KR20020001547A - Rotation suppressing mechanism and geared motor - Google Patents

Abstract

PURPOSE: A rotation stopping device and a geared motor are provided to avoid the aging deterioration of a reverse-rotation preventive mechanism which prevents a rotor from the reverse-rotation in the initial rotation state of the rotor and whose placing position does not place restrictions upon the design of a drive wheel train. CONSTITUTION: The geared motor has a rotor(11) which turns an output shaft(3) via a drive wheel train(2) and an operation member which is coupled slippably with the rotor(11), linked with the rotor(11) to be turned in the same direction as the rotor(11) and not the component of the drive wheel train. Further, it has a reverse-rotation preventive member which, if the rotor(11) is turned in a direction opposite to the normal direction, operates in linkage with the turning operation of the operation member and invades the rotation region of the rotor(11) to block the reverse-rotation of the rotor(11) and makes the rotor(11) rotate forcibly in the normal direction by a reaction when the rotor(11) hits the reverse-rotation preventive member.

Description

ROTATION SUPPRESSING MECHANISM AND GEARED MOTOR}

The present invention mainly relates to an outline of a geared motor used as a drive mechanism for driving a drain valve of a washing machine, a shutter of a ventilation line, or the like.

Conventionally, Japanese Patent Laid-Open No. 3-198638 is known as a clutch system using a magnetic induction method.

According to the clutch system disclosed in Japanese Patent Laid-Open No. 3-198638, the planetary gear mechanism is used as the clutch, and the rotational force from the rotor is transmitted to the operating body with the locking piece by the lubrication with the magnetic induction means in the middle. When the operating body is rotated, the locking piece penetrates into the rotational trajectory of the rotating body engaging piece, and rotation of the rotating body is prevented, so that the clutch constituted by the planetary gear mechanism is connected. In this prior art, although the engaging piece is formed in two circumferential directions of the rotating body, the rotational track of the engaging piece is not disclosed. When the rotation of the rotating body is prevented as described above, since the engaging piece of the rotating body constantly collides with the same position of the interlocking locking piece, the engaging part is badly worn, which shortens the life of the product.

The first aspect of the present invention provides a rotation stopping mechanism and a geared motor device using the rotation stopping mechanism such that the engagement portion between the engaging portion of the rotating member and the blocking portion of the rotating blocking member does not cause abrasion due to a collision in the long term. The purpose.

In addition, in this prior art, the reversal prevention mechanism for calibrating the rotor in the normal rotational direction is composed of a reversal prevention mounted to frictionally engage the shaft outer circumference of the gear engaged with the rotor pinion. In this prior art, when the rotor rotates in the normal direction, friction always occurs in the sliding surface between the shaft outer circumference of the gear and the reversal prevention, which causes the sliding surface to wear and shorten the product life. Moreover, the problem of the friction sound by friction cannot be avoided.

It is a second object of the present invention to provide a geared motor aimed at extending the life of the reversal prevention mechanism by not using any friction sliding to drive the reversal prevention member.

In addition, in the prior art, the magnetic induction is performed only by the magnet and the induction ring, so there is only freedom in configuration due to the specification change of the magnet and the induction ring.

A third object of the present invention is to provide a geared motor capable of increasing the degree of freedom in construction by providing assist means for assisting magnetic induction in addition to the magnet and the induction ring, and securing sufficient magnetic induction by appropriate selection of the assist means. It is done.

1 is a plan view showing an embodiment in the rotation stopping mechanism of the present invention.

2 is a cross-sectional view taken along the line II-II of FIG.

3 is a perspective view showing a rotating member of the rotation stopping mechanism of FIG.

Figure 4 is a plan view showing another embodiment of the rotation stopping mechanism of the present invention.

Figure 5 is a longitudinal cross-sectional view for explaining the internal mechanism of the geared motor device using the rotation stopping mechanism of the present invention.

6 is a plan view of the cover and the case top cover removed from the geared motor device of FIG.

Fig. 7 is an enlarged plan view for explaining the operation of the reversing preventing mechanism part in the geared motor according to the embodiment of the present invention, and (a) is a view showing the positional relationship between the reversing preventing member and the rotor in the initial state of non-energization. (b) shows the positional relationship between the reversal preventing member and the rotor in the state where the rotor has started to rotate in the normal direction from the beginning, and (c) shows that the rotor has started to rotate in the opposite direction to the normal direction from the beginning. A figure showing the positional relationship between the inversion prevention member of a state and a rotor.

Fig. 8 is a sectional view showing a rotor with a ring-shaped magnet that is a main part of the geared motor of Fig. 1 and an induction rotor with a nonmagnetic conductive ring.

Fig. 9 is a sectional view showing a rotor with a ring-shaped magnet which is a main part of a geared motor of a second embodiment of the present invention, and an induction rotor with a nonmagnetic conductive ring.

The rotation stopping mechanism of the present invention is capable of advancing and retracting each rotary trajectory of the rotary member having different types of engaging portions of the rotary trajectory, and the various types of engaging portions, and joining the engaging portion at the same time as the entry of the rotating member. It has a rotation stopping member having a blocking unit for preventing the rotation operation, characterized in that the locking unit is arranged in accordance with each rotational trajectory of the coupling portion with each of the coupling portion of the various kinds.

As described above, various kinds of coupling parts having different rotation trajectories are disposed on the rotating member, and the rotation preventing member is driven at a predetermined position by coupling with any one of the coupling portions having multiple stoppers. That is, in the conventional rotation stopping mechanism, since there is only one engaging portion of the rotating member, the predetermined position of the stopping portion repeatedly encounters the same position of the engaging portion every time, but in the present invention, the contact position with the engaging portion of the stopping portion is equal to the number of rotation trajectories. It becomes the structure to distribute. For this reason, abrasion is reduced at the predetermined position of the blocking part of the rotation stopping member. Further, in the engaging portion of the rotating member, there is a possibility that the number of times of contact with the blocking portion is dispersed as much as the installed number, so that wear is also reduced at the contact position. As a result, abrasion is reduced at the contact positions of the two members hitting each other during rotational restraint, and problems such as a coupling failure during rotational restraint caused by abrasion can be prevented, resulting in a structure that can withstand long-term use. .

Still another invention is characterized in that in the above-described rotation stopping mechanism, various kinds of engaging portions are arranged at different positions in the axial direction at equal intervals from the rotation center of the rotating member. For this reason, each engaging portion is set to have the same rotational moment when engaging the stopping portion of the rotation stopping member, and any engaging portion strikes with the same force against the blocking portion at the time of its engagement. For this reason, several coupling | bonding parts of a blocking part receive the same force at the time of the coupling | bonding, and become equal.

Another invention is characterized in that in the above-described rotation stopping mechanism, the blocking portion is formed at a series of portions provided with a plurality of coupling portions at different positions in the same position and in the axial direction in the radial direction. have. In this way, the blocking portion having a plurality of coupling portions is formed in a series of portions, thereby improving the strength of the blocking portion.

According to another aspect of the present invention, in the above-described rotation stopping mechanism, the blocking portion is urged in the direction of being pushed out of the normal rotational track by the biasing member, and at the same time, the rotation blocking member is driven by the rotational force from the other member so as to surpass the biasing force of the biasing member. It is configured to enter the trajectory, and is characterized in that it is pushed out of the rotation trajectory by the biasing force of the biasing member by dissipating the rotational force from the other member.

According to the invention described above, when the stopping force is pushed out from the rotational trajectory of the engaging portion of the rotating member by dissipating the rotational force from the other member, the force of the urging means for evacuating is weakly set. The reason for this is that, when shifting from the non-rotation stop state to the rotation stop state, it is necessary to drive the rotation restraining member beyond the force of the biasing means. Therefore, in the present invention, the biasing force of the biasing member is set weakly, and the frictional coupling at the time of detachment between the engaging portion of the rotational member and the blocking portion of the rotational blocking member is great. However, in the present invention, as described above, a plurality of coupling portions are provided, and a plurality of coupling portions of the blocking portion are also arranged to disperse such a great frictional coupling.

Another invention is characterized in that in the above-described rotary stop mechanism, the rotary stop member is interlocked by using magnetic induction with respect to a rotor serving as a driving source. In the present invention, since the rotation stopping member is configured to follow the rotor using magnetic induction, the driving force when the rotation stopping member is driven to prevent rotation of the rotating member becomes very weak. Since the rotation stopping member needs to be rotated with the weak driving force over the biasing force of the biasing member, the biasing force in the direction of loosening the biasing member is also a very weak setting. For this reason, the frictional engagement becomes even greater when the coupling part of the rotational member and the stopper of the rotational restraining member are inherently larger. However, in the present invention, such a frictional coupling is distributed, so that such a great frictional coupling is dispersed.

In still another aspect of the present invention, in the above-described rotary stopping mechanism, the rotary blocking member and the rotary member are composed of the same type of metal member or the same type of resin member. Inherently, if the members that rub against each other are composed of the same kind of members, friction sliding becomes severe. However, in the present invention, since the friction coupling is dispersed as described above, the members rubbing against each other are composed of the same type of members. Even if the friction does not cause a loss to the member.

In addition, the geared motor of the present invention is a clutch means consisting of a planetary gear support gear for supporting planetary gears in the drive wheel heat disposed between the rotor and the output shaft, a planetary gear mechanism comprising a sun gear and a ring gear meshing with the planetary gears; A clutch operating mechanism is provided for performing the stepping operation of the clutch means, and as a part of the clutch operating mechanism, the rotary stopping mechanism according to any one of claims 1 to 6 is used. It is characterized in that the rotation of the rotor is transmitted to the output shaft through two other gears by preventing rotation of any one of the sun gear, the ring gear and the planetary gear support by the stopping operation of the gear. Therefore, the frictional sliding portions of the rotary stop mechanism portion serving as part of the clutch operating mechanism are dispersed to an appropriate degree, so that only a predetermined portion can be endured for long-term use without being consumed by friction.

