JP2015195637A - Drain valve driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drain valve driving device capable of preventing an axial position of an inductor from being deviated even in the case where an error is generated in a magnetic center of a member forming an induction motor mechanism, and capable of preventing the lifetime of the device from being reduced by eccentric wearing of a bearing part of the inductor as a result by suppressing vibrations during rotation of the inductor.SOLUTION: In a motor where an induction rotating body is placed, a permanent magnet is fixed in a circumferential direction on an inner peripheral surface of a rotor shank, and a cylindrical induction ring part formed from a non-magnetic conductor is provided at an inner peripheral side of the permanent magnet. A magnetic center in an axial direction of the induction rotating body is placed closer to an opening of a rotor than a magnetic center in an axial direction of the permanent magnet.

Description

  The present invention relates to a drain valve driving device, and more particularly to a drain valve driving device including an induction motor mechanism.

  Patent Document 1 below describes a geared motor that interrupts transmission of driving force from a motor to a driven body by clutch means using magnetic induction.

JP 2010-276093 A

  The axial lengths and arrangement positions of members such as the non-magnetic conductive ring 13b and the back yoke ring 13c of the magnetic induction rotating body 13 and the magnetic induction magnet 112, which constitute the induction motor mechanism of Patent Document 1, are generally defined as follows. The axial magnetic center is designed to coincide with the radial direction.

  However, due to the accumulated tolerance at the time of manufacture and assembly, the magnetic centers of these members do not always match as calculated. In particular, the magnetic center of the magnetic induction rotating body 13 is more than the magnetic center of the magnetic induction magnet 112. 3 (hereinafter referred to as “the same figure”) below, a force is exerted between the magnetic induction rotating body 13 and the magnetic induction magnet 112 to make the magnetic center coincide with the radial direction. Thus, there is a possibility that the magnetic induction rotating body 13 is slightly lifted upward in the figure.

  When the magnetic induction rotator 13 floats upward from the original position in the figure, the sliding contact area between the magnetic induction rotator 13 and the rotation support portion 11a is reduced, and the vibration during rotation of the magnetic induction rotator 13 is increased. . When the deflection of the magnetic induction rotator 13 increases, the position of the portion where the air gap between the magnetic induction rotator 13 and the magnetic induction magnet 112 becomes narrower, or the portion where the magnetization amount of the magnetic induction magnet 112 is larger than the others. The magnetic induction rotating body 13 may be sucked in a specific direction and rotate in a tilted state due to a combined factor with the position and the like, and there is a risk of causing uneven wear on the sliding surface with the rotation support portion 11a.

  When uneven wear occurs in the rotation support portion 11a, resistance is generated in the rotation of the magnetic induction rotating body 13, and the rotation load is transmitted to the sector gear 28 via the brake pinion 13a. When the rotational load becomes larger than the urging force of the return spring 27 of the sector gear 28, the sector gear 28 will not return to the original position even if the power supply to the stator 15 is cut off. There is a risk of causing a problem that it cannot return to the original position.

  In view of the above problems, the problem to be solved by the present invention is to prevent the displacement of the axial position of the derivative even if a slight error occurs in the magnetic center of the member constituting the induction motor mechanism, and thus Another object of the present invention is to provide a drain valve driving device capable of suppressing a vibration during rotation of a derivative and preventing a decrease in device life due to uneven wear of a bearing portion of the derivative.

  In order to solve the above problems, a drain valve driving device of the present invention includes a motor that rotates in one direction, and a first transmission train that is a gear train that transmits a driving force of the motor to a drain valve that is a driven body. The motor includes a rotor boss portion that is rotatably supported by a fixed shaft, and one end portion in the axial direction is fixed to the rotor boss portion so as to be integrated with the rotor boss portion. A rotor having a cylindrical rotor body having an opening formed at the other end, and a permanent magnet is fixed to the inner peripheral surface of the rotor body along the circumferential direction. And a derivative shaft portion rotatably supported by the rotor boss portion on the inner peripheral side of the permanent magnet, and a guide ring portion that rotates integrally with the derivative shaft portion by being fixed to the derivative shaft portion. An induction rotator comprising: the induction ring Comprises a cylindrical derivative made of a non-magnetic conductor and a sucked part made of a ferromagnetic material, and the sucked part of the guide ring part has a magnetic center in the axial direction of the induction rotating body, The gist is that the permanent magnet is disposed at a position closer to the opening than the magnetic center in the axial direction of the permanent magnet.

  By designing the magnetic center in the axial direction of the induction rotator in advance to be closer to the opening than the magnetic center in the axial direction of the permanent magnet, the induction rotator can be opened even if an error in the magnetic center due to cumulative tolerance occurs. Since the induction rotating body is lifted to the opening side, the phenomenon that the induction rotating body floats to the opening side can be prevented, the vibration during rotation of the induction rotating body is suppressed, and uneven wear of the bearing portion of the induction rotating body is suppressed. It is possible to prevent the device life from being reduced.

