JP4603826B2 - Motor driven drain valve - Google Patents

Description

  The present invention relates to a motor-driven drain valve used in a washing machine, a dishwasher, or the like, and in particular, a separate geared motor is assembled to a valve housing in which a valve body is incorporated. The present invention relates to a motor-driven drain valve configured to switch a drainage channel formed in a valve housing between a communication state and a shut-off state by driving a valve body.

  Conventionally, a motor-driven drain valve has been employed in washing machines, dishwashers, and the like in order to switch a water storage tank between a water storage state and a drainage state. This drainage valve is generally manufactured by separately manufacturing a valve housing having a drainage channel incorporating a valve body and a geared motor for driving the valve body, and connecting the output shaft of the geared motor to the valve body. It is configured.

  However, the structure of the motor-driven drain valve having a conventional structure in which the valve housing and the geared motor are independently manufactured and separately fixed to the body of the washing machine with bolts or the like requires a large mounting space. There is a problem. In addition, there are a problem that the number of parts before assembly is increased and the management of the parts is troublesome, and a work for fixing each part is complicated and takes time.

  In order to cope with such a problem, for example, it is conceivable that the motor-driven drain valve has a unit structure by directly fixing the geared motor to the valve housing. One specific example is disclosed as a drain valve in Japanese Patent Application Laid-Open No. 2001-340693 (Patent Document 1).

  However, in the drainage valve described in Patent Document 1, a rotating cam is mounted on a rotation output shaft of a geared motor, and a connecting rod connected to a valve element is driven to reciprocate with the rotating cam. Therefore, in addition to the geared motor and the valve housing, it is necessary to prepare a rotating cam and a connecting rod, and it is inevitable that the number of parts will be further increased and the assembling work will be further complicated. Moreover, there is a problem that a relatively large working space for the rotating cam and the connecting rod is required between the geared motor and the valve housing, which is not satisfactory.

  Therefore, it is conceivable to employ a geared motor as described in Japanese Patent Application Laid-Open No. 2003-61306 (Patent Document 2) according to the prior application of the present applicant and to directly fix the geared motor to the valve housing. That is, such a geared motor is configured to drive the output rod in a linear direction by transmitting the rotational driving force of the electric motor to the output rod through a speed reduction means comprising a gear train and a rack and pinion mechanism. Yes.

  Accordingly, the drain valve can be driven by directly connecting the tip of the output rod to the valve body incorporated in the valve housing. Accordingly, the target motor-driven drain valve is more compact with a small number of parts, without requiring separate parts such as a rotating cam and a connecting rod, unlike the drain valve described in Patent Document 1 described above. It becomes feasible.

  Moreover, such a geared motor as described in Patent Document 2 is a so-called two-terminal type in which only two external power supply terminals are provided, and the internal motor is compared with the three-terminal type geared motor described in Patent Document 1. The electrical switching contact is not required. Therefore, even when the geared motor is assembled very close to the drain valve, the two-terminal type geared motor as described in Patent Document 2 that does not require an electrical contact is an electric device caused by water splashing or the like. There is also an advantage that malfunction is prevented and excellent reliability is ensured.

  However, when such a geared motor as described in Patent Document 2 is used and the tip of the output rod is connected to the valve body of the valve housing, there is a problem that the connection itself cannot be skillfully performed.

  That is, since the geared motor is a two-terminal type, a clutch mechanism is provided on the driving force transmission path between the electric motor and the output rod. The output rod is easily displaced by an external force without the detent torque of the electric motor acting. Therefore, for example, as in the connecting rod described in Patent Document 1, even if the tip of the output rod is pushed into the valve body and locked, the output rod is retracted when the pushing reaction force is exerted on the output rod. It will be very difficult to lock onto the valve body.

  In order to cope with this, it is conceivable to connect the tip of the output rod of the geared motor to the valve body by fixing it with a bolt, rivet, adhesive or the like, but generally the valve body is connected to the valve housing. Since it is built-in, it is very difficult to fix with bolts and the like, and it takes time to connect with an adhesive and it is difficult to obtain sufficient reliability.

JP 2001-340693 A JP 2003-61306 A

  Here, the present invention has been made in the background as described above, and the problem to be solved is to avoid an increase in the number of parts required for connecting the output member and the valve body, It is an object of the present invention to provide a motor-driven drain valve having a novel structure that can directly connect the valve body to the valve body.

  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. Further, aspects or technical features of the present invention are not limited to those described below, but are described in the entire specification, or invention ideas that can be understood by those skilled in the art from these descriptions. It should be understood that this is recognized on the basis of

In the first aspect of the present invention, a drainage channel is formed inside, and a valve body for communicating / blocking the drainage channel is positioned and incorporated at a blocking position of the drainage channel by a return biasing means. A valve housing and a pair of power supply terminals are provided, and the electric motor is rotationally driven by power feeding between the pair of power supply terminals, whereby the rotational driving force of the electric motor is output via a speed reduction means such as a gear train and a clutch means. A return operation preventing means for transmitting to the member and causing the output member to be retracted from the projecting position to the retracted position, and for preventing the output member from returning from the retracted position to the projecting position; In a state where the transmission of the rotational driving force from the output member is interrupted, the return operation preventing means prevents the return operation of the output member from the retracted position to the protruding position, thereby maintaining the output member in the retracted position. The geared motor, which is operated separately, is configured so as to allow the return operation to the output member by releasing the return operation prevention means by stopping the power supply between the pair of power supply terminals. A motor-driven drainage valve that is assembled and connected to the valve body of the valve housing by driving the output member of the geared motor and switching the drainage path between a communication state and a shut-off state by driving the valve body. A coupling means for locking the output member and the valve body so that they cannot be pulled out by pushing one of the output member and the valve body into the other in the projecting operation direction of the output member; and the geared motor Bei example, the cited write operation preventing means, and pull actuation blocking means for deter operation of the pull-in direction is provided et Re said output member is that it is releasable by operation from outside, especially To.

  In the motor-driven drain valve having such a structure, either the output member or the valve body is pushed into the other in the projecting operation direction of the output member so that the output member and the valve body cannot be pulled out. Since the connecting means for stopping is adopted, when connecting the output member and the valve body, one of the output member and the valve body is connected to the other without any special parts. The output member and the valve body can be directly connected by an extremely simple operation of pushing in the protruding operation direction.

  Therefore, in the motor-driven drain valve according to this aspect, the geared motor is provided with a pull-in operation preventing means that removably blocks the operation of the output member in the pull-in direction by an external operation. Thus, it is advantageously avoided that the output member is actuated in the retracting direction by a reaction force when one of the output member and the valve body is pushed into the other in the projecting operation direction of the output member.

  Therefore, in the motor driven drain valve according to this aspect, the valve body and the output member are directly connected even when the valve body is positioned and incorporated at the shut-off position of the drainage passage by the return biasing means. This can be easily realized, so that the geared motor and the valve housing can be assembled in a close state.

