JP2000184656A - Motor with deceleration mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a motor with deceleration mechanism with improved durability and reliability by preventing the worm of an armature shaft from biting a counter gear or getting over it. SOLUTION: A deflection-reception rotary member 21 which, allocated near the other end part of an armature shaft 7, so provided as to collide is the armature shaft 7 when a second worm 11 deflects in such direction as a way from a second counter gear 13 while possible to rotate itself under the rotational force of the armature shaft 7 is provided to a motor 1 with deceleration mechanism.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a motor with a speed reduction mechanism for driving a load by decelerating the rotation of an armature shaft provided on an armature that rotates when energized.

[0002]

2. Description of the Related Art As a motor with a reduction mechanism for driving a load by decelerating the rotation of an armature shaft provided on an armature that rotates when energized, one end and a central portion of the armature shaft are rotatably supported by bearings. , Near the other end of this armature shaft
Is formed, and a second worm is formed at the other end of the armature shaft. The first worm meshes with the large-diameter tooth portion of the first counter gear, the second worm meshes with the large-diameter tooth portion of the second counter gear, and the small-diameter tooth portion of the first counter gear. The small-diameter tooth portions of the second counter gear are meshed with the wheel gears, respectively, and the wheel gears are fixed via a damper to an output shaft coupled to a load.

[0003]

However, in the motor with a speed reduction mechanism described above, when the output shaft is locked by the load being moved to the stroke end, the damper is elastically deformed by continuing the rotation of the armature shaft. While the wheel gear rotates slightly, the first
In the direction in which the worm approaches the first counter gear,
The armature shaft is bent in a direction in which the worm moves away from the second counter gear, and the armature shaft bends. As a result, the first worm may bite into the large-diameter tooth portion of the first counter gear, and the large-diameter tooth portion may be chipped or deformed. There is a problem that the thread of the large-diameter tooth portion may run over the thread, so that the durability and the reliability may be inferior. Therefore, it has been a problem to solve the above problems.

[0004]

An object of the present invention is to provide a motor with a speed reduction mechanism.
By preventing the armature shaft worm from biting into the counter gear or riding on it,
It is an object of the present invention to provide a motor with a speed reduction mechanism that can improve durability and reliability.

[0005]

Configuration of the Invention

[0006]

According to a first aspect of the present invention, there is provided a motor with a speed reduction mechanism, a motor case, a gear case screwed to the motor case, a magnet disposed inside the motor case, and a magnet. It has an armature shaft which is arranged on the inner peripheral side, one end and a central part are rotatably supported, and the other end protrudes into the gear case, and is formed near the other end of the armature which is rotated by energization and which is rotated by energization. And a second worm formed at the other end of the armature shaft.
Worm, a first counter gear having a first small-diameter gear and a first large-diameter gear, the first large-diameter gear being meshed with the first worm, a second small-diameter gear and a second large-diameter gear. A second large-diameter gear, a second large-diameter gear meshed with a second worm, and a first small-diameter gear of the first counter gear, and a second large-diameter gear. A wheel gear meshed with the second small-diameter gear of the counter gear and coupled via a damper to an output shaft coupled to a load;
A second armature shaft is disposed near the other end of the armature shaft.
When the worm turns in a direction away from the second counter gear, the worm can collide with the armature shaft, and has a bending receiving rotation member that can rotate by itself by receiving the rotation force of the armature shaft. It is characterized by.

According to a second aspect of the present invention, there is provided a motor with a speed reduction mechanism, a motor case having one end closed and the other end open, a magnet disposed inside the motor case, and one end in the motor case. A first bearing attached to the motor case, a gear case screwed to the other end of the motor case, a second bearing attached to the gear case at the other end of the motor case, and an inner peripheral side of the magnet. Placed in
One end is rotatably supported by the first bearing and the center is rotatably supported by the second bearing,
An armature having the other end protruding into the gear case and having an armature shaft rotated by energization, a first worm formed near the other end of the armature shaft, and an armature shaft independently of the first worm And a first counter gear having a first small-diameter gear and a first large-diameter gear, the first large-diameter gear being meshed with the first worm. A second counter gear having a second small-diameter gear and a second large-diameter gear, the second large-diameter gear meshed with a second worm, and a first small-diameter gear of the first counter gear. A wheel gear meshed with the second small-diameter gear of the second counter gear, a damper housed and coupled to the wheel gear, a hub coupled to the damper, and an output shaft fixed to the hub When, A wheel gear supporting portion which is arranged in the housing in a position facing the second counter gear via the second worm of the armature shaft and rotatably supports the hub; and a second worm of the armature shaft is provided with a second worm. When the counter gear is turned away from the second large-diameter gear, the counter gear can collide with the second worm so as to be rotatably mounted outside the wheel gear support. It is characterized in that it has a configuration provided with a rotatable bending receiving rotation member.

