JP7028576B2 - Reverse input cutoff device - Google Patents

Description

The present invention relates to a reverse input cutoff device having a function of transmitting a rotational torque input from an input shaft to an output shaft while cutting off a rotary torque reversely input from the output shaft.

For example, in a device such as a drive device for an electric shutter, which transmits a rotational torque in the forward and reverse directions input from a drive motor to an opening / closing mechanism on the output side to open / close the shutter, the shutter is opened / closed when the drive motor is stopped. A function of holding the shutter position so that the position does not change may be required.

In other words, if the drive motor stops due to some reason (power failure, etc.) during the opening / closing operation of the shutter, the drive motor will be damaged if the rotational torque that is reversely input due to the lowering of the shutter's own weight returns to the drive motor on the input side. May occur.

Therefore, a mechanism that holds the position of the shutter and does not return the rotational torque that is reversely input due to the lowering of the shutter's own weight to the drive motor on the input side is required.

The present applicant has disclosed in Patent Document 1 as a reverse input blocking device having a function of transmitting a rotational torque input from an input member to an output member while blocking a rotational torque reversely input from the output member. I'm proposing things first.

The reverse input blocking device disclosed in Patent Document 1 has a structure in which a clutch portion using a roller and an elastic member is arranged between an input member and an output member.

This clutch portion engages and disengages the roller in the wedge gap formed between the above-mentioned input member and the output member, thereby transmitting the rotational torque input from the input member and back-inputting the output member. It is configured to control the cutoff of rotational torque.

Japanese Unexamined Patent Publication No. 2002-266902

By the way, in the conventional reverse input blocking device disclosed in Patent Document 1, a lubricating oil such as grease is applied to a sliding portion of each component including an input member, an output member and a roller.

In the reverse input cutoff device in which lubricating oil is applied to the sliding portion of each component, the forward rotation torque and the reverse rotation torque may be alternately and continuously input to the output member.

At this time, the contact position of the roller up to the wedge gap between the output member and the stationary member is slightly displaced by the oil film, and the output member, the stationary member, the roller, and the elastic member to which the rotational torque is applied have a hysteresis of elastic deformation. Therefore, the output member will gradually rotate. As a result, a phenomenon occurs in which the lock position of the output member is slightly changed.

Therefore, the present invention has been proposed in view of the above-mentioned problems, and an object thereof is to ensure that the output member is reliably input even if rotational torques in the forward and reverse directions are alternately and continuously input back to the output member. It is an object of the present invention to provide a reverse input blocking device having a structure that can be locked.

The reverse input cutoff device according to the present invention includes an input member, an output member coaxially opposed to the input member, a stationary member that rotatably supports the input member and the output member, and an input member and an output member. It is provided with a structure including a clutch member arranged so as to be movable in the axial direction between the two.

As a technical means for achieving the above-mentioned object, the present invention provides a concavo-convex fitting portion that can be meshed in the rotational direction between the clutch member and the stationary member, and also provides a clutch between the input member and the clutch member. A cam portion for moving the member in the axial direction is provided, and the engagement and disengagement of the uneven fitting portion can be controlled by the axial movement of the clutch member by the cam portion.

In the reverse input blocking device of the present invention, a concave-convex fitting portion that can be meshed in the rotational direction is provided between the clutch member and the stationary member, and a cam portion that moves the clutch member axially between the input member and the clutch member. It is provided with a structure provided with.

With this structure, when the output member is locked, the rotational torque reversely input from the output member can be cut off by the meshing of the uneven fitting portion in the rotational direction due to the axial movement of the clutch member by the cam portion.

As a result, even if the rotation torque in the forward direction and the rotation torque in the reverse direction are alternately and continuously input to the output member, the output member is securely locked by the fitting force in the rotation direction at the uneven fitting portion. can do.

The uneven fitting portion in the present invention is composed of a gear portion provided on a part of the clutch member and a gear portion provided on a part of the stationary member, and includes a gear portion of the clutch member and a gear portion of the stationary member. It is desirable to have a structure that allows meshing in the direction of rotation.

