JP2017155903A - Induction ring and drain valve driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve dimensional accuracy of a bearing portion formed on an induction ring.SOLUTION: A drain valve driving device 1 includes a second clutch mechanism 80 for switching a rotating torque transmission state and a non-transmission state of a transmission wheel train 50. The second clutch mechanism 80 includes a lock lever 83, a fan gear 82, a coil spring 86, a planetary gear mechanism 81, and an induction ring 46, and the rotation in a direction opposite to a rotating direction, of a rotor 45 is input to the induction ring 46 by operation of the planetary gear mechanism 81. The induction ring 46 has a metallic portion 461 composed of a non-magnetic metal and radially opposed to a magnet 451, and a resin portio 462 holding the metallic portion 461, and manufactured by insert-molding the metallic portion 461 to a resin. The resin portion 462 includes a bearing portion 466 slidably kept into contact with a shaft portion 452. The bearing portion 466 is disposed on a position radially overlapped to the metallic portion 461.SELECTED DRAWING: Figure 9

Description

  The present invention relates to a drain valve driving device including a guide ring and a clutch mechanism using the guide ring.

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

  Patent Document 1 discloses a geared motor used in this type of drain valve driving device. The geared motor of Patent Document 1 meshes with a gear member of a transmission wheel train that transmits driving force to a driving member that drives a drain valve or the like (in Patent Document 1, a case member in which an internal gear of a planetary gear mechanism is formed). And a switching member (rotation restricting member) that prevents the rotation of the lever. The switching member is operated by a clutch driving motor.

JP 2002-247804 A

  In the geared motor of Patent Document 1, in order to hold a switching member (rotation restricting member) that restricts the rotation of the gear member at the clutch coupling position, a magnet and an induction ring are provided between the rotor of the clutch driving motor and the switching member. A holding mechanism is installed that is opposed to each other in the radial direction. When the magnet provided on the rotor rotates, a magnetic induction force is generated between the magnet and the induction ring. This magnetic induction force becomes a holding force for holding the switching member at the clutch coupling position.

  When a mechanism that uses a magnetic induction force generated between the induction ring and the magnet is configured, a metal part made of a nonmagnetic metal is insert-molded into a resin as the induction ring. In this type of induction ring, a bearing portion for rotatably attaching the induction ring to the shaft portion is formed in the resin portion that holds the metal portion. Here, when the guide ring is disposed to face the magnet, it is required to increase the positional accuracy of the metal portion with respect to the magnet. For this purpose, it is required to increase the dimensional accuracy of the resin portion. In particular, it is required to increase the dimensional accuracy of the bearing portion (roundness and coaxiality with the metal portion).

  In view of such a point, the object of the present invention is to form a guide ring in a guide ring having a structure in which a metal part made of a nonmagnetic metal is held by a resin part and a drain valve driving device using this kind of guide ring. It is to improve the dimensional accuracy of the bearing portion.

In order to solve the above-described problems, the present invention provides a guide ring that is rotatably supported by a shaft portion, and is a metal portion made of a nonmagnetic metal that is radially opposed to a magnet disposed coaxially with the shaft portion. And a resin part that holds the metal part, the resin part includes a bearing part that is in sliding contact with the shaft part, and the bearing part is provided at a position that overlaps the metal part in a radial direction. It is characterized by being.

  According to the present invention, in a guide ring including a metal part made of a nonmagnetic metal and a resin part, the bearing part and the metal part formed in the resin part overlap in the radial direction. In such a configuration, when the induction ring is manufactured by insert-molding the metal part into the resin, the bearing part is not easily affected by the shrinkage deformation of the resin at the time of molding. Therefore, since deformation of the bearing portion can be suppressed, the dimensional accuracy of the bearing portion can be increased.

  In the present invention, it is desirable that the metal portion includes a cylindrical portion that overlaps with the bearing portion in a radial direction and a flange portion that extends in a radial direction from one axial end of the cylindrical portion. If the metal part is provided with the flange part, the structure for holding the metal part in the mold at the time of insert molding can be simplified. Therefore, the mold structure can be simplified, which is advantageous for cost reduction.

  In the present invention, it is preferable that a rotation stop portion is provided in the collar portion, and an engagement portion that engages with the rotation stop portion is provided in the resin portion. If it does in this way, the integrity of a metal part and a resin part can be improved.

  Next, the present invention provides a clutch mechanism including the induction ring, a rotor including the magnet, a motor including a stator, a transmission wheel train to which rotation of the rotor is input, and an output gear of the transmission wheel train. And a drain valve drive member driven based on the rotation of the clutch, wherein the clutch mechanism interrupts transmission of rotational torque by the transmission wheel train.

