JP2009278819A - Geared motor for driving drain valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a geared motor for driving a drain valve having a new structure, which ensures a desired operation with a small number of components. <P>SOLUTION: In the geared motor 10 for driving the drain valve in which the drain valve to be operated and coupled to an output member 18 to receive a driving force of an electric motor 14 is driven and displaced from an initial position to an operation position, the drain valve is held at the operation position, and furthermore, the drain valve is allowed to return from the operation position to the initial position, the driving force of the electric motor 14 is transmitted to and cut off from the output member 18 by electric viscous fluid clutch means 44, 52, 60, 68, 70, 72, 76 utilizing a change in viscosity of an electric viscous fluid 76 based on a change in a voltage applied to the electric viscous fluid 76. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a drainage valve driving geared motor suitably employed as a driving means for opening and closing a drainage valve of a household washing machine, a dishwasher or the like.

  Conventionally, in order to obtain an effective output with a small electric motor, a geared motor in which a speed reduction means such as a gear is assembled to a motor drive shaft is known and has been adopted in consumer and general electric devices. As one type, for example, geared motors as described in Patent Documents 1 to 3 are known, and are employed as driving means for opening and closing drain valves of household washing machines and dishwashers.

  By the way, such a geared motor holds the operation object that has been driven and displaced from the initial position to the operation position at the operation position, and then cancels the action of the drive force or restraint force by the geared motor on the operation object. Thus, the operation object operates so as to allow the return operation from the operation position of the operation object to the initial position by the return force of the operation object itself. Therefore, in general, it is necessary to incorporate clutch means for transmitting / disconnecting the driving force of the motor to the operation target.

  Specifically, for example, Patent Document 1 discloses a geared motor incorporating an electromagnetic clutch means. The electromagnet clutch means includes an attracting piece that is attracted by a magnetic flux passing through the stator of the load driving motor. The clutch is engaged / disengaged by the operation of adsorption / separation of the adsorption piece.

  However, in the electromagnet type clutch means as described in Patent Document 1, it is difficult to amplify the stroke because the operation stroke of the attracting piece is small and the reciprocating motion is linear. For this reason, there has been a problem that it is difficult to reliably perform the switching operation of the clutch means.

  Further, Patent Document 2 discloses a guide ring type clutch means. This induction ring type clutch means includes a permanent magnet and a guide ring which are arranged to face each other, and one of the permanent magnet and the guide ring is driven to rotate by a load driving motor. Then, the other of the permanent magnet and the induction ring is rotationally driven by a magnetic induction action to operate the clutch operating piece to engage / disengage the clutch.

  However, in the induction ring type clutch means as described in Patent Document 2, a guide ring mechanism including a permanent magnet and a guide ring formed of a specific material is required to drive the clutch operating piece. There is a problem that the manufacturing cost becomes high.

  Further, Patent Document 3 discloses a winding clutch means using a flywheel and a coil spring. This winding-type clutch means includes a continuous rotation shaft disposed so as to be relatively rotatable on the same central axis with respect to a rotation drive shaft that is rotationally driven by a motor. Further, a connecting coil spring is extrapolated to the connecting rotating shaft, one end of the connecting coil spring is locked to the rotation driving shaft, and a flywheel is attached to the other end of the connecting coil spring. . As a result, the rotational acceleration and the stop acceleration of the rotational drive shaft are transmitted to the flywheel, and the tightening force of the coupled coil spring with respect to the coupled rotational shaft is controlled using the rotational mass of the flywheel. The transmission of the rotational driving force to the linked rotary shaft is controlled. Then, by rotating the linked rotary shaft with the rotary drive shaft, the clutch operating piece is driven to hold the clutch means in a joint state, while the linked rotary shaft is made independent of the rotary drive shaft, The clutch means is disengaged by returning it.

  However, the winding-type clutch means as described in Patent Document 3 requires a large number of parts, and a rotary drive shaft, a connected rotary shaft, a flywheel, a linked coil spring, etc. must be incorporated on the same central axis. There is a problem that the manufacturing work is extremely difficult because of the necessity. In addition, it is difficult to set the mass of the flywheel and the spring constant of the coil spring appropriately. If the tightening force of the connected coil spring to the connected rotating shaft is increased, the connected coil spring may be damaged. If the tightening force of the continuous coil spring to the continuous rotating shaft is small, stable driving force transmission becomes difficult and the clutch operation may become unstable.

JP-A-1-194833 Japanese Patent Laid-Open No. 3-198638 JP 2003-319609 A

  Here, the present invention has been made in the background of the above-described circumstances, and the problem to be solved is a novel structure that can reliably perform the intended operation with a small number of parts. The object is to provide a geared motor for driving a drain valve.

  Hereinafter, the aspect of this invention made | formed in order to solve such a subject is described. In addition, the component employ | adopted in each aspect as described below is employable by arbitrary combinations as much as possible.

  According to the present invention, an output member is driven by an electric motor through a reduction means such as a gear train, and a drain valve as an operation target having a return force connected to the output member is driven and displaced from an initial position to an operating position. In addition, in the drainage valve drive geared motor that holds the drain valve in the operating position and allows the return operation from the drain valve operating position to the initial position, the driving force of the electric motor is transmitted to the output member. As the clutch means for shutting off, an electrorheological fluid type clutch means using a change in the viscosity of the electrorheological fluid based on a change in the voltage applied to the electrorheological fluid is employed.

  In such a geared motor for driving a drain valve constructed in accordance with the present invention, an electric motor is provided by an electrorheological fluid type clutch means utilizing a change in viscosity of an electrorheological fluid based on a change in voltage applied to the electrorheological fluid. Since the driving force of the electric motor is transmitted / cut off to the output member, the driving force of the electric motor is transmitted / cut off to the output member by changing the voltage applied to the electrorheological fluid, that is, by electrical control. It becomes possible.

  Therefore, in the drainage valve driving geared motor according to the present invention, the intended operation can be realized with a small number of parts and a simple structure.

  In the present invention, the input side gear to which the rotational driving force of the electric motor is constantly exerted and the output side gear for outputting the rotational driving force of the electric motor toward the output member are arranged coaxially and One electrode provided on the input side gear and extending in the circumferential direction in the electrorheological fluid accommodated in the container provided on either the side gear or the output side gear, and provided on the output side gear The other electrode that extends in the circumferential direction and is opposed to one electrode in the radial direction is positioned, and a voltage is applied between the one electrode and the other electrode to increase the viscosity of the electrorheological fluid. As a result, transmission of the rotational driving force of the electric motor from the input side gear to the output side gear is allowed, while the application of voltage between one electrode and the other electrode is stopped to lower the viscosity of the electrorheological fluid. By By preventing the transmission of the rotational driving force of the electric motor from the power side gear to the output side gear, the electrorheological fluid clutch means may be configured. Thereby, the target drainage valve drive geared motor can be realized.

  In particular, if such a configuration is adopted, the electrorheological fluid clutch means is arranged on the transmission path of the driving force of the electric motor to the output member, and the driving force of the electric motor is directly transmitted / cut off. It becomes possible. As a result, the number of parts required for the drain valve driving motor can be reduced.

  In addition, when employ | adopting the above structures, the aspect which positions an electrode in an electrorheological fluid shall also include the aspect which uses the side wall of a storage container as an electrode.