  When the attracted portion is a cylindrical back yoke portion fixed to the inner peripheral side of the derivative, the axial center of the back yoke portion is closer to the opening than the axial center of the permanent magnet. By doing so, the magnetic center in the axial direction of the induction rotating body can be placed closer to the opening than the magnetic center in the axial direction of the permanent magnet. Further, when the derivative is sandwiched between the permanent magnet and the back yoke portion, the lines of magnetic force passing through the derivative are increased, and the rotational torque of the induction rotating body that rotates with the permanent magnet is increased.

  In addition, it is desirable that the derivative shaft portion is rotatably supported by the rotor boss portion when a part of the inner peripheral surface in the axial direction is in sliding contact with the rotor boss portion.

  Since the induction rotating body is an induction motor mechanism that rotates with the permanent magnet due to the electromagnetic induction effect of eddy current generated by the rotation of the permanent magnet, its torque is smaller than that of the synchronous motor. Therefore, by limiting the sliding contact area between the dielectric shaft portion and the rotor boss portion, it is possible to reduce the sliding resistance of the induction rotating body and to effectively use the torque of the induction rotating body. According to the motor of the present invention, since the phenomenon that the induction rotating body floats to the opening side is prevented, the reliability as a product is impaired even if the sliding contact area between the dielectric shaft portion and the rotor boss portion is minimized. I can't.

  In this case, both ends of the axial direction of the inner peripheral surface of the derivative shaft portion are in sliding contact with the rotor boss in the radial direction, and the opposite end portion of the derivative shaft portion on the opening side is the end portion in the axial direction of the derivative shaft portion. It can be considered that the rotor boss portion is configured to be rotatably supported by the rotor boss portion by slidingly contacting the rotor boss portion in the thrust direction. According to the motor of the present invention, the induction rotating body is pulled to the opposite side of the rotor opening by the action of the magnetic attraction force between the induction rotating body and the permanent magnet, and the derivative shaft portion is against the rotor boss portion. Since the sliding contact is ensured in the thrust direction, the inclination of the induction rotating body is further suppressed.

  In addition, a clutch means for switching the transmission of the driving force by the first transmission train to the “engaged” state or the “disconnected” state, and a second transmission train which is a gear train for transmitting the driving force of the motor to the clutch means. A pinion portion that is a gear portion having a radius smaller than the radius of the guide ring portion is formed at the opening side end portion of the derivative shaft portion, and the second transmission train is It has a gear member that meshes with the pinion part and rotates by the rotation of the pinion part, and the gear member is connected to a biasing member that biases the gear member in the original position direction. good.

  According to the motor of the present invention, the phenomenon that the induction rotator floats to the opening side is prevented, and vibration during rotation of the induction rotator is suppressed, so that uneven wear of the bearing portion of the induction rotator is also prevented. Is done. Therefore, even when the gear member that returns to the original position by the biasing member is engaged with the pinion portion of the induction rotating body, the return operation of the gear member is not hindered by the rotational load of the induction rotating body.

  According to the drain valve driving device according to the present invention, even when an error occurs in the magnetic center of the member constituting the induction motor mechanism, the displacement of the derivative in the axial direction can be prevented, and the deflection during rotation of the derivative can be prevented. Thus, it is possible to prevent a decrease in the device life due to uneven wear of the bearing portion of the derivative.

It is a disassembled perspective view of the drain valve drive device in this embodiment. It is sectional drawing which shows the internal structure of a motor. It is the figure which expanded the drain valve drive device along the transmission line. It is a top view of the drain valve drive device of the state where the upper case was removed. It is a top view of the drain valve drive device of the state where the upper case and the 1st transmission line were removed. It is an external view of a rotor, a second transmission train, and a first lock gear. It is the figure which decomposed | disassembled the clutch means (planetary gear mechanism), and was seen from the upper direction. It is the figure which decomposed | disassembled the clutch means (planetary gear mechanism), and was seen from the downward direction.

(overall structure)
Hereinafter, embodiments of a drain valve driving device 1 according to the present invention will be described in detail with reference to the drawings. In addition, the upper and lower in the following description shall mean the upper and lower in FIG. 1 (the upper case 91 side is the upper side and the lower case 92 side is the lower side). The “original position” refers to the position of each constituent member when the drain valve driving device 1 is stopped.

  The drain valve driving device 1 according to the present embodiment includes a motor 10 that is a drive source, a first transmission train that is a gear train that transmits the power of the motor 10 to a drain valve 95 that is a driven body, A clutch means for switching the transmission of the driving force by the transmission train to the “joined” state or the “disengaged” state, and a second transmission train which is a gear train for transmitting the driving force of the motor 10 to the clutch means. Members (except for pulleys 26 and wires 27 described later) are accommodated in a case 90 including an upper case 91 and a lower case 92.