In the motor with a speed reduction mechanism according to a third aspect of the present invention, a third bearing for rotatably supporting the hub is mounted inside the wheel gear supporting portion, and the inner peripheral portion is provided on the bending receiving rotary member. A gear case side sliding contact portion which is rotatably mounted on the wheel gear support portion coaxially with the third bearing is formed in the portion, and an armature shaft collision portion which collides with the second worm of the armature shaft is formed on the outer peripheral portion. It is characterized in that it is formed.

In the motor with a speed reduction mechanism according to a fourth aspect of the present invention, the first counter gear has a first small-diameter tooth portion formed above the first small-diameter gear, and the first small-diameter gear. In the lower stage, a second small-diameter tooth portion having a phase difference of 1/2 pitch is integrally formed with the first small-diameter tooth portion. And a fourth small-diameter tooth portion having a phase difference of 1/2 pitch is formed integrally with the third small-diameter tooth portion below the second small-diameter gear. Are located at the top of the first small-diameter tooth portion of the first counter gear and the third small tooth portion of the second counter gear.
First tooth portions respectively meshed with the small-diameter tooth portions of the first counter gear, and meshed with the second small-diameter tooth portion of the first counter gear and the fourth small-diameter tooth portion of the second counter gear at the lower stage, respectively. The second tooth portion is formed integrally with the first tooth portion with a phase difference of 1/2 pitch.

[0010]

In the motor with the speed reduction mechanism according to the first, second, third and fourth aspects of the present invention, the armature shaft is rotated after the output shaft is locked, so that the first worm is moved to the second worm. The second worm is subjected to bending stress on the armature shaft in a direction approaching the first counter gear and moving away from the second counter gear in the second direction.
When the worm flexes in the direction away from the second large-diameter gear of the second counter gear, the flexure receiving rotary member disposed near the other end of the armature shaft collides with the armature shaft, and Receives the torque of the armature shaft and rotates by itself, thereby suppressing the bending of the armature shaft. Therefore, the armature shaft does not allow the first worm to approach the first counter gear extremely, and the second worm does not largely separate from the second counter gear. There is no danger that the first counter gear will bite or deform due to biting into the first counter gear, and there is no danger that the second worm will run over the thread of the second large-diameter gear of the second counter gear.

[0011]

1 to 5 show an embodiment of a motor with a speed reduction mechanism according to the present invention, which is used for an electric reclining device.

The illustrated motor 1 with a speed reduction mechanism mainly includes a motor case 2, a gear case 3, a first magnet 4, a second magnet 5, an armature 6, an armature shaft 7, a first brush 8, a second brush Brush 9, first
Worm 10, second worm 11, first counter gear 12, second counter gear 13, wheel gear 1
4, damper 15, hub 16, output shaft 17, first bearing 1
8, a second bearing 19, a third bearing 20, and a bending receiving rotation member 21. The first worm 10, the second worm 11, the first counter gear 12, the second counter gear 13 The wheel gear 14 constitutes a speed reduction mechanism 40.

In the motor case 2, an end cap 2b is formed at one end of a cylindrical motor case main body 2a, and a first bearing 18 is mounted inside the end cap 2b. The first bearing 18 rotatably supports one end of the armature shaft 7. A flange 2c is formed at the other end of the motor case main body 2a.
2 screwed.