  According to the present invention, the induction ring that faces the magnet of the rotor in the radial direction is used for the clutch mechanism that interrupts transmission of rotational torque by the transmission wheel train. Therefore, the clutch mechanism can be held in the clutch engaged state or the clutch disengaged state using the magnetic induction force generated between the magnet and the induction ring. Therefore, the operation of the drain valve driving device can be stabilized.

  In the present invention, the rotor includes the shaft portion, the magnet is held by the shaft portion, and a structure is employed in which an annular recess is disposed between the shaft portion and the guide ring. it can. If it does in this way, since the induction | guidance | derivation ring is comprised so that the resin part and the metal part may overlap in radial direction, thickness of radial direction can be made thin. Therefore, the shaft portion can be thickened, and a gear shape for transmitting the rotation of the rotor can be provided in the shaft portion.

  In the present invention, the clutch 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. A planetary gear mechanism including a third rotating body provided with a planetary carrier that rotatably supports the gear; and a rotation regulating member that is driven based on the rotation of the third rotating body. 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, and formed on the shaft portion on the other of the first rotating body and the second rotating body. A structure in which a gear meshing with the rotor gear is provided can be adopted. In this case, when the rotation restricting member connected to the third rotating body stops in the clutch connected state or the clutch disengaged state, the first rotating body and the second rotating body rotate in opposite directions. A 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 magnetic induction force 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, and the operation of the drain valve driving device can be stabilized.

  In the induction ring of the present invention, since the bearing portion and the metal portion formed in the resin portion are overlapped in the radial direction, when the induction ring is manufactured by insert molding the metal portion into the resin, the bearing portion is Resistant to shrinkage deformation of resin. Therefore, deformation of the bearing portion can be suppressed, and the dimensional accuracy of the bearing portion can be increased. In addition, the operation of the drain valve driving device including the clutch mechanism using the induction ring can be stabilized.

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

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

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

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

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

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

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

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

The rotor 45 includes a substantially cylindrical magnet 451 and a shaft portion 452 disposed on the inner peripheral side of the magnet 451. The rotor 45 is formed by insert-molding a magnet 451 made of a ferrite magnet or the like at the end of the shaft portion 452 in the −Z direction. An annular recess is provided between the magnet 451 and the shaft 452, and a guide ring 46 described later is disposed here. The shaft portion 452 protrudes toward the + Z direction side of the guide ring 46, and a rotor gear 47 (see FIG. 9) is formed on the outer peripheral surface thereof. The rotor gear 47 is a gear that transmits the rotation of the rotor 45 to the second clutch mechanism 80, as will be described later. A fixed shaft 453 that rotatably supports the rotor 45 is disposed at the center of the rotor 45. The fixed shaft 453 extends in the third direction Z. One end of the fixed shaft 453 is fixed to the motor case 41 by press fitting or the like, and the other end of the fixed shaft 453 is fixed to the third case 23 by press fitting or the like.

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

(Transmission train)
The transmission wheel train 50 transmits the driving force of the motor 40 to the output pinion 12 of the rack-pinion mechanism that drives the slider 10. As shown in FIGS. 3 and 4, the transmission wheel train 50 includes a rotor pinion 51, a planetary gear mechanism 52, a reduction gear 53, and an output gear 54. The rotation center axis of the rotor pinion 51 is the O axis, the rotation center axis of the planetary gear mechanism 52 is the C axis, the rotation center axis of the reduction gear 53 is the B axis, and the rotation center axis of the output gear 54 is the A axis. It is. The transmission wheel train 50 transmits the driving force of the motor 40 in this order. The output pinion 12 is attached to the end of the output gear 54 in the Z direction and rotates integrally with the output gear 54. Accordingly, the slider 10 as the drain valve driving member is driven based on the rotation of the output gear 54.

  The rotor pinion 51 is formed of resin, and is supported by a fixed shaft 453 of the rotor 45 so as to be rotatable and movable in the axial direction (that is, the third direction Z). A first clutch mechanism 60 is provided between the rotor pinion 51 and the rotor 45. By switching the connection state of the first clutch mechanism 60, the rotor pinion 51 rotates integrally with the shaft 452 of the rotor 45 (clutch connection state), and the rotor pinion 51 does not rotate integrally with the shaft 452. (Clutch disengaged state).

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

When the rotation of the second rotating body 524 is restricted, the third rotating body 526 that is a planet carrier rotates based on the rotation of the sun gear 521. A small-diameter gear portion 529 that meshes with the large-diameter gear portion 531 of the reduction gear 53 is formed at the end portion of the third rotating body 526 in the −Z direction. That is, the planetary gear mechanism 52 is configured to transmit rotational torque to the reduction gear 53 when the rotation of the second rotating body 524 is restricted via the speed increasing gear 85 of the second clutch mechanism 80. On the other hand, when the speed increasing gear 85 of the second clutch mechanism 80 is switched to the idling state, even if the planetary gear 525 tries to revolve, the second rotating body 524 having the internal gear 523 is idling, so that the planet carrier The third rotating body 526 is not rotated. Therefore, the reduction gear 5
No rotation torque is transmitted to 3.