(Motor configuration)
FIG. 2 is a cross-sectional view showing a configuration of the motor 10 provided in the drain valve driving device 1. The motor 10 is an AC motor that rotates only in one direction by a later-described reverse rotation prevention mechanism. The motor 10 includes a motor case 11 made of a substantially cup-shaped magnetic metal whose upper surface is open, a stator 12 disposed along the inner peripheral surface of the motor case 11, and a rotor disposed on the inner peripheral side of the stator 12. 51, and an inner magnet 54 and an induction rotating body 55 fixed to the inner peripheral side of the rotor 51.

  A rotor support shaft 130 which is a fixed shaft made of metal such as stainless steel is press-fitted and fixed to the center of the bottom of the motor case 11 and extends upward. The upper surface of the stator 12 is covered with a support plate 121 made of a magnetic metal having an opening in a range where the rotor 51 is disposed. A through hole into which the lower end portion of the support shaft that supports the first transmission row (excluding the upper motor gear 21, the pulley 26, and the wire 27) and the members constituting the second transmission row is press-fitted into the support plate 121. Is formed.

  The rotor 51 is an outer magnet 53 that is a cylindrical rotor body made of a permanent magnet, and a resin member that is insert-molded to the outer magnet 53, and is a rotor boss portion 52 that is rotatably supported by the rotor support shaft 130. And consist of The outer magnet 53 rotates integrally with the rotor boss portion 52 by being fixed to the rotor boss portion 52. The rotor 51 is disposed on the inner peripheral side of the stator 12 so that the outer magnet 53 faces the stator 12.

  The outer magnet 53 has a fixed portion 531 extending from the inner peripheral surface in the vicinity of the lower end portion toward the center in the radial direction, and the upper end portion is an opening. A rotor-side reverse rotation prevention portion 532 that constitutes a reverse rotation prevention mechanism of the motor 10 to be described later is formed in the opening. The rotor-side reverse rotation prevention unit 532 extends above the upper surface of the support plate 121.

  The rotor boss portion 52 includes a shaft portion 521 having a through hole through which the rotor support shaft 130 is inserted, and a flange portion 522 in which a lower end portion of the shaft portion 521 extends radially outward. More specifically, in the vicinity of the flange portion 522 of the shaft portion 521, a first staircase portion 523 and a second staircase portion 524 whose diameter is increased stepwise toward the flange portion 522 side are formed. The flange portion 522 is a portion extending further outward in the radial direction from the second step portion 524. The flange portion 522 is formed so as to sandwich the upper surface and the lower surface of the fixed portion 531 of the outer magnet 53, and connects the rotor boss portion 52 and the outer magnet 53. On the upper surface of the shaft portion 521, there are formed lower engaging portions 525 which are four protrusion portions arranged at equal intervals in the circumferential direction.

  An inner magnet 54 that is a permanent magnet is fixed along the circumferential direction on the inner circumferential surface of the outer magnet 53 of the rotor 51.

  An induction rotating body 55 is disposed on the inner peripheral side of the inner magnet 54. The induction rotator 55 includes a induction ring portion 57 and a dielectric shaft portion 56 that is insert-molded on the induction ring portion 57 and is rotatably supported by the rotor boss portion 52. The guide ring portion 57 is fixed to the derivative shaft portion 56 and thereby rotates integrally with the derivative shaft portion 56.

  The guide ring portion 57 is a attracted body made of a copper tube 571 that is a cylindrical derivative made of copper, which is a nonmagnetic conductor, and iron, which is a ferromagnetic material, to which the magnetic attraction force of the inner magnet 54 acts. And an iron pipe 572 that is a cylindrical back yoke portion that is press-fitted into the inner peripheral side of the copper pipe 571. Each of the copper pipe 571 and the iron pipe 572 has fixed portions 5711 and 5721 extending from the inner peripheral surface of the upper end portion toward the radial center.

  The derivative shaft portion 56 is a guide ring coupling that connects the tubular portion 561 through which the shaft portion 521 of the rotor boss portion 52 is inserted, the fixed portion 5711 of the copper tube 571 and the fixed portion 5721 of the iron tube 572 to the derivative shaft portion 56. Part 562.

  A pinion portion 563 that is a gear portion having a radius smaller than the radius of the guide ring portion 57 is formed at the upper end portion of the cylindrical portion 561. The pinion part 563 extends above the upper surface of the support plate 121. The pinion portion 563 is meshed with a tooth portion of a sector gear 42 that is a gear member constituting a second transmission train described later. A tension coil spring 435 that is a biasing member that biases the sector gear 42 toward the original position is connected to the sector gear 42.

  The cylindrical portion 561 is in sliding contact with the rotor boss portion 52 only at the upper end portion and the lower end portion of the inner peripheral surface thereof. More specifically, the upper end portion of the tubular portion 561, that is, the inner peripheral surface of the pinion portion 563 is in sliding contact with the shaft portion 521 in the radial direction, and the inner peripheral surface of the lower end portion of the tubular portion 561 is the first staircase portion 523. The bottom surface of the lower end portion is in sliding contact with the upper surface of the second staircase portion 524 in the thrust direction.

