JP2006029538A - Motor driven drain valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a motor driven drain valve which has construction capable of easily varying operation of the drain valve in the motor driven drain valve of which working of handling and mounting can be facilitated and simultaneously which is compact as a whole and can easily secure any mounting space in a device itself of a washing machine or the like. <P>SOLUTION: The valve forms a endless cam groove 104 extending over entire periphery on outer peripheral surface of a driving shaft member 20 which is substantially arranged coaxially with a valve housing 14 at base end side of the valve housing 14 and is made to support so as to be capable of rotating around center of a shaft and incapable of shifting in axial direction and at the same time provides on a follower member 24 a slide element 162 which slidably engages in the cam groove 104 and enables the slide element 162 to be shifted in axial direction of the driving shaft member 20 by following to rotatably actuate the driving shaft member 20 and thereby, composes motion conversion means. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a motor-driven drain valve that can be suitably employed as a drain valve for a water storage tank such as a washing machine or a dishwasher.

  Conventionally, a drain valve used in a washing machine, a dishwasher, or the like is generally incorporated in a valve housing having a part of a drainage channel, and is opened and closed by a geared motor.

  In such a motor-driven drain valve, it is necessary to convert the rotary motion of the output shaft of the geared motor into a linear motion and to reciprocate the drain valve of the valve housing. Therefore, in general, the valve housing incorporating the drain valve and the geared motor have a separate structure, and the drain valve is driven by the geared motor via a motion conversion mechanism that converts the rotational motion into a linear reciprocating motion. It has become.

  Specifically, for example, as described in Japanese Patent Laid-Open No. 3-198638, a geared motor in which a crank mechanism or a rack and pinion mechanism as a motion conversion mechanism is assembled has been proposed. And the drive force of the geared motor converted into the linear reciprocating motion by this motion conversion mechanism is transmitted through a wire or a rod to the drain valve of the valve housing arranged separately from the geared motor.

  However, in such a conventional motor-driven drain valve, a geared motor with a motion conversion mechanism and a valve housing with a drain valve are manufactured, transported, and managed separately, and a device such as a washing machine. It is necessary to assemble to the main body. For this reason, there is a problem that manufacturing and parts management are troublesome and assembly work is complicated. There is also a problem that a space required for mounting on a main body of a washing machine or the like becomes large.

  Japanese Patent Laid-Open No. 2002-3261 (Patent Document 1) discloses a structure in which a geared motor housing is fixed to a valve housing and can be handled as a single member. However, since this is merely an integration of both housings, it is large overall, and the geared motors are located far away from the drain valve. For this reason, for example, when only the valve case is fixed to the washing machine body, a large force acts on the valve case by the geared motor, which tends to increase vibration and noise. There was a problem that it was difficult to ensure durability.

  Therefore, the present applicant, in the published patent publication 2003-336758 (Patent Document 2) that is the previous application, the drainage valve and the geared motor are arranged close to each other, and between the rotation output shaft of the geared motor and the drainage valve, A motor-driven drainage valve with a novel structure directly interposing a motion conversion mechanism that directly converts rotational motion into reciprocating motion was proposed.

  The motion conversion mechanism in the motor-driven drain valve disclosed in Patent Document 2 is such that an output member provided with a spiral guide groove on the cylindrical outer peripheral surface is rotationally driven by a geared motor and engaged with the guide groove. The drain valve is opened and closed with a slider. By adopting such a motion conversion mechanism, the output shaft of the geared motor can be disposed at a sufficiently close position on the same axis as the movable valve element. As a result, the entire combination of the valve housing and the geared motor can be made compact, and sufficient strength and durability can be ensured even with a small number of fixed positions with respect to the apparatus main body such as a washing machine.

  However, as a result of further investigation by the inventor of the motor-driven drain valve described in the prior application (Patent Document 2), it is clear that there is still room for improvement depending on the required characteristics. It became. In other words, the motor-driven drain valve of the prior application employs a spiral groove with ends as the guide groove of the output member, so that the drain valve can be opened and closed by normal rotation and inversion of the output member. It has become. Therefore, it has been difficult to give different operating characteristics to the opening operation and the closing operation of the drain valve.

  Specifically, since the output shaft of a geared motor is generally driven to rotate in one direction, controlling both the forward and reverse speeds of the output member by this output shaft makes the structure remarkably complicated. In reality, it is extremely difficult.

  Therefore, for example, only forward rotation of the output member (opening operation of the drain valve) is performed by driving the geared motor, and inversion of the output member (closing operation of the drain valve) is performed by energizing a compression coil spring or the like assembled to the drain valve. It is also possible to do this by means. However, even if such a structure is adopted, the drain valve opening operation and the closing operation are both realized by the sliding of the slider by the same guide groove in the output member. It is extremely difficult to set different operating characteristics for the closing operation and the closing operation.

  In particular, in order to suppress the sound and vibration at the time of contact at the opening / closing operation end of the drain valve while quickly opening / closing the drain valve, for example, when opening / closing the drain valve, for example, near the opening operation end There is a case where the operation is required to be performed at a high speed until the end of the closed operation, and the operation is performed at a low speed from the vicinity of the closed operation start end to the close operation end. However, considering the sliding position of the slider in the guide groove of the output member, as described above, the starting end during the opening operation is the end when the closing operation is performed, and the terminating end during the opening operation is the starting end during the closing operation. Therefore, it is practically impossible to adjust the operation speed of the drain valve at the start and end of operation with the inclination angle (pitch angle) of the guide member in consideration of both the opening operation and the closing operation. It will become.

Published Patent Publication No. 2002-3261 Published Patent Publication No. 2003-336758

  Here, the present invention has been made against the background as described above, and the problem to be solved is that it is easy to handle and attach and is compact as a whole, such as a washing machine. Provided is a motor-driven drain valve having a novel structure that is a motor-driven drain valve that requires only a small installation space in the apparatus body and that can easily adjust the operating characteristics of the drain valve with a large degree of freedom. There is.

  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 can be employ | adopted as arbitrary combinations 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 and drawings, or inventions that can be understood by those skilled in the art from those descriptions. It should be understood that it is recognized based on thought.

  That is, the first aspect of the present invention has a first water inlet opening at the axial tip portion and a second water outlet opening at the peripheral wall near the axial tip portion, such as a washing machine. A cylindrical valve housing that is attached to the main body of the apparatus having a water storage tank, and is disposed so as to be capable of reciprocating in the axial direction within the valve housing. On the other hand, a movable valve body that allows the first water flow port to communicate with the second water flow port in the valve housing by movement toward the proximal end side in the axial direction, and the movable valve body in the axial front end of the valve housing Urging means for urging toward the side, and extending from the movable valve body to the proximal end side in the axial direction of the valve housing so as to move integrally with the movable valve body in the axial direction of the valve housing One driven member and the other driven member A geared motor fixedly attached to the base end side in the axial direction of the valve housing, and an output shaft through which a rotational driving force of an electric motor driven to rotate is transmitted via a gear train; By converting the rotational driving force of the geared motor into a linear motion and transmitting it to the driven member, the driven member is driven in the axial direction of the valve housing, and the first water flow port and the In the motor-driven drain valve provided with the motion conversion means for switching the second water flow port between the communication state and the shut-off state, the output shaft of the geared motor is constituted by a driving shaft member having a cylindrical outer peripheral surface. The driving shaft member is disposed substantially coaxially on the base end side of the valve housing so as to be immovably supported in the axial direction, and the axial inclination angle on the outer peripheral surface of the driving shaft member The cam groove that changes on the circumference is formed with an endless structure that is continuous over the entire circumference, while the follower member is provided with a slider that slidably engages with the cam groove of the driving shaft member, and The movement of the driven shaft member in the circumferential direction of the driven member is prevented, and the sliding member slides along the cam groove along with the rotation of the driven shaft member, whereby the driven member is moved to the driven shaft. By providing a guide mechanism for guiding in the axial direction of the member, the motion converting means is configured to include a driving shaft member provided with these cam grooves, a slider, and a guide mechanism.

  In the motor-driven drain valve having the structure according to this aspect, the guide groove formed on the side surface of the driving shaft member is a circumferential groove extending over the entire circumference in the circumferential direction. Accordingly, the same portion of the guide groove is not used during the opening operation and the closing operation of the drain valve, and different portions in the circumferential direction can be used as the opening operation portion and the closing operation portion, respectively. Therefore, the operation speed and the magnitude of the driving force can be made different between the opening operation and the closing operation, and the required operation characteristics of the drain valve can be advantageously coped with.

  In addition, since the guide groove is a circumferential groove, it is not necessary to reversely rotate the driving shaft member in the opening operation and the closing operation. It is not always necessary to provide a clutch mechanism for preventing the motor from acting on the driving shaft member. Therefore, the motor type driving device can be made a simple structure.

  Further, a second aspect of the present invention is the motor-driven drain valve according to the first aspect, wherein the driven member extends from the movable valve body toward the driving shaft member as the driven member. Adopting an externally inserted cylindrical slider, and projecting the slider on the inner peripheral surface of the cylindrical slider, and the guide mechanism prevents the cylindrical slider from rotating about the central axis in the axial direction. It is characterized by being guided. In such an aspect, since the driving shaft member and the cylindrical slider are disposed inside and outside, it becomes easy to relatively position and support the driving shaft member and the cylindrical slider. A stable operation when transmitting the driving force between the member and the cylindrical slider can be realized with a compact structure.

