JP2001074064A - Motor-driven opening/closing device with braking mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent rapid opening and closing of a sliding door due to its self weight when opening and closing the sliding door on a slope without increasing load of a motor. SOLUTION: A braking mechanism 27 to give braking force to a braking shaft 15 of a two-way clutch 11 in reverse input from a sliding door 4 is provided in a device to transmit input rotation from a motor 1 to the sliding door 4 through an outer ring 12 of the two-way clutch 11 by interposing the two-way clutch 11 furnished with the outer ring 12 to rotate interlocked with input rotation from the motor 1 or reverse input rotation from the sliding door 4, the braking shaft 15 arranged on the same shaft as the outer ring 12 and a power breaking and connecting mechanism interposed between the outer ring 12 and the braking shaft 15, to block torque transmission to the braking shaft 15 for input rotation from the motor 1 and to carry out torque transmission to the braking shaft 15 for reverse input rotation from the sliding door 4 in a power transmission route to reach the sliding door 4 from the motor 1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electric opening / closing device having a braking mechanism, and more particularly, to a two-way clutch incorporated in an electric opening / closing device such as a power window of an automobile, an electric sliding door (one-box car), and an electric curtain. The present invention relates to an electric switching device with a braking mechanism provided with a braking mechanism.

[0002]

2. Description of the Related Art For example, in an electric sliding door opening / closing device in an automobile (one-box car), the rotational power of a motor 1 is reduced by a worm and wheel mechanism 2 as shown in FIG. Sliding door 4
Is transmitted to the output shaft that opens and closes. A belt 6 is wrapped around the output shaft via a pulley 5,
The slide door 4 attached to a part of the belt 6 is opened and closed by the rotational power of the motor 1. In the drawing, reference numeral 7 denotes the other pulley around which the belt 6 is hung.

In order to reduce the rotation of the motor 1 by the worm & wheel mechanism 2, it is necessary to use a small motor because the arrangement space is small, and the low rotation speed and high torque of the output shaft required for opening and closing the slide door 4. This is because the motor 1 has a higher rotation speed and a lower torque as compared with the above.

The electromagnetic clutch 3 is provided to enable manual input from the output shaft side, that is, manual opening and closing operation of the slide door 4. That is, since the reduction ratio of the worm & wheel mechanism 2 is generally large,
This is because when the motor 1 is stopped, the connection between the motor 1 and the output shaft must be released in order to enable manual opening and closing.

[0005]

In the above-described electric opening / closing device, the slide door 4 is normally operated with the electromagnetic clutch 3 in the ON state. Therefore, when the door is opened and closed on a sloping road, the slide door 4 is warmed by its own weight. Wheel mechanism 2
The worm-and-wheel mechanism 2 has a high reduction ratio even if the worm-and-wheel mechanism 2 is opened and closed at a speed higher than the output rotation speed of the worm-and-wheel mechanism 2. It does not open and close.

[0006] However, the ignition key OF
In F, the power supply to the electromagnetic clutch 3 is cut off, and the electromagnetic clutch 3 is turned off. In this case, when the slide door 4 is opened and closed on a slope,
May open and close rapidly due to its own weight.

In order to prevent the sliding door 4 from suddenly opening and closing due to its own weight, it is possible to control the opening and closing speed of the sliding door 4 by providing a brake means such as frictional resistance in the door sliding portion. Since the frictional resistance is dragged even when the motor is driven, there is a problem that the load on the motor 1 increases.

Accordingly, the present invention has been proposed in view of the above-mentioned problems. It is an object of the present invention to increase or decrease the load on the motor when the motor is driven, and to open and close the slide door on a slope when the motor is stopped. In such a case, it is to prevent the sliding door from opening and closing rapidly by its own weight.

[0009]

As a technical means for achieving the above object, the present invention provides a main rotating member which rotates in conjunction with an input rotation from a driving source or a reverse input rotation from an opening / closing element; A sub-rotating member disposed coaxially with the main rotating member, and interposed between the main rotating member and the sub-rotating member, and interrupts torque transmission to the sub-rotating member with respect to input rotation from a driving source. And, for a reverse input rotation from the opening and closing element, a two-way clutch equipped with a power connection and disconnection mechanism for transmitting torque to the sub-rotating member is interposed in a power transmission path from the driving source to the opening and closing element, In the one transmitting the input rotation from the drive source to the opening / closing element through the main rotating member of the two-way clutch, a braking mechanism for applying a braking force to the auxiliary rotating member of the two-way clutch at the time of reverse input from the opening / closing element is provided. That And butterflies.