  The induction rotating body 55 is an induction motor mechanism that rotates with the inner magnet 54 due to the electromagnetic induction action of the eddy current generated by the rotation of the inner magnet 54, and therefore is compared with the torque of the rotor 51 that is a synchronous motor mechanism. The torque is small. Therefore, the sliding contact area between the cylindrical portion 561 and the rotor boss portion 52 is minimized to suppress sliding resistance and effectively use torque.

  The guide ring coupling portion 562 is formed so as to sandwich the upper surfaces of the fixed portions 5711 and 5721 and the lower surface of the fixed portion 5721 and support the inner peripheral surface of the iron pipe 572. The lower surface of the fixed portion 5711 is supported by the upper surface of the fixed portion 5721, and the inner peripheral surface of the copper tube 571 is supported by the outer peripheral surface of the copper tube 571.

  Here, the center of the axial length of the iron pipe 572 is above the center of the axial length of the inner magnet 54. With this configuration, the magnetic center in the axial direction of the guide ring portion 57, that is, the guide rotator 55, is previously placed above the magnetic center in the axial direction of the inner magnet 54. Therefore, even if a slight error occurs in the magnetic center due to the accumulated tolerance, only the force by which the induction rotator 55 is pulled downward increases or decreases, and the induction rotator 55 floats to the opening side of the rotor 51. There is no. By ensuring the original sliding area between the induction rotator 55 and the rotor boss portion 52, vibration during rotation of the induction rotator 55 can be suppressed, and deterioration of the device life due to uneven wear of the rotor boss portion 52 can be prevented. Can do.

(First transmission line)
Hereinafter, another configuration of the drain valve driving device 1 will be described in detail with reference to FIGS. 3 to 8. The first transmission train constitutes an output system that transmits the driving force of the motor 10 to the drain valve 95. The first transmission train has a plurality of power transmission members. Specifically, the upper motor gear 21, the input side gear 22 that meshes with the upper motor gear 21, the output side gear 23 that rotates as the input side gear 22 rotates when the clutch means is in the “joint” state, A composite gear 24 meshed with the side gear 23, a cam gear 25 meshed with the composite gear 24, a pulley 26 that rotates integrally with the cam gear 25, and a wire 27 that is wound up by the rotation of the pulley 26. Among these, the input side gear 22, the output side gear 23, and the compound gear 24 are housed inside the case 90 and are rotatably supported on each support shaft formed of a metal such as stainless steel press-fitted and fixed to the support plate 121. Has been. The input side gear 22 and the output side gear 23 are also gears constituting clutch means (differential gear mechanism based on a planetary gear train) whose details will be described later.

  The upper motor gear 21 is a spur gear supported by the rotor support shaft 130 so as to be rotatable and movable in the axial direction, and is supported on the rotor boss portion 52. A locked projection 211 is integrally formed on the upper surface of the upper motor gear 21. The upper motor gear lock protrusion 62 of the sector lever 60 described later acts on the locked protrusion 211. An upper engagement portion 2111 that engages with the lower engagement portion 525 is formed on the lower surface of the upper motor gear 21, and the upper motor gear 21 is disposed between the lower engagement portion 525 and the upper engagement portion 2111. The rotor 51 in which the lower engaging portion 525 is formed is urged downward in the axial direction by the compression coil spring 48.

  An input side gear 22 meshes with the upper motor gear 21. The input side gear 22 is one gear constituting a planetary gear train and is a so-called sun gear. The input side gear 22 has a large tooth portion 221 having a relatively large diameter and a small tooth portion 222 having a relatively small diameter. The upper motor gear 21 meshes with the large tooth portion 221 of the input side gear 22, and the input side gear 22 rotates as the upper motor gear 21 rotates.

  Although details will be described later, when the clutch means is in the “joining” state, the driving force of the motor 10 is transmitted to the output side gear 23 via the upper motor gear 21. The output side gear 23 includes three planetary gears 231 and a planetary support gear 232 that are gears constituting a planetary gear train. The planetary gear 231 is rotatably supported by three planetary gear support shafts that protrude from the upper end surface of the planetary support gear 232 and are provided at equal intervals in the circumferential direction. A retaining ring 233 is fixed to the upper end of the planetary gear support shaft to prevent the planetary gear 231 from falling off. The planetary support gear 232 has a gear portion 2321 on the side opposite to the surface to which the planetary gear 231 is attached. The planetary gear 231 meshes with the small tooth portion 222 of the input side gear 22.

  The compound gear 24 meshes with the planetary support gear 232. Specifically, the compound gear 24 has a small tooth portion 241 having a relatively small diameter on the upper side and a large tooth portion 242 having a relatively large diameter on the lower side on the same axis, and the large tooth portion 242 is the planetary support gear 232. Is engaged with the gear portion 2321. As a result, the compound gear 24 rotates as the planetary support gear 232 rotates.

