JP2018062999A - Rotation regulation device and discharge water valve drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve workability during assembly of a torsion coil spring to be biased a rotation regulation member for regulating the rotation of a body of rotation.SOLUTION: In a discharge water valve drive device 1, a rotation regulation device 80A regulates the rotation of a lock gear 84 (the body of rotation) by rotating a sector gear 82 and a lock lever 83 based on the rotation of a rotor 45. The rotation regulation device 80A biases the sector gear 82 and the lock lever 83 in the return direction by a torsion coil spring 86 attached to a shaft portion 822 of the sector gear 82. The sector gear 82 includes a coil spring holding part 824 for holding the torsion coil spring 86 so as not to be dropped in the axial direction (a third direction Z). The coil spring holding part 824 has a structure in which the center part 825 of the shaft portion 822 is inserted into the center of a coil part 861; and an arm part 829 disposed on the outer peripheral side of the coil part 861 is engaged with a spring leg 862 so as to hold the coil spring.SELECTED DRAWING: Figure 11

Description

  The present invention relates to a rotation restricting device and a drain valve driving device that restrict the rotation of a rotating body.

  As a drain valve driving device for driving a drain valve of a washing machine or the like, there is one having a transmission wheel train and a clutch mechanism between a motor as a driving source and a driven member connected to the drain valve. Patent Document 1 discloses a motor actuator used in this type of drain valve driving device. The motor actuator of Patent Document 1 includes a transmission wheel train (first transmission train) that transmits a driving force to a driven member (wire). The clutch mechanism includes a second transmission train that includes a gear (first lock gear) that meshes with one of the gears of the first transmission train (fixed gear of the planetary gear mechanism) and prevents its rotation. The planetary gear mechanism transmits the driving force of the motor to the output gear in a state where the rotation of the fixed gear is blocked. That is, the clutch is engaged.

  The clutch mechanism of Patent Document 1 includes a rotation restricting device that restricts the rotation of one of the gears of the second transmission train (first lock gear). By restricting the rotation of the first lock gear, the rotation of the fixed gear of the planetary gear mechanism described above is restricted. Thereby, it will be in a clutch connection state. Further, by releasing the rotation restriction of the first lock gear, the fixed gear of the planetary gear mechanism can be rotated. As a result, the fixed gear rotates idle, and the planetary gear mechanism does not transmit the driving force of the motor to the output gear. That is, the clutch is disengaged.

  As described above, the clutch mechanism of Patent Document 1 switches the clutch mechanism to be engaged by restricting the rotation of the gear (rotating body) by the rotation restricting device and releasing the rotation. The rotation restricting device restricts the rotation of the first lock gear by rotating a lock lever (rotation restricting member) and engaging its tip with a protrusion on the outer peripheral surface of the first lock gear. The lock lever is provided on a driven gear that rotates based on the rotation of the driving gear, and the driving gear rotates based on the rotation of the rotor. When the rotor is energized, the driving gear and the driven gear rotate, the lock lever engages with the protrusion on the outer peripheral surface of the first lock gear, and the first lock gear is in the locked state (rotation restricted state). Become.

  In Patent Document 1, a driven gear on which a lock lever is formed is urged in a return direction by a coil spring. The coil spring is bridged between a first coil spring hook portion protruding from the shaft portion of the driven gear and a second coil spring hook portion provided on the support plate to which the wheel train shaft is fixed. When the power to the rotor is turned off, the lock lever is rotated in the return direction by the biasing force of the coil spring, so that the locked state (rotation restricted state) is released.

JP 2013-233000 A

In the rotation restricting device, when a biasing member (coil spring) for biasing the lock lever in the unlocking direction is provided, the structure for attaching the coil spring so as to expand and contract in the axial direction as in Patent Document 1 is an installation space for the coil spring. Will become bigger. Therefore, it is possible to employ a structure in which the driving side gear or the driven side gear is rotated in the releasing direction by using the torsional moment acting between one spring leg and the other spring leg of the coil spring. However, when such a coil spring (torsion coil spring) is assembled together with the drive side gear, there is a problem that the torsion coil spring easily falls off and the workability is poor.

  The subject of this invention is improving the workability | operativity at the time of the assembly | attachment of the torsion coil spring which urges | biases a rotation control member in view of such a point.

  In order to solve the above problems, the present invention provides a rotation restricting device that restricts the rotation of a rotating body by a rotation restricting member that is driven based on the rotation of a rotor. A rotation restricting member drive gear that rotates integrally with the rotation restricting member, and a torsion coil spring that biases the rotation restricting member drive gear in a direction opposite to a direction rotated based on rotation of the rotor, The rotation restricting member driving gear includes a coil spring holding portion that holds the torsion coil spring.

  According to the present invention, in the rotation restricting device that restricts the rotation of the rotating body, the torsion coil spring is used as the urging member for generating the urging force for releasing the rotation restriction, so the installation space for the urging member is reduced. be able to. In addition, when using a torsion coil spring as an urging member, the rotation restricting member drive gear and the torsion coil spring are assembled together while the torsion coil spring is held by the coil spring holding portion provided in the rotation restricting member drive gear. Can do. Therefore, workability when assembling the torsion coil spring can be improved.

  In the present invention, it has a planetary gear mechanism that rotates the rotation restricting member drive gear based on the rotation of the rotor, and a guide ring that faces a magnet provided in the rotor. A first rotating body formed with gears, a second rotating body formed with internal gears, a planetary gear meshing with the sun gear and the internal gears, and a planet carrier that rotatably supports the planetary gears. A third rotating body provided, and the guide ring is provided with a guide ring gear that meshes with a gear formed on one of the first rotating body and the second rotating body. A gear that meshes with a rotor gear formed on the rotor is provided on the other side of the second rotating body, and the rotation restricting member driving gear is configured to rotate based on the rotation of the third rotating body. Kill. In such a configuration, when the rotation restricting member connected to the third rotating body stops by forming a state (locked state) that restricts the rotation of the rotating body, the first rotating body and the second rotating body Is rotated in the opposite direction, and rotation in the direction opposite to the rotation direction of the rotor is input to the guide ring. Thereby, since the relative rotational speed of the induction ring and the magnet increases, the braking force due to the eddy current generated between the induction ring and the magnet is amplified. Accordingly, the holding force (brake torque) for holding the rotation restricting member can be increased. Therefore, a stable locked state can be formed.