  Furthermore, in the present invention, the mechanical clutch means is provided on the transmission path of the driving force of the electric motor to the output member, and on the path different from the transmission path of the driving force, A drive-side gear on which a rotational drive force is constantly exerted and a transmission-side gear that outputs the rotational drive force of the electric motor to a switching member that connects and disconnects the mechanical clutch means are arranged coaxially, and the drive-side gear And an electrorheological fluid accommodated in a container provided in one of the transmission side gears, one electrode provided in the drive side gear and extending in the circumferential direction, and a circumference provided in the transmission side gear. And an electrorheological fluid clutch means having a structure in which the other electrode, which extends in the direction and is opposed to one electrode in the radial direction, is positioned, and a voltage is applied between the one electrode and the other electrode. By increasing the viscosity of the electrorheological fluid, the transmission of the rotational driving force of the electric motor from the drive side gear to the transmission side gear is allowed, and the switching member is extended in the direction of breaking the mechanical clutch means. While driving the mechanical clutch means against the urging force, the drive side is stopped by stopping the application of voltage between one electrode and the other electrode to reduce the viscosity of the electrorheological fluid. The clutch means is configured by preventing transmission of the rotational driving force of the electric motor from the gear to the transmission side gear and allowing the switching member to be driven and displaced in the direction of disconnecting the mechanical clutch means by the biasing force. May be.

  Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described in detail with reference to the drawings.

  1 and 2 show a drainage valve driving geared motor 10 for opening and closing the drainage valve in the washing machine as the first embodiment of the present invention. The drainage valve driving geared motor 10 includes an electric motor 14, a reduction gear train 16 as a reduction means, and a slide lever 18 as an output member. And these electric motor 14, the reduction gear train 16, and the slide lever 18 are integrated in the state accommodated in the housing 12 attached to a washing machine main body.

  More specifically, the housing 12 includes a housing main body 20 that has a substantially rectangular open box shape as a whole, a lid 22 that overlaps the opening of the housing main body 20 and covers the opening, and the housing main body 20. It is comprised by the partition member 24 distribute | arranged between the cover body 22 and the. The housing body 20, the lid body 22, and the partition member 24 are screwed to each other, so that the housing 12 is formed with a hollow box structure having an internal space that is partitioned vertically by the partition member 24. . The electric motor 14 is accommodated in the recess 26 formed in the bottom of the housing 12 having such a structure.

  The electric motor 14 is a conventionally known AC synchronous motor. Specifically, a rotor 34 to which an output shaft 30 formed of a synthetic resin material such as ABS is fixed to an annular block-shaped permanent magnet 28, and a stator 38 around which an annular coil 36 is wound. It has. In the present embodiment, the rotor support shaft 32 on which the rotor 34 is rotatably inserted is provided between the stator 38 and the partition member 24. Then, when the coil 36 is energized, a rotational force is generated in the rotor 34 based on the magnetic force acting between the magnetic pole generated in the magnetic pole forming portion of the stator 38 and the magnetic pole of the permanent magnet 28 in the rotor 34. It can be tightened. In the present embodiment, the alternating current is supplied to the coil 36 through the pair of power supply terminals 40a and 40b.

  Further, an input side transmission wheel 44 as an input side gear is arranged near an output pinion 42 fixed to the output shaft 30 of the rotor 34. The input-side transmission wheel 44 is formed of a non-conductive material such as engineering plastic, and includes a disc portion 48 having meshing teeth 46 that mesh with the output pinion 42 formed on the outer peripheral surface. Further, a boss portion 50 protruding downward is integrally formed at the center of the disc portion 48.

  Further, in the present embodiment, an input side electrode 52 as one electrode is provided for the input side transmission wheel 44. The input side electrode 52 is formed of a conductive material such as copper, and in this embodiment, has a thin cylindrical shape having an inner and outer diameter dimension larger than the outer diameter dimension of the boss portion 50.

  Such an input side electrode 52 is arranged concentrically with the disc portion 48 and is provided integrally with the input side transmission wheel 44. In particular, in the present embodiment, the input side electrode 52 is provided integrally with the input side transmission wheel 44 in a state of penetrating the disc portion 48 in the thickness direction. As a method of integrally forming the input side electrode 52 with the input side transmission wheel 44, for example, in a state where the input side electrode 52 is disposed at a predetermined position in the molding cavity of the input side transmission wheel 44, the input side transmission wheel is provided. A method of integrally forming the input side transmission wheel 44 and the input side electrode 52 by injecting the forming material 44 into the molding cavity is employed.

  The input-side transmission wheel 44 having the above-described structure is arranged in a state of being rotatable around a support shaft 54 provided between the partition member 24 and the stator 38. In this state, the meshing teeth 46 formed on the outer peripheral surface of the disc part 48 are meshed with the output pinion 42.

  A reverse rotation prevention lever 56 is arranged below the input side transmission wheel 44 so as to be swingable around the support shaft 54. The reverse rotation prevention lever 56 is locked in one direction of rotation of the rotor 34 with respect to a locking claw 58 provided on the output shaft 30 of the rotor 34. Thereby, the rotation direction of the rotor 34 is prescribed | regulated.

  Further, an output side transmission wheel 60 as an output side gear is disposed above the input side transmission wheel 44. This output side transmission wheel 60 is made of a non-conductive material such as engineering plastic, and has a structure in which an output side transmission pinion 62 and an output side transmission gear 64 are integrally provided on the same central axis. . Further, a boss portion 66 projecting downward is provided on the lower surface of the output side transmission gear 64.

  Further, in the present embodiment, the storage container 68 is assembled to the output side transmission wheel 60. The container 68 is made of a conductive material such as copper. In the present embodiment, the axial ends of the inner cylinder 70 and the outer cylinder 72 that are concentrically arranged have a circular plate shape. It is the structure connected by. That is, in the present embodiment, an annular accommodation space formed between the inner cylinder 70 and the outer cylinder 72 in the radial direction is communicated to the outside through an opening on the other axial end side.

  The storage container 68 having such a structure is disposed concentrically with the output-side transmission wheel 60 and is provided integrally with the output-side transmission wheel 60. In particular, in the present embodiment, the connecting container 74 is embedded in the output side transmission gear 64, and the container 68 is connected to the output side transmission wheel 60 with the inner cylinder 70 and the outer cylinder 72 projecting toward the boss 66. It is provided integrally. In addition, as a method of integrally providing the storage container 68 with respect to the output side transmission wheel 60, for example, in a state where the storage container 68 is disposed at a predetermined position in the molding cavity of the output side transmission wheel 60, the output side transmission is performed. For example, a method of integrally forming the output-side transmission wheel 60 and the storage container 68 by injecting the forming material of the wheel 60 into the molding cavity is adopted.

  The output-side transmission wheel 60 having the above-described structure is rotatable around the support shaft 54, and the boss portion 66 is superimposed on the disk portion 48 of the input-side transmission wheel 44. It is arranged. Further, in the state where the output side transmission wheel 60 is arranged in this way, the input side electrode 52 provided on the input side transmission wheel 44 is connected to the inner cylinder 70 of the storage container 68 provided on the output side transmission wheel 60. It is positioned between the opposing surfaces of the outer cylinder 72. In other words, the input-side electrode 52 of the input-side transmission wheel 44 is positioned in the accommodation space of the storage container 68 of the output-side transmission wheel 60 in the state where the output-side transmission wheel 60 is arranged as described above. It is.

