JP2017155902A - Clutch mechanism and drain valve driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrict rotation of a rotor such as a gear by a rotation restricting mechanism, and to reduce a risk of forcibly rotating the rotor in releasing the restriction of rotation.SOLUTION: A drain valve driving device 1 includes a first clutch mechanism 60 for connecting and disconnecting transmission of rotary torque from a motor 40 to a transmission wheel train 50. The first clutch mechanism 60 includes a rotation restricting mechanism 70 for indirectly restricting rotation of a rotor pinion 51 through a first rotor 522 engaged with the rotor pinion 51. The rotation restricting mechanism 70 includes a rotation restriction face 73 disposed on the first rotor 522, and a rotation restricting projection 74 as a moving portion kept into contact with the rotation restriction face 73 and restricting the rotation of the first rotor 522, and the rotation restriction face 73 has the circular arc-shape along a moving locus B of the rotation restricting projection 74.SELECTED DRAWING: Figure 8

Description

  The present invention relates to a clutch mechanism and a drain valve driving device for interrupting transmission of rotational torque from a rotor to a transmission wheel train.

  As a drain valve driving device for driving a drain valve of a washing machine or the like, there is one provided with a clutch mechanism between a motor as a driving source and a driven member connected to the drain valve. When the clutch mechanism is in the connected state, the driving force of the motor is transmitted to the driving member, and the drain valve operates. Further, the drive member is held in a state where the clutch mechanism is connected, and the drain valve and the drive member are prevented from moving due to an external load applied to the drain valve. On the other hand, when the clutch mechanism is in a disconnected state, the drive member can be operated by an external load applied to the drain valve. Therefore, the drain valve can be returned to the original position by an external load.

  Patent Document 1 discloses a geared motor used in this type of drain valve driving device. The geared motor of Patent Document 1 includes a drive wheel train that transmits the driving force of the motor to the output shaft, and a clutch mechanism that intermittently transmits the rotational torque from the motor to the drive wheel train. The clutch mechanism includes a clutch pawl formed on the rotor and a pinion (clutch pinion) formed with a clutch pawl opposed to the clutch pawl. A compression coil spring is disposed between the pinion and the rotor. When the pinion is pushed down to the rotor side by the clutch lever, the clutch pawl is engaged and the clutch is engaged. When the clutch lever is retracted from above the pinion, the clutch pawl is released by the biasing force of the compression coil spring, and the clutch is disengaged.

JP 2002-242951 A

  In the geared motor of Patent Literature 1, when the clutch is disengaged, the rotation restricting shape provided on the clutch lever is engaged with the axial end of the pinion to restrict the rotation of the pinion. As a result, the rotation of the transmission wheel train meshing with the pinion is restricted, so that a load holding state in which the driving member does not move due to an external force is formed.

  However, when the rotation restricting shape of the clutch lever is engaged with the end of the pinion in the axial direction to restrict the transmission of the rotational torque, the rotation restricting portion is likely to come off because the pinion itself is small. Therefore, it has been proposed to indirectly restrict the rotation by engaging the rotation restricting shape of the clutch lever with a large gear meshing with the pinion. Specifically, it has been proposed to provide a rotation restricting surface that contacts the rotation restricting shape of the clutch lever on the gear of the transmission wheel train that meshes with the pinion.

  Here, when providing a rotation restriction surface that contacts the rotation restriction shape of the clutch lever on the gear of the transmission wheel train, the rotation restriction surface is pressed by the rotation restriction shape when the rotation restriction is released, and the gear is forced to rotate. However, such a rotation restricting shape requires a force for forcibly rotating the gear, and therefore has a problem that a load when releasing the rotation restriction is large. In addition, if the gear engaged with the pinion is forcibly rotated when releasing the rotation restriction, the rotation position of the clutch pawl formed on the pinion shifts, so the clutch pawl tips collide with each other during the clutch connection operation. There is a possibility that the claws cannot be engaged.

  In view of these points, an object of the present invention is to rotate a rotating body such as a gear by a rotation restricting protrusion formed on a clutch switching member in a clutch mechanism that interrupts transmission of rotational torque from a rotor to a transmission wheel train. It is intended to reduce the possibility that the rotating body is forced to rotate when the regulation is performed and the rotation regulation is released.

  In order to solve the above-mentioned problems, the present invention provides a clutch mechanism that interrupts transmission of rotational torque from a rotor to a transmission wheel train, and is a first clutch 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 is separated from the second clutch pawl, and opposite to the clutch disengagement direction Positioning for positioning the rotor pinion at a normal position, which is a rotational position in which the first clutch pawl and the second clutch pawl are alternately arranged in the circumferential direction; And the positioning mechanism includes a rotation restricting mechanism that restricts rotation of the rotating body that engages with the rotor pinion, and the rotation restricting machine Comprises a rotation restricting surface formed on the rotating body, a moving part movable to a position capable of contacting the rotation restricting surface and a position retracted from the rotation restricting surface, and the rotation restricting surface includes the movement It is the shape which follows the movement locus | trajectory of a part.

  According to the present invention, the rotation restricting mechanism that indirectly restricts the rotation of the rotor pinion through the rotating body engaged with the rotor pinion is provided. The rotation restricting mechanism includes a rotation restricting surface provided on the rotating body, and a moving unit that contacts the rotation restricting surface and restricts the rotation of the rotating member, and the shape of the rotation restricting surface is a movement locus of the moving unit. It has a shape along. If it does in this way, when a movement part moves along a rotation control surface, it can avoid that a rotation control surface is pressed by a movement part. Therefore, there is little possibility that the rotating body is forcibly rotated when releasing the rotation restriction. Therefore, it is possible to reduce the load when releasing the rotation restriction. Further, the possibility of the rotational position of the rotating body shifting when releasing the rotation restriction can be reduced. Therefore, a stable clutch disengagement operation can be performed.

  In the present invention, it is desirable that the moving part is a rotation restricting protrusion formed on the clutch switching member. If it does in this way, rotation control can be performed using a clutch switching member. Therefore, the rotation restricting operation can be performed in conjunction with the clutch connecting operation. Further, it is not necessary to provide a separate rotation restricting member, which is advantageous for simplification and miniaturization of the clutch mechanism.

  In the present invention, the clutch switching member may be a clutch switching lever that rotates in conjunction with the rotation of the transmission wheel train, and the rotation restricting surface may have an arc shape that follows the movement locus of the moving unit. . In this way, the clutch disengagement operation and the rotation restricting operation can be performed in conjunction with the rotation of the transmission wheel train. Further, the clutch disengagement operation and the rotation restricting operation can be performed in conjunction with each other by a simple mechanism.

  In the present invention, when the clutch switching lever rotates in a direction to move the rotor pinion in the clutch engagement direction, the rotor pinion is moved to a position where at least a part of the first clutch pawl and the second clutch pawl are engaged. It is desirable that the rotation restricting protrusion moves to a position not facing the rotation restricting surface after the movement. If it does in this way, before a clutch connection, the rotation regulation of a rotor pinion will be cancelled | released, and there is little possibility that the rotation position of a rotor pinion will shift | deviate. Therefore, a stable clutch connection operation can be performed.

