JP2003056596A - Rotating device with clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a lightweight, compact and inexpensive rotation drive with a function of locking an output side against reverse input torque, and of inhibiting reflux of the reverse input torque to a motor and a reduction gear on the input side. SOLUTION: A motor M, a reduction gear R for reducing input torque from the motor M, and a reverse input preventing clutch C are integrally unified. The reverse input prevention clutch C is provided with a lock means for locking an output side member 2 against the reverse input torque, a lock release means for unlocking a locking state by the lock means against the input torque from an input side member 1, and a torque transmission means for transmitting the input torque from the input side member 1 to an output side member 2, when the locking state by the lock means is unlocked.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotating device with a clutch used in, for example, a mirror driving device of an automobile. The clutch here means one having a function of transmitting the input torque from the input side to the output side and locking the reverse input torque from the output side so as not to recirculate to the input side.

[0002]

2. Description of the Related Art Conventionally, a structure in which a motor is used as a rotary drive source and a speed of a motor is reduced by a speed reducer has been widely used for applications requiring low-speed and large-torque power.

[0003]

In this case, there is no particular problem when the speed reducer is driven from the motor side,
When the torque is reversely input from the output side for some reason, the following problems may occur.

A) When a worm gear device is used as a speed reducer, this gear device cannot rotate due to reverse input, so a large load is applied to the teeth of the worm wheel or worm. Especially, a large thrust load acts on the worm. Therefore, the bearing that supports the teeth and the worm may be damaged, or the mechanism needs to be upsized in order to prevent such damage.

B) Even in a speed reducer using a spur gear, a helical gear, or the like, the teeth may be damaged when the reverse input torque becomes excessive (for example, when a shocking reverse input acts).

To solve the above problems, the input torque from the motor on the input side is transmitted to the output side, while the output side is locked against the reverse input torque from the output side, and the motor on the input side is locked. In addition, a mechanism having a function of preventing reverse input torque from flowing back to the speed reducer is required.

Therefore, an object of the present invention is to provide a light-weight, compact and low-priced rotating device with a clutch having the above-mentioned functions.

[0008]

In order to solve the above-mentioned problems, the present invention comprises a motor, a speed reducer for reducing the input torque from the motor, and a reverse input prevention clutch, which are integrated into a unit. The reverse input prevention clutch is provided between the input side member to which the torque from the reduction gear is input, the output side member to which the torque is output, the stationary side member to which rotation is restricted, and the stationary side member and the output side member. Lock means for locking the output side member and the stationary side member against reverse input torque from the output side member, and lock means for the input torque from the input side member provided on the input side member. A lock releasing means for releasing the locked state and a torque transmitting means for transmitting the input torque from the input side member to the output side member when the locked state by the lock means is released.

In the above structure, when an input torque is input to the input side member of the reverse input prevention clutch from the speed reducer, the lock state of the lock means is released by the lock release means, and in that state, the input side member is released. Input torque is transmitted to the output side member via the torque transmission means. on the other hand,
Reverse input torque from the output side member is locked between the output side member and the stationary side member via the locking means. Therefore, it is possible to obtain the function of transmitting the input torque from the input side to the output side and preventing the reverse input torque from the output side from being returned to the speed reducer or the motor on the input side. By unitizing this reverse input clutch together with the motor and the speed reducer, it is possible to avoid adverse effects of the reverse input torque on the speed reducer, etc., and to provide a lightweight, compact, and low-cost rotary drive device. It will be possible.

Further, an input side member to which the torque from the motor via the reduction gear is input, an output side member to which the torque is output, a stationary side member to which rotation is restricted, a stationary side member and an output side member. Locking means for locking the output side member and the stationary side member against the reverse input torque from the output side member, and the input side member provided for the input torque from the input side member. Reverse input having lock releasing means for releasing the locked state by the locking means and torque transmitting means for transmitting the input torque from the input side member to the output side member when the locked state by the lock means is released A rotation driven device having the same effect is integrally formed by integrally forming the prevention clutch and the output side mechanism that performs a predetermined operation with the torque transmitted to the output side member of the reverse input prevention clutch. It can be provided.

