JP2016005411A - Actuator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an actuator capable of reducing the cost of a changeover mechanism.SOLUTION: In the case where a motor 13 is driven and a first rotor 45 of a planetary gear mechanism 15 is switched into a rotation regulated state by a changeover mechanism 18, a rotational driving force of the motor 13 is transmitted to an actuation wheel body 12 via the planetary gear mechanism 15, and the actuation wheel body 12 is rotated in one direction. In the case where the motor 13 is stopped and the first rotor 45 is switched into a rotation allowed state by the changeover mechanism 18, the actuation wheel body 12 is rotated in another direction by an energizing force. When a second member 86 of the changeover mechanism 18 is switched to a first changeover position, the first rotor 45 is switched into the rotation allowed state. When the second member 86 is switched to a second changeover position, the first rotor 45 is switched into the rotation regulated state.

Description

  The present invention relates to an actuator for opening and closing a drain valve or the like of, for example, a washing machine or a dishwasher.

  2. Description of the Related Art Conventionally, as a driving means for opening and closing a drain valve of a household automatic washing machine, for example, a motor type actuator having an output member that is driven through a gear train by an electric motor is generally employed. Specifically, the drainage valve having a biasing force that returns to the initial position in the closed state is driven against the biasing force by the output member of the motor type actuator so as to be opened.

  By the way, in the automatic washing machine, not only driving the drain valve from the closed state to the open state after completion of washing and rinsing, but also holding the drain valve in the open state until draining of the washing tub is completed, After draining is completed, it is necessary to return the drain valve to the initial position and close it.

  In order to realize such operation control of the drain valve, conventionally, a motor type actuator 201 as shown in FIGS. 20 and 21 is used. That is, the motor type actuator 201 includes a wire winding pulley 202 that opens and closes the drain valve 220 by a rotational force, a motor 203 that rotates the wire winding pulley 202 in the winding direction A (one direction), and rotation of the motor 203. A driving force transmission path 204 that transmits a driving force to the wire hoisting pulley 202, a planetary gear mechanism 205 provided on the driving force transmission path 204, and a rotatable case 206 provided in the planetary gear mechanism 205 are allowed to rotate. A switching mechanism 207 that switches between two different switching states, a state and a rotation restricted state, and a speed adjusting mechanism 208 that adjusts the rotational speed of the wire winding pulley 202 in the delivery direction B (the other direction).

  The wire 209 wound around the wire winding pulley 202 is biased in the delivery direction B opposite to the winding direction A by a biasing force of a spring (not shown). The speed adjusting mechanism 208 is rotatable in conjunction with the case 206 of the planetary gear mechanism 205.

  The switching mechanism 207 includes a magnetic induction transmission mechanism 211 and a rocking body 212. The magnetic induction type transmission mechanism 211 includes an induction rotor 213 made of a magnet and an induction ring 214 made of a magnetic material. The induction rotor 213 is accommodated in the induction ring 214 and can be rotated integrally with the rotor 215 of the motor 203.

  When the motor 203 is driven, the rotational driving force of the motor 203 is transmitted to the induction rotor 213, the induction rotor 213 rotates, the rotational force of the induction rotor 213 is transmitted to the induction ring 214 by electromagnetic induction, and the induction ring 214 is transmitted to the induction rotor. It rotates in the same direction as 213. As a result, the oscillating body 212 oscillates in one direction, the locking portion 216 of the oscillating body 212 engages with the stopper protrusion 217 of the speed adjusting mechanism 208, and the rotation of the speed adjusting mechanism 208 is prevented. Therefore, the case 206 of the planetary gear mechanism 205 is switched to the rotation restricted state, the rotation of the case 206 is prevented, and the rotational driving force of the motor 203 is transmitted to the wire winding pulley 202 via the planetary gear mechanism 205, Since the wire winding pulley 202 rotates in the winding direction A against the urging force of the spring, the wire 209 is wound around the wire winding pulley 202 and the drain valve 220 is opened.

  Further, when the motor 203 is stopped, torque transmission based on the magnetic induction action is not performed between the induction rotor 213 and the induction ring 214, and the swinging body 212 swings in the other direction by the biasing force of the spring 218. The locking portion 216 of the moving body 212 is disengaged from the stopper protrusion 217 of the speed control mechanism 208, and the speed control mechanism 208 is allowed to rotate. As a result, the case 206 of the planetary gear mechanism 205 is switched to the rotation-permitted state, the case 206 is permitted to rotate, the wire winding pulley 202 is rotated in the delivery direction B by the biasing force of the spring, and the wire 209 is It is sent out from the upper pulley 202 and the drain valve 220 is closed. At this time, the case 206 of the planetary gear mechanism 205 is rotated by the rotation of the wire winding pulley 202 in the delivery direction B, and the speed adjusting mechanism 208 is rotated in conjunction with the rotation of the case 206. The rotational speed in the delivery direction B is adjusted.

  The motor actuator 201 as described above is described in Patent Document 1 below.

JP 2006-50857 A

  However, in the above-described conventional type, the magnetic induction transmission mechanism 211 used for the switching mechanism 207 has a configuration in which the induction rotor 213 is accommodated in the induction ring 214. Therefore, when the magnetic induction transmission mechanism 211 is manufactured. The induction rotor 213 and the induction ring 214 need to be processed with high accuracy to finely adjust the gap between the induction rotor 213 and the induction ring 214, and the cost of the switching mechanism 207 increases.

  An object of this invention is to provide the actuator which can aim at the cost reduction of a switching mechanism.

To achieve the above object, according to the first aspect of the present invention, there is provided an operating wheel body that operates an object by a rotational force, a motor that rotates the operating wheel body in one direction, and a rotational driving force of the motor transmitted to the operating wheel body. Switching for switching the driving force transmission path, the planetary gear mechanism provided on the driving force transmission path, and the first rotating body provided in the planetary gear mechanism to two different switching states of a rotation permission state and a rotation restriction state A mechanism,
An actuator biased so that the working wheel rotates in the other direction,
The motor has a rotor having a plurality of magnetic poles and a stator,
The rotor can be stopped at a predetermined angle according to the number of poles of the rotor with respect to the stator,
When the motor is driven and the first rotating body of the planetary gear mechanism is switched to one of the switching states by the switching mechanism, the rotational driving force of the motor is transmitted to the working wheel body via the planetary gear mechanism, and the working wheel The body rotates in one direction,
When the motor stops and the first rotating body of the planetary gear mechanism is switched to one of the other switching states by the switching mechanism, the working wheel is rotated in the other direction by the biasing force,
The switching mechanism includes a first member that is rotatable in conjunction with the rotor, and a second member that faces the first member in the direction of the rotation axis.
The second member does not rotate and can be moved toward and away from the first member in the direction of the rotation axis,
Different magnetic poles are alternately arranged in the circumferential direction on the first member and the second member,
When the rotor stops at a predetermined angle, the magnetic poles of the stopped first member and the magnetic poles of the second member are attracted opposite to each other so that the second member approaches the first member and is first Switched to the switching position,
When the rotor rotates, the second member is switched from the first switching position to the second switching position separated from the first member by repetitive repulsion and suction between the magnetic poles of the first member and the second member,
When the second member is switched to the second switching position, switching is made between a rotation permission state in which rotation of the first rotating body of the planetary gear mechanism is allowed and a rotation restriction state in which rotation is restricted. And
When the second member is switched to the first switching position, the first rotating body of the planetary gear mechanism is switched to the other switching state between the rotation permission state and the rotation restriction state.