  According to a third aspect of the present invention, in the motor-driven drain valve according to the first or second aspect, the cam groove in the driving shaft member is (a) a shaft in the rotational driving direction of the driving shaft member. An open operation area extending obliquely from the distal end side in the direction toward the proximal end side and moving the driven member from the distal end side in the axial direction toward the proximal end side when the driving shaft member is rotationally driven; In the rotational driving direction of the driving shaft member, the driving shaft member is inclined and extended from the axial base end side toward the distal end side, and the slider is moved from the axial base end side toward the distal end side when the driving shaft member is driven to rotate. A closed operation region, and (c) a circumferential direction without tilting a substantially constant axial position so as to connect between the end of the open operation region and the start end of the closed operation region in the rotational drive direction of the driving shaft member. An open holding working area extending. And butterflies. The drain valve can be operated at a set speed by the inclination of the opening operation portion and the closing operation portion provided in the guide groove. On the other hand, since the slider is positioned in the open holding operation region provided in the guide groove, the drain valve can be easily held in the open position.

  According to a fourth aspect of the present invention, in the motor-driven drain valve according to the third aspect, the inclination angle of the closed operation area and the inclination angle of the open operation area in the cam groove are only in positive and negative directions. Not only the absolute value but also the difference. In such a motor-driven drain valve structured according to this embodiment, different operating speeds can be given to the opening and closing operations of the drain valve, and simultaneously satisfy different requirements for the opening and closing operations. It becomes possible.

  Further, a fifth aspect of the present invention is the motor-driven drain valve according to the third or fourth aspect, wherein the inclination angle is set in at least one of the closed operation region and the open operation region in the cam groove. It is characterized by being changed around the circumference. In the motor-driven drain valve having such a structure according to the present embodiment, the opening / closing operation speed of the drain valve and the tensile force with respect to the drain valve can be easily changed.

  According to a sixth aspect of the present invention, in the motor driven drain valve according to any one of the first to fifth aspects, in the geared motor, transmission of rotational driving force from the electric motor to the output shaft. Clutch means arranged on the path for transmitting / cutting off the rotational driving force is provided. In the motor-driven drainage valve structured according to this embodiment, the drainage valve can be driven against the biasing force by the biasing means in a state where the clutch is connected, and in a state where the clutch is disconnected, Since the rotational driving force and detent torque of the load driving motor are not transmitted to the driving shaft member, the drain valve can be quickly displaced in the direction in which the biasing force acts by the biasing force of the biasing means.

  According to a seventh aspect of the present invention, in the motor driven drain valve according to any one of the first to sixth aspects, a motor housing is fixed to the axial base end portion of the valve housing. The geared motor is assembled to the motor housing in a substantially accommodated state. In the motor driven drain valve constructed according to this embodiment, the geared motor is accommodated in the motor housing so that the output shaft of the geared motor is positioned more coaxially with the drain valve. I can do it. Furthermore, since the motor housing protects the geared motor from dust and the like, the durability of the geared motor can be improved. Furthermore, by forming the motor housing separately from the valve housing and fixing it, the movable valve body and the geared motor can be easily incorporated into the housing.

  In addition, according to an eighth aspect of the present invention, in the motor driven drain valve according to any one of the first to seventh aspects, the geared motor includes three power supply terminals, and the three power supply terminals. And a mechanical switch mechanism for switching the connection state of the motor to the electric motor in accordance with the rotational position of the output shaft, switching the power supply state from the outside to the three power supply terminals, and the machine in the geared motor. The drive shaft member is driven and controlled by the switching operation of the type switch mechanism. In such a motor-driven drain valve structured according to this aspect, driving and stopping of the drain valve can be switched by driving and stopping of the electric motor, so that transmission that exerts rotational driving force from the electric motor to the motion conversion means. Even if the clutch means is not provided on the path, the operation of driving / stopping the drain valve can be realized, and the structure of the motor driven drain valve can be simplified.

  According to a ninth aspect of the present invention, in the motor-driven drain valve according to any one of the first to seventh aspects, the geared motor includes two power supply terminals. The electric motor is directly driven / stopped by switching the power supply state. In such a motor-driven drain valve structured according to this embodiment, the opening / closing control of the motor-driven drain valve can be made possible by a simple input that simply controls on / off of the power supply to the electric motor. . Therefore, the drive control of the motor-driven drain valve can be performed without requiring a complicated control function for an object to which the motor-driven drain valve is attached, that is, a household washing machine or a dishwasher.

  As is clear from the above description, in the motor-driven drain valve structured according to the present invention, the cam groove is a circumferential groove, and the inclination angle and length can be freely determined in the circumferential direction. Thereby, it may be possible to easily change the operating speed of the drain valve and the tensile force acting on the drain valve.

  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.

  First, FIGS. 1 to 3 show a motor-driven drain valve 10 for a washing machine as an embodiment of the present invention. The motor-driven drain valve 10 includes a valve housing 14 in which a motor housing 12 is integrally assembled. The motor housing 12 includes a load driving motor 16 as an electric motor, and a reduction gear train as a gear train. 18 and an output member 20 as a driving shaft member are incorporated, and an output member 20, a slider 24 as a driven member, and a drain valve 26 as a movable valve body are incorporated in the valve housing 14. It is. Then, the rotational driving force of the load driving motor 16 is transmitted to the output member 20 via the reduction gear train 18, and the drain valve 26 is opened and closed by rotating the output member 20 to displace the slider 24. It has become. In the following description, “up and down” refers to the right and left directions in FIG.

  More specifically, as shown in FIG. 4, the geared motor 22 includes a first partition plate 30 that spreads so as to partition an intermediate portion in the depth direction with respect to a housing body 28 having a box structure with a bottomed opening. A second partition plate 32 disposed above the first partition plate 30 and extending substantially parallel to the first partition plate 30; and a lid member 34 attached so as to substantially cover the opening. It is an assembled structure. The load driving motor 16 is disposed and fixed at the bottom of the housing main body 28 and is accommodated below the first partition plate 30.

  The load driving motor 16 is a known AC synchronous motor, and includes a stator 40 around which a rotor 36 and an annular coil 38 are wound. The rotor 36 has a structure in which a motor output shaft 54 is fixed to a substantially annular block-shaped permanent magnet 44, and a rotor support erected on the central axis of the stator 40 in the central hole of the motor output shaft 54. The shaft 42 is rotatably inserted. The N and S magnetic poles alternately magnetized in the circumferential direction on the outer peripheral surface of the permanent magnet 44 and the upper and lower magnetic pole portions 50 and 52 formed integrally with the upper and lower stator members 46 and 48 constituting the stator are connected to the coil 38. On the basis of the interaction with the N and S magnetic poles expressed by the energization of the alternating current, the rotational driving force and the detent force are exerted on the motor motor output shaft 54.

  The motor output shaft 54 is provided with a check claw 55, and in the vicinity of the check claw 55, a reverse hook that is locked to the check claw 55 in one direction of rotation of the rotor 36. A stop member 56 is disposed so as to be swingable about one axis. The check pawl 55 and the check member 56 constitute a reverse rotation prevention mechanism that defines the rotation direction of the rotor 36.

  The load driving motor 16 is connected to a motor terminal 57 for supplying power to the load driving motor 16 from the outside. The motor terminal 57 protrudes above the geared motor 22 in the state where the load driving motor 16 is assembled to the geared motor 22, and forms a terminal portion 58.

  The load driving motor 16 has an output pinion 60 fixed to the motor output shaft 54 in a state of being assembled to the housing body 28 as described above, and a notch window 62 formed in the first partition plate 30. And is exposed to a space above the first partition plate 30.

  The output pinion 60 is meshed with the first gear 64 that constitutes a part of the reduction gear train. The first gear 64 has a boss 66 that is cylindrical at the center in the radial direction and protrudes upward. On the upper surface of the first gear 64 is a substantially ring-shaped ratchet on substantially the same axis as the first gear 64. A foil 68 is integrally formed. As shown in FIGS. 5 and 6, the ratchet wheel 68 is formed with an internal gear 70 having teeth of a substantially right triangular prism shape on the inner peripheral surface, and the first gear 64 on the upper surface of the first gear 64. A ratchet pawl 74 integrally formed below the first pinion 72 disposed in an extrapolated state on the boss portion 66 is attached to the inner periphery thereof.

  The ratchet pawl 74 is attached to the first support shaft 76 that is the same as the first gear 64 and the first pinion 72 so as to be rotatable. The engaging claw 78 extending radially has a substantially right triangular prism shape at its tip, and meshes with the internal gear 70 formed on the ratchet wheel 68 by rotation in one direction, While the first pinion 72 is integrally rotated in the same direction as the first gear 64, the rotation to the other is performed by the inclination of the front end side surface of the engagement claw 78 and the inclined surface of the teeth of the internal gear 70. The engaging claw 78 does not mesh with the internal gear and slip occurs, so that the rotational driving force is not transmitted between the first gear 64 and the first pinion 72. In other words, the one-way clutch 80 serving as a clutch means for transmitting only one-way rotational force by the ratchet wheel 68 formed integrally with the first gear 64 and the ratchet pawl 74 formed integrally with the first pinion 72. Is configured.