In the present invention, it is preferable that the rotating body includes a gear of the transmission wheel train, and the gear meshes with the rotor pinion. If it does in this way, rotation control of a rotor pinion can be performed using the gear of a transmission wheel train. Therefore, there is no need to provide a separate rotating body, which is advantageous for simplification and miniaturization of the clutch mechanism.

  In order to solve the above problems, the drain valve driving device of the present invention is based on the rotation of the clutch mechanism, the motor including the rotor, the transmission wheel train, and the output gear of the transmission wheel train. A drain valve driving member to be driven.

  According to the present invention, transmission of rotational torque from the motor of the drain valve driving device to the transmission wheel train can be interrupted by the clutch mechanism. Since the clutch mechanism can perform a stable clutch disengagement operation, the operation of the drain valve driving device can be stabilized.

  According to the clutch mechanism of the present invention, as a rotation restricting mechanism for indirectly restricting the rotation of the rotor pinion via the rotating member engaged with the rotor pinion, the rotation restricting surface provided on the rotating member and the rotation restricting surface are provided. The moving part which contact | abuts is provided, and the shape of a rotation control surface is a shape which follows the movement locus | trajectory of a moving part. Therefore, when releasing the rotation restriction, there is little possibility that the rotation restriction surface is pressed by the moving portion and the rotating body is forcibly rotated. Therefore, it is possible to reduce the load when releasing the rotation restriction. Further, the possibility of the rotational position of the rotating body shifting when releasing the rotation restriction can be reduced. Therefore, a stable clutch disengagement operation can be performed. Further, the operation of the drain valve driving device using this clutch mechanism can be stabilized.

It is a perspective view of the drain valve drive device to which the present invention is applied. It is a disassembled perspective view of the drain valve drive device to which the present invention is applied. It is a top view of a gear unit and a 1st case. FIG. 4 is a development view of a train wheel showing a cross-section connecting shafts of gears of a gear unit. It is the disassembled perspective view which looked at the motor, the transmission wheel train, the 1st clutch mechanism, and the rotation control mechanism from the + Z direction side. It is the disassembled perspective view which looked at the motor, the transmission wheel train, the 1st clutch mechanism, and the rotation control mechanism from the -Z direction side. It is a side view of a rotor, a 1st clutch mechanism, and a planetary gear mechanism. It is explanatory drawing which shows the top view of a rotation control mechanism, and the movement locus | trajectory of a rotation control protrusion. It is the perspective view which looked at the rotor, the 2nd clutch mechanism, and the reverse rotation prevention mechanism from the + Z direction side. It is the perspective view which looked at the rotor, the 2nd clutch mechanism, and the reverse rotation prevention mechanism from the -Z direction side. It is sectional drawing of a rotor and a planetary gear mechanism. It is the top view and side view of a reverse rotation prevention mechanism.

(overall structure)
Hereinafter, a drain valve driving device according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a perspective view of a drain valve driving device to which the present invention is applied, and FIG. 2 is an exploded perspective view of the drain valve driving device to which the present invention is applied. The drain valve driving device 1 includes a slider 10 that is a drain valve driving member for driving the drain valve, a case 20 that slidably holds the slider 10, and a gear unit 2 that is accommodated in the case 20. As shown in FIG. 2, a rack 11 is formed on the side surface of the slider 10, and an output pinion 12 that meshes with the rack 11 is disposed at a predetermined position of the case 20. The drain valve driving device 1 rotates the output pinion 12 by the gear unit 2 to move the slider 10 in the linear direction.

  The slider 10 moves to a retracted position 10 </ b> A (see FIGS. 1 and 2) drawn into the case 20 except the tip, and a projecting position protruding from the case 20 by moving in the + X direction from the retracted position 10 </ b> A. The drain valve driving device 1 drives a drain valve (not shown) via the slider 10. When the slider 10 is located at the protruding position, the drain port is closed by the drain valve. On the other hand, when the slider 10 is drawn to the case 20 side, the drain valve is separated from the drain port and drainage is started. In the state where the slider 10 is pulled to the pulling position 10A, the drain valve driving device 1 continues to energize the motor 40 (see FIG. 4) that is the driving source, and holds the slider 10 at the pulling position 10A. Further, the drain valve driving device 1 stops energization of the motor 40 and releases the holding state of the slider 10. Thereby, the slider 10 can be returned to the protruding position by an external force. For example, the slider 10 is returned to the protruding position by a spring load connected to the valve body of the drain valve and biased in the drain port closing direction, and the drain port is closed by the drain valve.

  In this specification, the direction in which the slider 10 moves is defined as a first direction X, and the two directions orthogonal to the first direction X are defined as a second direction Y and a third direction Z. The second direction Y and the third direction Z are orthogonal to each other. The third direction Z is the rotational axis direction of the output pinion 12 that meshes with the rack 11 provided in the slider 10. Also, one side of the first direction X is the + X direction, the other side is the -X direction, one side of the second direction Y is the + Y direction, the other side is the -Y direction, and one side of the third direction Z is the + Z direction. The other side is the -Z direction. In this specification, the CW direction and the CCW direction are the CW direction and the CCW direction when the gear unit 2 is viewed from the + Z direction side.

  The case 20 includes a first case 21, a second case 22, and a third case 23. The first case 21 includes a bottom plate 211 located on the −Z direction side of the gear unit 2 and a side plate 212 that rises in the + Z direction from the outer peripheral edge of the bottom plate 211. The second case 22 includes a bottom plate 211, an upper plate 221 facing the third direction Z, and a side plate 222 extending from the outer peripheral edge of the upper plate 221 in the −Z direction. The first case 21 and the second case 22 constitute an exterior case of the drain valve driving device 1. The side plates 212 and 222 constitute the side surface of the exterior case.

  The space between the first case 21 and the second case 22 is partitioned in the third direction Z by the third case 23. The gear unit 2 is disposed between the first case 21 and the third case 23, and the slider 10 and the output pinion 12 are disposed between the second case 22 and the third case 23. An opening 24 is formed on the side surface of the case 20 in the + X direction to project one end of the slider 10 to the outside. The opening 24 includes a first recess 241 formed in the side plate 212 of the first case 21 and a second recess 242 formed in the side plate 222 of the second case 22. In the opening 24, the tip in the + X direction of the groove-shaped guide portion 30 formed in the third case 23 is disposed. The slider 10 slides in the first direction X along the guide portion 30.

  FIG. 3 is a plan view of the gear unit 2 and the first case 21. FIG. 4 is a development of a train wheel showing a section connecting the shafts of the gears of the gear unit 2. 3 and 4, the gear shaft (rotation center axis) of the gear unit 2 is denoted by reference symbols A, B, C, D, E, F, G, H, and O. These axes point in the third direction Z. The gear unit 2 includes a motor 40, a transmission wheel train 50 that transmits the rotation of the motor 40 to the output pinion 12, and a first clutch mechanism 60 that interrupts transmission of rotational torque from the motor 40 to the transmission wheel train 50; The transmission wheel train 50 includes a second clutch mechanism 80 that switches between a state in which rotational torque is transmitted and a state in which rotational torque is not transmitted, and a reverse rotation prevention mechanism 90 that regulates the rotational direction of the motor 40. The first clutch mechanism 60 includes a rotation restriction mechanism 70 that restricts the rotation of the gears of the transmission wheel train 50. The rotation restriction mechanism 70 holds the slider 10 by restricting the rotation of the transmission wheel train 50 when an external load is applied to the slider 10.