In the present invention, a braking mechanism for applying a braking force to the sub-rotating member of the two-way clutch at the time of reverse input from the opening / closing element is provided. By applying a braking force to the opening / closing element, the opening / closing element can be decelerated.

Specifically, the two-way clutch includes an elastic member that connects the main rotating member and the power connecting / disconnecting mechanism in a rotational direction, and a viscous fluid that is interposed between the power connecting / disconnecting mechanism and the stationary system member. Provided, based on the correlation between the spring constant of the elastic member and the viscous resistance of the viscous fluid, when the main rotating member reaches a predetermined number of rotations, relative rotation of the auxiliary rotating member with respect to the main rotating member, A structure in which a braking force is applied to the auxiliary rotating member by the braking mechanism is possible.

The power connection / disconnection mechanism includes a retainer connected to the main rotating member by an elastic member, and rollers accommodated in pockets formed at equal intervals in a circumferential direction of the retainer, A roller having a structure capable of engaging and disengaging the main rotating member and the sub-rotating member, and a first dog provided on the sub-rotating member side and a second dog provided on the main rotating member side. Along the axial direction, the second dog is in a disengaged position axially away from the first dog, and the second dog is axially close and engages the first dog circumferentially. A structure that can move in the axial direction between the engaging position and the engaging position is easily realized.

[0013]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below in detail. Note that the same parts as those in FIG.

First, in the electric switching device according to the first embodiment, as shown in FIG. 1, a rotation input from a motor 1 as a driving source is reduced by a worm & wheel mechanism 2 and further slid via an electromagnetic clutch 3. The light is transmitted to an output shaft that opens and closes the door 4, and is transmitted to a slide door 4 that is an opening and closing element via a belt 6 wrapped around a pulley 5 coaxially attached to the output shaft. In the present invention, a two-way clutch 11, which will be described in detail later, is interposed between one end of the belt 6 and a power transmission path from the motor 1 to the slide door 4.
That is, the outer ring 12 of the two-way clutch 11 is rotatably supported by the bearing 14 with respect to the casing 13 which is a stationary system, and the belt 6 is wrapped around the outer diameter of the outer ring 12 (corresponding to the pulley 7 in FIG. 12). Structure.

The two-way clutch 11 shown in FIG.
As shown in FIG. 2, an outer ring 12 as a main rotating member and an inner ring 15 as a sub-rotating member arranged coaxially with the outer ring 12.
(Hereinafter, referred to as a braking shaft), a plurality of rollers 16 constituting a power connection / disconnection mechanism interposed between the inner peripheral surface of the outer ring 12 and the outer peripheral surface of the braking shaft 15, and a retainer 17 for holding the rollers 16 And

The retainer 17 is a cylindrical body having a substantially H-shaped cross section, and has, at one end thereof, a plurality of pockets 18 for accommodating the rollers 16 [see FIG. 3B (cross section taken along line BB in FIG. 2). ], And an intermediate shaft 19 is inserted into the other end side with a gap in the axial direction and the radial direction.

The intermediate shaft 19 is, for example, polygonally fitted (for example, by fitting an end inner diameter thereof with a shaft of a stationary member (not shown)).
The inner diameter of the intermediate shaft is fixed to the stationary member by, for example, a square hole and the shaft of the stationary member is a square axis. A viscous fluid, for example, a viscous fluid 20 such as silicone oil is sealed in a gap between the retainer 17 and the intermediate shaft 19, and is sealed with a seal 21 and a stopper 22.

3 is provided between the outer race 12 and the retainer 17.
(A) A centering spring 23, which is an elastic member as shown in FIG. The centering spring 23 includes an annular portion 23a and a pair of engaging portions 23b extending outward from both ends of the annular portion 23a. The annular portion 23a is inserted into the inner diameter of the retainer 17, and a pair of engaging portions is formed. 23 b is inserted into a notch 24 provided at the end of the retainer 17.

In the state shown in FIG. 3 (a), the pair of engaging portions 23b come into contact with the circumferential side walls of the notch portion 24 with their respective elastic forces.
Are connected in the rotation direction, and the outer race 12 of the cage 17 is
Is positioned in the circumferential direction (centering).

