JP3069711B2 - Geared motor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a geared motor which can be used for driving a load having a restoring force.

[0002]

2. Description of the Related Art There is a geared motor including a motor, an output member for driving the load, and a transmission mechanism interposed therebetween.

[0003]

In the conventional geared motor, when the output member is operated by rotating the motor to drive the load, there is a risk that the load may be excessively driven and damaged. Therefore, in order to eliminate such a danger, it is necessary to interpose a clutch (first clutch) which becomes disconnected when the output member reaches the operating position in the transmission mechanism. However, there is a problem that if the load has a restoring force and the clutch is disengaged after driving it, the load will return unexpectedly. Therefore, in order to prevent the return, it is necessary to provide a check mechanism on the output member side of the clutch. However, if the check mechanism is provided, even if it is desired to restore the load, it cannot be performed. Therefore, another clutch (second clutch) is provided closer to the output member than the check mechanism, and It is necessary to be able to return the load as desired by operation. However, with such a configuration, there is a problem that the structure is complicated by many mechanisms such as the first clutch, the check mechanism, the second clutch, and the like, so that a large manufacturing cost is required and the product price becomes extremely high. .

The present invention has been made to solve the above-mentioned problems (technical problems) of the prior art. A clutch provided in a transmission mechanism has a main driving member and a driven member arranged side by side on the same axis. At the same time, by providing a configuration in which a coil spring is provided so as to straddle them, (a) driving of a load,
(B) prevention of breakage due to overdriving of the load, (c) holding of the load in the operating state (prevention of unintended return), and
(D) The load can be restored at the user's discretion, and such various actions can be performed by the clutch having the simple structure as described above. It is an object of the present invention to provide a geared motor that can be provided.

[0005]

In order to achieve the above object, a geared motor according to the present invention comprises a motor, an output member for driving a load having a restoring force, and a transmission interposed therebetween. Wherein the transmission mechanism is a geared motor having a clutch in the middle, wherein the clutch is provided with a round bar-shaped main driving member and a driven member, each of which is rotatably juxtaposed on the same axis. A coil spring which is provided so as to be able to pivot relative to the two in a state of being straddled, and the main driving member is connected to the motor side in the transmission mechanism, while the driven member is connected to the output member side, and The coil spring has a winding direction in which the coil spring is reduced in diameter when the end on the main driving member side is rotated in the same direction as the rotation direction of the main driving member by the motor with respect to the end on the driven member side. The inner peripheral surface of the portion located on the outer peripheral side of the driving member is elastically contacted with the outer peripheral surface of the driving member, and the end of the coil spring on the driving member side relative to the driving member. A first idler member rotatably provided is fixed to the first idler member, and the idler member is connected to a locking mechanism for locking the idler when the output member reaches the operating position. On the other hand, the end of the coil spring on the driven member side is fixed to a second idle member provided rotatably relative to the driven member, and the idle member is attached to the idle member when the motor rotates. An urging force applying mechanism for applying an urging force for winding a portion of the coil spring located on the outer peripheral side of the driven member around the driven member is connected to the idle member.

[0006]

When the motor rotates, the coil spring is wound around the driven member by the urging force applied to the second idler member. Therefore, the rotation of the motor is transmitted to the main driving member, the coil spring, and the driven member to reach the output member, which operates. When the output member reaches the operating position, the first idler member is locked. as a result,
Slip occurs between the coil spring and the driving member, and the operation of the output member stops. In this case, the transmission of the force to the output member is continued by the frictional force between the coil spring and the driving member. When the motor stops, the urging force applied to the second idler member disappears, and the winding of the coil spring on the driven member is released. As a result, the driven member can freely rotate, and the output member is in a free state.

[0007]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. In FIG. 1, A is a motor, B is an output member for driving a load, C is a transmission mechanism interposed between the motor A and the output member B, and a reduction section D, a clutch E, The speed reduction unit F and the output member drive mechanism G are connected to each other.