  According to a second aspect of the present invention, in the motor-driven drain valve according to the first aspect, the valve body includes a tapered cylindrical portion that gradually becomes smaller in diameter in the projecting operation direction of the output member. The tapered cylindrical portion is formed with at least one slit extending from the small diameter side opening end portion toward the large diameter side opening end portion, and the output member has a rod portion inserted into the tapered cylindrical portion. And a locking projection provided with a tapered cylindrical surface that gradually becomes smaller in diameter in the protruding operation direction of the output member at the protruding end of the rod portion, and the protrusion of the rod portion of the output member By pushing the end from the large-diameter side opening into the tapered cylindrical portion of the valve body and locking the large-diameter side end surface of the locking projection to the small-diameter side end surface of the tapered cylindrical portion, the connecting means It is composed of features and That. In the motor-driven drainage valve structured according to this embodiment, the rod part of the output member is provided with respect to the tapered tubular part that is provided in the valve body and gradually decreases in diameter in the projecting operation direction of the output member. The protruding end is pushed into the tapered cylindrical portion of the valve body from the large-diameter side opening, and has a tapered cylindrical surface that is formed at the protruding end of the rod portion and gradually decreases in diameter in the protruding operation direction of the output member. Since the connecting means is configured by locking the large-diameter side end surface of the locking projection to the small-diameter side end surface of the tapered tube portion, the protruding end of the rod portion of the output member is connected to the tapered tube portion of the valve body. When the rod portion is pushed in from the large-diameter side opening, the rod portion is guided by the tapered tube portion, so that, for example, even if the pushing direction of the rod portion with respect to the taper tube portion is deviated, Yo Due to the guide action of the rod part, it is possible to correct the deviation, and as a result, it is possible to advantageously realize the locking of the large-diameter side end face of the locking projection to the small-diameter side end face of the tapered cylindrical part. .

  Therefore, in the motor driven drain valve according to this aspect, the valve body and the output member are directly connected even when the valve body is positioned and incorporated at the shut-off position of the drainage passage by the return biasing means. Can easily be realized.

  Moreover, in this aspect, since the large-diameter side end surface of the locking projection provided with the tapered cylindrical surface is locked to the small-diameter side end surface of the tapered cylindrical portion, the rod portion of the output member protrudes. Even if the circumferential position of the rod portion with respect to the tapered cylindrical portion when the end is pushed into the tapered cylindrical portion of the valve body from the large-diameter side opening portion, the connection between the output member and the valve body is advantageously realized. It becomes possible.

  Furthermore, in this aspect, since at least one slit extending from the small diameter side opening end portion toward the large diameter side opening end portion is formed with respect to the tapered cylindrical portion, the protruding end of the rod portion of the output member is formed. When pushing into the tapered cylindrical portion of the valve body from the large-diameter side opening, the small-diameter side opening of the tapered cylindrical portion can be easily moved radially outward by the locking projection formed at the protruding end of the rod portion. As a result, the large-diameter side end surface of the tapered cylindrical portion can be advantageously locked to the small-diameter side end surface.

  A third aspect of the present invention is the motor-driven drain valve according to the first or second aspect, wherein in the pull-in operation preventing means, an external force due to an external operation is amplified by the speed reducing means. The output member is prevented from operating in the retracting direction by using the amplified external force. In such a motor-driven drain valve structured according to this aspect, the operation in the pull-in direction of the output member is prevented by utilizing the external force amplified by the speed reduction means and operated from the outside. Therefore, it is possible to advantageously ensure the force required to prevent the operation of the output member in the retracting direction.

  According to a fourth aspect of the present invention, in the motor-driven drain valve according to the third aspect, one of the speed reducing means is configured by a planetary gear mechanism, and the sun gear in the planetary gear mechanism is output from the electric motor. The planetary gear is rotationally driven by a shaft, and an output connecting gear is fixed on the center axis of the carrier on which the support shaft of the planetary gear meshed with the sun gear is fixed, and meshed with the sun gear The operation of the output member in the retracting direction by the pulling operation preventing means is prevented by preventing the rotation of the case having the internal gear with which the gear is engaged and blocking the transmission of the external force from the output member to the connecting gear. It is characterized by the fact that it is prevented. In the motor-driven drain valve structured according to this embodiment, since one of the speed reduction means is configured by a planetary gear mechanism, a large gear ratio can be set in a compact size. As a result, it is possible to more advantageously ensure the force required to prevent the output member from operating in the retracting direction.

  As is apparent from the above description, in the motor-driven drainage valve structured according to the present invention, either the output member or the valve body is pushed into the other in the projecting operation direction of the output member. A connecting means for locking the member and the valve body so as not to be pulled out is employed, and in the geared motor, there is provided a retracting operation preventing means for releasably blocking the operation of the output member in the retracting direction by an external operation. Therefore, it is advantageously avoided that the output member is actuated in the retracting direction due to a reaction force when either one of the output member or the valve body is pushed into the other in the projecting operation direction of the output member. In this state, the valve body is positioned and incorporated in the blocking position of the drainage channel formed inside the valve housing by the return biasing means. Even, to be connected becomes easily realized an output member and the valve body directly.

  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 motor-driven drain valve 10 for a washing machine as one embodiment of the present invention. This motor-driven drain valve 10 has a structure in which a geared motor 16 is fixedly assembled to a valve housing 14 in which a drain valve 12 as a valve body is incorporated.

  More specifically, as shown in FIGS. 3 and 4, the geared motor 16 has an electric motor 20, a reduction gear train 22 as a reduction means, and a rack lever as an output member with respect to the motor housing 18. 24 and the like are assembled. The motor housing 18 is superposed on the motor housing main body 26 having a substantially rectangular opening box shape as a whole, a partition plate 28 fitted in the opening of the motor housing main body 26, and the opening of the motor housing main body 26. The motor housing body 26, the partition plate 28, and the lid 30 are fixed to each other to form a hollow box structure having two internal spaces in the vertical direction. Yes. The electric motor 20 is accommodated in the lower internal space of the motor housing 18 having such a structure.

  The electric motor 20 is a conventionally known AC synchronous motor, and includes a stator 36 around which a rotor 32 and an annular coil 34 are wound. The rotor 32 has a structure in which an output shaft 40 is fixed to an annular block-shaped permanent magnet 38, and a rotor support shaft 42 erected on the central axis of the stator 36 in a central hole of the output shaft 40. It is extrapolated to be rotatable. The N and S magnetic poles magnetized in the circumferential direction on the outer peripheral surface of the permanent magnet 38 and the upper and lower magnetic pole portions 48 and 50 formed integrally with the upper and lower stator members 44 and 46 constituting the stator 36 are alternately connected to the coil 34. Based on the interaction with the N and S magnetic poles that are manifested by energization of the current, rotational torque and detent torque are exerted on the output shaft 40. Therefore, in the present embodiment, energization of the alternating current to the coil 34 is performed through a pair of power supply terminals 52 and 52. The electric motor 20 having such a structure is configured such that an output pinion 54 fixed to the output shaft 40 is positioned in the upper internal space when the electric motor 20 is assembled to the motor housing 18.

  Therefore, the output shaft 40 is formed with a locking claw 56, and in the vicinity of the locking claw 56, the locking claw 56 is locked to the locking claw 56 in one direction of rotation of the rotor 32. The lever 58 is arranged so as to be swingable around one axis. The locking claw 56 and the locking lever 58 constitute a reverse rotation prevention mechanism that defines the rotation direction of the rotor 32.

  The reduction gear train 22 includes a rotational force interrupting mechanism 60, a planetary gear mechanism 62, and an output wheel 64. The rotational force interrupting mechanism 60 includes an upper connecting member 66, a lower connecting member 68, and a coil spring 70. The upper connecting member 66 has a plate-like body portion, and the connecting pinion 72 projects from the upper surface of the upper connecting member 66, while there are a plurality (two in this embodiment) of locking recesses on the lower surface. 74 is formed. A plurality (four in this embodiment) of locking claws 76 are formed on the outer peripheral surface of the main body portion of the upper connecting member 66.