If such a structure is adopted, even if the rotational torque in the forward direction and the rotational torque in the reverse direction are alternately and continuously input to the output member, the gear portion of the clutch member and the gear portion of the stationary member are firmly connected. The output member can be locked more reliably with a flexible fitting force.

The cam portion in the present invention is composed of a cam surface provided on the input member and inclined with respect to the rotation direction and a cam surface provided on the clutch member and inclined with respect to the rotation direction. It is desirable to have a structure in which the rotation of the input member can be converted into the axial movement of the clutch member by sliding contact with the cam surface of the clutch member.

If such a structure is adopted, the clutch member can be moved in the axial direction by the sliding contact between the cam surface of the input member and the cam surface of the clutch member, and the locked state of the output member can be easily released.

In the cam portion of the present invention, a torque transmission portion is extended at one end of either the cam surface of the input member or the cam surface of the clutch member so that the input shaft and the clutch member abut in the rotational direction so as to be able to transmit torque. The structure is desirable.

If such a structure is adopted, after the locked state of the output member is released by the axial movement of the clutch member, the rotational torque from the input member is output via the torque transmission unit by the contact between the input member and the clutch member. It can be easily transmitted to the member.

It is desirable that the clutch member in the present invention is composed of a plate-shaped portion on which a gear portion and a cam surface are formed, and a cylindrical portion integrally extending in the axial direction from the inner circumference of the plate-shaped portion.

If such a structure is adopted, since the tubular portion of the clutch member is extrapolated to the output member, it is possible to prevent the clutch member from tilting with respect to the output member when the clutch member is moved in the axial direction.

In the present invention, it is desirable to have a structure in which a concave-convex fitting portion that meshes in the rotational direction is provided between the tubular portion of the clutch member and the output member.

If such a structure is adopted, the clutch member can be moved in the axial direction, and the uneven fitting portion functions as a detent mechanism.

According to the present invention, when the output member is locked, the rotational torque reversely input from the output member can be cut off by the meshing of the uneven fitting portion in the rotational direction due to the axial movement of the clutch member by the cam portion.

In this way, by providing the uneven fitting portion that can be meshed in the rotational direction between the clutch member and the stationary member, the output member is in a state where the rotational torque in the forward direction and the rotational torque in the reverse direction are alternately continuous. Even if the input is reversed, the output member can be reliably locked by the fitting force in the rotational direction at the uneven fitting portion.

In the embodiment of the present invention, the overall configuration of the reverse input cutoff device is shown, and is a cross-sectional view taken along the line QQ of FIG. It is sectional drawing which follows the PP line of FIG. It is a perspective view which looked at the reverse input cutoff device from the input shaft side. It is a side view which looked at the reverse input cutoff device from the input shaft side. It is a side view which looked at the reverse input cutoff device from the output shaft side. It is a perspective view which shows the input axis. It is sectional drawing which shows the input axis. It is a perspective view which shows the output shaft. It is a perspective view which shows the case. It is a perspective view which shows the clutch plate. It is a perspective view which shows the state which the output shaft and the clutch plate are assembled to the case. It is a partially enlarged sectional view which shows the state which the cam surface of a clutch plate is in contact with the cam surface of an input shaft. It is a partially enlarged sectional view which shows the other structural example of a cam part. It is a partially enlarged sectional view which shows the other structural example of a cam part. It is a perspective view which shows the other structural example of the torque transmission part in an input shaft. It is a perspective view which shows the other structural example of the torque transmission part in a clutch plate. It is a perspective view which shows the state which the input shaft of FIG. 15 and the clutch plate of FIG. 16 are assembled. It is sectional drawing which shows the whole structure of the reverse input cutoff device in another structural example of a clutch plate. It is sectional drawing which shows the whole structure of the reverse input cutoff device in another structural example of a clutch plate. It is sectional drawing which follows the RR line of FIG. 18 and the SS line of FIG.

