JPH0877Y2 - Motor actuator - Google Patents

Description

The present invention relates to a motor actuator suitable as a drive source for an opening / closing mechanism such as a drain valve of a washing machine, a shutter of a ventilation fan, or a damper for a refrigerator.

(Prior Art) Conventionally, for example, there is one using a motor actuator as a drive source for opening and closing a drain valve of a washing machine. This type of motor actuator connects the reduction gear train to the rotor of the synchronous motor, uses the final stage as the output shaft, rotates the rotor of the synchronous motor by energizing the coil winding, and uses the pulley provided on the output shaft. For example, the wire connected to the valve element biased in the closing direction is wound up to open the drain valve. When the drain valve is closed, the coil winding is de-energized and the drain valve is returned to the closed state by the biasing force of the valve body in the closing direction. At this time, the output shaft connected to the valve element also idles and returns to its original position.

(Problems to be Solved by the Invention) According to the conventional motor actuator as described above, when the driven mechanism such as the drain valve is driven and operated, and then the driven mechanism is returned, the driven mechanism is attached. There was a case where the force suddenly returned to the original position and a large impact force was generated, and this impact force generated a large impact noise, disconnection of the coil winding, and destruction of structural parts. .

The present invention has been made in order to solve the above-mentioned problems of the prior art, and prevents the generation of impact force by braking the rotational force that acts on the output shaft when the driven mechanism returns, It is possible to prevent the generation of large impact noise, disconnection of the coil winding, destruction of structural parts, etc. Also, the braking means does not load the motor when operating the driven mechanism, or is extremely small even if it becomes a load. An object of the present invention is to provide a motor actuator capable of protecting the motor by providing a load and preventing the rotational force from the driven mechanism from being transmitted to the rotor of the motor during the operation of the braking means.

(Means for Solving the Problems) The present invention provides a rotor that rotates by energizing a coil winding, and an output shaft that is connected to the rotor through a reduction gear train and that drives and operates a driven mechanism. A braking mechanism for braking the rotation of the output shaft when the output shaft is rotated by a load from the driven mechanism side, and a clutch provided in the reduction gear train. Having a rotating body that rotates with the rotation of the gears in a row, the rotating body rotating to generate a braking force on the rotating body itself, and the rotating body rotating at a high speed to increase the braking force. And on the driven side of the clutch,
It is characterized in that it is provided at a position where the speed is increased when viewed from the output shaft side and the output shaft is rotated to rotate at high speed.

(Operation) When the coil winding is energized, the rotor rotates, the output shaft is rotationally driven through the reduction gear train, and the driven mechanism is driven. When returning, the output shaft rotates due to the load from the driven mechanism side, but the braking means provided at the position where the speed is increased when viewed from the output shaft side rotates at high speed to perform braking operation, and the output shaft rotates. Apply braking so that the speed does not exceed a certain speed. Further, during this braking operation, the clutch releases the transmission of the rotational force, and the rotor of the motor does not rotate.

(Example) Hereinafter, an illustrated example configured to open and close a drain valve of a washing machine will be described.

1 to 3, a case 1 and the case 1 are shown.
An actuator box is formed by the cover 2 that is covered with the cover 2 and is fastened to the case 1 by the tapping screw 3. A cup-shaped motor case 21 (see FIG. 2) is fixed to the bottom of the case 1. Motor case 21
A motor bobbin 23 is fitted on the inner peripheral portion of the bottom of the. A motor winding 25 is provided on the motor bobbin 23. A rotor 31 is arranged on the inner peripheral side of the motor bobbin 23. The rotor 31 has a motor shaft 27 and a rotor magnet 32 fixed to the motor shaft 27 via a bush 33 and a holding body 49. A motor including such a rotor 31 and a motor winding 25 constitutes a known single-phase synchronous motor, and supplies a single-phase alternating current to the single-winding winding 25 to surround the rotor magnet 32. Every other comb-like pole tooth is N
An alternating magnetic field is generated by alternately magnetizing the poles and the S poles, and the rotor 31 rotates in synchronization with this alternating magnetic field. A spring 30 is interposed between the rotor 31 and the motor case 21, and the spring 30 biases the rotor 31 in the thrust direction. The rotor 31 has a fourth
As shown in the figure, the engaging projection 50 protruding in the radial direction is integrally formed, and the gear 48 is integrally formed.