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

(First clutch mechanism)
5 and 6 are exploded perspective views of the motor 40, the transmission wheel train 50, the first clutch mechanism 60, and the rotation restricting mechanism 70. FIG. 5 is an exploded perspective view seen from the + Z direction side, and FIG. It is the disassembled perspective view seen from the direction side. As shown in FIGS. 5 and 6, the first clutch mechanism 60 includes a first clutch pawl 61 formed on the end surface of the rotor pinion 51 in the −Z direction and a second clutch formed on the shaft portion 452 of the rotor 45. The claw 62, the coil spring 63 that urges the rotor pinion 51 in the direction away from the shaft portion 452 (in the + Z direction in this embodiment), and the rotor pinion 51 are pushed down toward the shaft portion 452 side (−Z direction) to be A fan-shaped clutch switching lever 64 for switching the 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. 6, the clutch switching lever 64 is formed with a cam pin 65 and an inclined cam 67 protruding in the −Z direction. The cam pin 65 is formed on the edge of the clutch switching lever 64 on the output gear 54 side, and is inserted into a cam groove 66 formed on the end surface of the output gear 54 in the + Z direction.

  The inclined cam 67 includes an inclined surface extending in the circumferential direction. When the clutch switching lever 64 rotates to the output gear 54 side, 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 a result, the first clutch pawl 61 and the second clutch pawl 62 are engaged, and the first clutch mechanism 60 switches to a clutch engaged state in which the rotor pinion 51 rotates integrally with the shaft portion 452. On the other hand, when the clutch switching lever 64 rotates to the planetary gear mechanism 52 side and moves to the clutch disengagement position 64A shown in FIG. 3, the inclined cam 67 is retracted from the position where it overlaps the rotor pinion 51. The rotor pinion 51 moves in the + Z direction. Thereby, the engagement between the first clutch pawl 61 and the second clutch pawl 62 is released, and the first clutch mechanism 60 is switched to the clutch disengaged state (see FIGS. 5 and 6).

  The clutch switching lever 64 rotates in conjunction with the rotation of the output gear 54. That is, the clutch switching lever 64 rotates toward the output gear 54 via the cam pin 65 and the cam groove 66 in conjunction with the rotation of the output gear 54 in the CW direction. Further, when the output gear 54 rotates in the CCW direction, the projection 55 protruding in the + Z direction from the output gear 54 presses the clutch switching lever 64 and rotates it toward the planetary gear mechanism 52 side. The drain valve driving device 1 starts drainage by rotating the output gear 54 in the rotation direction (that is, the CCW direction) when the slider 10 is pulled to the case 20 side, and the position of the protrusion 55 of the output gear 54 is the output. The clutch switching lever 64 is set so as to rotate toward the planetary gear mechanism 52 (in the CW direction) when the gear 54 reaches a predetermined rotational position. For this reason, when the slider 10 is retracted to the vicinity of the retracted position 10A, the above-described clutch disengaging operation is performed. As a result, the driving force of the motor 40 is not transmitted to the rotor pinion 51, and the operation of the transmission wheel train 50 is stopped. Therefore, the slider 10 can be prevented from being pulled in beyond the predetermined pulling position 10A, and excessive pulling of the slider 10 can be prevented.

A protruding portion that protrudes in the + Z direction is provided on the end surface of the rotor pinion 51 in the + Z direction. The protrusion is formed with a positioning recess 68 for positioning the first rotating body 522 of the planetary gear mechanism 52 and the rotor pinion 51 in the rotation direction when the rotor pinion 51 is assembled. Further, the first rotating body 522 of the planetary gear mechanism 52 is formed with a positioning projection 69 that engages with the positioning recess 68 of the rotor pinion 51. The positioning projections 69 protrude in the radial direction from the end in the + Z direction of the large-diameter gear portion 527 and are arranged at equal angular intervals in the circumferential direction.

  The rotor pinion 51 has a positioning recess 68 formed in the rotor pinion 51 and a positioning protrusion 69 formed on the first rotating body 522 of the planetary gear mechanism 52 when the first clutch mechanism 60 is in the clutch engaged state. Positioning in the rotational direction is performed and assembled so that the positional relationship is engaged. In the rotor pinion 51, the positioning recess 68 is formed at an angular position corresponding to the first clutch pawl 61. For example, in this embodiment, the first clutch pawl 61 and the positioning recess 68 are all provided at four locations at equal angular intervals. Further, the positioning protrusions 69 formed on the first rotating body 522 are provided at 16 positions at equal angular intervals. In such an arrangement, when one of the positioning protrusions 69 is engaged with the positioning recess 68, the rotational position of the rotor pinion 51 is such that the leading end of the first clutch pawl 61 and the leading end of the second clutch pawl 62 The rotor pinion 51 can be assembled so that the rotation position does not interfere with each other.

