JP2019122206A - Geared motor and drain valve drive device - Google Patents

Abstract

To suppress malfunctioning due to the inclusion of foreign matter into a wheel train in a geared motor that drives a drain valve drive member.SOLUTION: In a drain valve drive device 1, the rotation of a motor 40 is transmitted to a lever 10 by way of a transmission wheel train 50 that includes a speed reduction wheel train. A second clutch mechanism 80 switches between states where an acceleration gear 85 locks and does not lock the rotation of a planetary gear mechanism 52, switching between a first state where the lever 10 is driven by the rotation of the motor 40 and a second state where the acceleration gear 85 and a lock gear 84 run on idle allowing the lever 10 to be rotated by an external force. A toothed gear module MA of an acceleration wheel train including the acceleration gear 85 is larger than a toothed gear module MB of a deceleration wheel train consisting the transmission wheel train 50. Therefore, it is possible to suppress the inclusion of foreign matter in the second state where the acceleration wheel train runs on idle, and to suppress the malfunctioning due to foreign matter.SELECTED DRAWING: Figure 10

Description

  The present invention relates to a drainage valve driving device for transmitting the driving force of a motor to a drainage valve, and a geared motor for driving a driven member such as a drainage valve driving member.

  As a drainage valve drive device for moving a drainage valve such as a washing machine by a driving force of a motor, there is one including a drainage valve drive member connected to the drainage valve and a geared motor for driving the drainage valve drive member. In Patent Document 1, a lever is provided as a drain valve drive member, and a geared motor is a drain provided with a transmission wheel train (drive wheel train) using a motor as a drive source and a clutch mechanism (first and second clutch means). A valve drive is disclosed. In Patent Document 1, the transmission gear train transmits the rotation of the rotor to an output gear (output shaft) via a clutch pinion, a planetary gear mechanism, and a reduction gear (reduction gear train). Further, the first clutch means rotates the clutch lever in accordance with the rotational position of the output gear, thereby switching the engagement between the claws of the clutch pinion and the claws of the rotor.

  In Patent Document 1, the second clutch means switches between a state where the rotational torque of the motor is transmitted from the planetary gear mechanism to the reduction gear and a state where it is not transmitted. The second clutch means includes a speed increasing gear (speed increasing gear) meshing with a second rotating body (ring gear) on which the internal gear of the planetary gear mechanism is formed, and a lock gear (clutch gear) meshing with the speed increasing gear. And a fan gear having a lock lever formed to lock the rotation of the lock gear. The fan gear meshes with an induction rotating body that is rotated by magnetic induction with the rotor magnet.

  In Patent Document 1, when the motor is energized at startup, the rotor and the induction rotating body rotate, and the fan gear rotates against the biasing force of the spring. Thus, the lock gear is locked by the lock lever, so that the rotation of the lock gear and the acceleration gear is restricted, and the rotation of the second rotating body of the planetary gear mechanism that meshes with the acceleration gear is restricted. As a result, the planetary gear mechanism is switched to a state in which the rotation of the rotor pinion is transmitted to the reduction gear, so that the rotation of the motor is transmitted to the output gear via the reduction gear, and the drainage valve drive member is driven.

  When the output gear rotates to the predetermined position, in the first clutch means, the claws of the clutch pinion do not engage with the claws of the rotor, and the engagement portion of the clutch pinion engages with the clutch lever to lock the clutch pinion Be done. Therefore, the transmission wheel train is locked, and the drain valve drive member is held in a load holding state so as not to move by an external force.

  When the motor is deenergized in the load holding state, in the second clutch means, the lock lever is retracted from the lock gear by the biasing force of the spring because the induction rotating body is not held by magnetic induction. As a result, the rotation restriction of the lock gear and the acceleration gear is released, and the rotation restriction of the second rotation body of the planetary gear mechanism is also released, so that the lock gear, the acceleration gear, and the second rotation body can idle. . Therefore, even if the rotation of the clutch and pinion is locked, the second rotating body can idle, so that the transmission wheel train can idle the third rotating body of the planetary gear mechanism, the reduction gear, and the output gear. . Therefore, when an external force is applied to the drainage valve driving member, the output gear, the reduction gear, and the third rotating body idle, and the second rotating body, the acceleration gear, and the lock gear also idle to move the drainage valve driving member. It will be in the state that can be

Japanese Patent Application Laid-Open No. 2002-242951

  In Patent Document 1, as described above, when the drainage valve driving member is driven by the driving force of the motor, the clutch and pinion, the planetary gear mechanism (the first rotating body, the third rotating body), the reduction gear, and the output gear The rotation is transmitted in a first path. At this time, in the second clutch means, the rotation of the lock gear and the speed increasing gear is restricted. On the other hand, in a load release state where the drainage valve drive member can be moved by external force, the output gear, the reduction gear, and the planetary gear mechanism (third rotating body, second rotating body) are sequentially reversely to the first path. The rotation is transmitted through the path of (1), and the speed increasing gear and the lock gear rotate idle without transmitting the rotational torque to the motor side.

  In this type of drainage valve drive device, a large rotational torque is applied to the transmission wheel train and the wheel train that constitutes the clutch mechanism, so the gears that constitute these wheel trains are designed to have a small backlash. Therefore, since the gap between the meshing teeth is small, if foreign matter gets in between the gears during the assembly process of the geared motor or transportation of the device after assembly, the foreign matter gets caught in the gap between the gears There is a risk that the train wheel will lock. In particular, foreign matter when the drainage valve driving member is driven by an external force by causing the speed increasing gear train (second clutch means) including the speed increasing gear (second clutch means) to idle as well as the reduction gear train (transmission wheel train) including the reduction gear. It has been confirmed that a gear bite occurs and the gear locks.

  An object of the present invention is, in view of such a point, in a geared motor in which transmission of rotational torque by a transmission gear train provided with a reduction gear train is interrupted by a clutch mechanism provided with a speed increasing gear train. The purpose is to suppress malfunction caused by jamming.

  In order to solve the above problems, according to the geared motor of the present invention, a transmission wheel train including a motor, an output gear to which a driven member is connected, and the transmission wheel train transmit the rotation of the motor to the driven member. And a clutch mechanism for switching between the second state in which the transmission wheel train does not transmit the rotation of the motor to the driven member, and the transmission wheel train includes a reduction wheel train, The clutch mechanism includes a speed increasing wheel train meshing with one of the gears constituting the transmission gear train, and a module of the gear wheels constituting the speed increasing gear train is larger than a module of the gear wheels constituting the reduction gear train. It is characterized by

  The present invention thus provides a geared motor in which the transmission gear train including the output gear includes a reduction gear train, and the clutch mechanism includes a speed increasing gear train meshing with the gears of the transmission gear train. The module of the gear (speed increasing wheel train) is made larger than the module of the gear (speed reducing wheel train) of the transmission wheel train. As a result, in the speed increasing wheel train in which the foreign matter bites in, the gap between the teeth can be expanded, and a space through which the foreign matter passes can be secured. Therefore, it is possible to reduce the biting of the foreign matter, and to reduce the possibility that the foreign matter bites and the train wheel is locked. Therefore, the operation failure due to the biting of the foreign matter can be suppressed.