As shown in FIGS. 3 (b), 4 (a) and 4 (b), a plurality of cam surfaces 25 are provided on the inner peripheral surface of the outer race 12 at equal circumferential intervals. A wedge gap is formed symmetrically in both the forward and reverse rotation directions. Each roller 16 is disposed between each cam surface 25 and the outer peripheral surface of the brake shaft 15, and is accommodated and held in a pocket 26 of the retainer 17.

FIGS. 3 (a), 3 (b) and 4 (a) show a state where the retainer 17 is centered by the centering spring 23. In this state, the circle of the pocket 26 of the retainer 17 is shown. The center in the circumferential direction coincides with the center in the circumferential direction of the cam surface 25. Therefore, the roller 16 is located substantially at the center of the cam surface 25 (hereinafter, this state is referred to as a neutral position).
It has separated from the wedge gap in both the forward and reverse rotation directions.

In this embodiment, a braking mechanism 27 for applying a braking force to the braking shaft 15 of the two-way clutch 11 at the time of reverse input from the sliding door 4 is provided. The braking mechanism 27
For example, as shown in FIG. 2, a stationary member 28 is disposed at the end of the braking shaft 15 via a gap, and the gap between the braking shaft 15 and the stationary member 28 is, for example, silicone oil or the like. A viscous fluid 29 is sealed and sealed with a seal 30 or the like. The braking mechanism 27 includes a structure other than the viscous fluid, for example, a friction plate that can apply a braking force by slidingly contacting the braking shaft 15 and the braking shaft 15 and the stationary system member 28.
And may be arranged between them.

Further, in this embodiment, the viscous resistance of the viscous fluid 20 which is sealed in the gap between the intermediate shaft 19 and the retainer 17 and imparts rotational resistance to the retainer 17, and rotates the retainer 17 and the outer ring 12 The spring constant of the centering spring 23 connected in the direction is set in the following correlation.

Normally, a rotational resistance is given to the retainer 17 by viscous resistance of the viscous fluid 20 so that the centering spring 23
Is bent to turn on the two-way clutch 11 even with a slight rotation of the outer ring 12, but in this embodiment, the two-way clutch 11 is not turned on until the outer ring 12 around which the belt 6 is wrapped rotates by a considerable amount. To That is, the two-way clutch 11 is turned on when the sliding door 4 reaches a certain speed due to its own weight in order to prevent the sliding door 4 from opening and closing suddenly due to its own weight on a slope or the like when the sliding door 4 is manually opened and closed. To do it.

In the relationship between the rotational speed of the outer race 12 (door speed) and the rotational resistance, as shown in FIG. 5, as the rotational speed of the outer race 12 increases, the rotational resistance of the retainer 17 due to the viscous fluid 20 increases, and the centering occurs. The spring 23 also flexes gradually,
The spring constant increases. Two-way clutch 11 is O
Since the timing of N is determined at the point where the viscous resistance (viscous shear resistance) of the viscous fluid 20 and the spring constant of the centering spring 23 cross, in the case of this embodiment [point X in FIG. Means that the cross point is shifted to the right as compared with the normal case [point Y in FIG.

The shift of the cross point can be realized by arbitrarily selecting one or both of setting the viscous resistance of the viscous fluid 20 to a small value and setting the spring constant of the centering spring 23 to a large value. ,
Thus, it is possible to prevent the two-way clutch 11 from being turned on until the rotation speed of the outer ring 12 (and the retainer 17) becomes considerably large.

Normally, when the sliding door 4 is electrically opened and closed, the rotational power of the motor 1 is transmitted to the belt 6 while being decelerated by the worm & wheel mechanism 2 while the electromagnetic clutch 3 is ON as shown in FIG. The door 4 opens and closes automatically. Two-way clutch 11 interposed at one end of the belt 6
In this example, the outer ring 12 is rotated by the rotation of the belt 6, but as described above, the two-way clutch 11 is set not to be turned on until the number of rotations of the outer ring 12 (and the retainer 17) becomes considerably large. During the opening / closing operation by the operation of the motor 1, the two-way clutch 11 is always in the OFF state,
The retainer 17 rotates with the rotation of the outer ring 12 and the roller 1
6 maintains the neutral position, so that the outer ring 12
Run idle for 5. Therefore, the load on the motor 1 does not increase.