(Rotation restriction mechanism)
As shown in FIG. 5, the first rotating body 522 of the planetary gear mechanism 52 is formed with a protruding portion 71 that protrudes in the + Z direction from the end surface in the + Z direction of the large-diameter gear portion 527. A plurality of rotation restricting portions 72 projecting in the radial direction are formed on the projecting portion 71 at equal angular intervals. Each rotation restricting portion 72 is formed with a rotation restricting surface 73 that faces one side in the circumferential direction (CW direction).

  As shown in FIGS. 5 and 6, a rotation restricting protrusion 74 protruding in the −Z direction is formed on the edge of the clutch switching lever 64 on the planetary gear mechanism 52 side. As described above, when the slider 10 is retracted and the clutch switching lever 64 moves to the clutch disengagement position 64A (see FIG. 3) on the planetary gear mechanism 52 side, the rotation restricting protrusion formed on the clutch switching lever 64 is formed. 74 enters between the rotation restricting portions 72 adjacent in the circumferential direction. Thus, a state is formed in which the rotation restricting protrusion 74 and the rotation restricting surface 73 are opposed to each other in the circumferential direction, and the rotation restricting protrusion 74 restricts the rotation of the first rotating body 522.

  In the planetary gear mechanism 52, since the rotation of the second rotating body 524 is restricted by the speed increasing gear 85 when the drain valve driving device 1 is started as described above, the rotation restricting mechanism 70 restricts the rotation of the first rotating body 522. If it does, rotation of the 3rd rotary body 526 which meshes with the reduction gear 53 will also be controlled, and it will be in a locked state. Therefore, even if an external force is applied to the slider 10 and a rotational torque is applied to the transmission wheel train 50 from the output pinion 12 side, the rotational torque is not transmitted, and a load holding state in which the slider 10 is held at the retracted position 10A is formed. . Specifically, when an external force that pulls the slider 10 in the + X direction is applied in a state where the slider 10 is pulled to the pulling position 10 </ b> A, a rotational torque in the CW direction is applied to the first rotating body 522. At this time, the rotation restricting protrusion 74 abuts against the rotation restricting surface 73 and restricts the rotation of the first rotating body 522 in the CW direction.

(Second clutch mechanism)
7 and 8 are perspective views of the rotor 45, the second clutch mechanism 80, and the reverse rotation prevention mechanism 90. FIG. 7 is a perspective view seen from the + Z direction side, and FIG. 8 is a perspective view seen from the −Z direction side. It is. As shown in FIGS. 3, 4, 7, and 8, the second clutch mechanism 80 includes a planetary gear mechanism 81 in which the rotation of the rotor 45 is transmitted via the guide ring 46, a fan gear 82, and a lock lever 83. A lock gear 84, a speed increasing gear 85, and a coil spring 86. The second clutch mechanism 80 includes a rotation restricting device 80A that restricts the rotation of the lock gear 84 and the speed increasing gear 85. The rotation restricting device 80A includes the guide ring 46, the planetary gear mechanism 81, the fan gear 82, and the lock lever. 83 and a coil spring 86. In the rotation restricting device 80A, the lock lever 83 is a rotation restricting member that restricts the rotation of the lock gear 84 that is a rotating body, and the fan gear 82 is a rotation restricting member driving gear that rotates the lock lever 83. As shown in FIGS. 3 and 4, the rotation center axis of the planetary gear mechanism 81 is the H axis, the rotation center axis of the fan gear 82 is the G axis, and the rotation center axis of the lock lever 83 is the F axis. The rotation center axis of the lock gear 84 is the E axis, and the rotation center axis of the speed increasing gear 85 is the D axis.

  FIG. 9 is a sectional view of the rotor 45 and the planetary gear mechanism 81. The planetary gear mechanism 81 includes a first rotating body 812 formed with a sun gear 811, a second rotating body 814 formed with an internal gear 813, and a plurality of planetary gears 815 that mesh with the sun gear 811 and the internal gear 813. And a third rotating body 816 that rotatably holds the plurality of planetary gears 815. As shown in FIG. 9, the first rotating body 812 includes a large-diameter gear portion 817 that meshes with the rotor gear 47 formed on the shaft portion 452 of the rotor 45. Further, a large-diameter gear portion 818 that meshes with a guide ring gear 464 formed on the guide ring 46 disposed on the outer peripheral side of the shaft portion 452 is formed on the outer peripheral surface of the second rotating body 814. A small-diameter gear portion 819 that meshes with the fan gear 82 is provided at the end of the third rotating body 816 in the −Z direction.