  In the present invention, it is preferable that the gear constituting the speed-increasing wheel train has a top coefficient of greater than 0.25. In this way, a gap (crest) between the tooth top and the tooth bottom can be secured, so that the possibility of the foreign matter biting and locking the wheel train can be reduced.

  In the present invention, it is preferable that the speed increasing gear train and the speed reducing gear train be constituted by standard spur gears. In this way, it is possible to widen the gap between the teeth by changing the module, and it is possible to secure a space through which foreign matter passes. Therefore, it is possible to reduce the possibility that foreign matter bites and the train wheel is locked.

In the present invention, the first state is a state in which the rotation of the speed increasing gear train is restricted, and the reduction gear train is rotated based on the rotation of the motor, and the second state is the state It is preferable that the reduction gear train and the speed increasing gear train be idle. Thus, in the first state, the driven member can be moved by the driving force of the motor. In the second state, the reduction gear wheel train and the speed increasing wheel train can be idled to move the driven member by an external force. Therefore, in the operation of moving the driven member by the external force, it is possible to reduce the possibility that the foreign matter bites and the wheel train is locked.

  In the present invention, the transmission gear train includes a planetary gear mechanism, and the planetary gear mechanism includes a planetary gear, a first rotating body having a sun gear meshing with the planetary gear, and an internal gear meshing with the planetary gear. A second rotating body and a third rotating body for supporting the planetary gear, the speed increasing wheel train comprising a speed increasing gear meshing with the second rotation body, and a lock gear meshing with the speed increasing gear Preferably, the reduction gear train includes a reduction gear meshing with the output gear, and a module of the acceleration gear is larger than a module of the reduction gear. Thus, the tooth-to-tooth gap can be expanded between the speed increasing gear and the lock gear, and between the speed increasing gear and the planetary gear mechanism, and a space through which foreign matter can pass can be secured. Therefore, it is possible to reduce the possibility that foreign matter bites into the speed increasing wheel train and is locked.

  In order to solve the above-mentioned subject, the drainage valve drive of the present invention is characterized by having the above-mentioned geared motor and the drainage valve drive member driven based on rotation of the above-mentioned output gear. As a result, it is possible to reduce the possibility that the gears of the geared motor are locked due to the biting of foreign matter. Therefore, the malfunction of the drainage valve drive device can be suppressed.

  According to the present invention, the transmission gear train including the output gear includes the reduction gear train, and the clutch mechanism is a geared motor including the speed increasing gear train meshing with the gear of the transmission gear train. The module of the speed increasing gear train) is made larger than the module of the transmission wheel gear (reduction gear train). As a result, in the speed increasing wheel train in which the foreign matter bites in, the gap between the teeth can be expanded, and a space through which the foreign matter passes can be secured. Therefore, it is possible to reduce the biting of the foreign matter, and to reduce the possibility that the foreign matter bites and the train wheel is locked. Therefore, the operation failure due to the biting of the foreign matter can be suppressed.

It is a perspective view of a drainage valve drive provided with a geared motor to which the present invention is applied. It is a disassembled perspective view of the drainage valve drive device of FIG. It is a top view of the geared motor which removed the 2nd case. FIG. 5 is a developed wheel train diagram showing a cross section connecting the axes of the gears of the gear unit. It is the disassembled perspective view which looked at the motor and the gear unit from the + Z direction side. It is the disassembled perspective view which looked at the gear unit from the-Z direction side. FIG. 5 is a developed wheel train of the second clutch mechanism and a planetary gear mechanism. It is explanatory drawing of the meshing part of a speed-up gear and a lock gear. It is explanatory drawing of the meshing part of a speed-up gear and a planetary gear mechanism. It is a clearance list of the meshing part in a step-up wheel train, and a list of modules.

(overall structure)
Hereinafter, a geared motor 2 and a drainage valve driving device 1 according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a perspective view of a drainage valve drive device 1 including a geared motor 2 to which the present invention is applied, and FIG. 2 is an exploded perspective view of the drainage valve drive device 1 of FIG. The drainage valve drive device 1 includes a lever 10 which is a drainage valve driving member for driving a drainage valve (not shown), and a geared motor 2 which rotates the lever 10 to open and close the drainage valve. The lever 10 rotates about a rotation axis L extending in the Z direction. In this specification, one side in the Z direction is + Z direction, and the other side is -Z direction. Further, the CW direction and the CCW direction are the CW direction and the CCW direction when the drainage valve drive device 1 is viewed from the + Z direction side.

  The geared motor 2 includes a case 20 and a gear unit 3 and a motor 40 housed in the case 20. The rotation of the motor 40 is transmitted to the lever 10 via the gear unit 3. The case 20 includes a first case 21 and a second case 22. The motor 40 is accommodated at the bottom of the first case 21. The gear unit 3 is disposed on one side (+ Z direction) of the motor 40 in the Z direction, and the second case 22 is assembled to the first case 21 so as to cover the gear unit 3.

  The lever 10 is attached to a serration portion 13 provided at an end of the output gear 54 in the + Z direction, and rotates integrally with the output gear 54. The serration portion 13 is disposed in an opening 23 (see FIG. 4) formed in the second case 22. The lever 10 includes an arm 11 extending radially outward around the rotation axis L, and a drainage valve connection 12 provided at the tip of the arm 11. When the lever 10 is positioned at the first rotational position (closed position), the drainage port is closed by the drainage valve connected to the drainage valve coupling portion 12 via a wire or the like (not shown). When the lever 10 moves to a second rotational position (open position) different from the first rotational position, the drainage valve separates from the drainage port and drainage is started.

  The drainage valve drive device 1 holds the lever 10 by continuing energization of the motor 40 as a drive source in a state where the lever 10 is positioned at the second rotational position (open position). Further, when the drainage valve drive device 1 stops the energization of the motor 40 and releases the holding state of the lever 10, the lever 10 can be returned to the first rotational position (closed position) by an external force. For example, the lever 10 is returned to the first rotational position by an urging force such as a spring force connected to the valve body of the drainage valve, and the drainage port is closed by the drainage valve.

