JP2002242959A - Direct acting two-way rotary clutch and its application - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a direct acting two-way rotary clutch and its application suitable for use in the opening/closing device of an electric sliding door for an automobile or a travel drive transmission device of a travel vehicle body or the like, having a simple structure without requiring an electromagnetic clutch with electric control, and capable of reducing the cost and improving energy efficiency. SOLUTION: The rotary clutch comprises a fitting bracket 21 rotatably supporting a drive shaft 25, a drive cam 37 connected to the drive shaft 25 and rotated in the rotating direction integrally with it, a driven cam 41 idly coupled with the drive shaft 25 and capable of being displaced in the axial direction when receiving the cam action of the drive cam 37, a rotary driven member 31 having a pressure receiving section 36 receiving the pressing force by the displacement of the driven cam 41 and rotatably supported on the drive shaft 25, and an elastic spring means 43 inserted between the back face end section of the driven cam 41 and the bracket 21 and applying the rotation restraining force to cause relative rotary displacement between both cams 37 and 41 and the separation exciting force from a pressure contact section to the driven cam 41.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive shaft coupled to a motor, and to transmit the forward and reverse rotational forces from the drive shaft to a driven portion, so that the motor stops and the drive side rotates. When the driven side rotates in the forward or reverse direction when there is no rotation, the linear motion bidirectional rotation is such that this rotational movement can freely rotate on the driven side without being affected by the load of the motor on the driving side. The present invention relates to a clutch and its application device.

[0002]

2. Description of the Related Art Conventionally, a clutch means for controlling transmission and non-transmission of drive when necessary is provided between a drive shaft connected to a motor and a rotation driven member receiving rotational force. It is common. For example, a transmission clutch used in an electric slide door opening / closing device for an automobile reduces the rotation of a motor by a speed reducer, and transmits this power to a winding drum via an electromagnetic clutch. The sliding door is opened when the winding drum rotates forward and closed when the winding drum rotates reversely.

[0003] In addition, when a traveling drive wheel of a traveling vehicle body or the like is used as a rotation driven member by a motor, a clutch means is provided between the traveling motor and the motor. Generally, free running of the drive wheels is allowed.

[0004]

In any of the above arrangements, an electromagnetic clutch or the like is required, so that there is a problem that the cost is high. Further, in a sliding door for an automobile, when the driven sliding door is manually opened and closed, there is a problem that the electromagnetic clutch must be released.

Further, during the automatic opening / closing operation of the electric slide door or the traveling driving of the traveling vehicle body, the electromagnetic clutch must be constantly energized, so that the energy consumption is large and the energy efficiency is poor. There is a problem.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has an object to be applied to a case where it is used for an opening / closing device of an electric sliding door for an automobile, and a driving drive transmission device for a traveling vehicle body. A direct-acting bidirectional rotary clutch that is suitable when used, does not require an electromagnetic clutch accompanied by electrical control, has a simple structure, can reduce cost, and can improve energy efficiency. And an application device thereof.

[0007]

Means adopted by the present invention to solve the problem will be described with reference to the reference numerals used in the embodiments. The invention according to claim 1 is connected to a motor 12. Mounting bracket 2 for rotatably supporting drive shaft 25
1, a driving cam body 37 coupled to the driving shaft 25 and integrally rotating in the rotation direction, and a cam function of the driving cam body 37 which is loosely fitted to the driving shaft 25 and receives the cam action of the driving cam body 37. A driven cam member 41 that can be displaced and moved in the direction, a pressure receiving portion 36 that receives a pressure contact force due to the displacement of the driven cam member 41, and a rotatable driven member 31 rotatably supported on the drive shaft 25; A rotation restraining force which is interposed between the rear end portion of the driven cam body 41 and the bracket 21 to cause relative rotation displacement between the two cam bodies 37 and 41, and a biasing force for separating from the press contact portion. Is applied to the driven cam body 41, and the pressure of the rotation driven member 31 is received by the cam action of the two cam bodies 37 and 41 generated by the rotation of the drive shaft 25 in the normal rotation direction and the reverse rotation direction. Between the portion 36 and the driving cam body 37 Newsletter 突張 Ri forces, as well as configured to be a two-way rotary transmission, the time of stopping the motor 12,
It is characterized in that the rotation follower 31 is allowed to rotate in the forward and reverse directions.

According to a second aspect of the present invention, there is provided a mounting bracket for rotatably supporting a drive shaft connected to a motor.
And a drive cam body 37 coupled to the drive shaft 25 so as to rotate integrally in the rotation direction, and the drive cam body loosely fitted to the fixed shaft 22 integrated with the mounting bracket 21. 37 has a driven cam body 41 which can be displaced and moved in the axial direction by a cam action, and a pressure receiving portion 36 which receives a pressing contact force due to the displacement of the driven cam body 41, and is rotatably supported on the drive shaft 25. The rotation driven member 31 and a rotation restraining force which is interposed between the rear end of the driven cam body 41 and the bracket 21 to cause relative rotation displacement between the two cam bodies 37 and 41, and An elastic spring means 43 for applying a biasing force to the driven cam body 41 from the press contact portion, and the cam action of the two cam bodies 37 and 41 generated by the rotation of the drive shaft 25 in the normal rotation direction and the reverse rotation direction. The rotation driven member 3 Newsletter 突張 Ri forces between the pressure-receiving portion 36 and the drive cam member 37, as well as configured to be a two-way rotary transmission, when stopping the motor 12, rotating the driven member 3
The present invention is characterized in that it is configured to allow a rotational movement in the forward and reverse rotation directions on one side.

A third aspect of the present invention is characterized in that the cam surfaces of the driving cam body 37 and the driven cam body 41 are formed in a plurality of trapezoidal cam shapes arranged on the same circumference of the opposite end faces. Having.

The invention of claim 4 is characterized in that the cam surfaces of the driving cam body 37 and the driven cam body 41 are formed in an elliptical ring shape by the slopes of the opposite end faces.

The invention according to claim 5 is characterized in that the pressure contact surface of the driven cam body and the pressure receiving portion of the rotary driven member opposed thereto are formed by slopes.