The "locking means" of the reverse input preventing clutch described above includes a wedge engaging force, an uneven engaging force, a frictional force,
Includes magnetic force, electromagnetic force, fluid pressure, fluid viscous resistance force, fine particle medium, etc.
From the viewpoints of simplification of the structure and control mechanism, smooth operation, cost, etc., it is preferable to apply the rotation restraining force by the wedge engaging force. Specifically, a wedge gap is formed between the output side member and the stationary side member, and the lock / idle rotation is switched by engaging and disengaging the engaging element with respect to the wedge gap. good. Further, in this configuration, a cam surface for forming a wedge gap is provided on the output side member or the stationary side member (a roller, a ball or the like having a circular cross section is used as an engaging member), and the wedge gap is formed. A configuration in which a cam surface for this is provided on the engaging element (a sprag or the like is used as the engaging element) is included.

Further, an input side member of the reverse input preventing clutch,
By making the output side member and the stationary side member plastically processed products of metal plates respectively, it is possible to achieve compactness, weight reduction, and cost reduction compared to the case of forging products, casting products, and machined products. it can. The “metal plate” may be any one that can be formed into a desired size and shape by plastic working, and the material thereof is not particularly limited, but a steel plate, for example, can be adopted. Further, as the “plastic working”, for example, press working can be adopted.

In the above structure, the input side member can be provided with a connecting portion for connecting the output shaft of the speed reducer, and the connecting portion can be positioned inside the clutch. As a result, the axial dimension of the reverse input clutch itself can be made compact, and the axial dimensions of the rotary drive device and the rotary driven device as a whole can be made compact. This connecting portion is preferably provided in a tubular portion continuously extending inward from the inner peripheral side of the input side member in the clutch inward direction, and at least one flat surface portion which is fitted in a plane with the output shaft of the reduction gear is provided. It is provided. The flat surface portion provided on the output shaft of the speed reducer and the flat surface portion of the connecting portion are fitted in the flat surface, so that the output shaft and the input-side member are relatively non-rotatably connected.

Further, the output shaft portion may be provided with at least one flat surface portion which is fitted in a plane with the rotating member of the output side mechanism. When the flat surface portion of the rotating member and the flat surface portion of the output shaft portion are fitted in the flat surface, the output shaft portion and the rotating member are coupled to each other such that they cannot rotate relative to each other. Alternatively, the output shaft portion may be provided with a spline portion or a serration portion that engages with the rotating member of the output side mechanism by a spline or serration.

In the above structure, the locking means of the reverse input preventing clutch is provided on the stationary side member and on the output side member, and the wedge gap is provided between the circumferential surface and the circumferential surface in both forward and reverse rotation directions. And a pair of engagement elements interposed between the cam surface and the circumferential surface, and elastic members for pressing the pair of engagement elements in the wedge gap direction. The lock releasing means is an engaging element that selectively engages with either one of the pair of engaging elements and presses it in the direction opposite to the direction of the wedge gap, and the torque transmitting means is the input side member. And an engaging element in the rotational direction provided on the output side member. At the neutral position of the lock releasing means and the torque transmitting means, the rotational gap δ1 between the engaging element and the engaging element of the lock releasing means.
And the rotational gap δ2 between the engaging elements of the torque transmission means.
Have a relationship of δ1 <δ2.

In the above structure, when a reverse input torque in one direction is input to the output side member of the reverse input prevention clutch, one of the pair of engaging elements wedge-engages with the wedge gap in that direction, and the output side. When the member is locked in one direction with respect to the stationary side member and the reverse input torque in the other direction is input to the output side member, the other of the pair of engaging elements wedge-engages with the wedge gap in that direction, Lock the output member in the other direction with respect to the stationary member. Therefore, the output side member is locked in both the forward and reverse rotation directions with respect to the stationary side member via the pair of engaging elements. On the other hand, when the input torque is input to the input side member, first, the engagement element as the lock releasing means provided in the input side member has the wedge gap and the wedge engaging member in the direction of the input torque among the pair of engaging elements. The mating engagement element is pressed in the direction opposite to the direction of the wedge gap to disengage it from the wedge gap. As a result, the locked state of the output side member is released in the direction of the input torque.
Next, in the state where the output side member is unlocked, the engaging elements in the rotational direction as the torque transmitting means provided on the input side member and the output side member engage with each other. As a result, the input torque input to the input side member is transmitted through the route of the input side member → the torque transmitting means (engaging element in the rotation direction) → the output side member, and the output side member rotates.

