JPH0886134A - Actuator - Google Patents

Abstract

PURPOSE: To quietly operate an actuator for automatically locking and unlocking a door of an automobile with the use of a reversible motor, by providing a brake spring for damping a torque, to a first intermediate gear in the actuator. CONSTITUTION: A brake spring 8 for damping a torque of a first intermediate gear 7 meshed with a pinion 4 fitted on a reversible motor shaft 3a is provided to the first intermediate gear 7. Further, the brake spring may be also mounted on a second intermediate gear 6 so as to make contact with a power transmission gear 9 in order to damper the torque of the first intermediate gear 7. When the motor 3 is operated by manipulating a switch so as to operate the actuator 1, the motor is stopped after the torque of the first intermediate gear 7 is damped so that no shock occurs. With this arrangement, the operation can be quietly made.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an actuator used for automatically locking and unlocking an automobile door, for example.

[0002]

2. Description of the Related Art FIG. 6 illustrates an actuator used for automatically locking and unlocking a door of a vehicle.

The illustrated door lock actuator 50
When the positive side power is supplied from the external terminals 51a and 51b provided in the motor 51, the motor shaft 5 of the motor 51
Since the motor pinion 52 attached to 1c rotates in the clockwise direction in FIG. 6, which is the positive direction side, power is transmitted to the first intermediate gear 53 meshing with the motor pinion 52, and the first intermediate gear 53 moves. It rotates counterclockwise in FIG. 6 while being rotatably supported by the pivot 55 on the case 54.

Since the first intermediate gear 53 rotates counterclockwise in FIG. 6, a first spring contact provided so as to project rearward in FIG. 6 of the first intermediate gear 53. Since the portion 53a abuts on the one end side engagement portion 56a of the power transmission spring 56 and presses the power transmission spring 56 counterclockwise in FIG. 6, the other end side engagement portion 56b of the power transmission spring 56.
The second spring contact portion 57a, to which is fixed, is moved counterclockwise in FIG. The second spring contact portion 57a has a first
6 of the intermediate gear 53 of FIG.
The second intermediate gear 57 rotatably supported by the second intermediate gear 57 is provided so as to project toward the front side in FIG. 6, and the second intermediate gear 57 is moved by the movement of the second spring contact portion 57a.
Rotate counterclockwise inside.

Since the second intermediate gear 57 rotates counterclockwise in FIG. 6, the tooth 58b formed on the second intermediate gear 57 meshes with the sector 58 to move the sector 58 to the timepiece in FIG. Since the swing arm 60 mounted on the sector 58 via the output shaft 59 is rotated from the return position a to the output position b, the door opening / closing mechanism connected to the swing arm 60 is moved to the lock side. It is designed to switch.

In such an actuator 50, the second
The second spring abutment portion 57a of the intermediate gear 57 is provided at a position slightly separated in the centripetal direction of the first spring abutment portion 53a of the first intermediate gear 53, and the power transmission spring 5
6 is provided with a central support portion 56c which is substantially C-shaped and in which the first intermediate gear 53 and the second intermediate gear 57 are supported at the center of 57. Is provided with one end side engaging portion 56a that axially protrudes toward, and the other end side engaging portion 56b that protrudes outward from the other end side of the central support portion 56c in a ring shape, and the like. The end side engagement portion 56b is attached to the second spring contact portion 57a of the second intermediate gear 57.

Then, when the swing arm 60 and the second intermediate gear 57 stop at the turning end, the first intermediate gear 5 with respect to the one end side engaging portion 56a of the power transmission spring 56.
The first power transmission spring 60 is bent by abutting the first spring abutment portion 53a of the third intermediate gear 53a, so that the first intermediate gear 5
3 is stopped at the rotation end while being braked.

However, in the above-mentioned conventional actuator 50, the first spring contact portion 53a of the first intermediate gear 53 is engaged with the one end side engaging portion 56a of the power transmission spring 56.
Has a structure in which the first intermediate gear 53 is braked at the rotation end by the contact of the first intermediate gear 53 with the first end of the power transmission spring 56 from the other end side contact portion 56b toward the one end side contact portion 56a.
When the intermediate gear 53 of 1 rotates and the first spring contact portion 53a contacts the spring contact portion 56a on the one end side, the power transmission spring 56 cannot be deflected, whereby
There is a problem that it is difficult to brake the first intermediate gear 53, and when the first intermediate gear 53 is stopped without being braked, an impact is generated at the rotating end to cause abnormal noise.

[0009]

The problem to be solved is that if the first intermediate gear is stopped without being braked, abnormal noise may be generated.