  Therefore, in this embodiment, the housing 12 is attached to the washing machine with the connecting plate 74 positioned on the bottom side, that is, with the drainage valve driving geared motor 10 shown in FIG. 2 turned upside down. It is like that. In this state, the electrorheological fluid 76 is stored in the storage container 68.

  The electrorheological fluid 76 is not particularly limited as long as the viscosity is reversibly changed by application of a voltage, and any of various conventionally known electrorheological fluids can be employed. It is desirable that 1) excellent responsiveness to voltage application, (2) large viscosity change by voltage application, and (3) stable display of such characteristics over a long period of time. Thereby, transmission / cutoff of the rotational driving force of the electric motor 14 using the viscosity change of the electrorheological fluid 76 as described later can be stably performed over a long period of time. Further, it is desirable that the current flowing through the electrorheological fluid 76 when a voltage is applied is as small as possible. Thereby, it becomes possible to suppress power consumption. Furthermore, when using a dispersion-type electrorheological fluid in which polarizable powder is dispersed in an electrically insulating oily medium such as insulating oil, the powder may settle or agglomerate in the oily medium. In other words, it is desirable that the dispersion of the powder be stable over a long period of time. Thereby, stable characteristics can be exhibited over a long period of time. Furthermore, when a uniform type electrorheological fluid is used, there is no deterioration in characteristics due to phase separation due to the density difference between the powder and the oily medium in the dispersion type electrorheological fluid. Stable characteristics can be exhibited.

  In addition, a contact piece 80a connected to one connection terminal 78a is slidably contacted with the outer peripheral surface of the input side electrode 52 on the opposite side of the output side transmission wheel 60 across the disc portion 48. Yes. Furthermore, the contact piece 80b connected to the other connection terminal 78b is slidably contacted with the outer peripheral surface of the outer cylinder 72 constituting the container 68. Each of the contact pieces 80a and 80b is formed of an elastic and conductive material such as spring copper.

  When a DC voltage is applied between the pair of connection terminals 78a and 78b, the contact piece 80a connected to one connection terminal 78a is connected to the input side electrode 52 in sliding contact with the other connection terminal 78b. A direct current flows through the electrorheological fluid 76 between the outer cylinders 72 in which the contact piece 80b is in sliding contact. Thereby, the viscosity of the electrorheological fluid 76 can be changed.

  In the present embodiment, since the inner cylinder 70 is electrically connected to the outer cylinder 72 by the connecting plate 74, the electrorheological fluid 76 is also interposed between the input side electrode 52 and the inner cylinder 70. A direct current flows.

  That is, in this embodiment, the other electrode is constituted by each of the inner cylinder 70 and the outer cylinder 72.

  An intermediate wheel 84 is arranged near the output-side transmission wheel 60 so as to be rotatable around the support shaft 82. The intermediate wheel 84 has a structure in which an intermediate gear 86 and an intermediate pinion 88 are integrally formed on the same central axis. The intermediate gear 86 in the intermediate wheel 84 is meshed with the output side transmission pinion 62 in the output side transmission wheel 60. In the present embodiment, the support shaft 82 is provided between the partition member 24 and the stator 38.

  Further, a first transmission gear 94 is disposed near the intermediate wheel 84 so as to be rotatable around the support shaft 92. In this state, the first transmission gear 94 is meshed with the intermediate pinion 88 in the intermediate wheel 84. In the present embodiment, the support shaft 92 is provided between the support portion 90 fixed to the stator 38 and the lid body 22.

  Further, in the state where the first transmission gear 94 is arranged as described above, the central shaft portion of the first transmission gear 94 is inserted into an insertion hole formed in the partition member 24. Thereby, the protruding end of the first transmission gear 94 is positioned in a region above the partition member 24. A second transmission gear 96 is assembled to the projecting end of the central shaft portion of the first transmission gear 94 so as to be rotatable integrally with the first transmission gear 94.

  Furthermore, a slide lever 18 is disposed near the second transmission gear 96. The slide lever 18 has a structure including a main body portion 100 on which a rack 98 is formed and a connecting protrusion portion 102 protruding from the main body portion 100.

  The slide lever 18 having such a structure is arranged in a state where the guide rail 104 provided in the partition member 24 is positioned in the guide groove 106 formed in the main body 100. Thereby, the slide lever 18 can be reciprocally displaced by the guide action by the guide rail 104 and the guide groove 106.

  Further, the rack 98 formed in the main body 100 is engaged with the second transmission gear 96 in the state where the slide lever 18 is arranged in this way. Thereby, the rotational driving force of the electric motor 14 is slid through the output pinion 42, the input side transmission wheel 44, the output side transmission wheel 60, the intermediate wheel 84, the first transmission gear 94, and the second transmission gear 96. It can be transmitted to the lever 18. As is clear from this, in the present embodiment, the output pinion 42, the input side transmission wheel 44, the output side transmission wheel 60, the intermediate wheel 84, the first transmission gear 94 and the second transmission gear 96 are used. A reduction gear train 16 is configured.

  Further, in the state where the slide lever 18 is arranged as described above, the connecting protrusion 102 protrudes to the outside through the through hole 108 formed in the housing 12. In this state, a drain valve (not shown) is attached to the attachment piece 110 provided at the tip of the connection protrusion 102. When the rotational driving force of the electric motor 14 is transmitted to the slide lever 18, the slide lever 18 is retracted and displaced. As a result, the drain valve is displaced from the initial position to the operating position.

  Furthermore, a switch gear 112 is disposed near the second transmission gear 96. The switch gear 112 includes an operation protrusion 114 that protrudes upward at a radial intermediate portion thereof.

  The switch gear 112 is arranged in a state of being rotatable around a support shaft 116 provided between the lid body 22 and the partition member 24. In this state, the switch gear 112 is meshed with the second transmission gear 96.

  A switch operation member 118 is disposed above the switch gear 112. The switch operation member 118 has a structure including a peripheral wall 120 and a bottom wall 122. Here, the peripheral wall 120 is formed with a concave groove 124 that opens to the outer peripheral surface and extends over the entire axial direction of the peripheral wall 120. In particular, in the present embodiment, one side wall surface in the circumferential direction of the concave groove 124 extends in the direction perpendicular to the axis, but the other side wall surface in the circumferential direction has a groove width of the concave groove 124 toward the opening side of the concave groove 124. It is an inclined surface in which the dimension (dimension in the circumferential direction corresponding to the groove width direction) increases. Further, an insertion hole 126 penetrating in the thickness direction is formed in the outer peripheral edge portion of the bottom wall 122.

  The switch operation member 118 having such a structure is arranged so as to be able to rotate around the support shaft 116 so as to overlap the switch gear 112. With the switch operation member 118 arranged in this manner, the operation protrusion 114 provided on the switch gear 112 is positioned in the insertion hole 126 formed in the bottom wall 122 of the switch operation member 118. Yes. Thereby, the operation protrusion 114 can be engaged with each of the portions located at both ends in the circumferential direction on the inner peripheral surface of the insertion hole 126.

  Further, an internal switch 128 is disposed near the switch operation member 118. The internal switch 128 is composed of a pair of switch segments 130a and 130b. Each of the switch segments 130a and 130b is formed of a conductive and elastic material such as spring copper, and a base member thereof is formed of a non-conductive synthetic resin material. It is supported.