An embodiment of the reverse input blocking device according to the present invention will be described in detail below with reference to the drawings.

1 is a cross-sectional view showing the overall configuration of the reverse input cutoff device, FIG. 2 is a cross-sectional view taken along the line PP of FIG. 1, FIG. 3 is a perspective view of the reverse input cutoff device as viewed from the input shaft side, and FIG. 4 is a perspective view. FIG. 5 is a side view of the reverse input cutoff device as viewed from the input shaft side, and FIG. 5 is a side view of the reverse input cutoff device as viewed from the output shaft side.

As shown in FIGS. 1 to 5, the reverse input cutoff device of this embodiment is an input shaft 11 which is an input member, an output shaft 12 which is an output member, a case 13 which is a stationary member, and a clutch member. A main part is composed of a clutch plate 14 and a side plate 15.

As shown in FIGS. 6 and 7, the input shaft 11 is composed of a shaft portion 16 and a flange portion 17 integrally formed at the output side end portion of the shaft portion 16. Further, a recess 18 into which the input shaft side end portion of the shaft portion 19 of the output shaft 12 is fitted is formed in the central portion of the output side end surface of the input shaft 11 (see FIG. 1).

As shown in FIG. 8, the output shaft 12 is integrated with the shaft portion 19, the large-diameter portion 20 integrally formed at the substantially central portion of the shaft portion 19, and the input shaft side of the large-diameter portion 20. A main portion is composed of a flange portion 21 formed in the above portion and a pinion gear portion 22 (see FIGS. 1 and 5) formed coaxially with the large diameter portion 20.

As shown in FIG. 1, the case 13 houses a main portion including a flange portion 17 of the input shaft 11, a shaft portion 19 and a flange portion 21 of the output shaft 12, and a clutch plate 14. The shaft portion 16 of the input shaft 11 is derived from the input side opening hole 23 of the case 13. The input shaft 11 is supported so as to be rotatable forward and backward with respect to the case 13.

On the other hand, the output side opening 24 of the case 13 is closed by the side plate 15. Claw portions 25 extending in the axial direction are provided at a plurality of locations (three locations in the figure) on the outer periphery of the side plate 15 (see FIG. 3). As shown in FIG. 9, a concave groove 26 is formed on the outer peripheral surface of the case 13 with respect to the claw portion 25 (see FIGS. 2 to 5).

By fitting the claw portion 25 of the side plate 15 into the concave groove 26 of the case 13 and crimping the claw portion 25 so as to widen the bifurcated tip portion (see FIG. 3), the side plate 15 is attached to the case 13. It is attached and fixed. The output shaft 12 is supported so as to be rotatable forward and backward with respect to the side plate 15.

A friction ring 27 for imparting rotational resistance to the output shaft 12 is attached to the side plate 15 (see FIG. 1). The friction ring 27 is in sliding contact with the end surface of the flange portion 21 of the output shaft 12, and the frictional force imparts rotational resistance to the output shaft 12.

A clutch plate 14 is arranged so as to be movable in the axial direction between the flange portion 17 of the input shaft 11 and the flange portion 21 of the output shaft 12 (see FIG. 1). As shown in FIG. 10, the clutch plate 14 has a shaft hole 28 through which the shaft portion 19 of the output shaft 12 is inserted in the central portion thereof. The clutch plate 14 is elastically pressed toward the input shaft 11 by a wave spring 29 interposed between the output shaft 12 and the flange portion 21 (see FIG. 1).

The clutch plate 14 can be formed of a metal material and a resin material. When using a metal material, carburizing material is effective. Further, as a means for elastically pressing the clutch plate 14 toward the input shaft 11, other elastic members such as a disc spring and a coil spring can be used in addition to the above-mentioned wave spring 29.