  The lower connection member 68 includes a connection gear 78 that meshes with the output pinion 54. Further, boss portions 80 and 82 projecting outward in the axial direction are formed on the upper and lower surfaces of the lower connecting member 68, respectively. Furthermore, a plurality of (two in this embodiment) cutout grooves 84 are formed around the upper boss portion 80 in the lower cutout member 68, and the upper cutout 84 is formed in the cutout grooves 84. A locking piece 86 that can be engaged with the locking recess 74 of the member 66 is formed to be elastically displaceable in the axial direction.

  The upper connecting member 66 and the lower connecting member 68 having such a structure are disposed so as to be overlapped with each other in the axial direction with the coil spring 70 interposed therebetween. Under the state in which the lower connection member 68 is arranged, the upper connection member 66 and the lower connection member 68 are elastically separated by the urging force of the coil spring 70 and are opposed to each other.

  Then, the upper connecting member 66 and the lower connecting member 68 are brought close to each other in the axial direction against the urging force of the coil spring 70, so that the locking recess 74 and the lower connecting member of the upper connecting member 66 are closed. In a state where the locking piece 86 of the member 68 is engaged, the upper connecting member 66 and the lower connecting member 68 are rotated together, thereby rotating the electric motor 20. The force is transmitted to the connection pinion 72 of the upper connection member 66. Therefore, in this embodiment, the engagement of the locking recess 74 of the upper connecting member 66 and the locking piece 86 of the lower connecting member 68 is maintained in the forward rotation direction of the electric motor 20. On the other hand, the ratchet structure is released in the reverse rotation direction.

  The planetary gear mechanism 62 includes a case 88 and a driven body 90. The case 88 has a bottomed cylindrical shape as a whole, and an internal gear 92 and an external gear 94 are formed on the inner peripheral surface and the outer peripheral surface of the cylindrical wall portion, respectively. On the other hand, the follower 90 includes upper and lower disks 96 and 98 as carriers which are opposed to each other in the axial direction, and the upper and lower disks 96 and 98 are They are fixed to each other by gear pins 100 as a plurality of support shafts protruding from the lower disk 98. Each of the plurality of gear pins 100 has a planetary gear 102 rotatably mounted around the gear pin 100. Furthermore, a connecting gear 104 is formed on the upper disk 96 so as to protrude upward.

  The follower 90 having such a structure is assembled into the case 88 by being fitted into the case 88. Under such a state that the follower 90 is fitted into the case 88, the planetary gear 102 is provided. And the internal gear 92 are meshed with each other. In addition, with the follower 90 fitted in the case 88 as described above, the case 88 is assembled so as to be superimposed on the upper cut-off member 66. Furthermore, in a state where the case 88 is assembled so as to be superimposed on the upper connecting member 66 in this way, the connecting pinion 72 formed on the upper connecting member 66 is attached to the bottom wall portion of the case 88. It is inserted through the formed through hole and is positioned in the case 88. The connection pinion 72 meshes with the planetary gear 102 in a state where the connection pinion 72 is inserted into the through hole formed in the bottom wall portion of the case 88 and positioned in the case 88 as described above. It is supposed to be squeezed. As apparent from this, in the present embodiment, the sun gear of the planetary gear mechanism 62 is constituted by the connection pinion 72.

  The output wheel 64 has a structure in which an output gear 106 and an output pinion 108 are integrally formed on the same axis, and the output gear 106 is meshed with the connecting gear 104. Further, the output wheel 64 is formed with a protrusion 110 protruding downward on the lower surface of the output pinion 108.

  The rack lever 24 has a rectangular section as a whole and has a shape that extends straight, and a rack 112 is formed over a predetermined length at one end in the longitudinal direction. The rack 112 formed on the rack lever 24 is meshed with the output pinion 108, whereby the rotational driving force of the electric motor 20 is applied to the rotational force interrupting mechanism 60, the planetary gear mechanism 62, and the output vehicle. It is transmitted to the rack lever 24 via 64.

  The rack lever 24 is integrally formed with a longitudinal plate-like guide protrusion 114 that projects downward on the lower surface of the portion where the rack 112 is formed. The rack lever 24 is assembled to the motor housing 18 in a state where the guide protrusions 114 are inserted into the guide holes 116 formed in the partition plate 28. In this state where the rack lever 24 is assembled to the motor housing 18, the other end portion in the longitudinal direction of the rack lever 24 is projected to the outside through a through hole 118 formed in the peripheral wall portion of the motor housing 18. . The rack lever 24 is thicker at the portion where the rack 112 is formed than the portion projected outside through the through hole 118, so that the guide protrusion 114 formed on the rack lever 24 is formed. When the rack lever 24 is slid by moving along the guide hole 116, the rack lever 24 is prevented from coming off from the through hole 118, and the moving end of the rack lever 24 on the protruding side is defined. It is like that.

  Therefore, in the present embodiment, the other end portion in the longitudinal direction of the rack lever 24, that is, the end portion that protrudes to the outside through the through hole 118 is the other side in the longitudinal direction with the cylindrical outer peripheral surface. A rod portion 120 is formed to protrude from the one side in the axial direction toward the other side, that is, as the rack lever 24 moves in the direction in which the rack lever 24 protrudes. The locking projection 124 provided with the tapered cylindrical surface 122 is arranged on the same central axis as the rod portion 120 so that the large-diameter side end surface 125 is superimposed on the protruding tip surface of the rod portion 120. Are integrally formed at the protruding end of the. In particular, in the present embodiment, the outer diameter of the large-diameter end of the locking projection 124 is sufficiently larger than the outer diameter of the rod portion 120, whereby the large-diameter side of the locking projection 124. The outer peripheral edge portion of the end face 125 exists with a substantially constant width dimension over the entire circumference. Incidentally, in this embodiment, a flat surface that extends in the direction perpendicular to the axis of the locking projection 124 is formed on the protruding end side of the locking projection 124, whereby the locking projection 124 is conical in this embodiment. It is trapezoidal.

  Further, a cam lever 126 is disposed below the output wheel 64 in an axial direction so as to be swingable around the support shaft 128. The cam lever 126 includes a sliding contact piece 130 that protrudes in a direction perpendicular to the oscillation center axis, and the protruding tip portion of the sliding contact piece 130 is engaged with the guide protrusion 114 of the rack lever 24. It has become.

  Furthermore, the cam lever 126 is formed with a protruding piece 132 that protrudes in a direction different from the sliding contact piece 130, and the protruding tip portion of the protruding piece 132 is substantially orthogonal to the protruding direction of the protruding piece 132. The operation piece 134 extending in the direction to be formed is integrally formed. The operation piece 134 is formed in a longitudinal plate shape as a whole, and a guide hole 136 extending in the longitudinal direction is formed at a central portion thereof. Further, the operation piece 134 is bent in a step shape in the plate thickness direction at the central portion in the longitudinal direction, whereby the distal end portion of the operation piece 134 is positioned below the base end portion. And the guide hole 136 of the operation part 134 is loosely inserted with respect to the planetary gear mechanism 62 and the support shaft 138 of the rotational force transmission mechanism 60, and the lower boss part of the lower connection member 68 on the upper surface of the operation piece 134. 82 is slidably contacted.