  Here, one of the switch segments 130a has a structure in which a bent portion 134 is formed on the free end side. One switch segment 130 b is connected to one end of a coil 36 wound around a stator 38 constituting the electric motor 14. The other switch segment 130 a is connected to one of the pair of power supply terminals 40 a and 40 b used for power supply to the electric motor 14.

  When such an internal switch 128 is in sliding contact with the cylindrical outer peripheral surface of the peripheral wall 120 of the switch operating member 118, the one switch segment 130 a is formed when the tip of the bent portion 134 formed in one switch segment 130 a is in sliding contact. The contact terminal 136a provided on the other switch contacts the contact terminal 136b provided on the other switch section 130b. As a result, the internal switch 128 is turned on, and the electric motor 14 can be supplied with power. In addition, when the tip of the bent portion 134 formed in one switch segment 130a is positioned in the concave groove 124 formed in the peripheral wall 120 of the switch operation member 118, the one of the switch segment 130a The contact terminal 136a is separated from the contact terminal 136b of the other switch section 130b. As a result, the internal switch 128 is turned off, and power supply to the electric motor 14 cannot be performed.

  A speed control mechanism 138 is disposed in the housing 12. The speed control mechanism 138 includes a rotation operation shaft 142 on which a speed control pinion 140 is formed. In addition, a disc-shaped support base 144 is provided at the upper end of the rotation operation shaft 142. Therefore, a support pin 146 that protrudes upward in the axial direction is provided in the vicinity of the outer peripheral edge of the support base 144.

  The rotary operation shaft 142 having such a structure is disposed in a state of being rotatable around a support shaft 148 provided between the partition member 24 and the stator 38. In this state, the speed adjusting pinion 140 is meshed with the output side transmission gear 64 in the output side transmission wheel 60.

  In addition, a sliding body 150 having a substantially crescent-shaped or arc-shaped block shape is assembled to the rotary operation shaft 142. Specifically, the support pin 146 protruding from the support base 144 is inserted into an insertion hole formed on one end in the circumferential direction of the slide body 150, so that the slide body 150 can rotate around the support pin 146. It is arranged in the state.

  Furthermore, an elastic connecting member 152 is assembled to the rotation operating shaft 142. The elastic connecting member 152 extends at the upper end in the axial direction of the central shaft portion 154 that is externally attached to the support shaft 148 so as to protrude outward in the direction perpendicular to the axis, and then extends toward the other side in the circumferential direction. 156 is integrally formed.

  The elastic connecting member 152 having such a structure is disposed above the rotation operating shaft 142 in a state where the central shaft portion 154 is extrapolated to the support shaft 148 and placed on the support base 144. Yes. In the present embodiment, the central shaft portion 154 of the elastic connecting member 152 is placed on the bottom surface of the recess formed in the support base 144. In this state, the locking piece provided at the extending end of the elastic coupling piece 156 is locked to the inner peripheral surface of the locking hole formed at the other circumferential end of the sliding body 150.

  In the speed adjusting mechanism 138 as described above, when the rotary operation shaft 142 is rotated to one side in the circumferential direction, the sliding body 150 resists the urging force of the elastic connecting piece 156 by the centrifugal force. It can be displaced outward in the direction perpendicular to the axis.

  In this case, a cylindrical portion 160 is positioned outside the rotational operation shaft 142 in the direction perpendicular to the axis. The cylindrical portion 160 includes a cylindrical sliding surface 158 that is slid when the sliding body 150 is displaced outward in the direction perpendicular to the axis of the rotary operation shaft 142. In the present embodiment, the cylindrical portion 160 is integrally formed with the partition member 24. The sliding body 150 is displaced outward in the direction perpendicular to the axis of the rotational operation shaft 142 and is slid on the cylindrical sliding surface 158, whereby the rotational speed of the rotational operation shaft 142 is adjusted. ing.

  Further, as is clear from the above description, in the drainage valve driving geared motor 10, as shown in FIG. 3, a DC voltage is applied to the electrorheological fluid 76 through a pair of connection terminals 78a and 78b. In addition to the fluid circuit 162, a motor circuit 164 for supplying power to the electric motor 14 through a pair of power supply terminals 40a and 40b is provided. In particular, in the present embodiment, an internal switch 128 is provided on the motor circuit 164. Thus, power supply to the electric motor 14 can be controlled by turning on / off the internal switch 128.

  Next, the operation of the drainage valve driving geared motor 10 having the above-described structure will be described. First, in an initial state in which power is not supplied to the electric motor 14, the drain valve is in the initial position. In the initial state, as shown in FIG. 1, the bent portion 134 of one switch segment 130 a is in contact with the cylindrical outer peripheral surface of the peripheral wall 120. As a result, the internal switch 128 is turned on, so that the electric motor 14 can be fed. In such an initial state, when power is supplied to the electric motor 14 through the pair of power supply terminals 40a and 40b, the rotor 34 is rotated.

  In the present embodiment, power is supplied to the electric motor 14 through the pair of power supply terminals 40a and 40b, and at the same time, a DC voltage is applied between the pair of connection terminals 78a and 78b. Thereby, the viscosity of the electrorheological fluid 76 in the storage container 68 provided in the output side transmission wheel 60 is increased, and the input side electrode 52 immersed in the electrorheological fluid 76 is extended to the storage container 68, It will not rotate relative to the output side transmission wheel 60. As a result, the input-side transmission wheel 44 and the output-side transmission wheel 60 are integrally rotated, and the rotational driving force of the electric motor 14 is applied to the input-side transmission wheel 44, the output-side transmission wheel 60, the intermediate wheel 84, the second wheel. It is transmitted to the slide lever 18 via the one transmission gear 94 and the second transmission gear 96. Then, the drain valve is driven and displaced (retraction displacement) from the initial position toward the operating position against the restoring force of itself (see FIG. 4).

  In addition, in the state where the input side transmission wheel 44 and the output side transmission wheel 60 are rotating integrally, the rotation operation shaft 142 to which the rotation of the output side transmission wheel 60 is transmitted is rotated in the other circumferential direction. Thus, the sliding body 150 is prevented from swinging outward in the direction perpendicular to the rotation operation shaft 142 around the support pin 146 due to the centrifugal force generated with the rotation of the rotation operation shaft 142. As a result, the sliding body 150 does not slide on the cylindrical sliding surface 158 when the slide lever 18 is retracted.

  Further, in the switch gear 112 to which the rotation of the second transmission gear 96 is transmitted when the slide lever 18 is retracted, the operation projection 114 is formed on the inner peripheral surface on one end side in the circumferential direction of the insertion hole 126 of the switch operation member 118. It can be rotated in contact. As a result, the switch gear 112 and the switch operating member 118 are rotated together.

  As described above, when the rotational driving force of the electric motor 14 is transmitted to the slide lever 18 and the drain valve is driven and displaced to the operating position, the peripheral wall of the switch operating member 118 that is rotated integrally with the switch gear 112. The distal end of the bent portion 134 of one of the switch segments 130 a that has been slid on the cylindrical outer peripheral surface of 120 enters the recessed groove 124 formed in the peripheral wall 120 of the switch operating member 118. As a result, the contact terminal 136a provided on one switch segment 130a and the contact terminal 136b provided on the other switch segment 130b are separated, and the internal switch 128 is turned off. As a result, the power supply to the electric motor 14 is stopped and the rotation of the electric motor 14 is stopped. When the internal switch 128 is turned off, the protruding end of the other switch segment 130b comes into contact with a stopper piece 163 provided on the partition member 24. Thereby, the OFF state of the internal switch 128 is maintained.