A key groove 30 is formed on the inner peripheral surface of the shaft hole 28 of the clutch plate 14. Further, a key groove 31 is formed on the outer peripheral surface of the shaft portion 19 of the output shaft 12 (see FIG. 8). As shown in FIG. 11, by fitting the key 32 into the key groove 30 of the clutch plate 14 and the key groove 31 of the output shaft 12, the relative rotation between the clutch plate 14 and the output shaft 12 becomes impossible. ing. On the other hand, the clutch plate 14 can move in the axial direction along the key 32 with respect to the output shaft 12.

A cam portion 33 for moving the clutch plate 14 in the axial direction is provided between the input shaft 11 and the clutch plate 14 (see FIG. 2). The cam portion 33 includes a cam surface 34 provided on the input shaft 11 (see FIGS. 6 and 7) and a cam surface 35 provided on the clutch plate 14 (see FIG. 10). As shown in FIG. 12, the cam surface 34 of the input shaft 11 and the cam surface 35 of the clutch member 14 can be slidably contacted with each other.

An arcuate protruding wall portion 36 is integrally formed on the end surface of the flange portion 17 of the input shaft 11, and the cam surface 34 is formed at the circumferential end portion of the protruding wall portion 36 so as to be inclined with respect to the rotation direction. (See FIGS. 6 and 7). The cam surface 34 is provided at two peripheral end portions of the protrusion 36 of the input shaft 11 in order to correspond to the forward rotation and the reverse rotation.

On the other hand, an arcuate notch 37 is formed on the outer periphery of the clutch plate 14, and the cam surface 35 is formed so as to be inclined with respect to the rotation direction at the circumferential end of the notch 37 (FIG. 2 and FIG. See FIG. 10). The cam surface 35 is also provided at two peripheral end portions of the notch 37 of the clutch plate 14 in order to correspond to the forward rotation and the reverse rotation.

An uneven fitting portion 38 that can be meshed in the rotational direction is provided between the clutch plate 14 and the case 13. The uneven fitting portion 38 is composed of a gear portion 39 provided on the clutch plate 14 (see FIG. 10) and a gear portion 40 provided on the case 13 (see FIG. 9). The gear portion 39 of the clutch plate 14 and the gear portion 40 of the case 13 can be engaged (see FIG. 11).

The gear portion 39 is formed on the outer periphery of the clutch plate 14 (see FIG. 10). The outer side of the gear portion 39 in the circumferential direction is designated as a guide surface 41, and the guide surface 41 is in sliding contact with the inner peripheral surface of the case 13 to guide the axial movement of the clutch plate 14 (see FIG. 11). The gear portion 40 is formed in a partial phase of the inner peripheral surface of the case 13 (see FIG. 9).

A torque transmission portion 42 is provided at the end of the cam surface 34 of the input shaft 11 and the end of the notch 37 of the clutch plate 14 (see FIG. 2). As shown in FIGS. 6 and 7, the torque transmission unit 42 extends the cam surface 34 of the input shaft 11 in the circumferential direction, and has an upright surface 43 formed along the axial direction and a notch of the clutch plate 14. It is composed of a peripheral end portion 44 of the portion 37 (see FIG. 12).

The upright surface 43 of the input shaft 11 abuts in the rotational direction on the circumferential end 44 of the notch 37 of the clutch plate 14, so that the rotational torque from the input shaft 11 can be transmitted to the clutch plate 14. ..

An operation example of the reverse input cutoff device having the above configuration will be described in detail below.

When the rotational torque reversely input from the output shaft 12 is cut off, the clutch plate 14 is pressed toward the input shaft 11 by the elastic force of the wave spring 29 interposed between the output shaft 12 and the clutch plate 14. ..

In this state, the gear portion 39 of the clutch plate 14 and the gear portion 40 of the case 13 which is a stationary system are in mesh with each other in the uneven fitting portion 38 (see FIG. 2). The clutch plate 14 is locked by the engagement between the gear portion 39 of the clutch plate 14 and the gear portion 40 of the case 13.

That is, the output shaft 12 that is key-fitted with the clutch plate 14 is also locked. Due to the locked state of the clutch plate 14 and the output shaft 12, the rotational torque reversely input from the output shaft 12 is not transmitted to the input shaft 11.