In addition, the geared motor of the present invention has a rotor for rotating the output shaft through the driving lubrication, and an operation member that is coupled using magnetic induction so as to follow the rotation of the rotor and does not constitute the driving lubrication, and the rotor has a normal direction and When rotated in the reverse direction, it operates in conjunction with the rotational motion of the operating member, enters the rotational area of the rotor, prevents the reverse rotation of the rotor, and simultaneously forcibly converts the rotor to rotation in the normal direction by reaction when the rotor strikes. A reverse prevention member is provided. In other words, the operating member is connected in a non-contact manner by using a magnetic induction force on the rotor. Therefore, the friction caused by the contact between the rotors does not occur at all during normal rotation, and the life of the reversal prevention mechanism is extended. In addition, friction noise does not occur.

In addition, the geared motor of the present invention is an output shaft connected to the rotor through a drive lubrication rotationally driven, a clutch means arranged in the drive lubrication step to step the drive connection between the rotor and the output shaft, and a clutch operation mechanism for stepping the clutch means The clutch operating mechanism includes a magnet made of either a magnet or a nonmagnetic conductor that rotates integrally or in conjunction with a rotor, and the other of the magnet or nonmagnetic conductor that is harvested and rotated by magnetic induction on one side thereof. It has an induction rotation means, and operates in conjunction with the other side of the magnetic induction rotation means, and the operation of connecting the clutch means and at the same time when the rotor rotates in the opposite direction to the normal direction to regulate the reverse rotation to convert to the forward rotation A reverse prevention member is provided.

In the above-mentioned geared motor, the anti-reverse member combines the function of jointing the interlocking clutch means and the function of restricting the reverse rotation of the rotor, which can reduce the number of parts and at the same time use the magnetic induction force on the rotor. As a result, the non-contacting connection is achieved, and thus the service life can be improved without any friction caused by the contact between the operating member and the rotor during normal rotation.

Another invention is that the clutch means in the geared motor described above is composed of a planetary gear support gear for supporting planetary gears, and a planetary gear mechanism consisting of a sun gear and a ring gear engaged with the planetary gear, the other side of the magnetic induction rotating means. By using the rotation of, the rotation of the rotor is transmitted to the output shaft through the other two gears by preventing rotation of any one of the sun gear, the ring gear and the planetary gear support gear.

In still another aspect of the present invention, in the geared motor described above, a member for preventing a reversal is integrally formed on a gear meshing with a gear member which rotates integrally with the other side of the magnetic induction rotating means. Therefore, when the rotor starts to rotate in the reverse direction, the anti-reverse member immediately starts to operate so that the reverse rotation of the rotor can be prevented early.

In still another aspect of the present invention, in the geared motor described above, a rotation regulating portion for regulating the rotation of one of the teeth constituting the planetary gear mechanism is formed on the gear engaged with the gear member. In this way, the number of parts can be reduced by integrally forming a rotational restricting portion for regulating the rotation of one of the gears constituting the planetary gear mechanism.

The geared motor of the present invention has a drive shaft connected to the rotor for rotational driving, a clutch means for stairing the connection between the drive shaft and the rotor, and a clutch operating mechanism for stepping the clutch means, the clutch operating mechanism being interlocked with the rotor. One of the rotating ring magnet or the nonmagnetic conductive ring, the other rotating and harvested on one side by magnetic induction, and the back yoke ring of the magnetic body disposed at the position where the nonmagnetic conductive ring is fitted in the ring magnet. It is provided, and configured to connect the clutch means in conjunction with the other side of the harvest rotation.

Since the invention described above is configured to fit the non-magnetic conductive ring in the back yoke ring and the ring magnet, the magnetic flux of the ring magnet becomes easy to be led to the back yoke ring, and the rotor is increased by the increase in the amount of magnetic flux intersecting the back yoke ring. The magnetic induction to follow the other side of the non-magnetic conductive ring or ring-shaped magnet, which is located at the rear of the wheel, becomes strong. For this reason, the rotating body to which the other side of the nonmagnetic conductive ring or the ring-shaped magnet is attached reliably follows the rotating body to which one side is attached, and accordingly, the operation of the clutch operating mechanism that performs the step of the clutch means is assured. To securely engage the clutch means.

In yet another aspect of the invention, in the geared motor described above, the back yoke ring is attached to a rotating body to which a nonmagnetic conductive ring is attached, and is configured to rotate integrally with the nonmagnetic conductive ring.

Another invention is set so that the magnetic center in the thrust direction of the ring-shaped magnet and the magnetic center in the thrust direction of the back yoke ring match or disagree with a predetermined position in the geared motor described above.

In this way, by setting the magnetic centers of the back yoke ring and the ring magnet to each other at a predetermined position, it is possible to set the rotation position of the rotating body to which the nonmagnetic conductive ring and the back yoke ring are attached. In other words, by using the displacement of the magnetic center to make a strong contact with the thrust receiver to position in the thrust direction, or set to float in the thrust receiver to reduce the load (load) in the thrust direction, or Various settings are made, such as matching the enemy center to the appropriate thrust pressure.

Another invention is that in the above-described geared motor, the back yoke ring is attached to a rotating body with a ring magnet and is configured to rotate integrally with the ring magnet. Therefore, the positional relationship between the ring magnet and the back yoke ring is uniquely determined by attaching to the rotating body of the back yoke ring, and of course, the relative movement of both does not occur after the attachment. For this reason, alignment, such as setting the magnetic center of both, becomes unnecessary. In the case where both are attached to separate members, the two are relatively easy to move, and the attachment member may be damaged by friction or the like, but such a problem does not occur because there is no relative movement.

Another invention is characterized in that a gap portion is formed between the nonmagnetic conductive ring and the back yoke ring or between the nonmagnetic conductive ring and the ring-shaped magnet in the geared motor described above, and a viscous body is disposed in the gap portion. Therefore, the following rotation of the nonmagnetic conductive ring to the ring magnet can be made more certain due to the stickiness of the viscous body.

In still another aspect of the present invention, in the geared motor described above, the clutch operating mechanism includes a non-magnetic conductive ring facing through the gap in the operation of converting the clutch means from the end to the joint and the operation of the clutch means from the joint to the end. And the relative velocity of the back yoke ring or the non-magnetic conductive ring and the ring-shaped magnets are different, and the rotational speed is faster when the joint is disconnected from the breaker, so that the viscous force of the viscous body is stronger and at the same time disconnected from the joint. In this case, the relative speed is low so that the viscous force of the viscous body hardly acts.

In the above-described invention, the grease used as the viscous body has no strong force due to viscosity when the relative rotational speeds of the members rotating relative to the viscous body are below a certain speed. Strengthens. In other words, when the magnetic induction force is generated by high speed rotation and the following rotation is performed, the viscosity of grease is effectively exhibited. On the contrary, the magnetic induction force is small (almost no) by the low speed rotation or rotation stop and the following rotation is not performed. In this case, the grease viscosity is not exerted. Therefore, when the clutch operating mechanism is operated using magnetic induction, the grease effectively assists the magnetic induction and if the following operation is not performed by the magnetic induction, the grease is not exerted and the back yoke ring is ring-shaped magnet. It is possible to rotate freely with respect to.

In still another aspect of the present invention, in each of the geared motors described above, a bearing portion of a rotating body with a nonmagnetic conductive ring is disposed on the rotor, and a viscous body is attached to the bearing portion. For this reason, the following rotational power to the rotor of the rotating body with the nonmagnetic conductive ring can be made more certain by the force of the viscosity of the viscous body described above, so that the operation of connecting the clutch means of the clutch operating mechanism can be assured. Can be. In addition, since the rotating body with a nonmagnetic conductive ring can be arrange | positioned in the inner side or the outer side of a rotor in radial direction, the whole apparatus can be made compact.

According to another aspect of the present invention, in each of the geared motors described above, the clutch operating mechanism includes a rotating member biased in one rotational direction by a spring member, and the rotating member is subjected to a driving force of the rotor to receive a ring magnet and a nonmagnetic conductive material. One side of the ring rotates at high speed and the other side is harvested on one side to rotate in the other direction of rotation against the spring force of the spring member, and at the same time, one of the ring-shaped magnet and the non-magnetic conductive ring rotates or stops at low speed. It is configured to rotate in one direction of rotation by the spring force of the spring member when the other harvest rotation is slow or stopped, and when the pivot member is rotated in the other rotational direction against the spring force of the spring member or the spring The heating member is set to generate heat when rotating in one rotational direction by the bias force of the member. It is arranged in the room, and the spring force is changed to the spring force when the heating element is heated and non-heated, and the spring force is set to weaken when the rotating member rotates against the spring force of the spring member. It is composed.

Therefore, when the rotational force of the rotor is not transmitted to the rotating member by the magnetic induction force, the clutch operating mechanism can be forcibly and reliably returned to the initial state by the spring force of the spring member. In addition, when the spring force of the spring member acts on the clutch operation mechanism by using the magnetic induction force, it only reacts with this weak force and stops the transmission of the rotational force by the magnetic induction force and returns it to the initial state. Since the shape memory spring that changes to act strongly in reverse is used, the opposite operation (the operation of rotating the rotating member by the magnetic induction force against the spring force, and the transmission of the rotational force by the magnetic induction force, stops the spring force. Rotation of the rotating member) is performed reliably for both.

In addition, the geared motor of the present invention includes an output shaft connected to the rotor and rotationally driven to a predetermined load, a clutch means for stairing transmission of power between the output shaft and the rotor, and a clutch operating mechanism for stepping the clutch means. Has,

The clutch means has two teeth each capable of transmitting the power from the rotor to a separate series of lubrication heat, and among these two teeth, the clutch is brought into a joint state by stopping the rotation of one tooth by a clutch operating mechanism, and the other tooth Is configured to transfer power from the rotor to the output shaft through drive lubrication coupled to the output shaft,

The clutch operating mechanism comprises a magnetic induction means consisting of an increase in speed lubrication connected to a gear on one side, either a magnet or a non-magnetic conductive member interlocking with the rotor, and the other side harvested and rotated on one side by magnetic induction, and a magnetic induction means. By interlocking with the other side of the clutch, stopping the rotation of the coupling gear forming a part of the increase in lubrication heat, converting the clutch means from disconnection to joint, and stopping the rotor to disengage the coupling means as the magnetic induction disappears. A clutch converting member converts the joint from the joint to the stop, and the speed increase lubrication is performed when the output shaft is rotated in the opposite direction to the rotation direction of the output shaft by the driving force of the rotor by the clutch means being converted from the joint to the joint. It is configured to transmit the rotation while receiving and increasing the speed through the clutch means and at the same time In the rotary member in the increased lubrication heat, the rotational speed adjusting means made of a wing portion for adjusting the rotational speed by air resistance or a viscous body for adjusting the rotational speed by viscous resistance is arranged.

