JP3229780B2 - Actuator - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an actuator having a swing mediating gear mechanism as a clutch mechanism, and more particularly to an improvement of the swing mediating gear mechanism.

[0002]

2. Description of the Related Art For example, a compact electric motor and a geared motor integrated with a housing provided with a reduction gear mechanism are generally used as a linear actuator for unloading a recording medium in a CD (compact disk) player or the like. . High torque is output to the output shaft of the reduction gear mechanism by the rotation of the rotating shaft of the electric motor, and the output shaft rotates forward and backward by the forward and reverse rotation of the rotating shaft of the electric motor. However, with the motor drive stopped,
Since it is necessary to manually move the medium loading tray, which is the operation target (load) of the actuator itself, as needed, there is known a speed reduction mechanism provided with a clutch mechanism for intermittently connecting the drive side and the load side.

[0003] FIG. 3 is a Japanese Patent Application Laid-Open No. 6-1 of the present applicant.
FIG. 4 is a side sectional view showing a clutch device of a recording medium driving device disclosed in Japanese Patent No. 29442, and FIG. 4 is a plan view thereof. 3 and 4, the clutch device 10 has a chassis 25 fixed to a housing of the motor 11, and a driving gear (drive gear) connected to a rotating shaft 111 of the motor 11 via a multi-stage reduction gear mechanism. ) 15, an arm 17 swingable around its axis 151, and a driving gear (drive gear) 1
5 includes a medium gear 18 rotatable around a shaft 19 fixed to the arm 17, and a friction clutch mechanism 21 in which a disc spring 20 is interposed between the flange portion 191 of the shaft 19 and the medium gear 18. Have.

When the DC motor 11 operates and the rotating shaft 111 rotates, the driving gear 15 rotates around the shaft 151 by an arrow Cw.
The planetary kinetic force in the direction of the arrow Cw with the driving gear 15 as the sun wheel is transmitted to the intermediary gear 18 that rotates in the direction of the arrow, and the intermediary gear 18 moves in the direction of the arrow Cw around the driving gear 15. In order to revolve, the arm 17 has a shaft 151
Swing in the direction of arrow Cw. Here, since the intermediate gear 18 is connected to the arm 17 side via the friction clutch mechanism 21 having the disc spring 20, the drive transmitted to the intermediate gear 18 by the static friction force of the friction clutch mechanism 21. The force acts not as a driving force for the rotation of the intermediate gear 18 but as a driving force for the arm 17 to revolve around the shaft 151 in the direction of the arrow Cw. Accordingly, the intermediate gear 18 revolves around the driving gear 15 in the direction of the arrow Cw, and the arm 17 rotates around the axis 151 until the shaft 19 of the intermediate gear 18 contacts the inner edge 261 of the opening 26. However, the intermediate gear 18 does not rotate during the previous swing, and the rack 4 on the load side does not rotate.
1 contacts and meshes. Then, after the engagement, the friction clutch mechanism 21 enters a slip state, and the intermediate gear 18 starts to rotate around the shaft 19 in the direction of arrow CCw, so that the load-side rack 41 is sent out in the direction of arrow E. And ejects the tray 40. During this time,
The force for swinging the arm 17 causes the intermediate gear 18 to move to the rack 41.
It continues to act as a force to hold down.

Next, when the DC motor 11 rotates in the reverse direction, the intermediate gear 15 rotates around the shaft 151 in the direction of arrow CCw, and the arm 17 moves the rotation shaft 19 of the intermediate gear 18 to the inner edge 263 of the opening 26. Swings around the shaft 151 in the direction of the arrow CCw until it comes into contact with the intermediate gear 18 and the rack 41 is disengaged. Thereafter, the friction clutch mechanism 21 slips, and the intermediate gear 18
Around the vehicle in the direction of arrow CCw. In this state, since the intermediate gear 18 is not engaged with the rack 41, the drive source side and the load side rack 41 are in a mechanically free state. Therefore, the tray 40 must be manually loaded in the arrow L direction. Is possible.

[0006]

However, the actuator disclosed in Japanese Patent Laid-Open No. 6-129442 has the following problems.