  FIG. 3 is a plan view of the geared motor 2 with the second case 22 removed. FIG. 4 is a developed wheel train diagram showing a cross section connecting the axes of the gears of the gear unit 3. In FIG. 3 and FIG. 4, the axes (rotation center axes) of the gears of the gear unit 3 are indicated by symbols C, D, E, F, G, H and O. These axes point in the Z direction. The gear unit 3 includes a transmission gear train 50 for transmitting the rotation of the motor 40 to the lever 10, a first clutch mechanism 60 for switching transmission and reception of rotational torque from the motor 40 to the transmission gear train 50, and external load on the lever 10. Rotation regulation mechanism 70 which regulates the rotation of transmission wheel train 50 and holds lever 10 when a torque is added, and second clutch mechanism 80 which switches between a state where transmission wheel train 50 transmits rotational torque and a state where transmission torque is not transmitted. Prepare.

(motor)
FIG. 5 is an exploded perspective view of the motor 40 and the gear unit 3 as viewed from the + Z direction side. The motor 40 is an AC synchronous motor. As shown in FIGS. 4 and 5, the motor 40 includes a cup-shaped motor case 41, a support plate 42 attached to the end of the motor case 41 on the + Z direction side, and a bobbin disposed inside the motor case 41. 43, a stator coil 44 wound around the bobbin 43, and a rotor 45 disposed on the inner peripheral side of the bobbin 43. The rotor 45 is disposed in a central hole that opens at the center of the support plate 42.

The motor case 41 and the support plate 42 are made of a magnetic plate. The support plate 42 is formed with pole teeth bent and extended in the -Z direction from the edge of the central hole in which the rotor 45 is disposed. Further, in the motor case 41, pole teeth are formed by cutting and raising the bottom of the motor case 41 and bending it in the + Z direction. The pole teeth provided on the support plate 42 and the pole teeth cut and raised from the motor case 41 are alternately arranged in the circumferential direction and radially opposed to the outer circumferential surface of the magnet 451. That is, the motor case 41 and the support plate 42 also serve as a stator core. Further, in the support plate 42, the end portion in the -Z direction of the fixed shaft that rotatably supports the plurality of gears that constitute the transmission wheel train 50 is press-fitted. The end in the + Z direction of the fixed shaft is fixed to a recess provided in the second case 22 by press fitting or the like.

  As shown in FIG. 4, the rotor 45 includes a substantially cylindrical magnet 451 and a shaft 452 disposed on the inner peripheral side of the magnet 451. The rotor 45 is rotatably supported by a fixed shaft 453. The rotation center axis of the rotor 45 is an O-axis, and the fixed axis 453 extends in the Z direction about the O-axis. The rotor 45 is formed by insert molding a magnet 451 made of a ferrite magnet or the like on the end of the shaft 452 in the -Z direction.

  An induction rotating body 46 is disposed between the magnet 451 and the shaft 452. The induction rotating body 46 is obtained by insert molding an induction ring 461 made of nonmagnetic metal such as aluminum or copper on a shaft portion which is a resin member. When the motor 40 is energized and the rotor 45 rotates, an eddy current is generated between the magnet 451 and the induction ring 461, and a magnetic flux is generated due to the eddy current, and a braking force is generated that hinders the relative rotation of the induction rotor 46 with respect to the magnet 451. Do. The induction rotating body 46 and the rotor 45 are coupled to rotate together by this braking force (braking force due to eddy current). As shown in FIG. 5, the upper end portion of the induction rotating body 46 protrudes in the + Z direction side of the magnet 451, and the rotor gear 47 is formed on the outer peripheral surface of this protruding portion. The rotor gear 47 is a gear that transmits the rotation of the rotor 45 to the second clutch mechanism 80.

(Transmission wheel train)
FIG. 6 is an exploded perspective view of the gear unit 3 as viewed from the -Z direction side. As shown in FIGS. 3 to 6, the transmission gear train 50 includes a rotor pinion 51, a planetary gear mechanism 52, a reduction gear 53, and an output gear 54. The rotation center axis of the rotor pinion 51 is the O axis, the rotation center axis of the planetary gear mechanism 52 is the E axis, the rotation center axis of the reduction gear 53 is the D axis, and the rotation center axis of the output gear 54 is the C axis It is. The transmission wheel train 50 transmits the driving force of the motor 40 to the lever 10 in this order.

  The rotor pinion 51 is formed of resin, and is rotatably supported by the fixed shaft 453 of the rotor 45 and movable in the axial direction (that is, in the Z direction). A first clutch mechanism 60 is provided between the rotor pinion 51 and the rotor 45. The state in which the rotor pinion 51 rotates integrally with the rotor 45 by switching the connection state of the first clutch mechanism 60 (clutch connection state), and the state in which the rotor pinion 51 does not rotate integrally with the rotor 45 (clutch disconnection state) Can be switched to

  As shown in FIGS. 4 to 6, the planetary gear mechanism 52 includes a first rotating body 522 having a sun gear 521 formed thereon, a second rotating body 524 having an internal gear 523 formed thereon, a sun gear 521, and the like. A plurality of planetary gears 525 meshing with the tooth gear 523 and a third rotating body 526 rotatably holding the plurality of planetary gears 525 are provided. The first rotating body 522 includes a large diameter gear portion 527 that meshes with the rotor pinion 51. That is, the large diameter gear portion 527 is an input gear to which the rotation of the rotor pinion 51 is input. A large diameter gear portion 528 engaged with the speed increasing gear 85 of the second clutch mechanism 80 is formed on the outer peripheral surface of the second rotating body 524.

Since the rotation of the speed increasing gear 85 of the second clutch mechanism 80 is restricted at the time of activation of the drain valve drive device 1, the rotation of the second rotary body 524 is restricted by the speed increasing gear 85. As a result, based on the rotation of the first rotating body 522 on which the sun gear 521 is formed, the third rotating body 526 which is a planet carrier is rotated. A small diameter gear portion 529 engaged with the large diameter gear portion 531 of the reduction gear 53 is formed at an end portion of the third rotating body 526 in the −Z direction. Therefore, the rotation of the rotor pinion 51 is transmitted from the planetary gear mechanism 52 to the reduction gear 53, and the rotational torque of the motor 40 is transmitted to the reduction gear 53. When the lever 10 is rotated by an external force, the second clutch mechanism 80 is switched from the state in which the rotation of the speed increasing gear 85 is restricted to the state in which the speed increasing gear 85 idles. As a result, in the planetary gear mechanism 52, even if the planetary gear 525 tries to revolve, the second rotating member 524 on which the internal gear 523 is formed idles, so that the third rotating member 526, which is a planetary carrier, does not rotate. Absent. Therefore, in the transmission gear train 50, the rotational torque of the motor 40 is not transmitted to the reduction gear 53.