  According to this, when the motor is driven, the second member is switched to the second switching position, and either the rotation permission state in which the rotation of the first rotating body of the planetary gear mechanism is allowed or the rotation restriction state in which the rotation is restricted. It is switched to one of these switching states, the rotational driving force of the motor is transmitted to the working wheel body via the planetary gear mechanism, the working wheel body rotates in one direction, and the object is actuated in one direction.

  When the motor is stopped, the second member is switched to the first switching position, the first rotating body of the planetary gear mechanism is switched to either the rotation-permitted state or the rotation-restricted state, and the working wheel body. Is rotated in the other direction by the biasing force, and the object is actuated in the other direction.

  The switching mechanism includes a first member that is rotatable in conjunction with the rotor, and a non-rotating second member that is movable toward and away from the first member in the rotational axis direction. Since each of the two members has different magnetic poles alternately arranged in the circumferential direction, high-precision machining is not necessary when manufacturing the switching mechanism. Moreover, since the structure of the switching mechanism is simple, the cost of the switching mechanism can be reduced.

In the actuator according to the second aspect of the invention, when the motor is driven and the first rotating body of the planetary gear mechanism is switched to the rotation restricted state by the switching mechanism, the rotational driving force of the motor is applied to the working wheel body via the planetary gear mechanism. Is transmitted, the working wheel rotates in one direction,
When the motor stops and the first rotating body of the planetary gear mechanism is switched to the rotation-permitted state by the switching mechanism, the working wheel is rotated in the other direction by the biasing force,
By switching the second member to the second switching position, the first rotating body of the planetary gear mechanism is switched to the rotation restricted state,
When the second member is switched to the first switching position, the first rotating body of the planetary gear mechanism is switched to the rotation allowable state.

  According to this, when the motor is driven, the second member is switched to the second switching position, the first rotating body of the planetary gear mechanism is switched to the rotation restricted state, and the rotational driving force of the motor is operated via the planetary gear mechanism. It is transmitted to the ring body, the working wheel body rotates in one direction, and the object is operated in one direction.

  When the motor is stopped, the second member is switched to the first switching position, the first rotating body of the planetary gear mechanism is switched to the rotation-permitted state, and the operating wheel is rotated in the other direction by the biasing force. Is actuated in the other direction.

The actuator according to the third aspect of the present invention is provided with a speed regulating member that adjusts the rotational speed in the other direction of the working wheel,
The speed control member is rotatable in conjunction with the first rotating body of the planetary gear mechanism,
The switching mechanism has a stop member that can be freely engaged and disengaged with the speed control member,
When the second member is switched to the second switching position, the stop member engages the speed adjusting member to restrict the rotation of the speed adjusting member, and the first rotating body of the planetary gear mechanism is switched to the rotation restricted state.
When the second member is switched to the first switching position, the stop member is disengaged from the speed control member to allow the speed control member to rotate, and the first rotating body of the planetary gear mechanism is switched to the rotation allowable state. is there.

  According to this, when the motor is driven, the second member is switched to the second switching position, the stop member is engaged with the speed control member to restrict the rotation of the speed control member, and the first rotating body of the planetary gear mechanism is The rotation control state is switched, the rotational driving force of the motor is transmitted to the working wheel body via the planetary gear mechanism, the working wheel body rotates in one direction, and the object is actuated in one direction.

  When the motor is stopped, the second member is switched to the first switching position, the stop member is detached from the speed control member, and the speed control member is allowed to rotate, and the first rotating body of the planetary gear mechanism is allowed to rotate. The operating wheel is rotated in the other direction by the urging force, and the object is operated in the other direction.

  At this time, since the first rotating body of the planetary gear mechanism is switched to the rotation-permitted state, the first rotating body of the planetary gear mechanism is rotated by rotating the working wheel body in the other direction, and the first rotating body is moved to the first rotating body. Since the speed governing member rotates in conjunction with it, the rotational speed of the working wheel body in the other direction is adjusted.

The actuator according to the fourth aspect of the invention is provided with an interrupting mechanism for interrupting a driving force transmission path between the motor and the planetary gear mechanism,
The planetary gear mechanism includes first and second rotating bodies that are rotatable relative to each other, a sun gear that is provided in the intermittent mechanism, an internal gear that is provided in the first rotating body, and a sun gear that is provided in the second rotating body. A planetary gear meshing with the gear and the internal gear,
The rotation of the second rotating body of the planetary gear mechanism and the rotation of the working wheel body are linked,
When the motor is driven with the driving force transmission path connected by the intermittent mechanism and the first rotating body of the planetary gear mechanism is switched to the rotation restricted state by the switching mechanism, the rotation of the first rotating body is restricted, and the motor Is transmitted to the working wheel body through the planetary gear mechanism,
When the motor is stopped and the first rotating body of the planetary gear mechanism is switched to the rotation-permitted state by the switching mechanism, the working wheel body is rotated in the other direction by the urging force, and the rotation of the working wheel body causes the planetary gear mechanism to One rotating body rotates, and the speed regulating member rotates in conjunction with the first rotating body.

  As described above, according to the present invention, the switching mechanism has the first member that can rotate in conjunction with the rotor, and the non-rotating second member that can move toward and away from the first member in the direction of the rotation axis. In addition, since the first member and the second member have different magnetic poles alternately arranged in the circumferential direction, high-precision machining is not necessary when the switching mechanism is manufactured. Moreover, since the structure of the switching mechanism is simple, the cost of the switching mechanism can be reduced.

It is sectional drawing which shows the expansion structure inside the actuator in the 1st Embodiment of this invention. 2 is a plan view showing the internal structure of the actuator. FIG. It is a schematic plan view of the rotor and stator of the motor of the actuator. It is a figure of the reverse rotation prevention mechanism of the rotor of an actuator same as the above. FIG. 4 is an enlarged cross-sectional view of the intermittent mechanism and the planetary gear mechanism of the actuator, showing a case where the intermittent mechanism is switched to a connected state. FIG. 4 is a diagram showing the operation of the cam lever of the actuator, showing a case where the intermittent mechanism is switched to a connected state. FIG. 6 is a diagram showing the operation of the cam lever of the actuator, showing a case where the interrupting mechanism is switched to a disconnected state. FIG. 4 is an enlarged cross-sectional view of the intermittent mechanism and the planetary gear mechanism of the actuator, showing a case where the intermittent mechanism is switched to a disconnected state. FIG. 4 is a sectional view of the actuator switching mechanism, showing a state where the second disk is switched to the first switching position. FIG. 6 is a side view of the actuator switching mechanism, showing a state where the second disk is switched to the first switching position. FIG. 4 is a sectional view of the actuator switching mechanism, showing a state where the second disk is switched to the second switching position. FIG. 3 is a plan view of the actuator switching mechanism. It is a figure which shows the magnetic pole of the 1st and 2nd disk of the switching mechanism of an actuator similarly, (a) is a 1st disk, (b) is a 2nd disk. It is sectional drawing which shows the expansion structure inside the actuator in the 2nd Embodiment of this invention, and shows the state which the 2nd disk was switched to the 1st switching position. FIG. 6 is a cross-sectional view showing a developed structure inside the actuator, showing a state in which the second disk is switched to the second switching position. 2 is a plan view showing the internal structure of the actuator. FIG. FIG. 2 is a partially cutaway plan view showing the internal structure of the actuator. FIG. 3 is a plan view of the actuator switching mechanism. It is a figure which shows the magnetic pole of the 1st and 2nd disk of the switching mechanism of an actuator similarly, (a) is a 1st disk, (b) is a 2nd disk. It is sectional drawing which shows the expansion | deployment structure inside the conventional actuator. FIG. 3 is a plan view of the actuator switching mechanism.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
In the first embodiment, as shown in FIGS. 1 to 3, reference numeral 10 denotes an actuator that opens and closes a drain valve 1 (an example of an object) such as a household automatic washing machine. The actuator 10 includes a housing 11 having a hollow box structure attached to a main body of a washing machine or the like. In the housing 11, a wire hoisting pulley 12 (an example of a working wheel) that opens and closes the drain valve 1 by a rotational force, and a motor that rotates the wire hoisting pulley 12 in a winding direction A (an example of one direction). 13, a driving force transmission path 14 for transmitting the rotational driving force of the motor 13 to the wire winding pulley 12, a planetary gear mechanism 15 provided on the driving force transmission path 14, and a delivery direction B of the wire winding pulley 12 A speed control member 16 that adjusts the rotational speed in one direction (an example of the other direction), an intermittent mechanism 17, a switching mechanism 18, and an output wheel 19 are provided.