At the neutral position of the lock releasing means and the torque transmitting means, the rotational gap δ1 between the engaging element of the lock releasing means and the engaging element and the rotational gap δ2 between the engaging elements of the torque transmitting means are defined. , Δ1 <δ2, the lock release by the lock release means and the torque transmission by the torque transmission means can be sequentially and reliably performed.

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

FIGS. 1 and 2 show the overall construction of a rotating device with a clutch according to a first embodiment of the present invention.
In this rotating device, a motor M, a speed reducer R, and a reverse input preventing clutch C are unitized into an assembly. This rotation device functions as a rotation drive device that generates a rotation torque, and the torque generated by the motor M is decelerated by the reduction gear R and then output from the output shaft R1 of the reduction gear R via the reverse input prevention clutch C. Mechanism O (FIGS. 14 and 15)
Input). In the vehicle mirror drive device described above, the mirror unit (door mirror or the like) to be driven corresponds to the output side mechanism O.

The reverse input preventing clutch C includes an input side member 1 to which the torque from the speed reducer R is input, an output side member 2 to output the torque, and a stationary side member 3 that is restrained from rotating.
The stationary side plate 4 fixed to the stationary side member 3 and a locking means, an unlocking means, and a torque transmitting means, which will be described later, are configured as main elements. The input-side member 1, the output-side member 2, the stationary-side member 3, and the fixed-side plate 4 are metal plates, for example, stamped products of steel plate (members formed by press working).

As shown in FIGS. 1 and 3, the input side member 1
Is a flange portion 1a extending in the radial direction and a flange portion 1
A cylindrical portion 1b that continuously extends from the inner periphery of a in one axial direction (inward of the clutch), and a plurality of columns (e.g., eight columns) that continuously extend from the outer periphery of the flange portion 1a in one axial direction. The main component is a part 1c and a plurality of (e.g., eight) hole parts 1d formed through the flange part 1a.

The pillar portion 1c and the hole portion 1d are arranged at equal intervals around the circumference. The positions of the pillars 1c and the positions of the holes 1d are displaced from each other in the circumferential direction, and in this example, the holes 1d are located at intermediate positions between the pillars 1c adjacent in the circumferential direction. The space between the pillar portions 1c adjacent to each other in the circumferential direction constitutes a pocket 1e that is open toward one side in the axial direction,
A pair of rollers 6, which will be described later, are arranged in each pocket 1e.

The tubular portion 1b is located inside the clutch, and the tip portion thereof is slightly reduced in diameter to form a connecting portion 1f. In this embodiment, the inner periphery of the connecting portion 1f has a polygonal shape, for example, a quadrangular shape, and each of the sides of the quadrilateral forms four flat surface portions 1f.
f1 is formed. The output shaft R1 of the speed reducer R is inserted into the inner circumference of the connecting portion 1f. The outer circumference of the distal end of the output shaft R1 has a polygonal shape, for example, a quadrangular shape corresponding to the inner circumference of the connecting portion 1f, and four plane portions are formed by each side of the quadrangle. Then, the flat surface portions formed on the output shaft R1 and the flat surface portions 1f1 of the connecting portion 1f are flatly fitted to each other, so that the output shaft R1 and the input side member 1 are relatively non-rotatably connected. The connecting portion 1f may have a polygonal shape, for example, a quadrangular shape, not only on the inner circumference but also on the thick portion as a whole. Further, the output shaft R1 and the connecting portion 1f are connected to each other by one flat surface portion,
Alternatively, a structure may be adopted in which two flat surface portions formed at 180-degree opposite positions are flatly fitted to each other.

The output side member 2 has a flange portion 2a extending in the radial direction, a cylindrical output shaft portion 2b extending continuously from the inner circumference of the flange portion 2a in one axial direction, and the flange portion 2a.
Large-diameter portion 2c that continuously extends from the outer periphery of the shaft to the other axial direction
And a plurality of (for example, eight) protrusions 2d that axially protrude from one end of the large diameter portion 2c. The shaft end of the output shaft portion 2b is bottomed by the bottom portion 2b2. The output shaft portion 2b is connected to a rotating member (not shown) of the output side mechanism O.