  The reduction gear train 18 includes a second gear 82 and a second pinion 84 formed integrally with the lower surface of the second gear 82, a third gear 86, and a third gear 86 formed integrally with the lower surface of the third gear 86. No. pinion 88, No. 4 gear 90, and No. 4 pinion 92 integrally formed on the upper surface of No. 4 gear 90 are configured, with No. 1 pinion 72 having No. 2 gear 82 and No. 2 pinion 84 having three. The number gear 86 and the number 3 pinion 88 are meshed with the number 4 gear 90, respectively, and the rotational driving force generated by the load driving motor 16 is adjusted by reduction or the like to achieve the necessary rotational speed and torque. Yes. The second gear 82, the third gear 86, and the fourth gear 90 are attached to the second support shaft 94, the third support shaft 96, and the fourth support shaft 98 in an extrapolated state, respectively. Each is rotatably supported.

  In the reduction gear train 18 having such a structure, the first, second, third, and fourth support shafts 92, 94, 96, and 98 have a first partition plate 30 and a second partition plate 32, respectively. Are disposed between the opposing surfaces of the first partition plate 30 and the second partition plate 32. In other words, the first, second, third, and fourth support shafts 92, 94, 96, and 98 are disposed between the opposing surfaces of the first partition plate 30 and the second partition plate 32. Thus, the second partition plate 32 is disposed above the first partition plate 30.

  Further, the output gear 100 is engaged with the fourth pinion 92. The output gear 100 is provided at one end of the output member 20 in the axial direction, and is positioned between the first partition plate 30 and the second partition plate 32. The output member 20 includes a cam groove forming portion 102 having a thick cylindrical shape as a whole, and a cam extending over the entire circumference with a substantially constant cross-sectional shape on the outer peripheral surface of the cam groove forming portion 102. A guide groove 104 as a groove is formed. In the present embodiment, as shown in FIG. 7, the guide groove 104 includes a closed holding flat portion 106 as a closed holding operation area formed in the upper part of the axial direction and having an axial inclination angle of 0 degrees, Provided with an open holding flat portion 110 as an open holding operation region formed at the lower portion of the direction and having an axial inclination angle of 0 degrees, and the circumferential end portions of the closed holding flat portion 106 and the open holding flat portion 110 are They are connected to each other by an open operation inclined portion 108 as an open operation region and a closed operation inclined portion 112 as a closed operation region. In particular, in the present embodiment, the inclination angle of the opening action inclination part 108 and the inclination angle of the closing action inclination part 112 are different, and the circumferential length of the opening action inclination part 108 is larger than the circumferential length of the closing action inclination part 112. Have been long. Further, the inclination angle of the opening operation inclined portion 108 is gradually changed in the circumferential direction, and the inclination angle is gradually reduced in the rotation direction when the rotational driving force of the load driving motor 16 is applied. .

  A lid member 34 is disposed above the second partition plate 32 so as to cover the opening of the housing body 28. The lid member 34 has a shallow, substantially inverted dish shape, and its edge can be engaged with the edge of the housing body 28. In addition, a plurality of recesses formed at positions corresponding to the plurality of protrusions protruding from the upper surface of the second partition plate 32 and engageable with the protrusions are formed at the bottom. ing. Thereby, the lid member 34 is fixedly assembled to the second partition plate 32 and the housing body 28.

  In the state in which the lid member 34 is disposed in this manner, the output member 20 is inserted through the insertion hole 114 formed in the second partition plate 32 at the axial intermediate portion, and the cam groove forming portion 102 is An output member support portion 118 inserted into the lower end in the axial direction is fixed to the first partition plate 30 while being inserted into a through hole 116 formed in the lid member 34 and protruding upward. Accordingly, the output member 20 is disposed so as to be rotatable around one axis.

  In the cam groove forming portion 102, a cam member 120 as a cam mechanism is attached in an extrapolated state on the outer periphery of the lower end portion of the portion protruding upward from the lid member 34. The cam member 120 is a plate cam whose outer diameter varies around the rotation center axis. Further, a part of the cam member 120 is cut out to the middle in the axial direction from the portion where the outer diameter is maximum to the approximately 1/4 turn toward the small diameter side in the circumferential direction, and the step portion 122 is formed. Is formed. In the present embodiment, the guide groove 104 of the cam groove forming portion 102 is formed over a region reaching up to both ends in the axial direction in the upper portion of the cam member 120 that protrudes upward from the lid member 34. ing.

  The geared motor 22 thus formed is attached with a switch mechanism 124 as a mechanical switch mechanism so as to be superimposed on the upper surface of the terminal portion 58. The switch mechanism 124 includes a first switch fitting 126, a second switch fitting 127, and a third switch fitting 128 that are each formed of a plate-shaped metal material, and a first power supply terminal that is also formed of a plate-shaped metal material. The power supply terminal 130, the second power supply terminal 131, and the third power supply terminal 132 are configured.

  One end of each of the first, second, and third switch fittings 126, 127, and 128 has a substantially box shape and a terminal insertion hole 134 through which a motor terminal 57 for supplying power to the load driving motor 16 can be inserted. They are fixed by terminal fixing portions 136 penetrating on the upper surface, and are spaced apart from each other in the thickness direction. Further, a stopper 138 protruding toward the first and second switch fittings 126 and 127 is attached to a part of the middle of the third switch fitting 128, and the first switch fitting 126 and the third switch fitting 128 are stoppers. The length in the protruding direction of 138 is prevented from approaching. Furthermore, the tip ends of the second and third switch fittings 127 and 128 are bent at substantially right angles in the plate thickness direction, and the tips thereof are disposed near the outer peripheral surface of the cam member 120.

  Further, in the vicinity of the distal ends of the first, second, and third switch fittings 126, 127, and 128, protruding first to fourth contacts 140 and 142 projecting in the plate thickness direction at substantially the same position in the extending direction. , 144, 146 are formed. Such contacts are provided between the opposing surfaces of the first switch fitting 126 and the second switch fitting 127, and the first and second contacts 140 and 142 are connected to the terminals between the opposing faces of the second switch fitting 127 and the third switch fitting 128. 3, third and fourth contacts 144, 146 are formed on the respective terminals, the first switch 148 is formed between the first switch fitting 126 and the second switch fitting 127, and the second switch fitting 127 is provided. The second switch 150 is configured between the first switch fitting 128 and the third switch fitting 128. As is clear from the above description, the first switch fitting 126 and the third switch fitting 128 have contacts on one surface, and the second switch fitting 127 has contacts on both surfaces.

  On the other hand, the first, second, and third power supply terminals 130, 131, and 132 are fixed with the end portions on the extending direction side of the switch fittings 126, 127, and 128 positioned in the terminal fixing portion 136. At the same time, the other end portion is extended from the terminal fixing portion 136 to the outside. In particular, in the present embodiment, among these terminals, the first power supply terminal 130 is integrated with the first switch metal fitting 126, and the second power supply terminal 131 is integrated with the third switch metal fitting 128, respectively. When the power supply terminals 130 and 131 are connected to the power source, the first and third switch fittings 126 and 128 are energized.

  Here, the switch mechanism 124 is overlaid on the upper surface of the terminal portion 58 of the geared motor 22, and the motor terminal 57 extending from the upper surface of the terminal portion 58 is inserted into the terminal insertion hole 134 that is penetrated through the terminal fixing portion 136. By doing so, the motor terminal 57 is brought into contact with the third power supply terminal 132 and the second switch fitting 127 fixed to the switch mechanism 124 in the terminal fixing portion 136, respectively. Further, the three switch fittings provided in the switch mechanism 124 each have a tip positioned near the outer periphery of the cam member 120, and are provided between the switch fittings by the rotation of the cam member 120. Contact / separation between the contacts is switched, and connection / disconnection between the switch fittings is switched.

  Then, after the switch mechanism 124 is assembled to the geared motor 22, they are assembled into the motor housing 12. The motor housing 12 has a substantially bottomed cylindrical shape and is an opening / closing portion 152 that can be opened and closed downward. Further, a part of the side surface of the motor housing 12 is a terminal portion accommodating portion 153, and three slits 154, 154, and 154 through which the first, third, and fourth terminals 126, 130, and 132 are inserted, respectively. Is formed. A connecting portion 156 is integrally formed at the upper end portion of the motor housing 12. Further, an output shaft insertion hole 158 through which the cam groove forming portion 102 is inserted is formed in the upper bottom portion, and at a position slightly separated from the outer periphery of the output shaft insertion hole 158, A plate-shaped slider guide 160 protruding upward so as to be positioned on the substantially concentric shaft is formed. In the present embodiment, two slider guides 160 are formed in a circumferential length of approximately ¼ circumference and facing each other on the opposite sides in the radial direction.