Therefore, the rotary member in the speed increasing lubrication is provided with a wing portion for adjusting the speed by air resistance or a viscous body for adjusting the speed by viscous resistance. Strong braking force is applied.

Next, an embodiment in the rotation stopping mechanism of the present invention will be described with reference to Figs. 1 is a plan view for explaining the configuration and operation of the rotation blocking mechanism (A) of the present invention. FIG. 2 is a cross-sectional view taken along the line II-II of FIG. 1. 3 is a perspective view of a main part of the rotating member.

As shown in FIGS. 1 and 2, the rotation stopping mechanism A includes a rotating member 27 that rotates in the direction of an arrow R1 (see FIG. 1) by a driving force of a motor 1 to be described later, and an outer circumferential surface of the rotating member 27. Enter into any one of the rotational tracks x1 (x2) of the two types of coupling portions 27a and 27b (four coupling portions 27a and 27b are arranged so that all four coupling portions are arranged). It consists of a preliminary gear 25 to be a rotation preventing member having a stopper portion 26 to prevent the rotation of the rotating member (27).

The rotary member 27 is inserted into the shaft 27d so as to rotate freely and is provided with a receiving gear 27c for receiving rotation from the front gear (not shown) of the gear wheel. Moreover, the rotating member 27 has the engaging rotary part 27e which is larger in outer diameter than this bearing 27c. On the outer circumferential surface of the coupling rotation part 27e, two types of coupling parts 27a and 27b having different rotation trajectories are formed as shown in Figs.

Coupling portions 27a are formed at four positions at about 90 degree intervals in the upper half of FIG. 2 of the outer circumferential surface of the coupling rotating portion 27e. Therefore, when the rotating member 27 rotates in the direction of the arrow R1, the rotational track x1 of each engaging portion 27a is formed at the upper half of the outer circumferential surface of the engaging rotating portion 27. Further, in the rotational direction R1 of the engaging portion 27a, an inclined surface 27aa is formed on the front side to more smoothly solve the loosening of the coupling in the state of being engaged with the blocking portion 26.

On the other hand, the engaging portion 27b is the lower half in FIG. It is formed in four places alternately with the part 27a to become a zigzag shape. Therefore, the rotational track x2 of each engaging portion 27b when the rotating member 27 rotates in the direction of the arrow R1 is formed at the lower half of the outer circumferential surface of the engaging rotating portion 27. Further, in the rotational direction R1 of the engaging portion 27b, an inclined surface 27bb is formed on the front side to more smoothly loosen the loosening from the combined state with the stopper 26. In addition, the eight coupling parts 27a and 27b of the four types mentioned above are arranged equidistantly in the radial direction from the center of rotation of the rotating member 27.

In addition, the preliminary wheel 25 serving as the rotation stopping member for preventing rotation of the rotation member 27 described above is rotated by a drive series of heat separate from the driving lubrication row for rotating the rotation member 27 described above. . In other words, the rotation center portion 25a, which is an essential line of the line, is inserted to rotate freely on the shaft 25d and has a linear gear portion 25b. And the gear part 25b is comprised so that it may engage with the gear (not shown) arrange | positioned at the drive wheel row | line | column, and the tooth gear 25 rotates to the arrow R2 direction in FIG.

The rotation center portion 25a of the tooth gear 25 is in the shape of a hollow shaft inserted into the shaft 25d, and the blocking portion 26 described above is formed in FIG. 2 of the rotation center portion 25a. This stop 26 is formed to protrude radially outward from the center of rotation 25. As described above, the stopper portion 26 rotates the teeth arranged in the driving wheel row, and the tooth teeth 25 rotate in the direction of the arrow R2, so that the tip portion thereof rotates in the direction of the arrow R3 in FIG. That is, the tip portion of the stopper portion 26 is driven to approach the outer circumferential surface of the rotating member 27 by receiving the rotation of the gear disposed in the drive wheel.

The stopper portion 26 has a dimension in the axial direction approximately equal to the dimension in the axial direction of the rotational engaging portion 27e of the rotating member 27 described above, and moves to reach the outer circumferential surface of the rotating member 27. Both of the above-described rotation trajectories x1 and x2 formed at positions displaced in the direction can be simultaneously entered. The stopper portion 26 configured as described above has an engaging portion 26a for engaging with the upper engaging portion 27a having the rotational trajectory x1 in the upper half of the axial direction and a lower engaging portion having the rotational trajectory x2. A coupling portion 26b for engaging with 27b is provided in the lower half of the axial direction, respectively. One of the engaging portions 27a and 27b of the rotating member 27 being rotated (which of the eight engaging portions) is connected to the stopping portion 26 which is simultaneously entering the rotation trajectories x1 and x2. By combining, rotation of the rotating member 27 is prevented.

Moreover, the toothed gear 25 is provided with the spring stop part 25e which protrudes radially outward from the rotation center part 25a. One end of a rotation force applying spring (not shown) serving as a biasing means for biasing the tooth car 25 in the direction of the arrow R5 (see FIG. 1) is latched on the spring locking portion 25e. For this reason, the toothed tooth 25 is urged in the direction of an arrow R5 by the spring for regular rotational force. That is, the tooth tooth 25 is always biased in the opposite direction to the driving direction (see arrow R2) caused by the gear of the above-described driving wheel heat. Therefore, when driving in the direction of arrow R2 mentioned above, the preload car 25 is rotated by the force beyond that of this rotational force provision spring. As a result, the biasing force of the spring for applying the rotational force is set weaker than the driving force of the gear of the driving lubrication train.

When the driving force from the gear arrange | positioned by the drive wheel row is dissipated by the structure mentioned above, the toothed gear 25 is driven in the direction of arrow R5 by the weak biasing force of the above-mentioned rotational force provision spring. For this reason, the stopper portion 26 formed integrally with the tooth car 25 is moved away from the outer circumferential surface of the rotating member 27 while sliding on the inclined surfaces 27aa and 27bb of the engaging portions 27a and 27b coupled thereto. (See arrow R4 in FIG. 1). As a result, the stopping part 26 is pushed out by the above-mentioned both rotation traces x1 and x2, and the rotating member 27 is in the state which does not prevent rotation by this blocking part 26. As shown in FIG.

In the rotation stopping mechanism A of the present embodiment, four engaging portions 27a and 27b are arranged at different positions in the axial direction of the outer circumferential surface of the rotating member 27, respectively. On the other hand, the stopper portion 26 which prevents rotation of the rotating member 27 has two coupling portions corresponding to the two rotational tracks x1 and x2 of the eight coupling portions 27a and 27b. 26a) 26b are disposed.

Therefore, as compared with the conventional rotary stop mechanism where the coupling part frictionally engages at the same position, each coupling part 27a is applied to each engaging portion 26a, 26b of the blocking part 26 of the rotary stop mechanism A of the present embodiment. The probability of frictional engagement of 27b) is 1/2. As such, the probability of frictional engagement decreases as compared with the prior art, thereby reducing the degree of damage due to wear of the blocking portion 26, thereby increasing the life of the component.

In addition, in the embodiment of the present invention, on the rotating member 27 side, the number of the coupling portions is four times as compared with the rotational locking mechanism having only two coupling portions, so that the damages caused by the wear of the respective coupling portions 27a and 27b are caused. This reduces the accuracy of the component and extends the life of the component.

Moreover, in the above-mentioned embodiment, although the rotation stopping member provided with the stopper part 26 was comprised by the toothed tooth | wheel 25, the shape of the rotary stopping member is not limited to a toothed tooth difference. That is, as shown in FIG. 4, a circular gear 25A having a gear portion 25B for receiving rotation of the drive lubrication train of a series separate from the driving lubrication train for rotating the above-described rotating member 27 may be used.

In the portion about half of the outer circumferential surface of the circular gear 25A, the stopping portion for preventing rotation of the rotating member 27 shown in Figs. Five blocking portions 26A and 26B which are coupled to the engaging portions 27a and 27b to prevent rotation of the rotating member 27 are intensively formed (the rotating member 27 shown in FIG. Rotation member 27 shown in Figs. 1 to 3). In other words, in the other half of the outer peripheral surface of the circular gear 25A, three engaging portions 27A and detachable engaging portions 26A are disposed every 90 degrees, and each interfering portion 26A of both outer sides is disposed at the same time. At each intermediate portion with the stopper 26A disposed at the position, the coupling part 27b and the stopper part 26B detachable from each other are disposed in two.

The rotational position of the circular gear 25A is set so that any one of the five stoppers 26A and 26A enters any one of the rotational tracks x1 and x2 of the coupling parts 27a and 27b. By adjusting, any one of the blocking portions 26A and 26B is engaged with any one of the coupling portions 27a and 27b, thereby preventing rotation of the rotating member 27. In addition, the circular gear 25A is rotated about 180 degrees in this state, for example, so that all the stopping portions 26A and 26B are pushed out of the above-described rotation traces x1 and x2 to rotate the rotating member 27. To free.

In the above-described tooth car 25 shown in Figs. 1 to 3, the stopping portion 26 is made one, and the other positions of the one blocking portion 26 are combined with the engaging portions 27a and 27b, respectively. Although it is set as 26a) and 26b, in FIG. 4, several blocking parts themselves are arrange | positioned. Even with such a configuration, it is possible to have the effect of the present invention that no excessive wear is caused at a specific position of the blocking portion.