According to a sixth aspect of the present invention, there is provided a mounting bracket for rotatably supporting a drive shaft connected to a motor.
And a first tapered cone 52 for forward rotation consisting of a frusto-conical body having a press-contact surface for transmitting a press-contact force due to axial displacement to an outer peripheral surface thereof, which is loosely fitted to the drive shaft 51, and disposed axially symmetrically therewith. Second tapered cone 53 for reverse rotation transmission
And cam long holes 56a, 56b, 57a, 57b formed in the first and second taper cones 52, 53 at a predetermined inclination angle with respect to their axes, respectively, and in each of the cam long holes 56a, Each of the drive pins 56 b, 57 a, and 57 b attached to the drive shaft 51 so as to rotate integrally with the drive shaft 51, and the pressure receiving portions 64 and 65 that receive the pressing force due to the axial displacement of the tapered cones are provided on the inner periphery. Having a drive shaft 5
A rotation driven member 61 rotatably supported with respect to 1;
The first and second tapered cones 53, 54 are interposed between the outer end surfaces of the first and second tapered cones 53 and the inner end of the rotation driven member 61, and the relative rotational displacement between the drive shaft 51 and the respective tapered cones 52, 53. And the pressure receiving portion 64,
An elastic spring means 43 for applying a biasing force to the taper cones 52, 53 from the position 65. The drive pins 54, 55 generated by the drive shaft 51 rotating in the forward and reverse directions. And the cam slots 56a, 56b, 57
a, 57b, each taper cone 5
2 and 53, it is possible to obtain a pressure contact force due to axial displacement of either one of the motors, thereby enabling bidirectional rotation transmission.
Is characterized in that it is configured to allow the rotation of the rotation driven member 61 in the forward and reverse directions when stopped.

According to a seventh aspect of the present invention, the first and second tapered cones 52a and 53a are formed integrally, and a single cam elongated hole 59a extending beyond the axis and a single cam elongated hole attached to the drive shaft 51 are provided. It is characterized in that a single drive pin 54a is used to generate an axial displacement that enables a single tapered cone 71 to perform bidirectional rotation transmission.

According to an eighth aspect of the present invention, the rotation driven member 61
Are rotatably supported by the mounting bracket 21, and elastic spring means 43 for applying a biasing force to the tapered cones 52, 53 are provided on the outer end surfaces of the tapered cones 52, 53 and the mounting bracket 21. It is characterized by being interposed between them.

According to a ninth aspect of the present invention, the sliding door 2 provided on the side of the automobile, the winding drums 31 and 74 driven by the electric motor 12 to rotate forward and backward, and the drum 31 and the sliding door 2 are provided. Indexing means 6a, 6b such as a belt or a wire, the ends of which are bound, respectively, and the sliding door 2 can be opened and closed by rewinding and rewinding the indexing means 6a, 6b by controlling the forward / reverse rotation of the electric motor 12. The rotation driven member 3 in the direct acting bidirectional rotary clutch 20 according to claim 1, wherein
1, 61, 72 are the winding drum body 31 and
One end of each of the indexing means 6a and 6b is connected to the rotation driven member 3
1, 74, and the rotational force in the forward and reverse directions with respect to the rotation driven members 31, 74 by the opening / closing operation from the slide door 2 side is not transmitted to the drive shafts 25, 51 of the rotary clutch. The sliding door 2 is characterized in that it can be freely opened and closed manually.

A tenth aspect of the present invention is characterized in that the rotation driven member 61 is the winding drum body 31 of a slide door for a vehicle.

According to an eleventh aspect of the present invention, there is provided an electric traveling vehicle body in which a traveling drive shaft of a vehicle is driven forward and reverse by an electric motor 12. The rotation driven member 61 of the clutch 50 'is used as the traveling drive shaft, and when the electric motor 12 is stopped, the rotational force of the rotation driven member 61 in both the forward and reverse directions is transmitted to the drive shaft of the rotation clutch 50'. The present invention is characterized in that the traveling drive wheels are configured to be able to travel freely without any trouble.

According to a twelfth aspect of the present invention, a rotation driven member 61 is provided.
Is a traveling drive shaft of the electric traveling vehicle body.

[0019]

BEST MODE FOR CARRYING OUT THE INVENTION In the following, claims 1, 3 and 4 of the present invention will be described.
A first embodiment of the direct acting bidirectional rotary clutch 20 according to the present invention will be described with reference to FIGS. A mounting bracket 21 for rotatably supporting a drive shaft 25 coupled to a motor (not shown) has a fixed shaft 22 fixed to one support plate,
A ball bearing 23 is attached to the other support plate. A ball bearing 24 is attached to an inner end surface of the fixed shaft 22.
A drive shaft 25 is rotatably supported between 3 and 24.

The rotation driven member 31 is composed of a drum body 32 having a flange on the end face and a flange 33, and a ball bearing 34 attached to the outer periphery of the fixed shaft 22.
And a ball bearing 35 fitted to the drive shaft 25 and rotatably supported by the mounting bracket 21. The rotation driven member 31 has a drive shaft 2 on its inner peripheral portion.
The surface orthogonal to 5 is a pressure receiving portion 36.

The drive shaft 25 has a drive cam body 37 located inside the rotation driven member 31 and serving as a clutch transmission operation part.
Are desirably fitted. The driving cam body 37 has an oval-shaped hole, and has a flat surface 37 formed on the driving shaft 25.
b, it is non-rotatably fitted to the drive shaft 25. A thrust bearing 38 is interposed between the inner end surface of the flange 33 and the thrust bearing 38. In addition, the end face on the opposite side has a predetermined intersection angle with respect to the drive shaft 25 (the following cam body 4 described later).
The cam surface 37a is formed at an angle (an angle at which 1 causes a necessary axial displacement by a cam action).

The driven cam body 41 is located between the driving cam body 37 and the pressure receiving portion 36 and is loosely fitted to the drive shaft 25 so as to be rotatable and axially movable. The driven cam body 41 has an end face on the pressure receiving portion 36 side orthogonal to the drive shaft 25, and a cam surface 41 a as an inclined surface portion corresponding to the cam surface 37 a is formed on the drive cam body 37 side. In addition, the driven cam body 4
A slide plate 42 may be interposed between the cam surface 37a and the cam surface 37a in order to facilitate the return to the original position.