(motor)
As shown in FIG. 4, the motor 40 that is the drive source of the drain valve driving device 1 is disposed at the bottom of the first case 21. The motor 40 is an AC synchronous motor. The motor 40 is wound around the bobbin 43, 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 disposed inside the motor case 41, and the bobbin 43. A stator coil 44 and a rotor 45 disposed on the inner peripheral side of the bobbin 43 are provided. The rotation center axis of the rotor 45 is the O axis. The support plate 42 has a through hole in which the rotor 45 is disposed. Further, the end portion in the −Z direction of the fixed shaft that rotatably supports the gears constituting the transmission wheel train 50 is press-fitted into the support plate 42. The + Z direction end of the fixed shaft is fixed to the third case 23 by press fitting or the like.

  The rotor 45 includes a substantially cylindrical magnet 451 and a shaft portion 452 disposed 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 at the end 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 described later is disposed here. The shaft portion 452 protrudes toward the + Z direction side of the guide ring 46, and a rotor gear 47 (see FIG. 11) 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 will be described later. A fixed shaft 453 that rotatably supports the rotor 45 is disposed 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 third case 23 by press fitting or the like.

  The motor case 41 and the support plate 42 are made of a magnetic plate. The support plate 42 is formed with pole teeth that bend and extend in the −Z direction from the edge of the through hole in which the rotor 45 is disposed. 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 circumferential surface of the magnet 451 in the radial direction. That is, the motor case 41 and the support plate 42 also serve as a stator core. Further, a part of the outer circumferential surface of the motor case 41 is cut away in the circumferential direction, and a terminal block 48 (see FIG. 3) formed on the bobbin 43 is disposed here. The terminal block 48 is connected to a wiring for supplying power to the stator coil 44. The wiring connected to the terminal block 48 is taken out from the wiring take-out portion 25 formed in the case 20.

(Transmission train)
The transmission wheel train 50 transmits the driving force of the motor 40 to the output pinion 12 of the rack-pinion mechanism that drives the slider 10. As shown in FIGS. 3 and 4, the transmission wheel train 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 C axis, the rotation center axis of the reduction gear 53 is the B axis, and the rotation center axis of the output gear 54 is the A axis. It is. The transmission wheel train 50 transmits the driving force of the motor 40 in this order. The output pinion 12 is attached to the end of the output gear 54 in the Z direction and rotates integrally with the output gear 54. Accordingly, the slider 10 as the drain valve driving member is driven based on the rotation of the output gear 54.

  The rotor pinion 51 is formed of resin, and is supported by a 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. By switching the connection state of the first clutch mechanism 60, the rotor pinion 51 rotates integrally with the shaft 452 of the rotor 45 (clutch connection state), and the rotor pinion 51 does not rotate integrally with the shaft 452. (Clutch disengaged state).

The planetary gear mechanism 52 includes a first rotating body 522 in which the sun gear 521 is formed, a second rotating body 524 in which the internal gear 523 is formed, and a plurality of planetary gears 525 that mesh with the sun gear 521 and the internal gear 523. And a third rotating body 526 that rotatably holds the plurality of planetary gears 525. 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. 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 will be 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 an idle state in which the speed increasing gear 85 runs idle. When the drain valve driving device 1 is started, 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 that 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 end portion of the third rotating body 526 in the −Z direction. That is, the planetary gear mechanism 52 is configured to transmit 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 having the internal gear 523 is idling, so that the planet carrier The third rotating body 526 is not rotated. Accordingly, the rotational 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)
5 and 6 are exploded perspective views of the motor 40, the transmission wheel train 50, the first clutch mechanism 60, and the rotation restricting mechanism 70. FIG. 5 is an exploded perspective view seen from the + Z direction side, and FIG. It is the disassembled perspective view seen from the direction side. As shown in FIGS. 5 and 6, the first clutch mechanism 60 includes a first clutch pawl 61 formed on the 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 that is a biasing member that biases the rotor pinion 51 in the direction away from the shaft portion 452 (in the + Z direction in this embodiment), and the rotor pinion 51 on the shaft portion 452 side (−Z direction) A fan-shaped clutch switching lever 64 which is a clutch switching member which is pushed down to switch the connection of the first clutch mechanism 60. The clutch switching lever 64 is disposed on the + Z direction side of the reduction gear 53 and is rotatably supported by the fixed shaft 533. As shown in FIG. 6, the clutch switching lever 64 is formed with a cam pin 65 and an inclined cam 67 protruding 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 a 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 extending in the circumferential direction.

  7A and 7B are side views of the rotor 45, the first clutch mechanism 60, and the planetary gear mechanism 52. FIG. 7A shows a clutch disengaged state, and FIG. 7B shows a clutch connected state. As shown in FIG. 3, when the clutch switching lever 64 is located at the clutch disengagement position 64A on the planetary gear mechanism 52 side, as shown in FIG. 7 (a), the first clutch mechanism 60 has the first clutch pawl 61. And the second clutch pawl 62 are separated from each other. In this embodiment, the direction in which the first clutch pawl 61 moves away from the second clutch pawl 62 (+ Z direction) is the clutch disengagement direction, and the direction in which the first clutch pawl 61 approaches the second clutch pawl 62 (−Z direction) is the clutch. Connection direction.

When the clutch switching lever 64 rotates to the output gear 54 side (CCW direction), the inclined cam 67
Thus, the rotor pinion 51 is pushed down toward the shaft portion 452 (−Z direction side). Accordingly, as shown in FIG. 7B, the rotor pinion 51 moves to the connection position 51 </ b> B where the first clutch pawl 61 and the second clutch pawl 62 are engaged. As a result, the first clutch mechanism 60 switches to a clutch connection state in which the rotor pinion 51 rotates integrally with the shaft portion 452.

  When the clutch switching lever 64 rotates to the planetary gear mechanism 52 side (CW direction) from the clutch connected state, the inclined cam 67 is retracted from the position where it overlaps the rotor pinion 51, so that the rotor pinion 51 is moved in the + Z direction by the biasing force of the coil spring 63. Move to. Thereby, as shown in FIG. 7A, the rotor pinion 51 moves to the separation position 51C where the engagement between the first clutch pawl 61 and the second clutch pawl 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 toward the output gear 54 via the cam pin 65 and the cam groove 66 in conjunction with the rotation of the output gear 54 in the CW direction. Further, when the output gear 54 rotates in the CCW direction, the projection 55 protruding in the + Z direction from the output gear 54 presses the clutch switching lever 64 and rotates it toward the planetary gear mechanism 52 side. The drain valve driving device 1 starts drainage by rotating the output gear 54 in the rotation direction (that is, the CCW direction) when the slider 10 is pulled to the case 20 side, and the position of the protrusion 55 of the output gear 54 is the output. The clutch switching lever 64 is set so as to rotate toward the planetary gear mechanism 52 (in the CW direction) when the gear 54 reaches a predetermined rotational position. For this reason, when the slider 10 is retracted to the vicinity of the retracted position 10A, the above-described clutch disengaging 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 wheel train 50 is stopped. Therefore, the slider 10 can be prevented from being pulled in beyond the predetermined pulling position 10A, and excessive pulling of the slider 10 can be prevented.