  The wire hoisting pulley 12 and the drain valve 1 are interlocked and connected via a wire 21. When the wire 21 is wound around the wire hoisting pulley 12, the drain valve 1 is opened, and the wire 21 is pulled into the wire hoisting pulley. By being sent out from 12, the drain valve 1 is closed. The wire 21 is urged in the feeding direction B sent out from the wire hoisting pulley 12 by a biasing tool (not shown) such as a spring, whereby the wire hoisting pulley 12 is urged in the sending direction B. .

  The motor 13 is an 8-pole inductor synchronous motor, and includes a rotor 22 having an 8-pole magnetic pole and a stator 23. When the motor 13 is stopped, the rotor 22 stops at a predetermined angle C corresponding to the number of poles of the motor 13 with respect to the stator 23. In the case of 8 poles, the predetermined angle C is 45 °.

  The rotor 22 has a structure in which a rotary drive shaft 25 is provided on an annular block-shaped permanent magnet 24. A rotor support shaft 26 fixed to the stator 23 is inserted through the rotation center of the rotor 22, and the rotor 22 is rotatable with respect to the rotor support shaft 26.

  Rotation drive based on the interaction between the plurality of N and S magnetic poles magnetized in the circumferential direction of the permanent magnet 24 and the plurality of N and S magnetic poles developed by the application of alternating current to the coil 27 of the stator 23 In the shaft 25, rotational torque and detent torque are exhibited.

  As shown in FIGS. 1 and 4, the rotation drive shaft 25 is formed with a motor pinion 37 and a plurality of locking claws 28. Near the locking claw 28, an anti-reverse member 29 that is locked to the locking claw 28 in one direction of rotation of the rotor 22 is disposed so as to be swingable about one axis. The locking claw 28 and the reverse rotation prevention member 29 constitute a reverse rotation prevention mechanism that defines the rotation direction of the rotor 22.

  As shown in FIGS. 1, 5, and 6, the interrupting mechanism 17 interrupts the driving force transmission path 14 between the motor 13 and the planetary gear mechanism 15, and includes an upper interrupting member 31 and a lower interrupting member. 32 and a compression coil spring 33.

  The upper intermittent member 31 includes a disk-shaped portion having a locking claw 34 formed on the outer peripheral surface. A sun gear 35 projects from the upper surface of the disk-shaped portion, and a plurality of engagements are formed on the lower surface. A recess 36 is formed.

  The lower intermittent member 32 includes an intermittent gear 38 that can mesh with the motor pinion 37 of the rotary drive shaft 25. Boss portions 39 and 40 that protrude outward in the axial direction are formed on the upper and lower surfaces of the lower intermittent member 32, respectively. The lower interrupting member 32 is formed with a plurality of locking pieces 41 around the upper boss portion 39, and these locking pieces 41 can be engaged with the locking recesses 36 of the upper interrupting member 31.

  The upper intermittent member 31 and the lower intermittent member 32 having such a structure are arranged so as to overlap each other in the axial direction with the compression coil spring 33 interposed therebetween. Under the state in which the intermittent member 32 is arranged, the upper intermittent member 31 and the lower intermittent member 32 are elastically separated and opposed to each other by the urging force of the compression coil spring 33.

  As shown in FIG. 5, the upper intermittent member 31 and the lower intermittent member 32 are made to approach each other in the axial direction against the urging force of the compression coil spring 33, and the locking recess of the upper intermittent member 31. In a state where the engagement piece 36 and the locking piece 41 of the lower intermittent member 32 are engaged with each other, the upper intermittent member 31 and the lower intermittent member 32 are integrally rotated. Thereby, the rotational driving force of the motor 13 is transmitted to the sun gear 35 of the upper intermittent member 31. The engagement between the locking recess 36 of the upper interrupting member 31 and the locking piece 41 of the lower interrupting member 32 is maintained in the forward rotation direction of the motor 13, while in the reverse rotation direction. The ratchet structure is released. The locking recess 36 of the upper interrupting member 31 and the locking piece 41 of the lower interrupting member 32 constitute a locking mechanism.

  The planetary gear mechanism 15 is provided in the case 45 (an example of the first rotating body) and the driven body 46 (an example of the second rotating body) that are rotatable with respect to each other, the sun gear 35 provided in the intermittent mechanism 17, and the case 45. And a plurality of rotatable planetary gears 49 that are provided on the driven body 46 and mesh with the sun gear 38 and the internal gear 47.

  The case 45 is a bottomed cylindrical member, and the internal gear 47 and the external gear 48 are formed on the inner peripheral surface and the outer peripheral surface of the cylindrical wall portion of the case 45. The follower 46 includes a disc 51, and a plurality of support shafts 52 are provided on the disc 51, and the support shafts 52 are inserted into the shaft holes of the planetary gear 49. Further, the disc 51 is formed with a connecting gear 53 protruding upward.

  The driven body 46 is assembled to the case 45 by being fitted into the case 45, and the planetary gear 49 is rotatably attached to the support shaft 52. In the state where the follower 46 is assembled to the case 45, the case 45 is assembled so as to be superimposed on the upper intermittent member 31. The sun gear 35 of the upper intermittent member 31 is inserted into a through hole formed in the bottom wall portion of the case 45 so as to be positioned in the case 45. Further, the sun gear 35 and the connecting gear 53 are positioned coaxially.

As shown in FIGS. 1 and 2, the output wheel 19 has a structure in which an output gear 55 and an output pinion 56 are integrally formed on the same axis, and the output gear 55 is engaged with the connecting gear 53.
As shown in FIG. 1, the wire winding pulley 12 includes a groove 57 continuously extending in the circumferential direction on the outer peripheral surface thereof, and the wire 21 is wound around the groove 57. The wire hoisting pulley 12 includes a locking tooth 58 that meshes with the output pinion 56 of the output wheel 19. As a result, the rotation of the wire winding pulley 12 and the rotation of the driven body 46 of the planetary gear mechanism 15 are linked via the output wheel 19, and the rotational driving force of the motor 13 is connected to the intermittent mechanism 17, the planetary gear mechanism 15, and the output. It is transmitted to the wire 21 via the wheel 19 and the wire hoisting pulley 12, and the opening and closing of the drain valve 1 is switched.