  In the transmission gear train 50, in the planetary gear mechanism 52, the large diameter gear portion 527 having a larger diameter than the rotor pinion 51 meshes with the rotor pinion 51, whereby the rotation of the rotor 45 is decelerated and input to the planetary gear mechanism 52. Ru. Then, the rotation is further decelerated in the planetary gear mechanism 52 and input to the reduction gear 53. The reduction gear 53 is a compound gear including a large diameter gear portion 531 meshing with the small diameter gear portion 529 of the planetary gear mechanism 52 and a small diameter gear portion 532 meshing with the output gear 54. Therefore, the rotation is further decelerated in the reduction gear 53 and transmitted to the output gear 54. Therefore, the transmission gear train 50 constitutes a reduction gear train.

(First clutch mechanism)
As shown in FIGS. 5 and 6, the first clutch mechanism 60 includes a first clutch claw 61 formed on the end surface of the rotor pinion 51 in the −Z direction and a second clutch formed on the shaft 452 of the rotor 45. The claw 62, a coil spring 63 (see FIG. 4) for urging the rotor pinion 51 in a direction away from the shaft 452 (in the present embodiment, + Z direction), and the rotor pinion 51 toward the rotor 45 (−Z direction) A fan-shaped clutch switching lever 64 for switching the first clutch mechanism 60 is provided. The clutch switching lever 64 is disposed on the + Z direction side of the reduction gear 53, and is rotatably supported by a fixed shaft 533 that rotatably supports the reduction gear 53.

  The clutch switching lever 64 is formed with a cam pin 65 and an inclined cam 67 which project in the −Z direction. The cam pin 65 is formed on the edge of the clutch switching lever 64 on the output gear 54 side, and is inserted into a cam groove 66 formed on the end surface of the output gear 54 in the + Z direction. The inclined cam 67 is formed along the edge of the arc groove 68 passing through the clutch switching lever 64. The inclined cam 67 is a cam portion for moving the rotor pinion 51 in the -Z direction, and extends in the circumferential direction on the inclined surface 671 extending in the circumferential direction and the planetary gear mechanism 52 side (CCW direction) of the inclined surface 671 A cam surface 672 is provided. The cam surface 672 is a horizontal surface perpendicular to the rotational axis direction (Z direction) of the clutch switching lever 64.

  The fixed shaft 453 of the rotor 45 is inserted into the arc groove 68 of the clutch switching lever 64. When the clutch switching lever 64 rotates about the fixed shaft 533, the fixed shaft 453 moves in the circumferential direction in the arc groove 68. As shown in FIG. 6, the inclined cam 67 is formed on the end of the arc groove 68 on the planetary gear mechanism 52 side (CCW direction). Further, at an end of the arc groove 68 on the output gear 54 side (CW direction), a lock protrusion 69 projecting in the −Z direction is formed. As described later, the lock projection 69 constitutes a rotation restricting mechanism 70 for indirectly locking the planetary gear mechanism 52 by restricting the rotation of the rotor pinion 51.

  When the clutch switching lever 64 rotates toward the output gear 54, the fixed shaft 453 and the rotor pinion 51 attached to the fixed shaft 453 move relative to the cam surface 672 along the arc groove 68. At that time, the rotor pinion 51 is pushed down to the shaft 452 side (−Z direction side) by the inclined surface 671 of the inclined cam 67. Thereby, the first clutch claw 61 and the second clutch claw 62 are engaged, and the first clutch mechanism 60 is switched to the clutch connected state in which the rotor pinion 51 integrally rotates with the shaft portion 452. On the other hand, when the clutch switching lever 64 rotates to the planetary gear mechanism 52 side, the inclined cam 67 retracts from the position overlapping the rotor pinion 51, so the rotor pinion 51 is pushed up in the + Z direction by the biasing force of the coil spring 63. As a result, the engagement between the first clutch claw 61 and the second clutch claw 62 is released, and the first clutch mechanism 60 is switched to the clutch disengaged state.

  The clutch switching lever 64 rotates in conjunction with the rotation of the output gear 54. That is, the clutch switching lever 64 rotates to the output gear 54 side in conjunction with the rotation of the output gear 54 in the CW direction via the cam pin 65 and the cam groove 66. Thereby, the clutch connection operation is performed. Further, when the output gear 54 rotates in the CCW direction, the projection 55 protruding from the output gear 54 in the + Z direction presses the clutch switching lever 64 to rotate it toward the planetary gear mechanism 52 side. Thereby, the clutch disengagement operation is started.

  The drainage valve driving device 1 rotates the output gear 54 in the CCW direction to start drainage, but the position of the projection 55 of the output gear 54 presses the clutch switching lever 64 when the output gear 54 reaches a predetermined rotational position. It is set to rotate to the planetary gear mechanism 52 side. Therefore, when the lever 10 moves to the above-described second rotational position (open position), the above-described clutch disengagement operation is performed. As a result, the driving force of the motor 40 is not transmitted to the rotor pinion 51, and the operation of the transmission wheel train 50 is stopped. Thus, the lever 10 can be prevented from rotating beyond the second rotational position, and excessive rotation of the lever 10 can be prevented.

(2nd clutch mechanism)
The second clutch mechanism 80 includes a rotor gear 47 formed on an induction rotating body 46 that rotates together with the rotor 45 when the rotor 45 rotates, a rotating member 81 formed with a fan gear 82 meshing with the rotor gear 47 and a lock lever 83; A lock gear 84, an acceleration gear 85, and a torsion coil spring 86 are provided. The second clutch mechanism 80 drives the lock lever 83 by the driving force of the motor 40 and the biasing force of the torsion coil spring 86 to switch between the state in which the rotation of the lock gear 84 and the speed increasing gear 85 is restricted. Thus, as described above, it is possible to switch between the state in which the transmission wheel train 50 transmits the driving force and the state in which the transmission wheel train 50 does not transmit the driving force.

  FIG. 7 is a developed wheel train of the second clutch mechanism 80 and the planetary gear mechanism 52, and is a partially enlarged view of a range of E axis, F axis, G axis, and H axis in FIG. As shown in FIGS. 3, 4 and 7, the rotation center axis of the rotating member 81 is the H axis, the rotation center axis of the lock gear 84 is the G axis, and the rotation center axis of the speed increasing gear 85 is the F axis It is. When the rotor 45 rotates in the forward rotation direction (CW direction), the rotation of the rotor 45 is input to the fan gear 82 meshing with the rotor gear 47. The fan gear 82 rotates in the direction opposite to the rotation direction of the rotor 45 (CCW direction). As shown in FIGS. 3 and 5, the fan gear 82 is biased in the same direction (CW direction) as the rotation direction of the rotor 45 by the torsion coil spring 86 which is a biasing member. Therefore, the fan gear 82 rotates in the CCW direction against the biasing force of the torsion coil spring 86.