The large diameter portion 2c has a polygonal shape, for example, a regular octagonal shape, and the outer circumference of each side is a cam surface 2c1. Therefore, there are eight cam surfaces 2c1 on the outer circumference of the large diameter portion 2c.
Are arranged at equal intervals on the circumference.

As shown in an enlarged view in FIG. 4, the output side member 2
The protrusions 2d of each of the
It is inserted in d with a rotational gap (rotational gap δ2 shown in FIG. 7). Note that, as shown in FIG. 5, each hole 1d may be subjected to a burring process to form a built-up portion 1d1. Thereby, the protrusion 2d and the hole 1d can be reliably engaged with each other in the rotation direction.

The stationary member 3 has a flange portion 3a extending in the radial direction, a cylindrical portion 3b extending continuously in one axial direction from the inner circumference of the flange portion 3a, and an axial direction from the outer circumference of the flange portion 3a. The main component is a large-diameter portion 3c extending to the other side and a flange portion 3d protruding from one end of the large-diameter portion 3c in the outer diameter direction.

The flange portion 3a is mounted on the outer surface of the flange portion 2a of the output side member 2, and the tubular portion 3b is a bearing that rotatably supports the outer periphery of the output shaft portion 2b of the output side member 2 in the radial direction. Part (slide bearing).

On the inner circumference of the large diameter portion 3c, there is provided a circumferential surface 3c1 which faces the cam surface 2c1 of the output side member 2 in the radial direction and forms a wedge gap in both the forward and reverse rotation directions.

A plurality (for example, four) of rectangular notch portions 3d1 and a plurality (for example, four) of arc-shaped notch portions 3d2 are formed on the flange 3d at equal intervals on the circumference. The notch 3d1 is fitted with a caulking portion 4c of the fixed side plate 4 which will be described later. The notch portion 3d2 is the bracket portion 4b of the fixed side plate 4.
It is provided in order to avoid interference with a mounting bolt mounted on the.

As shown in FIGS. 1 and 2, the fixed side plate 4
Is a flange portion 4a extending in the radial direction and a flange portion 4a.
a plurality of (for example, four) bracket portions 4b protruding from the outer periphery of a in the outer diameter direction, and a plurality of (for example, four) crimping portions 4c protruding from the outer periphery of the flange portion 4a in one axial direction,
It is mainly configured by a cylindrical portion 4d continuously extending from the inner circumference of the flange portion 4a to one side in the axial direction (inward direction of the clutch).

The flange portion 4a is attached to the outer surface of the flange portion 1a of the input side member 1. 4 bracket parts 4
b are formed at equal intervals around the circumference, and through holes 4b1 are formed in each. A mounting bolt (not shown) is inserted into the through hole 4b1. By attaching this mounting bolt to a member (frame, housing, etc.) on the reducer R side,
The reverse input prevention clutch C is directly fixed to the speed reducer R. The means for fixing the reverse input prevention clutch C to the speed reducer R is not limited to the bolt, and can be arbitrarily selected. The reverse input preventing clutch C may be fixed to a motor with a reducer, which is commercially available as an assembly of the motor M and the reducer R.

The four caulking portions 4c are formed at equal intervals around the circumference, and each of the four caulking portions 4c is provided with a pair of bifurcated claws 4c1 (see FIG. 2). The caulking portion 4c is fitted into the cutout portion 3d1 of the stationary side member 3, the pair of claws 4c1 are folded back in opposite directions in the circumferential direction, and caulked to the collar portion 3d of the stationary side member 3. As a result, the stationary side member 3 and the fixed side plate 4 are coupled to each other in the axial and rotational directions such that they cannot move relative to each other.

The tubular portion 4d is the tubular portion 1b of the input side member 1.
Is a bearing portion (sliding bearing) that is inserted on the inner peripheral side of and that supports the outer periphery of the output shaft R1 of the reduction gear R rotatably in the radial direction.