  As shown in FIGS. 1 and 6, a sliding wall 60 curved in an arc shape is erected on the lower surface of the wire winding pulley 12, and near one end in the circumferential direction of the sliding wall 60. The protrusion 61 is erected so as to form a gap with the sliding wall 60. The protrusion 61 is positioned radially outward from the sliding wall 60.

  A cam lever 63 is disposed below the output wheel 19 so as to be swingable around the support shaft 64. The cam lever 63 includes a slidable contact piece 65 that protrudes in a direction perpendicular to the support shaft 64 serving as a swing center. The tip of the sliding contact piece 65 is slidable with respect to the sliding wall 60 of the wire winding pulley 12.

  As shown in FIGS. 1, 5, and 6, the cam lever 63 is formed with an operation piece 66 that protrudes in a direction different from the sliding contact piece 65. A guide hole 67 extending in an arc shape along the circumferential direction of 63 support shafts 64 is formed. The tip end portion of the operation piece 66 (that is, the portion where the guide hole 67 is formed) gradually increases in thickness as it goes from one side in the circumferential direction to the other side in the circumferential central portion. The thickness dimension is substantially constant at both end portions. As a result, the distal end of the operation piece 66 is positioned on one side in the circumferential direction below the other side in the circumferential direction.

  The support shaft 69 of the planetary gear mechanism 15 and the intermittent mechanism 17 is loosely inserted into the guide hole 67 of the operation piece 66, and the lower boss portion 40 of the lower intermittent member 32 is slidably contacted with the upper surface of the operation piece 66. It has become so.

Further, the cam lever 63 is formed with a locking piece 70 that is locked to a locking claw 34 formed on the upper intermittent member 31 in a direction different from the sliding contact piece 65 and the operation piece 66.
As shown in FIG. 6, when the sliding contact piece 65 of the cam lever 63 is in sliding contact with the sliding wall 60 of the wire winding pulley 12, the lower boss portion 40 of the lower intermittent member 32 is operated by the operation piece. The lower intermittent member 32 is lifted upward by being brought into contact with the other circumferential side of the protruding tip portion of 66. As a result, a relative displacement force in the approaching direction is exerted between the intermittent gear 38 and the sun gear 35 in the axial direction. As a result, as shown in FIG. The locking recess 36 of the upper intermittent member 31 is locked, and the rotational driving force of the motor 13 is transmitted to the sun gear 35. In this state, when the locking piece 41 of the lower interrupting member 32 and the locking recess 36 of the upper interrupting member 31 are locked, the locking piece 70 of the cam lever 63 is intermittently connected as shown in FIG. It is not latched by the latching claw 34 of the member 31, thereby allowing the upper intermittent member 31 to rotate.

  As shown in FIG. 7, when the sliding contact piece 65 of the cam lever 63 is in contact with the protrusion 61 of the wire winding pulley 12, the lower boss portion 40 of the lower intermittent member 32 protrudes from the operation piece 66. As shown in FIG. 8, the lower interrupting member 32 is separated from the upper interrupting member 31 by the urging force of the compression coil spring 33 and is positioned downward as shown in FIG. Thereby, the relative displacement force in the approach direction in the axial direction exerted between the intermittent gear 38 and the sun gear 35 is released. As a result, the locking piece 41 and the upper side of the lower intermittent member 32 are released. The locking of the intermittent member 31 with the locking recess 36 is released so that the rotational driving force of the motor 13 is not transmitted to the sun gear 35. In this state where the locking of the locking piece 41 and the locking recess 36 is released, the locking piece 70 of the cam lever 63 is engaged with the locking claw 34 of the upper intermittent member 31 as shown in FIG. Accordingly, the upper intermittent member 31 is prevented from rotating.

  As shown in FIGS. 1, 2, 9, and 12, a pin 72 (support shaft) is inserted through the speed adjusting member 16. The speed adjusting member 16 includes a rotating shaft portion 73 that is rotatably supported by the pin 72, a speed adjusting pinion 74 provided on the rotating shaft portion 73, and a pair (plurality) provided at the distal end portion of the rotating shaft portion 73. ) And a plurality of stopper projections 76 projecting radially outward from the rotary shaft portion 73, and has a brake type configuration of a centrifugal clutch structure. The stopper protrusion 76 is provided between the speed adjusting pinion 74 and the sliding body 75 in the axial direction.

  A cylindrical portion 78 is formed in the housing 11, and the sliding body 75 is accommodated in the cylindrical portion 78. If the rotational speed of the speed adjusting member 16 exceeds the allowable value, the sliding body 75 moves in the diameter-expanding direction due to centrifugal force and comes into sliding contact with the inner peripheral surface of the cylindrical portion 78, thereby controlling the speed controlling member 16. Power is generated.

  As shown in FIGS. 1, 2, and 5, a rotatable transmission ring body 79 is provided between the speed control member 16 and the planetary gear mechanism 15. The transmission ring body 79 includes a transmission gear 80 that meshes with the speed adjusting pinion 74 of the speed regulating member 16, and a transmission pinion 81 that meshes with the external gear 48 of the case 45 of the planetary gear mechanism 15. . Thereby, the speed adjusting member 16 is rotatable in conjunction with the case 45 of the planetary gear mechanism 15 via the transmission wheel 79.

  The switching mechanism 18 allows the case 45 of the planetary gear mechanism 15 to be switched between two different switching states, a rotation permission state and a rotation restriction state, by allowing and restricting the rotation of the speed control member 16.

  As shown in FIGS. 1, 2, and 9 to 13, the switching mechanism 18 includes a first disk 85 (an example of a first member) that is rotatable integrally with the rotor 22 of the motor 13, and a rotary drive shaft 25. A second disk 86 (an example of a second member) that faces the first disk 85 in the rotational axis direction D, and a stop lever 87 (an example of a stop member) that can be engaged with and disengaged from the stopper protrusion 76 of the speed governing member 16. Have.

  The first disk 85 is provided at the tip of the rotary drive shaft 25 of the rotor 22. The first disk 85 and the second disk 86 are fitted on the rotor support shaft 26. The second disk 86 is fixed in the circumferential direction and does not rotate. The second disk 86 is guided by the rotor support shaft 26 and can be moved toward and away from the first disk 85 in the rotational axis direction D.

  As shown in FIG. 13, a plurality of different magnetic poles (N poles and S poles) are alternately arranged in the circumferential direction on the opposing surfaces of the first disk 85 and the second disk 86, respectively. These magnetic poles are formed by arranging a plurality of magnets on a first disk 85 and a second disk 86, respectively. The number of poles of the first disk 85 and the second disk 86 is set to an even multiple of the number of poles of the rotor 22 of the motor 13. In this case, as an example, the number of poles of each of the first disk 85 and the second disk 86 is set to be twice the number of poles of the rotor 22, that is, 16 poles. Thereby, the N pole and the S pole of the first disk 85 are alternately arranged at an angle of 22.5 ° (an example of a constant angle) in the circumferential direction, and the same applies to the second disk 86. The angle 22.5 ° is a half angle of the predetermined angle C, but may be an even angle other than 2.