As shown in FIG. 3, a bottom plate 22 is fixed to the inner bottom surface of the case 1, and an intermediate plate 65 is arranged above the case 1 with a certain distance from the case 1. Above main plate
A shaft 28 is supported between the motor 22 and the intermediate plate 65 in the vicinity of the gear 48 of the motor, and further shafts 46, 47, 29 are supported and an output shaft 44 is also supported. The output shaft 44 can rotate itself. The shaft 28 has a gear that meshes with the gear 48.
34 is rotatably fitted and a one-way regulating lever 35 is rotatably fitted under it. Lever 35 is gear 34
The rotation of the gear 34 allows the gear 34 to rotate in the rotation direction by frictional force, but the rotation range is restricted by the stopper. More specifically, as shown in FIG. 4 (a), the rotation of the protrusion 50 is restricted by contacting the boss portion of the protrusion 50, and the pin of the lever 35 is pinned as shown in FIG. 4 (b). 35b comes into contact with the stopper 68 to restrict the counterclockwise rotation.
Then, at the position shown in FIG. 4 (a), one end 35a of the lever 35 advances into the counterclockwise rotation passage of the engaging projection 50, and the engaging projection 50 further rotates counterclockwise. In the position shown in FIG. 4 (b), one end of the lever 35 is blocked.
35a escapes to the outside of the rotation path of the engaging projection 50. Above lever 35
Is for restricting the rotation direction of the rotor 31 of the synchronous motor to one direction, and when the rotor 31 tries to rotate in the direction opposite to the predetermined direction, the engagement projection 50 is generated as shown in FIG. 4 (a). It abuts on one end 35a of the lever 35, and its reaction reverses the direction of rotation of the rotor 31 to rotate it in a predetermined direction. Rotor 31
Is rotated in the specified direction, the lever 34
35 rotates counterclockwise as shown in FIG. 4 (b), and one end 35a thereof escapes from the rotation range of the engaging projection 50, and allows the rotor 31 to rotate in a predetermined direction.

The shaft 28 also has a repulsion spring above the gear 34 and above.
A gear 37 is fitted via 36 so as to be rotatable and slidable along a shaft 28. The lower end of the gear 37 has an engaging hole for the gear 34.
An engaging protrusion 37a that can be engaged with 34a is formed, but normally the engaging protrusion 37a is separated from the engaging hole 34a by the elastic force of the spring 36. An operating piece 39, which is slidable along the shaft 28 and along an appropriate guide hole, is mounted on the upper end of the gear 37. Working piece
39 includes, for example, a disc-shaped lower portion and a plurality of transmission portions that penetrate the sliding contact chamber 46. The plunger 7 is further mounted on the upper end of the operating piece 39. The plunger 7 has a solenoid winding 10
The center hole of the bobbin 8 provided with can be slid up and down. The bobbin 8 is magnetically connected at its upper and lower ends by two iron cores 5 and 6. When the winding 10 is energized, the plunger 7 is attracted downward, and the gear 37 is pushed downward against the urging force via the operating piece 39, as shown in FIG. The gear 37 is engaged with the engagement hole 34a of the gear 34 to rotate the gear 37 integrally with the gear 34. Above winding 10,
The plunger 7, the gear 37, the gear 34, and the spring 36 constitute a clutch mechanism. The gear 34 forms the clutch driving body, and the gear 37 forms the clutch driven body.

The gear 37 constantly meshes with a large diameter gear 40a rotatably provided on a shaft 46, and a small diameter gear 40b formed integrally with the gear 40a.
Meshes with a large diameter gear 41a rotatably provided on the shaft 47, and a small diameter gear 41b integrally formed with the gear 41a meshes with a large diameter gear 42a rotatably provided on the shaft 29 to form an integral body with the gear 42a. The formed small diameter gear 42b meshes with a gear 43 integrally provided on the output shaft 44. Gear train 48-3 described above
The 4-37-40a-40b-41a-41b-42a-42b-43 configures a reduction gear train for transmitting the rotational force of the rotor 31 to the output shaft 44.