(Rotation restriction mechanism)
As shown in FIGS. 5 and 6, the first rotating body 522 of the planetary gear mechanism 52 is formed with a protruding portion 71 protruding in the + Z direction from the end surface in the + Z direction of the large-diameter gear portion 527 that is an input gear. Yes. 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 equiangular intervals. Each rotation restricting portion 72 is formed with a rotation restricting surface 73 that faces one side in the circumferential direction (CW direction).

  As shown in FIGS. 5 and 6, 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 protrusion 74 is a moving part that can move 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 slider 10 is retracted, the clutch switching lever 64 rotates to the planetary gear mechanism 52 side (CW direction) to move the rotor pinion 51 in the clutch disengagement direction (+ Z direction). The rotation restricting protrusion 74 formed on the lever 64 enters between the rotation restricting portions 72 adjacent in the circumferential direction. Thus, a state is formed in which the rotation restricting protrusion 74 and the rotation restricting surface 73 are opposed to each other in the circumferential direction, and the rotation restricting protrusion 74 restricts the rotation of the first rotating body 522.

FIG. 8A is a plan view of the rotation restricting mechanism 70, and FIG. 8B is an explanatory diagram showing a movement locus of the rotation restricting protrusion 74. As shown in FIG. 8B, the rotation restricting projection 74 moves along a movement locus B <b> 1 on an arc centered on the fixed shaft 533 by the rotation of the clutch switching lever 64. The rotation restricting surface 73 has an arc shape having the same radius as the movement locus B1 of the rotation restricting protrusion 74. Therefore, when the first rotating body 522 is positioned at a position where the rotation restricting protrusion 74 and the rotation restricting surface 73 are in contact with each other, the rotation restricting surface 73 has a shape along the movement locus B1. First rotating body 522
When the rotation restriction is released, the clutch switching lever 64 rotates to the output gear 54 side (CCW direction) with the rotation restriction protrusion 74 in contact with the rotation restriction surface 73. At this time, since the rotation restricting surface 73 substantially coincides with the movement locus B <b> 1, no force is applied from the rotation restricting projection 74 to the rotation restricting surface 73 in the direction of pressing the rotation restricting surface 73. That is, the rotation restricting mechanism 70 is configured such that the rotation restricting protrusion 74 does not press the first rotating body 522 to forcibly rotate when the rotation restriction of the first rotating body 522 is released.

  When the clutch engaging 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 rotates the first rotating body 522 by the rotation restricting projection 74. It is configured so that the restriction is released. That is, when the clutch switching lever 64 moves from the clutch disengagement position 64A (see FIGS. 3 and 8A) to a predetermined rotation position in the middle of rotating to the output gear 54 side (CCW direction), it is pushed down by the inclined cam 67. The leading end of the first clutch pawl 61 is moved to a position on the −Z direction side of the leading end of the second clutch pawl 62 and the leading ends of the first clutch pawl 61 and the second clutch pawl 62 are engaged with each other. Is formed. If the clutch switching lever 64 further rotates in the CCW direction from this state, the rotation restricting projection 74 is completely retracted from between the rotation restricting portions 72 and moves to a position where the rotation restricting projection 74 does not face the rotation restricting surface 73. . If the clutch engagement operation is performed in this order, the rotational position of the rotor pinion 51 is shifted before the first clutch pawl 61 and the second clutch pawl 62 are engaged during the clutch engagement operation. It can avoid that the front-end | tips of the 1st clutch nail | claw 61 and the 2nd clutch nail | claw 62 collide, and a clutch connection operation | movement is prevented.

  The rotation restricting mechanism 70 restricts the rotation of the first rotating body 522 at a 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, if the rotation position at which the rotation of the first rotating body 522 is restricted by the rotation restricting protrusion 74 is the lock position 522A (see FIGS. 5 and 8), in this embodiment, the rotation restricting portion 72 that contacts the rotation restricting protrusion 74. Since there are a plurality (four places), there are a plurality (four places) of 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 started as described above, the rotation restricting mechanism 70 restricts the rotation of the first rotating body 522. If it does, rotation of the 3rd rotary body 526 which meshes with the reduction gear 53 will also be controlled, and it will be in a locked state. Therefore, even if an external force is applied to the slider 10 and a rotational torque is applied to the transmission wheel train 50 from the output pinion 12 side, the rotational torque is not transmitted, and a load holding state in which the slider 10 is held at the retracted position 10A is formed. . Specifically, when an external force that pulls the slider 10 in the + X direction is applied in a state where the slider 10 is pulled to the pulling position 10 </ b> A, a rotational torque in the CW direction is applied to the first rotating body 522. At this time, the rotation restricting protrusion 74 abuts against the rotation restricting surface 73 and restricts the rotation of the first rotating body 522 in the CW direction.

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

(Positioning mechanism)
The first clutch mechanism 60 is configured to prevent the first clutch pawl 61 and the second clutch pawl 62 from rotating in order 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 in the rotational direction and assembled so as to have a positional relationship of being alternately arranged in the direction. Hereinafter, the rotational position of the rotor pinion where the first clutch pawls 61 and the second clutch pawls 62 are alternately arranged in the circumferential direction is referred to as a normal position 51A (see FIGS. 5 and 7). In this embodiment, since the number of the first clutch pawls 61 is 4, there are four regular positions 51A.

  The first clutch mechanism 60 includes a positioning mechanism 60A. The positioning mechanism 60A positions the rotor pinion 51 at the normal position 51A when the rotor pinion 51 is assembled. The positioning mechanism 60 </ b> A indirectly restricts the rotation of the rotor pinion 51 via the first rotating body 522 in which the large-diameter gear portion 527 that meshes with the rotor pinion 51 is formed. The positioning mechanism 60A includes a positioning recess 68 formed in the rotor pinion 51, a first rotating body 522 formed with a positioning projection 69, and a rotation restricting mechanism 70.

  The rotor pinion 51 includes a protruding portion 511 (see FIGS. 5 and 7) that protrudes in the + Z direction from the end surface in the + Z direction. The positioning recess 68 is formed on the outer peripheral surface of the projecting portion 511 and opens toward the outer peripheral side. A plurality of positioning recesses 68 are provided and formed at an angular position corresponding to the first clutch pawl 61. In this embodiment, the same number of positioning recesses 68 as the first clutch pawls 61 (four in this embodiment) are provided and arranged at equal angular intervals.