  Further, a slider 24 is disposed between the radial facing surfaces of the cam groove forming portion 102 and the slider guide 160. The slider 24 has a thin cylindrical shape as a whole, and a sliding contact projection 162 as a slider projecting radially inward is integrally formed on the inner peripheral surface side of one end portion in the axial direction. Yes. In addition, a valve body locking portion 164 having a substantially disk shape larger than the outer dimension of the slider 24 is integrally formed at the other end portion in the axial direction. The slider 24 having such a structure is externally inserted into the cam groove forming portion 102 from one side in the axial direction (the side on which the valve body locking portion 164 is not formed), and one side surface of the slider 24 is disposed. The guide groove 166 formed over substantially the entire length in the axial direction is engaged with the slider guide 160 so that the cam groove forming portion 102 and the slider guide 160 are disposed between the radially opposed surfaces. Under such an arrangement state, the sliding protrusion 162 is positioned in the guide groove 104 provided on the outer peripheral surface of the cam groove forming portion 102 and extending over the entire circumference. As the cam groove forming portion 102 rotates, the sliding contact protrusion 162 provided on the slider 24 is guided by the guide groove 104 extending over the entire circumference, so that the slider 24 can move in the axial direction. In particular, in the present embodiment, the slider 24 is displaced in the axial direction by the rotation of the cam groove forming portion 102. Since the slider guide 160 is positioned in the guide groove 166 provided in the slider 24, the rotation of the slider 24 accompanying the rotation of the cam groove forming portion 102 is prevented, and the slider 24 is only displaced in the axial direction. Is to be allowed. As is clear from this, in this embodiment, the motion conversion means is constituted by the slider 24 having the sliding contact projection 162 and the output member 20 having the guide groove 104 extending over the entire circumference, and the guide The groove 166 and the slider guide 160 constitute a guide mechanism.

  In addition, a coil spring 168 as an urging means is disposed on the slider guide 160 between the valve body locking portion 164 of the slider 24 and the opposing surface of the upper bottom surface of the motor housing 12.

  A drain valve 26 is attached to the valve body locking portion 164 of the slider 24. This drain valve 26 includes a substantially inverted cup-shaped main body 170, and a valve body locking portion 164 of the slider 24 with respect to a locking groove 174 provided inside the cylindrical portion 172 of the main body 170. The outer peripheral edge of is fitted. Accordingly, the drain valve 26 is displaced in the axial direction as the slider 24 is displaced in the axial direction. Further, the upper bottom portion 176 of the main body portion 170 has a central portion protruding in a hemispherical shape upward in the axial direction, and a cylindrical contact portion 178 is integrally formed on the outer peripheral edge portion thereof. Yes. Further, a bellows-like seal cylinder 180 is integrally formed at the opening side end of the main body 170 so as to cover the slider 24 and the slider guide 160, and the lower end in the axial direction of the bellows-like seal cylinder 180 is provided. An annular flange portion 182 that protrudes outward in the radial direction is integrally formed at the end of the body portion, that is, the end portion of the main body portion 170 that is not connected to the cylindrical portion 172.

  The valve housing 14 is disposed so as to cover the drain valve 26 having such a structure. The valve housing 14 is generally cup-shaped in the reverse direction, and a first water passage 184 is formed in the upper bottom, and a second passage is formed in the peripheral wall near the upper bottom. A water port 186 is formed. The first water inlet 184 is connected to the washing tub of the washing machine, while the second water outlet 186 is connected to the outside. In the present embodiment, a dewatering tank connection port connected to the dewatering tank of the washing machine is provided at the second water flow port 186. In addition, connecting claws 187 that project outward in the radial direction are integrally formed in the opening of the valve housing 14 at a plurality of locations in the circumferential direction. In the valve housing 14 having such a structure, the connecting claw 187 protruding from the opening engages with the connecting portion 156 formed in the opening of the motor housing 12, so that the motor housing 12 is integrated. As a result, the drain valve 26 is positioned in the valve housing 14. Further, under such a state that the valve housing 14 is assembled to the motor housing 12, the flange portion 182 of the seal cylinder 180 is formed between the axial lower end surface of the valve housing 14 and the outer peripheral edge portion of the upper bottom portion of the motor housing 12. The pressure is held between them. Accordingly, the contact of water flowing into the valve housing 14 with respect to the slider 24 and the slider guide 160 covered with the seal cylinder 180 can be prevented, and the durability of the motor driven drain valve 10 can be improved.

  Further, the central portion of the upper bottom portion 176 protruding in a hemispherical shape of the drain valve 26 is positioned in the first water passage 184, and the contact portion 178 is the upper bottom portion, that is, the first water passage. It is made to contact | abut to the opening peripheral part of 184, and, thereby, the 1st water flow hole 184 is obstruct | occluded. When the first water inlet 184 is closed by the drain valve 26 as described above, the coil spring 168 is compressed between the valve body locking portion 164 of the slider 24 and the opposing surface of the second partition plate 32. As a result, an upward biasing force is always applied to the slider 24 and the drain valve 26. Then, the output member 20 is rotated by the rotational driving force of the load driving motor 16, and the slider 24 is displaced toward the base end side of the cam groove forming portion 102 against the urging force of the coil spring 168. In a state where the lower end surface of 24 is brought into contact with the upper bottom portion of the motor housing 12, the first water passage 184 is communicated with the second water passage 186 in the valve housing 14.

  The motor-driven drain valve 10 having such a structure is fixedly attached to the main body of the washing machine by bolting an attachment piece 188 formed integrally with the valve housing 14.

  Next, the operation of the motor-driven drain valve 10 having such a structure will be described with reference to FIGS.

  Note that the load driving motor 16 starts driving when a power source is connected to the motor terminal 57. In addition, the motor terminal 57 is connected to the second switch fitting 127 and the third power supply terminal 132 in the switch mechanism 124 assembled outside the geared motor 22. Accordingly, the load driving motor 16 starts to be driven when a power source is connected to the second switch fitting 127 and the third power supply terminal 132 from the outside.

  First, in a state where the household washing machine to which the motor-driven drain valve 10 is attached is not operating, the switch members of the cam member 120 and the switch mechanism 124 are in a state as shown in FIG. That is, while the first power supply terminal 130 and the third power supply terminal 132 are connected to the power source, the first contact 140 and the second contact 142 are separated from each other, and the first and second switch fittings 126 and 127 are separated from each other. The first switch 148 configured as described above is mechanically disconnected, and the third contact 144 and the fourth contact 146 are brought into contact with each other, and are configured between the second and third switch fittings 127 and 128. A second switch 150 is connected. Further, the sliding contact projection 162 is positioned in the closed holding flat portion 106 of the guide groove 104 formed at the uppermost position in the axial direction of the cam groove forming portion 102 in FIG.

  Therefore, the input to the second switch fitting 127 is not made due to the relationship between the terminal being fed and the connected switch, and the load driving motor 16 remains stopped. Further, since the urging force by the coil spring 168 and the sliding contact projection 162 are positioned on the closed holding flat portion 106, the drain valve 26 is held in the closed position.

  Next, when the household washing machine moves to the drainage process, the switch fittings and the power supply terminals of the cam member 120 and the switch mechanism 124 are in a state as shown in FIG. That is, the power supply from the home washing machine main body is switched, and the power source is connected to the second and third power supply terminals 131 and 132. Further, the second switch fitting 127 and the third switch fitting 128 continue to have their tips at the small diameter portion of the cam member 120, the first switch 148 is held in a disconnected state, and the second switch 150 is connected. Held in a state.

  As a result, the power supply is connected to the second switch fitting 127 and the third power supply terminal 132 from the relationship between the connected terminal of the motor drive power supply and the connected switch, and the load The drive motor 16 is driven. Then, when the driving force of the load driving motor 16 is transmitted to the output member 20 via the reduction gear train 18, the output member 20 rotates, and as shown in FIG. The sliding contact projection 162 positioned at the position moves from the closed holding flat portion 106 to the opening operation inclined portion 108 along the guide groove 104. Here, since the slider 24 is non-rotatably attached by engaging with the slider guide 160, the rotational movement of the output member 20 is caused to move in the axial direction of the slider 24 by the inclination of the opening operation inclined portion 108 in the axial direction. It is converted into a downward linear motion, and the slider 24 is displaced in the opening direction. Accordingly, the drain valve 26 fixedly attached to the slider 24 is displaced in the opening direction in accordance with the displacement of the slider 24, and the opening operation of the drain valve 26 is realized.

  In this embodiment, the inclination angle of the opening operation inclination portion 108 is not constant, the inclination angle near the closed position is increased, and the inclination angle is gradually decreased toward the open position. Yes. Thereby, the tensile force of the drain valve 26 can be changed. That is, in the vicinity of the closed position where the pressing force of the coil spring 168 is small, the tensile force may be reduced accordingly, so the inclination angle is increased to increase the amount of tension. On the other hand, if the pressing force of the coil spring 168 gradually increases as the drain valve 26 moves in the open position direction, a gradually increasing tensile force is required accordingly. Instead of decreasing, a large tensile force can be obtained.

  Next, when the above-described opening operation is continued and the drain valve 26 is displaced to the open position, the switch mechanism 124 is mechanically switched by the cam member 120 that rotates together with the output member 20. That is, as shown in FIG. 10, the tip of the third switch fitting 128 is positioned at the stepped portion 122 formed on the cam member 120, so that the third switch fitting 128 is separated from the second switch fitting 127. The second switch 150 is in a disconnected state. On the other hand, since the third switch fitting 128 moves away from the first switch fitting 126, it is attached to the middle of the third switch fitting 128 and protrudes in the direction of the first switch fitting 126. The stopper 138 is moved away from the first switch fitting 126, and the first switch fitting 126 is displaced toward the second switch fitting 127, so that the first switch 148 is connected. In addition, the input of the power supply from the household washing machine main body is not switched, and is input between the second and third terminals 131 and 132 as described above.