  Further, even when the internal switch 128 is OFF, as shown in FIG. 4, a state in which a DC voltage is applied is continued between the pair of connection terminals 78a and 78b. Thus, the detent torque of the electric motor 14 is transmitted to the slide lever 18 via the input side transmission wheel 44, the output side transmission wheel 60, the intermediate wheel 84, the first transmission gear 94, and the second transmission gear 96. The Rukoto. As a result, the drainage valve is held in the operating position without returning to the initial position by the return force of itself (see FIG. 4).

  And when predetermined time passes, application of the DC voltage between a pair of connection terminals 78a and 78b is stopped. As a result, the viscosity of the electrorheological fluid 76 decreases, and relative rotation between the input side transmission wheel 44 and the output side transmission wheel 60 is allowed. As a result, the detent torque of the electric motor 14 is not transmitted to the slide lever 18. Then, the drain valve returns to the initial position by the return force of itself (see FIG. 4).

  As is apparent from the above description, in the present embodiment, the output side transmission wheel 60 provided with the storage container 68, the input side transmission wheel 44 provided with the input side electrode 52, and the storage container 68 store it. The electrorheological fluid type clutch means 165 (see FIG. 3) as the clutch means is configured including the electrorheological fluid 76 that is provided.

  Accordingly, in the drainage valve driving geared motor 10 as described above, transmission / cutoff of the rotational driving force of the electric motor 14 to the slide lever 18 is energized / disconnected to the electrorheological fluid 76 through the pair of connection terminals 78a and 78b. It can be realized by a very simple method of blocking. As a result, transmission / interruption of the rotational driving force of the electric motor 14 to the slide lever 18 can be reliably performed with a small number of parts and a simple structure.

  In particular, in the present embodiment, the electrorheological fluid clutch means is arranged in the reduction gear train 16 that constitutes the transmission path of the rotational driving force of the electric motor 14 to the slide lever 18. Thereby, the number of parts required for the drainage valve driving geared motor 10 can be reduced.

  In the present embodiment, an electric current flows between the input side electrode 52 and the inner cylinder 70 via the electrorheological fluid 76, and the electrorheological fluid 76 between the input side electrode 52 and the outer cylinder 72. A current flows through the. As a result, the input side electrode 52 is restrained by the electrorheological fluid 76 having increased viscosity on both the inner peripheral side and the outer peripheral side. As a result, it is possible to efficiently transmit the rotational driving force of the electric motor 14 from the input side transmission wheel 44 to the output side transmission wheel 60.

  Furthermore, in the present embodiment, the inner cylinder 70 and the outer cylinder 72 constituting the container 68 in which the electrorheological fluid 76 is accommodated are the other electrodes. Thereby, it is not necessary to separately provide the electrode itself in addition to the container 68. As a result, it is possible to advantageously secure a space for arranging the electrodes.

  Next, a drain valve driving geared motor 166 as a second embodiment of the present invention will be described with reference to FIGS. 5 and 6. In the following description, members and parts having the same structure as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and detailed descriptions thereof are omitted. To do.

  The drainage valve driving geared motor 166 of this embodiment differs from the drainage valve driving geared motor (10) of the first embodiment in the configuration of the reduction gear train 168.

  More specifically, the reduction gear train 168 of the present embodiment includes a rotational force interrupting mechanism 170, a planetary gear mechanism 172, and an intermediate wheel 174.

  The rotational force relay mechanism 170 includes an upper joint member 176, a lower joint member 178, and a coil spring 180. The upper connecting member 176 includes a disk-shaped portion 184 having a locking claw 182 formed on the outer peripheral surface. Further, a connection pinion 186 is formed on the upper surface of the disk-shaped portion 184 so as to protrude. Furthermore, a plurality of locking recesses 188 are formed in the lower surface of the disk-shaped portion 184.

  The lower connection member 178 includes a connection gear 190 that meshes with an output pinion 42 fixed to the output shaft 30. Also, a boss portion 192 that protrudes downward in the axial direction is formed on the lower surface of the lower joint member 178. Furthermore, a plurality of (in this embodiment, two) notch grooves are formed around the central axis in the intermediate portion in the radial direction of the connection gear 190 in the lower connection member 178. A locking piece 194 that can be engaged with the locking recess 188 of the upper connecting member 176 is formed in the cutout groove so as to be elastically displaceable in the axial direction of the lower connecting member 178. Yes.

  The upper joint member 176 and the lower joint member 178 having such a structure are arranged so as to be overlapped with each other in the axial direction with the coil spring 180 interposed therebetween. Then, in the state where the upper connecting member 176 and the lower connecting member 178 are arranged in this way, the upper connecting member 176 and the lower connecting member 178 are elastically separated by the urging force of the coil spring 180. And it is made to oppose. In the present embodiment, the upper end portion of the coil spring 180 is housed in a recess formed in the lower surface of the upper connecting member 176. In addition, the lower end portion of the coil spring 180 is extrapolated to a positioning protrusion that is formed to protrude from the center of the upper surface of the lower joint member 178.

  Then, the upper connecting member 176 and the lower connecting member 178 are caused to approach each other in the axial direction against the urging force of the coil spring 180, and the locking recess 188 of the upper connecting member 176 and the lower connecting member 176 are connected. In a state where the locking piece 194 of the member 178 is engaged, the upper connecting member 176 and the lower connecting member 178 are integrally rotated. Thereby, the rotational driving force of the electric motor 14 is transmitted to the connection pinion 186 of the upper connection member 176. Accordingly, in the present embodiment, the engagement between the locking recess 188 of the upper connecting member 176 and the locking piece 194 of the lower connecting member 178 is maintained in the forward rotation direction of the electric motor 14. However, the ratchet structure is released in the reverse rotation direction.

  The planetary gear mechanism 172 includes a case 196 and a follower 198. The case 196 has a bottomed cylindrical shape as a whole. An internal gear 200 is formed on the inner peripheral surface of the cylindrical wall portion, while an external gear 202 is formed on the outer peripheral surface of the cylindrical wall portion.

  The follower 198 has a structure in which a disc portion 204 and an annular plate-like portion 206 that are spaced apart in the axial direction are connected by a plurality of gear pins 208. Further, a connecting pinion 210 that protrudes upward in the axial direction is integrally formed at the central portion of the disc portion 204.

  The follower 198 having such a structure is assembled to the case 196 by being fitted into the case 196. The planetary gear 212 is rotatably attached to each gear pin 208 with the follower 198 assembled to the case 196 in this manner. In this state, the planetary gear 212 is meshed with the internal gear 200.

  Further, the case 196 is superposed on the upper joint member 176 in the state where the follower 198 is assembled to the case 196 as described above. In this state, the connection pinion 186 of the upper connection member 176 is inserted into a through hole formed in the bottom wall of the case 196 and is positioned in the case 196. The connection pinion 186 positioned in the case 196 is meshed with the planetary gear 212. As apparent from this, in the present embodiment, the sun gear of the planetary gear mechanism 172 is constituted by the connection pinion 186.

  Furthermore, the intermediate wheel 174 has a structure in which an intermediate gear 214 and an intermediate pinion 216 are integrally formed on the same central axis. The intermediate wheel 174 is arranged in a rotatable state around the support shaft 218. In this state, the intermediate gear 214 is engaged with the connection pinion 210, and the intermediate pinion 216 is engaged with the rack 98 of the slide lever 18.