As shown in FIG. 2, between each cam surface 2c1 of the output side member 2 and the circumferential surface 3c1 of the stationary side member 3, a pair of rollers 6 (for example, a total of 8 pairs) as engaging elements are provided. Are arranged and housed in the pocket 1e formed between the pillar portions 1c of the input side member 1. A tongue piece portion 7b of an elastic member 7, which will be described later, is interposed between the pair of rollers 6 and presses the pair of rollers 6 in directions away from each other. Cam surface 2c1, circumferential surface 3
c1, the pair of rollers 6, and the tongue portion 7b of the elastic member 7.
The lock means is constituted by the lock means, and the lock releasing means is constituted by the pillar portions 1c (engagement elements) of the input side member 1 located on both sides in the circumferential direction of the pair of rollers 6.
1d of the hole and the protrusion 2 of the output side member 2 inserted in the hole 1d
Torque transmitting means is constituted by d. Note that, for example, grease is sealed as a lubricant in a space between the outer circumference of the output side member 2 and the inner circumference of the stationary side member 3, particularly between the cam surface 2c1 and the circumferential surface 3c1.

As shown in FIG. 6, the elastic member 7 includes a base portion 7
a and a tongue piece portion 7b extending from the base portion 7a to one side in the axial direction
It has and. The elastic member 7 has an integral ring shape, and a plurality of pairs of tongue pieces 7b are arranged at equal intervals on the circumference on a ring-shaped base portion 7a. The elastic member 7 is a pressed product of a metal plate, for example, a spring steel plate.

In this embodiment, the outer periphery of the base 7a has a regular octagonal shape, and a pair of tongue pieces 7b are provided on each side of the outer periphery of the base 7a. A pair of tongue pieces 7b
Is formed into a bent piece by cutting and raising each side portion of the outer periphery of the base portion 7a, and each is continuous to the base portion 7a via the standing portion 7c. As shown in FIG. 6C, the pair of tongue pieces 7b is interposed between the pair of rollers 6 and elastically presses the pair of rollers 6 in a direction in which they are separated from each other.

As shown in an enlarged view in FIG. 7, at the neutral position, the pair of rollers 6 are pressed by the tongue pieces 7b of the elastic member 7 in the directions away from each other, and the respective cam surfaces 2c.
1 and the circumferential surface 3c1 are engaged with the wedge gaps in both the forward and reverse rotation directions. At this time, each pillar portion 1c of the input side member 1
There is a rotational gap δ1 between each of the rollers and each roller 6. Further, between the protrusion 2d of the output side member 2 and the hole 1d of the input side member 1, there are rotational gaps δ2 in both the forward and reverse rotational directions. The rotational gap δ1 and the rotational gap δ2 have a relationship of δ1 <δ2. The size of the rotational gap δ1 is, for example, about 0 to 0.4 mm (0 to 1.5 ° about the clutch axial center), and the rotational gap δ1.
The size of 2 is, for example, about 0.4 to 0.8 mm (1.8 to 3.7 ° about the axis of the clutch).

In the state shown in FIG. 7, when a counterclockwise input torque is input to the output member 2 from the output mechanism O, the counterclockwise (rotational rear) roller 6 causes the wedge gap in that direction. The output side member 2 is locked to the stationary side member 3 in a clockwise direction by wedge-engaging with the stationary side member 3. When a counterclockwise reverse input torque is input to the output side member 2, the clockwise (rotationally rearward) roller 6 is wedge-engaged with the wedge gap in that direction,
The output side member 2 is locked in the counterclockwise direction with respect to the stationary side member 3. Therefore, the reverse input torque from the output side member 2 is locked by the roller 6 in both the forward and reverse rotation directions, whereby the rotating member of the output side mechanism O is fixed.

FIG. 8 shows an initial state in which the input torque (clockwise in the figure) is input to the input side member 1 and the input side member 1 starts to rotate clockwise in the figure. Since the rotational gap is set to δ1 <δ2, first, the counterclockwise direction (rotational direction rear) column portion 1c of the input side member 1 engages with the roller 6 in that direction (rotational direction rear), This is pressed clockwise (forward in the rotational direction) against the elastic force of the tongue piece 7b. As a result, the roller 6 in the counterclockwise direction (rearward in the rotational direction) is released from the wedge gap in that direction, and the locked state of the output side member 2 is released {the roller 6 in the clockwise direction (forward in the rotational direction) is released. , Does not engage with the wedge gap in that direction. }. Therefore, the output side member 2 can be rotated clockwise.