Here, even if the forward rotation torque and the reverse rotation torque are alternately and continuously input to the output shaft 12, the gear portion 39 of the clutch plate 14 and the gear portion 40 of the case 13 are firmly fitted. The output shaft 12 can be reliably locked by the resultant force.

Next, when the rotational torque that is reversely input from the output shaft 12 disappears and the rotational torque is input from the input shaft 11, the clutch plate 14 is rotated by the cam portion 33 between the input shaft 11 and the clutch plate 14. Axial movement to the 12 side.

That is, in the cam portion 33, the cam surface 34 of the protruding wall portion 36 of the input shaft 11 and the cam surface 35 of the recess 37 of the clutch plate 14 come into contact with each other, and the cam surface 34 of the input shaft 11 is the cam surface 35 of the clutch plate 14. (See FIG. 12).

When the pressing force on the clutch plate 14 overcomes the elastic force of the wave spring 29, the cam surface 35 of the clutch plate 14 is in sliding contact with the cam surface 34 of the input shaft 11 due to the rotation of the input shaft 11, so that the input shaft 11 The rotation of the clutch plate 14 is converted into the axial movement of the clutch plate 14 (see the arrow in FIG. 12).

When the clutch plate 14 is moved in the axial direction, the guide surface 41 of the clutch plate 14 is in sliding contact with the inner peripheral surface of the case 13. The clutch plate 14 moves smoothly in the axial direction by the guide provided by the guide surface 41. As a result, the gear portion 39 of the clutch plate 14 is disengaged from the gear portion 40 of the case 13. When the gear portion 39 of the clutch plate 14 is disengaged from the gear portion 40 of the case 13, the locked state of the clutch plate 14 and the output shaft 12 is released.

When the output shaft 12 is unlocked, the friction ring 27 imparts appropriate rotational resistance to the output shaft 12. By applying rotational resistance to the output shaft 12, the input shaft 11 rotates slightly with respect to the clutch plate 14, so that in the torque transmission unit 42, the upright surface 43 of the protrusion 36 of the input shaft 11 is the clutch plate 14. It abuts on the circumferential end 44 of the notch 37.

The upright surface 43 of the protruding wall portion 36 of the input shaft 11 comes into contact with the circumferential end portion 44 of the notch portion 37 of the clutch plate 14, so that the rotational torque from the input shaft 11 is the protruding wall portion 36 of the input shaft 11. The output shaft 12 is transmitted to the output shaft 12 via the peripheral end portion 44 of the upright surface 43 and the notch portion 37 of the clutch plate 14, that is, the torque transmission portion 42, and the output shaft 12 rotates in the same direction as the input shaft 11.

In the embodiment described above, as shown in FIG. 12, the cam portion 33 composed of the cam surface 34 of the protruding wall portion 36 of the input shaft 11 and the cam surface 35 of the clutch plate 14 is exemplified. The present invention is not limited to this, and as shown in FIG. 13, the cam portion 54 can be configured by the cam surface 51 of the input shaft 11 and the cam surface 53 of the protruding wall portion 52 of the clutch plate 14. be.

Further, as shown in FIG. 14, a cam groove 55 is formed on the input shaft 11 and a cam groove 56 is formed on the clutch plate 14, between the cam groove 55 of the input shaft 11 and the cam groove 56 of the clutch plate 14. It is also possible to form the cam portion 58 by interposing the ball 57. It is also possible to use a roller other than the ball 57.

Further, in the above embodiment, the torque transmission portion 42 composed of the upright surface 43 of the protruding wall portion 36 of the input shaft 11 and the circumferential end portion 44 of the notch portion 37 of the clutch plate 14 is exemplified. The torque transmission unit 62 may have a structure as shown in FIGS. 15 to 17.