The first, inside of the motor case body 2a
The second magnets 4 and 5 are respectively fixed, and the armature 6 is provided on the inner peripheral side of the first and second magnets 4 and 5.
Is arranged. An armature core 23 having a coil winding portion 23a having a predetermined number of slots is fixed to the armature 6 near one end of the armature shaft 7, and a commutator 24 is fixed on the armature shaft 7 near the armature core 23. I have. The commutator 24 is provided with the same number of commutator pieces 24a as the coil winding portions 23a of the armature core 23. The armature 6 is wound around each of the coil winding portions 23a of the armature core 23, and the commutator pieces 24a are wound. Armature coil 25 electrically connected to each of them.

The armature shaft 7 has the other end protruding into a shaft hole 3 a formed in the gear case 3. A first part of the speed reduction mechanism 40 is formed near the other end of the armature shaft 7. A second worm 11 is formed at the other end of the armature shaft 7 and is independent of the first worm 10 and constitutes another part of the speed reduction mechanism 40. The first worm 10 is right-handed and the second worm 11 is left-handed.

A holder base 26 is attached to one end of the gear case 3.
As shown in FIG. 1, first and second brush holders 27 and 28 to which first and second brushes 8 and 9 are electrically connected are mounted, respectively.

The first and second brush holders 27, 28
Since each of them is electrically connected to a seat control circuit (not shown), when the front reclining switch provided in the seat control circuit is turned on, power is supplied from the first brush 8 to the second brush 9. The armature shaft 7 rotates forward. On the other hand, when the rear reclining switch provided in the seat control circuit is turned on, power is supplied from the second brush 9 to the first brush 8, and the armature shaft 7 rotates in the reverse direction. When the rotation of the armature shaft 7 is locked, the seat control circuit includes a lock detection circuit that cuts off the power supply to the first and second brushes 8 and 9.

The gear case 3 has a shaft hole 3 at the center.
a is formed, and a speed reduction mechanism housing portion 3b is formed so as to communicate with the shaft hole 3a. A second bearing 19 is attached to one end of the shaft hole 3a. The second bearing 19 rotatably supports a central portion of the armature shaft 7. The armature shaft 7 has one end rotatably supported by the first bearing 18 and the center portion rotatably supported by the second bearing 19, but the other end is not supported by a bearing or the like. , First and second worm 1
0 and 11 are cantilevered by a second bearing 19.

As shown in FIG. 3, a wheel gear support 3c is formed in the reduction mechanism housing 3b. The wheel gear support portion 3c is formed in an annular shape so as to protrude from the bottom surface portion 3d substantially at the center of the speed reduction mechanism housing portion 3b. As shown in FIG. 2, the wheel gear support 3c has an outer diameter d1 and a height h1. A third bearing 20 is mounted inside the wheel gear support 3c. The third bearing 20 rotatably supports the other end of the hub 16. The reduction gear housing 3b is covered with a cover 3e. A fourth bearing 31 is provided on the cover 3e.
The fourth bearing 31 rotatably supports one end of the hub 16.

A bending receiving rotation member 21 is arranged outside the wheel gear support 3c. As shown in FIG. 2, the deflection receiving rotation member 21 has a height h2 substantially equal to the height h1 of the wheel gear supporting portion 3c and a thickness t1. Rotating member body 2
A gear case side sliding contact portion 21b is formed on the inner peripheral portion of 1a. The gear case side sliding contact portion 21b has an inner diameter d slightly larger than the outer diameter d1 of the wheel gear support 3c.
2 The armature shaft collision part 21c is formed in the bending receiving rotation member 21 on the outer peripheral part of the bending receiving rotation member main body 21a. The armature shaft collision portion 21c has an outer diameter d3.

Since the inner diameter dimension d2 of the gear case side sliding contact portion 21b is slightly larger than the outer diameter dimension d1 of the wheel gear support section 3c, the bending receiving rotation member 21 is rotatably supported by the wheel gear support section 3c. I have.