  The lock lever 83 rotates in the same direction (CCW direction) as the fan gear 82. As shown in FIGS. 6 and 7, the lock gear 84 has a large diameter portion 842 in which a plurality of projections 841 are formed at equal angular intervals on the outer peripheral surface, and a small diameter gear portion 843 smaller than the large diameter portion 842. Prepare. When the fan gear 82 rotates in the CCW direction, the lock lever 83 rotates in the CCW direction and contacts the outer peripheral surface of the large diameter portion 842 of the lock gear 84. As a result, the lock lever 83 and the projection 841 are engaged, and the rotation of the lock gear 84 is restricted. At the time of rotation restriction, the tip end of the lock lever 83 and the projection 841 abut in a tangential direction of the outer peripheral surface of the lock gear 84.

  The second clutch mechanism 80 regulates the rotation of the speed increasing gear 85 by forming a locked state in which the lock lever 83 regulates the rotation of the lock gear 84. As shown in FIGS. 5 and 7, the speed increasing gear 85 is a compound gear including a large diameter gear portion 851 and a small diameter gear portion 852. The large diameter gear portion 851 meshes with the small diameter gear portion 843 of the lock gear 84, and the small diameter gear portion 852 meshes with the large diameter gear portion 528 formed on the second rotating body 524. Therefore, the rotation of the second rotating body 524 is restricted via the speed increasing gear 85. Thus, the transmission gear train 50 is switched to a state in which the driving force of the motor 40 is transmitted to the output gear 54.

  Further, in the second clutch mechanism 80, when the lock lever 83 engages with the projection 841 of the lock gear 84, the rotation of the lock lever 83 and the fan gear 82 is restricted, and the second clutch mechanism 80 is guided by the rotor gear 47 meshing with the fan gear 82. The rotation of the rotating body 46 is restricted. As a result, the relative rotational speed of the rotor 45 and the induction rotating body 46 is increased. The second clutch mechanism 80 has a rotational force when a rotational force is applied to the lock gear 84 from the speed increasing gear 85 side by an external force or the like by the braking force by the eddy current generated between the induction rotating body 46 and the magnet 451. Thus, the lock gear 84 and the lock lever 83 are held so as not to be disengaged. Therefore, it is possible to hold the locked state for restricting the rotation of the lock lever 83.

  In the second clutch mechanism 80, when energization of the motor 40 is stopped in a state where the lock gear 84 is locked by the lock lever 83, the lock state of the lock gear 84 is released and switched to a state in which idling can be performed. That is, when the rotation of the rotor 45 is stopped, the braking force acting between the induction rotating body 46 and the magnet 451 disappears. Therefore, the rotor gear 47 can not hold the fan gear 82 against the biasing force of the torsion coil spring 86, and the fan gear 82 rotates in the biasing direction by the torsion coil spring 86. Since the lock lever 83 is separated from the lock gear 84 by the rotation of the fan gear 82, the lock gear 84 is unlocked. Thereby, the second clutch mechanism 80 switches to a state in which the lock gear 84 and the speed increasing gear 85 can idle.

  When the speed increasing gear 85 of the second clutch mechanism 80 is switched to the idleable state, in the transmission wheel train 50, as described above, the second rotation is performed with the rotation of the third rotating body 526 engaged with the speed reducing gear 53. The body 524 idles, and the rotational torque of the motor 40 is not transmitted to the reduction gear 53. Further, at this time, the speed increasing gear 85 and the lock gear 84 idle. Accordingly, the external load applied to the lever 10 is not transmitted to the motor 40 side due to the idle rotation of the planetary gear mechanism 52, the acceleration gear 85, and the lock gear 84.

  In the second clutch mechanism 80, when the speed increasing gear 85 and the lock gear 84 idle, the input portion of the speed increasing gear 85 meshing with the second rotating body 524 of the planetary gear mechanism 52 is a large diameter gear of the second rotating body 524 The small diameter gear portion 852 has a smaller number of teeth than the portion 528, and the output portion meshing with the lock gear 84 is a large diameter gear portion 851 having a larger number of teeth than the small diameter gear portion 843 of the lock gear 84. Therefore, the second clutch mechanism 80 constitutes a speed increasing wheel train whose rotation is accelerated between the second rotating body 524 and the speed increasing gear 85 and between the speed increasing gear 85 and the lock gear 84. .

(Rotation restriction mechanism)
As shown in FIG. 5, the rotor pinion 51 has a diameter from the outer peripheral surface of the gear portion 511 having teeth formed on the outer peripheral surface, a shaft portion 512 projecting from the end surface of the gear portion 511 in the + Z direction, The locking projections 71 are provided to protrude outward in the direction. The rotation restricting mechanism 70 restricts the rotation of the rotor pinion 51 by engaging the lock projection 69 formed at the end of the arc groove 68 of the clutch switching lever 64 in the CW direction with the locked projection 71. The rotor pinion 51 meshes with the large diameter gear portion 527 of the first rotating body 522. Therefore, the rotation restricting mechanism 70 indirectly restricts the rotation of the first rotating body 522.

When the output gear 54 rotates until the lever 10 moves to the second rotational position (open position), the drain valve drive device 1 moves the clutch switching lever 64 toward the planetary gear mechanism 52 by the projection 55 of the output gear 54. Press. As a result, the clutch disconnecting operation is performed, and the lock projection 69 and the locked projection 71 are engaged, and the rotation of the rotor pinion 51 and the first rotating body 522 is restricted. Here, since the planetary gear mechanism 52 restricts the rotation of the second rotating body 524 by the second clutch mechanism 80 by the second clutch mechanism 80 when the drainage valve drive device 1 is activated, the rotation restriction mechanism 70 When the rotation of the one rotation body 522 is restricted, the rotation of the third rotation body 526 meshing with the reduction gear 53 is also restricted, and the lock state is established. Therefore, even if external force is applied to the lever 10 and rotational torque is applied to the transmission gear train 50 from the output gear 54 side, the rotational torque is not transmitted, and a load holding state for holding the lever 10 at the second rotational position is formed. Be done.

  When the motor 40 is deenergized in the load holding state, as described above, the second clutch mechanism 80 no longer restricts the rotation of the second rotating body 524, so that the locked state of the planetary gear mechanism 52 is released. That is, even if the rotation of the first rotary body 522 is restricted, the second rotary body 524 and the third rotary body 526 are in a load open state where the second rotary body 524 and the third rotary body 526 can idle due to the rotation of the reduction gear 53.