  Therefore, in the present embodiment, when the sliding contact piece 130 is engaged with the guide protrusion 114 of the rack lever 24, the lower boss portion 82 of the lower connecting member 68 is at the proximal end portion of the operation piece 134. The lower connecting member 68 is lifted toward the upper side of the support shaft 138 by being brought into contact with the supporting shaft 138, so that the engaging piece 86 of the lower connecting member 68 and the engaging recess of the upper connecting member 66 are retained. The point 74 is engaged, and the rotational driving force of the electric motor 20 is transmitted to the connection pinion 72. On the other hand, in a state where the sliding contact piece 130 is not engaged with the guide protrusion 114 of the rack lever 24, the lower boss portion 82 of the lower connecting member 68 is brought into contact with the distal end portion of the operation piece 134, The lower connecting member 68 is separated from the upper connecting member 66 by the urging force of the coil spring 70 and is positioned below, so that the locking piece 86 of the lower connecting member 68 and the upper piece The engagement of the locking recess 74 of the connecting member 66 is released so that the rotational driving force of the electric motor 20 is not transmitted to the connecting pinion 72. In the present embodiment, the sliding contact piece 130 is not engaged with the guide protrusion 114 when the rack lever 24 is at the retracted end.

  Further, as shown in FIG. 5, a locking lever 140 is disposed near the cam lever 126 so as to be swingable around a central axis parallel to the swing central axis of the cam lever 126. The locking lever 140 has a locking piece 142 extending in a direction perpendicular to the axis, and the locking piece 142 is locked to the locking claw 76 of the upper connecting member 66. Further, the locking lever 140 is formed with a protruding piece 144 at a position different from the circumferential position where the locking piece 142 is formed. The protruding piece 144 is adapted to be engaged with any one of the pair of protruding pieces 146 and 146 formed on the cam lever 126, whereby the locking lever 140 is moved against the swing of the cam lever 126. It is designed to be linked.

  Therefore, in this embodiment, when the sliding contact piece 130 of the cam lever 126 is engaged with the guide protrusion 114 of the rack lever 24, the locking piece 142 of the locking lever 140 is engaged with the upper connecting member 66. The upper pawl member 66 is not locked by the pawl 76, so that the upper connecting member 66 is allowed to rotate, while the sliding contact piece 130 of the cam lever 126 is engaged with the guide protrusion 114 of the rack lever 24. In the state where the locking lever 140 is not engaged, the locking piece 142 of the locking lever 140 is locked to the locking claw 76 of the upper connecting member 66, thereby preventing the upper connecting member 66 from rotating. It has come to be.

  A speed control mechanism 148 is disposed in the motor housing 18. The speed control mechanism 148 has a speed control pinion 150, and the speed control pinion 150 is meshed with an external gear 94 formed on the outer peripheral surface of the case 88 constituting the planetary gear mechanism 62. A speed control gear 152 is integrally formed above the speed control pinion 150 in the axial direction. Supporting pins 154 that protrude upward in the axial direction are fixed to the upper surface of the speed control gear 152 at a plurality of locations on the circumference. The slide body 156 having an arc-shaped block shape is assembled by being inserted by being inserted into the support pin 154 through an insertion hole formed at one end in the circumferential direction thereof. It can swing around 154.

  Each sliding body 156 spreads outward in the radial direction around the support pin 154 by the centrifugal force when the speed adjusting gear 152 is rotated. Thus, the sliding body 156 is caused by the centrifugal force. When spreading outward in the radial direction, the outer peripheral surface of the sliding body 156 comes into sliding contact with the inner peripheral surface of the cylindrical sliding cylinder portion 158 formed integrally with the lid 30, and as a result, The rotational speed of the speed adjusting gear 152 is adjusted. Therefore, in the present embodiment, a plurality of inner urging members 160 for holding the plurality of sliding bodies 156 at positions spaced inward from the sliding cylinder portion 158 in a state where centrifugal force is not working are provided. The sliding body 156 is assembled.

  In the motor housing 18, a stopper gear 162 that meshes with the speed control gear 152 is disposed in the vicinity of the speed control mechanism 148. A cylindrical outer peripheral surface 164 is formed below the stopper gear 162, and a locking projection 166 is formed so as to protrude radially outward from the cylindrical outer peripheral surface 164.

  Furthermore, a magnetic induction transmission mechanism 168 is disposed in the motor housing 18. The magnetic induction transmission mechanism 168 includes an input side induction pinion 170, and the input side induction pinion 170 is engaged with a transmission gear 172 that is engaged with the output pinion 108. In addition, above the input side induction pinion 170, an induction rotor 174 made of a permanent magnet is disposed so as to be superimposed on the upper surface of the input side induction pinion 170. A concave groove 176 extending continuously in the circumferential direction is formed on the lower surface of the induction rotor 174, whereby a projection 178 protruding downward is formed at the center of the lower surface of the induction rotor 174. A winding spring 180 is wound around the protrusion 178. One end of the coil spring 180 is brought into contact with a contact piece 182 formed in the concave groove 176 of the induction rotor 174, and the other end of the coil spring 180 is in the concave groove 176 of the induction rotor 174. And is brought into contact with a contact piece 184 protruding from the input-side induction pinion 170. Then, the rotation of the input side induction pinion 170 that is rotationally driven by the rotational driving force of the electric motor 20 transmitted through the transmission gear 172 is buffered by the winding spring 180 and transmitted to the induction rotor 174. ing.

  In addition, a guide ring 186 having a substantially reverse cup shape is disposed so as to cover the induction rotor 174, and the rotational driving force of the induction rotor 174 is induced by magnetic induction between the induction rotor 174 and the induction ring 186. By being transmitted to the ring 186, the guide ring 186 is rotated in the same direction as the guide rotor 174. As a result, the output-side induction pinion 188 provided so as to protrude outward in the axial direction on the central axis of the upper bottom portion of the induction ring 186 is rotated in the same direction as the induction rotor 174.

  Furthermore, an oscillating body 190 is disposed near the magnetic induction type transmission mechanism 168. The oscillating body 190 has a substantially sector shape extending around the oscillating central axis, and an output side induction pinion 188 is meshed with a locking tooth 192 formed on an arcuate outer peripheral surface. Further, a locking piece 194 is formed on the upper surface on the outer side of the rocking body 190 so as to protrude upward. The rocking body 190 is rocked by a coil spring 196 locked to the locking piece 194. A return force in one direction of movement is applied.

  Furthermore, a locking portion 198 that protrudes in the direction of rotation opposite to the direction in which the restoring force is applied by the coil spring 196 is integrally formed at one end edge in the circumferential direction of the rocking body 190. When 190 is rotated against the restoring force of the coil spring 196, the locking portion 198 is locked to the locking protrusion 166 formed on the stopper gear 162. Thereby, the rotation of the speed adjusting gear 152 meshed with the stopper gear 162 is prevented, and the rotation of the case 88 having the external gear 94 meshed with the speed governing pinion 150 formed integrally with the speed controlling gear 152 is prevented. It has come to be. In the state where the rocking body 190 is in the initial position, the locking portion 198 does not interfere with the locking protrusion 166 of the stopper gear 162 that is rotated.

  As is clear from this, in the present embodiment, the rotation of the case 88 constituting the planetary gear mechanism 62 is performed in a state where the locking portion 198 of the rocking body 190 is locked to the locking protrusion 166 of the stopper gear 162. On the other hand, when the locking portion 198 of the rocking body 190 is not locked to the locking protrusion 166 of the stopper gear 162, the rotation of the case 88 constituting the planetary gear mechanism 62 is allowed. Yes.

  In the present embodiment, an insertion hole 200 is formed in the peripheral wall portion of the motor housing 18 near the rocking body 190, and an operation rod 202 is inserted into the insertion hole 200. Then, by pressing the operating rod 202 from the outside of the motor housing 18, the operating rod 202 is brought into contact with the rocking body 190, so that the rocking body 190 is rocked. ing. Therefore, in this embodiment, the coil spring 204 is extrapolated with respect to the operation rod 202, and when the force for pressing the operation rod 202 is released thereby, the operation rod 202 is The coil spring 204 returns to the initial position by the return force. Further, when the operating rod 202 returns to the initial position in this way, the swinging body 190 also returns to the initial position by the return force of the coil spring 196.