As shown in FIG. 5, the bending receiving rotating member 21 has a thickness smaller than a distance L1 from the second worm 10 of the armature shaft 7 to the wheel gear supporting portion 3c by a predetermined clearance dimension L2. Size t
1, the armature shaft 7 is normally subjected to no bending stress and the armature shaft collision portion 2
1c is spaced apart without impacting on the second worm 10 of the armature shaft. However, the first worm 10 of the armature shaft 7 is
, The second worm 11 of the armature shaft 7 is subjected to bending stress on the armature shaft 7 in a direction away from the second counter gear 13, and the first and second worms 10, 11 of the armature shaft 7 When bending from the second bearing 19, the second worm 11 of the armature shaft 7 deflects and collides with the armature shaft collision portion 21c of the rotation receiving member 21, and the armature shaft collision portion 21c is pressed by the second worm 11. Meanwhile, the second worm 11 is rotated by the movement of the helical winding of the screw. At this time, the bending receiving rotation member 21 rotates clockwise in FIG. 3 when the armature shaft 7 rotates forward, and rotates counterclockwise in FIG. 3 when the armature shaft 7 rotates reversely. Is done.

When the armature shaft colliding portion 21c collides with the armature shaft 7 to which the bending stress has been applied, the bending force of the armature shaft 7 causes the bending receiving rotary member 21 to rotate in the forward and reverse directions. The bending of the armature shaft 7 is suppressed, so that the first worm 10 does not extremely approach the first large-diameter gear 12 b of the first counter gear 12, and the first worm 10 is moved to the first counter gear 12. Not to bite into the first large-diameter gear 12b,
Of the second large-diameter gear 1b of the second counter gear 13 so that the worm 11 of the second counter gear 13 does not largely separate from the second large-diameter gear 13b of the second counter gear 13.
Do not run over the thread 3b.

The bending receiving rotation member 21 is provided with the second worm 1.
When rotating by the rotational force given from 1, since the gear case side sliding contact portion 21 b is rotatably supported by the wheel gear support portion 3 c, the pressing force received from the second worm 11 is dispersed and concentrated at one point. Therefore, uneven wear is prevented, and the clearance dimension L2 is secured. In this case, the bending receiving rotation member 21 is rotatably attached to the wheel gear support portion 3c of the gear case 3, but is not limited thereto. , A shaft-like support may be provided near the support, and the shaft may be rotatably attached to the support. Of course, also in this case, the bending of the receiving rotation member 2 is performed at a position where the clearance L2 is set from the second worm 11.
One armature shaft collision portion 21c is arranged.

A first pivot shaft 29 and a second pivot shaft 30 are mounted in the speed reduction mechanism housing 3b.
The first pivot shaft 29 is disposed on the first worm 10 side of the armature shaft 7, and the first pivot shaft 2
9, a first counter gear 12 is rotatably inserted. The second pivot 30 is arranged on the second worm 11 side of the armature shaft 7, and the second counter gear 13 is rotatably inserted through the second pivot 30.

As shown in FIG. 3, the first counter gear 12 constituting another part of the reduction mechanism 40 is provided with a first small-diameter gear 12a and a first large-diameter gear 12b. I have.

In the first small-diameter gear 12a, a first small-diameter tooth portion 12a1 is formed in an upper stage, and a second small-diameter tooth portion 1a is formed in a lower stage.
2a2 is formed.

The first small-diameter tooth portion 12a1 is a flat tooth having ten teeth. The second small-diameter tooth portion 12a2 is formed with a phase difference of 1/2 pitch in the first small-diameter tooth portion 12a1, and the number of ten flat teeth is selected.

The first large-diameter gear 12b has a first large-diameter tooth portion 12b1 formed thereon.
Are arranged below the second small-diameter tooth portion 12a2 concentrically with the first small-diameter gear 12a, and the number of helical teeth is 30.

The first counter gear 12 has a first small-diameter gear 12a and a first large-diameter gear 12b formed by integral molding, and a central hole 12c formed in the center portion has a first pivot shaft. The first large-diameter gear 12 b is meshed with the first worm 10 of the armature shaft 7 by being rotatably supported by being inserted through the first gear 29. The first counter gear 12 is reversely rotated by the forward rotation of the armature shaft 7, and is normally rotated by the reverse rotation of the armature shaft 7.

As shown in FIG. 3, the second counter gear 13, which forms another part of the reduction mechanism 40, includes a second small-diameter gear 13a and a second large-diameter gear 13b. I have.

In the first small-diameter gear 13a, a third small-diameter tooth portion 13a1 is formed in an upper stage, and a fourth small-diameter tooth portion 1a is formed in a lower stage.
3a2 is formed.