The contact surface between the driven cam body 41 and the pressure receiving portion 36 is preferably subjected to a measure for increasing frictional resistance, for example, knurling or engaging groove processing, or a friction plate is bonded.

As shown in FIG. 1, when the driven cam surface 37a and the driven cam surface 41a are in close contact with each other, as shown in FIG. α is formed. Then, when the drive shaft 25 rotates and the drive side cam surface 37a and the driven side cam surface 41a are relatively displaced, the driven cam body 41 is moved leftward in the figure according to the predetermined rotation angle and inclination angle. Pressure receiving part 3
6 is pressed.

Further, between the fixed shaft 22 and the driven cam body 41, there is provided an urging force for returning the driven cam body 41 to the original position when the drive shaft 25 stops, and the two cam bodies 37 and 41. And a return spring 43 and a thrust plate 44 as elastic means for applying a rotation restraining force for generating a predetermined relative rotational displacement.

FIG. 3 shows a second embodiment.
This embodiment is different from the first embodiment in that a driving cam body 45 is used instead of the driving cam body 37, and the driven cam body 4 is used instead of the driven cam body 41.
No. 6 is used, and other configurations are the same. However, in the former case, machining of the cam body is easy, and in the latter case, a plurality of cam action points are used to achieve good operability and balance. There are advantages that can be.

The cam surface portions of the driven cam body 46 and the driving body cam body 45 as the driving side in the second embodiment are as follows.
Each of them is constituted by a plurality of trapezoidal cam portions 45a and 46a which are alternately meshed and formed on the same circumference of the opposing contact surfaces, and a predetermined trapezoidal slope between the two cam portions 45a and 46a. A cam action for generating a predetermined axial displacement accompanying the relative angular displacement is obtained.

In these first and second embodiments,
In the initial state in which the drive shaft 25 is stopped, a gap α is maintained between the pressure receiving portion 36 of the rotation driven member 31 and the driven cam bodies 41 and 46. Therefore, even if the rotation driven member 31 rotates with a rotational force equal to or more than the friction load on the thrust bearing 38 subjected to the force of the spring 43 as the elastic means,
Since the load of the motor and the reducer (not shown) coupled to the drive shaft 25 is larger than the friction load of the thrust bearing 38, the drive shaft 25 maintains the stopped state without transmitting the rotational force, and the driven member 31 idles. I do. At this time, the frictional load of the thrust bearing 38 can be set so as to restrict the free rotation of the rotary transmission member 31 to some extent, if necessary, or can be set freely.

Next, when the drive shaft 25 rotates in the forward (right) or reverse (left) direction, the driven cam body 41 (46) is pressed by the return spring 43. The cam surface 37a (45a) and the driven cam surface 41a (46a) are relatively rotated and displaced, and the cam action corresponding to the relative rotation angle displacement of the cam surface 37a (45a) and the set inclination angle is performed. The driven cam body 41 (46) is moved leftward in the drawing by the amount of axial displacement generated below and pressed against the pressure receiving portion 36.

As long as the drive shaft 25 is continuously driven to rotate in accordance with the load applied to the rotation driven member 31, the cam 37 between the pressure receiving portion 36 of the driven member 31 and the thrust bearing 38 is used. Due to the projecting action of 41 or 45, 46, the transmission of the rotational driving force of the drive shaft 25 is achieved together with the integral rotation of the two cam bodies 37, 41 or 45, 46.

It should be noted that the driving cam body 3 in the above embodiment is
As shown in FIG. 2, the connection procedure between the drive shafts 7 and 45 and the drive shaft 25 does not depend on the two-face width 37 b between the drive shaft 25 and the drive shaft 25, but they are integrally formed or fixedly connected by another connecting means. (Not shown), the slide bearing 38 may be omitted to allow free rotation of the rotation driven member 31. At this time, the pressing force of the driven cam bodies 41 and 46 serves as a projecting action between the pressure receiving portion 36 of the rotary driven member 31 and the drive cam body fixedly connected, and does not act on the thrust bearing 38. However, in any case, the driven cam bodies 41 and 46 with respect to the pressure receiving portion 36 of the present invention.
The rotational force of the drive shaft 25 is transmitted to the driven member 31 in accordance with the frictional force caused by the pressing action of the driven member 31. At this time, the return spring 43 and the thrust plate 44 supported by the fixed shaft 22
Since the thrust plate 44 receives a rotational force greater than the spring load and allows the sliding rotation, the return spring 43 is not twisted.

When the drive shaft 25 stops, the driven cam 41
(46) is returned to the original position by the return spring 43, and a gap α is formed again between the driven cam body 41 (46) and the pressure receiving portion 36.

FIG. 9 shows a direct acting bidirectional rotary clutch 70 according to a third embodiment of the present invention. Only differences from the direct acting bidirectional rotary clutch 20 will be described. I do.

A sleeve-like fitting shaft 22a is press-fitted into the fixed shaft 22 at a position outside the ball bearing 24 supporting the drive shaft 25, and a driven cam body 46 'is fitted to the fitting shaft 22a. Then, it is configured such that relative rotation displacement between the two cam bodies is easily generated in opposition to the driving body cam body 45.

A plurality of trapezoidal cam portions 46a are formed on the side surface of the driven cam body 46 '.
a is adapted to obtain a cam action for generating a predetermined axial displacement accompanying a predetermined relative angular displacement between the trapezoidal slopes of the cam portion 45a of the driving body cam body 45.

An urging force for returning the driven cam body 41 to the original position when the drive shaft 25 is stopped is provided between the fixed shaft 22 and the driven cam body 41 on the outer peripheral portion of the fitting shaft 22a. A return spring 43 and a thrust plate 44 as elastic means for applying a rotation restraining force for causing the two cam bodies 37 and 41 to generate a predetermined relative rotational displacement are interposed.

FIG. 10 shows a modification of the third embodiment, in which the fitting shaft 22a is formed integrally with the fixed shaft 22 by machining to reduce the number of parts.

The direct-acting bidirectional rotary clutch 70 also provides a sufficient relative rotation restraining force of the driven cam body 46 'in addition to the operation and effects of the direct-acting bidirectional rotary clutch 20, and the The movement of the cam portion 45a of the fork 45 and the cam portion 46a of the driven cam body 46 'can be carried out smoothly, and there is an effect that the driven cam body 46' can be reliably and easily moved in the axial direction.