  As a result, the second switch fitting 127 is not connected to the power supply because of the relationship between the power-supplied terminal and the connected switch, and the load driving motor 16 stops driving. At this time, since the sliding contact projection 162 is located at the position shown in FIG. 7C, that is, at the open holding flat portion 110 on the guide groove 104, the detent torque or the like of the load driving motor 16 acts. Even if it is not in the state, the drain valve 26 is not closed by the urging force of the coil spring 168.

  Next, when the home washing machine moves to the washing / rinsing process, the power supply from the home washing machine main body is switched to the first and third terminals 130 and 132 as shown in FIG. On the other hand, since the tip of the second switch fitting 127 is positioned at the large diameter portion of the cam member 120 and the tip of the third switch fitting 128 is positioned at the small diameter portion of the cam member 120, While the first switch 148 is connected, the second switch 150 is kept disconnected.

  Accordingly, the power is input to the second switch fitting 127 and the third power supply terminal 132 from the relationship between the terminal to which the motor driving power is input and the connected switch, and the load driving motor 16 is driven. Is resumed, and the output member 20 is rotated. Here, as shown in FIG. 7D, when the sliding contact projection 162 moves from the open holding flat portion 110 on the guide groove 104 to the closing operation inclined portion 112, the load driving force is applied by the urging force of the coil spring 168. The drain valve 26 can be closed more quickly than the drain valve 26 can be closed by the driving force of the motor 16.

  Specifically, the drain valve 26 is always pulled in the closed position direction (downward in the axial direction) by the urging force of the coil spring 168, and the urging force is converted into a rotational force by the motion conversion means, and is output from the output gear 112. This is transmitted to the first pinion 72 via the reduction gear train 18. However, in the rotational direction of the first pinion 72 by the rotational force transmitted to the first pinion 72 in this way, the one-way clutch 80 formed between the first pinion 72 and the first gear 64 is disconnected as described above. Therefore, the rotational force is not transmitted to the load driving motor 16. Therefore, during the closing operation of the drain valve 26, the closing operation of the drain valve 26 by the biasing force of the coil spring 168 is not hindered by the detent torque or the rotational driving force of the load driving motor 16, and the load driving motor Since it is possible to drive the drain valve 26 at a speed equal to or higher than the driving speed of the drain valve 26 by the rotational driving force of the motor 16, the drain valve 26 can be quickly closed by the biasing force of the coil spring 168. In the present embodiment, the axial inclination angle of the closing operation inclination portion 112 is larger than the average inclination angle in the axial direction of the opening operation inclination portion 108, and is driven by the coil spring 168. The drain valve 26 can complete the closing operation more quickly than the opening operation.

  When the drain valve 26 moves to the closed position, the first and third power supply terminals 130 and 132 are connected to the power source as shown in FIG. Since the tip portion moves to the small diameter portion of the cam member 120, the first switch 148 is disconnected, while the second switch 150 is connected. Further, as shown in FIG. 7A, the sliding contact projection 162 is positioned on the closed holding flat portion 106 on the guide groove 104. Therefore, the drain valve 26 is held in the closed position by the biasing force of the coil spring 168 acting and the sliding contact projection 162 being positioned on the closed holding flat portion 106.

  The motor-driven drain valve 10 having such a structure is formed on the outer peripheral surface of the output member 20 by forming the guide groove 104 as an endless peripheral groove extending over the entire outer peripheral surface of the output member 20. In the guide groove 104, the opening operation inclined portion 108 for realizing the opening operation and the closing operation inclination portion 112 for realizing the closing operation are separately formed on different portions in the circumferential direction on the same guide groove 104. It becomes possible. Therefore, for example, it is possible to individually set different operation characteristics of the opening operation and the closing operation, such as performing the opening operation slowly, but quickly performing the closing operation, which is required for the drain valve 26. Various opening / closing operations can be advantageously realized without requiring a complicated structure such as reverse rotation of the output member 20.

  Further, in the motor-driven drain valve 10 structured according to the present embodiment, the guide groove 104 is provided with the flat portions of the closed holding flat portion 106 and the open holding flat portion 110, the open operation inclined portion 108, and the closed operation inclined portion 112. It is formed by an inclined part. Therefore, opening / closing operation is realized by positioning the sliding contact projections 162 on the inclined portions 108 and 112, and draining at the open position and the closed position by positioning the sliding contact projections 162 on the flat portions 106 and 110. The valve 26 can be reliably held.

  In the present embodiment, the inclination angle in the axial direction of the opening operation inclined portion 108 of the guide groove 104 is formed so as to change in the circumferential direction. As a result, the tensile force of the load driving motor 16 of the drain valve 26 is changed in accordance with the change of the biasing force in the closing direction by the coil spring 168 accompanying the displacement of the drain valve 26, so that the load driving motor 16 The difference between the tensile force and the pressing force due to the urging force of the coil spring 168 is made substantially constant. That is, when the biasing force by the coil spring 168 is small and the drain valve 26 is in the vicinity of the closed position, the tensile force exerted by the load driving motor 16 may be small accordingly, and the inclination angle of the guide groove 104 is increased. Thus, the amount of tension per unit rotation amount of the drain valve 26 is increased so that the drain valve 26 operates quickly. On the other hand, if the drain valve 26 moves to the vicinity of the open position where the urging force by the coil spring 168 is large, the tensile force by the load driving motor 16 needs to be increased accordingly, and the tension is reduced by reducing the inclination angle of the guide groove 104. Realize increased power. Therefore, the drain valve 26 can be opened quickly by effectively utilizing the excessive rotational driving force of the load driving motor 16 generated when the drain valve 26 is displaced near the closed position. .

  Furthermore, the required performance for the load driving motor 16 can be lowered by skillfully setting the inclination of the opening operation inclined portion 108 as compared with the case where the inclination of the opening operation inclination portion 108 is made constant. The motor driven drain valve 10 can also be realized at low cost.

  Further, by adopting a three-terminal type geared motor 22 for driving the drain valve 26, a complicated locking mechanism or the like is not required in the geared motor, and the motor driven type of the present embodiment with a more inexpensive and simple structure. A geared motor 22 used for the drain valve 10 can be realized.

  Furthermore, in the present embodiment, by providing the coil spring 168 that imparts an urging force in the closing direction to the drain valve 26, a load is applied by the urging force of the coil spring 168 when the drain valve 26 is closed. It is possible to close the drain valve 26 more quickly than driving by the driving motor 16. In particular, in this embodiment, since the geared motor 22 includes the one-way clutch 80, the closing operation of the drain valve 26 due to the urging force of the coil spring 168 is hindered by the detent torque of the load driving motor 16. It has come to be realized without. In this embodiment, when the drain valve 26 is held in the open position, the sliding contact projection 162 is positioned on the open holding flat portion 110 in the guide groove 104, so that the one-way clutch 80 is in a disconnected state. However, the drain valve 26 is not driven to be displaced to the closed position by the urging force of the coil spring 168.

  A geared motor 22 incorporating a motion conversion mechanism is fixed to the motor housing 12 in a stowed state, and the motor housing 12 is integrally attached to a valve housing 14 incorporating a drain valve 26. As a result, the motor housing 12 to which the geared motor 22 is attached and the valve housing 14 having the drain valve 26 can be handled in an integrated manner, so that parts management, transportation and the like can be simplified, and a household washing machine, etc. Can be easily assembled. Furthermore, the size of the motor driven drain valve 10 can be reduced by positioning the geared motor 22 and the drain valve 26 close to each other on substantially the same axis.

  Further, by incorporating the geared motor 22 in the motor housing 12 in a housed state, it is possible to prevent malfunction of the geared motor 22 due to dust entering from the outside and a decrease in durability, and the reliability of the motor driven drain valve 10. Improved durability and durability.

  Furthermore, by forming the motor housing 12 separately from the valve housing 14 and fixing it, the drain valve 26 and the geared motor 22 can be easily incorporated in the housing, respectively, and the motor-driven drain valve 10 can be handled easily. Can be .

  Next, FIG. 12 shows a motor-driven drain valve 190 as a second embodiment of the present invention. The motor-driven drain valve 190 employs a two-terminal geared motor 192. In addition, in the following description, about the member or site | part substantially the same as 1st embodiment, description is abbreviate | omitted by attaching | subjecting the same code | symbol in a figure.

  As shown in FIG. 13, a two-terminal geared motor 192 employed in the motor-driven drain valve 190 of this embodiment includes a rotational force interrupting mechanism 194 as a motor side clutch, and a planetary gear mechanism 196 as a clutch means. And an output gear 100 and a locking mechanism 198.