  A cam gear 25 meshes with the compound gear 24. Specifically, the gear portion 251 of the cam gear 25 meshes with the small tooth portion 241 of the compound gear 24. As a result, the cam gear 25 rotates as the compound gear 24 rotates. A cam groove 252 is formed on the upper end surface of the portion where the gear portion 251 is formed on the outer periphery of the cam gear 25. An engaging protrusion 61 formed on the lower end surface of the sector lever 60 is engaged with the cam groove 252. The configuration and operation of the sector lever 60 will be described later.

  A pulley 26 is fixed to the cam gear 25. The fixing method is not particularly limited as long as the pulley 26 rotates integrally with the cam gear 25. Thereby, the pulley 26 rotates with the rotation of the cam gear 25. The pulley 26 is exposed to the outside of the case 90. A wire groove 261 is formed on the outer periphery of the pulley 26.

  One end of a wire 27 is fixed to the pulley 26. The fixing method is not particularly limited as long as it can reliably prevent the wire 27 from falling off. When the pulley 26 rotates in the direction in which the wire 27 is drawn, the wire 27 is wound up so as to fit into the wire groove 261 of the pulley 26. A drain valve 95 is fixed to the other end side of the wire 27, and the drain valve 95 always has a biasing force or a magnetic force by a spring in a direction to return to the original position (position where the valve body is closed). The load is acting. When the wire 27 is wound around the pulley 26, the drain valve 95 is opened.

(Clutch means)
The clutch means plays a role of switching the transmission (output system) of the driving force by the first transmission train to the “joined” state or the “disconnected” state. The operation of the clutch means in this embodiment is based on a planetary gear train having an input side gear 22 (sun gear), an output side gear 23 (planetary gear 231 and planetary support gear 232), and a fixed gear 31 (ring gear). A differential gear mechanism is used.

  In the center of the fixed gear 31 that is a ring gear, a hole through which the small tooth portion 222 of the input side gear 22 that is a sun gear passes is provided. The fixed gear 31 has an outer tooth portion 311 and an inner tooth portion 312. The external tooth portion 311 of the fixed gear 31 is positioned below the large tooth portion 221 of the input side gear 22 and meshes with a second lock gear 33 that is one gear constituting a second transmission train described later. Yes. That is, when the rotation of the second lock gear 33 is blocked, the rotation of the fixed gear 31 is blocked. The internal gear portion 312 of the fixed gear 31 meshes with the three planetary gears 231.

  In the clutch means having such a configuration, whether or not the planetary gear 231 revolves and the planetary support gear 232 rotates depends on whether or not the rotation of the fixed gear 31 is blocked. In the case where the rotation of the fixed gear 31 is blocked, when the input side gear 22 rotates, the internal tooth portion 312 of the fixed gear 31 does not move. Therefore, the small teeth of the input side gear 22 along the internal tooth portion 312. The planetary gear 231 meshing with the portion 222 revolves and the planetary support gear 232 rotates. On the other hand, when the rotation of the fixed gear 31 is not blocked, even if the input side gear 22 rotates and the planetary gear 231 tries to revolve, the fixed gear 31 rotates idly, so that the planetary support gear 232 does not rotate.

  That is, if the rotation of the fixed gear 31 is prevented, the first transmission train is in the “join” state, and if the rotation of the fixed gear 31 is not blocked, the first transmission train is in the “disconnected” state. . If the first transmission train is in the “joining” state by the clutch means, that is, if the output system is in the “joining” state, the driving force of the motor 10 is transmitted to the drain valve 95 via the first transmission train. On the other hand, if the first transmission train is in the “disconnected” state by the clutch means, that is, if the output system is in the “disconnected” state, the driving force of the motor 10 is disconnected by the clutch means (the input gear 22 and the output gear 23 are Are not transmitted to the drain valve 95.

  The clutch means in this embodiment further includes a first lock gear 32 and a second lock gear 33 as members acting on the fixed gear 31. The first lock gear 32 has a disk-shaped portion formed with a locked portion 321 that is a protrusion (claw) projecting radially outward on the outer surface, and a disk-shaped portion below the disk-shaped portion. A first lock tooth portion 322 having a smaller diameter than the outer diameter of the portion is provided. The second lock gear 33 includes a relatively large-diameter large-diameter second lock tooth portion 331 and a relatively small-diameter small-diameter second lock tooth portion 332. The large-diameter second lock tooth portion 331 meshes with the first lock tooth portion 322. The small-diameter second lock tooth portion 332 meshes with the external tooth portion 311 of the fixed gear 31 constituting the planetary gear train. When the lock lever 432 (described later) of the sector gear 42 is caught by the locked portion 321 of the first lock gear 32, the rotation of the first lock gear 32 is prevented. When the rotation of the first lock gear 32 is blocked, the rotation of the second lock gear 33 meshed with the first lock gear 32 and the fixed gear 31 meshed with the first lock gear 32 are blocked, and the first transmission train enters the “joint” state.