Next, an embodiment of the geared motor device using the rotation stopping mechanism A shown in Figs. 1 to 3 described above as part of the clutch operation mechanism will be described with reference to Figs. 5, 6 and 7. Moreover, although the example which arrange | positioned the above-mentioned rotation stopping mechanism A in a geared motor apparatus as a part of clutch operation mechanism was demonstrated, the above-mentioned rotation stopping mechanism A is not specifically limited to what is used for such a geared motor apparatus. . That is, the above-described rotation stopping mechanism A can be applied to various devices as long as it has a configuration using a mechanism for preventing rotation of the rotating member 27 by the blocking portion 26.

5 is a view for explaining the internal mechanism of the geared motor device. In particular, FIG. 5 is an exploded cross-sectional view for illustrating in detail the relationship between the gears constituting the driving wheel and the clutch operating mechanism. 6 is a plan view showing the cover for covering the lever and the case top cover for covering the drive mechanism. 7 is an enlarged plan view for explaining the operation of the reversal prevention mechanism part.

As shown in FIG. 5, the geared motor device according to the embodiment of the present invention is connected to a motor 1 using AC as a driving source, and an output shaft connected to the rotor 11 of the motor 1 through a driving wheel 2 to rotate. 3), a planetary gear mechanism 22 serving as a first clutch means for stepping the connection between the output shaft 3 and the rotor 11, a clutch operating mechanism 5 for stepping the first clutch means, and an output shaft ( 3) and the second clutch means 4 which stairs the connection of the rotor 11 to each other. In addition, the above-mentioned rotation stopping mechanism A is incorporated in this geared motor device as part of the clutch operating mechanism 5.

In addition, as described above, the geared motor is constituted by the AC motor 1, and it cannot be specified in which direction the motor starts to rotate. Therefore, when the rotor 11 starts to rotate in reverse at the time of starting, it enters the rotation area of the rotor 11, prevents the reverse rotation of the rotor 11, and at the same time recoils when the rotor 11 comes into contact with the rotor ( A reversal prevention member (corresponding to the projection 25c of the line tooth 25 to be described later) is provided, which forcibly converts 11) to rotation in a normal direction.

In addition, in the geared motor of the present invention, the above-described reversal preventing member and the operation member for operating the reversing preventing member (the induction pinion 16 which will be described later) correspond to a configuration independent of the driving wheel 2. All of these members are arranged in the clutch operating mechanism 5 which is not particularly made of deceleration lubrication heat. Therefore, the driving lubrication heat 2 can be arranged freely without being aware of the positional relationship between the reversing preventing member and the rotor 11.

This geared motor device connects the second clutch means 4 to transmit the driving force of the motor 1 to the output shaft 3 side, and to pull the lever 8 by rotating the output shaft 3. The clutch pinion 21 which cuts the above-described second clutch means 4 to disconnect the rotor 11 and the output shaft 3 and frees the rotor 11 with the clutch lever 41. Locking prevents the rotation of each part of the drive wheels 2 in the reverse direction (meaning the direction opposite to lifting the lever 8), and lifts the lever 8 at the position after pulling the lever 8 to a predetermined position. It is supposed to be fixed. This state is performed by maintaining the energization to the motor 1. In this state as well, by stopping the energization to the motor 1, the clutch pinion 21 is unlocked to promote rotation of the driving wheel 2 in the reverse direction and to the position before the lever 8 is raised. It is supposed to revert.

Next, a configuration for realizing the operation will be described. The drive mechanism part comprised of the motor 1, the drive lubrication heat 2, and the clutch operating mechanism 5 etc. which convert the 1st clutch means arrange | positioned in the drive lubrication heat 2 is accommodated in the case body 12. As shown in FIG. This case body 12 is comprised by the case body 12a and the case top cover 12b which coat | covered this case body 12a. In addition, a cover 12d is coated on the case top cover 12b so as to cover the lever 8.

A motor 1 serving as a driving source for operating the lever 8 is disposed on the bottom face side in the case body 12. The motor 1 includes a stator portion 14 disposed in a cup-shaped motor case 13, a rotor 11 disposed opposite to the stator portion 14 on the inner circumference of the stator portion 14, The rotor shaft 15 which supports this rotor 11 to rotate freely is provided. Then, the electric power is supplied to the coil 14a of the stator section 14 so that the rotor 11 rotates with the rotor shaft 15 as the rotation center. In addition, one end of the rotor shaft 15 penetrates the bottom surface of the motor case 13 to contact the bottom surface of the case body 12a, and the other end of the rotor shaft 15 protrudes upward of the motor 1 to the case top cover 12b. It fits into the formed bearing hole 12e.

Next, the rotor 11 and the induction rotating body 16 disposed inside the rotor 11 will be described with reference to FIG. 8.

As shown in Fig. 8, the rotor 11 includes a rotation support portion 11a having a hole through which the rotor shaft 15 (see Fig. 6) is inserted, and an upper end side thereof on the outer peripheral side of the rotation support portion 11a. It has the substantially cup-shaped rotor magnet 11b fixed so that it may protrude. In addition, in this embodiment, the ring magnet 11c which interlocks with the rotor 11 is fitted in the surface of the rotor magnet 11b on the inner peripheral space side.

As shown in Fig. 8, a nonmagnetic conductive ring 16a and a back yoke ring 16b, which are disposed opposite to the ring-shaped magnet 11c, are attached to the inner side of the ring-shaped magnet 11c, and the pinion portion 16d is attached. The induction rotating body 16 having is arranged to rotate freely. Also, when the induction rotor 16 rotates the ring magnet 11c by the rotation of the rotor 11, the nonmagnetic conductive ring 16a follows the rotation by the magnetic induction to the rotation of the ring magnet 11c. As a result, the induction rotating body 16 rotates integrally with the rotor 11 as a whole.

A hook 11d is formed at the upper end of the rotary branch 11a. This hook 11d constitutes a part of the driving wheel 2 as described later, and engages with a hook 21d formed at the lower end of the clutch pinion 21 that becomes part of the second clutch means 4, It is for transmitting the rotational force of the rotor 11 to the clutch pinion 21. And the 2nd clutch means 4 makes a state which the said hook 11d and 21d couple | bonded and the rotational force of the rotor 11 transmitted to the output shaft 3 side through the clutch pinion 21. On the other hand, since the rotational force of the rotor 11 is not transmitted to the clutch pinion 21 due to the non-engagement of these hooks 11d and 21d, the rotational force of the rotor 11 is not transmitted to the output shaft 3 side. The second clutch means 4 is cut off. In other words, the hook 11d at the upper end of the rotor 11, the hook 21d at the lower end of the clutch pinion 21, and the mechanism for releasing these hooks 11d and 21d are provided with the second clutch means 4. do.

A compression coil spring 18 serving as a part of the second clutch means 4 for disengaging the rotor 11 and the clutch pinion 21 is fitted into the upper inner circumferential side portion of the rotation support portion 11a. In addition, the guide end portion 11e for guiding the lower end portion of the guide pinion 16 is disposed on the outer peripheral portion of the upper end of the rotation support portion 11a. The guide pinion 16 is coaxially arranged above the rotor 11 by placing a ring-shaped lower end on the guide end 11e.

In addition, as shown in FIG. 7, the protrusion 25c serving as a member for preventing reverse rotation, which prevents reverse rotation of the rotor 11, is fitted into the outer peripheral surface of the main body magnet portion 11b of the rotor 11. Four recesses 11k are equally arranged in the circumferential direction. These recessed parts 11k have the contact surface 11h which becomes substantially perpendicular to the circumferential surface of the rotor 11 at the rear end in the circumferential direction when the rotor 11 rotated in the opposite direction to the normal direction.

This contact surface 11h rotates in reverse direction to the normal direction when the rotor 11 and the induction pinion 16 harvested on the rotor 11 are reversely rotated in the reverse direction to the normal direction. It becomes a part where the projection 25c which fits into the recessed part 11 touches. Further, when the projection 25c touches the contact surface 11h of the recess 11k, the rotor 1 is further prevented from reverse rotation and temporarily locked, and immediately afterwards, in the forward rotation due to the reaction at the time of collision. Is converted.

7 (A) is a diagram showing the positional relationship between the toothed car 25 and the rotor 11 in a state where no energization is performed to the geared motor of the present embodiment. According to this FIG. 7A, in the home position where no energization is performed, the protrusion 25c is in contact with the outer circumferential surface of the rotor 11. In this state, as shown in Fig. 7 (B), when the tooth gear 25 rotates in the normal direction of the rotor 11 (see arrow Y1), the projection 25c rotates in the normal direction (see arrow X1). It becomes farther from the outer circumferential surface of 11) and the rotor 11 can rotate freely without contacting the projection 25c.

On the other hand, as shown in Fig. 7 (c), when the tooth gear 25 is rotated in the opposite direction to the normal direction (see arrow X2) by the reverse rotation (arrow Y2) of the rotor 11, the projection 25c moves toward the outer peripheral surface side of the rotor 11. It is urged and enters the rotation area of the rotor 11 of reverse rotation and fits into the recessed part 11k. For this reason, in this embodiment, even if the rotor 11 starts to reverse rotation, the time until it locks becomes very fast.

In addition, in this embodiment, since the four concave portions 11k are arranged on the outer circumferential surface of the rotor 11 as described above, the front teeth 25 reversely rotate by the reverse rotation of the rotor 11, and the projections 25c. The protrusion 25 enters into the recess 11k of any one of the four at a quick timing when the C1 approaches the outer circumferential surface of the rotor 11. This configuration can shorten the time until the rotor 11 is locked, and can also shorten the time and distance for friction sliding between the protrusion 25c and the outer circumferential surface of the rotor 11.

For this reason, it is possible to shorten the time until the rotor 11 is changed from reverse rotation to rotation in the normal direction and the operation of lifting the lever 8 is started, and frictional sliding between the rotor 11 and the projection 25c is performed. This can reduce the deterioration of both members. In addition, although the number of the recessed parts 11k formed in the outer peripheral surface of the rotor 11 was four in the present Example mentioned above, this number may be less than four, and may be five or more.

The induction rotating body 16 has a non-magnetic conductive ring 16a made of copper or the like disposed at its outermost circumference, and a back yoke ring made of a magnetic material (specifically, steel, etc.) inside the non-magnetic conductive ring 16a ( 16b) is press-fitted and consists of insert molding with resin.