When the input side member 1 further rotates clockwise, the wall surface of the hole 1d of the input side member 1 engages with the projection 2d of the output side member 2 in the clockwise direction as shown in FIG. As a result, the clockwise input torque from the input side member 1 is transmitted to the output side member 2 via the engaging portion between the hole 1d and the protrusion 2d, and the output side member 2 rotates clockwise. When a counterclockwise input torque is input to the input side member 1, the output side member 2 rotates counterclockwise by the operation opposite to the above. Therefore, the input torque from the input side member 1 in both the normal and reverse rotation directions is transmitted to the output side member 2 via the hole portion 1d and the projection portion 2d as the torque transmission means, and the output side member 2 rotates in the forward and reverse directions. Rotate in the direction. When the input torque from the input side member 1 disappears, the elastic restoring force of the tongue piece 7b restores the neutral position shown in FIG.

10 to 12 show a second embodiment of the present invention. In the second embodiment, as the torque transmitting means, the protrusion 22d is projected in the outer diameter direction and engaged with the notch 21d. As shown in FIG. 12, the cutout portion 21 d is formed on the outer peripheral side portion of the flange portion 1 a of the input side member 1. A plurality of notches 21d (for example, 8
Formed) and arranged at equal intervals around the circumference. The base end 1c1 of the column portion 1c is slightly wider in the circumferential direction, and the notch 21d is located between the base ends 1c1 adjacent in the circumferential direction. The projection 22d in the outer diameter direction has a base end 22d1 in the axial direction.
Through the end of the large diameter portion 2c of the output side member 2. A plurality of (for example, eight) protrusions 22d are formed and arranged at equal intervals on the circumference. Each protrusion 22d of the output side member 2
Are respectively fitted to the respective cutout portions 21d with a rotational gap δ2 (see FIG. 7).

Incidentally, the input side member 1 may be provided with a cutout portion 21d 'of the form shown in FIG. 13 in place of the cutout portion 21d. According to this example, compared to the form shown in FIG.
Since it is not necessary to cut out the flange portion 1a of the input side member 1, the manufacturing process is simplified. Further, as a torque transmitting means, a notch portion provided on the input side member 1 and an axial projection portion provided on the output side member 2 are provided in the rotational gap δ2.
(See FIG. 7).

As shown in FIGS. 10, 12 and 13, for example, one flat surface portion 2b1 is provided at the shaft end portion of the output shaft portion 2b. This shaft end portion is connected to the rotating member of the output side mechanism O. Then, the flat surface portion 2b1 of the shaft end portion
And the plane portion formed on the rotating member are fitted in the plane, the output shaft portion 2b and the rotating member are coupled to each other so as not to rotate relative to each other. It should be noted that the two flat portions 2b1 may be formed to face each other by 180 degrees, or the shaft end portion may have a polygonal shape, and the shaft end portion and the rotating member may be flatly fitted to each other by a plurality of flat portions. good. Of course, if such a plane fitting structure is not particularly required, the flat surface portion 2b1 may be omitted and the outer periphery of the output shaft portion 2b may be formed into a cylindrical surface shape, as in the first embodiment. The above-mentioned plane fitting structure can be applied to the first embodiment.

Since the other matters are the same as those in the first embodiment, duplicated description will be omitted.

In the above description, as shown in FIG.
Of the rotary drive system that drives the output side mechanism O with the rotary torque of the motor M, the rotary drive device in which the motor M, the speed reducer R, and the reverse input prevention clutch C are unitized is illustrated (the unit part is indicated by a broken line). As shown in FIG. 15, the reverse input prevention clutch C is separated from the speed reducer R and is unitized with the output side mechanism O to form a rotary driven device that operates by receiving a rotation torque. You can also The structure of the reverse input preventing clutch C at this time conforms to the clutch structure of the rotary drive device described with reference to FIGS. 1 to 13. In this case, the connecting portion 1f of the input side member 1 is connected to the transmission shaft 10 extending from the output side of the speed reducer R, and the output shaft 2b of the output side member 2 is connected to the input side (rotating member) of the output side mechanism O. Be connected.