[0010]

Configuration of the Invention

[0011]

According to the present invention, since the first intermediate gear is braked and then stopped, the first intermediate gear is normally rotated by the power supply on the positive side and is reversely rotated by the power supply on the opposite side. A motor provided with a motor shaft; a first intermediate gear that is provided with a first spring contact portion and rotates by receiving the power of the motor shaft; and a first spring contact portion of the first intermediate gear. A second intermediate gear having a second spring abutment portion near the centripetal direction side, and in a state of meshing with the second intermediate gear, is rotated integrally with the output shaft by the power of the second intermediate gear. The sector is in contact with the first spring contact portion of the first intermediate gear and in contact with the second spring contact portion of the second intermediate gear. Two
In the actuator provided with the power transmission spring for transmitting to the intermediate gear, a brake spring for damping the rotational force of the first intermediate gear is provided near the rotation end of the first intermediate gear. In a more preferable embodiment, the brake spring is attached to the second intermediate gear, and the rotational force of the first intermediate gear is attenuated by contact with the power transmission spring. , The first intermediate gear is reliably braked and then stopped to achieve the purpose of quieting the operating noise.

[0012]

In the actuator according to the present invention, the braking force of the first intermediate gear is attenuated at the rotation end by the brake spring, and then the actuator is stopped. Therefore, the speed of the first intermediate gear is temporarily reduced at the rotation end. Since it stops, there is no stress that causes an impact.

[0013]

1 to 5 show an embodiment of an actuator according to the present invention.

In the illustrated actuator 1, a motor 3 is assembled on the lower side of the case 2 in FIG. 1, and a motor pinion 4 is press-fitted onto a motor shaft 3a provided on the motor 3 so as to be fixed. The motor pinion 4 is rotated in the forward direction or the backward direction side by supplying the positive side or the reverse side power from the external terminals 3b and 3c connected to the brush (not shown) of the motor 3.

A second intermediate gear 6 having a spur gear and a spur gear having a diameter larger than that of the second intermediate gear 6 are provided on a pivot 5 supported on the upper side of the motor 3 substantially at the center of the case 2. 2, the first intermediate gear 7 is formed concentrically with the first intermediate gear 7 being superposed on the left side of the second intermediate gear 6 in FIG.

The tooth portion 6a provided on the second intermediate gear 6 is shown in FIG.
At the center of the top wall 6b formed on the right side of the inside, there is provided an annular convex portion 6c for holding the first intermediate gear 7 at a position with a predetermined separation dimension, and the annular convex portion 6c. A second spring contact portion 6d, which has a substantially rectangular shape and protrudes toward the first intermediate gear 7 side, is provided on a part of the top wall 6b outside of.

At the center of the bottom wall 7b formed on the inner peripheral side of the tooth portion 7a provided in the first intermediate gear 7, a fitting portion is loosely fitted on the inner peripheral side of the annular convex portion 6c of the second intermediate gear 6. 7c is provided, and at a position slightly separated outside the second spring abutting portion 6d on the outside of the fitting portion 7c, a substantially rectangular shape is formed and a second intermediate portion on the left side in FIG. A first spring contact portion 7d that projects toward the gear 6 side is provided.

On the outer side of the first spring contact portion 7d of the first intermediate gear 7, as shown in FIG.
An annular brake spring mounting groove 7 on the inner peripheral side of a
e is formed, the motor pinion 4 of the motor 3 is engaged with the tooth portion 7a, and the brake spring 8 is mounted in the brake spring mounting groove 7e.

The brake spring 8 is formed by bending an elastic material into a C shape, and is bent toward the inner peripheral side at one end side of the spring body 8a to form a first spring contact of the first intermediate gear 7. A gear locking portion 8b for locking the contact portion 7d is provided,
The other end of the spring body 8a is provided with a power transmission spring engaging projection 8c which is triangular and slightly protrudes toward the inner peripheral side.

The gear locking portion 8b of the brake spring 8
Is locked to the first spring contact portion 7d of the first intermediate gear 7, the brake spring 8 is mounted in the brake spring mounting groove 7e of the first intermediate gear 7, and in this state, The power transmission spring engagement protrusion 8c projects toward the second spring contact portion 6d side of the second intermediate gear 6, which is the inner peripheral side.

A power transmission spring 9 is attached to the outside of the annular convex portion 6c of the second intermediate gear 6. The power transmission spring 9 is formed by bending an elastic material, and as shown in FIG. 1, the power transmission spring 9 is formed.
An approximately C-shaped pivot support 9a having an inner diameter larger than the outer diameter of the annular projection 6c of the second intermediate gear 6 is provided substantially at the center of the pivot support 6a. Is mounted on the outer side of the annular convex portion 6c of the second intermediate gear 6.