The output shaft 44 projects above the intermediate plate 65 and further projects above the cover 2. The cam 11 is integrally fitted to the output shaft 44 between the intermediate plate 65 and the cover 2, and the pulley 18 is integrally fitted thereon. The pulley 18 has its boss portion fitted in the shaft hole of the cover 2 and also has a stopper spring.
It is locked by 20. As shown in FIG. 1, a recess 11a is formed in the outer peripheral portion of the cam 11 which forms the cam edge. The bent portion 12a of the contact plate 12 is in sliding contact with the cam edge of the cam 11, and the contact plate is attached to the contact 14 fixed to the tip of the contact plate 12.
13 tips are facing each other. The two contact plates 12 and 13 constitute a switch for controlling the energization of the motor, and when the bent portion 12a of the contact plate 12 falls into the concave portion 11a of the cam 11, the switch is turned off to the motor. Turn off the power supply. It is when the driven mechanism is driven to a predetermined position that the two contact plates 12 and 13 are separated from each other and the switch is turned off.

In FIG. 1, a single-phase AC power source is externally supplied between the contact plate 13 and another contact plate 15, and this AC power source is rectified by a diode 16 and smoothed by a capacitor 17 so that the winding 10 is It is used as a DC power supply for excitation.

As shown in FIG. 10 and FIG. 11, the pulley 18 is provided with an axial hole 18a for fitting and connecting one end of a wire 19 for driving and operating a driven mechanism, and an axial hole 18a following this. Radial groove 18b followed by circumferential winding groove 1
With 8c. One end of the wire 19 is fitted into the hole 18a, then bent along the groove 18b to be connected to the pulley 18, and further wound around the winding groove 18c. Winding groove 1
8c can wind the wire 19 within a range of about 270 degrees, and as shown in FIG. 10, the radius decreases as the winding angle of the wire 19 increases.

The other end of the wire 19, one end of which is connected to the pulley 18,
As shown in FIG. 9, it is connected to a rod 57 of a drain valve mechanism 63 of a washing machine as a driven mechanism via an intermediary plate 51 and a connecting body 58. The drainage valve mechanism 63 includes a casing 53, a lid 56 thereof, a bellows 55 arranged in the casing 53, and a rod 57 to urge the conical end portion 55a of the bellows 55 into an inclined wall 53a of the casing 55. And a spring 59 for pressing against. A water inlet 52 and a water outlet 54 are formed in the casing 55, and between the water inlet 52 and the water drain 54 when the end portion 55a of the bellows 55 is pressed against the inclined wall 53a of the casing 53 by the urging force of the spring 59. Will be closed. On the other hand, when the wire 19 is wound around the pulley 18 by the rotational drive of the pulley 18, the rod 57 is pulled against the urging force of the spring 59 and the end portion 55 of the bellows 55 is pulled.
a is separated from the inclined wall 53a of the casing 53, and the water inlet
The water introduced from 52 is drained through the drain port 54.

In FIG. 3, the center hole of the friction braking body 38 made of rubber or the like is fitted and fixed to the upper boss portion of the gear 37 on the shaft 28. As shown in FIG. 6, the friction braking body 38 includes a hole 38a for fitting into the boss portion of the gear 37, a boss portion 38b surrounding the hole 38a, and a pair of radially extending boss portions 38b. It has an arm portion 38d, a pair of weight portions 38e extending in the circumferential direction from the arm portion 38d, and a narrow circumferential arm portion 38c connecting the weight portion 38e and the arm portion 38d. . The friction brake 38 has its weight portion when not rotating.
38e is placed on the brim-shaped portion of the gear 37 so as not to hang down. The friction braking body 38 constitutes a rotating body of braking means, and is a sliding contact chamber integrally formed with the intermediate plate 65.
When the friction braking body 38 is rotationally driven and the weight portion 38e is expanded from the arm portion 38c by the centrifugal force,
A braking force is generated by the tip outer peripheral portion 38f of the weight portion 38e slidingly contacting the friction wall 46a which is the inner peripheral surface of the sliding contact chamber 46. Here, the rotor 31 of the synchronous motor is rotationally driven in a predetermined direction, the output shaft 44 is rotationally driven in a predetermined direction, the wire 19 is wound around the pulley 18, and the drain valve mechanism 63 as a driven mechanism is opened. When the friction braking body 38 is rotated, the friction braking body 38 rotates in the direction of the solid line arrow in FIG. 6, and even if the weight portion 38e expands, the tip outer peripheral portion 38f makes sliding contact with the friction wall 46a in a slippery direction. Therefore, a large braking force is not applied to the rotation of the motor. On the other hand, the drain valve mechanism 63 uses the spring 59
When returning to the original position by the elastic force of, the friction braking body 38 is rotationally driven in the opposite direction via the pulley 18, the output shaft 44, and the gear train as shown by the broken line arrow in FIG. Since the tip outer peripheral portion 38f of the expanded weight portion 38e slides in a direction to bite into the friction wall 46a, a large braking force is exerted, and the drain valve mechanism 63 is returned relatively slowly. The components including the friction braking body 38 and the cylindrical portion 46 are braking means 64.
Is composed.