As the motor A, a small motor known as a timer motor is used. For example, an inductor motor using a permanent magnet for a rotor is used. Reference numeral 1 denotes a pinion attached to the rotation shaft. 2 indicates a power switch, and 3 indicates a power plug.

Next, as the output member B, a rack capable of freely moving in the longitudinal direction is used. As shown in FIGS. 1 and 4, this rack is formed by forming teeth 5 on both one side of the rod-shaped member and the side opposite thereto, and furthermore, the distance between the center line 5a in the reciprocating direction and the teeth. The distance is changed in the forward and backward directions in accordance with the drive gear described later.
Reference numeral 6 denotes a connection member with a load, to which a load having a restoring force is connected. As the output member B, a gear or pulley that performs a rotation operation may be used instead of the rack.

Next, the speed reduction section D is composed of large and small gears 8-10. The gears 8 and 9 are integrated. In the drawings, the chain line connecting the teeth of the gears indicates the meshing of the teeth.

Next, the clutch E will be described with reference to FIGS. Reference numeral 12 denotes a driving member and reference numeral 13 denotes a driven member, each of which is formed in a round bar shape and is arranged side by side so as to be relatively rotatable on the same axis. Any of these may be formed of a material having high wear resistance. In this example, it is formed of brass. In each thickness, the diameter of the main driving member 12 is large, and the diameter of the driven member 13 is smaller than that. The driving member 12 is integrated with the gear 10. Next, 14 is a coil spring,
It is provided so as to straddle both the driven member 12 and the driven member 13. That is, the half part 15 on one end side is located on the outer peripheral side of the main driving member 12, and the half part 16 on the other end side is located on the outer peripheral side of the driven member 13. The inner diameter of the coil spring 14 in the free state is smaller than the outer diameter of the driving member 12 and larger than the outer diameter of the driven member 13, and the inner peripheral surface of the half portion 15 is formed on the outer peripheral surface of the driving member 12. There is a gap between the inner peripheral surface of the other half 16 and the outer peripheral surface of the driven member 13 due to elastic contact. The coil spring 14 is formed using a wire having a rectangular cross section so as to increase the contact area with the outer peripheral surfaces of the driving member 12 and the driven member 13. The winding direction of the coil spring 14 is such that when the one end 15a is turned in the same direction as the rotation direction of the driving member 12 by the motor A with respect to the other end 16a, the diameter of the coil spring 14 decreases. A first idler member 17 is attached to the driving member 12 so as to be rotatable relative to the driving member 12. The first idler member 17 controls the transmission and cutoff of rotation between the driving member 12 and the coil spring 14. One end 15 of the coil spring 14 is fitted to a fitting portion 18 formed partially.
a is fitted. Further, on the outer periphery, a large number of concave and convex engaging portions 19 for connection with a locking mechanism H described later are formed. Reference numeral 20 denotes a second idler mounted on the driven member 13 so as to be relatively rotatable.
It controls rotation transmission and cutoff between the coil spring 14 and the driven member 13, and the other end 16a of the coil spring 14 is fitted to a fitting portion 21 provided therein. Further, teeth are formed on the outer periphery, and gears for linking with an urging force applying mechanism I described later.
22.

Next, the speed reduction unit F is constituted by large and small speed reduction gears 24 to 26 as shown in the figure. Gears 25, 26
Are integrated. The gear 24 is integrally connected to the driven member 13.