That is, as shown in FIG. 15, two pins 59 are projected in the axial direction on the flange portion 17 of the input shaft 11, and as shown in FIG. 16, the pin 59 of the input shaft 11 is inserted into the clutch plate 14. The two elongated holes 60 to be formed are formed along the circumferential direction.

As shown in FIG. 17, the torque transmission portion 62 can be configured by allowing the pin 59 of the flange portion 17 of the input shaft 11 to come into contact with the circumferential end surface 61 of the elongated hole 60 of the clutch plate 14. .. The number of pins 59 and the elongated holes 60 may be other than two, and the number and position thereof are arbitrary.

In the above embodiment, the substantially disk-shaped clutch plate 14 (see FIG. 10) is exemplified as the clutch member, but the clutch plate 14 may have a structure as shown in FIGS. 18 to 20 as the clutch member. In FIGS. 18 to 20, the same parts as those in FIGS. 1 and 2 are designated by the same reference numerals, and duplicate description will be omitted.

The clutch plate 14 of the embodiment shown in FIGS. 18 and 19 has a cylindrical portion 63 in which a gear portion 39 and a cam surface 35 are formed, and a cylindrical portion that extends axially from the inner circumference of the plate-shaped portion 63. It is composed of a part 64. The tubular portion 64 of the clutch plate 14 is extrapolated to the shaft portion 19 of the output shaft 12.

The tubular portion 64 of the clutch plate 14 of the embodiment shown in FIG. 18 is formed so as to extend from the inner circumference of the plate-shaped portion 63 toward the output shaft 12. An annular groove 65 is formed in the flange portion 21 of the output shaft 12 so that the output shaft side end portion of the tubular portion 64 of the clutch plate 14 can be inserted.

In the reverse input cutoff device of this embodiment, when the output shaft 12 is unlocked, the output shaft side end portion of the tubular portion 64 of the clutch plate 14 enters the annular concave groove 65 of the output shaft 12, whereby the clutch plate 14 Axial movement is possible.

The tubular portion 64 of the clutch plate 14 of the embodiment shown in FIG. 19 is formed so as to extend from the inner circumference of the plate-shaped portion 63 toward the input shaft 11. An annular groove 66 is formed in the flange portion 17 of the input shaft 11 so that the input shaft side end portion of the tubular portion 64 of the clutch plate 14 can be inserted.

In the reverse input cutoff device of this embodiment, when the output shaft 12 is locked, the input shaft side end portion of the tubular portion 64 of the clutch plate 14 enters the annular concave groove 66 of the input shaft 11, whereby the shaft of the clutch plate 14 is inserted. Directional movement is possible.

In the embodiment shown in FIGS. 18 and 19, the clutch plate 14 has a tubular portion 64, so that the tubular portion 64 of the clutch plate 14 is extrapolated to the shaft portion 19 of the output shaft 12. Therefore, it is possible to prevent the plate-shaped portion 63 of the clutch plate 14 from tilting with respect to the case 13 when the clutch plate 14 moves in the axial direction.

As a result, when the output shaft 12 is unlocked, the gear portion 39 of the clutch plate 14 is smoothly disengaged from the gear portion 40 of the case 13 due to the axial movement of the clutch plate 14. Further, when the output shaft 12 is locked, the gear portion 39 of the clutch plate 14 smoothly meshes with the gear portion 40 of the case 13 due to the axial movement of the clutch plate 14.

In the reverse input cutoff device of the embodiment shown in FIGS. 18 and 19, as shown in FIG. 20, uneven fitting that meshes in the rotational direction between the tubular portion 64 of the clutch plate 14 and the shaft portion 19 of the output shaft 12. A joint 67 is provided.

The uneven fitting portion 67 is composed of a spline 68 formed on the inner peripheral surface of the tubular portion 64 of the clutch plate 14 and a spline 69 formed on the outer peripheral surface of the shaft portion 19 of the output shaft 12 (FIG. FIG. 18 and FIG. 19), the structure is provided in which both splines 68 and 69 are fitted.