  As described above, the guide ring 46 is disposed between the magnet 451 and the shaft portion 452. The guide ring 46 includes a cylindrical metal portion 461 made of a nonmagnetic metal such as aluminum or copper, and a resin portion 462 provided on the inner peripheral side of the metal portion 461. The guide ring 46 is manufactured by insert-molding the metal portion 461 into a resin. 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. Bearing portions 465 and 466 are formed on the inner peripheral surface of the guide ring 46, and are rotatably supported by the shaft portion 452 by the bearing portions 465 and 466. The bearing portion 466 provided at the end in the −Z direction is provided at a position overlapping the metal portion 461 in the radial direction. When the motor 40 is driven and the rotor 45 rotates, a magnetic induction force is generated between the magnet 451 and the metal portion 461. The induction ring 46 and the rotor 45 are coupled to rotate together by this magnetic induction force.

  FIG. 10A is a perspective view of the guide ring 46, and FIG. 10B is a perspective view of the metal portion 461. As shown in FIG. 10B, the metal part 461 includes a cylindrical part 467 and an annular flange part 468 that extends in the radial direction from one end of the cylindrical part 467 in the axial direction (that is, the end part in the + Z direction). When the guide ring 46 is manufactured by insert molding, the metal part 461 is held in the mold by bringing the flange part 468 into contact with the mold. On the outer peripheral edge of the flange portion 468, rotation stoppers 469 are formed at four locations that are equally spaced in the circumferential direction. The rotation stopper 469 is a cutout part in which the outer peripheral edge of the flange part 468 is cut out in a semicircular shape. As shown in FIG. 10A, the resin portion 462 includes an engagement portion 470 that engages with the rotation stop portion 469. The engaging portion 470 is formed of a resin that has entered the rotation stopper 469 during molding. In addition, the notch shape of a rotation stop part may be shapes other than a semicircle, and the number is not limited to four places. Moreover, you may provide a convex part and a hole instead of a notch part as a rotation stop part.

The guide ring 46 is configured by laminating a metal portion 461 and a resin portion 462 except for a portion where the guide ring gear 464 is formed. The bearing portion 465 positioned at the end in the + Z direction of the guide ring 46 is formed on the inner peripheral surface of the guide ring gear 464 made of only resin. On the other hand, the bearing portion 466 located at the end of the guide ring 46 on the −Z direction side is formed at a portion where the cylindrical portion 467 of the metal portion 461 and the resin portion 462 overlap in the radial direction. The bearing portion 466 is an annular recess formed on the inner peripheral surface of the resin portion 462. In addition, an annular end plate portion 471 that covers an end surface of the cylindrical portion 467 on the −Z direction side is formed at the end portion in the −Z direction of the resin portion 462. The shaft portion 452 of the rotor 45 is formed with an annular convex portion 454 positioned on the inner peripheral side of the bearing portion 466 and a flange portion 455 that contacts the end plate portion 471 from the −Z direction side. When the guide ring 46 rotates, the inner peripheral surface of the bearing portion 466 is in sliding contact with the outer peripheral surface of the annular convex portion 454, and the flange portion 455 and the end plate portion 471 are in sliding contact. Further, the bearing portion 465 is in contact with the outer peripheral surface of the shaft portion 452 and restricts the guide ring 46 from falling with respect to the shaft portion 452.

  When the rotor 45 rotates in the forward rotation direction (CW direction), the rotation of the rotor 45 is input to the first rotating body 812 that meshes with the rotor gear 47. The rotation direction of the first rotating body 812 is the CCW direction. At this time, in a state where a magnetic induction force is applied to the guide ring 46, the second rotating body 814 that meshes with the guiding ring 46 does not rotate, and the third rotating body 816 that is a planet carrier has the same rotational direction as the first rotating body 812 ( Rotate in the CCW direction). As a result, the fan gear 82 rotates in the CW direction. The fan gear 82 is biased in the CCW direction by a coil spring 86 that is a biasing member, and rotates against the biasing force of the coil spring 86.

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

  The lock gear 84 includes a large-diameter portion 842 in which a plurality of protrusions 841 are formed at equiangular intervals on the outer peripheral surface, and a small-diameter gear portion 843 having a smaller diameter than the large-diameter portion 842. When the fan gear 82 rotates in the CW direction, the lock lever 83 rotates in the CCW direction and contacts the outer peripheral surface of the large diameter portion 842 of the lock gear 84. As a result, the lock lever 83 and the protrusion 841 are engaged to restrict the rotation of the lock gear 84. At this time, the rotation center P of the lock lever 83 is located on the tangent line A1 of the large diameter portion 842 of the lock gear 84 (see FIG. 3). Accordingly, when rotation is restricted, the tip of the lock lever 83 and the protrusion 841 abut on the tangent line A1 of the lock gear 84.