  In the present embodiment, the support shaft 138 of the rotational force interrupting mechanism 60 and the planetary gear mechanism 62, the support shaft 128 of the output wheel 64 and the cam lever 126, the support shaft 206 of the locking lever 56 and the transmission gear 172, and the speed control mechanism. The support shaft 208 of 148, the support shaft 210 of the stopper gear 162, the support shaft 212 of the magnetic induction transmission mechanism 168, the support shaft 214 of the rocking body 190, and the support shaft of the locking lever 140 are all divided into the partition plate 28 and the lid. 30. Each support shaft is parallel to the rotor support shaft 42 of the electric motor 20.

  The valve housing 14 to which the geared motor 16 having such a structure is fixedly assembled has a bottomed cylindrical shape as a whole, and a first water inlet 216 is formed at the bottom. A second water inlet 218 is formed in the peripheral wall near the bottom. The first water inlet 216 is connected to a water storage tank such as a washing tub of a washing machine, for example, while the second water outlet 218 is connected to the outside. In other words, in this embodiment, the drainage passage 220 is formed in the valve housing 14 with the first water inlet 216 as one end and the second water outlet 218 as the other end.

  The mounting cylinder 222 is assembled to the opening end of the valve housing 14 having such a structure. The mounting cylinder 222 has a shape that extends straight in the axial direction with an inner diameter that is slightly larger than the outer diameter of the valve housing 14. In addition, the mounting cylinder 222 is integrally formed with an annular flange 224 that protrudes inward on one axial side.

  The mounting cylinder 222 is extrapolated from one side in the axial direction to the opening end side of the valve housing 14, and the mounting cylinder 222 is extrapolated to the opening end side of the valve housing 14 in this way. Under the state, the locking projection 228 formed on the outer peripheral surface on the opening end side of the valve housing 14 is locked in the locking hole 226 formed on one side of the mounting cylinder 222 in the axial direction. The mounting cylinder 222 is fixedly assembled to the valve housing 14. Further, the geared motor 16 is fixed to the other axial side of the mounting cylinder 222 in a state of being housed on the other axial side of the mounting cylinder 222 by the mounting screw 230 and the mounting piece 232. It is like that.

  In this way, the drain valve 12 is accommodated between the bottom surface of the valve housing 14 and the facing surface of the inner flange 224 of the mounting cylinder 222 under the state where the mounting cylinder 222 is fixedly assembled to the opening end side of the valve housing 14. It is positioned. The drain valve 12 includes a slider 234 and a valve body 236. The slider 234 has a thin cylindrical shape as a whole, and an annular locking piece 238 protruding outward in the radial direction is formed at one end in the axial direction. In addition, at the other end of the slider 234 in the axial direction, a tapered cylindrical portion 240 that gradually increases in diameter from one side to the other in the axial direction has an end on the large diameter side at the other end in the axial direction of the slider 234. In an integrally formed state, the slider 234 is integrally formed so as to be positioned inside the slider 234. Therefore, in this embodiment, slits 242 extending toward the large-diameter side opening end are formed at the small-diameter side opening end of the tapered cylindrical portion 240 at a plurality of locations on the circumference, thereby The small-diameter side opening end portion of the tapered cylindrical portion 240 can be deformed radially outward.

  On the other hand, the valve body 236 has a lateral cup shape, and an abutting rib 244 that protrudes outward in the axial direction is formed on the outer peripheral edge of the bottom portion of the valve main body 236 over the entire circumference. Further, a locking groove 246 that opens to the inner peripheral surface is formed in the peripheral wall portion of the valve body 236, and the locking piece 238 of the slider 234 is fitted into the locking groove 246, whereby the slider 234 is fitted. And the valve body 236 are movable together. Furthermore, a bellows-like seal cylinder 248 is integrally formed on the opening end side of the valve body 236 so as to cover the slider 234, and on the opening end side of the bellows-like seal cylinder 248, An annular flange portion 250 extending outward in the radial direction is integrally formed. In a state where the mounting cylinder 222 is fixedly assembled to the valve housing 14, the flange portion 250 is held between the outer peripheral edge portion of the inner flange 224 and the open end of the valve housing 14. This prevents water from entering the inner peripheral side of the seal cylinder 248.

  Furthermore, the coil spring 252 as the return biasing means is inserted into a cylindrical guide portion 254 formed on the inner flange 224 between the opposing surfaces of the locking piece 238 of the slider 234 and the inner flange 224. It is arranged. In this embodiment, the coil spring 252 disposed between the opposing surfaces of the inner flange 224 and the locking piece 238 is compressed in the axial direction, whereby the slider 234 and the drain valve 12 are extended. On the other hand, the urging force to the bottom side of the valve housing 14 is always exerted.

  Then, the manufacturing method of the motor drive type drain valve 10 made into the above structures is demonstrated. First, the valve main body 236 to which the slider 234 is integrally attached is placed in the valve housing 14, and then the attachment cylinder body with the coil spring 252 located between the inner flange 224 and the locking piece 238. 222 is fixedly assembled to the opening end side of the valve housing 14.

  Subsequently, the geared motor 16 is accommodated at the other side in the axial direction of the mounting cylinder 222 in a state where the operating rod 202 is pressed, and the rack lever 24-is connected to the slider 234, and the mounting piece 232 and mounting screw are connected. The geared motor 16 is fixed to the mounting cylinder 222 by 230. At this time, since the operating rod 202 is pressed, the rocking body 190 is swung to one side in the circumferential direction, and the locking formed on the rocking body 190 as shown in FIG. The portion 198 is pressed against the cylindrical outer peripheral surface 164 or the locking projection 166 formed below the stopper gear 162, thereby preventing the stopper gear 162 from rotating. ing. In FIG. 6, the coil spring 196 is not shown.

  Further, since the rotation of the stopper gear 162 is prevented in this way, the rotation of the speed adjusting gear 152 meshed with the stopper gear 162 is blocked, and the speed adjusting gear that is rotated integrally with the speed adjusting gear 152. The rotation of the pinion 150 is prevented, and as a result, the rotation of the case 88 including the external gear 94 meshed with the governing pinion 150 is prevented.

  Therefore, in the present embodiment, when the rack lever 24 is not at the retracted end in a state in which the rotation of the case 88 is thus prevented, that is, when the sliding contact piece 130 is engaged with the guide protrusion 114, The lower connecting member 68 is pushed upward in the axial direction against the restoring force of the coil spring 70 by the base end portion of the operation piece 134 of the cam lever 126, and the locking piece 86 of the lower connecting member 68 is moved upward. By being locked in the locking recess 74 of the cutting member 66, the rotation of the upper connecting member 66 is prevented by the detent torque of the electric motor 20. Thereby, the rotation of the driven body 90 fitted in the case 88 is prevented, and the sliding operation of the rack lever 24 including the rack 112 meshed with the connecting gear 104 constituting the driven body 90 is blocked. ing. In the present embodiment, the slider 234 is positioned at a position separated from the inner flange 224 by the biasing force of the coil spring 252, so that the rack lever 24 is positioned at the protruding end. It is desirable to prevent the sliding operation of the rack lever 24 by pressing the operation rod 202, whereby it is possible to advantageously secure the protruding length of the rack lever 24 from the motor housing 18.