  The positioning protrusions 69 protrude in the radial direction from the end in the + Z direction of the first rotating body 522 and are arranged at equal angular intervals. The rotor pinion 51 and the first rotating body 522 are positioned in the rotational direction so that the positioning recess 68 and the positioning protrusion 69 are in a positional relationship when the first clutch mechanism 60 is in the clutch engaged state. Are assembled. Further, the rotor pinion 51 and the large diameter gear portion 527 mesh with each other and rotate. Therefore, the number of positioning projections 69 and the rotor pinion are set so that the number of teeth of the rotor pinion 51 corresponding to the angular interval of the positioning recess 68 and the number of teeth of the large-diameter gear portion 527 corresponding to the angular interval of the positioning projection 69 are equal. 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 4, and the number of teeth N2 of the large-diameter gear portion 527 is 48. Accordingly, 16 positioning protrusions 69 are provided.

  The rotation restricting mechanism 70 restricts the rotation of the first rotating body 522 when the rotation position of the first rotating body 522 is the lock position 522A (see FIGS. 5 and 8). In the positioning mechanism 60A, when the first rotating body 522 is positioned at the lock position 522A by the rotation restricting mechanism 70, the positioning protrusion 69 and the positioning recess 68 are engaged, and the rotor pinion 51 is positioned at the normal position 51A. It is configured to be. That is, when the rotation of the first rotating body 522 is restricted by the lock position 522A, the rotation position of the rotor pinion 51 is a rotation position where the tip of the first clutch pawl 61 and the tip of the second clutch pawl 62 do not interfere with each other. The 1st rotary body 522 and the rotor pinion 51 are assembled | attached so that it may become. The lock position 522 </ b> A is a position where one of the positioning protrusions 69 protrudes in the direction of the rotation center of the rotor pinion 51 and engages with the positioning recess 68. 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 this embodiment, since the number of positioning recesses 68 is 16 and the number of rotation restricting portions 72 is 4, one of the positioning protrusions 69 is always engaged with the positioning recess 68 at the lock position 522A.

There are four regular positions 51A of the rotor pinion 51 and lock positions 522A of the first rotating body 522. Therefore, when the first rotating body 522 is positioned at any one of the four lock positions 522A, the rotor pinion 51 is positioned at a corresponding one of the four regular positions 51A. Note that a position corresponding to a part of the regular position 51A may be the lock position 522A. For example, the rotation restricting mechanism 70 may be configured to restrict the rotation of the first rotating body 522 at positions corresponding to two of the four regular positions 51A. In this case, two rotation restricting portions 72 may be provided.

  During the clutch engagement operation, since the first rotating body 522 is positioned at the lock position 522A, the rotor pinion 51 is positioned at the normal position 51A, and one of the positioning protrusions 69 and one of the positioning recesses 68 are positioned. The two are engaged with each other. Accordingly, the clutch connection 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 configure the rotor pinion 51 so that the rotor pinion 51 is positioned at the normal position 51A as a result, one of the positioning protrusions 69 is always engaged with the positioning recess 68 at the lock position 522A. The number of teeth N1 and the number of teeth N2 of the large-diameter gear portion 527 need not be the same as described above. For example, as long as the relational expression of N2 = N1 × n (n: the number of rotation restricting portions 72) is satisfied, a configuration different from the above may be used. If this relational expression is satisfied, the angular position of the rotation restricting portion 72 provided in the first rotating body 522 and the positioning recess 68 provided in the rotor pinion 51 and the first rotating body 522 during 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 normal position 51A, and interference between the first clutch pawl 61 and the second clutch pawl 62 can be avoided.

(Second clutch mechanism)
9 and 10 are perspective views of the rotor 45, the second clutch mechanism 80, and the reverse rotation prevention mechanism 90. FIG. 9 is a perspective view seen from the + Z direction side, and FIG. 10 is a perspective view seen from the −Z direction side. It is. As shown in FIGS. 3, 4, 9, and 10, the second clutch mechanism 80 includes a planetary gear mechanism 81 in which rotation of the rotor 45 is transmitted via the guide ring 46, a fan gear 82, and a lock lever 83. A lock gear 84, a speed increasing gear 85, and a coil spring 86. 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, and the lock lever. 83 and a 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 driving 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 H axis, the rotation center axis of the fan gear 82 is the G axis, and the rotation center axis of the lock lever 83 is the F axis. The rotation center axis of the lock gear 84 is the E axis, and the rotation center axis of the speed increasing gear 85 is the D axis.

  FIG. 11 is a cross-sectional view of the rotor 45 and the planetary gear mechanism 81. 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, and a plurality of planetary gears 815 that mesh with the sun gear 811 and the internal gear 813. And a third rotating body 816 that rotatably holds the plurality of planetary gears 815. As shown in FIG. 11, 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, a large-diameter gear portion 818 that meshes with a guide ring gear 464 formed on the guide ring 46 disposed on the outer peripheral side of the shaft portion 452 is formed on the outer peripheral surface of the second rotating body 814. A small-diameter gear portion 819 that meshes with the fan gear 82 is provided at the end of the third rotating body 816 in the −Z direction.

As described above, the guide ring 46 is disposed between the magnet 451 and the shaft portion 452. The guide ring 46 includes a cylindrical metal portion 461 made of a nonmagnetic metal such as aluminum or copper, and a resin portion 462 provided on the inner peripheral side of the metal portion 461. The guide ring 46 is manufactured by insert-molding the metal portion 461 into a 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 bearing portion 466 provided at the end in the −Z direction is provided at a position overlapping the metal portion 461 in the radial direction. The guide ring 46 includes a flange portion 463 that protrudes to the outer peripheral side, and a guide ring gear 464 that is provided on the + Z direction side of the flange portion 463. The flange portion 463 is configured by overlapping the metal portion 461 and the resin portion 462, and the guide ring gear 464 is configured only by the resin portion 462. When the motor 40 is driven and the rotor 45 rotates, a magnetic induction force is generated between the magnet 451 and the metal portion 461. The induction ring 46 and the rotor 45 are coupled to rotate together by this magnetic induction force.

  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, in a state where a magnetic induction force is applied to the guide ring 46, the second rotating body 814 that meshes with the guiding ring 46 does not rotate, and the third rotating body 816 that is a planet carrier has the same rotational direction as the first rotating body 812 ( Rotate in the 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 coil spring 86 that is a biasing member, and rotates against the biasing force of the coil spring 86.

  The lock lever 83 is assembled so as to rotate in the opposite direction (CCW direction) to the fan gear 82 in conjunction with the rotation of the fan gear 82 in the CW direction. That is, the fan gear 82 is rotatably supported by the fixed shaft 821, and the lock lever 83 is rotatably supported by the fixed shaft 831. As shown in FIG. 8, the lock lever 83 is formed with an engagement pin 832 that is engaged with an engagement recess 822 formed in the fan gear 82.

  The lock gear 84 includes a large-diameter portion 842 in which a plurality of protrusions 841 are formed at equiangular intervals on the outer peripheral surface, and a small-diameter gear portion 843 having a smaller diameter than 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 contacts 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 to restrict the rotation of the lock gear 84. At this time, the rotation center P of the lock lever 83 is located on the tangent line A of the large diameter portion 842 of the lock gear 84 (see FIG. 3). Therefore, when rotation is restricted, the tip of the lock lever 83 and the protrusion 841 abut on the tangent line A direction of the lock gear 84.