Next, the output member driving mechanism G will be described. The mechanism G includes a distribution mechanism 30 for distributing the rotational force given from the speed reducer F to two, and two drive gears 31 and 32 for transmitting the distributed rotational force to the output member B.
First, the distribution mechanism 30 will be described with reference to FIGS. The mechanism 30 includes a driving body 33 and first and second driven bodies 34 and 35 arranged side by side so as to be relatively rotatable on the same axis.
And a transmission piece 36 for transmitting the rotational power of the driving body 33 to each of the driven bodies 34 and 35. The driving body 33 has a through hole 37,
The middle part of the transmission piece 36 is left there. One wall surface of the through hole 37 serves as a driving unit 37a. Also, teeth are formed on the outer periphery of the driving body 33 to form a gear 38,
It meshes with the gear 26 of the reduction section F. Driven object 34, 35
Are formed with recesses 39 and 40 for transmitting piece, respectively, in which one end and the other end of the transmitting piece 36 are provided. One of the wall surfaces of the concave portions 39, 40 serves as driven portions 39a, 40a. The driven body 34 is formed integrally with the first drive gear 31. The driven body 35 is formed in the form of a gear 41 having teeth on the outer circumference. Next, reference numeral 42 shown in FIG. 6 denotes a receiving portion of the transmission piece 36, which is formed on an arc surface and
37a. Reference numerals 43 and 44 denote pressing portions, each of which is formed in an arcuate surface, and the driven portions 39a and 39a of the driven members 34 and 35, respectively.
It is facing 40a. The distance between the arc center of the receiving part 42 and the arc center of the pressing part 43, and the arc center of the receiving part 42 and the pressing part 44
The distances from the center of the circular arc are equal to each other, so that the same magnitude of driving force is always applied to both driven bodies 34 and 35 as described later. Next, drive gear 3
As shown in FIG. 4, reference numerals 1 and 32 are formed in a shape whose radius changes in the circumferential direction. As shown in FIG. 1, a connecting gear 46 is formed integrally with the drive gear 32, and the gear 46 is
Gear 41. The radii of the gears 41 and 46 are configured to be equal.

Next, a mechanism related to the clutch E will be described. FIG. 1H shows a locking mechanism connected to the first idler member 17 of the clutch E, and I shows an urging force applying mechanism connected to the second idler member 20. First, the locking mechanism H
Will be described with reference to FIGS. An operation lever 48 pivotally supports a base 48a. Reference numeral 49 denotes a driven portion, which is a portion of the output member B which is pushed by the operation portion 49a. Reference numeral 50 denotes a locking portion, which is opposed to the engaging portion 19 of the first idler member 17. Reference numeral 51 denotes a biasing member integrally formed with the lever 48, which has a sufficient elasticity by being formed thin as shown in the figure. 52 is a pin for urging member locking provided on a case (not shown). The operating lever 48 is configured such that the engaging portion 50 is separated from the engaging portion 19 when the urging member 51 contacts the pin 52 in a normal state.

Next, the urging force applying mechanism I will be described. In this embodiment, in this embodiment, the rotating power from the motor A is transmitted by a clutch by electromagnetic induction, and an urging force as described later is applied to the second idler member 20 by the transmitted rotating power. A centrifugal clutch may be used instead of the electromagnetic induction clutch. Reference numeral 54 denotes a main moving body of the mechanism, which is constituted by using a permanent magnet, and
Is provided integrally. Reference numeral 55 denotes a driven member, which is provided on the outer peripheral side of the main moving member 54 so as to be relatively rotatable, and an inner peripheral surface thereof is provided with an induction ring 57 (for example, a copper ring) for generating electromagnetic induction with the magnet. . The driven body 55 is provided with a gear 58 for connection.

Next, J is a braking mechanism connected to the speed reduction unit F. This mechanism is similar to a known mechanism using centrifugal force. Reference numeral 60 denotes a rotatable support base on which a connecting gear 61 is integrally formed. The gear 61 meshes with a gear 62 integrally formed with the connecting gear 24 in the speed reduction unit F. A rotating member 63 is mounted on the support base 60 so as to be integrally rotatable. Reference numeral 64 denotes an arm integrally formed with the rotating member 63, which has elasticity, and has an end face on the outer peripheral side serving as a rubbing portion 65.
66 is a weight attached to a portion near the outer peripheral end of the arm 64. 67
Is an outer box attached to a case (not shown) and located on the outer peripheral side of the rubbing portion 65.