FIG. 11 shows a direct-acting bidirectional rotary clutch 71 according to a fourth embodiment of the present invention. The difference from the direct-acting bidirectional rotary clutch 70 is as follows. And the shape of the press contact surface, and only the differences will be described.

The driven cam body 72 of the rotary clutch 71 has an outer peripheral surface formed of a tapered cone-shaped inclined surface, which is used as a press contact portion 73. On the side surface, a plurality of trapezoidal cam portions 46a are formed, and the cam portions 46a are provided in a predetermined axial direction with a predetermined relative angular displacement between the trapezoidal slopes of the cam portions 45a of the driving body cam body 45. A cam action that causes displacement is obtained.

The rotation driven member 74 is formed by connecting a drum body 75 having a flange on the end surface and a flange 33, and includes a ball bearing 34 attached to the outer periphery of the fixed shaft 22, and a drive shaft 25. Ball bearing 35 fitted to
, And rotatably supported by the mounting bracket 21. The rotation driven member 74 has an inclined surface formed on the inner peripheral portion of the drum body 75, and the inclined surface is formed on the driven cam body 72.
The pressure receiving portion 76 is opposed to the pressure contact portion 73 with a gap α when stopped.

In the rotary clutch 71, since the pressure contact portion 73 and the pressure receiving portion 76 are constituted by inclined surfaces,
When the driven cam body 72 moves in the axial direction and the pressure contact portion 73 and the pressure receiving portion 76 are pressed against each other, the contact area is larger than that of the rotary clutch 70. In addition, since the connection between the two is strengthened by the wedge action, in addition to the operation and effect of the rotary clutch 70, an effect that the transmission force is further increased is exhibited.

Next, the direct acting bidirectional rotary clutch 20,
An embodiment according to claim 9 in which 70 and 71 are used for a sliding door opening / closing device for a vehicle will be described. First, in FIG. 4, a slide door 2 is attached to a side surface of a vehicle. A rail 4 is attached to the vehicle body 3, and return pulleys 5 are attached to both ends of the rail 4. Between the return pulleys 5, pulling means (in the case of the present embodiment, the wires 6 a and 6 b are shown) such as belts or wires for opening and closing the door are arranged along the rail 4. One end of wires 6a and 6b as pulling means is connected to the connecting member 7 of the sliding door 2, and the sliding door 2 is provided with a connecting member 7 having a guide roller for the rail 4 and a connecting member 7b having a guide roller for the front rail 4b. And is opened and closed along the rails 4 and 4b.

The other ends of the wires 6a, 6b are fixed to the rotation driven members 31, 74 of the direct acting bidirectional rotary clutches 20, 70, 71 according to the present invention used as a winding drum body. The motor 12 rotates forward and reverse through the drive shaft 25 of the direct acting bidirectional rotary clutches 20, 70, 71. For example, when the motor 12 rotates forward in one direction (clockwise rotation), the driven member 31 winds up the wire 6a for opening the door to open the slide door 2, and the motor 12 rotates reversely in the other direction (left rotation). When the door is closed)
The slide door 2 is closed by winding the b.

Next, the direct acting bidirectional rotary clutch 20,
FIGS. 1 and 3 and FIGS.
This will be described in detail with reference to FIG. 1) At the time of automatic opening operation of the slide door 2 When the slide door 2 is automatically opened, the motor 12 is rotated clockwise. When the motor 12 and the drive shaft 25 are rotated clockwise, the drive cam bodies 37 and 45 are integrally rotated clockwise because they are fitted to the drive shaft 25 across the width. An inclined cam surface 37a provided on each end surface of the driving cam body 37 or 45, or a driven cam body 41 or 4 having a driven cam surface 41a or a trapezoidal cam portion 46a on a circumferential end surface so as to face the trapezoidal cam portion 45a.
6, 46 'and 72 are relatively displaceable in the rotation direction and the axial direction with respect to the drive shaft 25, and receive the load of the return spring 43, so that the cam action by the rotation of the drive cam bodies 37 and 45 is performed. As a result, the driven member 31 moves along the axis against the return spring 43 and is pressed against the pressure receiving portions 36 and 76 inside the rotation driven members 31 and 74 (drum) to keep the drive shaft 25 rotating. , 74 (drum), the door can be automatically opened via indexing means (belt or wire). At this time, the return spring 43, which is fixed and supported, does not hinder sliding on the thrust plate 44, and the resistance of the thrust bearing 38 caused by the spring load of the return spring 43 has an effect of preventing self-running of the door described later. You can also set and use it to get it.

When the rotation input of the drive shaft 25 is stopped, the driven cam body 41 is pushed back by the return spring 43, returns to the original position, and a slight gap α is formed between the driven cam body 41 and the pressure receiving portion 36.

2) At the time of automatic closing operation of the slide door 2 When the slide door 2 is automatically closed, the motor 12 is rotated counterclockwise. When the motor 12 and the drive shaft 25 are rotated counterclockwise, the drive cam bodies 37 and 45 are integrally rotated counterclockwise because they are fitted to the drive shaft 25 across the two faces. The inclined cam surface 37 provided on each end surface of the drive cam body 37 or 45, or the driven cam surface 41a facing the trapezoidal cam portion 45a, or the driven cam body 41 or 46 having the trapezoidal cam portion 46a on the circumferential end surface is:
Since it is made relatively displaceable in the rotation direction and the axial direction with respect to the drive shaft 25 and receives the load of the return spring 43,
By the cam action by the rotation of the driving cam bodies 37 and 45, the driving cam bodies 37 and 45 move along the axis against the return spring 43, and are pressed against the pressure receiving portion 36 inside the rotation driven members 31, 74 (drum), and the driving shaft 25 is moved. By continuing to rotate, the driven member 3
The door can be automatically closed via indexing means (belt or wire) attached to 1, 74 (drum). At this time, the return spring 43, which is fixed and supported, does not hinder the sliding of the thrust plate 44, and also has the effect of preventing the door from running by the thrust bearing 38 subjected to the spring load. When the rotation input of the drive shaft 25 is stopped, the driven cam body 41 is pushed back by the return spring 43,
It returns to the original position, and a slight gap α is again generated between the pressure receiving portion 36 and the pressure receiving portion 36.