  In the present invention, the rotation restricting member driving gear is a fan gear including a first shaft portion provided with the coil spring holding portion and a fan tooth portion formed integrally with the first shaft portion, and the coil spring. The holding portion includes a central portion that is passed through the coil portion of the torsion coil spring and an arm portion that extends in the circumferential direction on the outer peripheral side of the coil portion, and one spring leg of the torsion coil spring is provided on the arm portion. It is desirable to engage. If it does in this way, since the center part of a rotation control member drive gear can be used as an axis | shaft which attaches a torsion coil spring, it is not necessary to provide the axis | shaft which attaches a torsion coil spring separately. Therefore, the installation space for the torsion coil spring can be reduced. Further, since the torsion coil spring is held through the central portion of the coil portion and is held by engaging the spring leg with the arm portion, the torsion coil spring can be made difficult to fall off in the axial direction.

In the present invention, the rotation regulating member is a lock lever including a second shaft portion rotatably attached to a fixed shaft and a first arm portion protruding from the second shaft portion, and the second shaft portion includes It is preferable that a notch for exposing the fixed shaft to the outside is formed, and the other spring leg of the torsion coil spring abuts on an outer peripheral surface of the fixed shaft exposed to the outside by the notch. If it does in this way, since a torsion coil spring can be assembled | attached on the basis of the fixed axis | shaft located in the rotation center of a lock lever, the positional accuracy of a torsion coil spring can be improved. Therefore, the operation accuracy of the rotation restricting device can be increased and malfunctions can be suppressed. Further, since the spring foot is supported not by the outer peripheral surface of the rotating second shaft portion but by the fixed shaft, it is possible to avoid the influence of the pressing force from the spring foot from affecting the operation of the lock lever that is the rotating member. it can. That is, when the outer peripheral surface of the second shaft portion is pressed by the spring foot, a sliding load is generated between the spring foot and the outer peripheral surface of the second shaft portion during the operation of the lock lever, and the lock lever operates. Effects, but such effects can be eliminated.

  In the present invention, the rotation restriction member includes an engagement pin formed on a second arm part protruding from the second shaft part, and in the rotation restriction member drive gear, the first shaft part is the center part. It is preferable that a cylindrical portion surrounding the outer peripheral side of the cylindrical portion is formed, and the cylindrical portion is formed with an engagement recess capable of engaging the arm portion and the engagement pin. If it does in this way, rotation of a rotation control member drive gear can be transmitted to a rotation control member via an engagement pin and an engagement crevice. And if an engagement recessed part and an arm part are provided in the same cylindrical part, these parts can be arrange | positioned inside the outer peripheral surface of a cylindrical part. Therefore, the structure can be simplified and the space efficiency is good. Moreover, since a part of cylindrical part is used as an arm part, the intensity | strength of an arm part is securable.

  In the present invention, it is preferable that the cylindrical portion includes a notch, and the notch extends from an axial edge of the cylindrical portion to an engagement position of the spring foot with respect to the arm portion. In this way, when the torsion coil spring is attached to the coil holding part, the spring leg can be passed through the notch, and the spring leg can be moved to the engagement position with the arm part to be engaged. Therefore, the operation | work which mounts a torsion coil spring to a coil holding part is easy.

  In the present invention, it is desirable that the coil spring holding portion includes a position restricting portion that restricts a position of the torsion coil spring in the axial direction. If it does in this way, the position accuracy of the direction of an axis of a torsion coil spring can be raised.

  In order to solve the above-described problem, a drain valve driving device of the present invention includes the above-described rotation regulating device, a motor including the rotor, and a gear meshing with a gear provided on the rotating body. It has a transmission wheel train to which rotation is input, and a drain valve drive member that is driven based on the rotation of the output gear of the transmission wheel train.

  According to the present invention, transmission of rotational torque by the transmission wheel train of the drain valve driving device can be interrupted by the rotation restricting device. And since said rotation control apparatus can form the stable locked state, the operation | movement of a drain valve drive apparatus can be stabilized.

  In the drain valve driving device according to the present invention, the drain valve driving device includes a clutch mechanism that interrupts transmission of rotational torque by the transmission wheel train, and the rotating body is a lock gear provided in the clutch mechanism, and the lock is provided by the rotation restricting member. In a state where the rotation of the gear is restricted, the transmission wheel train transmits rotational torque, and in a state where the rotation restriction of the lock gear by the rotation restricting member is released, the transmission wheel train does not transmit the rotational torque. Can be configured. In this way, the holding force for holding the lock gear in the locked state can be increased, and the operation of the clutch mechanism can be stabilized. Therefore, the transmission of the rotational force by the transmission wheel train can be stably performed, and the operation of the drain valve driving device can be stabilized.

According to the rotation restricting device of the present invention, in the rotation restricting device that restricts the rotation of the rotating body, the torsion coil spring is used as the urging member that generates the urging force for releasing the rotation restriction. Space can be reduced. In addition, when using a torsion coil spring as an urging member, the rotation restricting member drive gear and the torsion coil spring are assembled together while the torsion coil spring is held by the coil spring holding portion provided in the rotation restricting member drive gear. Can do. Therefore, workability when assembling the torsion coil spring can be improved.

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 the drain valve drive device which removed the pulley and the 2nd 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 explanatory drawing of a motor, a transmission wheel train, a 1st clutch mechanism, and a rotation control mechanism. It is operation | movement explanatory drawing (plan 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 the rotor and the 2nd clutch mechanism from the + Z direction side. It is the perspective view which looked at the rotor and the 2nd clutch mechanism from the -Z direction side. It is a cross-sectional perspective view of a rotor and a guide ring. It is a disassembled perspective view of a rotor and a guidance ring. It is explanatory drawing of a fan gear and a torsion coil spring. It is a disassembled perspective view of a motor and a 2nd clutch mechanism. It is the perspective view and top 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 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 the pulley 11 is rotated to wind the wire 10 A 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 that is accommodated in the case 20, and a motor 40.

  As shown in FIG. 2, a circular opening 12 is formed on the surface of the case 20 to which the pulley 11 is attached. A serration portion 13 a formed on the output shaft 13 of the gear unit 30 is disposed in the opening 12. The pulley 11 is assembled in a state of rotating integrally with the output shaft 13 via the serration portion 13 a and is screwed to the output shaft 13 by a fixing screw 14. The case 20 is formed with an annular rib 15 surrounding the pulley 11 and a substantially rectangular outer peripheral rib 16 surrounding the annular rib 15. The annular rib 15 is connected to the outer peripheral rib 16 by radial ribs. 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 so as to cover the pulley 11.