The above-mentioned members are mounted on a case (not shown) by a known method so that the members can be turned or moved forward and backward.

Next, the operation of the geared motor having the above configuration will be described. In the non-operating state as shown in FIG. 1, the output member B is in the state of being returned to the return position by the return force of the load connected thereto. When the switch 2 is turned on in this state, the pinion 1 of the motor A rotates and the gear 8
~ 10 turns in the direction of the arrow. The driving member 12 and the coil spring 14 of the clutch E also rotate in the direction of the arrow. On the other hand, the rotation of the motor A is also transmitted to the main body 54 of the urging force applying mechanism I, and the main body rotates in the direction of the arrow. And follower
Due to electromagnetic induction between the driven member 55 and the driven member 55, a force is exerted on the driven member 55 to rotate the driven member 55 in the arrow direction. The force is applied to the second idler member 20 as an urging force that causes the second idler member 20 to rotate in the direction opposite to the rotational direction of the coil spring 14 as indicated by the arrow. When such a biasing force is applied to the second idler member 20, the coil spring 14 rotated as described above has its half 16 attached to the outer peripheral surface of the driven member 13 as shown in FIG. It is wound up like this. When the coil spring 14 and the driven member 13 are integrated by the tightening, the driven member 13 is thereafter moved to the state shown in FIG.
The gear 24 rotates in the same direction as the driving member 12 as shown by the arrow in FIG.
Also rotate in the same direction. In this case, the end of the coil spring 14
16a 'is fitted to the fitting portion 21 of the second idler member 20,
After the half portion 16 of the coil spring 14 has been wound around the driven member 13 as described above, the second idler member 20 rotates together with the coil spring 14 in the direction of the arrow in FIG. The driven body 55 in the mechanism I rotates in a direction opposite to the direction of the arrow in FIG. Even during this rotation, in the biasing force applying mechanism I, a force in a direction opposite to the rotation direction is applied to the driven body 55 by the main body.
The force is applied to the second idler member
The same biasing force as described above is continuously applied to the coil spring 20, and the tightened state of the half portion 16 of the coil spring 14 is always maintained.

When the gear 24 rotates as described above, the rotation is transmitted to the driving body 33 of the output member driving mechanism G via the speed reduction portion F, and the rotation is performed. The rotation is transmitted to the driven bodies 34 and 35 via the transmission piece 36, and they rotate. The rotation of the driven body 34 causes the first drive gear 31 to rotate in the direction of the arrow in FIG. 4, and the rotation of the driven body 35 causes the second drive gear 32 to move through the gears 41 and 46 to cause the arrow in FIG. Rotate in the direction. By the rotation of these drive gears 31, 32, the output member B moves toward the operating position in the direction of the arrow in FIG. As a result, the load connected thereto is directed in the same direction and is acted upon against its return force.

The driving of the output member B by the driving mechanism G will be described in more detail. The rotating force of the driver 33 is the transmission piece
As shown in FIGS. 6A to 6C, the driven bodies 34 and 35 are supplied to the driven bodies 34 and 35 through the base 36. That is, the rotating force of the driving body 33 is
It is transmitted from 37a to the receiving part 42 of the transmission piece 36, and further transmitted from the pressing parts 43, 44 of the transmission piece 36 to the driven parts 39a, 40a of the driven bodies 34, 35. In this case, the transmission piece 36 is
3 and 44 are seesaw-shaped, so the first drive gear 31
Between the gears and the teeth 5 of the output member B and in the driven body 35
Output member B from 41 through a connecting gear 46 and a driving gear 32
In any of the areas up to the teeth 5, no gap is formed in the teeth 5 so that the rotational power is always transmitted. 6A or 6C when a gap is generated in any one of them.
As a result, the gap is filled, and the output member B is always driven by both drive gears 31 and 32. Moreover, since the relationship between the arc centers of the receiving portion 42 and the pressing portions 43 and 44 is as described above, the force applied to the output member B from the first drive gear 31 and the output member B from the second drive gear 32 Is always equal to the force applied to Therefore, the output member B is always driven from both the left and right sides with the same driving force, and moves straight toward the operating position without generating a lateral force. When the output member B is moved toward the operation position as described above, the driving force applied to the output member B from the drive gears 31 and 32 increases as the output member B approaches the operation position.
The driving forces applied to the output member B gradually increase since the output members B 31 and 32 drive the output member B in a portion having a small radius.
Therefore, even if the drag increases as the operation of the load proceeds, the driving force of the output member B can overcome the drag and drive the load reliably.