  The second clutch mechanism 80 restricts the rotation of the speed increasing gear 85 by restricting the rotation of the lock gear 84 by the lock lever 83. 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 in the second rotating body 524. As described above, when the rotation of the second rotating body 524 is restricted via the speed increasing gear 85, the transmission wheel train 50 is in a state where the rotational torque is transmitted from the planetary gear mechanism 52 to the reduction gear 53. That is, when the lock gear 84 is brought into the locked state, the transmission wheel train 50 having a gear (large-diameter gear portion 851) that meshes with a gear train (the lock gear 84 and the speed increasing gear 85) including the lock gear 84 has a driving force. Switch to the state of transmission.

  Further, in the second clutch mechanism 80, when the lock lever 83 is engaged 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 engaged with the fan gear 82 is engaged. Rotation is regulated. 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 in which the internal gear 813 is formed rotates. 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 rotational speed of the rotor 45 and the guide ring 46 increases.

  The second clutch mechanism 80 rotates 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 magnetic induction force generated between the metal portion 461 of the induction ring 46 and the magnet 451. The lock gear 84 and the lock lever 83 are held so as not to be disengaged by force. Since the magnetic induction force generated between the metal part 461 of the induction ring 46 and the magnet 451 has a magnitude corresponding to the relative rotational speed of the metal part 461 and the magnet 451, the second rotating body 814 of the planetary gear mechanism 81 When the magnetic induction force is amplified by rotating in the reverse direction to the first rotating body 812, the holding force for holding the lock gear 84 increases. Therefore, the locked state that restricts the rotation of the lock lever 83 can be reliably maintained.

  When the energization of the motor 40 is stopped in a state where the lock gear 84 is locked by the lock lever 83, the second clutch mechanism 80 is released from the lock state of the lock gear 84 and is switched to the idle state. That is, when the rotation of the rotor 45 stops, the planetary gear mechanism 81 stops the rotation of the first rotating body 812 that meshes with the rotor gear 47, and the second rotating body 814 that meshes with the guide ring gear 464 can idle. As a result, the third rotating body 816 cannot hold the fan gear 82 against the biasing force of the coil spring 86, and the fan gear 82 rotates in the biasing direction of the coil spring 86. Since the lock lever 83 is separated from the lock gear 84 by the rotation of the fan gear 82, the lock 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 are idle.

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

  In the present embodiment, the fan gear 82 and a separate lock lever 83 are used as a rotation restricting member for restricting 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. However, the lock lever 83 and the fan gear 82 may be configured to rotate integrally. For example, if the fan gear 82 is provided with a lock lever-shaped protrusion, the protrusion (lock lever) contacts the lock gear 84 by the rotation of the fan gear 82 and engages with the protrusion 841. Accordingly, the rotation of the lock gear 84 can be restricted. Alternatively, another rotation transmission member may be interposed between the fan gear 82 and the lock lever 83. Further, a member that engages with the lock gear 84 by an operation other than rotation may be used as the rotation restricting member.

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

(Reverse rotation prevention mechanism)
12A is a plan view of the reverse rotation prevention mechanism 90, and FIG. 12B is a side view of the reverse rotation prevention mechanism 90. FIG. The reverse rotation prevention mechanism 90 includes a reverse rotation prevention protrusion 91 formed on the shaft portion 452 of the rotor 45 and a reverse rotation prevention lever 92 attached to the upper part of the planetary gear mechanism 81. The reverse rotation prevention lever 92 is bent in the −Z direction from the disk portion 93 that contacts the end surface in the + Z direction of the first rotating body 812 of the planetary gear mechanism 81 and the circumferential portion of the outer peripheral edge of the disk portion 93. The bending part 94 and the arm part 95 extended from the edge part of the -Z direction of the bending part 94 to an 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 prevention protrusion 91 is disposed on the outer peripheral side of the second clutch pawl 62. ing. The reverse rotation preventing protrusions 91 are convex portions that protrude from the end surface of the shaft portion 452 in the + Z direction, and are arranged at equiangular intervals in the circumferential direction. The reverse rotation prevention protrusion 91 has an arc shape and includes an end face 96 facing in the circumferential direction. The second clutch pawl 62 is disposed on the inner peripheral side with respect to the reverse rotation prevention protrusion 91. Further, a part of the second clutch pawl 62 is disposed 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 a plate spring 98 disposed on the grease viscosity and the upper portion of the reverse rotation preventing lever 92. Therefore, when the rotation of the rotor 45 starts, the reverse rotation prevention lever 92 rotates together with the first rotating body 812 that meshes 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 that the tip of the arm portion 95 enters between the reverse rotation prevention protrusions 91 adjacent in the circumferential direction. As a result, the circumferential end surface 96 of the reverse rotation prevention protrusion 91 and the tip of the arm portion 95 of the reverse rotation prevention lever 92 collide with each other. Due to the impact at the time of the collision, the rotation direction of the rotated rotor 45 is corrected to the normal rotation direction (CW direction).

  Since the second clutch pawl 62 is disposed at an angular position between the reverse rotation prevention protrusions 91 adjacent in the circumferential direction, the arm portion 95 of the reverse rotation prevention lever 92 collides with the second clutch pawl 62, and the reverse rotation prevention protrusion 91. It will not enter the inner circumference. Therefore, the end face 96 in the circumferential direction of the reverse rotation preventing projection 91 and the tip of the arm portion 95 can be made to collide with each other at the time of reverse rotation. When the end surface 96 of the reverse rotation preventing projection 91 and the tip of the arm portion 95 collide, 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, there is little possibility that the reverse rotation prevention lever 92 is deformed by the impact force.

(Operation at startup)
The operation | movement at the time of starting of the drain valve drive apparatus 1 is demonstrated. It is assumed that the slider 10 is pulled out to the position where the drain valve is closed at the time of activation. When energization of the motor 40 is started in this state, the rotor 45 starts to rotate. At this time, since the rotation of the rotor 45 in the reverse rotation direction is restricted by the above-described reverse rotation prevention mechanism 90, the rotor 45 rotates in the normal rotation direction.

  Next, the rotation restricting device 80 </ b> A of the second clutch mechanism 80 is switched to a state in which the lock gear 84 is locked by the rotation of the rotor 45 in the forward rotation direction. First, the fan gear 82 rotates against the urging force of the coil spring 86 by the output rotation of the planetary gear mechanism 81, the lock lever 83 abuts on the lock gear 84 and engages with the protrusion 841, and locks the lock gear 84. To do. Thereby, the transmission wheel train 50 is switched to a state in which the rotational torque is transmitted. That is, in the transmission wheel train 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. Switch to the state transmitted to Accordingly, the retracting operation of the slider 10 is performed by the rotation of the rotor 45 in the forward rotation direction.