(Second transmission line)
The second transmission train constitutes a clutch operating system that transmits the driving force of the motor 10 to the clutch means. The second transmission train includes a pinion portion 563 and a sector gear 42 that meshes with the pinion portion 563.

  The sector gear 42 has a tooth portion 422 that meshes with the pinion portion 563, and rotates as the pinion portion 563 rotates.

  Further, the sector gear 42 is formed with a reverse rotation preventing portion 423 protruding downward from one end side of the tooth portion 422. When the rotor 51 located at the original position rotates in the reverse direction, the rotor-side reverse rotation prevention unit 532 and the reverse rotation prevention unit 423 of the sector gear 42 collide with each other. Due to the impact at the time of the collision, the rotation of the reversely rotated rotor 51 is corrected to normal rotation.

  The sector gear 42 is integrally formed with a lock lever 432 that protrudes radially outward from an axial portion through which the sector gear support shaft 430 is inserted. When the sector gear 42 rotates in the direction in which the lock lever 432 approaches the first lock gear 32, the lock lever 432 is hooked on the locked portion 321 formed on the outer surface of the first lock gear 32. As a result, the rotation of the first lock gear 32 is prevented.

(Biasing means)
The urging means urges the second transmission train in a direction to place the clutch means in the “disengaged” state. In this embodiment, a tension coil spring 435 is used. One end of the tension coil spring 435 is hooked on a first coil spring hooking portion 433 formed on the sector gear 42, and the other end is hooked on a second coil spring hooking portion 434 that is press-fitted and fixed to the support plate 121. The sector gear 42 is urged by the tension coil spring 435 in a direction in which the lock lever 432 moves away from the first lock gear 32 (locked portion 321).

(Other configurations)
A sector lever 60 is disposed on the compound gear 24. An engagement protrusion 61 (see FIG. 1) is formed on the lower surface of the sector lever 60. The engaging protrusion 61 is engaged with a cam groove 252 (see FIG. 1) formed on the upper surface of the cam gear 25. Similarly, an upper motor gear lock projection 62 and an inclined cam (not shown) are formed from the lower surface of the sector lever 60. These functions are as follows. The sector lever 60 moves in conjunction with the operation of the cam gear 25 by the engagement protrusion 61 that engages with the cam groove 252. When the fan-shaped lever 60 moves to a predetermined position (the wire 27 is wound up to a predetermined position), the upper motor gear lock projection 62 acts on the locked projection 211 of the upper motor gear 21 to prevent the upper motor gear 21 from rotating. At the same time, the upper motor gear 21 pressed downward in the axial direction by the inclined cam is released and moved upward in the axial direction by the compression coil spring 48. Thereby, the upper engagement portion 2111 of the upper motor gear 21 and the lower engagement portion 525 of the rotor boss portion 52 are disengaged. That is, the power of the motor 10 is not transmitted to the upper motor gear 21 (refer to the operation description below for details).

(Operation of drain valve drive device)
Operation | movement of the drain valve drive device 1 provided with the above structure is demonstrated. In the following description, the power of the motor 10 is transmitted to the drain valve 95 in the original position, 1) the power transmission operation, and the power transmission of the motor 10 is cut off and the drain valve 95 is returned to the original position. This will be explained separately.

1) Power transmission operation When the drain valve 95 is in the original position (the wire 27 is not wound around the pulley 26), the upper motor gear 21 resists the biasing force of the compression coil spring 48 by the inclined cam of the sector lever 60. Thus, the upper engagement portion 2111 and the lower engagement portion 525 are engaged with each other. When the motor 10 is driven in one direction from this state and the rotor 51 rotates, the upper motor gear 21 having the upper engagement portion 2111 that engages with the lower engagement portion 525 formed on the rotor boss portion 52 of the rotor 51 rotates. To do. Further, the induction rotating body 55 is rotated by being guided by the inner magnet 54 fixed inside the rotor 51. As the induction rotating body 55 rotates, the pinion portion 563 also rotates. Since the copper tube 571 is sandwiched between the inner magnet 54 and the iron tube 572 acting as a back yoke, the lines of magnetic force passing through the copper tube 571 are increased, and the rotation of the induction rotating body 55 that rotates with the inner magnet 54 rotates. Torque is increased.

  When the pinion part 563 rotates, the sector gear 42 having the tooth part 422 engaged therewith rotates. The sector gear 42 rotates in a direction in which the lock lever 432 approaches the first lock gear 32 (locked portion 321) against the urging force of the tension coil spring 435.

  When the lock lever 432 enters the movement locus of the locked portion 321 and is caught by the locked portion 321, the rotation of the first lock gear 32 is prevented. When the rotation of the first lock gear 32 is blocked, the rotation of the second lock gear 33 having the large-diameter second lock tooth portion 331 that meshes with the first lock tooth portion 322 of the first lock gear 32 is blocked. The fixed gear 31 having the external tooth portion 311 that meshes with the small-diameter second lock tooth portion 332 of the second lock gear 33 is prevented from rotating.