  When the rotation of the first disk 85 is stopped, the magnetic poles of the first disk 85 and the magnetic poles of the second disk 86 are attracted opposite to each other as shown in FIGS. The disk 86 approaches the first disk 85 and is switched to the first switching position P1. When the first disk 85 rotates, the second disk 86 is moved from the first switching position P1, as shown in FIG. 11, by repulsion and suction between the magnetic poles of the first disk 85 and the second disk 86, as shown in FIG. Is also switched to the second switching position P2 spaced from the first disk 85.

  A coil spring 88 (an example of a biasing member) that biases the second disk 86 from the second switching position P2 toward the first switching position P1 is externally fitted to the rotor support shaft 26, and the second disk 86 and It is arranged between the inner surface of the housing 11.

  The stop lever 87 is reciprocally movable in the rotational axis direction D integrally with the second disk 86, the base end of the stop lever 87 is attached to the second disk 86, and the guide shaft 89 is attached to the distal end of the stop lever 87. Is inserted. The guide shaft 89 is fixed in the housing 11 and is erected in parallel with the rotor support shaft 26. The stop lever 87 has an engaging protrusion 90 at the tip.

  As shown in FIGS. 9 and 10, when the second disk 86 is switched to the first switching position P1, the stop lever 87 is guided by the guide shaft 89 and moves in one direction, and the engaging protrusion 90 is adjusted. It is detached from the stopper projection 76 of the speed member 16. Further, as shown in FIG. 11, when the second disk 86 is switched to the second switching position P2, the stop lever 87 is guided by the guide shaft 89 and moves in the other direction, and the engaging protrusion 90 is controlled. Engage with the stopper protrusion 76 of the member 16.

Hereinafter, the operation of the above configuration will be described.
(1) In an initial state in which no power is supplied to the motor 13, the wire 21 is fed from the wire winding pulley 12 and the drain valve 1 is closed. In such an initial state, the rotor 22 of the motor 13 is closed. Is stopped at every predetermined angle C, and accordingly, the first disk 85 is stopped, and the magnetic poles of the first disk 85 and the magnetic poles of the second disk 86 are attracted opposite to each other. 9. As shown in FIG. 10, the second disk 86 is switched to the first switching position P1. As a result, the engaging protrusion 90 of the stop lever 87 is disengaged from the stopper protrusion 76 of the speed adjusting member 16 and the rotation of the speed adjusting member 16 is allowed, so that the case 45 of the planetary gear mechanism 15 is switched to the rotation allowed state. It has been.
(2) Thereafter, when power is supplied to the motor 13 and the motor 13 is driven, the rotor 22 rotates in one direction. As a result, the first disk 85 rotates in one direction together with the rotor 22, and the second disk 86, as shown in FIG. 11, is obtained by repulsion and suction between the magnetic poles of the first disk 85 and the second disk 86. Is switched from the first switching position P1 to the second switching position P2 against the urging force of the coil spring 88, and the engaging protrusion 90 of the stop lever 87 engages with the stopper protrusion 76 of the speed adjusting member 16, thereby adjusting the speed. Since the rotation of the member 16 is restricted, the case 45 of the planetary gear mechanism 15 is switched from the rotation permission state to the rotation restriction state, and the rotation of the case 45 is restricted via the transmission wheel body 79.

  Further, when the rotor 22 is rotated, the sliding contact piece 65 of the cam lever 63 is in sliding contact with the sliding wall 60 of the wire winding pulley 12 as shown in FIG. The lower intermittent member 32 is pushed upward in the axial direction against the restoring force of the compression coil spring 33 by the other circumferential side of the tip of the piece 66.

  As a result, as shown in FIG. 5, the locking piece 41 of the lower intermittent member 32 is locked in the locking recess 36 of the upper intermittent member 31, and the intermittent mechanism 17 is in a connected state. At this time, as shown in FIG. 6, the locking piece 70 of the cam lever 63 is not locked to the locking claw 34 of the upper intermittent member 31, thereby allowing the upper intermittent member 31 to rotate.

When the rotor 22 rotates in one direction as described above in this state, the motor pinion 37 rotates in one direction, the upper intermittent member 31 rotates with the lower intermittent member 32 meshed with the motor pinion 37, and the upper intermittent member. The 31 sun gear 35 rotates. At this time, since the rotation of the case 45 of the planetary gear mechanism 15 is restricted (blocked), the planetary gear 49 revolves while rotating, the connection gear 53 of the driven body 46 rotates, the output wheel 19 rotates, As shown in FIG. 2, the wire winding pulley 12 rotates in the winding direction A against the urging force of the urging tool. Thereby, the wire 21 is wound up by the wire winding pulley 12, the drain valve 1 is opened, and drainage is started.
(3) When the drain valve 1 is fully opened, the sliding contact piece 65 of the cam lever 63 is pushed in the rotation direction (winding direction A) of the wire winding pulley 12 by the protrusion 61 of the wire winding pulley 12 as shown in FIG. As a result, the cam lever 63 is rotated around the support shaft 64. As a result, one side in the circumferential direction of the distal end portion of the operation piece 66 in the cam lever 63 is brought into contact with the lower boss portion 40, and as a result, it is pushed upward in the axial direction against the urging force of the compression coil spring 33. The lower intermittent member 32 that has been pressed is pushed downward in the axial direction by the urging force of the compression coil spring 33, and as shown in FIG. 8, the locking recess 36 of the upper intermittent member 31 and the lower intermittent member 32. The engagement state with the locking piece 41 is released, the intermittent mechanism 17 is disconnected, and the rotational driving force of the motor 13 is not transmitted to the upper intermittent member 31.

In this state, the drain valve 1 tries to start the return operation from the open state to the closed state by the biasing force of the biasing tool, but the rotation of the case 45 of the planetary gear mechanism 15 is prevented as described above. 7 and the locking piece 70 of the cam lever 63 is locked to the locking claw 34 of the upper intermittent member 31 to prevent the upper intermittent member 31 from rotating in the reverse direction, as shown in FIG. It is like that. Thereby, the reverse rotation of the driven body 46 of the planetary gear mechanism 15 is prevented, and the drain valve 1 can be kept open.
(4) When the drain valve 1 is opened as described above and a predetermined time has elapsed, the motor 13 is stopped by a timer or the like. Accordingly, the rotor 22 stops at every predetermined angle C, and accordingly, the first disk 85 stops, and the magnetic poles of the first disk 85 and the magnetic poles of the second disk 86 are opposed to each other with different poles. Then, as shown in FIGS. 9 and 10, the second disk 86 is switched from the second switching position P2 to the first switching position P1.

  As a result, the engaging protrusion 90 of the stop lever 87 is disengaged from the stopper protrusion 76 of the speed adjusting member 16 and the speed adjusting member 16 is allowed to rotate, so that the case 45 of the planetary gear mechanism 15 rotates from the rotation restricted state. Switch to an acceptable state. Accordingly, the reverse rotation prevention force of the upper intermittent member 31 obtained by the engagement piece 70 of the cam lever 63 shown in FIG. 7 being engaged with the engagement claw 34 of the upper intermittent member 31 is the wire winding pulley 12. The wire hoisting pulley 12 is rotated in the delivery direction B by the urging force of the urging tool, the wire 21 is fed out from the wire hoisting pulley 12, the drain valve 1 is closed, and the operation returns to the initial state. .