  As a result, the rotational driving force of the electric motor 14 is transmitted to the slide lever 18 via the rotational force interrupting mechanism 170, the planetary gear mechanism 172, and the intermediate wheel 174. As a result, the drain valve attached to the attachment piece 110 of the slide lever 18 can be driven and displaced.

  A cam lever 220 is disposed below the intermediate wheel 174 so as to be swingable around the support shaft 218. As shown in FIG. 7, the cam lever 220 is provided with an extending plate portion 222 that extends in a direction orthogonal to the swing center axis. An operation piece 224 extending in the circumferential direction around the swinging central axis of the cam lever 220 is provided at the extension end of the extension plate portion 222. The operation piece 224 is formed with a guide hole 226 extending in the extending direction.

  Therefore, the operation piece 224 of the present embodiment is formed with an inclined surface 228 at an intermediate portion in the extending direction. Thereby, the extended end side is positioned below the base end side of the operation piece 224.

  Further, the cam lever 220 is provided with a protruding piece 230 that protrudes in a direction different from that of the extending plate portion 222. The protruding piece 230 comes into contact with a guide protruding portion 232 provided on the slide lever 18 on the tip side. Further, the protruding piece 230 comes into contact with an operation protrusion 234 provided on the intermediate wheel 174 on the base end side.

  Furthermore, the cam lever 220 is formed with a pair of engaging pieces 236 protruding in a direction different from the extending plate portion 222 and the protruding piece 230 with an appropriate interval in the circumferential direction around the central axis.

  The cam lever 220 having such a structure is arranged so as to be swingable around the support shaft 218. In this state, the planetary gear mechanism 172 and the support shaft 238 of the rotational force interrupting mechanism 170 are loosely inserted into the guide holes 226 formed in the operation piece 224. In this state, the boss portion 192 of the lower joint member 178 is slidably brought into contact with the upper surface of the operation piece 224.

  In addition, a locking member 240 is disposed near the cam lever 220 as shown in FIG. The locking member 240 includes a locking claw 242 that extends outward in the direction perpendicular to the axis. The locking member 240 includes an engagement piece 244 that extends in a direction different from that of the locking claw 242.

  The locking member 240 having such a structure is arranged so as to be swingable around the support shaft. In this state, the locking claw 242 provided on the locking member 240 can be engaged with the locking claw 182 provided on the upper joint member 176. In this state, the engaging piece 244 provided on the locking member 240 is positioned between the pair of engaging pieces 236 and 236 provided on the cam lever 220.

  Therefore, in this embodiment, as shown in FIG. 8, when the protruding piece 230 of the cam lever 220 is in sliding contact with the guide protrusion 232 provided on the slide lever 18, the lower connecting member 178 is provided. The boss portion 192 is brought into contact with the proximal end portion of the operation piece 224, and the lower joint member 178 is lifted upward. Thus, a relative displacement force in the approach direction is exerted between the connecting gear 190 and the connecting pinion 186 in the axial direction. As a result, the locking piece 194 of the lower connecting member 178 and the locking recess 188 of the upper connecting member 176 are locked so that the rotational driving force of the electric motor 14 is transmitted to the connecting pinion 186. It has become.

  Then, in a state where the locking piece 194 of the lower connection member 178 and the locking recess 188 of the upper connection member 176 are locked, as shown in FIG. The claw 242 is not locked to the locking claw 182 of the upper joint member 176. Thereby, the rotation of the upper joint member 176 is allowed.

  On the other hand, as shown in FIG. 7, when the operation protrusion 234 provided on the intermediate wheel 174 is in contact with the protruding piece 230 of the cam lever 220, the boss 192 of the lower joint member 178 is The lower connecting member 178 is brought into contact with the extended end portion of the operation piece 224, and is separated from the upper connecting member 176 by the urging force of the coil spring 180 and is positioned below. Thereby, the relative displacement force in the approach direction in the axial direction, which has been exerted between the connection gear 190 and the connection pinion 186, is released. As a result, the locking state of the locking piece 194 of the lower connecting member 178 and the locking recess 188 of the upper connecting member 176 is released, and the rotational driving force of the electric motor 14 is not transmitted to the connecting pinion 186. (See FIG. 6).

  When the locking state of the locking piece 194 of the lower connecting member 178 and the locking recess 188 of the upper connecting member 176 is released in this way, as shown in FIG. The locking claw 242 of the member 240 is locked to the locking claw 182 of the upper joint member 176. Thereby, the rotation of the upper joint member 176 is prevented.

  Further, in the present embodiment, meshing teeth are formed on the outer peripheral surface of the disc portion provided on the rotation operation shaft 142 constituting the speed adjusting mechanism 138. As a result, the rotational operation shaft 142 has a structure in which the speed adjusting gear 246 is formed on the axially upper side of the speed adjusting pinion 140. In this embodiment, the speed adjusting pinion 140 is meshed with the external gear 202 of the planetary gear mechanism 172.

  Furthermore, a stopper gear 248 is disposed near the speed adjusting mechanism 138 in a state of being rotatable around the support shaft 250. In this state, the stopper gear 248 is meshed with the speed control gear 246.

  In addition, a transmission gear 252 is arranged in the housing 12 so as to be rotatable around the support shaft 254. In this state, the transmission gear 252 is meshed with an output pinion 42 fixed to the output shaft 30. In the present embodiment, a reverse rotation prevention lever 56 is disposed below the transmission gear 252.

  Furthermore, in this embodiment, the input side transmission wheel 44 has no meshing teeth (46) formed on the outer peripheral surface of the disc portion 48, and instead, the outer peripheral surface of the lower end portion in the axial direction of the boss portion 50. The meshing teeth are formed on. Thus, the input side transmission wheel 44 has a structure including the input side transmission pinion 256. In this embodiment, the input side transmission pinion 256 is meshed with the transmission gear 252.

  Furthermore, the output-side transmission wheel 60 of the present embodiment is not provided with the output-side transmission gear 64, but instead is provided with a disk-shaped portion 258. In this embodiment, the connecting plate 74 of the storage container 68 is embedded in the disc-shaped portion 258.

  In the vicinity of the output-side transmission wheel 60 of the present embodiment having such a structure, an oscillating body 260 as a switching member is disposed. The oscillating body 260 has a substantially fan shape extending around the oscillation central axis. The output side transmission pinion 62 of the output side transmission wheel 60 is meshed with the meshing teeth 262 formed on the arcuate outer peripheral surface. Thereby, the rocking body 260 can be rocked based on the rotation of the output side transmission wheel 60. Further, the rocking body 260 is formed with a locking piece 264. A restoring force in one direction of the swinging direction is applied to the swinging body 260 by the coil spring 266 locked by the locking piece 264.

  A stopper portion 268 is formed on the rocking body 260. When the oscillator 260 is rotated against the restoring force of the coil spring 266, the stopper 268 is placed on the stopper projection 270 provided on the stopper gear 248 as shown in FIG. It can be engaged. Accordingly, the rotation operation of the rotation operation shaft 142 is blocked, and the rotation of the case 196 including the external gear 202 engaged with the speed control pinion 140 formed on the rotation operation shaft 142 is blocked. Yes. In the state where the oscillator 260 is in the initial position, the stopper portion 268 does not interfere with the stopper protrusion 270 of the stopper gear 248 as shown in FIG.