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

  In the state where the wire 10 is wound around the pulley 11 by a predetermined amount, the drain valve driving device 1 continues to energize the motor 40 that is a driving source and holds the pulley 11 at the winding position. Thereby, the valve body of the drain valve connected to the wire 10 is held at a position away from the drain port. Further, the drain valve driving device 1 stops energization of the motor 40 and releases the holding state of the pulley 11. As a result, the wire 10 can be pulled out by an 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 drain valve, the drain port is closed by the valve body.

  In this specification, the rotation axis direction of the pulley 11 is defined as a third direction Z, and two directions orthogonal to the third direction Z are defined as a first direction X and a second direction Y. The first direction X is a direction in which the wire 10 is pulled out. 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. For example, the drain valve driving device is disposed in a posture in which the + Z direction is directed upward and the −Z direction is directed downward, but may be disposed in another posture. For example, it can be arranged in a posture in which the −Z direction is upward and the + Z direction is downward. In this 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 disposed between the first case 21 and the second case 22. A terminal accommodating portion 23 in which a terminal for supplying power to the motor 40 is disposed 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. FIG. 4 is a development view of the train wheel showing a section connecting the shafts of the gears of the gear unit 30, and is a sectional view taken along line AA in FIG. 3 and 4, the gear shaft (rotation center axis) of the gear unit 30 is denoted by reference characters B, C, D, E, F, G, H, J, and O. These axes point in the third direction Z. The gear unit 30 includes a transmission wheel train 50 that transmits the rotation of the motor 40 to the output shaft 13, a first clutch mechanism 60 that interrupts transmission of rotational torque from the motor 40 to the transmission wheel train 50, and 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 restricts the rotational direction of the motor 40.

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

(motor)
As shown in FIG. 4, the motor 40 is disposed at the bottom of the first case 21, and the gear unit 30 is disposed on the + Z direction side of the motor 40. 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 second case 22 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. Further, the shaft portion 452 protrudes 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 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 second case 22 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.

  FIG. 5 is an explanatory view of the motor 40, the transmission wheel train 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. ) Is a perspective view of the clutch switching lever 64 viewed from the -Z direction side. A part of the outer peripheral surface of the motor case 41 is notched in the circumferential direction, and a terminal block 48 formed on the bobbin 43 is disposed here. A terminal 49 is attached to the terminal block 48 to which power supply wiring to the stator coil 44 is connected. 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 wheel train 50 transmits the driving force of the motor 40 to the output shaft 13 that rotates the pulley 11. 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 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. It is. The transmission wheel train 50 transmits the driving force of the motor 40 in this order. The output shaft 13 is disposed at the rotation center of the output gear 54 and rotates integrally with the output gear 54. Accordingly, the wire 10 that is 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 together with the rotor 45 (clutch connection state), and the rotor pinion 51 does not rotate together with the rotor 45 (clutch disengagement state). Can be switched to.

As shown in FIG. 4, 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, the sun gear 521 and the internal gear 523. A plurality of planetary gears 525 that mesh with each other, 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)
As shown in FIG. 5A, the first clutch mechanism 60 includes a first clutch pawl 61 formed on the end surface in the −Z direction of the rotor pinion 51 and a second clutch formed on the shaft portion 452 of the rotor 45. A claw 62, a coil spring 63 (see FIGS. 7 and 8) that is a biasing member that biases the rotor pinion 51 in a direction away from the shaft 452 (in this embodiment, the + Z direction), and the rotor pinion 51 as a shaft. A fan-shaped clutch switching lever 64 that is a clutch switching member that is pushed down to the part 452 side (−Z direction) to switch the connection of the first clutch mechanism 60 is provided. 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. 5B, the clutch switching lever 64 is formed with a cam pin 65 and an inclined cam 67 that protrude 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.

  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 includes a clutch disengagement position 64A (see FIG. 6C) rotated to the planetary gear mechanism 52 side, and a clutch connection position 64B (FIG. 6 (FIG. 6) rotated to the output gear 54 side. Rotate between a)). As shown in FIG. 6 (c), when the clutch switching lever 64 is located at the clutch disengagement position 64A, the first clutch mechanism 60 has a first clutch pawl 61 and a second clutch pawl as shown in FIG. 7 (b). The clutch is disengaged from 62.

  When the clutch switching lever 64 rotates from the clutch disengagement position 64A to the output gear 54 side (CCW direction), the rotor pinion 51 is pushed down to the shaft portion 452 side (−Z direction side) by the inclined surface of the inclined cam 67. As shown in FIG. 6 (a), when the clutch switching lever 64 moves to the clutch engagement position 64B, the rotor pinion 51 has a first clutch pawl 61, a second clutch pawl 62, and the like, as shown in FIG. 7 (a). Moves to the connecting position 51B where the two engage. 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 from the clutch connection position 64B to the planetary gear mechanism 52 side (CW direction), the inclined cam 67 is retracted from the position where it overlaps the rotor pinion 51, so that the rotor pinion 51 is + Z by the urging force of the coil spring 63. Move in the direction. Accordingly, as shown in FIG. 7B, 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. Thereby, a clutch connection operation is performed. 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. Thereby, the clutch disengagement operation is started.

  Here, in the clutch disengagement operation, the section until the clutch switching lever 64 moves from the clutch connection position 64B shown in FIG. 6A to the midway position 64C shown in FIG. The section rotated by the pressure but moved from the midway position 64C shown in FIG. 6 (b) to the clutch disengagement position 64A shown in FIG. 6 (c) is inclined cam by the force by which the rotor pinion 51 is pushed up by the coil spring 63. When the slope of 67 is pressed, the clutch switching lever 64 rotates.

  The drain valve driving device 1 starts the drainage by rotating the output gear 54 in the rotation direction when winding the wire 10 (that is, the CCW direction). The position of the protrusion 55 of the output gear 54 is determined by the position of the output gear 54. When a predetermined rotational position is reached, the clutch switching lever 64 is pressed to rotate to the planetary gear mechanism 52 side (CW direction). For this reason, when the pulley 11 rotates to the vicinity of one end of the rotation range defined by the concave portion 17, 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, excessive rotation of the pulley 11 can be prevented, and excessive winding of the wire 10 can be prevented.