When the output member B reaches the operating position by the above operation, the operating portion 49a of the output member B pushes the driven portion 49 of the locking mechanism H, so that the locking portion 50 is moved to the position shown in FIG.
As shown in (1), it engages with the engaging portion 19 of the first idler member 17, and stops the idler member 17 from rotating. When this happens,
Slip occurs between the driving member 12 and the half portion 15 of the coil spring 14 to prevent the output member B from moving excessively, and to transmit the force in the slip state, and to restore the output member B by the return force of the load. Is prevented from returning. In that case,
The frictional force between the driving member 12 and the half portion 15 of the coil spring 14 causes the driving force of the driving member 12 to move the coil spring 14 in the driving direction (rotation by the motor) indicated by the solid arrow in FIG. The direction in which the coil spring 14 is turned in the X direction and the return force of the load causes the coil spring 14 to move in the driving direction X.
The self-adjustment is performed so that the force to be turned in the return direction Y indicated by the broken line opposite to the above becomes substantially equal. As a result, the output member B is maintained in the operating position without being driven beyond the operating position or returned by the return force of the load. Therefore, the load is kept in operation.

The self-adjustment will be described. When the frictional force is large, the driving member 12 moves the coil spring 14 in the driving direction X.
When the force to turn the coil spring 14 is larger than the force to turn the coil spring 14 in the return direction Y by the driven member 13, the coil spring 14 turns in the driving direction X together with the main driving member 12. However, when the coil spring 14 rotates in that direction, the rotation of the first idler member 17 is prevented by the engagement of the engaging portion 50 with the engaging portion 19, and the coil spring 14 has one end 15a at its first end 15a. Of the coil spring 14 around the driving member 12 is loosened. Then, the frictional force decreases. On the other hand, the frictional force is small,
If the force by which the coil spring 14 is turned by the driven member 13 in the return direction Y is greater than the force by which the coil spring 14 turns the coil spring 14 in the drive direction X, the coil spring 14
It rotates in the return direction Y together with 13. However, as the coil spring 14 turns around in that direction, one end of the coil spring 14
15a is fixed to the first idler member 17 whose rotation is prevented, so that a half of the coil spring 14 with respect to the driving member 12 is provided.
15 tightening becomes stronger. Then, the frictional force increases. By such an operation, the frictional force is such that the driving force of the driving member 12 to rotate the coil spring 14 in the driving direction X by the frictional force and the coil spring 14 is rotated in the return direction Y by the return force of the load. Is adjusted to a state in which the force is substantially equal.

Next, when it is desired to return the load to the original state, the switch 2 is opened. Then, the pinion 1 of the motor A stops rotating. As a result, in the urging force applying mechanism I, the transmission of the force from the main moving body 54 to the driven body 55 is stopped. Therefore, no urging force for tightening the half portion 16 of the coil spring 14 is applied to the second idler member 20. In this case, the half portion 16 of the coil spring 14 is restored by its own elasticity,
The tightening of the outer peripheral surface of the driven member 13 is released. That is, the clutch E is disengaged. When this happens,
The load returns to its original state by its own restoring force.
In this case, the operation of restoring the load is transmitted to the braking mechanism J through the output member driving mechanism G and the speed reduction unit F in the reverse direction. In the braking mechanism J, the rotating member is driven by the force transmitted in the reverse direction.
The arm 63 spreads due to the centrifugal force caused by the rotation of the arm 63, and the rubbing portion 65 rubs against the inner peripheral surface of the outer box 67 to apply braking.
Therefore, the load is restored at a slow speed.