As described above, the winding 10, the plunger 7, the gear 3
A clutch consisting of a gear 34 and a spring 36 is provided between the gear 34 and the gear 37 that form the reduction gear train, and the braking means 64 is a gear that is a driven body of the clutch. It is provided at the position where the speed is increased on the 37 side when viewed from the output shaft 44 side.

The braking means may be of the type shown in FIGS. 7 and 8, for example. In FIGS. 7 and 8,
The friction braking body indicated by reference numeral 60 has a hole 60a to be fitted to the shaft 28, a pair of thin arm portions 60b extending radially from a boss portion around the hole 60a, and an outer portion from the arm portion 60b. It has a weight portion 60c extending in one direction and a sliding contact portion 60d integrally provided on the upper end of the weight portion 60c. The center of gravity of the weight portion 60c is below the arm portion 60b. When the friction braking body 60 rotates together with the shaft 28, the arm portion 60b warps upward due to the centrifugal force acting on the weight portion 60c, and the sliding contact portion 60d slides on the friction plate 61 to generate a braking force.
However, when the gear 37 descends and engages with the gear 34, the friction braking force is not generated because it is away from the friction plate 61,
Only when the gear 37 is moving upward is the sliding contact portion 60d the friction plate 61d.
The frictional braking force is generated by sliding on.

 Next, a series of operations of the above embodiment will be described.

In the initial state in which AC power is not supplied between the two contact plates 15 and 17, the cam 11 is rotating from the position shown in FIG. 1, and the bent portion 12a of the contact plate 12 is caused by the large-diameter cam edge of the cam 11. Is pushed outward to bring the contact plates 12 and 13 into conduction. Therefore, when the dehydration work is to be started, AC power is supplied between the contact plates 15 and 13 by a predetermined switch operation, and a single phase is applied to the coil winding 25 of the synchronous motor through the switch composed of the contact plates 12 and 13. AC power is supplied to rotate the rotor 31.
At this time, if the rotor 31 tries to rotate in the direction opposite to the predetermined direction, the engaging projection 50 contacts the one end 35a of the lever 35 as described with reference to FIG. 4, and the reaction thereof causes the rotor 31 to rotate normally. It reverses the direction and continues to rotate in the regular direction.

Further, at the same time as the supply of the AC power, the DC power rectified by the diode 16 and smoothed by the capacitor 17 is supplied to the solenoid winding 10. As shown in FIG.
6 and the gear 37 is actuated against the urging force of the spring 36.
Moved down via 9. As a result, the engagement portion 37a of the gear 37 and the engagement hole 34a of the gear 34 are engaged with each other, the gears 34, 37 rotate integrally, and the rotational force on the rotor 31 is applied to the output shaft 44 via the reduction gear train. This is transmitted, and the output shaft 44 is rotationally driven.
At this time, the friction braking body 38 also rotates, but the rotation speed of the friction braking body 38 at this time is relatively slow, the centrifugal force acting on the weight portion 38e is small, and the friction load with the friction wall 46a is extremely small.

By rotating the output shaft 44, the cam 11 and the pulley 18 also move to the 10th position.
In the figure, it is driven to rotate counterclockwise. The wire 19 is wound around the winding groove 18c by the rotational drive of the pulley 18, the rod 57 of the drainage valve mechanism 63 shown in FIG. 9 is pulled against the biasing force of the spring 59, and the end 55a of the bellows 55 is pulled. Is separated from the inclined wall 53a of the casing 53, and the water inlet 52 and the water outlet 54
And the water introduced from the water inlet 52 are discharged from the water outlet 54.

Further, when the sliding contact position of the bent portion 12a of the contact plate 12 reaches the concave portion 11a of the cam 11 by the rotation of the cam 11 as shown in FIG. The supply of power to the motor is cut off, and the rotation of the rotor 31 stops.
However, since the solenoid winding 10 is continuously energized, the gear 34 and the gear 37 are integrally connected. When the motor is stopped, the wire 19 is pulled back toward the original position by the urging force of the spring 59 of the drainage valve mechanism 63, the pulley 18 tries to rotate in reverse with this, and the wire of the motor is moved through the gear train. Although the rotor 31 tends to be rotationally driven in the opposite direction, the gear train becomes a speed increasing gear train when viewed from the output shaft 44 side, and the torque for rotating the gear 28 is extremely small, and the rotor 31 rotates. In order to make the gear 34 rotate in the reverse direction, the lever 35 frictionally engaged with the gear 34 is rotated and one end 35a of the lever 35 is engaged with the engagement protrusion 50 of the rotor 31. Rotating into the rotating passage of the rotor 31
In order to prevent the reverse rotation of the drain train, the gear train and the pulley 18 cannot rotate, the drain valve mechanism 63 cannot return to the original position, and the drain valve is held in the open state. Work is done.