3) When the slide door 2 is manually opened, the motor 12 is opened when the slide door 2 is manually opened.
And the drive shaft 25 is stopped. When the slide door 2 is manually opened, the rotation driven members 31, 74 (drum) are driven to rotate rightward as the door is opened via the wires 6a, 6b. Then, the driving cam bodies 37 and 45 try to rotate in the same direction due to friction from the thrust bearing 38. However, the driving cam bodies 37 and 45 are connected to the driving shaft 25 on which the load of the motor and the reduction gear is applied. The driving cam bodies 37 and 45 do not rotate due to the friction because of the surface width fitting state. That is, only the driven members 31, 74 (drum) can freely rotate rightward by slipping due to the thrust bearing 38, and the manual door opening operation can be performed without any trouble. In other words, the door can be manually opened regardless of the motor load or the clutch load. At this time, the driven cams 41, 46, 72 are pushed back to the original position by the return spring 43, and the driven members 31,
Since the clearance α is secured between the pressure receiving portion 36 and the pressure receiving portion 36 (drum), it is independent of the rotation of the driven members 31 and 74 (drum). Note that the self-running phenomenon of the door when the above-described manual door opening operation is performed while the vehicle is stopped on a slope or the like can be prevented by setting the friction of the thrust bearing 38.

4) When the slide door 2 is manually closed, the motor 12 is closed when the slide door 2 is manually closed.
And the drive shaft 25 is stopped. When the sliding door 2 is manually closed, the rotation driven members 31, 74 (drum) are driven to rotate leftward as the door is closed via the wires 6a, 6b. Then, by the same action as when opening,
Since the drive shaft 25 is separated from the driven members 31 and 74 (drum) and is not in contact with the driven shaft 25, manual closing operation can be easily performed.

As described above, when the direct-acting bidirectional rotary clutches 20, 70 and 71 of the present invention are used for a sliding door opening / closing device for an automobile, an electromagnetic clutch is not required, so that the structure is extremely simple. Can be Also,
The structure of the direct acting bidirectional rotary clutch 20 itself is simple, the number of parts is small, the cost can be reduced, and the energy efficiency can be improved.

FIGS. 5 and 6 show fifth and sixth direct acting bidirectional rotary clutches 50 according to the sixth and seventh aspects. The difference from the direct acting bidirectional rotary clutch 20 will be mainly described. However, the mounting bracket is eliminated, and the rotation driven member 61 is directly connected to the drive shaft 51 by the ball bearing 34 ′,
35. In addition, as shown in FIGS. 5 and 6, in the direct acting bidirectional rotary clutch 50, a first taper cone 52 for right rotation and a second taper for left rotation are used as driven cams as driven cams. The cone 53 is loosely fitted. Each of the first taper cone 52 and the second taper cone 53 is formed of a truncated cone, and is arranged axially symmetrically so that the large diameter portions are in contact with each other.

The drive shaft 51 has two drive pins 54, 5
5 are planted. Also, the first taper cone 52
Slots 56a and 56b into which the drive pin 54 is inserted are formed in the second taper cone 53.
Are formed therein. These cam slots 56a, 56b, 57a, 57b
In a state of being inclined at an angle β (0 <β <90 degrees) with respect to the axis of the drive shaft 51, and on the near side 56 a, 5
One end is common to the sides 56b and 57b facing the side 7a, and are symmetrically distributed (56a, 56b and 57a, 57b, respectively).
b) The holes are arranged so as to be positioned. Then, the position of the pin 54 in the initial position coincides with the lower end of the long cam hole 56a on the near side of the drawing in the first taper cone 52 (the upper end in the long cam hole 56b on the opposite side),
In the second taper cone 53, the position of the pin 55 is set at the upper end of the front cam long hole 57a (the opposite cam long hole 57a).
b at the bottom). The cam mechanism 58 for obtaining a cam function for the bidirectional rotation clutch function includes the drive pins 54 and 55 and the cam slots 56a, 56b,
57a and 57b.

The first taper cone 52 and the second taper cone 53 have a return spring 43 and a thrust plate 44 interposed at their end surfaces, respectively, and are biased toward the center.

The rotation driven member 61 connects a first drum 62 and a second drum 63 at the center, and has an inner peripheral portion corresponding to the first taper cone 52 and the second taper cone 53. Tapered pressure receiving portions 64 and 65 are formed. Pressure receiving portion 64 and first taper cone 52
Is formed between the pressure receiving portion 65 and the pressure receiving portion 65.
A gap α is also formed between the first tapered cone 53 and the second tapered cone 53.

FIG. 7 shows a sixth embodiment.
A difference from the direct acting bidirectional rotary clutch 50 according to the embodiment will be described. Followed cam body 7 in the sixth embodiment
Reference numeral 1 denotes a first tapered cone portion 52a and a second tapered cone portion 53a which are formed by integrating the first and second tapered cones 52 and 53, respectively. 59b is provided, and the long hole 59a on the near side of the axis in the drawing and the long hole 59b on the opposite side are perforated and arranged so as to have an intersecting relationship at the center thereof, thereby reducing the number of parts. A single drive pin 54a implanted in the drive shaft 25 is inserted into the long cam holes 59a, 59b. In an initial state, the drive pin 54a is located at the center of both long cam holes 59a, 59b. The drive pin 54a and the cam slot 5 are rotated in accordance with the right or left rotation of the drive shaft 25.
A cam action occurs between the driven cam body 9a and the driven cam body 59b to move the driven cam body 71 along the axis. The fourth embodiment also has the same effects as the third embodiment.

The details of the operation when the direct-acting bidirectional rotary clutch 50 shown in FIGS. 5 and 6 is used in, for example, a sliding door opening / closing device for an automobile will be described. a) At the time of automatic opening operation of the slide door 2 When the slide door 2 is automatically opened, the motor 12 is rotated clockwise. When the motor 12 and the drive shaft 51 are rotated clockwise, the second taper cone 53 for left rotation is not axially driven because the drive pin 55 for left rotation does not produce the inclined cam action of the long cam holes 57a and 57b. It rotates at that position without any displacement, that is, while maintaining the gap α with the rotation driven member 61 (drum).