  In the present embodiment, the electric circuit for driving the drainage valve driving geared motor 166 has a motor circuit 164 as compared with the electric circuit of the first embodiment, as shown in FIG. The internal switch (128) is not provided on the top.

  Next, the operation of the drainage valve driving geared motor 166 having the above-described structure will be described. First, in an initial state in which power is not supplied to the electric motor 14, the drain valve is in the initial position. When power is supplied to the electric motor 14 in such an initial state, the rotor 34 is rotated.

  Here, when the rotor 34 is rotated from the initial state, the protruding piece 230 of the cam lever 220 is in sliding contact with the guide protrusion 232 of the slide lever 18. Thus, the lower connecting member 178 is pushed upward in the axial direction against the restoring force of the coil spring 180 by the proximal end portion of the operation piece 224 of the cam lever 220. As a result, the locking piece 194 of the lower connection member 178 is locked to the locking recess 188 of the upper connection member 176, and the rotational force transmission mechanism 170 is in the connection state. At that time, the locking claw 242 of the locking member 240 is not locked to the locking claw 182 of the upper joint member 176. Thereby, the rotation of the upper joint member 176 is allowed.

  In addition, when the rotor 34 is rotated from the initial state, a DC voltage is applied between the pair of connection terminals 78a and 78b. In particular, in the present embodiment, a DC voltage is applied between the pair of connection terminals 78a and 78b simultaneously with power feeding to the electric motor 14. Thereby, the viscosity of the electrorheological fluid 76 is increased, and the rotation of the input side transmission wheel 44 can be transmitted to the output side transmission wheel 60. As a result, the rocking body 260 including the meshing teeth 262 meshed with the output side transmission pinion 62 of the output side transmission wheel 60 is rocked against the restoring force of the coil spring 266. When the rocking body 260 is swung against the restoring force of the coil spring 266, the stopper 268 of the rocking body 260 is engaged with the stopper protrusion 270 of the stopper gear 248 as shown in FIG. Combined. Thereby, the rotation of the rotation operating shaft 142 is prevented. As a result, the rotation of the case 196 provided with the external gear 202 meshed with the speed adjusting pinion 140 of the rotation operating shaft 142 is prevented.

  By preventing the rotation of the case 196 in this way, the rotational driving force of the electric motor 14 is transmitted to the slide lever 18 via the rotational force interrupting mechanism 170, the planetary gear mechanism 172, and the intermediate wheel 174. As a result, the slide lever 18 is retracted and displaced. As a result, the drain valve attached to the attachment piece 110 of the slide lever 18 is driven and displaced from the initial position toward the operating position (see FIG. 11). In the present embodiment, as described above, the drain valve is not driven and displaced until the rotation of the case 196 is prevented.

  In this state, the input side transmission wheel 44 is connected to the output side transmission wheel 60 in a state where the stopper 268 of the rocking body 260 is engaged with the stopper protrusion 270 of the stopper gear 248 and the output side transmission pinion 62 is prevented from rotating. It can be rotated relative to. At that time, the transmission of torque from the electric motor 14 is maintained by the viscous resistance of the electrorheological fluid 76. As a result, the stopper 268 of the oscillator 260 is engaged with the stopper protrusion 270 of the stopper gear 248 so that the state in which the rotation of the case 196 is prevented is maintained.

  Then, when the drain valve is driven and displaced to the operating position, as shown in FIG. 7, the protruding piece 230 provided on the cam lever 220 is moved by the operation protrusion 234 provided on the intermediate wheel 174 to the intermediate wheel. 174 in the direction of rotation. As a result, the cam lever 220 is swung around the support shaft 218, and the extended end portion of the operation piece 224 of the cam lever 220 comes into contact with the boss portion 192 of the lower connecting member 178. As a result, as shown in FIG. 6, the lower connecting member 178 pushed up in the axial direction against the urging force of the coil spring 180 is pushed down in the axial direction by the urging force of the coil spring 180. It is done. Then, the engagement state between the engagement recess 188 of the upper connection member 176 and the engagement piece 194 of the lower connection member 178 is released, and the rotational driving force of the electric motor 14 is transmitted to the upper connection member 176. Will not be.

  There, the drain valve tries to start the return operation toward the initial position by the return force that it has. However, the transmission of torque based on the viscosity of the electrorheological fluid 76 as described above maintains the state in which the stopper portion 268 of the oscillator 260 is engaged with the stopper protrusion 270 of the stopper gear 248. Further, the locking claw 242 of the locking member 240 is locked to the locking claw 182 of the upper connecting member 176, and the upper connecting member 176 is prevented from rotating in the reverse direction. As a result, the connection pinion 210 provided on the driven body 198 constituting the planetary gear mechanism 172 is prevented from rotating in the reverse direction, and the drain valve can be held in the operating position (see FIG. 11). .

  And when predetermined time passes, the electric power feeding to the electric motor 14 is stopped. At that time, the application of the DC voltage between the pair of connection terminals 78a and 78b is also stopped. Thereby, torque transmission between the input side transmission wheel 44 and the output side transmission wheel 60 is not performed. As a result, the oscillating body 260 is oscillated toward the initial position by the urging force of the coil spring 266. When the rocking body 260 is in the initial position, the stopper portion 268 of the rocking body 260 is not engaged with the stopper protrusion 270 of the stopper gear 248. Thereby, the rotation of the rotation operation shaft 142 is allowed, and the rotation of the case 196 having the external gear 202 meshed with the speed adjusting pinion 140 provided on the rotation operation shaft 142 is also allowed. As a result, the reverse rotation prevention force of the upper connection member 176 obtained by the engagement of the engagement claw 242 of the engagement member 240 with the engagement claw 182 of the upper connection member 176 is transmitted to the slide lever 18. Disappear. The drainage valve is returned from the operating position to the initial position by the return force of itself.

  Then, when the drain valve starts returning operation, the protruding piece 230 of the cam lever 220 is released from the state in contact with the operation protruding portion 234 of the intermediate wheel 174, and as shown in FIG. 18 guide protrusions 232 are slidably contacted. As a result, the base end portion of the operation piece 224 is brought into contact with the boss portion 192 of the lower joint member 178. As a result, the lower connecting member 178 is pushed upward in the axial direction against the urging force of the coil spring 180, and the engaging recess 188 of the upper connecting member 176 and the engaging piece of the lower connecting member 178. 194 is engaged. When the drain valve is returned from the operating position to the initial position, the engaging recess 188 of the upper connecting member 176 and the engaging piece 194 of the lower connecting member 178 are engaged. Thereby, the positioning force (detent torque) of the rotor 34 by the magnetic force of the electric motor 14 is transmitted to the upper connecting member 176. As a result, the upper connecting member 176 is prevented from rotating in the reverse direction.

  Further, when the drain valve is returned from the operating position to the initial position, the connecting pinion 210 formed on the driven body 198 constituting the intermediate wheel 174 and the planetary gear mechanism 172 is rotated in the reverse direction. Since the rotation of the case 196 is permitted and the rotation of the connection pinion 186 (sun gear) in the reverse direction is prevented, the rotation of the case 196 is transmitted to the rotary operation shaft 142. It has become so. Then, by rotating the rotation operation shaft 142, each sliding body 150 spreads outward in the direction perpendicular to the axis of the rotation operation shaft 142 by the centrifugal force and is slid on the cylindrical sliding surface 158. As a result, the speed when the drain valve returns is adjusted.