  Thus, under the state in which the sliding operation of the rack lever 24 is prevented, the protruding end of the rod portion 120 formed on the rack lever 24 has a large-diameter side opening portion with respect to the tapered tube portion 240 formed on the slider 234. It can be pushed in. At that time, since the tapered cylindrical portion 240 gradually becomes smaller in diameter in the protruding operation direction of the rack lever 24, the locking projection 124 formed on the protruding end of the rod portion 120 is formed on the tapered cylindrical portion 240. Guided by the inner surface.

  Then, the locking projection 124 expands the small-diameter-side opening end portion of the tapered cylindrical portion 240 in which the slit 242 is formed, and then the locking projection 124 is more axially outward than the small-diameter-side end portion of the tapered cylindrical portion 240. Accordingly, the outer peripheral edge portion of the large-diameter side end surface 125 of the locking projection 124 is locked to the small-diameter side end surface 241 of the tapered tube portion 240. Thereby, the rack lever 24 is prevented from coming off from the slider 234, and the rack lever 24 and the slider 234 are connected.

  After the rack lever 24 and the slider 234 are connected in this manner, the pressing operation of the operating rod 202 is stopped, whereby the swinging body 190 is swung by the return force of the coil spring 196, and the locking portion of the swinging body 190 is engaged. The state where 198 is pressed against the cylindrical outer peripheral surface 164 or the locking projection 166 of the stopper gear 162 is released. Accordingly, the rotation of the stopper gear 162 is allowed and the rotation of the speed adjusting gear 152 meshed with the stopper gear 162 is allowed. As a result, the speed adjusting pinion that is rotated integrally with the speed adjusting gear 152. The rotation of 150 is allowed, and the rotation of the case 88 including the external gear 94 meshed with the speed adjusting pinion 150 is allowed, and the state where the sliding operation of the rack lever 24 is prevented is released.

  Next, the operation of the motor driven drain valve 10 having the above-described structure will be described. First, in an initial state where the electric motor 20 is not supplied with power, the drain valve 12 is in a position where the drain passage 220 formed in the valve housing 14 is blocked by the urging force of the coil spring 252, and the rack lever 24 is moved to the motor. It is positioned at the protruding end from the housing 18. Under such an initial state, when power is supplied to the electric motor 20, the rotor 32 is rotated.

  When the rotor 32 is rotated from the initial state, the sliding contact piece 130 of the cam lever 126 is in contact with and engaged with the guide protrusion 114 of the rack lever 24 as shown in FIG. The lower connecting member 68 is pushed upward in the axial direction against the restoring force of the coil spring 70 by the proximal end portion of the operation piece 134 in the cam lever 126, and the locking piece 86 of the lower connecting member 68 is moved upward. By being locked in the locking recess 74 of the cutting member 66, the rotational force cutting mechanism 60 is in a connected state.

  Here, the locking piece 142 of the locking lever 140 is not locked to the locking claw 76 of the upper connecting member 66, thereby allowing the upper connecting member 66 to rotate.

  Further, the rotational driving force of the electric motor 20 is transmitted to the magnetic induction transmission mechanism 168 via the transmission gear 172 and is engaged with the output side induction pinion 188 constituting the magnetic induction transmission mechanism 168. The oscillating body 190 provided with is rotated in the direction opposite to the rotation direction of the stopper gear 162 against the restoring force of the coil spring 196. As a result, the locking portion 198 formed on the rocking body 190 is locked to the locking protrusion 166 formed on the stopper gear 162, and the rotation of the speed control gear 152 engaged with the stopper gear 162 is prevented. As a result, the rotation of the case 88 including the external gear 94 meshed with the speed control pinion 150 that is rotated integrally with the speed control gear 152 is prevented.

  By preventing the rotation of the case 88 in this way, the rotational driving force of the electric motor 20 is transmitted to the rack lever 24 via the rotational force interrupting mechanism 60, the planetary gear mechanism 62 and the output wheel 64, and the rack lever. 24 is operated to be retracted from the protruding position toward the retracted position. Thereby, the drain valve 12 connected to the rack lever 24 resists the urging force of the coil spring 252 and the first water inlet 216 and the first water inlet 216 from the blocking position where the first water inlet 216 is covered by the drain valve 12. The second water outlet 218 is driven and displaced toward the open communication position. As a result, the drainage channel 220 formed in the valve housing 14 is switched from the shut-off state to the communication state.

  In this state, under the state where the locking portion 198 of the rocking body 190 is locked by the locking protrusion 166 formed on the stopper gear 162 and the rotation of the output side guide pinion 188 is prevented, the induction rotor 174 It can be rotated relative to the ring 186. At that time, the transmission of torque from the electric motor is maintained by the magnetic induction action between the induction rotor 174 and the induction ring 186, so that the locking portion 198 of the oscillator 190 becomes a stopper gear. The state of being latched by the latching protrusion 166 formed on 162 is held.

  When the drain valve 12 is driven and displaced to the communication position, the sliding contact piece 130 of the cam lever 126 is pushed in the rotation direction of the output wheel 64 by the projection 110 of the output wheel 64, thereby rotating the cam lever 126. It is rotated around the central axis, resulting in a state as shown in FIG. As a result, the distal end portion of the operation piece 134 in the cam lever 126 is brought into contact with the lower boss portion 82, and as a result, the lower joint that has been pushed up in the axial direction against the urging force of the coil spring 70. The cutting member 68 is pushed downward in the axial direction by the urging force of the coil spring 70, and the engagement state between the locking recess 74 of the upper connecting member 66 and the locking piece 86 of the lower connecting member 68 is released. Thus, the rotational driving force of the electric motor 20 is not transmitted to the connecting gear 104.

  The drain valve 12 tries to start the return operation toward the shut-off position by the biasing force of the coil spring 252, but the torque based on the magnetic induction action between the induction rotor 174 and the induction ring 186 as described above. , The state in which the locking portion 198 of the rocking body 190 is locked to the locking protrusion 166 formed on the stopper gear 162 is maintained, and the locking lever 140 is rocked in conjunction with the cam lever 126. As a result, the locking piece 142 of the locking lever 140 is locked to the locking claw 76 of the upper connecting member 66 so that the upper connecting member 66 is prevented from rotating in the reverse direction. . As a result, the connecting gear 104 is prevented from rotating in the reverse direction, and the drain valve 12 can be held in the communication position.

  When the supply of power to the electric motor 20 is stopped after a predetermined holding time has elapsed, the magnetic pole portions 48 and 50 that form the magnetic poles of the permanent magnet 38 and the magnetic poles of the stator 36 provided on the rotor 32. The magnetic force between the rotor 32 and the rotor 36 acts as a braking force against the rotation of the rotor 32. As a result, the rotor 32 has the inertial force of the rotor 32 itself, the magnetic poles of the permanent magnet 38 provided on the rotor 32, and the stator 36. Rotate to a position balanced with the magnetic force exerted between the magnetic pole portions 48 and 50, and stop once. Thereafter, the rotor 32 rotates in the reverse direction based on the magnetic attractive action of the permanent magnet 38 and the stator 36 due to the absence of the inertial force, and reaches a stable position based on the magnetic attractive action of the permanent magnet 38 and the stator 36. Come back and stop.

  In this way, when the rotor 32 rotates in the positive direction until the rotor 32 is braked in the positive direction and temporarily stops, the stopper in the locking portion 198 of the oscillating body 190 is based on the magnetic induction action between the induction rotor 174 and the induction ring 186. The locked state of the gear 162 to the locking projection 166 is maintained.