The above-mentioned reverse input preventing clutch can be used not only for the mirror driving device of an automobile but also for various mechanisms and devices. For example, the lead screw part of machine tools and control devices,
In a nursing bed driven by a ball screw, a ball screw portion of a household elevator, or the like, by disposing a reverse input preventing clutch C between the screw portion and the motor, the screw portion (the rotating member of the output side mechanism O is rotated). Corresponding to the reverse input torque from the output side member 2 is locked, and the reverse input torque is prevented from flowing back to the motor side.

In tools such as electric screwdrivers,
If the reverse input prevention clutch C is arranged between the motor and the chuck, the reverse input torque applied from the chuck is
Since the output side member is locked, the screw can be electrically screwed in and then manually tightened (by rotating the main body), and the functionality of the tool can be enhanced.

Further, in a power seat or power window for an automobile, the reverse input preventing clutch C can be arranged between the motor and the seat (or window). With these mechanisms, worm &
In many cases, the wheel mechanism is used and the reverse input torque from the seat or window is not circulated to the motor side, but the torque transmission efficiency is poor in the worm & wheel mechanism, so the motor capacity must be increased. There is inconvenience. On the other hand, if the reverse input prevention clutch is used, it is possible to prevent the reverse input torque from flowing back from the seat in the same manner. Therefore, instead of the worm & wheel mechanism, a spur gear with good transmission efficiency is used as the reduction gear. It is possible,
The motor capacity can be reduced.

Further, the reverse input preventing clutch may be arranged in the rotation driving portion of the C arm of the X-ray inspection apparatus.
The C-arm is a C-shaped member provided with an X-ray irradiator and a light receiver, and during inspection, the C-arm is rotated around the subject and an image is taken at an arbitrary position. By arranging the reverse input prevention clutch C between the C arm and the motor, it becomes possible to suppress the swing of the C arm and perform high-precision shooting.

In vehicles such as motorcycles, buggy cars, and tractors, kickback from the road surface is applied to the steering wheel during traveling. In this case, if the reverse input preventing clutch C is arranged between the handle shaft and the axle, kickback can be suppressed and steering stability can be improved.

[0052]

According to the present invention, since the motor, the speed reducer, and the clutch (or the clutch and the output side mechanism) are integrally unitized, it is possible to provide a compact and lightweight rotating device with a clutch. it can. The clutch has a function of transmitting the input torque from the input side to the output side and locking the reverse input torque from the output side so that it does not flow back to the input side, so that the reverse input torque also causes rotation in the rotary drive system. It never happens. Therefore, it is possible to avoid an adverse effect on the reducer and the motor due to an excessive reverse input torque, and it is suitable for an application in which the position variation of the output side mechanism due to the reverse input torque is disliked.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view {cross-sectional view taken along the line BB of FIG. 2} of a rotating device with a clutch according to a first embodiment.

FIG. 2 is a horizontal cross-sectional view {a cross-sectional view taken along the line AA of FIG. 1} showing the rotating device with a clutch according to the first embodiment.

FIG. 3 is a perspective view showing an input side member, an output side member, and a stationary side member of the reverse input prevention clutch.

FIG. 4 is an enlarged vertical cross-sectional view showing a peripheral portion of torque transmission means (a cutout portion of an input side member and a protrusion portion of an output side member).

FIG. 5 is an enlarged vertical cross-sectional view showing a peripheral portion of torque transmission means (a cutout portion of an input side member and a protrusion portion of an output side member) according to another example.

FIG. 6 is a front view showing an elastic member {FIG. 6 (a)}, a view seen from the outer peripheral side {FIG. 6 (b)}, and an enlarged view showing a state in which a tongue piece is interposed between a pair of rollers. It is FIG.6 (c)}.

FIG. 7 is a partially enlarged cross-sectional view illustrating the action of the reverse input prevention clutch (neutral position).

FIG. 8 is a partially enlarged cross-sectional view illustrating the operation of the reverse input prevention clutch (when unlocked).

FIG. 9 is a partially enlarged cross-sectional view illustrating the operation of the reverse input prevention clutch (during torque transmission).