The third small-diameter tooth portion 13a1 is a flat tooth having ten teeth. The fourth small-diameter tooth portion 13a2 is formed with a phase difference of ピ ッ チ pitch in the third small-diameter tooth portion 13a1, and the number of ten flat teeth is selected.

The second large-diameter gear 13b has a second large-diameter tooth portion 13b1 formed thereon.
Is arranged below the fourth small-diameter tooth portion 13a2 concentrically with the second small-diameter gear 13a, and the number of helical teeth is 30.

The second counter gear 13 has a second small-diameter gear 13a and a second large-diameter gear 13b formed by integral molding, and a central hole 13c formed in the center portion has a second pivot shaft. The second large-diameter gear 13 b is meshed with the second worm 11 of the armature shaft 7 by being rotatably supported by being inserted into the armature shaft 7. The second counter gear 13 is reversely rotated by the forward rotation of the armature shaft 7, and is normally rotated by the reverse rotation of the armature shaft 7.

As shown in FIG. 3, a first tooth portion 14a and a second tooth portion 14b are integrally formed on the wheel gear 14 constituting the remaining part of the speed reduction mechanism 40. .

The first tooth portion 14a is arranged on the upper stage of the wheel gear 14, and the number of spur teeth is 72. The second tooth portion 14b is disposed concentrically with the first tooth portion 14a and arranged below the wheel gear 14, and has 72 flat teeth having a phase difference of 1/2 pitch in the first tooth portion 14a. Number of teeth is selected.

As shown in FIG. 4, a damper accommodating portion 14c is formed at the center of the wheel gear 14.
A damper 15 formed of an elastic member is fitted into the damper accommodating portion 14c. The outer periphery of the damper 15 is connected to the wheel gear 14. The wheel gear 14 rotates forward with the output shaft 17 when the first and second counter gears 12 and 13 rotate in the reverse direction, and rotates the output shaft 17 when the first and second counter gears 12 and 13 rotate forward. Is rotated in reverse.

A hub 16 is connected to the center of the damper 15. As shown in FIG. 2, the hub 16 has a damper coupling portion 16b formed on the outer periphery of one end of a hub body 16a having a cylindrical shape.
The inner periphery of the damper 15 is connected to b. Hub body 1
An output shaft coupling portion 16c is formed on an inner peripheral portion at one end of the output shaft 6a, and a hub coupling portion 17a formed at a distal end portion of the output shaft 17 is coupled to the output shaft coupling portion 16c.
The outer periphery of the other end of the hub body 16a has a bearing insertion portion 16
The bearing insertion portion 16 d is inserted into the third bearing 20.

The output shaft 17 has a hub coupling portion 17 at its tip.
a is disposed, and the base end of the output shaft 17 is connected to a seat driving mechanism provided in an electric reclining device (not shown). The electric reclining device has an output shaft 17.
Causes the seat to recline forward by the forward rotation, and conversely, causes the seat to recline backward by the reverse rotation of the output shaft 17.

The motor 1 with the speed reduction mechanism having such a structure is as follows.
The gear case 3 is screwed to a seat frame, the output shaft 17 is connected to a seat driving mechanism, and the first and second brushes 8 and 9 are electrically connected to a seat control circuit and mounted on a vehicle body.

When the front reclining switch of the seat control circuit is turned on, power is supplied from the first brush 8 to the second brush 9 and the armature shaft 7 is turned on.
Rotates forward, the first and second counter gears 12, 1
3 rotate in the reverse direction, and the first and second counter gears 1
Due to the reverse rotation of 2 and 13, the wheel gear 14
, And the seat back provided on the seat is tilted forward.

When the seat back is moved to the front end,
The movement of the seat back is stopped, whereby the output shaft 17 is restrained from rotating forward. However, since the power supply to the armature 6 is not cut off, the armature shaft 7 continues to rotate forward, the wheel gear 14 rotates forward and the damper 15 is elastically deformed, and the armature shaft 7 is first and secondly rotated. Forward rotation is restricted by the worms 10 and 11.