  On the other hand, at the time of reverse rotation after the rotor 32 is temporarily stopped, the induction rotor 174 is rotated in the reverse direction in accordance with the reverse rotation operation of the input side induction pinion 170 by the rotor 32, and between the induction rotor 174 and the induction ring 186. Due to the magnetic induction action, the rocking body 190 can be swung in the reverse direction. As a result, the locking portion 198 of the oscillating body 190 is not locked to the locking protrusion 166 of the stopper gear 162, and the rotation of the speed adjusting gear 152 is allowed and the external teeth meshed with the speed adjusting pinion 150. The rotation of the case 88 having the gear 94 is also permitted. As a result, the reverse rotation preventing force of the upper connecting member 66 obtained by the engaging piece 142 of the engaging lever 140 being engaged with the engaging claw 76 of the upper connecting member 66 is transmitted to the rack lever 24. The drain valve 12 is returned from the communication position to the shut-off position by the urging force of the coil spring 252. Thereby, the drainage channel 220 formed in the valve housing 14 is switched from the communication state to the cutoff state.

  Accordingly, when the return operation of the drain valve 12 is started, the positioning of the cam lever 126 by the projection 110 of the output wheel 64 is released, and the guide projection 114 of the rack lever 24 is moved by the cam lever 126 as shown in FIG. By engaging with the sliding contact piece 130, the base end portion of the operation piece 134 is brought into contact with the lower boss portion 82, and the lower connecting member 68 is used as the return force of the coil spring 70. As a result, it is pushed upward in the axial direction, and the engaging recess 74 of the upper connecting member 66 and the engaging piece 86 of the lower connecting member 68 are engaged. As a result, when the drain valve 12 is returned from the communication position to the shut-off position, the locking recess 74 of the upper connecting member 66 and the locking piece 86 of the lower connecting member 68 are engaged, and the electric motor The positioning force (detent torque) of the rotor 32 due to the magnetic force of 20 is transmitted to the upper connecting member 66, thereby preventing the upper connecting member 66 from rotating in the reverse direction.

  Further, when the drain valve 12 is returned from the communication position to the shut-off position, the output wheel 64 and the connecting gear 104 formed on the driven body 90 constituting the planetary gear mechanism 62 are rotated in the reverse direction. However, since the rotation of the case 88 is allowed and the rotation of the connection pinion 72 (sun gear) in the reverse direction is prevented, the rotation of the case 88 is transmitted to the governing pinion 150. As a result, the speed adjusting pinion 150 is rotated. Then, when the speed adjusting pinion 150 is rotated, the speed adjusting gear 152 that is rotated integrally with the speed adjusting pinion 150 is rotated, so that each sliding body 156 is radially outward around the support pin 154 by centrifugal force. The speed at the time of the return operation of the drain valve 12 is adjusted by spreading in the direction and being brought into sliding contact with the inner peripheral surface of the sliding cylinder portion 158.

  As is clear from the above description, in this embodiment, the locking recess 74 of the upper connecting member 66 and the locking piece 86 of the lower connecting member 68, and the locking protrusion 166 of the stopper gear 162. Clutch means is constituted by the locking portion 198 of the rocking body 190. The engaging recess 74 of the upper connecting member 66 and the engaging piece 86 of the lower connecting member 68 are engaged, and the engaging member 190 is engaged with the engaging protrusion 166 of the stopper gear 162. While the stop portion 198 is locked and the rotation of the case 88 is prevented, the clutch is engaged. On the other hand, the locking recess 74 of the upper connecting member 66 and the lower connecting member 68 are connected. When the engagement of the locking piece 86 is released, or the locking portion 198 of the swinging body 190 is released from the locking projection 166 of the stopper gear 162 and the rotation of the case 88 is allowed. As a result, the clutch is disengaged.

  Further, in the present embodiment, the locking portion 198 of the swinging body 190 is locked to the locking protrusion 166 of the stopper gear 162 to prevent the rotation of the case 88, and the locking at the lower connecting member 68 is also performed. The engagement of the stop piece 86 with the engaging recess 74 in the upper connecting member 66 is released, and the engaging piece 142 of the engaging lever 140 is engaged with the engaging claw 76 of the upper connecting member 66. By doing so, a return operation preventing means is configured. Furthermore, in the present embodiment, the outer peripheral edge portion of the large-diameter side end surface 125 of the locking projection 124 is locked to the small-diameter side end surface 241 of the tapered tube portion 240 to constitute a connecting means. Furthermore, in this embodiment, the rocking body 190 is rocked against the restoring force of the coil spring 196 by the pressing operation of the operating rod 202, and the locking portion 198 of the rocking body 190 is the cylindrical shape of the stopper gear 162. The case 88 is prevented from rotating due to being pressed against the outer peripheral surface 164 or the locking projection 166, thereby constituting a pull-in operation preventing means.

  In the motor-driven drain valve 10 having such a structure, the protruding end of the rod portion 120 of the rack lever 24 is pushed into the tapered cylindrical portion 240, and the locking projection 124 formed on the protruding end of the rod portion 120. Since the large-diameter side end surface 125 is locked to the small-diameter side end surface 241 of the tapered cylindrical portion 240, the rack lever 24 and the slider 234 (valve element 12) are locked and connected so that they cannot be pulled out. The rack lever 24 and the slider 234 (valve element 12) can be directly connected without using other members.

  In particular, the connection between the rack lever 24 and the slider 234 (valve element 12) is realized by an extremely simple structure in which the large-diameter side end surface 125 of the locking projection 124 is locked to the small-diameter side end surface 241 of the tapered cylindrical portion 240. Therefore, it is possible to improve the reliability of the connection between the rack lever 24 and the slider 234 (valve body 12). Further, the connecting operation of the rack lever 24 and the slider 234 (valve body 12) is facilitated, and the connecting operation of the rack lever 24 and the slider 234 (valve body 12) can be performed quickly.

  Furthermore, the operation of the rack lever 24 in the retracting direction due to the reaction force when the protruding end of the rod portion 120 of the rack lever 24 is pushed into the tapered tube portion 240 is prevented based on the pressing operation of the operation rod 202. Therefore, it is possible to easily realize the connection between the rack lever 24 and the slider 234 (valve body 12).

  Therefore, in the motor-driven drain valve 10 of the present embodiment, the slider 234 (valve element 12) is positioned and incorporated in the blocking position of the drain passage 220 formed in the valve housing 14 by the coil spring 252. Even in this case, it is possible to easily connect the rack lever 24 and the slider 234 (drainage valve 12) directly.

  Further, the rack lever 24 and the slider 234 (valve body 12) are directly connected in such a state that the slider 234 (valve body 12) is positioned at the blocking position of the drainage passage 220 formed in the valve housing 14 by the coil spring 252. Since the geared motor 16 and the valve housing 14 can be assembled close to each other, the overall size of the motor driven drain valve 10 can be made compact.

  Furthermore, by allowing the geared motor 16 and the valve housing 14 to be assembled close to each other, the geared motor can be attached to the valve housing 18 and, moreover, the mounting position of the motor-driven drain valve 10 on the washing machine body or the like. As a result, the load exerted on the attachment position of the motor-driven drain valve 10 to the washing machine main body or the like due to the displacement of the geared motor 18 due to, for example, vibration in the dehydration process of the washing machine or the like. Can be reduced, and durability against vibration can be ensured.

  Furthermore, in this embodiment, by stopping the pressing operation of the operating rod 202, the operating rod 202 is returned to the initial position by the return force of the coil spring 204, and the swinging body 190 is returned to the return force of the coil spring 196. The state where the locking portion 198 of the swinging body 190 is pressed against the cylindrical outer peripheral surface 164 or the locking projection 166 of the stopper gear 162 is released. It is possible not to adversely affect the operation of the motor 16.