When the lock lever 83 abuts on the lock gear 84 and the lock gear 84 is locked, the second clutch mechanism 80 rotates the guide ring 46 in the direction opposite to the rotation direction of the rotor 45 by the planetary gear mechanism 81. Thereby, the relative rotational speed of the rotor 45 and the guide ring 46 is increased, the magnetic induction force 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 slider pulling)
In the drain valve driving device 1, when the end of the pulling of the slider 10 is reached, the clutch switching lever 64 of the first clutch mechanism 60 is rotated to perform the clutch disengaging operation, and the rotation of the rotor 45 is not input to the transmission wheel train 50. Accordingly, the slider 10 is not pulled beyond the predetermined pulling position 10A. Further, since the rotation restricting projection 74 of the rotation restricting mechanism 70 restricts the rotation of the first rotating body 522 of the planetary gear mechanism 52 due to the rotation of the clutch switching lever 64, the planetary gear mechanism 52 is locked, and the transmission wheel train 50 Cannot transmit rotational torque. Therefore, even if an external force for pulling the slider 10 in the + X direction is applied, the slider 10 is in a load holding state where the slider 10 does not move. As a result, the drain valve is held open.

(Operation when the load is released)
When the drain valve driving device 1 stops energization of the motor 40 in the load holding state, the drain valve driving device 1 shifts to a load releasing state in which the slider 10 can be pulled out in the + X direction by an external force. When the motor 40 is de-energized, the rotation of the rotor 45 stops. Since the fan gear 82 returns to the biasing direction of the coil spring 86 when the rotation of the rotor 45 stops, the second clutch mechanism 80 releases the engagement between the lock lever 83 and the lock gear 84, and the lock gear by the rotation restricting device 80A. The rotation restriction 84 is released. As a result, the transmission wheel train 50 switches to a state in which the rotational torque is not transmitted. That is, since the rotation restriction of the second rotating body 524 is released in the planetary gear mechanism 52 of the transmission wheel train 50, the planetary gear mechanism 52 is unlocked. As a result, the transmission wheel train 50 enters a load release state in which the transmission wheel train 50 can idle. In this state, when an external force in the direction of pulling out the slider 10 is applied, the transmission wheel train 50 idles and the slider 10 is pulled out. A brake rubber 87 (see FIG. 9) is incorporated in the lock gear 84. The brake rubber 87 expands by centrifugal force when the slider 10 is pulled out by an external force, and generates a frictional force with the lock gear 84. As a result, the return speed when the slider 10 is pulled out decreases. Therefore, the risk of damage due to the slider 10 being pulled out rapidly can be reduced.

  When the slider 10 is pulled out to a predetermined position before reaching the maximum pulling position, the clutch engagement operation starts based on the rotation of the output gear 54 in the CW direction. That is, the clutch switching lever 64 rotates to the output gear 54 side by the cam groove 66 formed in the output gear 54 and the cam pin 65 provided in the clutch switching lever 64, and the clutch connection operation is performed. As a result, the state returns to the state in which the rotation of the rotor 45 is input to the transmission wheel train 50. Further, by the rotation of the clutch switching lever 64, the lock of the first rotating body 522 of the planetary gear mechanism 52 by the rotation restricting mechanism 70 is released. Accordingly, the transmission wheel train 50 returns to a state where the rotational torque can be transmitted.

(Main effects of the present invention)
As described above, the drain valve driving device 1 of the present embodiment includes the slider 10 that is a drain valve driving member, the motor 40 that is a driving source, and the transmission wheel train 50 that transmits the rotational torque of the motor 40 to the output pinion 12. The first clutch mechanism 60 for interrupting transmission of rotational torque from the motor 40 to the transmission wheel train 50 is provided. The first clutch mechanism 60 includes a first clutch pawl 61 formed on a rotor pinion 51 disposed coaxially with the rotor 45, a second clutch pawl 62 formed on a shaft portion 452 of the rotor 45, and a rotor pinion. A coil spring 63 that is a biasing member that biases 51 in the + Z direction (clutch disengagement direction), and a fan-shaped clutch switching lever 64 that is a clutch switching member that pushes down the rotor pinion 51 in the −Z direction (clutch connection direction). The positioning mechanism 60A is provided. The positioning mechanism 60A includes a positioning recess 68 that is an engaged portion formed on the rotor pinion 51, a large-diameter gear portion 527 on which a positioning projection 69 that is an engaging portion is formed, and a rotation restricting mechanism 70.

  In this embodiment, the rotation of the rotor pinion 51 is indirectly restricted via the first rotating body 522 provided with the large-diameter gear portion 527 that meshes with the rotor pinion 5 as described above, and the positioning recess 68 and the positioning protrusion 69 are engaged. To position the rotor pinion 51 in the rotational direction. In this way, the rotation of the rotor pinion 51 can be reliably controlled as compared with the case where the rotation is directly controlled for the small rotor pinion 51. In addition, by separating the part that performs the rotation restriction from the rotor pinion 51, it is easy to adjust the timing for releasing the rotation restriction and the timing for performing the rotation restriction. Therefore, rotation regulation can be performed at an appropriate timing both when the clutch is engaged and when the clutch is disengaged, and a stable clutch disengaging operation can be performed.

  The rotation restricting mechanism 70 of this embodiment includes a rotation restricting surface 73 provided on the first rotating body 522 and a rotation restricting protrusion 74 that is a moving part that contacts the rotation restricting surface 73 and restricts the rotation of the first rotating body 522. The rotation restricting surface 73 has a circular arc shape along the movement locus B1 of the rotation restricting protrusion 74. Therefore, when the rotation restriction is released, the rotation restriction surface 73 is not pressed by the rotation restriction protrusion 74, so that there is little possibility that the first rotation body 522 is controlled by the rotation restriction protrusion 74. Therefore, it is possible to reduce the load when releasing the rotation restriction. In addition, when releasing the rotation restriction, the rotation position of the first rotating body 522 is less likely to shift, and the rotation position of the rotor pinion 51 is less likely to shift. Therefore, a stable clutch disengagement operation can be performed.

  In this embodiment, when the clutch switching lever 64 rotates in a direction to move the rotor pinion 51 from the clutch disengagement position to the clutch engagement position, first, the first clutch pawl 61 is reached when the clutch switching lever 64 reaches a predetermined rotation position. When the tip of the second clutch pawl 62 is engaged with the tip of the second clutch pawl 62 and the clutch switching lever 64 is further rotated, the rotation restricting projection 74 is completely retracted from between the rotation restricting portions 72 and the first rotating body 522 is moved. The rotation restriction is released. Therefore, there is little possibility that the rotation restriction of the rotor pinion 51 is released before the clutch is connected and the rotation position of the rotor pinion 51 is shifted. Therefore, a stable clutch connection operation can be performed.

  In this embodiment, the rotor pinion 51 meshes with the large-diameter gear portion 527 of the planetary gear mechanism 52 that is the input gear of the transmission wheel train 50, and the positioning protrusion is formed on the first rotating body 522 provided with the large-diameter gear portion 527. 69 is formed, and the rotation restricting mechanism 70 restricts the rotation of the large-diameter gear portion 527 to restrict the rotation of the rotor pinion 51. Thus, since the rotation of the rotor pinion 51 is regulated using the gears of the transmission wheel train 50, there is no need to separately provide a rotating body for regulating the rotation. Further, the rotation restricting mechanism 70 can restrict the rotation in conjunction with the operation of moving the rotor pinion 51 in the clutch engagement direction (−Z direction) by using the clutch switching lever 64 of the first clutch mechanism 60. . Therefore, the positioning mechanism 60A can have a simple structure, which is advantageous for simplification and miniaturization of the first clutch mechanism 60. Moreover, the clutch disengagement operation, the rotation restricting operation of the rotor pinion 51, and the release operation of the rotation restriction can be performed in conjunction with each other by a simple mechanism.