  In the rotation restricting mechanism 70, when the lever 10 is rotated by switching the lever 10 to a rotatable load released state by an external force, the clutch switching lever 64 is directed to the output gear 54 side (CW direction) as the output gear 54 rotates. When rotated, the locked projection 71 separates from the locking projection 69. Thereby, the rotation restriction of the rotor pinion 51 and the first rotating body 522 by the rotation restriction mechanism 70 is released. At this time, since the rotor pinion 51 is pushed down by the inclined cam 67, the clutch connecting operation of the first clutch mechanism 60 is performed.

(Operation of drain valve drive: Operation at start up)
Hereinafter, the operation of the drainage valve drive device 1 will be described. At start-up, it is assumed that the lever 10 is rotated to a position (first rotational position) at which the drain valve is closed. When energization of the motor 40 is started in this state, the rotor 45 starts to rotate. At this time, since the rotation of the rotor 45 in the reverse direction is restricted by the reverse rotation preventing mechanism (not shown), the rotor 45 rotates in the normal direction.

  Next, the second clutch mechanism 80 switches to the state of locking the lock gear 84 by the rotation of the rotor 45 in the normal direction. First, due to the rotation of the rotor 45, the fan gear 82 meshing with the rotor gear 47 rotates against the biasing force of the torsion coil spring 86, and the lock lever 83 abuts on the lock gear 84 and engages with the projection 841. Lock 84 Thereby, the transmission wheel train 50 is switched to the state of transmitting the rotational torque. That is, in the transmission gear train 50, the rotation of the second rotating body 524 of the planetary gear mechanism 52 is restricted by the acceleration gear 85 of the second clutch mechanism 80, and the rotation of the rotor pinion 51 is reduced from the planetary gear mechanism 52 to the reduction gear 53. Switch to the state of being transmitted to Accordingly, the rotation of the rotor 45 in the forward direction rotates the lever 10 in the direction to open the drain valve.

(Operation when forming a load holding state)
In the drain valve drive device 1, when the lever 10 is rotated to the second rotation position, the clutch switching lever 64 of the first clutch mechanism 60 is rotated to perform the clutch disconnection operation, and the transmission wheel train 50 rotates the rotor 45. It will not be input. Thus, the lever 10 does not rotate beyond the second rotational position. Further, since the lock projection 69 of the rotation restricting mechanism 70 engages with the locked projection 71 of the rotor pinion 51 by the rotation of the clutch switching lever 64, the rotation of the first rotating body 522 of the planetary gear mechanism 52 meshed with the rotor pinion 51 Is regulated. Therefore, the planetary gear mechanism 52 is in a locked state in which the rotations of the first rotating body 522 and the second rotating body 524 are restricted, and the transmission wheel train 50 can not transmit the rotational torque. As a result, even when an external force to rotate the lever 10 is applied, the lever 10 does not rotate so as to hold the load. Thereby, the drainage valve is held open.

(Operation at the time of load release)
The drainage valve drive device 1 shifts to a load open state where the lever 10 can be rotated by an external force when the motor 40 is deenergized in a load holding state. That is, when the motor 40 is deenergized, the rotation of the rotor 45 is stopped. Since the second clutch mechanism 80 loses the magnetic induction force causing the rotor 45 and the induction rotating body 46 to rotate together by stopping the rotation of the rotor 45, the fan gear 82 meshing with the rotor gear 47 has an urging direction of the torsion coil spring 86. Return to As a result, the engagement between the lock lever 83 and the lock gear 84 is released, and the rotation restriction of the lock gear 84 and the speed increasing gear 85 is released. Thereby, the transmission gear train 50 is switched to a state in which the rotational torque is not transmitted. That is, since the rotation restriction of the second rotating body 524 is released in the planetary gear mechanism 52 of the transmission wheel train 50, the lock of the planetary gear mechanism 52 is released. As a result, a load release state in which the transmission wheel train 50 can idle can be obtained. In this state, when an external force to rotate the lever 10 is applied, the transmission wheel train 50 idles and the lever 10 rotates. At this time, the speed increasing gear 85 and the lock gear 84 meshing with the second rotating body 524 of the planetary gear mechanism 52 also idle.

  In the present embodiment, the brake rubber 87 is incorporated in the lock gear 84. When the lever 10 is rotated by an external force, the brake rubber 87 is expanded by centrifugal force to generate a frictional force with the lock gear 84. Thereby, the rotational speed at the time of rotating the lever 10 falls. Therefore, the possibility of breakage due to the lever 10 rapidly rotating due to the external force can be reduced.

  When the lever 10 is rotated to a predetermined position before reaching the maximum rotation position, the clutch connection operation is started based on the rotation of the output gear 54 in the CW direction. That is, the clutch switching lever 64 is rotated to the output gear 54 side by the cam groove 66 formed in the output gear 54 and the cam pin 65 provided on the clutch switching lever 64 to perform the clutch connecting operation. As a result, the rotation of the rotor 45 is input to the transmission wheel train 50 and returns to the state. Further, the rotation of the clutch switching lever 64 releases the lock of the first rotating body 522 of the planetary gear mechanism 52 by the rotation restricting mechanism 70. Therefore, the transmission wheel train 50 returns to the state capable of transmitting the rotational torque.

(Gear shape)
In the first state in which the lever 10 is rotated by the driving force of the motor 40 in the drainage valve drive device 1, the transmission gear train 50 transmits the rotation in the first path. That is, in the first state, the transmission gear train 50 includes the rotor pinion 51, the planetary gear mechanism 52 (the first rotating body 522 and the third rotating body 526), the reduction gear 53, and the output gear 54 in this order of the motor 40. Transmit the rotation by decelerating. Further, in the first state, the rotation of the lock gear 84 and the speed increasing gear 85 of the second clutch mechanism 80 is restricted, and only the transmission gear train 50 (reduction gear train) is rotated.

  On the other hand, in the second state (load release state) where the lever 10 can be rotated by an external force, the transmission wheel train 50 and the second clutch mechanism 80 transmit the rotation through the second path. That is, in the second state, the output gear 54, the reduction gear 53, and the planetary gear mechanism 52 (third rotating body 526) transmit rotation in a direction reverse to that by the motor 40 by external force applied to the lever 10. . Further, at this time, since the first rotating body 522 of the planetary gear mechanism 52 is locked and rotational torque is not transmitted to the motor 40 side, the second rotating body 524 is idled, and the second clutch mechanism 80 is The speed increasing gear 85 meshing with the second rotating body 524 and the lock gear 84 idle. That is, in the second state, the transmission gear train 50 (deceleration gear train) idles, and the speed increasing gear train formed by the second rotating body 524, the acceleration gear 85, and the lock gear 84 idles.