On the other hand, when the power supply to the motor 1 and the electromagnetic clutch 3 is cut off, the operation system of the slide door 4 is released from the input system. Therefore, at this time, the sliding door 4
Can be manually opened and closed. When manually opening and closing the slide door 4, if the slide door 4 tries to open and close rapidly due to its own weight on a slope or the like, the rotation speed of the outer ring 12 becomes considerably larger than when the motor 1 is operated. In this case, the sliding door 4 has a predetermined speed, that is, the number of revolutions of the outer ring 12 (and the retainer 17) is a predetermined value set by the viscous resistance of the viscous fluid 20 and the spring constant of the centering spring 23 [FIG. )), The engaging portion 23b of the centering spring 23 bends,
The relative rotation between the cage 17 and the outer ring 12 is caused by the rotation of the cage 17 with a corresponding delay with respect to the outer ring 12.

When relative rotation occurs between the retainer 17 and the outer ring 12, the roller 16 housed in the pocket 26 of the retainer 17 is pushed by the retainer 17 as shown in FIG. Engages the wedge gap. At this time, since the outer ring 12 is rotating in the direction of the arrow, the roller 16 is engaged with the outer ring 12 and the braking shaft 15 and clamped by the principle of wedge, and is rotated from the outer ring 12 to the braking shaft 15 via the roller 16. The power is transmitted, and the brake shaft 15 rotates integrally with the retainer 17 and the outer ring 12.

When the braking shaft 15 rotates, the braking force is generated by viscous resistance (viscous shear resistance) of a viscous fluid 29 sealed between the braking mechanism 27 provided at an end thereof, for example, a stationary member 28. Works, and the opening and closing speed of the slide door 4 can be reduced through the outer ring 12 that rotates integrally with the braking shaft 15 and the belt 6 wrapped around the outer ring 12.

The present invention can be applied to a two-way clutch other than the two-way clutch applied in the first embodiment, for example, a dog type two-way clutch. The dog type two-way clutch is attached to one end of the belt 6 as in the first embodiment (see FIG. 1). Note that the same or corresponding parts as those of the two-way clutch according to the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

The dog type two-way clutch 31 used in the second embodiment has a braking shaft 15 rotatably supported as shown in FIG. The clutch ring 33 constituting the connection / disconnection mechanism is the second dog 3
4 and is circumferentially fixed to the outer race 12 which is rotated by engaging with the belt 6, and the second dog 34 is
Has a structure in which the second dog 34 is axially movable between a detached position axially separated from the dog 32 and an engagement position at which the second dog 34 is engaged with the first dog 32 in the circumferential direction.

Specifically, the first cam member 35 is attached to the outer race 12.
Are rotatably accommodated, and the outer ring 12 and the first cam member 35 are held at predetermined relative angular positions by the centering spring 23. A V-shaped trough-shaped cam surface 36 is formed on an end surface of the first cam member 35. A second cam member 38 having a V-shaped mountain-shaped cam surface 37 corresponding to the cam surface 36 of the first cam member 35 is accommodated in the inner diameter of the outer ring 12 so as to be movable in the axial direction.

The first cam member 35 and the second cam member 38 which constitute a power connection / disconnection mechanism together with the clutch ring 33 constitute a cam mechanism. As shown in FIG. 7, the second cam member 38 has a convex portion 39 on the outer periphery, and the convex portion 39 engages with an axial groove 40 formed on the inner diameter of the outer ring 12 so that the second cam member 38 12 is fixed (rotationally stopped) in the rotation direction.

The second cam member 38 has a small-diameter shaft portion 42 integrally with a flange portion 41 having a convex portion 39, and the outer periphery of the small-diameter shaft portion 42 is slidably fitted into a through hole of the clutch ring 33. (See FIG. 6). The clutch ring 33 has a disk shape, and its outer peripheral surface is accommodated in the outer ring 12 so as to be movable in the axial direction, and has a convex portion 43 that engages with the axial groove 40, and is fixed to the outer ring 12 in the rotational direction ( Has been stopped).