Here, the pivot support portion 9 of the power transmission spring 9 is used.
On the upper side in FIG. 1, which is the one end side of a, the pivot support portion 9
An extension portion 9b is provided so as to project from the a along the radial direction of the second intermediate gear 6, and the second spring contact portion 6d of the second intermediate gear 6 is provided on the tip side of the extension portion 9b. Is provided with a fixing portion 9c having a fitting dimension smaller than the spacing dimension of the side walls 6d1 and 6d2 located at the opposite positions of the second spring contact portion 6 of the second intermediate gear 6.
It is fixed by elastically fitting to d.

A second spring contact portion 6d of the second intermediate gear 6 is provided at the central portion of the fixed portion 9c of the power transmission spring 9.
9d protruding from the first intermediate gear 7 in the radial direction of the second intermediate gear 6 toward the first spring contact portion 7d of the first intermediate gear 7.
Is provided, and the projecting dimension of this convex portion 9d from the second spring contact portion 6d is the second spring contact portion 6 of the second intermediate gear 6.
It is larger than the distance from the distance d to the first spring contact portion 7d of the first intermediate gear 7.

The pivot support portion 9 of the power transmission spring 9
On the lower side in FIG. 1 which is the other end side of a, the pivot support portion 9
The shaft portion 9e linearly protrudes from the a along the radial direction of the second intermediate gear 6, and the protruding size of the shaft portion 9e is the distance from the pivot support portion 9a to the first intermediate gear 7. Is bigger than

When the first intermediate gear 7 is rotated clockwise in the figure in the state shown in FIG. 1, the first spring contact portion 7d of the first intermediate gear 7 causes the power transmission spring to move. Shaft 9
Since the shaft portion 9e is pressed against the shaft portion 9e in a clockwise direction,
The power of the intermediate gear 7 is transmitted to the second intermediate gear 6 via the power transmission spring 9 to rotate the second intermediate gear 6 in the clockwise direction, and at the rotation end of the second intermediate gear 6, Since the first spring contact portion 7d of the first intermediate gear 7 bends the shaft portion 9e of the power transmission spring 9 toward the extension portion 9b, the first intermediate gear 7 is braked and then stopped. It has become.

When the first intermediate gear 7 is rotated counterclockwise in the figure, the first spring contact portion 7d of the first intermediate gear 7 is projected on the fixing portion 9c of the power transmission spring 9. When engaged with the portion 9d, the power of the first intermediate gear 7 is transmitted to the second intermediate gear 6 via the power transmission spring 9, and the second intermediate gear 6 is rotated counterclockwise to 2 intermediate gear 6
At the rotation end of the first intermediate gear 7, the first spring contact portion 7d
Engages with the convex portion 9d of the power transmission spring 9 assembled to the second intermediate gear 6, and the first intermediate gear 7 is braked by the elastic repulsive force of the convex portion 9d and then stopped. It is like this.

On the other hand, FIG. 1 of the first and second intermediate gears 7, 6
An output shaft 10 is rotatably supported by a case 2 on the upper side in the inside, and a sector 11 is fixed to an inner portion of the case 2 of the output shaft 10 and an output shaft 1 is provided.
The base end side of the swing arm 12 is fixed to the outer portion of the case 0 of 0, and the tooth portion 6a of the second intermediate gear 6 is meshed with the sector 11 to correspond to the rotation of the sector 11. Thus, the swing arm 12 outputs and moves from the return position A to the output position B.

The actuator 1 having such a structure
Is to connect a power source to the external terminals 3b and 3c of the motor 3 via a switch (not shown), connect a door opening / closing mechanism as a load to the tip end side of the swing arm 12, and then switch the switch to the lock-on side. External terminal 3
When the positive side power is supplied to the motor 3 from b and 3c, the motor pinion 4 is rotated in the counterclockwise direction in FIG. 1, which is the positive side, so that the first intermediate gear 7 meshing with the motor pinion 4 receives power. Is transmitted to rotate the first intermediate gear 7 in the clockwise direction in FIG.

As the first intermediate gear 7 rotates clockwise in FIG. 1, the first spring contact portion 7d of the first intermediate gear 7 is moved to the power transmission spring 9 as shown in FIG. Shaft 9
Since the shaft portion 9e is pressed in the clockwise direction when engaged with e, the power of the first intermediate gear 7 is transmitted by the power transmission spring 9
Is transmitted to the second intermediate gear 6 via the to rotate the second intermediate gear 6 in the clockwise direction.

As shown in FIG. 4, since the second intermediate gear 6 is rotated clockwise by the first intermediate gear 7 in the figure, the sector 11 receives power from the second intermediate gear 6. 1 to rotate clockwise in FIG. 1, the swing arm 12 is output-moved from the return position A to the output position B in FIG. 1, and the output movement of the swing arm 12 locks the door opening / closing mechanism from the unlocked state. Switch to the state.