The arm 1 is driven by the forward rotation of the motor 11.
7 is swung in the direction of the arrow Cw so that the intermediate gear 18 and the rack 4
After the gear 1 is engaged, the tray 40 can be ejected by a motor drive in the direction of arrow E by rotating the intermediate gear 18 in the direction of arrow CCw, but the arm 17 swings in the direction of arrow CCw by the reverse rotation of the motor 11, and Gear 18
Only the disengagement of the tray 40 with the rack 41 is released, and the tray 40 must be manually pushed in instead of being sent in the direction of arrow L by the motor drive.

For example, when the actuator disclosed in JP-A-6-129442 is applied to a curtain driving device for opening and closing a curtain for a vehicle, the driving side and the load side can be separated. Can be opened and closed manually. However, since either the opening operation or the closing operation of the curtain can only be driven by the motor, it is not suitable for application to a curtain driving device in which both the forward movement and the forward movement on the load side are driven by the motor.

In order to release the engagement between the intermediate gear 18 and the rack 41, it is necessary to separate the arm 17 by a slight reverse rotation of the motor, so that a short reverse rotation period is provided at the end of the forward rotation of the motor. It must be generated by the motor control circuit. However, since there is an inherent variation between the actuator products, the separation distance of the intermediary gear 18 retreating from the meshing point due to the reverse rotation varies, so that this time until the gear reaches the meshing point by the forward rotation. Variations occur in time, resulting in variations in load drive response characteristics.

[0010] In view of the above problems, a first object of the present invention is to make it easy to intermittently connect the power between the load side and the drive source side and to manually operate the load side. An object of the present invention is to provide an actuator which enables reciprocal movement (forward / reverse rotation) on the load side by forward / reverse rotation of a motor. An object of the present invention is to provide an actuator capable of realizing a uniformly defined neutral state without variation among products by achieving the reverse rotation instead of the reverse rotation.

[0011]

In order to solve the above problems, a first means of the present invention is characterized by using two pairs of oscillating intermediate gears. That is, the present invention provides a driving gear connected to a rotating shaft of a motor via a reduction gear mechanism, an arm swingable around the axis of the driving gear, and a rotatably supported by the arm. In an actuator having an intermediary gear meshed with a driving gear and a frictional force applying means interposed between the arm side and the intermediary gear side, the arm is located at a point symmetrical position with respect to the swing center thereof. The first and second intermediate gears are supported by a shaft.
Ri, the axis of the driven gear to be meshed with the first and second intermediary vehicle substantially located on the rotation axis of the motor, also first mediated wheel center of rotation and the second mediator with respect to the swing center The angle formed by the center of rotation of the car is less than 180 ° .
You . Further, as the frictional force applying means, a spring member that pushes a gap between the arm side and the intermediate gear side can be adopted.

A second means taken by the present invention is the actuator having the above-mentioned structure, wherein the swing position of the arm is set to a neutral position when the rotation shaft of the motor stops rotating,
It is characterized by having a clutch operating means for releasing the above-mentioned regulation when the rotation shaft of the motor rotates. here,
It is preferable to employ electromagnetic solenoid driving means as the clutch operating means.

[0013]

In the first means of the present invention, when the driving gear (motor) rotates in one direction, the two intermediate gears, ie, planetary gears meshing with the driving gear, revolve in one direction, and accordingly the arm is driven by the driving gear. Swings around one direction. Here, since the frictional force applying means is interposed between the arm side and the intermediate gear side, the intermediate gears revolve without rotating due to the static frictional force during the swing of the arm. By the swing of the arm in one direction, the first intermediate gear approaches and meshes with the driven gear including the rack and the like, and the engagement causes the frictional force applying means to slip, and the first intermediate gear shifts in the other direction. It rotates and transmits driving force to the driven gear. Conversely, when the driving gear (motor) rotates in the other direction, the two intermediate gears revolve in the other direction, and accordingly, the arm swings in the other direction about the driving gear. This swing of the arm in the other direction causes the second intermediate gear to approach and mesh with the driven gear including the rack and the like. It rotates in the direction and transmits the driving force to the driven gear. As described above, the rotation direction of the driven gear can be changed depending on the difference in the rotation direction of the motor, and it is possible to drive the motor in both rotation directions. Of course, no driving force is transmitted (neutral state) between the one-way swing position of the arm where the first intermediate gear meshes with the driven gear and the other direction swing position of the arm where the second intermediate gear meshes with the driven gear. It is. Therefore, after transmitting the driving force,
By generating the motor reverse rotation drive for a short time so as to release the engagement between the intermediate gear and the driven gear, a neutral state can be easily obtained. Therefore, the load side can be manually operated in any direction. Even if you do not release the mesh,
The driven gear on the load side can be manually rotated in the direction opposite to the biting direction of the intermediate gear, that is, in the direction of the arm's swing allowance.