As shown in FIG. 8, the clutch ring 33 has a second dog 34 protruding from one end surface thereof. The output shaft 15 rotatably fitted to the outer ring 12 has a first dog 32 protruding from an end face facing the clutch ring 33.
Having. Each of the illustrated clutch ring 33 and brake shaft 15 has four dogs 34, 32 at equal intervals in the circumferential direction.
Are exemplarily provided. The clutch ring 33 moves in the axial direction, and the dog 34 of the clutch ring 33
When they are engaged with the dog 32 of the fifth, both are integrated in the rotational direction. That is, a dog clutch is constituted by the clutch ring 33 and the braking shaft 15.

A compression coil spring 44 is interposed between the second cam member 38 and the clutch ring 33 to resiliently press the two in a direction to separate them from each other. Also, the clutch ring 33
Another compression coil spring 45 is also interposed between the brake shaft 15 and the brake shaft 15 to resilient the two in a direction to separate them from each other. The axial movement of the clutch ring 33 downward in the figure is restricted by a retaining ring 46 mounted on the inner diameter of the outer ring 12. When the motor 1 is stopped, the elastic force of the two compression coil springs 44 and 45 is set to have a predetermined relationship so that the clutch ring 33 and the brake shaft 15 do not mesh with each other.

In the second embodiment, as in the first embodiment, the braking shaft 15 of the two-way clutch 31 is provided with a braking mechanism 27 for applying a braking force when the sliding door 4 is reversely input. The braking mechanism 27 includes, for example, a stationary member 28 disposed at an end of the braking shaft 15 via a gap as shown in FIG.
, A viscous fluid 29 such as silicone oil is sealed in the gap between them, and sealed with a seal 30 or the like. The braking mechanism 27 has a structure other than the viscous fluid, for example,
A friction plate capable of applying a braking force by sliding contact with the braking shaft 15 may be disposed between the braking shaft 15 and the stationary member 28.

As in the case of the first embodiment, the viscous resistance of the viscous fluid 20 which is sealed in the gap between the intermediate shaft 19 and the first cam member 35 and imparts rotational resistance to the first cam member 35, The spring constant of the centering spring 23 that holds the first cam member 35 at a predetermined relative angular position is set to a predetermined correlation (see FIG. 5A).

Normally, when the sliding door 4 is electrically opened and closed, the outer ring 12 is also rotated by the rotation of the belt 6 in the second embodiment. The clutch 31 is not turned on. Since the V-shaped cam surface 37 of the second cam member 38 is fitted into the V-shaped valley cam surface 36 of the first cam member 35 by the elastic force of the compression coil spring 44,
The first cam member 35 and the second cam member 38 together with the outer race 12
, The clutch ring 33 does not move in the axial direction, and the outer ring 12 idles with respect to the brake shaft 15, so that the load on the motor 1 does not increase.

On the other hand, when the slide door 4 is manually opened and closed, if the slide door 4 is suddenly opened and closed by its own weight on a slope or the like, the rotation speed of the outer ring 12 is considerably larger than the rotation speed when the motor 1 is operated. Since the sliding door 4 becomes large, the sliding door 4 has a predetermined speed, that is, the rotation speed of the outer ring 12 is a predetermined value set by the viscous resistance of the viscous fluid 20 and the spring constant of the centering spring 23 [point X in FIG. When the first cam member 35 and the outer ring 12 are rotated relative to the outer ring 12, the engaging portion 23b of the centering spring 23 bends. Rotation occurs.

On the other hand, as described above, when the first cam member 35 rotates relative to the outer ring 12 due to the rotation of the first cam member 35 with respect to the outer ring 12, the second cam member 35 fixed in the circumferential direction. V-shaped mountain-shaped cam surface 37 of cam member 38
Moves in the axial direction while sliding on the slope of the V-shaped valley-shaped cam surface 36 of the first cam member 35. The axial movement of the second cam member 38 causes the compression coil springs 44 and 45 to press the clutch ring 33 toward the brake shaft 15. As a result, the clutch ring 33 moves in the axial direction, the dogs 34 and 32 mesh with each other, and the brake shaft 15 rotates.

When the brake shaft 15 rotates, the braking force is generated by the viscous resistance (viscous shear resistance) of the viscous fluid 29 sealed between the brake mechanism 27 provided at the end thereof, for example, the stationary system member 28. Works, and the opening and closing speed of the slide door 4 can be reduced through the outer ring 12 that rotates integrally with the braking shaft 15 and the belt 6 wrapped around the outer ring 12.