When the dehydration work is completed, the power supply between the terminals 13 and 15 is stopped, and the energization of the solenoid winding 10 is stopped. Winding
When the power supply to 10 is stopped, the plunger 7, the operating piece 39 and the gear 37 are returned to the original position shown in FIG. 3 by the urging force of the spring 36, and the gear 34 and the gear 37 forming a part of the clutch are engaged. Is released, the rotation stop of the gear train due to the motor load and the rotation stop of the gear train due to the engagement between the lever 35 and the engagement projection 50 are released, and the pulley 59 is released by the biasing force of the spring 59 of the drainage valve mechanism 63.
18, gear train 43-42b-42a-41b-41a-40b-4 via output shaft 44
0a-37 spins in the opposite direction. Since the gear train constitutes a speed-increasing gear train when viewed from the output shaft 44 side, the gear 37 tends to be rotationally driven at high speed. However, due to the rotation of the gear 37, a centrifugal force is generated in the weight portion 38e of the friction braking body 38 shown in FIG. 6, the centrifugal force is expanded from the arm portion 38c, and the tip outer peripheral portion 38f is brought into sliding contact with the friction wall 46a to generate a braking force. . Moreover, the direction of rotation of the friction braking body 38 at this time is the direction shown by the broken line arrow in FIG. 6, and the tip outer peripheral portion 38f is the direction that bites into the friction wall 46a, so that the braking force is effective. appear. Thus, when the gear 37 tries to rotate at a high speed, the braking force acts to control the gear 37 at a substantially constant speed, and the return operation of the drain valve mechanism 63 is performed slowly. On the other hand, when the speed of the gear 37 decreases, the centrifugal force generated in the friction braking body 38 decreases and the tip outer peripheral portion
Since 38f separates from the friction wall 46a and releases the braking force, the return of the drainage valve mechanism 63 does not stop halfway.

As the output shaft 44 reversely rotates, the cam 11 also rotates toward the original position, and the bent portion 12a of the contact plate 12 is attached to the large diameter portion of the cam edge.
Slides into contact with each other to turn on the switch composed of the two contact plates 12 and 13, and the drain valve mechanism 63 returns to its original position and stops at a position where the pulling force applied to the wire 19 becomes zero.

According to the embodiment described above, when the drain valve mechanism is opened and then closed by the urging force of the drain valve mechanism, the load from the drain valve mechanism side, that is, when the output shaft 44 rotates in the opposite direction by the urging force, The output shaft 44 and the drainage valve mechanism 63 connected thereto are braked by the braking means 64, and the drainage valve mechanism 63 slowly returns to the original position, so that the impact force due to the return of the drainage valve mechanism 63 is small, It is possible to reduce impact noise and prevent disconnection of coil windings and destruction of structural parts due to impact force. At this time, since the clutch releases the transmission of the rotational force, the rotor of the motor is not rotated at a high speed, and the motor can be protected. Also, when trying to hold the driven mechanism at a predetermined operating position, by engaging the clutch, the reduction gear train becomes a speed-increasing gear train when viewed from the output shaft 44 side and becomes a large resistance. Since the detent torque can be added, there is an advantage that it is not necessary to separately provide means for holding the driven mechanism at a predetermined operating position. On the other hand, the braking means 64 is provided on the gear 37 side, which is the driven body of the clutch, at a position where the speed is increased when viewed from the output shaft 44. Rotational force is increased and rotationally driven at high speed, braking force can be effectively generated, and when the drainage valve mechanism 63 is opened by the rotational force of the motor, it rotates at low speed, so it does not become a load on the motor. However, even if it becomes a load, it becomes only a very small load.