  As described above, the fixed gear 31 constitutes the planetary gear train of the clutch means. Therefore, when the rotation of the fixed gear 31 is prevented, the transmission of power by the first transmission train is brought into a “joint” state by the clutch means, and the driving force of the motor 10 is discharged through the first transmission train. It is possible to transmit up to 95.

  On the other hand, the upper motor gear 21 that rotates together with the rotor boss portion 52 by driving the motor 10 meshes with the large tooth portion 221 of the input side gear 22 (sun gear) constituting the planetary gear train. Accordingly, the input side gear 22 rotates with the rotation of the upper motor gear 21.

  Three planetary gears 231 constituting the output side gear 23 are meshed with the outside of the small tooth portion 222 of the input side gear 22. An inner tooth portion 312 of the fixed gear 31 meshes with the outside of the planetary gears 231 arranged at equal intervals in the circumferential direction. As described above, the fixed gear 31 is prevented from rotating by the second lock gear 33. Therefore, when the input side gear 22 rotates, the planetary gear 231 revolves around the small tooth portion 222. When the planetary gear 231 revolves, the planetary support gear 232 that supports the planetary gear 231 rotates. That is, all the rotational power of the input side gear 22 is transmitted to the output side gear 23.

  If the input side gear 22 rotates when the rotation of the first lock member 32 is not blocked, that is, when the rotation of the fixed gear 31 is not blocked, the rotation is fixed via the planetary gear 231. The gear 31 idles. Since the power transmission train after the planetary support gear 232 includes a load on the transmission train itself and a load on the drain valve 95, all the rotational power of the input side gear 22 is transmitted to the fixed gear 31 side. is there.

  The large gear portion 242 of the compound gear 24 meshes with the gear portion 2321 of the planetary support gear 232. Therefore, the compound gear 24 rotates as the planetary support gear 232 rotates.

  The gear portion 251 of the cam gear 25 meshes with the small tooth portion 241 of the compound gear 24. Therefore, the cam gear 25 rotates with the rotation of the compound gear 24.

  When the cam gear 25 rotates, the pulley 26 fixed to the upper end of the cam gear 25 rotates. When the pulley 26 rotates, the wire 27 fixed to the pulley 26 is wound up along the wire groove 261. A drain valve 95 is fixed to the tip of the wire 27. When the drain valve 95 is pulled up, the drain port is opened and drainage is started.

  The winding of the wire 27 by the pulley 26 is stopped as follows. When the cam gear 25 rotates to a predetermined position (when the wire 27 is wound up by a predetermined amount), the sector lever 60 having the engagement protrusion 61 that engages with the cam groove 252 rotates in a direction away from the cam gear 25. When the sector lever 60 rotates in this manner, the upper motor gear lock projection 62 of the sector lever 60 contacts the locked projection 211 of the upper motor gear 21 from the circumferential direction. As a result, the upper motor gear 21 is prevented from rotating. Further, the upper motor gear 21 pressed downward in the axial direction by the inclined cam of the sector lever 60 is released and moved upward in the axial direction by the compression coil spring 48. As a result, the upper engagement portion 2111 of the upper motor gear 21 and the lower engagement portion 525 of the rotor boss portion 52 are disengaged, and the power of the motor 10 is not transmitted to the upper motor gear 21. When the upper motor gear 21 is prevented from rotating, the operation of each member constituting the first transmission train is also stopped. That is, the winding of the wire 27 by the pulley 26 is stopped, and the pulley 26 is held at the winding position (a state in which the drain outlet is kept open).

  In this way, the power transmission operation for transmitting the power of the motor 10 to the drain valve 95 is completed.

2) Power cut-off operation When the drain valve 95 is returned to the original position after the power transmission operation is completed, the drive of the motor 10 is stopped (power supply to the motor 10 is stopped). Then, the magnetic induction force between the inner magnet 54 provided inside the rotor 51 and the induction rotating body 55 disappears. That is, the magnetic induction force that has operated the clutch means in the direction to bring the first transmission train into the “joining” state against the urging force of the tension coil spring 435 disappears. Therefore, the sector gear 42 rotates in a direction in which the lock lever 432 is separated from the first lock gear 32 (the locked portion 321) by the biasing force of the tension coil spring 435. That is, the state in which the rotation of the first lock gear 32 is prevented is eliminated, and the clutch means places the first transmission train in the “disconnected” state. The urging force rotates the sector gear 42 and the pinion portion 563 (induction rotating body 55) in a direction to return to the original position.

  In the present invention, the phenomenon that the induction rotator 55 floats to the opening side of the rotor 51 is prevented, and the vibration during rotation of the induction rotator 55 is suppressed, so that uneven wear of the rotor boss portion 52 is also prevented. . Therefore, even when the sector gear 42 that returns to the original position by the tension coil spring 435 is engaged with the pinion portion 563 of the induction rotating body 55, the return operation of the sector gear 42 is hindered by the rotational load of the induction rotating body 55. There is no.