  The rotational force disconnecting mechanism 194 includes an upper connecting member 200, a lower connecting member 202, and a coil spring 204. The upper connecting member 200 has an upper pinion 206 and a locking claw 208 that are integrally formed on the same axis, and a locking portion 210 is formed on the lower surface thereof. Further, the lower connecting member 202 has a lower gear 212, and the lower gear 212 is engaged with an output pinion 60 fixed to the cam groove forming portion 102 of the load driving motor 16. . Further, upper and lower bosses 214 and 216 projecting outward in the axial direction are integrally formed at the center portions of the upper and lower surfaces of the lower joint member 202, and on the upper surface of the lower joint member 202. Around the upper boss portion 214, a valve body locking portion 164 that can be engaged with the locking portion 210 of the upper joint member 200 is formed in a state in which the displacement in the axial direction is possible. In the state where the coil spring 204 is extrapolated to the upper boss portion 214 of the lower connecting member 202, the upper connecting member 200 and the lower connecting member 202 are separated from each other in the axial direction and are on the same central axis. The upper connecting member 200 and the lower connecting member 202 are integrated with each other in a state where the engaging portions 210 of the upper connecting member 200 and the engaging pieces 218 of the lower connecting member 202 are engaged with each other. The rotational driving force of the output pinion 60 fixed to the cam groove forming portion 102 of the load driving motor 16 is transmitted to the upper pinion 206 of the upper connecting member 200. Yes. Note that the engagement of the locking portion 210 of the upper connection member 200 and the locking piece 218 of the lower connection member 202 is maintained in the forward rotation direction of the load driving motor 16 and vice versa. It is released in the rotation direction.

  The planetary gear mechanism 196 includes a case 220 and a planetary gear member 222. The case 220 has a bottomed cylindrical shape as a whole, and an internal gear 224 and an external gear 226 are formed on the inner peripheral surface and the outer peripheral surface of the cylindrical wall portion, respectively, and the bottom wall portion Has a central hole penetrating on the central axis. The planetary gear member 222 has upper and lower disks 220 and 222 as carriers that are opposed to each other in the axial direction, and the upper and lower disks 220 and 222 are lower. A plurality of gear pins projecting around the central axis of the side disk 230 are fixed to each other, and a planetary gear 232 is rotatably mounted on each gear pin. Further, an insertion hole is formed in the central portion of the lower disk 230. Then, the upper pinion 206 of the upper connecting member 200 is inserted into the insertion hole formed in the lower disc 230 in a state where the planetary gear member 222 is rotatably fitted to the case 220, and this state Below, the upper pinion 206 and the planetary gear 232 are meshed, and the planetary gear 232 and the internal gear 224 are meshed. That is, in the present embodiment, the sun gear of the planetary gear mechanism 196 is configured by the upper pinion 206. Further, a connecting gear 234 is integrally formed on the central axis of the upper disc 228 of the planetary gear member 222 so as to protrude upward, and the connecting gear 234 is an output gear provided in the output member 20. 112 is meshed.

  A cam portion 236 is integrally formed below the output gear 112. The cam portion 236 is formed with a cam protrusion 238 protruding in the radial direction.

  Further, a cam lever 240 is disposed near the output member 20 so as to be swingable around the support shaft. The cam lever 240 has a sliding contact portion 242 that protrudes outward in the direction perpendicular to the axis on the outer peripheral surface of the cylindrical shaft portion. The protruding tip portion of the sliding contact portion 242 is brought into sliding contact with the cam portion 236 provided on the output member 20.

  Further, near the cam lever 240, a leaf spring 244 is disposed with one end in the longitudinal direction fixedly supported. Under such an arrangement state, the leaf spring 244 is in contact with the sliding contact portion 242 of the cam lever 240 so that the sliding contact portion 242 of the cam lever 240 is always in sliding contact with the cam portion 236 of the output member 20. It has become.

  Further, on the outer peripheral surface of the shaft portion of the cam lever 240, a protruding portion 246 that is protruded in a radial direction different from the protruding direction of the sliding contact portion 242 is provided. An operation unit 248 is integrally formed. The operation portion 248 has a rectangular block shape as a whole, and a through hole extending in the longitudinal direction is formed at the center of the plate surface. The operating portion 248 is integrally formed at the protruding tip portion of the protruding portion 246 so that the protruding direction of the protruding portion 246 and the longitudinal direction of the operating portion 248 are substantially perpendicular. Further, the distal end portion (the other end portion in the longitudinal direction) of the operation portion 248 is positioned below the base end portion (the one end portion in the longitudinal direction) by an inclined portion formed in the central portion in the longitudinal direction. . The through hole of the operation unit 248 is extrapolated so as to be movable with respect to the support shafts of the rotational force interrupting mechanism 194 and the planetary gear mechanism 196, and the upper surface of the operation unit 248 is placed on the lower surface of the lower boss 216 It comes to contact.

  Here, in the present embodiment, in a state where the base end portion of the operation portion 248 is in contact with the lower boss portion 216 and the lower joint member 202 is lifted upward by the operation portion, the lower joint member The valve body locking portion 164 of 202 and the locking portion 210 of the upper connecting member 200 are locked, and the rotational driving force of the output pinion 60 is transmitted to the upper pinion 206. Further, in a state where the distal end portion of the operation portion 248 is in contact with the lower boss portion 66 and the lower connecting member 202 is separated from the upper connecting member 200 by the urging force of the coil spring 168, the lower connecting member Since the valve body locking portion 164 of 202 and the locking portion 210 of the upper connecting member 200 are not locked, the rotational driving force of the output pinion 60 is not transmitted to the connecting gear 234.

  Further, on the outer peripheral surface of the cam lever 240 shaft portion, a locking lever operation piece 250 is provided in a direction different from the sliding contact portion 242 and the protruding portion 238 in the radial direction.

  Further, a locking lever 252 as a locking means is disposed near the cam lever 240 so as to be swingable around a central axis parallel to the swinging central axis of the cam lever 240. The locking lever 252 has a locking arm 256 extending outward in a direction perpendicular to the axis, and the locking arm 256 is locked to the locking claw 208 of the upper connecting member 200. . In addition, a protruding piece 254 protruding in the radial direction is integrally formed at the lower end in the axial direction of the locking lever 252, and the protruding piece 254 is formed on the cam lever 240 in a state where the locking lever 252 is disposed. It is positioned in the vicinity of the locking lever operation piece 250 that is formed to project in the radial direction on the outer peripheral surface of the shaft portion. When the cam lever 240 is swung by the sliding contact of the cam protrusion 238, the protruding piece 254 engages with a locking lever operation piece 250 provided on the cam lever 240, and the locking lever 252 It is designed to interlock with the swing.

  In this embodiment, in the state where the sliding contact portion 242 of the cam lever 240 is not in sliding contact with the cam protrusion 238 formed on the outer peripheral surface of the cam portion 236, the locking claw 208 of the locking lever 252 is It is not latched by the latching claws 208 of the upper joint member 200, thereby allowing the upper joint member 200 to rotate. When the sliding contact portion 242 of the cam lever 240 is in sliding contact with the cam protrusion 238 formed on the outer peripheral surface of the cam portion 236, the locking lever operation piece 250 provided on the cam lever 240 is provided on the locking lever 252. The locking lever is driven to rotate in contact with the protruding piece 254. Thereby, the latching claw 208 of the latching lever 252 is latched by the latching claw 208 of the upper joint member 200 so that the upper joint member 200 is prevented from rotating.

  On the other hand, the geared motor 192 includes a locking mechanism 198. The locking mechanism 198 includes a magnetic induction type transmission mechanism 258. The rotor 260 included in the magnetic induction type transmission mechanism 258 is substantially reversed as a whole by a substantially thick cylindrical permanent magnet 262 and a sleeve 264 disposed at the radial center at the upper axial end of the permanent magnet 44. It is a cup shape. A plurality of magnetic poles are alternately set on the outer peripheral surface of the permanent magnet 262.

  In addition, an input side induction pinion 266 is inserted through the rotor 260 from below in an interpolated state. The input-side induction pinion 266 has a portion inserted into the rotor 260 having a substantially thick cylindrical shape, and a transmission gear meshed with the output pinion 60 by an input gear 270 provided below the cylindrical portion. 268, and the rotational driving force of the load driving motor 16 is transmitted. Further, a connecting coil spring 272 is attached to the cylindrical portion of the input side induction pinion 266 inserted through the rotor 260 in an extrapolated state. One end of the connection coil spring 272 is brought into contact with a contact piece (not shown) formed in a recess of the rotor 260 having a substantially reverse cup shape, and the other end of the connection coil spring 272 is input. The side guide pinion 266 is brought into contact with a contact piece 274 projecting from the side guide pinion 266. As a result, the input side induction pinion 266 and the rotor 260 are elastically connected via the coupling coil spring 272, and are rotationally driven by the rotational driving force of the load driving motor 16 transmitted via the transmission gear 268. The rotation of the input induction pinion 266 to be damped is buffered by the coupling coil spring 272 and transmitted to the rotor 260.

  In addition, a guide ring 276 having a substantially inverted cup shape is disposed so as to cover the rotor 260. The induction ring 276 is made of a magnetic material and has an inner diameter that is larger than the outer dimension of the permanent magnet 262. The rotational driving force of the rotor 260 is transmitted to the induction ring 276 by magnetic induction between the rotor 260 and the induction ring 276 so that the induction ring 276 is rotated in the same direction as the rotor 260. As a result, the output-side induction pinion 278 provided so as to protrude upward in the axial direction on the central axis of the upper bottom portion of the induction ring 276 is rotated in the same direction as the rotor 260.

  Furthermore, a swing gear 280 is disposed near the magnetic induction transmission mechanism 258. The oscillating gear 280 has a substantially sector shape extending around the oscillating central axis, and the output side induction pinion 278 is meshed with a locking tooth 282 formed on an arcuate outer peripheral surface. . Further, a locking piece 284 is formed on the outer peripheral surface of the rotation center shaft of the swing gear 280 so as to protrude outward in the axis-perpendicular direction, and by a coil spring 286 locked to the locking piece 284, A return force in one direction of swing is applied to the swing gear 280.