As for the nonmagnetic conductive ring 16a which is arrange | positioned at the outermost periphery of the induction rotating body 16 comprised in this way, the ring-shaped magnet 16c attached to the rotor 11 mentioned above is arrange | positioned facing radially inward. As described above, the nonmagnetic conductive ring 16a becomes a member that rotates following the ring-shaped magnet 11c, and is a nonmagnetic and conductive nonmagnetic inductive member, specifically, a member formed of a metal such as copper or aluminum. It consists of.

As a result, a magnetic induction force for driving the non-magnetic conductive ring 16a to the ring-shaped magnet 11c is generated, and the induction rotating body 16 which fixes the non-magnetic conductive ring 16a to the outer circumferential surface of the rotor 11 is used. It rotates in the same direction as the rotor 11 by rotation. That is, the above-described ring-shaped magnet 11c and the induction ring 16a are magnetic induction rotating means for driven rotation of the induction rotating body 16 with respect to the rotor 11 by magnetic induction, and the induction rotating body 16. Becomes an operating member for operating the member for preventing the reversal as a rotating body driven and rotated on the rotor 11 by magnetic induction.

In addition, the magnetic induction rotating means becomes part of the clutch operating mechanism 5. In this embodiment, since the induction pinion 16 follows the rotor 11 in a non-contact manner using magnetic induction, the induction pinion 16 is forced to stop the rotation of the induction pinion 16. And a slip occurs between the rotor 11 and the rotor 11. In addition, the guide pinion 16 configured as described above is engaged with the clutch 25 of the clutch operating mechanism 5.

Meanwhile, as shown in FIG. 8, the magnetic back yoke ring 16b disposed inside the nonmagnetic conductive ring 16a is disposed to fit the nonmagnetic conductive ring 16a into the ring magnet 11c. By this structure, a lot of magnetic flux passes between the ring-shaped magnet 11c and the back yoke ring 16b to form a magnetic path. Therefore, the magnetic induction of the nonmagnetic conductive ring 16a by the ring-shaped magnet 11c is strengthened. Thereby, the certainty of the operation | movement of the induction rotating body 16 improves, and the certainty of the operation | movement of the clutch operating mechanism 5 demonstrated later improves.

8, the magnetic center C2 in the thrust direction of the back yoke ring 16b in the state where the induction rotating body 16 is thrust by the thrust bearing part 11e of the rotor 11 is shown. It is comprised so that it may shift | deviate slightly upward from the magnetic center C1 in the thrust direction of this ring-shaped magnet 11c. For this reason, the induction rotating body 16 with the back yoke ring 16b is attracted by the magnetic force of the ring-shaped magnet 11c, and is tensioned toward the thrust bearing part 11e. Accordingly, the induction rotating body 16 is slightly biased toward the thrust bearing portion 11e, so that the position precision rotates accurately.

In addition, the magnetic centers C1 and C2 of both may coincide. As a result, the thrust pressure to the thrust bearing portion 11e can be reduced while improving the position accuracy to some extent.

In addition, in this embodiment, a ring-shaped magnet 11c is attached to the rotor 11 side, which is one side of the magnetic induction rotating means, and a nonmagnetic conductive ring is placed on the induction rotating body 16 side, which is the other side of the magnetic induction rotating means. Although 16a is attached, the ring magnet 11c and the nonmagnetic conductive ring 16a may be reversed. That is, a nonmagnetic conductive ring may be attached to the rotor side and a ring magnet may be attached to the induction rotating body side. Also in this case, the nonmagnetic conductive ring attached to the rotor side is inserted into the ring magnet and the back yoke ring. Specifically, when the nonmagnetic conductive ring 16a is attached to the ring magnet 11c in FIG. 8, the back yoke ring 16b is attached to the outer side of the nonmagnetic conductive ring 16a.

In addition, the second embodiment will be described with reference to FIG.

As shown in FIG. 9, the rotor 51 has the rotation support part 51a provided with the hole which penetrates the rotor shaft 15, and the upper end side protrudes upward on the outer peripheral side of this rotation support part 51a. It has the fixed substantially ring-shaped rotor magnet 51b and the back yoke ring 51g attached to the position which becomes the inside of the rotor magnet 51b from the outer side of the rotation support part 51a. In addition, a ring-shaped magnet 51c interlocking with the rotor 51 is fitted to the inner peripheral space side of the rotor magnet 51b. The ring magnet 51c may be integrated with the rotor magnet 51b as in the first embodiment described above.

In addition, the induction rotating body 56 is disposed inside the rotor magnet 51b so as to rotate freely. The induction rotating body 56 has a nonmagnetic conductive ring 56a with a flange portion near the upper end of the cylindrical portion 56c serving as the rotation center. The nonmagnetic conductive ring 56a is arranged inside the ring-shaped magnet 51c and in the gap portion that is outside the back yoke ring 51g.

In addition, a gap portion is disposed between the nonmagnetic conductive ring 56a and the back yoke ring 51g (see symbol G in FIG. 9), and the gap portion G has a viscous body having the same action as that of the first embodiment described above. Is placed. For this reason, the operation | movement of the clutch operating mechanism 5 can be stabilized further. In addition, in this second embodiment, a gap is formed between the nonmagnetic conductive ring 56a and the ring magnet 51c (see Fig. 9G1), but a viscous body may be disposed in the gap portion G1. However, when the viscous body is disposed only in the gap portion G, the viscous body is difficult to scatter to the outside in the space where the outside and the compartment are blocked by the rotor 51 and the induction rotating body 56.

Each embodiment described above is a suitable embodiment of the present invention, but is not limited thereto, and various modifications can be made without departing from the gist of the present invention. For example, in each of the above-described embodiments, the ring magnets 11c and 51c are arranged integrally with the rotors 11 and 51, and the ring magnets 11c and 51c and the nonmagnetic conductive ring 16a. Magnetic induction rotating means (co) coaxial with the rotor (11) (51), but the magnetic induction rotating means is not coaxial with the rotor (11) (51), for example, the clutch operating mechanism (5). It may be arranged at another position of the wheel heat that constitutes.

In addition, the spring member 39 shown in Fig. 6 is formed of a shape memory spring configured to reduce the spring constant by heat generation, and the rotational force of the rotors 11 and 51 is induced by magnetic induction in the vicinity of the shape memory spring. You may arrange | position the heat generating member which generate | occur | produces when it transmits to the prechamber 25. In this configuration, since the spring force decreases due to the exothermic action of the heat generating member when the preload vehicle 25 is rotated against the negative force of the shape memory spring, the preload vehicle 25 using magnetic induction is rotated with a light force. On the other hand, by stopping the rotation of the rotor 11, by returning the spring gear 25 by the spring member 39 does not generate heat to return the spring force to the original, and to the original position of the tooth car 25 with a strong force The return operation is performed. Accordingly, even if an induction magnet with a weak magnetic force is used, the spring force of the spring member 39 is less likely to impede the rotational motion due to magnetic induction, and the clutch operation mechanism is smoothly and surely performed in both directions. The operation of (5) can be made sure.

Further, the shape memory spring may have a low spring constant when there is no heat generation action and improve the spring constant by heat generation action. In the case of using such a spring to generate heat when the tooth car 25 is rotated by the spring force, and conversely, when the tooth car 25 is rotated by magnetic induction against the spring force, it is configured not to generate heat. Since it can induce magnetic force with light force, it is possible to use an induction magnet with weak magnetic force.

Next, FIG. 5 is a view of the clutch operating mechanism 5 for converting the driving wheel heat 2 for transmitting the driving force of the next motor 1 to the output shaft 3 and the first clutch means disposed in the drive wheel heat 2. And it demonstrates using FIG.

The driving lubrication 2 is composed of a fingerboard formed by pulling the upper end of the motor case 13 outward and each gear supported to rotate freely on a plurality of axes supported at both ends on the case top cover 12b. . That is, the drive wheel heat 2 is described in the right half of FIG. 5, which is a sectional cross-sectional view, and has a planetary gear mechanism 22 having a clutch pinion 21 and a support tooth 32b engaged with the clutch pinion 21. ), An output shaft 3 including a transmission gear 23 that receives the rotational force of the planetary gear mechanism 22, and an output gear part 3a that meshes with the transmission gear 23. This drive lubrication heat 2 becomes deceleration lubrication heat which decelerates the rotation of the rotor 11 and transmits it to the output shaft 3, and the above-mentioned lever 8 is pulled up to a predetermined position in the initial state in which energization is not performed. It is connected through the second clutch means 4 described above.

The upper end of the clutch pinion 21 faces the cam surface 41a of the clutch lever 41. For this reason, the clutch pinion 21 is pushed to the cam surface 41a by the constant force of the compression coil spring 18 at all times. The clutch lever 41 is supported so that one end rotates freely on the shaft supporting the transmission gear 23, and the upper surface of this portion is in contact with the bearing into which the shaft supporting the transmission gear 23 is fitted. The other end side of the clutch lever 41, that is, the side having the cam surface 41a is supported to swing freely on the rotor shaft 15, and the upper surface of this portion is in contact with the bearing into which the rotor shaft 15 is fitted. . Moreover, the long hole 41b (refer FIG. 6) which fits loosely to the rotor shaft 15 is formed in the side provided with the cam surface 41a of this clutch lever 41, and the clutch lever 41 is this long hole 41b. It is designed to rotate with the pivot centering on the transmission gear 23 within the range of.

In addition, the clutch lever 41 is provided with the operation protrusion 41e (refer FIG. 5) which enters into the clutch lever operation groove 3b formed in the one side surface of the output gear part 3a. For this reason, the rotational force of the rotor 11 is transmitted from the clutch pinion 21 to the output gear part 3a via the planetary gear mechanism 22 and the transmission gear 23, and the output shaft 3 rotates a predetermined rotation (this rotation). By pulling up the lever 8), the operation projection 41e is guided to the clutch operation groove 3b, whereby the clutch lever 41 is rotated. That is, the clutch lever 41, which is the main member of the second clutch means 4, is configured to perform the step change operation depending on the rotation angle of the output shaft 3.