  At this time, the sliding contact piece 65 of the cam lever 63 is released from the contact state with the protrusion 61 of the wire winding pulley 12 and is slidably contacted with the sliding wall 60 as shown in FIG. As a result, the other circumferential side of the distal end portion of the operation piece 66 comes into contact with the lower boss portion 40, and the lower intermittent member 32 acts as a restoring force of the compression coil spring 33 as shown in FIG. 5. As a result, it is pushed upward in the axial direction, and the engaging recess 36 of the upper intermittent member 31 and the engaging piece 41 of the lower intermittent member 32 are engaged. Thus, when the drain valve 1 is returned from the open state to the closed state, the engagement recess 39 and the engagement piece 45 are engaged, and the positioning force (detent torque) of the rotor 22 by the magnetic force of the motor 13 is increased. This is transmitted to the upper intermittent member 31, thereby preventing the upper intermittent member 31 from rotating in the reverse direction.

  Further, as shown in FIGS. 1 and 2, when the drain valve 1 is returned from the open state to the closed state, the wire hoisting pulley 12 rotates in the feeding direction B. In conjunction with the rotation, the output wheel 19 and the follower 46 of the planetary gear mechanism 15 are allowed to rotate in the direction opposite to that during winding of the wire. Since the intermittent gear 31 is prevented from rotating in the reverse direction of the sun gear 35, the planetary gear 49 rotates and revolves in conjunction with the follower 46, and the case 45 rotates to rotate the case 45. Is transmitted to the speed control member 16 via the transmission wheel 79, and the speed control member 16 rotates.

  As a result, as shown in FIGS. 1, 2, and 9, each sliding body 75 of the speed adjusting member 16 spreads radially outward due to centrifugal force and slidably contacts the inner peripheral surface of the cylindrical portion 78. 16 is applied with a braking force, and the rotation speed of the case 45 is adjusted. Therefore, the rotation speed of the wire winding pulley 12 in the delivery direction B is adjusted, and the drain valve 1 is returned from the open state to the closed state. Is adjusted.

  When the motor 13 stops, the rotor 22 stops at an angle of 45 ° (predetermined angle C) with respect to the stator 23 as shown in FIG. 3, whereas the first disk 85 and the rotor 13 stop as shown in FIG. The N pole and the S pole of the second disk 86 are alternately arranged at an angle of 22.5 ° in the circumferential direction, and the angle 45 ° is twice as large as the angle 22.5 °. For this reason, when the motor 13 is stopped and the first disk 85 is stopped together with the rotor 22, even if the stop position of the rotor 22 is shifted in the rotation direction, the stop position of the rotor 22 is shifted every 45 °. The stop position of the disk 85 is also shifted every 45 ° (that is, twice of 22.5 °), and the position of the N pole of the first disk 85 skips the position of the adjacent S pole and the adjacent N pole. And the position of the S pole of the first disk 85 is shifted to the position of the adjacent S pole by skipping the position of the adjacent N pole. Thereby, when the rotation of the rotor 22 stops, the N pole of the first disk 85 and the S pole of the second disk 86 always face each other, and the S pole of the first disk 85 and the N pole of the second disk 86 Are sucked to face each other, and as shown in FIG. 9, the second disk 86 is switched from the second switching position P2 to the first switching position P1.

  When the motor 13 is driven to rotate the first disk 85 together with the rotor 22, the repulsion between the magnetic poles (N pole and S pole) of the first disk 85 and the magnetic poles (N pole and S pole) of the second disk 86. By repeating the suction, the second disk 86 is switched from the first switching position P1 to the second switching position P2, as shown in FIG. At this time, the repulsive force between the magnetic pole of the first disk 85 and the magnetic pole of the second disk 86 increases as the distance between the first disk 85 and the second disk 86 decreases, and thus the second disk 86 shown in FIG. Is maximized in a state in which it is switched to the first switching position P1.

  Therefore, when the first disk 85 starts to rotate together with the rotor 22 from the state where the second disk 86 is switched to the first switching position P1, the N pole of the first disk 85 faces the N pole of the second disk 86. At the same time, the repulsive force when the S pole of the first disk 85 faces the S pole of the second disk 86 is maximized, so that the second disk 86 moves from the first switching position P1 to the second switching position P2. The distance between the first disk 85 and the second disk 86 increases. Immediately after that, the N pole of the first disk 85 faces the S pole of the second disk 86 and the S pole of the first disk 85 faces the N pole of the second disk 86, and a suction force is generated. Since the distance between the first disk 85 and the second disk 86 has already increased, the suction force acting on the second disk 86 becomes weak according to the increase in the distance. As a result, when the first disk 85 rotates together with the rotor 22, the second disk 86 is repelled and attracted by the magnetic poles of the first disk 85 and the second disk 86, as shown in FIG. The first switching position P1 is switched to the second switching position P2, and the second switching position P2 is maintained.

  The switching mechanism 18 includes a first disk 85 that can rotate integrally with the rotor 22 of the motor 13, and a non-rotating second disk 86 that can move toward and away from the first disk 85 in the rotational axis direction D. The first disk 85 and the second disk 86 each have a plurality of different magnetic poles that are alternately arranged in the circumferential direction, so that high-precision machining is not necessary when the switching mechanism 18 is manufactured. . Moreover, since the structure of the switching mechanism 18 is simple, the cost of the switching mechanism 18 can be reduced.

  In the first embodiment, the motor 13 has eight poles as an example, but a plurality of poles other than eight poles may be used. The number of poles (number of magnetic poles) of the first disk 85 and the second disk 86 is set to 16 poles, but is not limited to 16 poles, and is an even multiple of the number of poles of the motor 13 ( For example, the number of poles may be twice.

In the first embodiment, the coil spring 88 is provided as shown in FIG. 9 to FIG.
(Second Embodiment)
In the second embodiment, as shown in FIGS. 15 to 17, the speed adjusting member 16 includes a rotating shaft portion 73 that is rotatably supported by a pin 72, and a speed adjusting member provided on the rotating shaft portion 73. A pinion 74, a pair (several) of sliding bodies 75 provided at the tip of the rotating shaft portion 73, and a speed adjusting gear 101 provided on the outer peripheral portion of the rotating shaft portion 73, are provided with a centrifugal clutch structure. It has a brake type configuration. The speed adjusting pinion 74 meshes with the external gear 48 of the case 45 of the planetary gear mechanism 15.

  Next to the speed control member 16, an interlocking wheel body 103 that is rotatable in conjunction with the speed control member 16 is provided. The interlocking ring body 103 has a stopper projection 104 projecting radially outward and an interlocking pinion 105 integrally on the same axis. The interlocking pinion 105 meshes with the speed control gear 101 of the speed control member 16.

  The switching mechanism 18 includes a first disk 85 (an example of a first member) that is rotatable in conjunction with the rotor 22, and a second disk 86 (an example of a second member) that faces the first disk 85 in the rotational axis direction D. ), A stop lever 87 (an example of a stop member) detachably engageable with the stopper protrusion 104 of the interlocking wheel body 103, and a first coil spring 114 (first attachment) for urging the second disk 86 to the first switching position P1. An example of a biasing member) and a second coil spring 115 (an example of a second biasing member) that biases the second disk 86 to the second switching position P2. The first disk 85 and the second disk 86 are externally fitted to a support shaft 106 fixed in the housing 11.