10 is a vertical cross-sectional view of the reverse input preventing clutch according to the second embodiment {FIG. 10 (a): BB cross-sectional view of FIG. 11}, and an X-direction arrow view of the output shaft portion {FIG. 10 ( b)}.

FIG. 11 is a transverse cross-sectional view {a cross-sectional view taken along the line AA of FIG. 10 (a)} showing the rotating device with a clutch according to the second embodiment.

FIG. 12 is a perspective view of an input side member, an output side member, and a stationary side member of the reverse input prevention clutch.

FIG. 13 is a perspective view of an input side member, an output side member, and a stationary side member according to another example.

FIG. 14 is a schematic diagram showing a rotary drive system including a motor, a speed reducer, a reverse input prevention clutch, and an output side mechanism.

FIG. 15 is a schematic diagram showing a rotary drive system including a motor, a speed reducer, a reverse input prevention clutch, and an output side mechanism.

[Explanation of symbols]

1 Input side member 1f connecting part 1f1 flat part 2 Output side member 2b Output shaft 3 stationary member 4 Fixed side plate 6 Engagement element (roller) 7 Elastic member 7a base 7b Tongue part M motor R reducer R1 output shaft C Reverse input prevention clutch O output side mechanism

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Masahiro Kawai             Mie Prefecture Kuwana City Oogata Oyumi 3066 N             Inside Thien Co., Ltd.

Claims (7)

[Claims] 1. A motor, a speed reducer for reducing the input torque from the motor, an input side member to which the torque from the speed reducer is input, an output side member to which the torque is output, and a stationary rotation restrained. A side member, a locking means provided between the stationary side member and the output side member, for locking the output side member and the stationary side member against a reverse input torque from the output side member; , The unlocking means for releasing the locked state by the locking means against the input torque from the input side member, and the input torque from the input side member to the output side member when the locked state by the locking means is released. A rotating device with a clutch, characterized in that a reverse input preventing clutch having a torque transmitting means for transmitting is integrated into a unit. 2. An input side member to which torque is input from a motor via a reduction gear, an output side member to which torque is output, a stationary side member to which rotation is restricted, a stationary side member and an output side member. Locking means for locking the output side member and the stationary side member against the reverse input torque from the output side member, and the input side member provided for the input torque from the input side member. Reverse input having lock releasing means for releasing the locked state by the locking means and torque transmitting means for transmitting the input torque from the input side member to the output side member when the locked state by the lock means is released A rotation device with a clutch, wherein the prevention clutch and an output side mechanism that performs a predetermined operation with the torque transmitted to the output side member of the reverse input prevention clutch are unitized into a unit. 3. The rotating device with a clutch according to claim 1, wherein each of the input side member, the output side member and the stationary side member of the reverse input preventing clutch is a plastically worked product of a metal plate. 4. The input side member of the reverse input prevention clutch has a connecting portion for connecting the output shaft of the speed reducer, and the connecting portion is located inside the clutch. 2. A rotating device with a clutch according to 2. 5. The rotating device with a clutch according to claim 4, wherein the connecting portion is provided on a tubular portion continuously extending inward of the clutch from an inner peripheral side of the input side member. 6. The rotating device with a clutch according to claim 4, wherein the connecting portion is provided with at least one flat portion which is fitted in a plane with the output shaft of the speed reducer. 7. The locking means of the reverse input prevention clutch is provided on the output side member and the circumferential surface provided on the stationary side member, and forms a wedge gap between the circumferential surface and the circumferential surface in both forward and reverse rotation directions. The cam surface, the pair of engagement elements interposed between the cam surface and the circumferential surface, and the elastic members that press the pair of engagement elements in the direction of the wedge gap, respectively. The torque transmitting means is an engaging element that selectively engages with either one of the mates and presses it in the direction opposite to the direction of the wedge gap. The torque transmitting means is provided on the input side member and the output side member. An engaging element in the rotational direction, and in the neutral position of the unlocking means and the torque transmitting means, a rotational gap δ1 between the engaging element of the unlocking means and the engaging element, and the engaging element of the torque transmitting means. The rotational gap δ2 between them has a relationship of δ1 <δ2. Clutched rotating apparatus according to claim 1 or 2 wherein the.