In this embodiment, in order to reduce the possibility of the gears constituting the gear unit 3 being locked due to the biting of foreign matter, the gears of the speed increasing gear train configured by the second rotating body 524, the speed increasing gear 85 and the lock gear 84. Of the gear of the reduction gear train formed by the third rotating body 526, the reduction gear 53, and the output gear 54 as MB, the gear unit 3 so that the condition of MA> MB is satisfied. Configure In the gear unit 3, the gears forming the speed increasing wheel train and the speed reducing wheel train are all standard spur gears. Further, in the present specification, the definition of the module M of the gear is a value (M = d / n) obtained by dividing the pitch circle diameter d of the gear by the number of teeth n.

  The reason why the configuration satisfying the condition of MA> MB is adopted is the drainage valve drive device 1 having the reduction gear train (transmission gear train 50) and the speed increasing gear train (the second clutch mechanism 80) as in this embodiment: The second state in which the lever 10 is rotated by an external force from the first state in which the lever 10 is rotated by the driving force of the motor 40 when the module of the gears in the reduction gear train and the speed increasing gear train are equal to each other In the open state, a large amount of foreign matter bites have occurred. That is, a large amount of foreign matter biting occurs when the speed increasing wheel train is rotating. Therefore, in the present embodiment, a structure is adopted in which the biting of the foreign matter in the gear unit 3 in the drainage valve driving device 1 is suppressed by suppressing the biting of the foreign matter in the speed increasing wheel train. Therefore, the module MB of the gear of the reduction gear train is not changed, and the module MA of the gear of the speed increasing gear train is made larger than the module MB of the gear of the reduction gear train.

(Example)
8, 9, and 10 are diagrams for explaining an example according to the present embodiment. 8 and 9 are explanatory views of the meshing portion of the gear in the speed increasing wheel train. FIG. 8 is an explanatory view of the meshing portion between the speed increasing gear 85 and the lock gear 84, where the large diameter gear portion 851 of the speed increasing gear 85 meshes with the small diameter gear portion 843 of the lock gear 84 (FIG. 7). It is explanatory drawing which looked at area | region B1 of 1 from the axial direction. FIG. 9 is an explanatory view of the meshing portion between the speed increasing gear 85 and the planetary gear mechanism 52 (second rotating body 524), and the small diameter gear portion 852 of the speed increasing gear 85 and the large diameter of the second rotating body 524 are shown. It is explanatory drawing which looked at the location (area | region B2 of FIG. 7) which the gear part 528 is meshing from the axial direction. In FIGS. 8 and 9, (a) shows the shape of the conventional product, and (b) shows the shape adopted in this embodiment. As is apparent from FIGS. 8 and 9, in the embodiment, in the meshing portion of the speed increasing wheel train, the gap between one tooth tip of the meshing teeth and the other tooth bottom is larger than that of the conventional product. Regarding the dimension of the gap between the tooth top and the tooth bottom, the circumferential clearance C1 is larger than the radial clearance C2.

  FIG. 10 is a list showing the clearance C1 in the circumferential direction of the meshing portion, the clearance C2 in the radial direction, and the module MA for each of the prior art and the speed increasing wheel train of the embodiment shown in FIG. 8 and FIG. It is. In the meshing portion between the speed increasing gear 85 and the lock gear 84 shown in FIG. 8, the gear module MA is 1.8 times or more as large as that of the conventional module M1. Further, in the meshing portion between the speed increasing gear 85 and the planetary gear mechanism 52 (the second rotating body 524) shown in FIG. 9, the module MA of the gear is 1.6 times or more the module M2 of the conventional product.

  As a result of adopting such a module MA, the clearance C1 in the circumferential direction and the clearance C2 in the radial direction are as shown in FIG. First, with respect to the meshing portion between the speed increasing gear 85 and the lock gear 84 shown in FIG. 8, the circumferential clearance C1 which was C1a in the conventional product is enlarged to twice or more (C1 ≧ 2C1a). Further, the clearance C2 in the radial direction, which was C2a in the conventional product, was enlarged to 2.3 times or more (C2 ≧ 2.3 C2a). And about the meshing part of the acceleration gear 85 and the planetary gear mechanism 52 (2nd rotary body 524) shown in FIG. 9, the clearance C1 of the circumferential direction which was C1b in the conventional product is twice or more (C1.gtoreq.2C1b) Expanded to Further, the clearance C2 in the radial direction, which was C2b in the conventional product, was expanded to 2.6 times or more (C2 ≧ 2.6C2b). Thus, as a result of making the gear module MA 1.6 times or more of that of the conventional product, the clearance C2 in the radial direction between the tooth tip and the tooth bottom is at least 2.3 times or more than that of the conventional product. The The circumferential clearance C1 was larger than the radial clearance C1.

In the gear unit 3 of the embodiment, the thickness in the axial direction of each gear is larger than the clearance C1 in the circumferential direction and the clearance C2 in the radial direction. Therefore, since the height in the axial direction of the gap between the tooth top and the tooth bottom is sufficiently secured, there is a structure that there is little risk of catching foreign matter in the axial direction.

  Here, the dimension shown as "radial clearance C2" in FIG. 8 to FIG. 10 is the radial distance from one tip circle of the meshing gear to the other tooth bottom circle (common to teeth and tooth spaces) Means the distance on the center line).

  In adopting the gear shape of the present embodiment shown in FIGS. 8 to 10 as a speed increasing wheel train, the influence of the shape change was verified. As verification items, the rotational torque of the lever 10 and the return time of the lever 10 were verified as initial performance. In addition, as endurance performance, verification of continuous operation of 50,000 times and 100,000 times was conducted. In addition, for each size of foreign matter and each occurrence position, the operation failure due to the foreign matter was confirmed. As a result, it was confirmed that there was no problem in the initial performance and the durability performance. Moreover, about the foreign material to cube size of 0.3 mm of one side length, it confirmed that the malfunctioning by the biting of a foreign material can be suppressed.

(Main function and effect of the present invention)
As described above, the drainage valve drive device 1 of this embodiment includes the motor 40 and the gear unit 3 for transmitting the rotation of the motor 40 as the geared motor 2 for driving the lever 10 which is the drainage valve drive member. The gear unit 3 includes a transmission gear train 50 including an output gear 54 to which the lever 10 as a driven member is connected, and a transmission gear train 50 transmits the rotation of the motor 40 to the lever 10. And a second clutch mechanism 80 that switches between the second state in which the transmission wheel train 50 does not transmit the rotation of the motor 40 to the lever 10. Further, the transmission gear train 50 includes a reduction gear train including the reduction gear 53, and the second clutch mechanism 80 is a speed increasing gear engaged with the second rotating body 524 of the planetary gear mechanism 52 constituting the transmission gear train 50. A speed increasing wheel train including a gear 85 is provided. Then, as the gear shape of the gear unit 3, a module MA of the gears forming the speed increasing gear train has a larger shape than the module MB of the gears forming the transmission gear train 50 (reduction gear train).