  Further, an arc-shaped block-shaped locking portion 288 that protrudes in the rotational direction opposite to the direction in which the restoring force is applied by the coil spring 286 is integrated with one end portion in the circumferential direction of the rocking gear 280. When the swinging gear 280 is rotated against the restoring force of the coil spring 286, the locking portion 210 is locked to the locking protrusion 292 formed on the stopper gear 290. It has become so.

  The stopper gear 290 includes a locking protrusion 292 that is locked by the locking portion 288 and a locking gear 294 that meshes with an external gear 226 provided on the case 220 that forms the planetary gear mechanism 196. . When the locking projection 292 is locked by the locking portion 288, the stopper gear 290 is made non-rotatable and the case 220 having the external gear 226 that meshes with the locking gear 294 of the stopper gear 290. The rotation is prevented.

  As is clear from this, in this embodiment, the locking portion 288 of the rocking gear 280 is locked to the locking protrusion 292 of the stopper gear 290 to prevent the rotation of the case 220 constituting the planetary gear mechanism 196. In this state, the rotational driving force of the load driving motor 16 is transmitted to the output member 20, while the locking portion 288 of the swing gear 280 is locked to the locking protrusion 292 of the stopper gear 290. In a state where the rotation is not performed, the rotation of the case 220 constituting the planetary gear mechanism 196 is allowed, and the rotational driving force of the load driving motor 16 is not transmitted to the output member 20. That is, the state in which the rotation of the case 220 is prevented is a state in which the clutch is engaged, and the state in which the rotation of the case 220 is allowed is a state in which the clutch is disengaged.

  Next, the operation of the motor-driven drain valve 190 having a structure according to the second embodiment will be described with reference to FIG.

  First, in a state where no power is input to the load driving motor 16 from a household washing machine or the like to which the motor driven drain valve 190 is attached, the magnetic induction transmission mechanism 258 is in a disconnected state, and the planetary gear mechanism 196 The clutch is kept disconnected. Further, the sliding contact projection 162 is positioned on the guide groove 296 in the closed holding flat portion 106 located at the position of FIG. 14A, that is, the uppermost portion in the axial direction of the cam groove forming portion 102. Therefore, the drain valve 26 is held in the closed position by the urging force of the coil spring 168.

  Next, when power is input to the load driving motor 16 and the load driving motor 16 generates a rotational driving force, magnetic induction is generated between the rotor 260 and the induction ring 276 constituting the magnetic induction type transmission mechanism 258. Occurs and the guide ring 276 rotates in the same direction as the rotor 260. By this rotation, the output side induction pinion 278 fixed to the induction ring 276 is rotated, and this rotation is transmitted to the oscillating gear 280 via the locking teeth 282, and the oscillating gear 280 is turned into a coil spring. It rotates against the return force of 286. Then, the locking portion 210 provided on the rocking gear 280 is locked to the locking piece 284 provided on the stopper gear 290, thereby preventing the stopper gear from rotating and meshing with the stopper gear 290. The case 220 having the external gear 226 is prevented from rotating. As a result, the clutch is engaged and the rotational force of the load driving motor 16 is transmitted to the output member 20 via the reduction gear train. Further, by the rotation of the cam groove forming portion 102, the sliding contact projection 162 is positioned at the position of FIG. 14B, that is, the opening operation inclined portion 108 on the guide groove 296, so that the inside of the opening operation inclination portion 108. To move. Here, since the slider 24 on which the sliding contact protrusion 162 is formed is prevented from rotating by the slider guide 160, the rotational driving force of the output member 20 is converted into the axial linear motion of the slider 24, and the drainage is performed. The valve 26 is driven to open from the closed position to the open position.

  Further, when the drain valve 26 is opened to reach the open position, the cam projection 238 of the cam portion 236 formed on the output member 20 is brought into sliding contact with the sliding contact portion 242 formed on the cam lever 240. As a result, the cam lever 240 rotates, and the distal end portion of the operation portion 248 comes into contact with the lower boss portion 66 of the lower joint member 202. Therefore, the upper connecting member 200 and the lower connecting member 202 are separated from each other, and the rotational force of the load driving motor 16 is not transmitted to the upper connecting member 200. That is, the rotational force interrupting mechanism 194 as the motor side clutch is in a disconnected state. Further, since the load driving motor 16 maintains the driving state, as described above, the case 220 of the planetary gear mechanism 196 is not rotatable. Here, as described above, since the rotational force interrupting mechanism 194 as the motor side clutch is in the disconnected state, the rotational driving force of the load driving motor 16 is not transmitted to the output member 20, and the slider 24 extends. The drain valve 26 is not driven. On the other hand, a biasing force in the closing direction by the coil spring 168 acts on the drain valve 26, but the planetary gear mechanism 196 fitted with the output gear 112 has a very large rotation ratio, so that the case 220 rotates. Under the state of being immovably locked, the drain valve 26 can be held in the open position against the urging force of the coil spring 168. Here, the open position refers to the position of the drain valve 26 in a state in which the sliding contact projection 162 provided on the slider 24 is positioned at the starting point of the closing operation inclined portion 112 in the guide groove 104.

  Next, when a predetermined time elapses with the drain valve 26 held in the open position, the power input to the load driving motor 16 is turned off, the rotation of the rotor 36 is stopped, and the magnetic induction transmission mechanism 258 is turned on. The cut state is set, and the swing gear 280 is driven back by the urging force of the coil spring 286. As a result, the locking portion 288 that has prevented the rotation of the stopper gear 290 is separated from the locking protrusion 292 formed integrally with the stopper gear 290, and the rotation of the stopper gear 290 is allowed. Since the case 220 of the planetary gear mechanism 196 in which the external gear 226 is engaged with the stopper gear 290 is also allowed to rotate, the clutch by the planetary gear mechanism 196 is disengaged, and the rotational driving force of the load driving motor 16 is output. It is not transmitted to the member 20. On the other hand, since the rotation of the case 220 constituting the planetary gear mechanism 196 is allowed, the planetary gear mechanism 196 is idled without resisting the urging force of the coil spring 168. Therefore, the drain valve 26 is driven and displaced to the closed position according to the urging force of the coil spring 168. As described above, when the drainage valve 26 is held in the open position while the sliding contact projection 162 is positioned in the closed operation inclined portion 112, power supply to the load driving motor 16 is turned off. In this case, the closing operation is surely performed by the urging force of the coil spring 168.

  In such a motor-driven drain valve 190 of this embodiment, compared with the motor-driven drain valve 10 shown as the first embodiment, a two-terminal type geared motor 192 is adopted, so that a motor-driven drain valve 190 is used. An output signal from a household washing machine or the like equipped with a drain valve 190 to the geared motor 192 can be made simple by only on / off switching. Therefore, the drive control of the drain valve 26 can be realized without requiring complicated control for a home washing machine or the like.

  In the present embodiment, since it is not necessary to provide the cam member 120, it is not necessary to provide a space for arranging the cam member between the geared motor 192 and the upper bottom portion of the motor housing 12. Therefore, the distance between the geared motor 192 and the mounting piece 188 can be made closer, and the problem of noise and vibration at the time of driving the drain valve 26 by reducing the rotational moment can be realized more advantageously.

  Furthermore, this embodiment does not require the switch mechanism 124 as in the first embodiment. Therefore, the distance between the geared motor 192 and the mounting position of the motor-driven drain valve 190 on the household washing machine can be further reduced.

  As mentioned above, although some embodiment of this invention has been described, 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 first and second embodiments, an AC synchronous motor is employed as the electric motor, but the specific structure such as the number of coils of the AC synchronous motor employed in the present invention is the same as that of the present embodiment. The description is not intended to limit the present invention. In addition to the structure of the reduction gear train and the reduction ratio of each gear pair, the number of gears constituting the reduction gear train is not limited to that of the above embodiment.

  In the first and second embodiments, the guide groove 104 is configured such that the inclination angles of the opening operation inclined portion 108 and the closing operation inclination portion 112 are different not only in the positive and negative directions but also in absolute values, and opened. The operating inclination portion 108 is configured such that the inclination gradually changes in the circumferential direction, but the shape of the guide groove only needs to be a circumferential groove extending over the entire circumference, and is the same as that of the above embodiment. Depending on the required operating characteristics, it is appropriately set.

  Further, in the first and second embodiments, the guide groove 104 is configured by the closed holding flat portion 106, the opening operation inclined portion 108, the open holding flat portion 110, and the closing operation inclined portion 112 being continuously arranged in the circumferential direction. However, the closed holding flat portion 106 and the open holding flat portion 110 are not necessarily required in the guide groove. Specifically, for example, as illustrated in FIG. 15, a guide groove 302 configured by connecting a closed operation inclined portion 298 and an open operation inclined portion 300 may be employed. When the guide groove 302 is employed, when the drain valve 26 is held open, the boundary between the opening operation inclined portion 300 and the closing operation inclined portion 296 of the guide groove 302, that is, the lowermost end portion of the guide groove 302. By stopping the motor slightly in front of the portion where the is formed (position (c) in FIG. 15), it is possible to prevent the closing operation by the biasing force of the coil spring 168 by the inclination of the guide groove 302. I can do it. Specifically, when a pressing force is applied to the drain valve 26 in the closing operation direction by the biasing force of the coil spring 168, the sliding contact projection 162 that is stopped slightly in front of the lowermost end portion of the guide groove 302 is guided. In order to move along the inclination of the groove 302, a rotational force in the direction opposite to the rotation provided by the load driving motor 16 is applied to the output member. For example, in the first embodiment, the reverse rotational torque is transmitted to the one-way clutch 80 by the reduction gear train 18, but the reverse rotational force is the first pinion 72 from the reduction gear train 18 side. , The one-way clutch 80 is engaged, and the rotational force is transmitted to the load driving motor 16. However, since the stopped load driving motor 16 generates a large detent torque, such reverse rotation is not allowed. Therefore, the closing operation of the drain valve 26 can be prevented and the drain valve 26 can be held in the open position. In the second embodiment, the drain valve 26 is held in the open position by the rotation ratio of the planetary gear mechanism 196, and the rotation is prevented regardless of whether the rotation is normal or reverse, and the drain valve is open. Retention is surely made.