When the forward rotation of the armature shaft 7 is restrained by the first and second worms 10 and 11, the armature shaft 7 attempts to continue the forward rotation by energizing the armature 6 so that the armature shaft 7
The first counter gear 1 with respect to the first worm 10
A force in a direction away from 2 acts on the second worm 11 and a force in a direction away from the second counter gear 13 acts on the second worm 11. However, the force at that time is the second bearing 19
Thus, the distance is determined by the meshing position of the first counter gear 12 and the first worm 10 and the distance to the meshing position of the second counter gear 13 and the second worm 11. Therefore, the force acting on the armature shaft 7 is greater at the portion where the first worm 10 and the first counter gear 12 mesh with each other, so that the armature shaft 7 bends. Then, the second armature shaft 7
Worm 11 collides with the armature shaft collision portion 21c of the bending receiving rotation member 21, and the armature shaft collision portion 21c is pressed by the second worm 11, and the bending reception rotation member 21 The winding rotates clockwise in FIG. 3 due to the displacement of the winding. After that, the lock of the armature shaft 7 is detected by the lock detection circuit, and the energization from the first brush 8 to the second brush 9 is cut off by the seat control circuit, so that the forward rotation of the armature shaft 7 is stopped. I do.

The second worm 11 of the armature shaft 7 to which the bending stress has been applied is bent and collides with the armature shaft collision portion 21c of the rotation receiving member 21, whereby the armature shaft collides with the second worm 11.
Since the bending of the armature shaft 7 is suppressed, the first
Worm 10 does not approach the first large-diameter gear 12b of the first counter gear 12 more than necessary, so that the first worm 10 becomes the first large-diameter tooth portion 12 of the first counter gear 12.
b1 and the second worm 11 does not move far away from the second large-diameter gear 13b of the second counter gear 13, so that the second worm 11 does not go into the second large diameter of the second counter gear 13. Since the thread of the radial tooth portion 13b1 does not run over, the idling of the armature shaft 7 is prevented, and the second worm 11 and the second counter gear 1 are prevented from rotating.
As a result, the durability of the second worm 11 and the second counter gear 12 is improved. The bending receiving rotation member 21 rotates by receiving the rotation force of the armature shaft 7, so that the collision position with the second worm 11 is constantly changed, so that the durability is improved.

When the rear reclining switch of the seat control circuit is turned on, power is supplied from the second brush 9 to the first brush 8 and the armature shaft 7 is turned on.
Are rotated in reverse, so that the first and second counter gears 12, 1
3 rotate in the reverse direction, and the first and second counter gears 1
Due to the reverse rotation of 2 and 13, the wheel gear 14
, And the seat back of the seat is tilted backward.

When the seat back is moved to the rear end,
The movement of the seat back is stopped, whereby the output shaft 17 is restrained from rotating in the reverse direction. However, since the power supply to the armature 6 is not cut off, the armature shaft 7 continues to rotate in the reverse direction, the wheel gear 14 rotates in the reverse direction, the damper 15 is elastically deformed, and the armature shaft 7 eventually becomes the first and the second. The reverse rotation is restricted by the worms 10 and 11.

When the armature shaft 7 is restrained from rotating in the reverse direction by the first and second worms 10 and 11, the armature shaft 7 attempts to continue rotating in the reverse direction by energizing the armature 6, thereby causing the armature shaft 7 to rotate.
The first counter gear 1 with respect to the first worm 10
A force in a direction away from 2 acts on the second worm 11 and a force in a direction away from the second counter gear 13 acts on the second worm 11. However, the force at that time is the second bearing 19
Thus, the distance is determined by the meshing position of the first counter gear 12 and the first worm 10 and the distance to the meshing position of the second counter gear 13 and the second worm 11. Therefore, the force acting on the armature shaft 7 is larger at the portion where the second worm 11 and the second counter gear 13 mesh with each other, so that the armature shaft 7 bends. Then, the second armature shaft 7
Worm 11 collides with the armature shaft collision portion 21c of the bending receiving rotation member 21, and the armature shaft collision portion 21c is pressed by the second worm 11, and the bending reception rotation member 21 The winding rotates counterclockwise in FIG. 3 due to the displacement of the winding. afterwards,
The lock of the armature shaft 7 is detected by the lock detection circuit, and the energization from the second brush 9 to the first brush 8 is cut off by the seat control circuit, so that the armature shaft 7 stops reverse rotation.