The present invention is not limited to the two-way clutches 11 and 31 applied in the first and second embodiments described above, but can be applied to a two-way clutch having another structure. For example, in the electric switching device according to the third embodiment, a two-way clutch 51 described later is interposed between the electromagnetic clutch 3 and the pulley 5 of the output shaft as shown in FIG.

As shown in FIGS. 10 and 11, the two-way clutch 51 applied to the third embodiment has a main rotating member which extends along an axis from both sides of an outer ring 52 which is a sub-rotating member. The input shaft 53 and the output shaft 54
The cylindrical retainer 56 is press-fitted and fixed to the outer diameter of the input shaft 53 through the shaft. A plurality of pockets 57 are formed at equal intervals in a circumferential direction of the retainer 56 constituting the power connection / disconnection member, and a roller 58 and a leaf spring 59 for holding the roller 58 are inserted and arranged in each pocket 57. ing. When the input shaft 53 and the output shaft 54 are in a neutral state in the circumferential direction, the leaf spring 59
Is held at a neutral position in the pocket 57 by pressing the same from both sides.

A switch pin 60 extending in the radial direction is implanted at the outer diameter of the output shaft 54, and the tip of the switch pin 60 is fitted into a square hole 61 provided on the peripheral surface of the retainer 56. . A play in the rotation direction is formed between the circumferential side walls of the square hole 61 and the switch pin 60 to allow relative rotation between the retainer 56 and the output shaft 54. A plurality of flat cam surfaces 62 are formed on the outer diameter surface of the output shaft 54. When the input shaft 53 and the output shaft 54 rotate relative to each other in the forward and reverse directions, each of the cam surfaces 62 and the cylinder of the outer ring 52 are formed. The roller 58 is adapted to be engaged with the surface.

In the third embodiment, the outer ring 52 is provided with a braking mechanism 63 for applying a braking force when a reverse input is made from the slide door 4. In the braking mechanism 63, a stationary member 64 is disposed on the outer diameter surface of the outer ring 52 via a gap, as in the first and second embodiments described above, and between the outer ring 52 and the stationary member 64. A viscous fluid 65 such as silicone oil is sealed in the gap and sealed with a seal 66 or the like. The brake mechanism 63 has a structure other than the viscous fluid, for example, a friction plate that can apply a braking force by being in sliding contact with the outer ring 52, is disposed between the outer ring 52 and the stationary system member 64. Is also good.

In the third embodiment using the two-way clutch 51 having the above-described structure, when the slide door 4 is normally opened and closed electrically, as shown in FIG. The power is reduced by the worm & wheel mechanism 2. In the two-way clutch 51, the input shaft 5
3 rotates the wall surface of the square hole 61 of the cage 56 and the output shaft 5.
4 comes into contact with the switch pin 60 implanted in the output shaft 5, the rotational power of the input shaft 53 is transmitted via the switch pin 60 to the output shaft 5.
4 is transmitted. The rotational power is transmitted to the belt 6 via the two-way clutch 51, and the slide door 4 automatically opens and closes. However, at this time, in the two-way clutch 51,
Since the roller 58 does not clamp, the outer ring 52 does not rotate, so that the load on the motor 1 does not increase.

On the other hand, when the slide door 4 is manually opened and closed, and the slide door 4 is suddenly opened and closed by its own weight on a slope or the like, the rotational power is input to the output shaft 54 of the two-way clutch 51. Its output shaft 54
As a result, the switch pin 60 comes into contact with the retainer 56, and the input shaft 53 rotates through the switch pin 60.
At this time, since the roller 58 is engaged and clamped between the cam surface 62 of the output shaft 54 and the inner diameter surface of the outer ring 52, the outer ring 52 also rotates. The rotation of the outer ring 52 causes the outer ring 5
2, for example, a stationary system member 64
The braking force is applied by viscous resistance of the viscous fluid 65 sealed between the sliding door 4 and the opening / closing speed of the slide door 4 is reduced.

In the above embodiment, the case where the present invention is applied to an electric sliding door opening / closing device in an automobile (one box car) has been described. However, the present invention is not limited to this. It can also be applied to other electric switchgears.