  Further, in the motor-driven drain valve 10 of the present embodiment, power is supplied to the electric motor 20 constituting the geared motor 16 through a pair of power supply terminals 52, 52, so-called three terminals. Compared to the type of geared motor, an internal electrical switching contact is not required, and the overall size of the geared motor 16 can be made compact. Furthermore, since an internal electrical switching contact is not required, an electrical malfunction due to water spattering or the like is prevented, whereby the geared motor 16 is very close to the valve body 12. Even if it is provided, it is possible to ensure stability and reliability with respect to the operation of the rack lever 24.

  Further, in the motor driven drain valve 10 of the present embodiment, since the geared motor 16 is provided with a rack lever 24 that is operated linearly, a rotary cam is attached to the rotational output shaft of the geared motor, and the valve Compared to the case where the connecting rod connected to the body is driven back and forth by the rotating cam, it is not necessary to prepare a rotating cam or connecting rod. As a result, an increase in the number of parts can be avoided, and the assembly work of the geared motor 16 and the valve housing 14 can be simplified.

  In this embodiment, a rack lever 24 that is linearly driven is employed as the output member, and the end of the rack lever 24 on which the rod portion 120 is not formed is in the motor housing 18. Compared to the case where a rotary cam is attached to the rotary output shaft of the geared motor outside the geared motor and the connecting rod connected to the valve element is driven back and forth by the rotary cam. The operating space outside the geared motor 16 when the body 12 is displaced can be reduced.

  Further, in the present embodiment, since screws are not used to connect the rack lever 24 and the slider 234, for example, when the motor-driven drain valve 10 of the present embodiment is used in a household washing machine, the dehydration process. It is possible to advantageously avoid the problem that the screw is loosened due to the vibration at this point, and thereby the connection state between the rack lever 24 and the slider 234 is released.

  Furthermore, in this embodiment, since the rack lever 24 is reciprocated between the protruding position and the retracted position, the rack lever is mainly used with respect to the small-diameter side end of the tapered cylindrical portion 240. An external force is exerted in the 24 reciprocating operation directions. Thereby, in particular, it becomes possible to make it difficult for external force to be exerted on the small diameter side end of the tapered cylindrical portion 240 in a direction in which the small diameter side end of the tapered cylindrical portion 240 is expanded. As a result, the connected state of the rack lever 24 and the slider 234 (drain valve 12) can be stably maintained over a long period of time.

  Further, in the present embodiment, the locking protrusion 124 includes the tapered cylindrical surface 122 that gradually becomes smaller in diameter in the protruding operation direction of the rack lever 24, so that the protruding end of the rod portion 120 can be easily pushed. It becomes possible.

  As mentioned above, although one Embodiment of this invention was explained in full detail, this is an illustration to the last, Comprising: This invention is not limited at all by the specific description in this Embodiment.

  For example, in the above-described embodiment, the operation rod 202 is arranged on the geared motor 16, and the slide operation of the rack lever 24 is prevented by pressing the operation rod 202. Without inserting the rod 202, only the insertion hole is formed in the peripheral wall portion of the motor housing 18, and only when the sliding operation of the rack lever 24 is prevented, a finger or an operation rod is inserted from the insertion hole to The moving body 190 may be swung to prevent the rack lever 24 from sliding. Further, the rotation of the case 88 may be directly prevented.

  Furthermore, the shape of the rod projection 120, the locking projection 124 formed at the tip of the rod portion 120, the tapered tube portion 240, and the like are not limited to those of the above embodiment.

  Further, the structure of the reduction gear train, the number of gears constituting the reduction gear train, and the like are not limited to those of the above embodiment. Furthermore, the number and specific shape of the coils of the electric motor are not limited to those of the above embodiment.

  In addition, although not enumerated 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.

It is sectional drawing which shows the motor drive type drain valve as one Embodiment of this invention, Comprising: It is drawing equivalent to the II direction in FIG. It is II-II sectional drawing in FIG. FIG. 2 is an assembly explanatory diagram of a part of a geared motor employed in the motor-driven drain valve shown in FIG. 1. It is assembly explanatory drawing of the other part of the geared motor employ | adopted as the motor driven drain valve shown by FIG. It is a top view for demonstrating the latching lever which comprises the geared motor shown by FIG. It is a top view for demonstrating the state by which the latching | locking part of the rocking body was pressed on the cylindrical outer peripheral surface of the stopper gear. It is a top view for demonstrating the operating state of the cam lever which comprises a geared motor. It is a top view for demonstrating the other operating state of the cam lever which comprises a geared motor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Motor drive type drain valve 12 Drain valve 14 Valve housing 16 Geared motor 20 Electric motor 22 Reduction gear train 24 Rack lever 120 Rod part 124 Locking protrusion 220 Drain passage 252 Coil spring

Claims (4)

A valve housing in which a drainage channel is formed, and a valve body that communicates / blocks the drainage channel is positioned and incorporated at a blocking position of the drainage channel by a return biasing means;
A pair of power supply terminals is provided, and the electric motor is driven to rotate by supplying power between the pair of power supply terminals, whereby the rotational driving force of the electric motor is transmitted to the output member via a speed reduction means such as a gear train and a clutch means. The output member is retracted from the projecting position to the retracted position, and is provided with a return operation preventing means for preventing the output member from returning from the retracted position to the projecting position, and the clutch means rotates the electric motor from the electric motor. While the transmission of force is interrupted, the return operation preventing means prevents the return operation of the output member from the retracted position to the projecting position and holds the output member in the retracted position, while the pair of power supply terminals The geared motor, which is configured so as to allow the return operation to the output member by releasing the return operation prevention means by stopping the power supply between the two, is assembled separately Is, in the motor-driven drain valve which is adapted to switch the exhaust waterways cutoff state to the communicating state by the output member of the geared motor coupled to the valve body of the valve housing for driving the valve body,
A connecting means for locking the output member and the valve body so as not to be pulled out by pushing one of the output member and the valve body into the other in the projecting operation direction of the output member;
A pull actuation blocking means for deter operation of the pull-in direction is provided et Re said output member to the geared motor,
Bei example, the cited write operation preventing means is a motor-driven drain valve, which is a releasable by operation from outside the.
  The valve body includes a tapered cylindrical portion that gradually decreases in diameter as it goes in the projecting operation direction of the output member, and the tapered cylindrical portion extends from the small diameter side opening end toward the large diameter side opening end. While at least one slit is formed, the output member has a rod portion inserted into the tapered tube portion, and gradually increases in the protruding operation direction of the output member at the protruding end of the rod portion. A locking projection having a tapered cylindrical surface having a small diameter is provided, and the projecting end of the rod portion of the output member is pushed into the tapered cylindrical portion of the valve body from the large-diameter side opening. 2. The motor-driven drain valve according to claim 1, wherein the connecting means is configured by locking the large-diameter side end surface of the stop protrusion to the small-diameter side end surface of the tapered tube portion.   In the pull-in operation preventing means, an external force due to an operation from the outside is amplified by the deceleration means, and the operation of the output member in the pull-in direction is blocked using the amplified external force. The motor-driven drain valve according to claim 1 or 2. One of the speed reducing means is constituted by a planetary gear mechanism, the sun gear in the planetary gear mechanism is driven to rotate by the output shaft of the electric motor, and the support shaft of the planetary gear meshed with the sun gear is fixedly installed. An output connecting gear is fixed on the center axis of the carrier, and the rotation of the case having the internal gear meshed with the planetary gear meshed with the sun gear is prevented, and the coupling from the output member is performed. The motor-driven drain valve according to claim 3, wherein the operation of the output member in the retracting direction is blocked by the pull-in operation blocking means by blocking transmission of an external force to the gear.

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