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

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

The second clutch mechanism 80 rotates when a rotational force is applied to the lock gear 84 from the speed increasing gear 85 side by an external force or the like due to a magnetic induction force generated between the metal portion 461 of the induction ring 46 and the magnet 451. The lock gear 84 and the lock lever 83 are held so as not to be disengaged by force. Since the magnetic induction force generated between the metal part 461 of the induction ring 46 and the magnet 451 has a magnitude corresponding to the relative rotational speed of the metal part 461 and the magnet 451, the second rotating body 814 of the planetary gear mechanism 81 When the magnetic induction force is amplified by rotating in the reverse direction to the first rotating body 812, the holding force for holding the lock gear 84 increases. Therefore, the locked state that restricts the rotation of the lock lever 83 can be reliably maintained.

  When the energization of the motor 40 is stopped in a state where the lock gear 84 is locked by the lock lever 83, the second clutch mechanism 80 is released from the lock state of the lock gear 84 and is switched to the idle state. That is, when the rotation of the rotor 45 stops, the planetary gear mechanism 81 stops the rotation of the first rotating body 812 that meshes with the rotor gear 47, and the second rotating body 814 that meshes with the guide ring gear 464 can idle. As a result, the third rotating body 816 cannot hold the fan gear 82 against the biasing force of the coil spring 86, and the fan gear 82 rotates in the biasing direction of the coil spring 86. Since the lock lever 83 is separated from the lock gear 84 by the rotation of the fan gear 82, the lock state of the lock gear 84 is released. As a result, the second clutch mechanism 80 switches to a state in which the lock gear 84 and the speed increasing gear 85 are idle.

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

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

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

(Reverse rotation prevention mechanism)
11A is a plan view of the reverse rotation prevention mechanism 90, and FIG. 11B is a side view of the reverse rotation prevention mechanism 90. FIG. The reverse rotation prevention mechanism 90 includes a reverse rotation prevention protrusion 91 formed on the shaft portion 452 of the rotor 45 and a reverse rotation prevention lever 92 attached to the upper part of the planetary gear mechanism 81. The reverse rotation prevention lever 92 is bent in the −Z direction from the disk portion 93 that contacts the end surface in the + Z direction of the first rotating body 812 of the planetary gear mechanism 81 and the circumferential portion of the outer peripheral edge of the disk portion 93. The bending part 94 and the arm part 95 extended from the edge part of the -Z direction of the bending part 94 to an outer peripheral side are provided.

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

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

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

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

  Next, the rotation restricting device 80 </ b> A of the second clutch mechanism 80 is switched to a state in which the lock gear 84 is locked by the rotation of the rotor 45 in the forward rotation direction. First, the fan gear 82 rotates against the urging force of the coil spring 86 by the output rotation of the planetary gear mechanism 81, the lock lever 83 abuts on the lock gear 84 and engages with the protrusion 841, and locks the lock gear 84. To do. Thereby, the transmission wheel train 50 is switched to a state in which the rotational torque is transmitted. That is, in the transmission wheel train 50, the rotation of the second rotating body 524 of the planetary gear mechanism 52 is restricted by the speed increasing gear 85 of the second clutch mechanism 80, and the rotation of the rotor pinion 51 is reduced from the planetary gear mechanism 52 to the reduction gear 53. Switch to the state transmitted to Accordingly, the retracting operation of the slider 10 is performed by the rotation of the rotor 45 in the forward rotation direction.

  When the lock lever 83 abuts on the lock gear 84 and the lock gear 84 is locked, the second clutch mechanism 80 rotates the guide ring 46 in the direction opposite to the rotation direction of the rotor 45 by the planetary gear mechanism 81. Thereby, the relative rotational speed of the rotor 45 and the guide ring 46 is increased, the magnetic induction force generated between the guide ring 46 and the magnet 451 is amplified, and the holding force for holding the lock gear 84 is increased.

(Operation at the end of slider pulling)
When the drain valve driving device 1 reaches the end of pulling of the slider 10, the first clutch mechanism 60
The clutch switching lever 64 is rotated to perform the clutch disengagement operation, and the rotation of the rotor 45 is not input to the transmission wheel train 50. Accordingly, the slider 10 is not pulled beyond the predetermined pulling position 10A. Further, since the rotation restricting projection 74 of the rotation restricting mechanism 70 restricts the rotation of the first rotating body 522 of the planetary gear mechanism 52 due to the rotation of the clutch switching lever 64, the planetary gear mechanism 52 is locked, and the transmission wheel train 50 Cannot transmit rotational torque. Therefore, even if an external force for pulling the slider 10 in the + X direction is applied, the slider 10 is in a load holding state where the slider 10 does not move. As a result, the drain valve is held open.