Moreover, the cam surface 41a mentioned above is provided with the pushing part 41c which pushes the clutch pinion 21 down against the spring bias force of the compression coil spring 18. As shown in FIG. The pushing portion 41c pushes the clutch pinion 21 toward the rotor 11 side until energization is performed in the initial state where no energization is conducted and the lever 8 is pulled up to a predetermined position. When the cam surface 41a of the clutch lever 41 pushes the clutch pinion 21 toward the rotor 11 in this manner, the hook 21d of the clutch pinion 21 engages with the hook 11d of the rotor 11. The rotor 11 and the clutch pinion 21 are integrally rotated. In other words, the second clutch means 4 is in a joint state.

And when the output gear part 3a finishes predetermined rotation, the part 41c which pushes down the cam surface 41a of the clutch lever 41 by the guidance of the clutch lever operating groove 3b is the upper end of the clutch pinion 21. Move away from the face. Accordingly, the clutch pinion 21 moves upward by the spring biasing force of the compression coil spring 18, and the connection between the clutch pinion 21 and the rotor 11 is released. In other words, the second clutch means 4 is converted to the disconnected state. As a result, the connection between the rotor 11 and the output shaft 3 is broken. For this reason, each gear constituting the driving wheel 2 is intended to rotate in the reverse direction under the load of the lever 8.

In addition, the clutch lever 41 has a blocking member (not shown) capable of preventing rotation of the clutch pinion 21 at this upper position when the clutch pinion 21 is moved upward by the bushing spring force. have. Therefore, the clutch pinion 21 stops rotation by the above-mentioned blocking member of the clutch lever 41 after the second clutch means 4 is cut off and freed from the rotor 11. As a result, each gear of the driving wheels 2 is locked, so that it does not rotate in the reverse direction even under the load of the lever 8. That is, the sun gear 32 engaged with the clutch pinion 21 is locked, and at the same time, the clutch operating mechanism 5 is operated by using magnetic induction force so that the ring tooth 33 is locked so that the output shaft 3 ends its rotation. Is fixed in position.

When the energization to the motor 1 is cut off, the first clutch means is cut off and the ring tooth difference is free to rotate. As a result, the lever 8 is rotated in the direction of pulling the lever 8 by the load force of the lever 8, that is, in the reverse direction of the motor driving. At this time, following the reverse rotation of the transmission gear 23 in the drive wheel 2, the above-mentioned clutch lever 41 rotates to the position side before pulling up the lever 8. As shown in FIG. As a result, the pushing portion 41c of the clutch lever 41 pushes the clutch pinion 21 toward the rotor 11 side, and the second clutch means 4 becomes a joint. That is, the second clutch means 4 is connected (= the hook 21d of the clutch pinion 21 and the rotor 11 of the clutch pinion 21) by breaking the energization to the motor 1 and pulling up the lever 8 to open it from the fixed position. Hook 11d is combined).

In addition, the planetary gear mechanism 22 meshes with the clutch pinion 21 to receive the driving force on the rotor 11 side, and a plurality of planetary gears 36 mesh with the outer circumference to transmit the driving force to the planetary gear 36. Solar gear 32 having a transmission gear 32a, an inner gear 33a meshing with the planetary gear 36, and an outer gear gear meshing with the speed increasing gear 28 of the last part of the clutch operating mechanism 5. Planetary gearbox having a ring gear 33 having a portion 33b, a support plate 34a supporting the planetary gear 36 to rotate freely, and a pinion portion 34b engaged with the transmission gear 23, respectively. The support gear 34 is comprised. The planetary gear mechanism 22 configured as described above receives the rotation of the clutch pinion 21, and the sun gear 32 rotates. As a result of the rotation of the sun gear 32, the planetary gear 36 rotates the sun gear 32. Each of the planetary gears 36 rotates in the opposite direction to the rotational direction of the crankshaft, and rotates in response to the rotation of the planetary gears 36 in the opposite direction.

For this reason, if the above-mentioned rotation stopping mechanism A disposed in the clutch operating mechanism 5 is operated, the rotation of the rotating member 27 is prevented and the operation of each member of the clutch operating mechanism 5 is stopped, thereby increasing the speed difference. Rotation of the ring tooth 33 which meshes with 28 stops. As a result, each planetary gear 36 revolves about the solar gear 32. That is, the planetary gear support gear 34 which supports each planetary gear 36 to rotate freely rotates. Accordingly, the rotational force of the rotor 11 transmitted to the planetary gear mechanism 22 through the clutch pinion 21 is transmitted to the output gear portion 3a through the transmission gear 23 engaged with the planetary gear support gear 34. Is transmitted, and the lever 8 is pulled up by the driving force of the motor 1. In other words, in the geared motor device of the present embodiment, the above-described rotation stopping mechanism A is used as the conversion operation of the first clutch means.

As described above, the clutch operating mechanism 5 is for converting the planetary gear mechanism 22 serving as the first clutch means disposed in the above-described driving wheels 2. In other words, the clutch operating mechanism 5 is described in the left half of FIG. 5, which is a sectional cross-sectional view, and includes a blocking portion 26 driven by an induction pinion 16 that interlocks with the rotor 11 by magnetic induction. The planetary gear is engaged with the rotary stop mechanism A composed of the rotary member 27 which prevents rotation by engaging the pre-chamber 25 and the stopper 26 and the receiving tooth 27c of the rotary member 27. It consists of an increase gear 28 which meshes with the ring gear 33 of the mechanism 22.

In addition, although the structure of the rotation stopping mechanism A was demonstrated using FIG. 1 thru | or FIG. 3, it supplements and demonstrates a little using FIG. As shown in FIG. 6, the other end of the rotational force applying spring 39, one end of which is fixed to the pin 38 installed in the motor case 13, is fixed to the spring latching portion 25e of the tooth car 25. The preliminary wheel 25 is provided with the rotational force which rotates to the opposite direction (direction of arrow R5 in FIG. 6) by rotational force by the driving force of the motor 1 by the biasing force of the rotational force provision spring 39. As shown in FIG. However, since the rotational torque of the induction pinion 16 which follows the rotor 11 of the motor 1 exceeds the driving torque of the spring 39 for providing rotational force, the induction pinion 16 is applied to the rotor 11. In the case of following the rotation, the line tooth 25 rotates in the opposite direction to the arrow R5 direction described above in response to the biasing force of the rotational force applying spring 39.

The clutch operating mechanism 5 using the rotation stopping mechanism A described above rotates the tooth car 25 using magnetic induction when the motor 1 is energized, and the blocking part 26 rotates the rotating member 27. It is configured to engage with any one of the engaging portion (27a) (27b) of. The rotation of the rotary member 27 is prevented by this engagement, and the respective members constituting the clutch operating mechanism 5 are locked up to that time. Then, in the planetary gear mechanism 22 serving as the first clutch means, the rotation of the ring gear 33 is locked, and the first clutch means becomes a joint.

In addition, when the second clutch means 4 described above also becomes a joint in the state where the first clutch means is joined, the rotation of the rotor 11 causes the sun gear 32 and the planetary gear of the planetary gear mechanism 22 to rotate. It is transmitted to the output shaft (3) side via 34. In this state, if only the first clutch means 4 is cut off and the first clutch means remains in the engaged state, the connection with the output shaft 3 to the rotor 11 is released, but as described above, the lever 8 Is fixed in the retracted position.

In this state, when the energization to the motor 1 is cut off and the magnetic induction force between the rotor 11 and the induction pinion 16 is extinguished, It rotates by a negative force, and the engagement of the stopper part 26 and the engaging part 27a or 27b of the rotating member 27 is loosened. As a result, the locked state of each part of the clutch operating mechanism 5 is released. For this reason, the rotational force of the output shaft 3 to be reversely rotated by the external load is transmitted to reverse the driving lubrication heat 2, and is transmitted to the rotating member 27 through the planetary gear mechanism 22 and the speed increase gear 28. The rotating member 27 is free to rotate. As a result, the fixed state of the lever 8 is released.

At this time, the rotating member 27 is accelerated and tries to rotate at high speed. However, since four wing portions 27f are arranged on the upper end side of the rotating member 27, the higher the speed of rotation, the higher the resistance of these wing portions 27f. As a result, the rotating member 27 is not rotated at such a high speed and rotates slowly in a state in which the speed is controlled. Accordingly, the rotary member 27 and the gears of the front end thereof rotate slowly in a state in which the speed is adjusted without being rotated at that speed. That is, the rotating member 27 having the wing portion 27c becomes a rotating speed adjusting member for adjusting the rotating speed of each rotating member. In this embodiment, the rotational speed adjusting member is constituted by the rotating member 27 having four blade portions 27f. However, the number of the blade portions 27f may not be four, or may be smaller or more.

In addition, a viscous body for adjusting the rotational speed of the rotating member 27 is provided between the upper end of the wing portion 27f and the case top cover 12b, and in addition to the above-described air resistance, the speed is increased as the rotational speed increases. As a viscous body to be adjusted (reduced) by viscosity, the rotational speed of the rotating member 27 may be adjusted. Incidentally, the rotation speed adjusting member may not be provided with a wing portion, but only the viscosity of the viscous body may be provided as the rotation speed adjusting member.

For example, a disk-shaped member may be disposed at the upper end of the rotating member 27, and a viscous body for adjusting the rotational speed may be provided in the gap between the disk-shaped member and the case top cover 12b. For example, a wall is formed on the case top cover 12b to surround a part of the outer circumference of the rotating member 27, and a viscous body is provided at a gap portion between the inner circumferential surface of the wall and the outer circumferential portion of the rotating member 27. You may also As the viscous body, it is preferable to use a grease of a type that can exhibit higher viscosity and suppress high speed as the rotational force of the rotating member is increased.

In addition, although the rotation member 27 was used as the rotation speed adjustment member in the above-mentioned embodiment, the other gear of the clutch operating mechanism 5 comprised by the speed increase lubrication may be used as the rotation speed adjustment member. Moreover, you may make it apply a viscous body to the engagement part of the gear which comprises the planetary gear mechanism 22. As shown in FIG.

Each part which comprises the clutch operating mechanism 5 is demonstrated in more detail.