The swing arm 12 has an output position B in FIG.
Since the second intermediate gear 6 also stops rotating at the point where the second intermediate gear 6 has been moved to and stopped, the first spring contact portion 7d of the first intermediate gear 7 causes the shaft portion 9e of the power transmission spring 9 to extend to the extension portion 9b. In order to bend the first side gear 7 to the side, the first intermediate gear 7 is braked by the elastic deformation of the power transmission spring 9 and then stops.

At the same time when the power supply to the motor 3 is stopped, the power from the motor 3 side is applied to the first intermediate gear 7
Therefore, the elastic force of the power transmission spring 9 causes the first intermediate gear 7 to return and rotate counterclockwise from the state shown in FIG.

Since the first intermediate gear 7 returns and rotates in the counterclockwise direction in FIG. 4, the brake spring 9 also rotates integrally with the first intermediate gear 7 in the counterclockwise direction in FIG. As shown in FIG. 5, in the second intermediate gear 6 in the stopped state corresponding to the stop of the swing arm 12 at the output position B, the power transmission spring of the brake spring 8 is opposed to the convex portion 9d of the power transmission spring 9. Since the engagement protrusion 8c is engaged, the first intermediate gear 7 is braked and then stopped.

Therefore, by switching the switch to the unlock side from the state shown in FIG. 5, the external terminal 3b,
When the reverse side power is supplied to the motor 3 from 3c, the motor pinion 4 is rotated in the clockwise direction in FIG. 1, which is the reverse side, so that power is transmitted to the first intermediate gear 7 meshing with the motor pinion 4. , The first intermediate gear 7 is rotated counterclockwise in FIG.

When the first intermediate gear 7 rotates counterclockwise in FIG. 5, the brake spring 8 also rotates integrally with the first intermediate gear 7 counterclockwise in FIG. The engagement of the spring 8 with the power transmission spring engagement projection 8c is released,
When the first spring contact portion 7d of the first intermediate gear 7 engages with the convex portion 9d of the power transmission spring 9, the second intermediate gear 6
Is rotated counterclockwise in FIG.

Since the second intermediate gear 6 rotates counterclockwise in FIG. 5, the swing arm 1 passes through the sector 11.
Since 2 is moved back from the output position B in FIG. 1 to the return position A, the return movement of the swing arm 12 switches the door opening / closing mechanism from the locked state to the unlocked state.

[0037]

As described above, since the actuator according to the present invention has the above-mentioned structure, the brake spring damps the rotational force of the first intermediate gear at the rotational end and then stops, so that the impact is reduced. It is possible to stop the first intermediate gear in a state where there is no rotational force to generate, and thereby, there is an excellent effect that a quiet operation can be performed.

[Brief description of drawings]

FIG. 1 is a partially cutaway front view of an embodiment of an actuator according to the present invention.

FIG. 2 is a partially cutaway side view of the actuator shown in FIG.

FIG. 3 is a front view illustrating a positional relationship between a first intermediate gear and a second intermediate gear when the actuator illustrated in FIG. 1 is operated.

4 is a front view illustrating a positional relationship between a first intermediate gear and a second intermediate gear when the actuator illustrated in FIG. 1 is operated.

5 is a front view for explaining the positional relationship between the first intermediate gear and the second intermediate gear when the actuator shown in FIG. 1 is operating.

FIG. 6 is a partially cutaway front view of a conventional actuator.

[Explanation of symbols]

 1 Actuator 3 Motor 3a Motor shaft 6 Second intermediate gear 6d Second spring contact part 7 First intermediate gear 7d First spring contact part 8 Brake spring 9 Power transmission spring member 10 Output shaft 11 Sector

Claims (2)

[Claims] 1. A motor provided with a motor shaft that rotates forward when power is supplied to the positive side and reversely rotates when power is supplied to the opposite side, and a first spring contact portion is provided and receives power from the motor shaft. A rotating first intermediate gear, a second intermediate gear having a second spring abutting portion provided in the vicinity of the centripetal direction side of the first spring abutting portion of the first intermediate gear, and the second intermediate gear A sector that rotates integrally with the output shaft by the power of the second intermediate gear while meshing with the intermediate gear; and a sector that abuts the first spring abutment portion of the first intermediate gear and the second intermediate gear. An actuator provided with a power transmission spring for transmitting power from the first intermediate gear to the second intermediate gear in a state of being in contact with the second spring contact portion of the first intermediate gear, A brake for damping the rotational force of the first intermediate gear near the rotation end. Actuator, characterized in that a spring. 2. The actuator according to claim 1, wherein a brake spring is mounted on the second intermediate gear, and the rotational force of the first intermediate gear is attenuated by contact with the power transmission spring.