(Rotation restriction mechanism)
As shown in FIG. 5A, 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 FIG. 5B, a rotation restricting protrusion 74 that protrudes 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 movable to a position where it can come into contact with 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 to 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 projection 74 formed on the switching lever 64 enters between the rotation restricting portions 72 adjacent in the circumferential direction. Thereby, the state which the rotation control protrusion 74 and the rotation control surface 73 oppose in the circumferential direction is formed, and rotation of the 1st rotary body 522 is controlled by the rotation control protrusion 74 (refer FIG.6 (c)).

As shown in FIG. 6C, the rotation restricting protrusion 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. When the rotation restriction of the first rotating body 522 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. Therefore, when the rotation restriction of the first rotator 522 is released, the rotation restricting projection 74 does not press the first rotator 522 to forcibly rotate it.

  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 FIG. 6C) to a predetermined rotation position in the middle of rotating toward the output gear 54 (CCW direction), The leading end of the first clutch pawl 61 moves to a position on the −Z direction side of the leading end of the second clutch pawl 62, and the leading end of the first clutch pawl 61 and the second clutch pawl 62 are engaged with each other. The 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 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 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), 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 when an external force is applied to the wire 10 and a rotational torque is applied to the transmission wheel train 50 from the output shaft 13 side, the rotational torque is not transmitted, and the load that holds the pulley 11 at a position where the wire 10 is wound up by a predetermined amount. A holding state is formed. Specifically, when an external force for pulling out the wire 10 is applied in a state where the wire 10 is wound up by a predetermined amount, 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 rotation restriction mechanism 70 is switched to a load release state where the wire 10 can be pulled out by an external force and the wire 10 is pulled out, the clutch switching lever 64 moves 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 assembled by positioning in the rotational direction so as to have a positional relationship of being alternately arranged in the direction. Hereinafter, the rotational position of the rotor pinion 51 in which 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 FIG. 7). In this embodiment, since the number of the first clutch pawls 61 is 4, there are four regular positions 51A.

  The second clutch pawl 62 is formed on the shaft portion 452 of the rotor 45. The rotor 45 is disposed at a magnetically stable position when the motor 40 is in a non-excited state. In this embodiment, the second clutch pawl 62 is positioned by arranging the rotor 45 in a magnetically stable position. Therefore, it is not necessary to position the second clutch pawl 62 with 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 pawls 62 and the first clutch pawls 61 are alternately arranged in the circumferential direction when the rotor 45 is positioned at a magnetically stable position. If such a position is the normal position 51A, when the rotor pinion 51 is assembled, the second clutch pawl 62 is moved by the first clutch pawl 61, and the rotor 45 is moved from a position where it is magnetically stable. Can be avoided. Therefore, it is possible to avoid the assembly of the first clutch mechanism 60 in a state of being deviated 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 normal 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 one of two positions. The positioning mechanism 60A 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. Therefore, the positioning mechanism 60A includes a positioning recess 68 formed in the rotor pinion 51, a first rotating body 522 in which the positioning protrusion 69 is formed, and a rotation restricting mechanism 70 that restricts the rotational position of the first rotating body 522. .

  8 and 9 are explanatory diagrams of the operation 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. FIGS. 8A and 9A show a state where the rotor pinion 51 is positioned and incorporated. FIGS. 8B and 9B show a state where the rotor pinion 51 is rotated to a position where it engages 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 the end surface of the gear portion 510 in the + Z direction, and a protrusion A shaft portion 512 protruding in the + Z direction from the center of the portion 511 is provided. The shaft portion 512 is a portion that is pressed by the inclined cam 67 of the clutch switching lever 64 during the clutch engagement operation by the first clutch mechanism 60 described above.

  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 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 rotating body 522 in the + Z direction, and are arranged at equiangular intervals over the entire circumference of the first rotating body 522. At the end in the + Z direction of the first rotating body 522, an edge portion 691 extending in the circumferential direction over an angular range corresponding to two tooth grooves of the large-diameter gear portion 527 formed on the outer peripheral surface of the first rotating body 522. Is formed. A plurality of edge portions 691 are arranged at equiangular intervals on the outer peripheral edge of the first rotating body 522. The positioning protrusion 69 protrudes from the center in the circumferential direction of the edge 691 to the outer peripheral side. Therefore, the tip of the positioning protrusion 69 protrudes more outward than the tooth tip of the large-diameter gear portion 527 and is at the same angular position as the tooth tip 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 with the edge portion 691 in the axial direction (third direction Z).

  The rotor pinion 51 and the first rotating body 522 are assembled so as to have a positional relationship in which the positioning recess 68 and the positioning projection 69 are engaged. Then, in the positional relationship where the positioning recess 68 and the positioning projection 69 are engaged, the rotor pinion 51 is located at the normal position 51A where the first clutch mechanism 60 can be brought into the clutch engaged state. The positional relationship in which the positioning recess 68 and the positioning projection 69 are engaged 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. 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 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 two, and the number of teeth N2 of the large-diameter gear portion 527 is 48. Accordingly, eight 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. 6C and 8A). The positioning mechanism 60A is a direction in which the positioning protrusion 69 can be engaged with the positioning recess 68 in a state where the first rotating body 522 is positioned at the lock position 522A by the rotation restricting mechanism 70, that is, the direction of the rotation center of the rotor pinion 51. It 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 this embodiment, since the number of positioning recesses 68 is 8 and the number of rotation restricting portions 72 is 4, one of the positioning protrusions 69 always protrudes toward the rotation center of the rotor pinion 51 at the lock position 522A. To do.

  With the above configuration, the positioning mechanism 60A can engage the positioning recess 68 and the positioning projection 69 to determine the rotational positions of the first rotating body 522 and the rotor pinion 51, and as a result, the first rotating body can be assembled. When the 522 is positioned at the lock position 522A, the rotor pinion 51 is positioned at the normal position 51A. In this 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. Accordingly, during the clutch engagement operation, the first rotating body 522 is positioned at the lock position 522A by the rotation restricting mechanism 70, and as a result, the rotor pinion 51 is positioned at the normal position 51A. Therefore, 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 make sure 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 described above. There is no need. 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 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 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.

  In this 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 at two of the four regular positions 51A. The number of positioning recesses 68 may be one or four. That is, the positioning recess 68 may be any position and number that can position the rotor pinion 51 in at least one of the four regular positions 51A. Further, the lock position 522A by the rotation restricting mechanism 70 may be any position and number corresponding to at least one of the four regular positions 51A.