When the bending force is applied to the second worm 11 of the armature shaft 7, the armature shaft colliding portion 21 c of the rotation receiving member 21 collides with the second worm 11.
Since the bending of the armature shaft 7 is suppressed, the first
Worm 10 does not approach the first large-diameter gear 12b of the first counter gear 12 more than necessary, so that the first worm 10 becomes the first large-diameter tooth portion 12 of the first counter gear 12.
b1 and the second worm 11 does not move far away from the second large-diameter gear 13b of the second counter gear 13, so that the second worm 11 does not go into the second large diameter of the second counter gear 13. Since the thread of the radial tooth portion 13b1 does not run over, the idling of the armature shaft 7 is prevented, and the second worm 11 and the second counter gear 1 are prevented from rotating.
As a result, the durability of the second worm 11 and the second counter gear 12 is improved. The bending receiving rotation member 21 rotates by receiving the rotation force of the armature shaft 7, and thus the collision position with the second worm 11 is constantly changed, so that the durability is improved.

As described above, when the output shaft 17 is in the locked state, the armature shaft collision portion 21c of the bending receiving rotating member 21 collides with the second worm 11, and the bending receiving rotating member 21 rotates the armature shaft 7. Armature shaft 7 by rotating itself under the force
Is prevented, the first worm 10 of the armature shaft 7 does not approach the first counter gear 12 more than necessary, and the second worm 11 of the armature shaft 7 is moved to the second counter gear 13.
As a result, the first worm 10 does not bite into the first large-diameter tooth portion 12b1 of the first counter gear 12 to cause chipping or deformation, and The second worm 11 does not run on the thread of the second large-diameter tooth portion 13b1 of the second counter gear 13.

[0051]

As described above, according to the motor with the speed reduction mechanism according to the first, second, third and fourth aspects of the present invention, the armature shaft is rotated after the output shaft is locked. As a result, a bending stress is applied to the armature shaft in a direction in which the first worm approaches the first counter gear and a direction in which the second worm moves away from the second counter gear. When bending in the direction away from the second large-diameter gear, the bending receiving rotating member disposed on the other end side of the armature shaft collides with the armature shaft, and the bending receiving rotating member receives the rotational force of the armature shaft. The rotation of the armature shaft suppresses the bending of the armature shaft. Therefore, the armature shaft does not allow the first worm to approach the first counter gear extremely, and the second worm does not largely separate from the second counter gear. There is no danger that the first counter gear will bite into the first counter gear, and that the second worm will not run on the thread of the large-diameter gear of the second counter gear. Further, the bending receiving rotation member rotates by receiving the rotation force of the armature shaft, so that the collision position with the second worm is constantly changed, so that the durability is improved. In addition, the durability of the second worm and the second counter gear is also improved in order to prevent the armature shaft from idling and to ensure the engagement between the second worm and the second counter gear. Therefore, there is an excellent effect that the durability and reliability of the entire motor can be improved.

[Brief description of the drawings]

FIG. 1 is a cross-sectional plan view illustrating an internal structure of an embodiment of a motor with a speed reduction mechanism according to the present invention.

FIG. 2 is a vertical sectional side view around a speed reduction mechanism in the motor with a speed reduction mechanism shown in FIG. 1;

FIG. 3 is an external perspective view illustrating an assembling relationship between a speed reduction mechanism and a bending receiving rotation member in the motor with a speed reduction mechanism shown in FIG. 1;

FIG. 4 is a plan view for explaining an assembling relationship between a wheel gear and a damper in the motor with a speed reduction mechanism shown in FIG. 1;

FIG. 5 is a plan view illustrating an assembling relationship between a bending receiving rotation member and an armature shaft in the motor with a speed reduction mechanism shown in FIG. 1;

[Explanation of symbols]

 Reference Signs List 1 motor with reduction mechanism 2 motor case 3 gear case 3c wheel gear support 4 (magnet) first magnet 5 (magnet) second magnet 6 armature 7 armature shaft 10 first worm 11 second worm 12 first Counter gear 12a First small diameter gear 12a1 First small diameter toothed portion 12a2 Second small diameter toothed portion 12b First large diameter gear 13 Second counter gear 13a Second small diameter gear 13a1 Third small diameter toothed portion 13a2 4 small-diameter tooth portion 13b second large-diameter gear 14 wheel gear 14a first tooth portion 14b second tooth portion 15 damper 16 hub 17 output shaft 18 first bearing 19 second bearing 20 third bearing 21 Deflection receiving rotation member 21b Gear case side sliding contact part 21c Armature shaft collision part