Next, the operation of the geared motor device of the above-described embodiment will be described.

In the geared motor apparatus, the pushing portion 41c of the cam face 41a of the clutch lever 41 described above is used to compress the clutch pinion 21 in the initial state in which no power is supplied to the motor 1. It is in the position to push against spring force of 18). For this reason, the clutch pinion 21 is pushed down in FIG. 5, and the hook 21d of the lower end of the clutch pinion 21 and the hook 11d of the upper end of the rotor 11 are combined. . That is, the second clutch means 4 is in a joint state, and the driving lubrication heat 2 connecting the rotor 11 and the output shaft 3 through the clutch pinion 21 is connected.

In such a state, when the clutch pinion 21 rotates together with the rotor 11 by the driving force of the motor 1, the rotation is performed by the sun gear 32 of the planetary gear mechanism 22 and several planet gears 36. And each planetary gear 36 rotates on the planetary gear support gear 34. For this reason, the ring gear 33 provided with the internal gear 33a which meshes with this planetary gear 36 rotates.

On the other hand, in this state, the induction pinion 16 rotates on the clutch operating mechanism 5 side in accordance with the rotation of the rotor 11. When the rotor 11 starts to rotate in the direction opposite to the normal direction at the beginning of rotation, as described above, the four recesses in which the protrusions 25c of the line tooth 25 are formed on the outer circumferential surface of the rotor 11 are described. It inserts into either of 11k, and changes the reverse rotation of the rotor 11 into a forward rotation.

In addition, immediately after the rotor 11 starts to rotate forward, the stopper portion 26 formed in the toothed gear 25 is in a position not engaged with any of the engaging portions 27a and 27b of the rotating member 27. . In other words, the rotation blocking mechanism A has not yet acted, and the blocking portion 26 is in a state where the rotation of the rotating member 27 is not prevented.

For this reason, the planetary gear mechanism 22 cannot stop the rotation of the ring gear 33 mentioned above. If the rotation of the ring gear 33 cannot be stopped, the rotational force on the rotor 11 side will cause the clutch pinion 21 to stop. After input to the planetary gear mechanism 22 through the transmission to the output shaft (3) and the rotating member 27 side from the planetary gear mechanism (22). Since the rotational torque transmitted to this rotating member 27 side is very small compared with the rotational torque of the driving wheel 2 side, the output shaft 3 cannot be rotated by the driving force between them. In this embodiment, such a state is referred to as the first clutch means being disconnected.

In the state where the first clutch means is cut off, the guide pinion 16 is rotated by the rotation of the rotor 11 without the reeling operation of the lever 8. Only the operation of rotating (26) integrally is performed. In addition, since the transmission path split from the planetary gear mechanism 22 toward the rotating member 27 becomes a speed lubrication heat, the time until the coupling between the stopper 26 and the rotating member 27, which is the starting point of the next operation, is extremely short. do.

In this operation, when the stop gear 25 receives the rotation of the guide pinion 16 and the stop portion 26 is rotated by a predetermined angle, the stop portion 26 is engaged with the rotating member 27 (27a) (27b). Move to a position that can be combined with any one of As a result, the rotation stopping mechanism A functions, and rotation of the rotating member 27 is prevented. As a result, all the parts constituting the clutch operating mechanism 5 are connected and rotation is stopped, and the gear teeth of the planetary gear mechanism 22 are stopped by the acceleration gear 28 being the last part of the clutch operating mechanism 5. 33) stops.

In this way, the rotation stopping mechanism A functions so that the respective parts of the clutch operating mechanism 5 (except the ring-shaped magnet 11c disposed on the rotor 11) and the planetary gear mechanism 22 serving as the first clutch means are provided. Rotation of the ring tooth difference 33 is stopped. As a result, the rotational force of the clutch pinion 21 which rotates integrally with the rotor 11 is transmitted only to the transmission gear 23 through the planetary gear mechanism 22, and the output gear part 3a is transmitted from the transmission gear 23. The output shaft 3, which receives the rotational force, rotates. That is, the first clutch means described above is connected, the rotational force of the rotor 11 is efficiently transmitted to the output shaft 3 through the drive wheel heat 2, and the output shaft 3 is rotated so that the lever 8 is pulled up. .

Then, when the output shaft 3 rotates by a predetermined angle and the lever 8 is pulled up to a predetermined position, the pushing portion 41c of the cam surface 41a of the clutch lever 41 is between the upper end of the clutch pinion 21. Move away from the face. Accordingly, the clutch pinion 21 is moved upward in FIG. 5 by the spring force of the compression coil spring 18, and the clutch pinion 21 is uncoupled from the rotor 11 to release the first clutch means ( 4) is cut off.

Of course, the rotor 11 continues to rotate if the energization state is maintained when the pulling operation is completed. In addition, the induction pinion 16 tries to follow the rotation operation of the rotor 11 while generating slip by the magnetic induction force, so that the above-described rotation stopping function of the rotation stopping member A is maintained. As a result, the joint state of the first clutch means described above is maintained.

On the other hand, the lever 8 tries to return to its original position by the load force exerted on itself. However, the return operation of the lever 8 is prevented by the lock of the clutch pinion 21 by the clutch lever 41 described above, and the lever 8 is fixed at the lifted position. That is, the blocking member (not shown) disposed on the clutch lever 41 contacts the contact member (not shown) disposed on the clutch pinion 21 which moves up and down by the rotation of the clutch lever 41, and thus the clutch pinion ( 21) to lock.

As described above, the clutch pinion 21 follows the slope of the cam surface 41a of the clutch lever 41 to move up and down. When the power is cut off and the output gear 3a rotates in the opposite direction to the normal driving by the load force, the cam surface of the clutch lever 41 is guided by the clutch lever operating groove 3b of the output gear 3a. The pushing down portion 41c of the 41a moves to a position away from the upper surface portion of the clutch pinion 21. At this time, the blocking member (not shown) disposed on the clutch lever 41 is away from the contact member (not shown) disposed on the clutch pinion 21. For this reason, when returning to the initial state where electricity was cut off, the clutch pinion 21 is pushed down by the clutch lever 41, and rotation rotation is not performed, and it becomes rotatable integrally with the rotor 11.

If the energized state is maintained when the pulled-up operation is completed in this way, the rotation stopping mechanism A in the clutch operating mechanism 5 functions to prevent rotation of the ring gear 33 of the planetary gear mechanism 22, and on the other side, The rotation of the sun gear 32 of the planetary gear mechanism 22 engaged with the clutch pinion 21 is prevented by the reverse rotation of the clutch pinion 21. That is, in such a state, two of the three main gears constituting the planetary gear mechanism 22 are stopped, and as a result, the entire driving lubrication train 2 does not operate at all. Can be. For this reason, the lever 8 does not go out to the outside of the case by the load force exerted on itself, and maintains the state in the raised position.

When the energization to the motor 1 is stopped in this state, the rotation of the rotor 11 stops. For this reason, the magnetic induction force between the induction pinion 16 and the rotor 11 disappears. For this reason, the preliminary wheel 25 which lost the driving force in the induction pinion 16 side rotates by the driving force which the induction pinion 16 receives by the biasing force of the spring 39 for rotational force with the blocking part 26. It rotates in the direction opposite to the direction (direction of arrow R5 in FIG. 6). As a result, the coupling between the stopping part 26 and the coupling part 27a and 27b of the rotating member 27 is released and the rotating member 27 is freed with respect to the blocking part 26. That is, the first clutch means described above is cut off.

Thus, when the connection by the magnetic induction force between the rotor 11 and the ring tooth 33 is released and the rotating member 27 is free, the return force of the lever 8 which cooperates with the rotation of the output shaft 3 is the ring tooth difference. It becomes a force to rotate 33, and the ring gear 33, the speed gear 28, and the rotating member 27 rotate. For this reason, the lever 8 comes out to a case outer side direction by the load which exceeded it. That is, the lever 8 returns to the position before drawing out. By the sliding operation of the lever 8 at this time, the output shaft 3 is integrally rotated in the opposite direction as in the above-mentioned pulling drive. The output gear 3a rotates integrally with the output shaft 3 by the rotation of the output shaft 3, and the clutch lever 41 is guided by the clutch lever operating groove 3b formed in the output gear 3a. ) Rotates. Accordingly, the clutch lever 41 makes the cam surface 41a contact the upper surface of the clutch pinion 21, and the clutch pinion 21 faces the spring biasing force of the compression coil spring 18 in the rotor 11 direction. Stop at the position to push down. As a result, the hook 21d of the clutch pinion 21 and the hook 11d of the rotor 11 are arranged to be engageable, and the first clutch means 4 returns to the initial state of being joined.

In addition, although each of the above-described embodiments is a suitable embodiment of the present invention, various modifications are possible without departing from the gist of the present invention. For example, in each of the above-described embodiments, the engaging portions 27a and 27b coupled to the stopping portion 26 of the tooth gear 25 serving as the rotation stopping member alternately in a zigzag pattern on the outer circumferential surface of the rotating member 27. Although arranged one by one, the order of arranging the engaging portions 27a and 27b may be random rather than zigzag. In addition, three or five or more may be used instead of four, and the number of coupling parts 27a and 27b may not be the same.

In each of the above-described embodiments, the rotational trajectory of the engaging portion of the rotary member 27 is composed of two types, but the rotary trajectory may be two or more kinds. For example, three engaging portions may be arranged on the outer circumferential surface of the rotating member 27 at different positions in the axial direction, and these three kinds of engaging portions may be arranged in a spiral or randomly arranged.

In each of the above-described embodiments, each engaging portion 27a, 27b is formed on the outer circumferential surface of the rotating member 27 so that all the engaging portions 27a, 27b are radially from the center of rotation of the rotating member 27. Although it arrange | positioned in equidistant position, it is not specifically limited to this structure. For example, engaging portions may be arranged at two or more different positions at rotation centers on one side in the axial direction of the rotating member 27, and two or more kinds of rotational trajectories may be formed. Even in this configuration, since the respective coupling portions are respectively coupled to different portions of the blocking portion, there is an effect of preventing excessive frictional coupling at a specific position of the blocking portion.