When the follower is moved directly, a rack can be employed. However, when the follower is rotated, the shaft of the driven gear to be meshed with the first and second intermediate gears in order to downsize the geared motor. Is positioned substantially on the motor rotation axis, and the angle θ between the rotation center of the first intermediate gear and the rotation center of the second intermediate gear with respect to the swing center is set to less than 180 °. Here, since the arm swings due to a couple due to the two intermediate gears caused by the meshing pressure angle, the arm length of the arm can be made shorter than in the case of one intermediate gear. Further, since the opening of the arm can be narrowed, the intermediate gear can be arranged closer to the driven gear, and the intermediate gear displacement region can be contained within the end face region of the motor. Therefore, compactness can be achieved. Also,
Since the distance between the motor rotation axis and the intermediate gear is short, the response speed when switching the rotation direction can be increased.

According to a second aspect of the present invention, there is provided a clutch operating means for defining the swinging position of the arm at the neutral position when the rotation of the rotating shaft of the motor is stopped, and releasing the above-mentioned regulation when the rotating shaft of the motor is rotated. Consisting of Instead of bringing the arm to the neutral position by the motor drive, the arm is directly driven by the dedicated clutch operating means to regulate the arm to the neutral position, so the swing of the arm varies between actuator products. Even if there is, the neutral state can be directly secured, and the product yield can be improved, and the response characteristics of the switching of the rotating direction can be standardized. Further, even in the neutral state, the arm does not swing due to vibration or the like applied to the actuator, and the neutral state is maintained.

When an electromagnetic solenoid driving means is used as the clutch operating means, when the motor is driven, the electromagnetic solenoid is energized to release the pressing of the plunger to the arm so that the arm can freely swing. By stopping the energization of the electromagnetic solenoid, the arm can be pressed from the plunger and restrained in a neutral state, so that the energization control of the motor drive can be directly used for the control of the clutch operating means, and the configuration of the control system Can be simplified. Further, since the swing control of the arm requires only a small load, the configuration of the electromagnetic solenoid driving means itself can be reduced in size.

[0017]

Next, an embodiment of the present invention will be described with reference to the accompanying drawings.

[First Embodiment] FIG. 1 is a plan view showing an actuator according to a first embodiment of the present invention. The actuator of this embodiment includes a driving gear 41 connected to a rotating shaft 11 a of the motor 11 via a reduction gear mechanism 30, an arm 50 swingable about the driving gear 41, and an arm 5.
A pair of intermediate gears 61 rotatably supported at 0 and meshed with the driving gear 41, and a wave washer (shown in the drawing) as frictional force applying means interposed between the arm side and the intermediate gear side. Z).

In this embodiment, a lower chassis 21, a middle chassis (not shown),
The upper chassis 22 is hierarchically stacked with through screws 22b and 22b and a sleeve-like spacer (not shown), and a first floor space between the lower chassis 21 and the middle chassis;
In a second floor space between the middle chassis and the upper chassis 22, a gear mechanism and the like to be described later are housed. The output shaft 23 supported by the bearing 22 a of the upper chassis 22 is a rotating shaft 1 of the motor 11.
They are aligned on the axis of 1a. First, in the first floor space,
The first small gear 31 fixed to the rotating shaft 11a of the motor
It is in mesh with the large gear 32. The second small gear 33 fixed to the shaft on the first large gear 32 meshes with a second large gear 34 having a different axis. The third gear fixed to the shaft on the second large gear 34
The small gear 35 meshes with a third large gear 36 having a different axis from the shaft on the first large gear 32. The shaft of the third large gear 36 penetrates the middle chassis and protrudes into the second floor space, and has a fourth small gear 37 in the second floor space. In the second floor space, the fourth small gear 37 meshes with a fourth large gear 38 having an axis on the axis of the rotating shaft 11 a of the motor 11. Gear 31
The gear mechanism constituted by the gears 38 to 38 is a four-stage reduction gear mechanism 30.
Is composed.