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

(Escape part)
On the outer peripheral surface of the first rotating body 522, an escape portion 692 is provided between the edge portions 691 adjacent in the circumferential direction. The escape portion 692 is a region where 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 this embodiment, each relief portion 692 has four tooth spaces. 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 are provided. 691 overlaps with 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 tooth portion of the rotor pinion 51 is 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 assembly work of the rotor pinion 51 is performed, the rotor pinion 51 is rotated by a predetermined amount after the positioning states shown in FIGS. 8A and 9A are formed. Thereby, as shown in FIG. 9B, a state in which the escape portion 692 faces the rotor pinion 51 can be formed. In the escape 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 and move the first rotating body 522 in the axial direction. ), 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 being moved in the + Z direction via the rotor pinion 51 and disengaging the gears of the planetary gear mechanism 52.

  In this embodiment, the escape portions 692 are provided one by one between the positioning protrusions 69 adjacent in the circumferential direction, and therefore, eight escape portions 692 are provided in total. However, it is sufficient that at least one escape portion 692 is provided. If there is at least one escape portion 692, the first rotating body 522 can be rotated until the escape portion 692 faces the rotor pinion 51, and the tooth portion of the rotor pinion 51 does not overlap the edge portion 691 in the axial direction. Can be formed. Therefore, it is possible to avoid the tooth portion of the rotor pinion 51 from pressing and moving 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. 3 and 1
As shown at 0 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. The second clutch mechanism 80 drives the lock lever 83 based on the rotation of the motor 40 to switch between the state where the rotation of the lock gear 84 and the speed increasing gear 85 is restricted and the state where it is not restricted. As a result, the state where the rotational torque is transmitted from the planetary gear mechanism 52 meshing with the speed increasing gear 85 to the speed reduction gear 53 is switched to the state where it is not transmitted. Therefore, it is possible to switch between a state in which the transmission wheel train 50 transmits the driving force and a state in which the driving force is not transmitted.

  The second clutch mechanism 80 includes a rotation restricting device 80 </ b> A that restricts the rotation of the lock gear 84 and the speed increasing gear 85. The rotation restricting device 80 </ b> A includes a guide ring 46, a planetary gear mechanism 81, a fan gear 82, a lock lever 83, and a 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 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 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. And a plurality of planetary gears 815 meshing with each other, and a third rotating body 816 that rotatably holds the plurality of planetary gears 815. 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 tooth portion 823 of 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 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 a metal portion 461 and a resin portion 462 (see FIG. 12), and the guide ring gear 464 is configured 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 part 461, and a magnetic force is generated by the eddy current, and a braking force that prevents relative rotation of the metal part 461 with respect to the magnet 451 is generated. . The induction ring 46 and the rotor 45 are coupled so as to rotate together by this braking force (braking force caused by eddy current).

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, in a state where the braking force due to the eddy current is applied to the induction ring 46, the second rotating body 814 that meshes with the induction ring 46 does not rotate, and the third rotating body 816 that 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 urged in the CCW direction by a torsion coil spring 86 that is an urging member. Accordingly, the fan gear 82 rotates against the urging 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 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. Specifically, as will be described later, an engagement pin 835 formed on the lock lever 83 is engaged with an 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 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. When rotation is restricted, the tip of a first arm portion 833 (described later) formed on the lock lever 83 and a projection 841 abut on the tangential direction of the outer peripheral surface of the lock gear 84.

  The second clutch mechanism 80 restricts the rotation of the speed increasing gear 85 when the lock lever 83 restricts 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 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 including 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, 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 caused by an eddy current 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 the rotational force. Since the braking force due to the eddy current 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 of the planetary gear mechanism 81. When the 814 rotates in the opposite direction to the first rotating body 812 and the eddy current is amplified and the braking force is amplified, 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 has the sector gear 82.
Cannot be held against the biasing force of the torsion coil spring 86, and the fan gear 82 rotates in the biasing direction of the torsion 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 the external load applied to the wire 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 meshing with the reduction gear 53. . Therefore, the load holding state of the wire 10 is released, and the wire 10 can be fed out by an external load.

(Structure of rotor and induction ring)
FIG. 12 is a cross-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 at the end portion in the −Z direction of the shaft portion 452. 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 center shaft portion 454 into which the fixed shaft 453 is inserted, and a cylindrical portion 455 that surrounds the outer peripheral side of the first center shaft portion 454. The cylindrical portion 455 and the first central shaft portion 454 extend from the lower end surface of the rotor gear 47 to the −Z direction side. At the lower end of the cylindrical portion 455, protrusions 455a are formed at two locations on the opposite side with respect to the central axis of the cylindrical portion 455. The second shaft portion 452B includes a substantially disc-shaped insert portion 456 and a second center shaft portion 457 protruding from the center of the insert portion 456 in the + Z direction. At the lower end of the magnet 451, an annular convex portion 451 a that protrudes to the inner peripheral side is formed, and the annular convex portion 451 a is inserted into the outer peripheral edge of the insert portion 456. In the insert portion 456, recesses 456a are formed at two locations on the opposite side with the second central shaft portion 457 as the center.

  When the guide 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. Thereafter, the cylindrical portion 455 of the first shaft portion 452A is dropped to the inner peripheral side of the guide ring 46. Accordingly, the rotor gear 47 having the same diameter as that of the guide ring gear 464 is disposed on the + Z direction side of the guide ring gear 464. When dropping the first shaft portion 452A 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. Accordingly, the first shaft portion 452A is prevented from rotating with respect to the second shaft portion 452B, and the first shaft portion 452A and the second shaft portion 452B are assembled so as to rotate integrally.

  Thus, in this embodiment, since the first shaft portion 452A on which the rotor gear 47 is formed and the second shaft portion 452B on which the magnet 451 is insert-molded are separated, the rotor gear 47 is placed on the inner peripheral side of the guide ring 46. There is no need to pass through. Therefore, since it is not necessary to make the outer diameter of the rotor gear 47 smaller than the inner diameter of the guide ring 46, the root circle of the guide ring gear 464 can be made smaller than the outer diameter of the rotor gear 47. Therefore, the large-diameter gear portion 818 is enlarged in order to ensure a gear ratio (reduction ratio) with the gear meshing with the guide ring gear 464 (in this embodiment, the large-diameter gear portion 818 of the second rotating body 814). There is no need to let them. Therefore, it is not necessary to secure an arrangement space for the large gear. In this embodiment, the guide ring gear 464 has the same diameter as the rotor gear 47, but the guide ring gear 464 may not have the same diameter as the rotor gear 47.