(Operation when the load is released)
When the drain valve driving device 1 stops energization of the motor 40 in the load holding state, the drain valve driving device 1 shifts to a load releasing state in which the slider 10 can be pulled out in the + X direction by an external force. When the motor 40 is de-energized, the rotation of the rotor 45 stops. Since the fan gear 82 returns to the biasing direction of the coil spring 86 when the rotation of the rotor 45 stops, the second clutch mechanism 80 releases the engagement between the lock lever 83 and the lock gear 84, and the lock gear by the rotation restricting device 80A. The rotation restriction 84 is released. As a result, the transmission wheel train 50 switches to a state in which the rotational torque is not transmitted. That is, since the rotation restriction of the second rotating body 524 is released in the planetary gear mechanism 52 of the transmission wheel train 50, the planetary gear mechanism 52 is unlocked. As a result, the transmission wheel train 50 enters a load release state in which the transmission wheel train 50 can idle. In this state, when an external force in the direction of pulling out the slider 10 is applied, the transmission wheel train 50 idles and the slider 10 is pulled out. A brake rubber 87 (see FIG. 7) is incorporated in the lock gear 84. The brake rubber 87 expands by centrifugal force when the slider 10 is pulled out by an external force, and generates a frictional force with the lock gear 84. As a result, the return speed when the slider 10 is pulled out decreases. Therefore, the risk of damage due to the slider 10 being pulled out rapidly can be reduced.

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

(Main effects of the present invention)
As described above, the drain valve driving device 1 of the present embodiment includes the slider 10 that is a drain valve driving member, the motor 40 that is a driving source, and the transmission wheel train 50 that transmits the rotation of the motor 40 to the output pinion 12. 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. Specifically, the second clutch mechanism 80 includes a gear train (acceleration gear 85 and lock gear 84) that meshes with the second rotating body 524 of the transmission gear train 50, and a rotation restricting device 80A that restricts the rotation of the gear train. The rotation restricting device 80 </ b> A restricts the rotation of the lock gear 84 by rotating the lock lever 83 based on the rotation of the rotor 45.

The rotation restricting device 80 </ b> A includes a lock lever 83, a fan gear 82, a coil spring 86, a planetary gear mechanism 81, and a guide ring 46, and the rotation of the rotor 45 on the guide ring 46 by the operation of the planetary gear mechanism 81. The rotation in the direction opposite to the direction is input to increase the relative rotational speed between the magnet 451 provided on the rotor 45 and the guide ring 46. Accordingly, since the magnetic induction force generated between the induction ring 46 and the magnet 451 is amplified, the holding force (brake torque) for holding the lock lever 83 can be increased. Therefore, a stable locked state can be formed. Thereby, the operation of the second clutch mechanism 80 can be stabilized, and the transmission of the rotational force by the transmission wheel train 50 can be stably performed.
Can be stabilized.

  In this embodiment, as the guide ring 46 that is rotatably supported by the shaft portion 452 of the rotor 45, a magnet 451 disposed coaxially with the shaft portion 452 and a metal portion 461 made of a non-magnetic metal facing the radial direction, The resin portion 462 that holds the metal portion 461 includes the bearing portion 466 that is in sliding contact with the shaft portion 452, and the bearing portion 466 is provided at a position that overlaps the metal portion 461 in the radial direction. Is used. When such a guide ring 46 is manufactured by insert-molding the metal part 461 into a resin, the bearing part 466 is not easily affected by shrinkage deformation of the resin during molding. Therefore, since deformation of the bearing portion 466 can be suppressed, the dimensional accuracy of the bearing portion 466 can be increased. Therefore, the roundness of the bearing portion 466 and the coaxiality with the metal portion 461 can be increased, and the positional accuracy of the metal portion 461 can be increased.

  In this embodiment, the metal portion 461 of the guide ring 46 has a shape including a flange portion 468 that extends in the radial direction from one end in the axial direction of the cylindrical portion 467 that overlaps the bearing portion 466 in the radial direction. Thus, if the metal part 461 is provided with the collar part 468, the structure for hold | maintaining the metal part 461 within a metal mold | die at the time of insert molding can be simplified. Therefore, the mold structure can be simplified, which is advantageous for cost reduction.

  In this embodiment, the collar portion 468 is provided with the rotation preventing portion 469, and the resin portion 462 is provided with the engaging portion 470 that engages with the rotation stopping portion 469. Therefore, the integrity of the metal portion 461 and the resin portion 462 is improved. Can be increased.

  In this embodiment, the rotor 45 holds the magnet 451 by the shaft portion 452, and an annular recess is provided between the magnet 451 and the shaft portion 452 so as to arrange the guide ring 46. Since the guide ring 46 is configured by overlapping the resin portion 462 and the metal portion 461 in the radial direction, the thickness of the resin portion 562 in the radial direction can be reduced. When the guide ring 46 is thinned, the shaft portion 452 that is a component on the rotor 45 side can be thickened. Therefore, a gear shape (rotor gear 47) for transmitting the rotation of the rotor 45 can be provided in the shaft portion 452.