[0024]

As described above, according to the present invention, when the motor A is rotated, the coil spring 14 of the clutch E is tightly wound around the driven member 13 by the urging force applied by the urging force applying mechanism I. Thus, the rotation of the motor A is driven by the driving member 12,
There is a feature that the load is transmitted to the output member B via the coil spring 14 and the driven member 13, and the load is operated against the return force.

Further, when the output member B reaches the operating position as described above, the first idler member 17 is locked by the locking mechanism H, so that the coil spring 14 is loosened relative to the driving member 12. In addition, there is an effect that the transmission of the rotation is interrupted due to a slip between the two, and the damage due to excessive driving of the load can be prevented.

Further, in this state, the transmission of the force from the main driving member 12 to the coil spring 14 is continued even during the slip, so that the load can be maintained in the operating state against the returning force.

Further, when the rotation of the motor A is stopped, the winding of the coil spring 14 on the driven member 13 is released, the driven member 13 becomes free, the output member B can return freely, and the load is released. There is an effect that the original state can be restored by the force.

Further, even if the load can be variously controlled as described above, the clutch E which is the main part of the control is used.
The structure of the main part is very simple because the main driving member 12 and the driven member 13 are arranged side by side on the same axis, and the coil spring 14 is provided straddling them. There is an economic effect that can be provided at low cost.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view of a geared motor.

2A is a longitudinal sectional view of a clutch in a state where a coil spring is not wound around a driven member, and FIG. 2B is a longitudinal sectional view of a clutch in a state where the coil spring is wound around.

FIGS. 3A and 3B are partial views for explaining the operation of the geared motor of FIG. 1;

FIG. 4 is a horizontal sectional view showing a relationship among an output member, a driving gear, and a locking mechanism.

FIG. 5 is a vertical sectional view of a distribution mechanism.

6 (A), (B), and (C) are drawings for explaining the operation of the distribution mechanism, and are sectional views taken along line VI-VI in FIG. 5;

[Explanation of symbols]

 A Motor B Output member E Clutch 12 Main driving member 13 Follower member 14 Coil spring

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) H02K 7/116

Claims (1)

(57) [Claims] 1. A geared motor comprising a motor, an output member for driving a load having a restoring force, and a transmission mechanism interposed therebetween, wherein the transmission mechanism has a clutch in the middle. The above-mentioned clutch includes a round bar-shaped main driving member and a driven member which are rotatably arranged side by side on the same axis, and a coil spring which is straddled over both of them and is rotatably provided around both of them. And the driven member is connected to the motor side of the transmission mechanism, while the driven member is connected to the output member side, and the coil spring has its winding direction on the driven member side with respect to the end on the driven member side. When the end is turned in the same direction as the rotation direction of the driving member by the motor, the coil spring is directed to reduce the diameter, and the inner peripheral surface of the portion located on the outer peripheral side of the driving member is On the outer surface The end of the coil spring on the main drive member side is fixed to a first idler member rotatably provided relative to the main drive member, and the idler member has When the output member reaches the operating position, a locking mechanism for locking the idle rotation is linked,
On the other hand, the end of the coil spring on the driven member side is fixed to a second idler member rotatably provided relative to the driven member, and the idler member is provided with the idler member when the motor rotates. A geared motor in which an urging force applying mechanism for applying an urging force for winding a portion of the coil spring located on the outer peripheral side of the driven member around the driven member is connected to the idler member.