On the other hand, the first taper cone 5 for clockwise rotation
2, the right rotation drive pin 54 causes the inclined cam action of the long cam hole 56 to overcome the resistance provided by the return spring 43 and is relatively displaced in the axial direction.
1 (drum) is pressed against the pressure receiving portion 64 of the first (drum) and frictionally transmits the right rotation power of the drive shaft 51 via the right rotation drive pin 54. The drive shaft 51 and the driven member 61 (drum) are driven by a motor driving force. As long as the rotation is continued. When the rotation of the drive shaft 51 is stopped, the first taper cone 52 for right rotation is moved relative to the drive shaft 51 along the cam long holes 56a and 56b by the action of the return spring 43 and returns to the original position. .

B) At the time of automatic closing operation of the sliding door 2 When the sliding door 2 is automatically closed, the motor 12 is rotated counterclockwise. When the motor 12 and the drive shaft 51 are rotated counterclockwise, the first taper cone 52 for right rotation causes the right rotation drive pin 54 not to cause the inclined cam action of the long cam hole 56, so that the axial displacement is reduced. No rotation occurs, that is, at the position while maintaining the gap α with the rotation driven member 61 (drum).

On the other hand, the second taper cone 5 for left rotation
3 is a case where the driving pin 55 for left rotation is the cam long hole 57a, 57
b, which causes the cam to be inclined and overcomes the resistance provided by the return spring 43 to be relatively displaced in the axial direction, and is brought into pressure contact with the pressure receiving portion 65 of the rotation driven member 61 (drum) to turn the left rotation guide pin 55. The rotational power of the left rotation of the drive shaft 51 that has been interposed therebetween is frictionally conducted, and the drive shaft 51 and the driven member 61 (drum) integrally rotate left as long as the motor driving force is continuously applied. When the rotation of the drive shaft 51 is stopped, the second taper cone 53 for left rotation is moved relative to the drive shaft 51 along the cam long holes 57a and 57b by the action of the return spring 43 and returns to the original position. .

C) When the slide door 2 is manually opened: When the slide door 2 is manually opened, the motor 12
And the drive shaft 51 is stopped.

When the rotation driven member 61 (drum) is rotated clockwise as the door is opened, the first taper cone 52 for clockwise rotation receives a clockwise rotation force by the load of the return spring 43, but the cam slot 56a. , 56b in driving pin 5
4 cannot be generated (transmitted) to rotate the drive shaft 51, and stays at the same place. That is, the return spring 43
Is smaller than the motor load of the drive shaft 51, the drive shaft 51 cannot be rotated via the drive pin 54. On the other hand, the second taper cone 5 for left rotation
Similarly, when the right rotation is performed by the load of the return spring 43, the driving pin 55 does not move due to the motor load. Therefore, the second taper cone 53 for left rotation compresses the return spring 43 by itself and rotates the rotation driven member. 61 (drum), but this contact force does not become larger than the return spring 43, so that the drive pin 5 in a fixed state
5 cannot be rotated. That is, the rotation driven member 6
The rotation force of 1 (drum) can slide freely on the thrust plate 44 without rotating the drive shaft 51, and can freely rotate, so that the manual opening operation is not hindered, in other words, it is related to the motor load and the like. It can be operated without opening door.

D) When the slide door 2 is manually closed: When the slide door 2 is manually closed, the motor 12
And the drive shaft 51 is stopped. When the slide door 2 is manually closed, the rotation driven member 61 (drum) is driven to turn left as the door is closed. Then, by the same operation as the opening operation, the drive shaft 51 is rotated by the rotation driven member 61.
Since it is separated from the (drum) and is not in contact with the drum, the manual closing operation can be easily performed.

Here, also in the case of the direct acting bidirectional rotary clutch of the fourth embodiment constituted by the integral driven cam body 71 shown in FIG. 7, the cam action and the door opening / closing operation in the third embodiment are performed. Since there is not much difference from the above, the operation description is omitted.

In the first to fourth embodiments, when the load of the rotation driven members 31 and 61 (drum) is large, the rotation driven members 31 and 61 (drums) are used as support members for the return spring 43 and the thrust plate 44 (can be regarded as fixed members). Member 31,
61 can be used, the friction of the holding mechanism for obtaining the rotation restraining force by the return spring 43 and the thrust plate 44 is reduced to the driving cam bodies 37 and 45, the pins 54 and 55, the driven cam bodies 41 and 46, and the cone 52. , 53, and 71 to generate relative rotational displacement to move the driven cam bodies 41 and 46 and the cones 52, 53, and 71 in the axial direction, so that there is no need to separately provide a fixing member.

However, when the rotation driven member is light, when the load is smaller than the friction of the holding mechanism for obtaining the above-mentioned rotation restraining force, or when it is desired to freely rotate the rotation driven member, for example, like a running wheel, the cam may be used. A holding mechanism for the mechanism, that is, a fixed support member for generating friction (for generating a rotation restraining force or for generating a relative rotational displacement) is required.

In the case of the sliding door 2, since the friction of the holding mechanism can be relatively large in the former case,
Utilizing this, it is convenient as a door holding force on a slope. This friction is useful at the start of operation to prevent the slide door 2 from running idle and to prevent delay, and is necessary to prevent idle play.

On the other hand, when it is desired that the rotation driven members 31 and 61 have a free rotation support structure by minimizing the rotation restraining force such as friction, a direct acting bidirectional rotary clutch 5 is provided.
An example of 0 'will be described below with reference to FIG.

In the case of FIG. 8, it is required that the load applied to the rotation driven member 61 is light or that the rotation can be rotated without resistance. For example, the present invention is suitable for a device in which a traveling drive wheel of a traveling vehicle body (not shown) is driven forward and reverse by an electric motor. That is, the difference from the embodiment of FIG. 5 is that the drive shaft 51 and the rotation driven member 61 connected to a motor (not shown) are mounted on the fixed shaft 22 with the ball bearings 24 and 34 by the mounting bracket 21 ′. Through and
The boss portion of the mounting bracket 21 'is rotatably supported via ball bearings 23 and 35', and the return spring 43 and the thrust plate 44 are fixed not on the rotation driven member 61 but on the mounting bracket 21 'side. The present invention is characterized in that the support portion is supported by contact.