  Furthermore, in the first and second embodiments, the motor-driven drain valve is one that is positioned at two positions, the open position and the closed position, but the motor-driven drain valve has three or more positions. The present invention can also be applied to a device positioned at a position.

  Furthermore, although two slider guides 160 are provided in the first and second embodiments, any number of such slider guides 160 may be formed. Further, the slider guide may have any form as long as the rotation of the slider can be prevented. Specifically, for example, a plurality of engagement grooves extending over the entire length in the axial direction are formed on the inner peripheral surface of the cylindrical slider guide, and the engagement is engaged with the engagement grooves on the outer peripheral surface of the slider. It is possible to provide a slider guide that prevents the rotation of the slider by protrudingly forming the protrusion and engaging the engaging protrusion with the engaging groove.

  In the first embodiment, the one-way clutch 80 is provided as a clutch mechanism so that the closing operation is quickly performed by the biasing force of the coil spring 168. However, the geared shown in the first embodiment is used. A clutch mechanism is not necessarily required in the motor 22. That is, both the opening operation and the closing operation can be realized by the rotational driving force of the load driving motor 16.

  Further, in the second embodiment, the magnetic induction type transmission mechanism 258 including the permanent magnet 262 and the induction ring 276 is used to control the operation of the locking mechanism. The magnetic induction transmission mechanism 258 is not necessarily employed. Specifically, for example, a friction clutch using a sliding resistance of a coil spring can be used.

  Furthermore, in the above embodiment, an AC synchronous motor is employed as the load driving motor 16, but the load driving motor that can be employed in the present invention is not limited to the AC synchronous motor, and is conventionally known. In addition to the DC motor, any AC motor such as a synchronous motor or an induction motor can be employed.

  In addition, in the said embodiment, although the specific example of what applied this invention to the drive source for opening and closing of the drain valve of a washing machine was shown, this invention is a drive source of the drain valve of a dishwasher, etc. It is also possible to apply to.

  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 a longitudinal section showing a motor driven drain valve as one embodiment of the present invention. It is a figure which shows the bottom face and cross section of the motor drive type drainage valve shown by FIG. It is assembly explanatory drawing of the motor drive type drainage valve shown by FIG. It is assembly explanatory drawing of a part of motor-driven drainage valve shown by FIG. It is a top view which shows the one-way clutch which comprises the motor drive type drain valve shown by FIG. FIG. 6 is a longitudinal sectional view of the one-way clutch shown in FIG. 5, corresponding to a VI-VI section in FIG. 5. It is an expanded view explaining the operating state of the motion conversion mechanism which comprises the motor drive type drain valve shown by FIG. It is a top view explaining the operating state of the switch mechanism which comprises the motor drive type drain valve shown by FIG. It is a top view explaining the operating state of the switch mechanism which comprises the motor drive type drain valve shown by FIG. It is a top view explaining the operating state of the switch mechanism which comprises the motor drive type drain valve shown by FIG. It is a top view explaining the operating state of the switch mechanism which comprises the motor drive type drain valve shown by FIG. It is a longitudinal cross-sectional view which shows the motor drive type drain valve as another one Embodiment of this invention. FIG. 13 is an exploded view of a portion of the motor driven drain valve shown in FIG. 12. It is an expanded view explaining the operating state of the motion conversion mechanism which comprises the motor drive type drain valve shown by FIG. It is an expanded view explaining the action | operation state of the motion conversion mechanism which comprises the motor drive type drain valve as another one Embodiment of this invention.

Explanation of symbols

10 motor driven drain valve 12 motor housing 14 valve housing 16 load drive motor 18 reduction gear train 20 output member 22 geared motor 24 slider 26 drain valve 80 one-way clutch 104 guide groove 120 cam member 124 switch mechanism 160 slider guide 162 slide Contact projection 166 Guide groove 168 Coil spring 184 First water flow port 186 Second water flow port 190 Motor driven drain valve 192 Geared motor 194 Rotational force interrupting mechanism 196 Planetary gear mechanism 198 Locking mechanism 296 Guide groove 302 Guide groove

Claims (9)

It has a first water passage opening that opens at the tip end in the axial direction and a second water passage opening that opens at the peripheral wall near the tip end portion in the axial direction, and is attached to the apparatus main body equipped with a water storage tank such as a washing machine. A tubular valve housing;
The valve housing is arranged so as to be reciprocally movable in the axial direction, and closes the first water flow port by movement toward the distal end in the axial direction, while the first water flow port by movement toward the proximal direction in the axial direction. A movable valve body that allows the second water passage to communicate within the valve housing;
Biasing means for biasing the movable valve body toward the distal end side in the axial direction of the valve housing;
A follower member that extends from the movable valve body to the proximal side in the axial direction of the valve housing and is moved integrally with the movable valve body in the axial direction of the valve housing;
A geared device having an output shaft through which a rotational driving force of an electric motor that is rotationally driven in one direction by power feeding is transmitted via a gear train, and fixedly attached to a base end side in the axial direction of the valve housing A motor,
By converting the rotational driving force of the geared motor into a linear motion and transmitting it to the driven member, the driven member is driven in the axial direction of the valve housing, and the movable valve body and the first water flow port. In the motor-driven drain valve provided with the motion conversion means for switching the second water inlet to the communication state and the cutoff state,
The output shaft of the geared motor is constituted by a driving shaft member having a cylindrical outer peripheral surface, and the driving shaft member is disposed substantially coaxially on the base end side of the valve housing and cannot move in the axial direction. While forming a cam groove with an axial inclination angle varying on the circumference on the outer circumferential surface of the driving shaft member with an endless structure continuous over the entire circumference,
A slider that slidably engages with the cam groove of the driving shaft member in the driven member;
The driven member is prevented from moving in the circumferential direction by the driven member, and the sliding member slides along the cam groove as the driven shaft member rotates. By providing a guide mechanism that guides in the axial direction of the shaft member,
A motor-driven drainage valve characterized in that the motion conversion means is configured to include a driving shaft member provided with these cam grooves, a slider, and a guide mechanism.   A cylindrical slider that extends from the movable valve body toward the driving shaft member and is externally inserted into the driving shaft member is employed as the driven member, and the slider is provided on the inner peripheral surface of the cylindrical slider. The motor-driven drain valve according to claim 1, wherein the guide mechanism prevents the cylindrical slider from rotating about a central axis and guides the cylindrical slider in the axial direction. The cam groove in the driving shaft member,
In the rotational driving direction of the driving shaft member, the driving shaft member extends obliquely from the distal end side in the axial direction toward the proximal end side, and moves the driven member from the distal end side in the axial direction toward the proximal end side when the driving shaft member is rotationally driven. An open operating range,
In the rotational drive direction of the driving shaft member, it extends while tilting from the axial base end side to the distal end side, and when the driving shaft member is driven to rotate, the slider is moved from the axial base end side toward the distal end side. A closed operating range,
An open holding operation region extending in the circumferential direction without inclining a substantially constant axial position so as to connect between the end of the open operation region and the start end of the closed operation region in the rotational drive direction of the driving shaft member; The motor-driven drain valve according to claim 1, wherein the motor-driven drain valve is formed.   The motor-driven drain valve according to claim 3, wherein an inclination angle of the closed operation area and an inclination angle of the open operation area in the cam groove are varied not only in a positive and negative direction but also in an absolute value.   5. The motor-driven drain valve according to claim 3, wherein an inclination angle of at least one of the closed operation region and the open operation region in the cam groove is changed on the circumference.   6. The geared motor according to claim 1, further comprising a clutch unit that is disposed on a transmission path of a rotational driving force from the electric motor to the output shaft and transmits / cuts off the rotational driving force. Motor driven drain valve.   The motor drive type according to any one of claims 1 to 6, wherein a motor housing is fixed to an axial base end portion of the valve housing, and the geared motor is assembled to the motor housing in a substantially accommodated state. Drain valve. The geared motor includes three power supply terminals, and a mechanical switch mechanism that switches the connection state of the three power supply terminals to the electric motor according to the rotation position of the output shaft,
The drive shaft member is driven and controlled by switching the power supply state from the outside to the three power supply terminals and by the switching operation of the mechanical switch mechanism in the geared motor. A motor-driven drain valve according to claim 1. The said geared motor is provided with two electric power feeding terminals, The said electric motor is directly driven / stopped by switching the electric power feeding state to these two electric power feeding terminals. Motor driven drain valve.

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