The uneven fitting portion 67 by spline fitting prevents the clutch plate 14 from rotating with respect to the output shaft 12 as an alternative to the rotation prevention mechanism by key fitting adopted in the reverse input blocking device of the embodiment shown in FIG. Has the function of

In the uneven fitting portion 67, the spline 68 of the tubular portion 64 of the clutch plate 14 and the spline 69 of the shaft portion 19 of the output shaft 12 are in a meshed state. The spline fitting between the tubular portion 64 of the clutch plate 14 and the shaft portion 19 of the output shaft 12 enables the clutch plate 14 to move in the axial direction and functions as a detent mechanism.

That is, the spline 68 of the clutch plate 14 and the spline 69 of the output shaft 12 are fitted to each other, so that the relative rotation between the clutch plate 14 and the output shaft 12 becomes impossible. On the other hand, the clutch plate 14 can move in the axial direction along the splines 68 and 69 with respect to the output shaft 12.

The configuration and operation of the clutch plate 14 other than the tubular portion 64 and the concave-convex fitting portion 67 in the reverse input cutoff device of the embodiment shown in FIGS. 18 to 20 and the operation example of the reverse input cutoff device are shown in FIGS. 1 and 20. Since it is the same as the case of the embodiment shown in FIG. 2, duplicate description will be omitted.

The present invention is not limited to the above-described embodiments, and it is needless to say that the present invention can be carried out in various forms without departing from the gist of the present invention. Indicated by the scope of the claim and further include the equal meanings set forth in the claims, and all modifications within the scope.

11 Input member (input shaft)
12 Output member (output shaft)
13 Stationary member (case)
14 Clutch member (clutch plate)
33 Cam part 34,35 Cam surface 38 Concavo-convex fitting part 39,40 Gear part 42 Torque transmission part 63 Plate-shaped part 64 Cylindrical part 67 Concavo-convex fitting part

Claims (6)

An input member, an output member coaxially arranged to face the input member, a stationary member that rotatably supports the input member and the output member, and an axially movable arrangement between the input member and the output member. Equipped with a clutch member
An uneven fitting portion having a pair of gear portions that can be meshed in the rotational direction is provided between the clutch member and the stationary member, and the clutch member is axially moved between the input member and the clutch member. A cam portion is provided, and the meshing and disengagement of the uneven fitting portion can be controlled by the axial movement of the clutch member by the cam portion.
One gear portion and an arcuate notch portion of the uneven fitting portion are provided at different positions in the circumferential direction of the outer peripheral surface of the clutch member, and the arcuate notch portion of the clutch member is provided at the circumferential end portion of the arcuate notch portion. A reverse input cutoff device characterized in that a cam surface of the cam portion is provided, and a cam surface of the cam portion and one gear portion of the uneven matching portion are provided at the same axial position. The reverse input blocking device according to claim 1, wherein the outer peripheral surface of the clutch member is provided with a guide surface that is in sliding contact with the inner peripheral surface of the stationary member . The cam portion is composed of a cam surface provided on the input member and inclined with respect to the rotation direction and a cam surface provided on the clutch member and inclined with respect to the rotation direction, and the cam surface of the input member and the clutch. The reverse input blocking device according to claim 1 or 2, wherein the rotation of the input member can be converted into axial movement of the clutch member by sliding contact of the member with the cam surface. The third aspect of claim 3, wherein a torque transmission portion is extended at one end of either the cam surface of the input member or the cam surface of the clutch member so that the input member and the clutch member are in contact with each other in the rotational direction so as to be able to transmit torque. Reverse input cutoff device. The clutch member is any of claims 1 to 4, wherein the clutch member includes a plate-shaped portion on which a gear portion and a cam surface are formed, and a cylindrical portion integrally extending in the axial direction from the inner circumference of the plate-shaped portion. The reverse input blocking device described in item 1. The reverse input cutoff device according to claim 5, wherein an uneven fitting portion that meshes in the rotational direction is provided between the tubular portion of the clutch member and the output member.

Images