That is, the rotation driven member 61 is in a supporting state in which the rotation can be freely rotated by the ball bearings 34 and 35 'without being influenced by the friction caused by the return spring 43 and the thrust plate 44, so that the motor is stopped. Thus, when the drive shaft 51 is not driven to rotate, it can freely rotate without resistance.

Therefore, the direct acting bidirectional rotary clutch 5
For example, when 0 'is used as a traveling drive wheel device in an electric traveling vehicle body, the rotation driven member 61 may be used as it is as a traveling drive wheel for traveling on a rail or on a road, and the rotation driven member 61 (travel driving wheel) may be used. Is driven by a motor (not shown), the driving pins 54 and 55 and the cam slots 56 in the first and second tapered cones 52 and 53 are used.
By the cam action with a, 56b, 57a, 57b, the outer periphery of each of the tapered cones 52, 53 is pressed against the pressure receiving portions 64, 65 on the inner periphery of the rotation driven member 61 (running drive wheel), and the rotational driving force is transmitted. Traveling driving can be performed in any of the opposite directions.

At the time of this traveling drive, the return shaft 43, one end of which is supported by the fixed shaft 22 and the boss of the mounting bracket 21 ′, receives a rotational force from each of the tapered cones 52, 53 that keep rotating with the drive shaft 51. That is, the thrust plate 44 with respect to the return spring 43 can slide and rotate under a rotational driving force equal to or greater than a predetermined frictional load, so that the return spring 43 can rotate without any trouble without being swung.

When the driving of the motor is stopped, the tapered cones 52 and 53 are returned to the original positions by the return spring 43, and the rotation driven member 61 (drive wheels) is driven.
Gap between the pressure receiving portions 64 and 65 is secured,
As described above, the free running rotation state of the rotation driven member 61 (running drive wheel) by the bearings of the ball bearings 34, 35 'can be maintained.

As described above, it is apparent that the embodiment shown in FIG. 8 is suitable for a device for driving the traveling drive wheels (rotary driven members 61) in the forward and reverse directions by the motor.

In the case of the embodiment shown in FIGS. 1 and 3, as described above, the connection procedure of each drive cam body 37, 45 to the drive shaft 25 is changed from the two-plane width connection. Whether the drive cam bodies 37 and 45 are formed integrally with the drive shaft 25,
By changing the structure of the return spring 43 to a structure (not shown) in which the load of the return spring 43 does not act on the thrust bearing 38 in a state where the thrust bearing 38 is fixed by welding or a set screw, the rotation driven member 31 (the driving wheel) is driven by the fixed shaft 22 and the driving shaft. The bearing can be changed to a freely rotatable supporting state with respect to the shaft 25 by ball bearings 34 and 35. In this case, too, the linear drive type bidirectional rotary clutch 20 is used as a traveling drive device capable of free rotation.
Can be applied.

[0075]

According to the present invention, there is provided a mounting bracket for rotatably supporting a drive shaft connected to a motor, and a drive cam body coupled to the drive shaft and integrally rotating in a rotational direction. A driven cam body that is loosely fitted to the drive shaft and receives the cam action of the drive cam body and is displaceable in the axial direction; and a pressure receiving portion that receives a pressing force due to the displacement of the driven cam body. A rotation driven member rotatably supported with respect to a rotation restraining force of a degree interposed between the rear end of the driven cam body and the bracket portion to cause relative rotation displacement between the two cam bodies. An elastic spring means for applying a biasing force for separating from the press-contact portion to the driven cam body; and a cam driven by the two cam bodies caused by the rotation of the drive shaft in the normal rotation direction and the reverse rotation direction. Between the pressure receiving part of the motor and the drive cam body Bidirectional rotation transmission is obtained by obtaining the rotation force, and when the motor is stopped, the rotation driven member side is allowed to rotate in the forward and reverse directions. It can perform both functions required as a rotary clutch, that is, transmission of driving force in the forward and reverse directions and free rotation of the driven side in the forward and reverse rotation directions, and in particular, the latter drive shaft is kept stationary. Since the rotation-side driven member on the driven side can be operated in the normal / reverse direction while being held, when used as an opening / closing device for an electric slide door for an automobile or as a driving device for a traveling drive wheel of an electrically driven vehicle body, Since no electromagnetic clutch is required, the structure can be significantly simplified. Further, the structure of the direct-acting bidirectional rotary transmission clutch itself is simple, the number of parts is small, the cost can be reduced, and the energy efficiency of the applied device can be improved.

[Brief description of the drawings]

FIG. 1 is a vertical sectional front view of a first embodiment of a direct acting bidirectional rotary clutch of the present invention.

FIG. 2 is an exploded perspective view.

FIG. 3 is a vertical sectional front view of the second embodiment.

FIG. 4 is a diagram showing a state where the apparatus is used as a sliding door opening / closing device for a vehicle.

FIG. 5 is a vertical sectional front view of the fifth embodiment.

FIG. 6 is an exploded perspective view.

FIG. 7 shows another embodiment of a driven cam body.

FIG. 8 is a longitudinal sectional view of a sixth embodiment.

FIG. 9 is a longitudinal sectional view of a third embodiment.

FIG. 10 is a longitudinal sectional view showing a modification of the third embodiment.

FIG. 11 is a longitudinal sectional view of a fourth embodiment.