  As is clear from the above description, in the present embodiment, the planetary gear mechanism 172 constitutes a mechanical clutch means. The mechanical clutch means (planetary gear mechanism 172) and the electrorheological fluid clutch means 165 (see FIG. 10) constitute a clutch means. In this embodiment, the input side transmission wheel 44 constitutes a drive side gear, and the output side transmission wheel 60 constitutes a transmission side gear.

  In the drainage valve driving geared motor 166 having such a structure, the rotational driving force of the electric motor 14 is transmitted to the oscillator 260 that connects and disconnects the planetary gear mechanism 172 as the mechanical clutch means. Since the electrorheological fluid type clutch means 165 is provided, it is possible to avoid deterioration of characteristics due to mechanical wear as compared with a geared motor using a conventional flywheel.

  As mentioned above, although several embodiment of this invention has been explained in full detail, these are illustrations to the last, Comprising: This invention is not limited at all by the specific description in this embodiment. .

  For example, in the first and second embodiments, an AC voltage may be applied between the pair of connection terminals 78a and 78b. Further, a pulse voltage may be applied between the pair of connection terminals 78a and 78b. In the case of applying a pulse voltage, it is possible to avoid a decrease in voltage when the voltage is continuously applied, and to prevent a dielectric breakdown from occurring inside the electrorheological fluid.

  In the first embodiment, the speed control mechanism 138 may not be provided. In this case, an appropriate voltage may be applied between the pair of connection terminals 78a and 78b to adjust the rotational speed of the output-side transmission wheel 60, thereby suppressing the speed during the return operation of the drain valve.

  Furthermore, in the first and second embodiments, a storage container 68 may be provided in the input side transmission wheel 44. In this case, the electrode positioned in the storage container 68 is provided in the output side transmission wheel 60.

  Furthermore, in the first and second embodiments, as shown in FIG. 12, annular rings 272 and 272 spaced apart in the axial direction are arranged so as to extend in the axial direction and line up in the circumferential direction. Alternatively, an input side electrode 276 (one electrode) having a structure in which the strip plates 274 are mutually connected may be employed. The band plate 274 does not need to extend in the axial direction, and may be inclined with respect to the axial direction, for example. Further, the annular ring 272 may be provided not only at both ends in the axial direction but also at an intermediate portion in the axial direction. That is, the input side electrode may have a lattice shape.

  Furthermore, in the first and second embodiments, the container 68 that does not include the connecting plate (74) may be employed.

  Furthermore, in the second embodiment, without using the stopper gear 248, a stopper protrusion is provided on the rotary operation shaft 142, and the stopper portion 268 of the oscillator 260 is engaged with the stopper protrusion of the rotation operation shaft 142. You may make it match.

  In addition, although not listed one by one, the present invention can be carried out in a mode to which various changes, modifications, improvements and the like are added based on the knowledge of those skilled in the art. It goes without saying that all are included in the scope of the present invention without departing from the spirit of the present invention.

The top view of the geared motor for the drain valve drive as 1st embodiment of this invention. The longitudinal cross-sectional explanatory drawing of the geared motor. The circuit diagram of the same geared motor. The graph which shows the operating state of a drain valve. The top view of the geared motor for the drain valve drive as 2nd embodiment of this invention. The longitudinal cross-sectional explanatory drawing of the geared motor. It is a top view which shows the positional relationship of a cam lever and a locking member, Comprising: The top view which shows the state which the operation protrusion part of the intermediate wheel contact | abutted to the protrusion piece of the cam lever. It is a top view which shows the positional relationship of a cam lever and a locking member, Comprising: The top view which shows the state which the guide protrusion of the slide lever contact | abutted to the protrusion piece of the cam lever. It is a top view of the geared motor shown in FIG. 5, Comprising: The top view which shows the state which the stopper part of the rocking | fluctuation body and the stopper protrusion of the stopper gear were engaged. FIG. 6 is a circuit diagram of the geared motor shown in FIG. 5. The graph which shows the operating state of a drain valve. The perspective view which shows the electrode employable in this invention.

Explanation of symbols

10: drainage valve drive geared motor, 14: electric motor, 16: reduction gear train, 18: slide lever, 44: input side transmission wheel, 52: input side electrode, 60: output side transmission wheel, 68: container 70: inner cylinder, 72: outer cylinder, 76: electrorheological fluid

Claims (3)

The output member is driven by an electric motor via a speed reducing means such as a gear train, and the drain valve as an operation target having a return force connected to the output member is driven and displaced from the initial position to the operating position. In the geared motor for driving the drainage valve which holds the drainage valve in the operating position and further allows the return operation of the drainage valve from the operating position to the initial position.
As a clutch means for transmitting / cutting off the driving force of the electric motor to the output member, an electrorheological fluid type clutch means using a change in viscosity of the electrorheological fluid based on a change in voltage applied to the electrorheological fluid is employed. A drainage valve drive geared motor characterized by   An input side gear to which the rotational driving force of the electric motor is constantly exerted and an output side gear for outputting the rotational driving force of the electric motor toward the output member are arranged coaxially, and the input side gear One electrode provided on the input side gear and extending in the circumferential direction in the electrorheological fluid accommodated in a container provided on one of the output side gears, and provided on the output side gear The other electrode which is extended in the circumferential direction and is opposed to the one electrode in the radial direction is applied to the electrorheological fluid by applying a voltage between the one electrode and the other electrode. By allowing the input side gear to transmit the rotational driving force of the electric motor to the output side gear, the voltage applied between the one electrode and the other electrode can be increased. Stop and reduce the viscosity of the electrorheological fluid 2. The drain valve according to claim 1, wherein the electrorheological fluid clutch means is constituted by preventing transmission of the rotational driving force of the electric motor from the input side gear to the output side gear. Drive geared motor.   Mechanical clutch means is provided on the transmission path of the driving force of the electric motor to the output member, while the rotational driving force of the electric motor is always on a path different from the transmission path of the driving force. A drive-side gear that is exerted, and a transmission-side gear that outputs the rotational driving force of the electric motor to a switching member that connects and disconnects the mechanical clutch means are arranged coaxially, and the drive-side gear and the gear Among the electrorheological fluids housed in a housing container provided on one of the transmission side gears, one electrode provided on the drive side gear and extending in the circumferential direction, and provided on the transmission side gear The electrorheological fluid type clutch means having a structure in which the other electrode that extends in the circumferential direction and is positioned opposite to the one electrode in the radial direction is provided, and the one electrode and the other electrode are provided Between the voltage By applying and increasing the viscosity of the electrorheological fluid, transmission of the rotational driving force of the electric motor from the drive side gear to the transmission side gear is allowed, and the switching member is replaced with the mechanical clutch means. Against the urging force exerted in the direction of cutting the mechanical clutch means, while driving the mechanical clutch means in the direction to connect, while stopping the application of voltage between the one electrode and the other electrode The direction in which the switching member disengages the mechanical clutch means by the biasing force by preventing the transmission of the rotational driving force of the electric motor from the driving side gear to the transmission side gear by reducing the viscosity of the fluid. 2. The drainage valve drive geared motor according to claim 1, wherein the clutch means is configured by allowing the displacement to be driven to the right.

Images