  The first disk 85 has a pinion 107 at the bottom. A rotatable intermediate ring body 109 is provided between the first disk 85 and the rotor 22. A support shaft 110 fixed in the housing 11 is inserted into the intermediate ring body 109. The intermediate ring body 109 is a gear that is rotatable about the support shaft 110, and the motor pinion 37 of the rotor 22 and the first disk. It meshes with 85 pinions 107. The second disk 86 is fixed in the circumferential direction and does not rotate. The second disk 86 is guided by the support shaft 106 and can be moved toward and away from the first disk 85 in the rotational axis direction D.

  One end of the stop lever 87 can be freely engaged with and disengaged from the stopper projection 104, and the support shaft 110 is inserted into the other end of the stop lever 87. The stop lever 87 is guided by the support shaft 110, and the second disk. 86 can be reciprocated in the direction of the rotational axis D together with 86.

  As shown in FIG. 14, when the second disk 86 is switched to the first switching position P1, the stop lever 87 is guided by the support shaft 110 and moves in one direction, and one end of the stop lever 87 is connected to the interlocking wheel. 103 is detached from the stopper projection 104. Further, as shown in FIG. 15, when the second disk 86 is switched to the second switching position P2, the stop lever 87 is guided by the support shaft 110 and moves in the other direction, and one end of the stop lever 87 is a stopper. Engages with the protrusion 104.

  As shown in FIG. 19, a plurality of different magnetic poles (N poles and S poles) are alternately arranged in the circumferential direction on the mutually opposing surfaces of the first disk 85 and the second disk 86. The number of poles of each of the first disk 85 and the second disk 86 is set to be equal to the number of poles of the rotor 22 of the motor 13. In this case, as an example, the number of poles of each of the first disk 85 and the second disk 86 is set to be the same as the number of poles of the rotor 22, that is, 8 poles.

The number of teeth of the motor pinion 37, the pinion 107, and the intermediate ring body 109 is set such that the rotor 22 rotates once while the first disk 85 rotates twice.
Hereinafter, the operation of the above configuration will be described.
(1) In an initial state in which power is not supplied to the motor 13, the magnetic poles of the first disk 85 and the magnetic poles of the second disk 86 that are stopped are attracted opposite to each other, as shown in FIG. In addition, the second disk 86 is switched to the first switching position P1. As a result, one end portion of the stop lever 87 is detached from the stopper projection 104 of the interlocking wheel body 103 and the rotation of the interlocking wheel body 103 and the speed control member 16 is allowed, so that the case 45 of the planetary gear mechanism 15 is allowed to rotate. It has been switched to the state.
(2) After that, when power is supplied to the motor 13 and the motor 13 is driven, the rotor 22 rotates in one direction, the first disk 85 rotates in one direction via the intermediate ring body 109, and the first disk 85 As shown in FIG. 15, the second disk 86 is switched from the first switching position P1 to the second switching position P2 by repulsion and suction between the magnetic pole of the second disk 86 and the magnetic pole of the second disk 86, and one end of the stop lever 87 Since the portion engages with the stopper protrusion 104 of the interlocking wheel body 103 and the rotation of the interlocking wheel body 103 and the speed control member 16 is restricted, the case 45 of the planetary gear mechanism 15 is switched from the rotation permission state to the rotation restriction state. The rotation of the case 45 is restricted.

When the rotor 22 rotates in one direction as described above in this state, the motor pinion 37 rotates in one direction, the upper intermittent member 31 rotates with the lower intermittent member 32 meshed with the motor pinion 37, and the upper intermittent member. The 31 sun gear 35 rotates. At this time, since the rotation of the case 45 of the planetary gear mechanism 15 is restricted (blocked), the planetary gear 49 revolves while rotating, the connection gear 53 of the driven body 46 rotates, the output wheel 19 rotates, The wire hoisting pulley 12 rotates in the winding direction A against the urging force of the urging tool. Thereby, the wire 21 is wound up by the wire winding pulley 12, the drain valve 1 is opened, and drainage is started.
(3) When the drain valve 1 is fully opened, the engagement state between the engagement recess 36 of the upper intermittent member 31 of the intermittent mechanism 17 and the engagement piece 41 of the lower intermittent member 32 is released, and the rotational driving force of the motor 13 is released. Is not transmitted to the upper intermittent member 31.

In this state, the drain valve 1 tries to start the return operation from the open state to the closed state by the biasing force of the biasing tool, but the rotation of the case 45 of the planetary gear mechanism 15 is prevented as described above. Is maintained and the upper intermittent member 31 is prevented from rotating in the reverse direction, so that the follower 46 of the planetary gear mechanism 15 is prevented from rotating in the reverse direction and the drain valve 1 is kept open. Can do.
(4) When the drain valve 1 is opened as described above and a predetermined time elapses, the motor 13 is stopped by a timer or the like, and the rotor 22 is stopped every predetermined angle C as shown in FIG. The disk 85 is stopped, the magnetic poles of the first disk 85 and the magnetic poles of the second disk 86 are attracted opposite to each other, and the second disk 86 is moved from the second switching position P2 to the second switching position P2, as shown in FIG. It is switched to the 1 switching position P1.

  As a result, one end portion of the stop lever 87 is detached from the stopper projection 104 of the interlocking wheel body 103 and the rotation of the interlocking wheel body 103 and the speed control member 16 is allowed, so that the case 45 of the planetary gear mechanism 15 is prevented from rotating. The state is switched to the rotation allowable state. As a result, the wire hoisting pulley 12 is rotated in the delivery direction B by the urging force of the urging tool, the wire 21 is fed out from the wire hoisting pulley 12, the drain valve 1 is closed, and the return operation is performed to the initial state.

  At the time of the returning operation, as shown in FIG. 14, the locking recess 36 of the interrupting mechanism 17 and the locking piece 41 are engaged, and the positioning force (detent torque) of the rotor 22 by the magnetic force of the motor 13 is intermittently interrupted on the upper side. It will be transmitted to the member 31, and the rotation to the reverse direction of the upper side intermittent member 31 will be prevented. In this state, when the wire winding pulley 12 rotates in the delivery direction B, the output wheel 19 and the follower 46 of the planetary gear mechanism 15 are interlocked with the rotation of the wire winding pulley 12 when winding the wire. The case 45 is allowed to rotate in the reverse direction, but the rotation of the case 45 is allowed and the rotation of the upper intermittent member 31 in the reverse direction of the sun gear 35 is prevented. The planetary gear 49 rotates and revolves in conjunction with the follower 46, the case 45 rotates, the rotation of the case 45 is transmitted to the speed control member 16, and the speed control member 16 rotates. Thereby, since the rotational speed of case 45 is adjusted, the rotational speed to the sending direction B of the wire winding pulley 12 is adjusted.