  The drain valve 95 is always going to return to the original position due to an external load acting on the drain valve 95. Therefore, when the clutch means is in the “disengaged” state and the fixed gear 31 can freely rotate, the load applied to the drain valve 95 causes the output side gear 23 ( Is transmitted to the planetary support gear 232). The energy based on the load applied to the drain valve 95 thus transmitted is output (consumed) by idling of the fixed gear 31. Thereby, the drain valve 95 returns to the original position.

  Further, when the cam gear 25 returns to the original position, the sector lever 60 having the engagement protrusion 61 that engages with the cam groove 252 rotates in a direction approaching the cam gear 25. When the sector lever 60 rotates in this way, the upper motor gear lock projection 62 of the sector lever 60 is separated from the locked projection 211 of the upper motor gear 21. As a result, the upper motor gear 21 is allowed to rotate. Further, the upper motor gear 21 urged upward in the axial direction by the compression coil spring 48 is pressed against the inclined cam and moves downward in the axial direction. As a result, the upper engagement portion 2111 of the upper motor gear 21 and the lower engagement portion 525 of the rotor boss portion 52 are engaged, and the driving force of the motor 10 is also transmitted to the upper motor gear 21.

  Thus, when the motor 10 is stopped, the lock of the fixed gear 31 constituting the planetary gear train is released by the action of the tension coil spring 435, and the clutch means places the first transmission train in the “disconnected” state. Thereby, the drain valve 95 returns to the original position.

  Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the gist of the present invention.

DESCRIPTION OF SYMBOLS 10 Motor 11 Motor case 12 Stator 121 Support plate 130 Rotor spindle 52 Rotor boss part 521 Shaft part 522 Flange part 523 First step part 524 Second step part 525 Lower engagement part 531 Fixed part 53 Outer magnet 54 Inner magnet 55 Guide Rotating Body 56 Derivative Shaft 561 Cylindrical Portion 562 Guide Ring Coupling Portion 563 Pinion Portion 57 Guide Ring Port 571 Copper Tube 5711 Fixed Portion 572 Iron Tube 5721 Fixed Portion 21 Upper Motor Gear 22 Input Side Gear 23 Output Side Gear 24 Compound gear 25 Cam gear 31 Fixed gear 32 First lock gear 33 Second lock gear 42 Fan gear 432 Lock lever 435 Tensile coil spring 60 Fan lever

Claims (5)

A motor that rotates in one direction;
A drainage valve driving device comprising: a first transmission train that is a gear train that transmits the driving force of the motor to a drainage valve that is a driven body;
The motor has a rotor boss portion that is rotatably supported by a fixed shaft, and one end portion in the axial direction rotates integrally with the rotor boss portion, and the other end portion has an opening. And a rotor having a cylindrical rotor body part formed with,
A permanent magnet is fixed along the circumferential direction on the inner peripheral surface of the rotor body,
On the inner peripheral side of the permanent magnet, a derivative shaft portion rotatably supported by the rotor boss portion, and a guide ring portion that rotates integrally with the derivative shaft portion by being fixed to the derivative shaft portion, An induction rotating body is provided,
The induction ring portion includes a cylindrical derivative made of a nonmagnetic conductor, and a sucked portion made of a ferromagnetic material,
The attracted portion of the guide ring portion is arranged such that the magnetic center in the axial direction of the induction rotating body is closer to the opening than the magnetic center in the axial direction of the permanent magnet. Drain valve drive device. The suctioned portion is a cylindrical back yoke portion fixed to the inner peripheral side of the derivative,
2. The drain valve driving device according to claim 1, wherein a center of an axial length of the back yoke portion is closer to the opening than a center of an axial length of the permanent magnet.   The said derivative | guide_body shaft part is rotatably supported by the said rotor boss | hub part, when a part of the axial direction of the internal peripheral surface is slidably contacted to the said rotor boss | hub part. Drain valve drive device.   The derivative shaft portion has both axial ends of its inner peripheral surface in sliding contact with the rotor boss in the radial direction, and the opposite end portion of the derivative shaft portion on the opening side is the rotor boss portion. The drain valve driving device according to claim 3, wherein the drain valve driving device is rotatably supported by the rotor boss portion by sliding contact in a thrust direction. Clutch means for switching the transmission of the driving force by the first transmission train to a "joining" state or a "disconnecting"state;
A second transmission train that is a gear train that transmits the driving force of the motor to the clutch means;
A pinion part that is a gear part having a radius smaller than the radius of the guide ring part is formed at the opening side end of the derivative shaft part,
The second transmission row has a gear member that meshes with the pinion portion and rotates by rotation of the pinion portion,
The drain valve driving device according to any one of claims 1 to 4, wherein a biasing member that biases the gear member in a direction toward an original position is coupled to the gear member. .

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