A fourth large gear 38 having an axis on the motor axis in the second floor space is meshed with a gear 40 coaxial with a driving gear 41. The driving gear 41 has its shaft 40
a. The arm 50 is a bifurcated plate that can swing around the axis 40a, and has a first
The second intermediate gear 62 and the second intermediate gear 62 are rotatably supported, and both the intermediate gears 61 and 62 of the planetary gear mesh with the driving gear 41 of the sun gear. Intermediate gear 61, 6
The second shafts 61a and 62a protrude above the upper chassis 22, and are pivoted by the arm 50 in the counterclockwise direction.
a comes into contact with the notch edge 61b for defining the appropriate meshing, and the shaft 62a comes into contact with the notch edge 62b for defining the appropriate meshing by swinging the arm 50 clockwise. Either one of the intermediate gears 61 and 62 can mesh with the driven gear 70 fixed to the center output shaft 22b.

When the motor 11 operates and the rotating shaft 11a rotates clockwise, the driving gear 41 serving as the sun gear rotates counterclockwise via the reduction gear mechanism 30, so that the planetary gear meshes with the driving gear 41. Two intermediate gears 6
1 and 62 revolve in the counterclockwise direction, and the arm 50
Swings around the shaft 40a in the counterclockwise direction. Here, since a wave washer as a frictional force applying means is interposed between the arm 50 side and the intermediary gears 61 and 62 side, the static frictional force is exerted while the arm 50 swings counterclockwise. Accordingly, the intermediate gears 61 and 62 revolve in the counterclockwise direction without rotating. The counterclockwise swing of the arm 50 causes the first intermediate gear 61 to start meshing with the center driven gear 70. This engagement produces a drag on the arm 50, so that the wave washer is in a slip state, and the first intermediate gear 61 rotates clockwise to transmit counterclockwise torque to the driven gear 70. When the first intermediate gear 61 starts meshing, the meshing is further deepened, and there is a possibility that excessive biting may occur. The first intermediate gear 61 is in contact with the notch edge 61b so that the meshing of the first intermediate gear 61 with the driven gear 70 is not excessive.

Conversely, the motor 11 operates and the rotating shaft 11a
When the gear rotates counterclockwise, the driving gear 41 serving as the sun gear rotates clockwise through the reduction gear mechanism 30.
The two intermediate gears 61 and 62, which are planetary gears meshing with the driving gear 41, revolve in the clockwise direction, and the arm 50
Swings around the shaft 40a in the time direction. This arm 50
The second intermediate gear 62 starts to mesh with the center driven gear 70 due to the clockwise swing of
Since a resistance to zero is generated, the wave washer slips, and the second intermediate gear 62 rotates counterclockwise and transmits clockwise torque to the driven gear 70. Arm 5
In the clockwise swinging process of 0, the shaft 62a abuts against the notch edge 62b for defining the appropriate meshing, so that the meshing of the second intermediate gear 62 with the driven gear 70 is not excessive. In this manner, the driven gear 70 rotates forward and backward by the forward and reverse rotation of the motor. Motor drive can be performed in both rotation directions.

Here, of course, the counterclockwise swing position of the arm 50 in which the first intermediate gear 61 meshes with the driven gear 70 and the arm 5 in which the second intermediate gear 62 meshes with the driven gear 70
Intermediate state with 0 clockwise swing position (state shown in FIG. 1)
In this state, the driving force is not transmitted (neutral state). Therefore, the neutral state can be easily obtained by generating the motor reverse rotation drive for a short time so as to release the engagement between the intermediate gear and the driven gear after the transmission of the driving force. Therefore, since the connection from the load side to the reduction gear mechanism 30 is disconnected, the load side can be manually operated lightly in any direction.
Even if the meshing is not released, the driven gear on the load side can be manually rotated in the direction opposite to the biting direction of the intermediate gear, that is, in the direction of the arm swing allowance.