  In this embodiment, the engaging portion provided in the first rotating body 522 is the positioning protrusion 69 protruding in the radial direction from the outer peripheral surface of the large-diameter gear portion 527, and the engaged portion provided in the rotor pinion 51 is the rotor. This is a positioning recess 68 that opens on the outer peripheral surface of the pinion 51. As described above, since the positioning shape on the rotor pinion 51 side is concave, the positioning shape is less likely to interfere with surrounding members when the rotor pinion 51 is moved. The engaging portion provided on one of the rotor pinion 51 and the first rotating body 522 and the engaged portion provided on the other are not limited to the positioning protrusion 69 and the positioning recess 68 described above. For example, a concave portion may be provided in the large diameter gear portion 527 and a convex portion may be provided in the rotor pinion 51.

(Modification)
In the above embodiment, the rotation of the rotor pinion 51 is regulated through the large-diameter gear portion 527 provided on the first rotating body 522, but the rotation of the rotor pinion 51 is regulated through another gear or the rotating body. May be. Further, the rotation of the large-diameter gear portion 527 may be restricted using a clutch switching member that has a shape or movement different from that of the clutch switching lever 64, or a rotation restricting member that is separate from the clutch switching lever 64. Furthermore, the operation of the rotation restricting member when restricting the rotation of the large-diameter gear portion 527 may not be an operation in the rotation direction. For example, a linear motion or a motion along various cam shapes may be used.

DESCRIPTION OF SYMBOLS 1 ... Drain valve drive device, 2 ... Gear unit, 10 ... Slider, 10A ... Pull-in position, 11 ... Rack, 12 ... Output pinion, 20 ... Case, 21 ... First case, 22 ... Second case, 23 ... Third Case, 24 ... Opening, 25 ... Wiring extraction part, 30 ... Guide part, 40 ... Motor, 41 ... Motor case, 42 ... Support plate, 43 ... Bobbin, 44 ... Stator coil, 45 ... Rotor, 46 ... Induction ring, 47 ... Rotor gear, 48 ... Terminal block, 50 ... Transmission wheel train, 51 ... Rotor pinion, 51A ... Regular position, 51B ... Separation position, 51C ... Connection position, 52 ... Planetary gear mechanism, 53 ... Reduction gear, 54 ... Output gear 55 ... protrusions, 60 ... first clutch mechanism, 60A ... positioning mechanism, 61 ... first clutch pawl, 62 ... second clutch pawl, 63 ... coil spring, 64 ... clutch disengagement Lever, 64A ... clutch disengagement position, 65 ... cam pin, 66 ... cam groove, 67 ... tilted cam, 68 ... positioning recess, 69 ... positioning projection, 70 ... rotation restricting mechanism, 71 ... projection, 72 ... rotation restricting, 73 Rotation restricting surface, 74 ... Rotation restricting protrusion, 80 ... Second clutch mechanism, 80A ... Rotation restricting device, 81 ... Planetary gear mechanism, 82 ... Fan gear, 83 ... Lock lever, 84 ... Lock gear, 85 ... Speed increasing gear 86 ... Coil spring, 87 ... Brake rubber, 90 ... Anti-reverse mechanism, 91 ... Anti-reverse protrusion, 92 ... Anti-reverse lever, 93 ... Disc part, 94 ... Bent part, 95 ... Arm part, 96 ... End face, 97 ... fixed shaft, 98 ... leaf spring, 211 ... bottom plate, 212 ... side plate, 221 ... top plate, 222 ... side plate, 241 ... first recess, 242 ... second recess, 451 ... magnet, 452 ... shaft, 453 ... fixed axis 461 ... Metal part, 462 ... Resin part, 463 ... Bridge part, 464 ... Induction ring gear, 511, Projection part, 521 ... Sun gear, 522 ... First rotating body, 522A ... Lock position, 523 ... Internal gear, 524 ... 2nd rotating body, 465, 466 ... bearing part, 525 ... planetary gear, 526 ... 3rd rotating body, 527 ... large diameter gear part, 528 ... large diameter gear part, 529 ... small diameter gear part, 531 ... large diameter gear Part, 532 ... small diameter gear part, 533 ... fixed shaft, 811 ... sun gear, 812 ... first rotating body, 813 ... internal gear, 814 ... second rotating body, 815 ... planetary gear, 816 ... third rotating body, 817 ... large diameter gear part, 818 ... large diameter gear part, 819 ... small diameter gear part, 821 ... fixed shaft, 822 ... engagement recess, 831 ... fixed shaft, 832 ... engagement pin, 841 ... protrusion, 842 ... large Diameter, 843 ... Small diameter gear, 851 ... Large Diameter gear portion, 852 ... Small diameter gear portion, A1 ... Tangent, B1 ... Movement locus, P ... Center of rotation, X ... First direction, Y ... Second direction, Z ... Third direction

Claims (6)

A clutch mechanism for interrupting transmission of rotational torque from the rotor to the transmission wheel train,
A first clutch pawl formed on a rotor pinion disposed coaxially with the rotor; a second clutch pawl formed on the rotor; and a clutch disengagement direction in which the first clutch pawl is separated from the second clutch pawl. An urging member that urges the rotor pinion, a clutch switching member that moves the rotor pinion in a clutch connection direction opposite to the clutch disengagement direction, and the first clutch pawl and the second clutch pawl alternately in the circumferential direction A positioning mechanism that positions the rotor pinion at a regular position that is a rotational position to be arranged;
The positioning mechanism includes a rotation restricting mechanism that restricts rotation of a rotating body that engages with the rotor pinion,
The rotation restricting mechanism includes a rotation restricting surface formed on the rotating body, a moving part movable to a position where the rotation restricting surface can come into contact with the rotation restricting surface and a position retracted from the rotation restricting surface,
The clutch mechanism according to claim 1, wherein the rotation regulating surface has a shape along a movement locus of the moving unit.   The clutch mechanism according to claim 1, wherein the moving part is a rotation restricting protrusion formed on the clutch switching member. The clutch switching member is a clutch switching lever that rotates in conjunction with rotation of the transmission wheel train;
The clutch mechanism according to claim 2, wherein the rotation restricting surface has an arc shape along a movement locus of the moving unit. When the clutch switching lever rotates in a direction to move the rotor pinion in the clutch connection direction,
The rotor pinion moves to a position where at least a part of the first clutch pawl and the second clutch pawl engages, and then the rotation restricting projection moves to a position not facing the rotation restricting surface. The clutch mechanism according to claim 3.   The clutch mechanism according to any one of claims 1 to 4, wherein the rotating body includes a gear of the transmission wheel train, and the gear meshes with the rotor pinion. The clutch mechanism according to any one of claims 1 to 5,
A motor comprising the rotor;
The transmission train wheel;
And a drain valve driving member that is driven based on rotation of an output gear of the transmission wheel train.

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