  Further, the positioning of the first shaft portion 452A in the axial direction (the third direction Z) is performed as shown in FIG. 12 with the tip surface 454a of the first center shaft portion 454 and the tip surface 457a of the second center shaft portion 457. Is made by abutting. The tip surfaces 454a and 457a of the first central shaft portion 454 and the second central shaft portion 457 are in contact with each other at substantially the center in the axial direction of the shaft portion 452. The first shaft 452A and the second shaft 452B are assembled with high accuracy because the rotation of the first shaft 452A and the positioning in the axial direction are different (first central shaft 454 and cylindrical portion 455). Can do.

(Torsion coil spring holding structure)
As described above, the lock lever 83 and the fan gear 82 rotate in conjunction with the engagement pin 835 formed on the lock lever 83 being engaged with the engagement recess 828 formed on the fan gear 82. It is assembled as follows. The fan gear 82 is urged in the CCW direction by a torsion coil spring 86. The fan gear 82 of this embodiment includes a coil spring holding portion 824 that can hold the torsion coil spring 86 so as not to drop 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 that protrude 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 to 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. 14 (a) is a perspective view showing a state where the torsion coil spring 86 is removed from the fan gear 82, and FIG. 14 (b) is a fan. It is the top view which looked at the gear 82 from + 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 the end of the shaft portion 822 in the −Z direction. The shaft portion 822 includes a central portion 825 that extends linearly in the third direction Z, and a cylindrical portion 826 that surrounds the outer peripheral side of the portion on the −Z direction side of the central portion 825. An end portion in the + Z direction of the cylindrical portion 826 is connected to the center portion 825. In addition, a protruding portion 827 that protrudes to the outer peripheral side is formed at the end portion of the cylindrical portion 826 in the + Z direction. The protrusion 827 is formed with an engagement recess 828 that opens to the outer peripheral side.

  The cylindrical portion 826 is formed with a notch 826a in which a part in the circumferential direction is notched. The notch 826a includes a narrow opening groove connected to the −Z direction edge of the cylindrical portion 826, and a wide portion having a stepped width on one side in the circumferential direction on the + Z direction side of the opening groove. By expanding the circumferential width of the notch 826a stepwise, an arm portion 829 extending in an arc shape in the circumferential direction is formed along the −Z direction side edge of the cylindrical portion 826. The coil spring holding portion 824 includes an end portion on the −Z direction side of the center portion 825 and an arm portion 829.

  The torsion coil spring 86 includes a coil portion 861 in which a wire is wound in a coil shape, and two spring legs 862 and 863 projecting outward from the coil portion 861. As shown in FIG. 11, the coil portion 861 is attached to the end portion in the −Z direction of the center portion 825 of the fan gear 82. At this time, the spring leg 862 protruding from the end on the + Z direction side of the coil portion 861 is inserted into the notch 826a. The notch 826a extends from the −Z direction edge of the cylindrical portion 826 to at least the + Z direction side of the arm portion 829 (that is, the engagement position of the spring leg 862 with respect to the arm portion 829). The position of the torsion coil spring 86 in the third direction Z is restricted by the other spring leg 863 coming into contact with the end surface 826b (see FIG. 14A) of the cylindrical portion 826 in the -Z direction. When the coil portion 861 is rotated in the circumferential direction in this state, a state where 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 such that the end surface 826b in the −Z direction of the cylindrical portion 826 with which the spring foot 863 abuts and the end surface 826c in the + Z direction 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 a position restricting portion that restricts the position of the torsion coil spring 86 in the third direction Z. Further, the end portion on the −Z direction side of the center portion 825 inserted on the inner peripheral side of the coil portion 861 is located at a position protruding to the −Z direction side from the end surface 826b on the −Z direction side of the cylindrical portion 826. Therefore, when the fan gear 82 is assembled so that the end portion in the −Z direction of the center portion 825 comes into contact with the support plate 42, the gap for disposing the spring feet 863 in the gap between the support plate 42 and the end surface 826 b 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. Thereby, the urging force of the torsion coil spring 86 acts on the fan gear 82. The other spring leg 863 abuts on a fixed shaft 831 disposed at the center of rotation 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 leg 863 is disposed. The spring leg 863 contacts the outer peripheral surface of the fixed shaft 831 exposed to the outside from the notch 836. In this embodiment, the fixed shaft 831 with which the spring foot 863 abuts is a metal shaft. Note that the fixed shaft 831 may not be made of metal.

  FIG. 15 is an exploded perspective view of the motor 40 and the second clutch mechanism 80. When the second clutch mechanism 80 is assembled, as shown in FIG. 15, the rotor 45 to which the guide ring 46 is assembled is assembled at the center of the support plate 42, and the speed increasing gear 85 is assembled. It should be noted that the speed increasing gear 85 may be assembled before the fan gear 82 and the lock lever 83 are assembled and before the lock gear 84 is assembled.

  Subsequently, the torsion coil spring 86 and the fan gear 82 are assembled 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 falling off the fan gear 82. At this time, the spring leg 863 on the −Z direction side 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. Subsequently, the lock lever 83 is assembled 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. Thereafter, the planetary gear mechanism 81 is assembled, and finally the lock gear 84 is assembled.

  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, the fan gear 82 can be provided with an arm portion that abuts on the lock gear 84 and can be engaged with the protrusion 841. However, in this case, it is necessary to separately provide a portion with which the spring foot 863 abuts. 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. For example, a member that moves in the axial direction based on the rotation of the fan gear 82 and restricts the rotation of the lock gear 84 can be provided.