In this embodiment, the angle θ between the rotation center of the first intermediate gear 61 and the rotation center of the second intermediate gear 62 with respect to the shaft 40a is set to about 140 °, which is less than 180 °. As described above, since the opening of the arm 50 can be reduced, even when one of the intermediate gears meshes with the driven gear, the other intermediate gear does not protrude out of the end face region of the motor, thereby realizing compactness. I have. Further, since the distance between the motor rotation axis and the intermediate gears 61 and 62 is short, the response speed at the time of switching the rotation direction can be increased.

Embodiment 2 FIG. 2 is a plan view showing an actuator according to Embodiment 2 of the present invention. In FIG. 2, the same portions as those shown in FIG. 1 are denoted by the same reference numerals, and description thereof will be omitted.

The actuator of this embodiment has a structure in which a clutch operating mechanism is added to the actuator of the first embodiment shown in FIG. The clutch operating mechanism is an electromagnetic solenoid driving mechanism 80, which includes an electromagnetic solenoid 81 fixed on the projecting portion 22c of the upper chassis 22, a positioning plate 83 fixed on the tip of a plunger 82, and a positioning plate wound around the plunger 82. And a return coil spring 84 for urging the elastic member 83 in the pushing direction.

When the motor 11 is operated, the electromagnetic solenoid 81 is also energized to be excited, so that the plunger 82 is pulled in against the urging force of the return coil spring 84. Evacuate until Therefore, the arm 50 can freely swing in the clockwise and counterclockwise directions, so that the arm 50 swings in any direction depending on the rotation direction of the rotating shaft 11a of the motor 11, and the first or second intermediate gear is rotated. It meshes with the driven gear 70 to transmit torque. When the energization is stopped and the operation of the motor 11 is stopped, the electromagnetic solenoid 81 is also demagnetized.
2 is fed out by the urging force of the return coil spring 84. As a result, the positioning plate 83 is displaced to the solid line position, so that the shaft 61a or 62a of the intermediate gear on the retreat side is pushed out to the output shaft 22b, and the radius 50 is forcibly returned to swing, and meshes with the driven gear 70 of the intermediate gear. Is released and a neutral state is set.

As described above, the arm 50 is directly driven by the dedicated clutch operating device to regulate the arm 50 to the neutral position. Therefore, even if there is a variation in the swing of the arm between actuator products, the arm 50 is directly controlled. In this case, the neutral state can be secured, and when the product yield is increased or the motor is stopped, the neutral state is immediately returned to the neutral state. Further, in the neutral state, the positioning plate 8
Since the arm 3 continues to restrain the swing of the arm 50, the arm 50 does not inadvertently swing due to vibration or the like applied to the actuator, and meshing between the intermediate gear and the driven gear when the motor is stopped can be prevented.

The electromagnetic solenoid 81 in the second embodiment is fixed on the overhang 22c.
May be in the way, but in order to avoid this, the mounting position of the electromagnetic solenoid 81 is set in the motor end face occupied area, and a simple link mechanism or the like arranged in the motor end face occupied area is used. Alternatively, the positioning plate may be moved.

Further, in the above embodiment, a gear mechanism is used as the actuator, but a friction wheel, a magnetic gear, or the like may be used.

[0031]

As described above, in the first means of the present invention, the arm which can swing around the axis of the driving gear as the sun gear is pivotally supported at a point symmetrical position with respect to the center of the swing. And first and second intermediate gears. Therefore, the following effects are obtained.

Since the intermediate gear to be meshed with the driven gear is different depending on the difference in the rotation direction of the motor, the rotation direction of the driven gear can be changed, and the motor can be driven in both rotation directions. The neutral state can be easily obtained by generating the motor reverse rotation drive for a short time so as to release the engagement between the intermediate gear and the driven gear after the transmission of the driving force. Therefore, the load side can be lightly manually operated in any direction. Further, the driven gear on the load side can be manually rotated in the direction opposite to the biting direction of the intermediate gear without releasing the meshing.