  The inventors of the present invention, as in this embodiment, the transmission gear train 50 including the output gear 54 includes a reduction gear train (the output gear 54, the reduction gear 53, the planetary gear mechanism 52), and the second clutch mechanism 80 , A speed increasing gear train (speed increasing gear 85, lock gear 84) engaged with the gear of the transmission gear train 50 (the large diameter gear portion 528 of the second rotating body 524 of the planetary gear mechanism 52); In the geared motor 2 that operates by switching the rotation transmission path by 80, it was confirmed that foreign matter biting occurs when the speed increasing wheel train rotates. Therefore, the module of the speed increasing gear train is made larger than that of the conventional one, and for the speed reducing gear train, the module of the speed increasing gear train is larger than the module of the reduction gear train as a conventional module.

  By adopting such a gear shape, it is possible to widen the gap between the teeth in the speed-increasing wheel train in which the biting of the foreign matter occurs, and it is possible to secure a space through which the foreign matter passes. Therefore, it is possible to reduce the biting of the foreign matter, and to reduce the possibility that the foreign matter bites and the train wheel is locked. Therefore, the operation failure of the geared motor 2 and the drainage valve drive device 1 can be suppressed. Further, in the present embodiment, as the transmission wheel train 50 including the reduction wheel train, the conventional module is adopted, so the gears of the transmission wheel train 50 are not upsized. Therefore, it can suppress that the geared motor 2 enlarges, and can suppress that the drainage valve drive device 1 enlarges.

In this embodiment, in the first state in which the speed increasing gear train (speed increasing gear 85, lock gear 84) of the second clutch mechanism 80 does not rotate, the transmission gear train 50 (speed reduction gear train) is rotated by the driving force of the motor 40. And the lever 10 can be moved. In the second state in which the speed increasing gear 85 and the lock gear 84 are made to freely rotate, the reduction gear train (the output gear 54, the reduction gear 53, the planetary gear mechanism 52 (the third rotating body 526, the second rotation) The body 524) and the speed increasing wheel train (speed increasing gear 85, lock gear 84) can be idled to move the lever 10 by an external force, so that foreign matter bites in the operation of moving the lever 10 by an external force. Can reduce the possibility of the train wheel locking.

(Other embodiments)
(1) Although the module M is used as an index of the tooth shape in the above embodiment, the index of the tooth shape is not limited to the module M. For example, in the design of gears, the "crest factor k" is used as an indicator of the shape of the teeth. In the present specification, the definition of the apex coefficient k is k = (height of root (distance from pitch circle to root) / module M) -1. In the above embodiment, although the top coefficient k of the gears constituting the speed increasing wheel train is 0.25, the top coefficient k may be designed to be larger than 0.25. The gear shape having a top coefficient of greater than 0.25 has made it possible to secure a space for foreign matter to pass through. For example, in the case of a foreign body having a cube size of 0.3 mm on one side, it has come through the gap between teeth. Therefore, it is possible to reduce the possibility that foreign matter bites and the train wheel is locked.

(2) Although the drain valve drive device 1 of the said form used the lever 10 as a drain valve drive member, it can also use a slider and a pulley as a drain valve drive member. Moreover, although the geared motor 2 of this form used the drainage valve drive member as a to-be-driven member, the geared motor 2 can also be used for the apparatus which drives the member different from a drainage valve.

DESCRIPTION OF SYMBOLS 1 ... Drain valve drive device, 2 ... Geared motor, 3 ... Gear unit, 10 ... Lever, 11 ... Arm part, 12 ... Drain valve connection part, 13 ... Serration part, 20 ... Case, 21 ... 1st case, 22 ... Second case, 23: opening, 40: motor, 41: motor case, 42: support plate, 43: bobbin, 44: stator coil, 45: rotor, 46: induction rotating body, 47: rotor gear, 50: transmission wheel Column 51: Rotor pinion 52: Planetary gear mechanism 53: Reduction gear 54: Output gear 55: Projections 60: first clutch mechanism 61: first clutch claws 62: second clutch claws 63: Coil spring, 64: clutch switching lever, 65: cam pin, 66: cam groove, 67: inclined cam, 68: arc groove, 69: locking protrusion, 70: rotation restricting mechanism, 71: locked protrusion, 80 Second clutch mechanism, 81: rotating member, 82: fan gear, 83: lock lever, 84: lock gear, 85: acceleration gear, 86: torsion coil spring, 87: brake rubber, 451: magnet, 452: shaft portion 453: fixed shaft 461: induction ring 511: gear portion 512: shaft portion 521: sun gear 522: first rotating body 523: internal gear 524: second rotating body 525: planetary gear 526 third rotary body 527 large diameter gear portion 528 large diameter gear portion 529 small diameter gear portion 531 large diameter gear portion 532 small diameter gear portion 533 fixed shaft 671 inclined surface 672 ... cam surface, 841 ... projection, 842 ... large diameter, 843 ... small diameter gear, 851 ... large diameter gear, 852 ... small diameter gear, L ... rotation axis

Claims (6)

Motor,
A transmission gear train including an output gear to which a driven member is connected;
A clutch mechanism that switches between a first state in which the transmission wheel train transmits the rotation of the motor to the driven member, and a second state in which the transmission wheel train does not transmit the rotation of the motor to the driven member And have
The transmission wheel train comprises a reduction wheel train,
The clutch mechanism includes a speed increasing wheel train meshing with one of the gears constituting the transmission wheel train,
A geared motor characterized in that a module of gears constituting the speed increasing gear train is larger than a module of gears constituting the speed reducing gear train.   The geared motor according to claim 1, wherein a gear that constitutes the speed increasing gear train has a top coefficient greater than 0.25.   The geared motor according to claim 1 or 2, wherein the gears forming the speed increasing gear train and the speed reducing gear train are standard spur gears. The first state is a state in which the rotation of the speed increasing gear train is restricted, and the reduction gear train is rotated based on the rotation of the motor.
The geared motor according to any one of claims 1 to 3, wherein the second state is a state in which the reduction gear train and the speed increasing gear train are idled. The transmission gear train includes a planetary gear mechanism, and the planetary gear mechanism includes a planetary gear, a first rotary body including a sun gear meshing with the planetary gear, and a second rotary body including an internal gear meshing with the planetary gear And a third rotating body supporting the planetary gear,
The speed increasing wheel train includes a speed increasing gear meshing with the second rotating body, and a lock gear meshing with the speed increasing gear.
The reduction gear train includes a reduction gear that meshes the output gear,
The geared motor according to any one of claims 1 to 4, wherein a module of the speed increasing gear is larger than a module of the speed reducing gear. A geared motor according to any one of claims 1 to 5;
And a drain valve drive member driven based on rotation of the output gear.

Images