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3B099 CB01 CB06 5H607 AA01 BB01 BB04 BB14 CC01 CC03 CC05 DD02 DD03 DD08 EE14 EE32 FF24

Claims (4)

[Claims] 1. A motor case, a gear case screwed to the motor case, a magnet arranged inside the motor case, and an inner peripheral side of the magnet, one end and a center of which are rotatable. An armature that has an armature shaft supported at the other end and protrudingly arranged in the gear case and that rotates when energized; a first worm formed near the other end of the armature shaft; and the other end of the armature shaft. A second worm formed in the portion; a first counter gear having a first small-diameter gear and a first large-diameter gear, wherein the first large-diameter gear is meshed with the first worm; A second counter gear having a second small diameter gear and a second large diameter gear, the second large diameter gear meshed with the second worm; A wheel gear meshed with a first small-diameter gear of the gear, meshed with a second small-diameter gear of the second counter gear, and coupled via a damper to an output shaft coupled to a load; It is located near the other end of the armature shaft,
When the second worm bends in a direction away from the second counter gear, the second worm is provided with a bending receiving rotating member which can collide with the armature shaft and can rotate by itself under the rotational force of the armature shaft. A motor with a speed reduction mechanism, characterized in that: 2. A motor case having one end closed and the other end open; a magnet disposed inside the motor case; and a first bearing mounted on one end in the motor case. A gear case screwed to the other end of the motor case; a second bearing mounted in the gear case at the other end of the motor case; and a first end disposed on the inner peripheral side of the magnet. Is the first
An armature rotatably supported by the bearing and having a central portion rotatably supported by the second bearing, the other end protrudingly arranged in the gear case, and having an armature shaft that rotates when energized; A first worm formed near the other end of the armature shaft, a second worm formed on the other end of the armature shaft independently of the first worm, a first small-diameter gear, A first large-diameter gear having a first counter gear meshed with the first worm; a second small-diameter gear and a second large-diameter gear; A second large-diameter gear meshed with the second worm; a second small-diameter gear of the first counter gear meshed with the second counter gear; 2, a wheel gear meshed with the small diameter gear, a damper housed and connected to the wheel gear, a hub connected to the damper, an output shaft fixed to the hub, and an armature shaft in the gear case. A wheel gear supporting portion that is arranged at a position facing the second counter gear via a second worm and rotatably supports the hub; and a second worm of the armature shaft is a second gear of the second counter gear. When turning away from the second large-diameter gear, the second large-diameter gear is allowed to collide with the second worm so as to be rotatably mounted outside the wheel gear support portion. A motor with a speed reduction mechanism, comprising a rotatable deflection receiving rotation member. 3. A third bearing for rotatably supporting the hub is mounted inside the wheel gear support portion. The flexure receiving rotation member is coaxial with the third bearing on the inner peripheral portion. A gear case side sliding contact portion rotatably attached to the wheel gear support portion, and an armature shaft collision portion that collides with a second worm of the armature shaft is formed on an outer peripheral portion. 2
A motor with a speed reduction mechanism according to item 1. 4. The first counter gear has a first small-diameter tooth portion formed above the first small-diameter gear, and a first small-diameter tooth portion formed below the first small-diameter gear. A second small-diameter tooth portion having a phase difference of / 2 pitch is integrally formed, and the second counter gear has a third small-diameter gear above the second small-diameter gear.
And a fourth small-diameter tooth portion having a phase difference of に pitch is formed integrally with the third small-diameter tooth portion below the second small-diameter gear. In the upper part, first tooth parts respectively meshed with the first small diameter tooth part of the first counter gear and the third small diameter tooth part of the second counter gear are formed, and in the lower part, Second tooth portions meshed with the second small-diameter tooth portion of the first counter gear and the fourth small-diameter tooth portion of the second counter gear respectively have a half pitch with the first tooth portion. 4. The motor with a speed reduction mechanism according to claim 1, wherein the motor is formed integrally with a phase difference.