  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 90)
FIG. 16A is a perspective view of the reverse rotation prevention mechanism 90, and FIG. 16B is a plan 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. At the time of start-up, it is assumed that the wire 10 is pulled out to a position where the drain valve is closed. 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 torsion 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 the lock gear 84 is moved. Lock it. 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 winding operation of the wire 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. As a result, the relative rotational speed of the rotor 45 and the induction ring 46 is increased, the braking force due to the eddy current generated between the induction 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 finished, 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. Therefore, the wire 10 is not wound more than a predetermined winding amount. 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 out the wire 10 is applied, the load 10 is kept in a state where the wire 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 turns off the power to the motor 40 in the load holding state, the drain valve driving device 1 shifts to a load releasing state in which the wire 10 can be pulled out by an external force. When the motor 40 is de-energized, the rotation of the rotor 45 stops. In the second clutch mechanism 80, since the fan gear 82 returns to the biasing direction of the torsion coil spring 86 when the rotation of the rotor 45 stops, the engagement between the lock lever 83 and the lock gear 84 is released, and the rotation restricting device 80A locks the second clutch mechanism 80. The rotation restriction of the gear 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 wire 10 is applied, the transmission wheel train 50 is idled and the wire 10 is pulled out. A brake rubber 87 is incorporated in the lock gear 84. The brake rubber 87 expands by a centrifugal force when the wire 10 is pulled out by an external force and generates a frictional force with the lock gear 84. Thereby, the drawing speed when the wire 10 is pulled out decreases. Therefore, the risk of breakage due to the wire 10 being pulled out abruptly can be reduced.

  When the wire 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 wire 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 rotation of the motor 40 to the output shaft 13. A second clutch mechanism 80 that switches between a state in which the transmission wheel train 50 transmits rotational torque and a state in which it does not transmit is provided. The second clutch mechanism 80 includes a train wheel (speed increasing gear 85 and lock gear 84) that meshes with the second rotating body 524 of the transmission train wheel 50, and a rotation restricting device 80A that restricts the rotation of the train wheel. The rotation restricting device 80A restricts the rotation of the lock gear 84 (rotary body) by rotating the fan gear 82 and the lock lever 83 based on the rotation of the rotor 45. Further, the rotation restricting device 80A returns the fan gear 82 (rotation restricting member drive gear) and the lock lever 83 (rotation restricting member) by the urging force of the torsion coil spring 86 when the power to the rotor 45 is cut off, and locks the lock. The rotation restriction of the gear 84 is released.

  The rotation restricting device 80 </ b> A of this embodiment biases the fan gear 82 and the lock lever 83 in the return direction by the torsion coil spring 86 attached to the shaft portion 822 of the fan gear 82. In this case, it is not necessary to separately provide a shaft for attaching the torsion coil spring 86, so that a space for arranging the torsion coil spring 86 can be reduced. A coil spring holding portion 824 that can hold the torsion coil spring 86 so as not to drop in the axial direction (third direction Z) is formed on the shaft portion 822 of the fan gear 82. Therefore, the fan gear 82 and the torsion coil spring 86 can be assembled together while the torsion coil spring 86 is held by the fan gear 82. In this way, the work of attaching the torsion coil spring 86 is easy.

  The coil spring holding portion 824 of this embodiment passes the center portion 825 through the coil portion 861 of the torsion coil spring 86 and engages and holds the spring foot 862 with the arm portion 829 arranged on the outer peripheral side of the coil portion 861. In such a holding structure, the torsion coil spring 86 is unlikely to fall off in the axial direction (third direction Z). Therefore, it is easy to assemble the fan gear 82 and the torsion coil spring 86 together. Further, the arm portion 829 with which the spring foot 862 engages is formed by cutting out the cylindrical portion 826, and only the spring foot 862 is inserted into the notch 826a formed in the cylindrical portion 826 and rotated in the circumferential direction. Thus, the spring leg 862 can be engaged with the arm portion 829. Therefore, the assembling work of the torsion coil spring 86 is easy.

  The coil spring holding portion 824 of this embodiment is configured such that the positions of the spring legs 862 and 863 are regulated by the end surface 826b of the cylindrical portion 826 in the −Z direction and the end surface 826c of the arm portion 829 in the + Z direction. The position in the third direction Z is restricted. By providing such a position restricting portion (end faces 826b, 826c), the positional accuracy of the torsion coil spring 86 in the axial direction (third direction Z) can be increased. Therefore, the torsion coil spring 86 can be attached at an accurate position. The spring leg 862 is assembled so as to abut on the inner edge 826d of the notch 826a in the circumferential direction. Therefore, the other spring leg 863 can be easily rotated and assembled against the torsional moment of the torsion coil spring 86.

  In the rotation restricting device 80A of this embodiment, a notch 836 is formed in the shaft portion 832 of the lock lever 83, and the fixed shaft 831 of the lock lever 83 is exposed to the outside. The spring leg 863 of the torsion coil spring 86 abuts on the outer peripheral surface of the fixed shaft 831 exposed to the outside from the notch 836. In this way, the torsion coil spring 86 can be assembled with the fixed shaft 831 positioned at the rotation center of the lock lever 83 as a reference. Therefore, the positional accuracy of the torsion coil spring 86 can be increased. Thereby, the operation | movement precision of the fan gear 82 and the lock lever 83 can be raised, and a malfunction can be suppressed. Further, since the spring foot 863 is supported not by the outer peripheral surface of the rotating shaft portion 832 but by the fixed shaft 831, the influence of the pressing force from the spring foot 863 affects the operation of the lock lever 83 which is a rotating member. Can be avoided. That is, when the outer peripheral surface of the shaft portion 832 is pressed by the spring foot 863, a sliding load is generated between the spring foot 863 and the outer peripheral surface of the shaft portion 832 when the lock lever 83 is operated, Although this affects the operation, such an influence can be eliminated.

In the rotation restricting device 80 </ b> A of this embodiment, an engagement recess 828 in which an engagement pin 835 formed on the lock lever 83 is engaged is provided in the fan gear 82. The engaging recess 828 is formed in the cylindrical portion 826 of the fan gear 82. The cylindrical portion 826 is formed with an arm portion 829 that engages with the spring foot 862. Thus, by forming the engaging recess 828 and the arm portion in the same cylindrical portion, the structure can be simplified and the strength can be secured. In addition, since the engaging recess 828 and the arm portion 829 can be provided on the inner peripheral side from the outer peripheral surface of the cylindrical portion 826, a compact configuration can be achieved.

  The rotation restricting device 80 </ b> A of this embodiment inputs a rotation in the direction opposite to the rotation direction of the rotor 45 to the induction ring 46 by the operation of the planetary gear mechanism 81, so that the magnet 451 provided on the rotor 45 and the induction ring 46 are relatively Increase rotational speed. As a result, the braking force due to the eddy current generated between the induction ring 46 and the magnet 451 is amplified, so that the holding force (brake torque) for holding the lock lever 83 in the locked state can be increased. Therefore, a stable locked state can be formed.