The inner peripheral portion of the sliding contact chamber 46 in which the friction braking body 38 is arranged is
When the upper half portion has a small diameter and the lower half portion has a large diameter, and the gear 37 is raised and disengaged from the gear 34 as shown in FIG. 3, the friction braking body 38 has a small diameter in the sliding contact chamber 46. The friction braking body 38 may face the large diameter portion of the sliding contact chamber 46 when the gear 37 is lowered and engaged with the gear 34 as shown in FIG.
With this configuration, a braking force is hardly generated during the normal rotation by the motor, and a large braking force can be generated when returning to the original position by the biasing force on the drain valve mechanism side.

Further, according to the illustrated embodiment, the winding groove of the pulley 18
Since the diameter of 18c is successively decreased, the winding torque increases as the wire 19 is wound. This is because the drain valve mechanism 63 is biased by the spring 59, and it is necessary to pull the rod 57 against this biasing force, and the pulling torque increases as the rod 57 is pulled. In response to this, the winding torque by the pulley 18 is gradually increased. FIG. 12 shows the relationship between the load L on the drain valve mechanism 63 side and the pulling torque Q by the pulley 18. When the wire 19 is started to be pulled by the pulley 18, the pulling force by the pulley 18 increases as the load L increases as described above, and the torque applied to the output shaft 44 becomes substantially constant. As described above, by increasing the pulling force with the increase of the load L, the torque of the motor can be effectively used, and the motor can be applied to a motor having a relatively small torque.

According to the present invention, when the driven mechanism is operated and then returned, the output shaft is rotated in the opposite direction by the load from the driven mechanism side, and the output shaft and the The driven mechanism connected to this is braked, and the driven mechanism slowly returns to its original position, so the impact force associated with the return of the driven mechanism is small, and therefore, the impact noise can be reduced and the impact sound can be reduced. It is possible to prevent disconnection of the coil winding and destruction of structural parts due to force. Also, when the driven mechanism is being braked by the braking means,
Since the clutch releases the transmission of the rotational force, the rotor of the motor is not rotated at high speed and the motor can be protected. When trying to hold the driven mechanism at a predetermined operating position, by engaging the clutch, the reduction gear train becomes a speed increasing gear train when viewed from the output shaft side and becomes a large resistance, which causes the motor detent torque to increase. Since it can be added, there is an advantage that it is not necessary to separately provide a means for holding the driven mechanism at a predetermined operation position. On the other hand, the braking means is provided on the driven body side of the clutch at a position where the speed is increased when viewed from the output shaft. Therefore, when the braking operation is performed, the rotational force from the output shaft is increased to rotate at high speed. It is driven to effectively generate a braking force, and the braking means does not rotate at a low speed when the driven mechanism is opened by the rotational force of the motor and does not become a load on the motor. Can be used.

[Brief description of drawings]

1 is a partial sectional plan view showing an embodiment of a motor actuator according to the present invention, FIG. 2 is a partial sectional side view of the same as above, and FIG. 3 is a sectional view taken along the line connecting points OABCDE in FIG. Fig. 4 is a development view, Fig. 4 is a plan view showing the one-way regulating mechanism portion in each of the above-mentioned embodiments for different operation modes, and Fig. 5 is a cross-sectional development view showing different operation modes of the above-mentioned embodiment according to Fig. 3, FIG. 6 is a plan view of the friction braking body in the above embodiment, FIG. 7 is a perspective view showing another example of the friction braking body, and FIG. 8 is a side view showing an example of braking means using the same friction braking body. FIG. 9 is a partial sectional plan view showing an example of a driven mechanism, FIG. 10 is a plan view showing a pulley in the above embodiment, FIG. 11 is a front sectional view of the same as above, and FIG. 12 is the above embodiment. 6 is a diagram showing the relationship between the load and the pulling force in FIG. 25 ... Coil winding, 31 ... Rotor, 44 ... Output shaft, 63 ...
... Driven mechanism, 64 ... Braking means.

Claims (1)

[Scope of utility model registration request] Claim: What is claimed is: 1. A rotor that rotates by energizing a coil winding, an output shaft that is connected to the rotor through a reduction gear train, and that drives and operates a driven mechanism, The output shaft is rotated by a load, and braking means for braking the rotation is provided, and a clutch provided in the reduction gear train. The braking means is provided with rotation of gears in the reduction gear train. The rotating body has a rotating body, and when the rotating body rotates, a braking force is generated in the rotating body itself, and when the rotating body rotates at a high speed, the braking force increases. A motor actuator, wherein the motor actuator is provided at a position on the driving body side where the speed is increased as viewed from the output shaft side and the output shaft is rotated to rotate at a high speed.