DESCRIPTION OF SYMBOLS 1 ... Drain valve drive device, 2 ... Gear unit, 10 ... Slider, 10A ... Pull-in position, 11 ... Rack, 12 ... Output pinion, 20 ... Case, 21 ... First case, 22 ... Second case, 23 ... Third Case, 24 ... Opening, 25 ... Wiring extraction part, 30 ... Guide part, 40 ... Motor, 41 ... Motor case, 42 ... Support plate, 43 ... Bobbin, 44 ... Stator coil, 45 ... Rotor, 46 ... Induction ring, 47 ... Rotor gear, 48 ... Terminal block, 50 ... Transmission wheel train, 51 ... Rotor pinion, 52 ... Planetary gear mechanism, 53 ... Reduction gear, 54 ... Output gear, 55 ... Projection, 60 ... First clutch mechanism, 61 ... First 1 clutch pawl, 62 ... second clutch pawl, 63 ... coil spring, 64 ... clutch switching lever, 64A ... clutch disengagement position, 65 ... cam pin, 66 ... cam groove, 67 ... inclination 68, positioning recess, 69 ... positioning protrusion, 70 ... rotation restricting mechanism, 71 ... rotation restricting portion, 72 ... projecting portion, 73 ... rotation restricting surface, 74 ... rotation restricting projection, 80 ... second clutch mechanism, 80A ... Rotation restricting device, 81 ... planetary gear mechanism, 82 ... fan gear, 83 ... lock lever, 84 ... lock gear, 85 ... speed increasing gear, 86 ... coil spring, 87 ... brake rubber, 90 ... 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 face, 97 ... Fixed shaft, 98 ... Leaf spring, 211 ... Bottom plate, 212 ... Side plate, 221 ... Top Plate, 222 ... Side plate, 241 ... First recess, 242 ... Second recess, 451 ... Magnet, 452 ... Shaft, 453 ... Fixed shaft, 454 ... Ring, 455 ... Flange, 461 ... Metal, 462 ... Resin part, 46鍔 part, 464 ... induction ring gear, 465, 466 ... bearing part, 467 ... cylindrical part, 468 ... collar part, 469 ... rotation stop part, 470 ... engagement part, 471 ... end plate part, 521 ... sun gear, 522 ... First rotating body, 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 , 531 ... large diameter gear part, 532 ... small diameter gear part, 533 ... fixed shaft, 811 ... sun gear, 812 ... first rotating body, 813 ... internal gear, 814 ... second rotating body, 815 ... planetary gear, 816 ... 3rd rotating body, 817 ... large diameter gear part, 818 ... large diameter gear part, 819 ... small diameter gear part, 821 ... fixed shaft, 822 ... engagement recess, 831 ... fixed shaft, 832 ... engagement pin, 841 ... Projection part, 842 ... Large diameter part, 843 ... Small diameter gear part, 85 DESCRIPTION OF SYMBOLS 1 ... Large diameter gear part, 852 ... Small diameter gear part, A1 ... Tangent, P ... Center of rotation, X ... 1st direction, Y ... 2nd direction, Z ... 3rd direction

Claims (6)

A guide ring rotatably supported by a shaft,
A magnet part disposed coaxially with the shaft part, a metal part made of a non-magnetic metal facing in the radial direction, and a resin part holding the metal part,
The resin portion includes a bearing portion that is in sliding contact with the shaft portion,
The guide ring, wherein the bearing portion is provided at a position overlapping the metal portion in a radial direction.   2. The induction ring according to claim 1, wherein the metal part includes a cylindrical part that overlaps the bearing part in a radial direction and a flange part that extends in a radial direction from one axial end of the cylindrical part. A rotation stopper is provided on the collar,
The guide ring according to claim 2, wherein an engagement portion that engages with the rotation stop portion is provided in the resin portion. A clutch mechanism comprising the guide ring according to any one of claims 1 to 3,
A rotor including the magnet and a motor including a stator;
A transmission wheel train to which rotation of the rotor is input;
A drain valve driving member driven based on rotation of the output gear of the transmission wheel train,
The drain valve driving device according to claim 1, wherein the clutch mechanism interrupts transmission of rotational torque by the transmission wheel train. The rotor includes the shaft portion;
The drain valve driving device according to claim 4, wherein the magnet is held by the shaft portion, and is disposed at a position where an annular concave portion for disposing the guide ring is provided between the magnet portion and the magnet portion. The clutch mechanism is
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 a planet carrier that rotatably supports the planetary gear A planetary gear mechanism comprising a third rotating body provided with
A rotation restricting member driven based on the rotation of the third rotating body,
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 drain valve driving device according to claim 4 or 5, wherein a gear that meshes with a rotor gear formed on the shaft portion is provided on the other of the first rotating body and the second rotating body.

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