  As shown in FIG. 19, since the number of poles of the first disk 85 and the second disk 86 is set to 8 poles, which is the same as the number of poles of the rotor 22 (see FIG. 3), As for the magnetic poles with the second disk 86, N poles and S poles are alternately arranged in the circumferential direction every 45 °. Further, since the rotation ratio is set so that the first disk 85 rotates twice while the rotor 22 rotates once, when the motor 13 stops, as shown in FIG. Is stopped every 45 ° with respect to the stator 23, whereas the first disk 85 stops every 90 ° (ie, an angle twice as large as 45 °), as shown in FIG. . As a result, the position of the N pole of the first disk 85 is shifted to the position of the adjacent N pole by skipping the position of the adjacent S pole, and the position of the S pole of the first disk 85 is shifted to the adjacent position. If the position of the N pole is skipped and the position of the adjacent S pole is shifted, and the rotation of the rotor 22 stops, the N pole of the first disk 85 and the S pole of the second disk 86 always face each other. At the same time, the S pole of the first disk 85 and the N pole of the second disk 86 are attracted to face each other, and the second disk 86 is switched from the second switching position P2 to the first switching position P1, as shown in FIG. .

  Further, the switching mechanism 18 includes a first disk 85 that can rotate in conjunction with the rotor 22 of the motor 13, and a non-rotating second disk 86 that can move toward and away from the first disk 85 in the rotational axis direction D. Since the first disk 85 and the second disk 86 each have a plurality of different magnetic poles alternately arranged in the circumferential direction, high-precision machining is necessary when the switching mechanism 18 is manufactured. No. Moreover, since the structure of the switching mechanism 18 is simple, the cost of the switching mechanism 18 can be reduced.

  In the second embodiment, the number of poles of the motor 13, the first disk 85, and the second disk 86 is set to 8 as an example, but a plurality of poles other than 8 may be used. The rotation ratio is set so that the first disk 85 rotates twice while the rotor 22 rotates once. However, the rotation ratio is not limited to such a one-to-two rotation ratio. You may set so that it may become a rotation ratio that the 1st disk 85 carries out an even number rotation, while 22 rotates 1 time.

In the second embodiment, as shown in FIGS. 14 and 15, the first coil spring 114 and the second coil spring 115 are provided, but they may not be provided.
In each of the above embodiments, the strength of the magnetic force can be adjusted by thinning out the number of poles (the number of magnets) of the first disk 85 or the second disk 86.

  In each said embodiment, although the drain valve 1 of the washing machine was mentioned as an example of a target object, it is not limited to the drain valve 1.

1 Drain valve (object)
10 Actuator 12 Wire winding pulley (working wheel)
13 Motor 14 Driving force transmission path 15 Planetary gear mechanism 16 Speed control member 17 Intermittent mechanism 18 Switching mechanism 22 Rotor 23 Stator 35 Sun gear 45 Case (first rotating body)
46 Follower (second rotating body)
47 Internal gear 49 Planetary gear 85 First disc (first member)
86 Second disk (second member)
87 Stop lever (stop member)
A Winding direction (one direction)
B Sending direction (other direction)
C predetermined angle D rotation axis direction P1 first switching position P2 second switching position

Claims (4)

Provided on the operating wheel body that operates the object by rotational force, a motor that rotates the operating wheel body in one direction, a driving force transmission path that transmits the rotational driving force of the motor to the operating wheel body, and a driving force transmission path A planetary gear mechanism, and a switching mechanism for switching the first rotating body provided in the planetary gear mechanism to two different switching states of a rotation permission state and a rotation restriction state,
An actuator biased so that the working wheel rotates in the other direction,
The motor has a rotor having a plurality of magnetic poles and a stator,
The rotor can be stopped at a predetermined angle according to the number of poles of the motor with respect to the stator,
When the motor is driven and the first rotating body of the planetary gear mechanism is switched to one of the switching states by the switching mechanism, the rotational driving force of the motor is transmitted to the working wheel body via the planetary gear mechanism, and the working wheel The body rotates in one direction,
When the motor stops and the first rotating body of the planetary gear mechanism is switched to one of the other switching states by the switching mechanism, the working wheel is rotated in the other direction by the biasing force,
The switching mechanism includes a first member that is rotatable in conjunction with the rotor, and a second member that faces the first member in the direction of the rotation axis.
The second member does not rotate and can be moved toward and away from the first member in the direction of the rotation axis,
Different magnetic poles are alternately arranged in the circumferential direction on the first member and the second member,
When the rotor stops at a predetermined angle, the magnetic poles of the stopped first member and the magnetic poles of the second member are attracted opposite to each other so that the second member approaches the first member and is first Switched to the switching position,
When the rotor rotates, the second member is switched from the first switching position to the second switching position separated from the first member by repetitive repulsion and suction between the magnetic poles of the first member and the second member,
When the second member is switched to the second switching position, switching is made between a rotation permission state in which rotation of the first rotating body of the planetary gear mechanism is allowed and a rotation restriction state in which rotation is restricted. And
An actuator characterized in that, when the second member is switched to the first switching position, the first rotating body of the planetary gear mechanism is switched to a switching state between the rotation permission state and the rotation restriction state. When the motor is driven and the first rotating body of the planetary gear mechanism is switched to the rotation restricted state by the switching mechanism, the rotational driving force of the motor is transmitted to the working wheel body through the planetary gear mechanism, and the working wheel body is integrated. Rotate in the direction
When the motor stops and the first rotating body of the planetary gear mechanism is switched to the rotation-permitted state by the switching mechanism, the working wheel is rotated in the other direction by the biasing force,
By switching the second member to the second switching position, the first rotating body of the planetary gear mechanism is switched to the rotation restricted state,
2. The actuator according to claim 1, wherein the first rotating body of the planetary gear mechanism is switched to a rotation-permitted state by switching the second member to the first switching position. A speed adjusting member for adjusting the rotational speed of the working wheel body in the other direction is provided,
The speed control member is rotatable in conjunction with the first rotating body of the planetary gear mechanism,
The switching mechanism has a stop member that can be freely engaged and disengaged with the speed control member,
When the second member is switched to the second switching position, the stop member engages the speed adjusting member to restrict the rotation of the speed adjusting member, and the first rotating body of the planetary gear mechanism is switched to the rotation restricted state.
When the second member is switched to the first switching position, the stop member is detached from the speed control member to allow the speed control member to rotate, and the first rotating body of the planetary gear mechanism is switched to the rotation allowable state. The actuator according to claim 2, wherein: An intermittent mechanism for interrupting the driving force transmission path between the motor and the planetary gear mechanism is provided,
The planetary gear mechanism includes first and second rotating bodies that are rotatable relative to each other, a sun gear that is provided in the intermittent mechanism, an internal gear that is provided in the first rotating body, and a sun gear that is provided in the second rotating body. A planetary gear meshing with the gear and the internal gear,
The rotation of the second rotating body of the planetary gear mechanism and the rotation of the working wheel body are linked,
When the motor is driven with the driving force transmission path connected by the intermittent mechanism and the first rotating body of the planetary gear mechanism is switched to the rotation restricted state by the switching mechanism, the rotation of the first rotating body is restricted, and the motor Is transmitted to the working wheel body through the planetary gear mechanism,
When the motor is stopped and the first rotating body of the planetary gear mechanism is switched to the rotation-permitted state by the switching mechanism, the working wheel body is rotated in the other direction by the urging force, and the rotation of the working wheel body causes the planetary gear mechanism to 4. The actuator according to claim 3, wherein the one rotating body rotates and the speed regulating member rotates in conjunction with the first rotating body.

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