In particular, according to the present invention, the shaft of the driven gear to be meshed with the first and second intermediate gears is located substantially on the axis of rotation of the motor, and the center of rotation of the first intermediate gear is positioned with respect to the center of oscillation. The angle θ formed by the rotation center of the second intermediate gear is 18
Since it is set to less than 0 °, it is possible to narrow the opening of the arm, intermediary gear can be arranged to approach the driven gear, it is possible to keep the intermediary gear displacement region on the end face region of the motor. Therefore, compactness can be achieved. In addition, since the distance between the motor rotation axis and the intermediate gear is short, the response speed when switching the rotation direction can be increased.

According to a second aspect of the present invention, there is provided a clutch operating means for defining the swinging position of the arm at the neutral position when the rotation of the rotating shaft of the motor is stopped, and releasing the above-mentioned regulation when the rotating shaft of the motor is rotated. Consisting of Even if the swinging condition of the arm varies among the actuator products, a neutral state can be directly secured, and the product yield can be improved and the response characteristics of the switching of the rotating direction can be standardized. Further, even in the neutral state, the arm does not swing due to vibration or the like applied to the actuator, and the neutral state is maintained.

When an electromagnetic solenoid driving unit is used as the clutch operating unit, the motor drive energization control can be directly used for the control of the clutch operating unit, and the configuration of the control system can be simplified. Further, since the swing control of the arm requires only a small load, the configuration of the electromagnetic solenoid driving means itself can be reduced in size.

[Brief description of the drawings]

FIG. 1 is a plan view showing an actuator according to a first embodiment of the present invention.

FIG. 2 is a plan view illustrating an actuator according to a second embodiment of the present invention.

FIG. 3 is a Japanese Patent Application Laid-Open No. 6-129442 filed by the present applicant.
Is a side cross-sectional view showing a clutch device of a recording medium driving device disclosed in Japanese Patent Application Laid-Open (JP-A) no.

FIG. 4 is a plan view of the clutch device of FIG. 3;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 11 ... DC motor 11a ... Rotating shaft 21 ... Lower chassis 22 ... Upper chassis 22a ... Bearing 22b ... Through screw 22c ... Projection part 23 ... Output shaft 30 ... Reduction gear mechanism 31, 33, 35, 37 ... Small gear 32, 34 , 36, 38 ... large gear 40 ... gear 40a, 61a, 62a ... shaft 41 ... driving gear 50 ... swing arm 61 ... first intermediate gear 61b, 62n ... notch edge for defining appropriate meshing 62 ... second Intermediate gear 70: driven gear 80: electromagnetic solenoid driving mechanism 81: electromagnetic solenoid 82: plunger 83: positioning plate 84: return coil spring θ: bending angle of the arm.

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁷ , DB name) F16H 1/00-1/26 F16D 11/00-23/14 G11B 17/04 F16H 37/06

Claims (4)

(57) [Claims] A driving gear connected to a rotating shaft of a motor via a reduction gear mechanism; an arm swingable about the driving gear; and an arm rotatably supported by the arm and rotatably supported by the arm. An actuator having an intermediate gear meshed with a gear and a frictional force applying means interposed between the arm side and the intermediate gear side, wherein the arm is pivoted at a point symmetrical position with respect to its swing center. Comprising the first and second supported intermediate gears ,
The shaft of the driven gear that should mesh with the first and second intermediate gears is
It is almost on the rotation axis of the motor, and
And the rotation center of the first intermediate gear and the second intermediate tooth
An actuator , wherein the angle formed by the center of rotation of the vehicle is less than 180 ° . 2. The actuator according to claim 1, wherein the frictional force applying means is a spring member that pushes a gap between the arm side and the intermediate gear side. 3. The actuator of claim 1 or claim 2, the rocking position of the arm defining a neutral position during the rotation stop of the rotation shaft of the motor, the specified upon rotation of the rotation shaft of the motor An actuator comprising: clutch operating means for releasing the clutch. 4. The actuator according to claim 3 , wherein said clutch operating means is an electromagnetic solenoid driving means.