[0051]

According to the present invention, by providing a braking mechanism for applying a braking force to the sub-rotating member of the two-way clutch at the time of reverse input from the opening / closing element, for example, electric opening / closing of a sliding door of an automobile or the like When the present invention is applied to a device, even if the slide door tries to open and close suddenly, the braking mechanism can apply a braking force to the slide door to decelerate the slide door. For example, it is possible to prevent sudden opening / closing due to its own weight, and it is possible to provide a highly safe electric switchgear. In addition, when the motor is driven, no braking force is exerted by the braking mechanism, so that the load on the motor is not increased.

[Brief description of the drawings]

FIG. 1 is a configuration diagram showing an example in which a two-way clutch is attached to one end of a belt according to a first embodiment of the present invention.

FIG. 2 is a sectional view showing a two-way clutch used in the first embodiment;

3A is a sectional view taken along line AA in FIG. 2; FIG. 3B is a sectional view taken along line BB in FIG. 2;

FIG. 4A is a cross-sectional view illustrating a state where the roller is not engaged with the outer ring in an enlarged view of a main part of FIG. 3B, and FIG. Sectional view showing engaged state

FIG. 5 (a) is a characteristic diagram showing the relationship between the rotational speed of the outer ring and the rotational resistance set in the present invention, and FIG. 5 (b) is a characteristic diagram showing the relationship between the rotational speed and the rotational resistance of a general outer ring.

FIG. 6 is a sectional view showing a two-way clutch used in a second embodiment of the present invention.

FIG. 7 is a sectional view taken along the line CC of FIG. 6;

FIG. 8 is a perspective view showing a clutch ring and a braking shaft used in the two-way clutch shown in FIG. 6;

FIG. 9 is a configuration diagram showing an example in which a two-way clutch is attached to an output shaft of a motor according to the third embodiment of the present invention.

FIG. 10 is a sectional view showing a two-way clutch used in the third embodiment.

11 is a sectional view taken along the line DD in FIG.

FIG. 12 is a configuration diagram showing a driving unit of an electric sliding door of an automobile.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 drive source (motor) 4 opening / closing element (slide door) 11 two-way clutch 12 main rotating member (outer ring) 15 auxiliary rotating member (brake shaft) 16 power connection / disconnection mechanism (roller) 17 power connection / disconnection mechanism (cage) 20 Viscous fluid 23 Elastic member (centering spring) 27 Braking mechanism 28 Stationary member 29 Viscous fluid

Claims (4)

[Claims] A main rotating member which rotates in conjunction with an input rotation from a driving source or a reverse input rotation from an opening / closing element, a sub-rotating member arranged coaxially with the main rotating member, and the main rotating member. And between the auxiliary rotating member and the input rotation from the drive source, to cut off the torque transmission to the auxiliary rotating member,
A two-way clutch having a power connection / disconnection mechanism for transmitting torque to a sub-rotating member with respect to reverse input rotation from the opening / closing element is interposed in a power transmission path from the driving source to the opening / closing element; A transmission mechanism for transmitting the input rotation from the main body to the opening / closing element through the main rotation member of the two-way clutch, wherein a braking mechanism for applying a braking force to the auxiliary rotation member of the two-way clutch at the time of reverse input from the opening / closing element is provided. An electric switchgear with a braking mechanism, characterized in that: 2. The two-way clutch includes an elastic member that connects a main rotating member and a power connecting / disconnecting mechanism in a rotational direction, and a viscous fluid interposed between the power connecting / disconnecting mechanism and a stationary member. Based on the correlation between the spring constant of the elastic member and the viscous resistance of the viscous fluid, when the main rotating member reaches a predetermined number of rotations, the auxiliary rotating member is rotated relative to the main rotating member, and the auxiliary rotating member is rotated. The electric switching device with a braking mechanism according to claim 1, wherein a braking force is applied to the rotating member by the braking mechanism. 3. The power connection / disconnection mechanism includes a retainer connected to a main rotating member and an elastic member, and rollers accommodated in pockets formed at equal intervals in a circumferential direction of the retainer,
The electric opening / closing device with a braking mechanism according to claim 2, wherein the roller has a structure capable of engaging with and disengaging from the main rotating member and the sub-rotating member. 4. The power connection / disconnection mechanism includes a first dog provided on the sub-rotation member side and a second dog provided on the main rotation member side arranged along an axial direction. Axially between a disengaged position in which the dog is axially separated from the first dog and an engaging position in which the second dog is axially close and engages the first dog in the circumferential direction. The electric switching device with a braking mechanism according to claim 2, wherein the switching device has a movable structure.