  The drain valve driving device 1 of the present embodiment interrupts transmission of rotational torque by the transmission wheel train 50 by the rotation restricting device 80A. Since the rotation restricting device 80A can form a stable locked state, the operation of the drain valve driving device 1 can be stabilized.

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 ... Peripheral rib, 17 ... concave portion, 18 ... convex portion, 19 ... opening, 20 ... case, 21 ... first case, 22 ... second case, 23 ... terminal accommodating portion, 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: Normal position, 51B: Connection position, 51C: Separation position, 52 ... Planetary gear mechanism, 53 ... Reduction gear, 54 ... Output gear, 55 ... Projection, 60 ... First clutch mechanism, 60A ... Position 61, first clutch pawl, 62 ... second clutch pawl, 63 ... coil spring, 64 ... clutch switching lever, 64A ... clutch disengagement position, 64B ... clutch engagement position, 64C ... intermediate 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 part, 73 ... Rotation restricting surface, 74 ... 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 ... torsion coil spring, 87 ... brake rubber, 90 DESCRIPTION OF SYMBOLS ... Reverse rotation prevention mechanism, 91 ... Reverse rotation prevention protrusion, 92 ... Reverse rotation prevention lever, 93 ... Disc part, 94 ... Bending part, 95 ... Arm part, 96 ... End surface, 97 ... Fixed shaft, 98 ... Leaf spring, 4 DESCRIPTION OF SYMBOLS 1 ... Magnet, 451a ... Annular convex part, 452 ... Shaft part, 452A ... 1st shaft part, 452B ... 2nd shaft part, 453 ... Fixed axis | shaft, 454 ... 1st center shaft part, 454a ... Tip surface, 455 ... Tube 455a ... projection, 456 ... insert part, 456a ... recess, 457 ... second central shaft part, 457a ... tip surface, 461 ... metal part, 462 ... resin part, 463 ... collar part, 464 ... induction ring gear, 465 ... Bearing portion, 510 ... Gear portion, 511 ... Projection portion, 512 ... Shaft portion, 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 section, 532 ... Small diameter gear section, 533 ... Fixed shaft, 691 ... Edge, 692 ... Escape , 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 section, 818 ... large diameter Gear portion, 819 ... Small gear portion, 821 ... Fixed shaft, 822 ... Shaft portion (first shaft portion), 823 ... Fan tooth portion, 824 ... Coil spring holding portion, 825 ... Center portion, 826 ... Cylindrical portion, 826a ... Notch, 826b ... end face (position restricting part), 826c ... end face (position restricting part), 826d ... inner edge, 827 ... projecting part, 828 ... engaging recess, 829 ... arm part, 831 ... fixed shaft, 832 ... shaft part (Second shaft part), 833 ... first arm part, 834 ... second arm part, 835 ... engagement pin, 836 ... notch, 841 ... projection part, 842 ... large diameter part, 843 ... small diameter gear part, 851 ... large diameter gear part, 852 ... small diameter gear part, 861 ... coil part, 862 863 ... Baneashi, B1 ... movement trajectory, X ... first direction, Y ... second direction, Z ... third direction

Claims (9)

A rotation regulating device that regulates rotation of a rotating body by a rotation regulating member that is driven based on rotation of a rotor,
A rotation restricting member driving gear that drives the rotation restricting member or rotates integrally with the rotation restricting member;
A torsion coil spring that biases the rotation restricting member drive gear in a direction opposite to the direction rotated based on the rotation of the rotor;
The rotation restricting device drive gear includes a coil spring holding portion that holds the torsion coil spring. A planetary gear mechanism for rotating the rotation regulating member drive gear based on the rotation of the rotor;
A guide ring facing the magnet provided in the rotor,
The planetary gear mechanism includes a first rotating body formed with a sun gear, a second rotating body formed with an internal gear, a planetary gear meshing with the sun gear and the internal gear, and the planetary gear rotating. A third rotating body provided with a planetary carrier to support it;
The guide ring is provided with a guide ring gear that meshes with a gear formed on one of the first rotating body and the second rotating body,
The other of the first rotating body and the second rotating body is provided with a gear that meshes with a rotor gear formed on the rotor,
The rotation restricting device according to claim 1, wherein the rotation restricting member driving gear rotates based on rotation of the third rotating body. The rotation restricting member driving gear is a fan gear including a first shaft portion provided with the coil spring holding portion and a fan tooth portion formed integrally with the first shaft portion,
The coil spring holding portion includes a central portion that is passed through the coil portion of the torsion coil spring, and an arm portion that extends in the circumferential direction on the outer peripheral side of the coil portion,
The rotation restricting device according to claim 1, wherein one spring leg of the torsion coil spring is engaged with the arm portion. The rotation restricting member is a lock lever including a second shaft portion rotatably attached to a fixed shaft, and a first arm portion protruding from the second shaft portion,
The second shaft portion is formed with a notch that exposes the fixed shaft to the outside.
The rotation restricting device according to claim 3, wherein the other spring leg of the torsion coil spring is in contact with an outer peripheral surface of the fixed shaft exposed to the outside by the notch. The rotation restricting member includes an engagement pin formed on a second arm portion protruding from the second shaft portion,
In the rotation restricting member drive gear, the first shaft portion includes a cylindrical portion surrounding an outer peripheral side of the center portion,
The rotation restricting device according to claim 4, wherein the cylindrical portion is formed with an engagement recess capable of engaging the arm portion and the engagement pin.   The rotation restriction according to claim 5, wherein the cylindrical portion includes a notch, and the notch extends from an axial edge of the cylindrical portion to an engagement position of the spring foot with respect to the arm portion. apparatus.   The rotation restricting device according to any one of claims 1 to 6, wherein the coil spring holding portion includes a position restricting portion that restricts an axial position of the torsion coil spring. The rotation restricting device according to any one of claims 1 to 7,
A motor comprising the rotor;
A transmission gear train having a gear meshing with a gear train including a gear provided on the rotating body;
And a drain valve driving member that is driven based on rotation of an output gear of the transmission wheel train. A clutch mechanism for interrupting transmission of rotational torque by the transmission wheel train;
The rotating body is a lock gear provided in the clutch mechanism,
In a state where the rotation of the lock gear is regulated by the rotation regulating member, the transmission wheel train transmits rotational torque,
The drain valve driving device according to claim 8, wherein the transmission wheel train does not transmit rotational torque in a state where the rotation restriction of the lock gear by the rotation restriction member is released.

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