of rotational torque from the rotor to the transmission train wheel,
A first clutch pawl formed on a rotor pinion arranged coaxially with the rotor;
A second clutch pawl formed on the rotor;
An urging member for urging the rotor pinion in a clutch disengagement direction in which the first clutch pawl is separated from the second clutch pawl;
A clutch switching member that moves the rotor pinion in a clutch connecting direction opposite to the clutch disengaging direction,
A positioning mechanism for positioning the rotor pinion at a normal position, which is a rotational position where circumferential positions of the first clutch pawl and the second clutch pawl are different,
The positioning mechanism includes an engaged portion formed on the rotor pinion, a rotating body including an engaging portion that engages with the engaged portion, and a rotation restricting mechanism that restricts rotation of the rotating body. Prepare,
The rotating body includes a relief portion provided at an angle position different from that of the engaging portion,
A clutch mechanism capable of moving the rotor pinion in an axial direction through the relief portion. The number of the first clutch pawls and the number of the second clutch pawls are the same,
The clutch mechanism according to claim 1, wherein the regular position is a position in which the first clutch claws and the second clutch claws are alternately arranged in a circumferential direction. The engagement portion includes a positioning protrusion that projects radially outward from an outer peripheral edge of the rotating body,
The engaged portion is a positioning recess that opens to the outer peripheral surface of the protruding portion that protrudes from the end surface of the rotor pinion in the axial direction,
The clutch mechanism according to claim 1 or 2, wherein a rotation locus of the positioning protrusion and a rotation locus of the positioning recess overlap each other. The clutch mechanism according to claim 3, wherein an outer peripheral surface of the protrusion has the same diameter as a root circle of the rotor pinion. The clutch mechanism according to any one of claims 1 to 4, wherein the engagement portion is provided at at least two angular positions. The clutch mechanism according to any one of claims 1 to 5, wherein the rotating body includes a gear that forms the transmission wheel train, and the gear meshes with the rotor pinion. The clutch mechanism according to claim 6, wherein the relief portion has a shape that is located radially inward of a surface of the tooth portion of the gear. 7. The clutch mechanism according to claim 6, wherein the relief portion has a planar shape that is substantially the same as the tooth portion of the gear when viewed in the axial direction of the rotating body. The engagement portion includes an edge portion that covers the tooth groove of the gear in the axial direction,
9. The clutch mechanism according to claim 6, wherein the positioning protrusion projects radially outward from the edge portion. The rotation regulating mechanism includes n rotation regulating surfaces formed on the rotating body,
When the number of teeth of the rotor pinion is N1 and the number of teeth of the gear is N2,
10. The clutch mechanism according to claim 6, wherein a relational expression N2=N1×n is satisfied. The rotation restricting mechanism includes a rotation restricting protrusion formed on the clutch switching member,
11. The clutch according to claim 10, wherein when the clutch switching member moves in a direction that moves the rotor pinion in the clutch connecting direction, the rotation restricting protrusion moves to a position facing the rotation restricting surface. mechanism. The clutch mechanism according to any one of claims 1 to 11, wherein the clutch switching member is a clutch switching lever that rotates in association with rotation of the transmission train wheel. A clutch mechanism according to any one of claims 1 to 12,
A motor including the rotor,
The transmission train wheel;
A drainage valve drive member that is driven based on rotation of an output gear of the transmission train wheel.

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