In the above embodiments, the materials of the rotating member 27 and the blocking portion 26 constituting the rotating stopping mechanism A are not specifically described. Since the number of frictional slidings at a predetermined portion is reduced by dispersing, the two members 27 and 26, which generate frictional friction, may be composed of members of the same material which are inherently prone to deterioration due to frictional sliding. You may comprise with a material. The absence of copper material makes the procurement of materials reasonable and reduces manufacturing costs.

As described above, according to the rotation stopping mechanism of the present invention and the geared motor device using the same, various types of coupling parts having different rotational trajectories are disposed on the rotating member, so that the rotating blocking member is driven with a predetermined drive, and any one of the coupling parts having multiple blocking parts is provided. Each time, they are combined at predetermined positions. That is, in the present invention, the contact position with the engaging portion of the stopper is distributed as many as the number of rotation trajectories. For this reason, the abrasion at the predetermined position of the blocking portion of the rotation stopping member is reduced. Further, in the engaging portion of the rotating member, since the number of times of contact with the blocking portion is distributed as much as the installed number, wear at the contact position is also reduced. As a result, abrasion is reduced at the contact positions of the two members that come into contact with each other in rotational restraint, and problems such as a failure in coupling in the rotational restraint caused by abrasion can be prevented, resulting in a structure that can withstand long-term use. do.

According to yet another aspect of the present invention, the operating member is connected in a non-contact manner by using a magnetic induction force on the rotor. Therefore, during normal rotation, friction due to contact between the operating member and the rotor does not occur at all, thereby improving service life. In addition, friction noise does not occur.

Further, according to another invention, by providing an assisting means for assisting other magnetic inducing forces of the magnet and the induction ring, the degree of freedom in construction can be increased to ensure sufficient magnetic induction by appropriately selecting the assisting means.

Claims (22)

It is possible to retreat forward and backward to the rotary member of the rotary member having different types of coupling parts having different rotation trajectories, and the rotary tracks of each of the various coupling parts, and to prevent the rotational operation of the rotating member by engaging somewhere in the coupling part at the time of entry. And a rotation stopping member having a blocking portion, wherein the blocking portion has a plurality of coupling portions engaging with the respective coupling portions according to rotational trajectories of the various types of coupling portions. The method of claim 1, And said various types of engaging portions are arranged at different positions in the axial direction at equidistant distances from the center of rotation of said rotating member, respectively. The method of claim 2, And the blocking portion is formed by a series of portions having a plurality of engaging portions with the respective engaging portions at the same position in the radial direction and at different positions in the axial direction. The method of claim 1, The blocking part is urged by the biasing member in the direction of stepping away from the rotational track at the same time and is driven to receive the rotational force from the other member so that the rotation stopping member is driven so as to enter the rotational track beyond the biasing force of the biasing member. And the rotational force from the other member is reduced so as to withdraw from the rotational trajectory by the force of the biasing member. The method of claim 4, wherein And the rotation stopping member is interlocked with a rotor serving as a driving source by using magnetic induction. Clutch means consisting of a planetary gear support gear for supporting planetary gears in the drive wheel heat disposed between the rotor and the output shaft, and a planetary gear mechanism comprising a sun gear and a ring gear engaged with the planetary gears; Iii) A clutch operating mechanism for performing the operation, and as a part of the clutch operating mechanism, the rotation stopping mechanism according to any one of claims 1 to 5 is used, and the rotation stopping mechanism restrains the rotating member. The geared motor, characterized in that the rotation of the rotor is transmitted to the output shaft through the other two gears by preventing the rotation of any one of the sun gear, the ring gear and the planetary gear support by the operation. And a rotor that rotates the output shaft through drive lubrication, and an operation member that is coupled by using magnetic induction to follow the rotation of the rotor and does not constitute the drive lubrication heat. It operates in conjunction with the rotational operation of the operating member, and enters the rotation region of the rotor to prevent the reverse rotation of the rotor and forcibly converts the rotor to the rotation in the normal direction by the reaction when the rotor is facing Geared motor comprising a member for preventing the reversal. An output shaft coupled to the rotor via drive lubrication to rotate and driven, a clutch means disposed in the drive lubrication to step through the drive connection between the rotor and the output shaft, and a clutch operating mechanism for stepping the clutch means; The operating mechanism is composed of one of a magnet or a nonmagnetic conductor that rotates integrally and interlocked with the rotor, and a magnet formed of the other of the magnet or nonmagnetic conductor that is rotated by magnetic induction on one side thereof. It has an induction rotation means and operates in conjunction with the other side of the magnetic induction rotation means, and when the rotor is rotated in the opposite direction to the normal direction while the clutch means are jointed, the reverse rotation is regulated and converted to the forward rotation. Geared motor, characterized in that provided with a member for preventing reverse. The method of claim 8, The clutch means is composed of a planetary gear support gear for supporting planetary gears, and a planetary gear mechanism comprising a sun gear and a ring gear meshing with the planetary gears, and utilizing the rotation of the other side of the magnetic induction rotating means. Geared motor, characterized in that for transmitting the rotation of the rotor to the output shaft through the other two gears by preventing the rotation of any one of the gear, the ring gear and the planetary gear support. The method of claim 9, The planetary gear supporting motor is connected to the output shaft side, and the planetary gear mechanism is used as a reduction mechanism. The method of claim 9, And the clutch operating mechanism regulates rotation of the ring gear of the planetary gear mechanism, and transmits rotation of the rotor to the output shaft by continuing the rotation of the sun gear and the planetary gear support gear. The method of claim 8, And the reversal preventing member is integrally formed with the gear engaging with the gear member which is integrally rotated with the other side of the magnetic induction rotating means. The method of claim 12, The geared motor, characterized in that the gear that is engaged with the gear member is formed with a rotation restricting portion for restricting the rotation of one of the gears constituting the planetary gear mechanism. An output shaft connected to the rotor and rotationally driven, a clutch means for stepping the connection between the output shaft and the rotor, and a clutch operation mechanism for stepping the clutch means, wherein the clutch operation mechanism is a ring interlocking with the rotor. One of a shape magnet or a nonmagnetic conductive ring, the other rotating and harvesting this one by magnetic induction, and a back yoke ring of a magnetic body disposed at a position where the nonmagnetic conductive ring is fitted to the ring-shaped magnet; And, Geared motor, characterized in that connecting the clutch means in conjunction with the other side to rotate the harvest. The method of claim 14, And said back yoke ring is attached to a rotating body to which said non-magnetic conductive ring is attached, and is configured to rotate integrally with said non-magnetic conductive ring. The method of claim 15, And the magnetic center in the thrust direction of the ring-shaped magnet and the magnetic center in the thrust direction of the back yoke ring are set to match or disagree with a predetermined position. The method of claim 14, The back yoke ring is attached to the rotating body attached to the ring-shaped magnet, the geared motor, characterized in that configured to rotate integrally with the ring-shaped magnet. The method of claim 17, A geared motor is formed between the nonmagnetic conductive ring and the back yoke ring or between the nonmagnetic conductive ring and the ring magnet, and a viscous body is disposed in the gap. The method of claim 18, The clutch operating mechanism includes the non-magnetic conductive ring and the back yoke ring facing each other through the gap in the operation of converting the clutch means from the end to the joint and the operation of the clutch means from the joint to the end. The nonmagnetic conductive ring and the ring-shaped magnet are configured to be different from each other, and the relative speed is high when the non-conductive ring is connected to the joint, so that the viscous force of the viscous body acts more strongly. In this case the geared motor, characterized in that the relative speed is slow so that the viscous force of the viscous body hardly acts. The method of claim 14, A geared motor, wherein a bearing portion of a rotating body having the nonmagnetic conductive ring is disposed on the rotor and a viscous body is attached to the bearing portion. The method of claim 14, The rotating member is provided with a rotating member biased in one rotational direction by a spring member in the clutch operating mechanism, and the rotating member is driven at a high speed by one of the ring-shaped magnet and the nonmagnetic conductive ring at high speed. The other side is harvested on one side and rotates in the other direction against the biasing force of the spring member, and at the same time, one of the ring-shaped magnet and the non-magnetic conductive ring rotates or stops at low speed and the other side is harvested. Iii) rotated in one rotational direction by the biasing force of the spring member when the rotation is slow or stopped, and when the pivoting member is rotated in the other rotational direction against the biasing force of the spring member or The heating member is set to generate heat when rotating in one rotational direction by the biasing force of the spring member When the spring member is disposed in the vicinity of the spring member, the spring force is changed at the time of heat generation and non-heating of the heat generating member, and the spring force rotates the rotating member against the spring force of the spring member. Geared motor, characterized in that consisting of a shape memory spring set to weaken. An output shaft connected to the rotor and rotationally driven against a predetermined load, a clutch means for stairing transmission of power between the output shaft and the rotor, and a clutch operating mechanism for stepping the clutch means, The clutch means is provided with two teeth each capable of transmitting power from the rotor to a separate series of lubrication heat, and becomes a jointed state by stopping rotation of one tooth by the clutch operating mechanism among these two teeth, Configured to transmit power from the rotor to the output shaft through drive lubrication coupled to the gear, The clutch operating mechanism includes a magnetic induction means composed of an increase in speed lubrication connected to one of the gears, one of a magnet or a non-magnetic conductive member interlocking with the rotor, and the other of which is harvested and rotated on one side by magnetic induction; By interlocking with the other side of the magnetic induction means to prevent the rotation of the coupling gear constituting a part of the speed increase lubrication means to convert the clutch means from disconnection to the joint and at the same time stop the rotor to stop the magnetic induction and the coupling gear and The clutch is provided with a clutch converting member for releasing the coupling to convert the clutch means from the joint to the stop, The speed increase lubrication is received through the clutch means when the output shaft is rotated in the direction opposite to the rotation direction of the output shaft by the driving force of the rotor by the clutch means is converted from the joint to the stop. It is configured to transmit the rotation while increasing the speed, and at the same time the rotational speed control means consisting of a wing portion for adjusting the rotational speed by air resistance or a viscous body for controlling the rotational speed by the viscous resistance is disposed on the rotating member Featuring a geared motor.