[Explanation of symbols]

2 Slide door 12 Motor 20, 50, 50 ', 70, 71 Direct-acting bidirectional rotary clutch 21 Mounting bracket 22 Fixed shaft 22a, 22b Fitting shaft 25, 51 Drive shaft 31, 61, 72 Rotary driven member 36, 64 , 65, 76 Pressure receiving portion 37, 45 Driving cam body 37a Cam surface (inclined surface) 38 Thrust bearing 41, 46, 72 Followed cam 41a Driven cam surface (inclined surface) 43 Return spring (elastic member) 44 Thrust plate 52 th 1 Taper cone (followed cam body) 53 Second taper cone (followed cam body) 54, 54a Drive pin 55 Drive pin 56a, 56b, 57a, 57b, 59a, 59b Elongated hole 58 Cam mechanism 73 Press-contact portion

 ────────────────────────────────────────────────── ─── Continued on the front page F term (reference) 2E052 AA09 CA06 DA00 DA01 DA03 DB00 DB01 DB03 EA16 EB01 EC01 KA06 KA15 KA16

Claims (12)

[Claims] 1. A mounting bracket for rotatably supporting a drive shaft connected to a motor, a drive cam body coupled to the drive shaft and adapted to rotate integrally in a rotational direction,
It is loosely fitted to the drive shaft and receives the cam action of the drive cam body,
A driven cam body displaceably movable in the axial direction, a pressure receiving portion receiving a pressing force due to the displacement of the driven cam body, and a rotation driven member rotatably supported on the drive shaft; An elastic spring interposed between the rear end portion and the bracket portion to apply to the driven cam body a rotation restraining force enough to cause relative rotation displacement between the two cam bodies and a biasing force from the press contact portion. Means, the cam action of the two cam bodies generated by the rotation of the drive shaft in the normal rotation direction and the reverse rotation direction, to obtain a projecting force between the pressure receiving portion of the rotation driven member and the drive cam body, A direct-acting bidirectional rotary clutch, wherein bidirectional rotation transmission is made possible, and a rotation movement of the rotation driven member side in the normal rotation direction is allowed when the motor is stopped. 2. A mounting bracket for rotatably supporting a drive shaft connected to a motor, a drive cam body coupled to the drive shaft and integrally rotating in a rotation direction,
A driven cam body which is loosely fitted to a fixed shaft integrated with the mounting bracket, receives the cam action of the drive cam body, and can be displaced and moved in the axial direction, and a pressure receiving portion which receives a pressing force due to the displacement of the driven cam body. A rotation driven member rotatably supported on the drive shaft, and a rotation displacement member interposed between the rear end portion of the driven cam body and the bracket portion to generate a relative rotational displacement between the two cam bodies. An elastic spring means for applying to the driven cam body a rotation restraining force and a biasing force for separating from the press-contact portion to such an extent that both the cam bodies are generated by the rotation of the drive shaft in the normal rotation direction and the reverse rotation direction. By the cam action, the projecting force between the pressure receiving portion of the rotation driven member and the driving cam body is obtained to enable bidirectional rotation transmission, and when the motor stops, the rotation driven member rotates forward and reverse. To allow rotational movement in any direction Direct-acting bidirectional rotary clutch. 3. A cam surface of a driving cam body and a driven cam body having a plurality of trapezoidal cams arranged on the same circumference at opposite end faces.
The rotating clutch as described. 4. The rotary clutch according to claim 1, wherein the cam surfaces of the driving cam body and the driven cam body are formed in an elliptical ring shape by slopes of both end faces facing each other. 5. The rotary clutch according to claim 2, wherein the pressure contact surface of the driven cam body and the pressure receiving portion of the rotary driven member opposed thereto are formed by slopes. 6. A frustum cone having a mounting bracket rotatably supporting a drive shaft connected to a motor, and a truncated cone having a press-contact surface for loosely fitting to the drive shaft and transmitting a press-contact force due to axial displacement to an outer peripheral surface. A first taper cone for normal rotation transmission, a second taper cone for reverse rotation disposed axially symmetrically with the first taper cone, and a predetermined inclination angle with respect to the axis of the first and second taper cones Each of the cam slots, each of which is bored with the same, each of the drive pins which are mounted in the respective cam slots to rotate integrally with the drive shaft, and each of which receives a press contact force due to an axial displacement of each of the taper cones. And a rotation driven member rotatably supported on the drive shaft, between the outer end surfaces of the first and second taper cones and the inner end of the rotation driven member. Interposed, drive shaft and each taper cord And a resilient spring means for applying to both of the tapered cones a rotational restraining force that causes relative rotational displacement between the tapered cone and the pressure receiving portion, and a reverse rotation with respect to the normal rotation direction of the drive shaft. By the cam action between each drive pin and the cam long hole generated by the rotational drive in the direction, the pressure contact force due to the axial displacement of any one of the tapered cones is obtained to enable bidirectional rotation transmission and the motor. A direct-acting bidirectional rotary clutch, characterized in that the rotary driven member is allowed to rotate in the forward and reverse directions when it is stopped. 7. A single tapered cone in which the first and second tapered cones are integrally formed and have a single cam slot extending beyond the axis and a single drive pin mounted on the drive shaft. 7. The rotary clutch according to claim 6, wherein the cone is configured to generate an axial displacement enabling bidirectional rotation transmission. 8. A rotation driven member is rotatably supported on the mounting bracket, and an elastic spring means for applying a biasing force to the tapered cone is provided between the outer end surface of the tapered cone and the mounting bracket. 8. The rotary clutch according to claim 6, wherein the rotary clutch is interposed therebetween. 9. A sliding door provided on a side of an automobile,
A winding drum body driven forward and backward by an electric motor;
The drum body and the slide door are each provided with an index means such as a belt or a wire whose end is connected to the slide body. In the electric sliding door, a rotation driven member in the direct acting bidirectional rotary clutch according to claim 1 is the winding drum body, and one end of each of the indexing means is connected to the rotation driven member. The sliding door can be freely opened and closed manually without transmitting the rotational force in the forward and reverse directions of the rotation driven member by the opening and closing operation from the sliding door side to the drive shaft of the rotary clutch. An opening and closing device for an electric sliding door. 10. The rotary clutch according to claim 1, wherein the rotation driven member is a take-up drum for a slide door for an automobile. 11. An electric traveling vehicle body in which traveling driving wheels of the vehicle are driven forward and reverse by an electric motor, wherein the rotation driven member in the direct acting bidirectional rotary clutch according to claim 1 is provided. In addition to the traveling drive wheels, when the electric motor is stopped, the traveling drive wheels can freely travel without transmitting the rotational force in the forward and reverse directions of the rotation driven member to the drive shaft of the rotary clutch. An electric traveling drive device characterized in that: 12. The rotary clutch according to claim 1, wherein the rotation driven member is a traveling drive wheel of an electric traveling vehicle body.