JP2017032007A - Reverse input cutoff clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To release residual torque applied to an input outer ring by simple means, in stopping input of rotation torque.SOLUTION: A reverse input cutoff clutch includes an input outer ring 11 to which rotation torque is input, an output shaft 12 from which the rotation torque is output, a side plate 13 restricted in rotation, a plurality of cylindrical rollers 16 controlling cutoff of rotation torque reversely input from the output shaft 12 and transmission of rotation torque input from the input outer ring 11 by engagement and disengagement between the input outer ring 11 and the output shaft 12, and retainers 17 for retaining the cylindrical rollers 16 between the input outer ring 11 and the output shaft 12, and further includes a friction plate 45 slidably rotatably disposed to the side plate 13, and a return spring 46 disposed between the input outer ring 11 and the friction plate 45. The return spring 46 is elastically deformed by rotation of the input outer ring 11 to the friction plate 45, the friction plate 45 is rotated to the side plate 13 integrally with the input outer ring 11 in a state that the elastic deformation of the return spring 46 is kept, and the input outer ring 11 is reversely rotated by elastic restoring force of the return spring 46 in stopping input of the rotation torque from the input outer ring 11.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a reverse input cutoff clutch having a function of blocking rotational torque input from an output side member while transmitting rotational torque input from an input side member to an output side member.

  For example, as a device that performs the required operation by transmitting the rotational torque input from the drive source to the output side mechanism, the door opening / closing operation is performed by inputting the rotational torque in the forward / reverse direction from the drive motor to the output side opening / closing mechanism. There are an electric slide door device and an electric back door device for performing the above.

  In this type of device, if the drive motor stops due to some reason during the door opening / closing operation, if the rotational torque reversely input from the output side opening / closing mechanism returns to the input side, the input side equipment is damaged. there is a possibility. Therefore, a mechanism having a function of preventing the rotational torque reversely input from the output-side opening / closing mechanism from returning to the input side is required.

  The applicant applies reverse input as a mechanism having a function of transmitting rotational torque input from the input side member to the output side member while blocking rotational torque input from the output side member by idling of the output side member. A shut-off clutch has been proposed previously (see, for example, Patent Document 1).

  As shown in FIG. 7 and FIG. 8, the reverse input cutoff clutch disclosed in Patent Document 1 has an input outer ring 111 to which rotational torque is input, an output shaft 112 to which rotational torque is output, and rotation restricted. By the engagement and disengagement of the side plate 113 and the cover 114, and the wedge clearance 115 formed between the input outer ring 111 and the output shaft 112, the rotational torque reversely input from the output shaft 112 and the input from the input outer ring 111 are input. A plurality of cylindrical rollers 116 that control transmission of rotational torque and a retainer 117 that holds the cylindrical rollers 116 between the input outer ring 111 and the output shaft 112 constitute a main part.

  The reverse input shut-off clutch is provided between the input outer ring 111 and the retainer 117, in addition to the input outer ring 111, the output shaft 112, the side plate 113, the cover 114, the cylindrical roller 116, and the retainer 117 that constitute the main part. And a centering spring 137 and a sliding spring 138 provided between the cage 117 and the cover 114.

  The centering spring 137 has a function of releasing the cylindrical roller 116 from the engaged state at the wedge clearance 115 and returning it to the center position in order to block the rotational torque reversely input from the output shaft 112 by idling of the output shaft 112. The sliding spring 138 has a function of imparting rotational resistance to the cage 117 by sliding with respect to the cover 114 when transmitting the rotational torque input from the input outer ring 111 to the output shaft 112.

  In the reverse input cutoff clutch having the above-described configuration, when rotational torque is input from the input outer ring 111, a cage that receives rotational resistance from the input outer ring 111 and a sliding spring 138 that slides against the cover 114. The centering spring 137 is elastically deformed between Due to the elastic deformation of the centering spring 137, the rotation of the retainer 117 is delayed and a rotational phase difference with the input outer ring 111 is generated.

  As a result, the cylindrical roller 116 relatively moves in the circumferential direction in the wedge clearance 115 between the input outer ring 111 and the output shaft 112 and engages with the wedge clearance 115. Due to the engagement of the cylindrical rollers 116, the rotational torque input from the input outer ring 111 is transmitted to the output shaft 112.

  When the input of the rotational torque from the input outer ring 111 is stopped, the input outer ring 111 is reversely rotated by the elastic restoring force of the centering spring 137 to a position where the rotational phase difference from the cage 117 is eliminated. As a result, the cylindrical roller 116 disengages from the wedge clearance 115 between the input outer ring 111 and the output shaft 112 and returns to the center position of the wedge clearance 115.

  When rotational torque is reversely input from the output shaft 112, the cylindrical roller 116 positioned at the center of the wedge clearance 115 between the output shaft 112 and the input outer ring 111 is held in a state of being detached from the output shaft 112 and the input outer ring 111. Therefore, the output shaft 112 is idled so that the rotational torque from the output shaft 112 is cut off so as not to return to the input outer ring 111.

JP 2009-21004 A

  By the way, as described above, the conventional reverse input shut-off clutch disclosed in Patent Document 1 is incorporated in an electric slide door device or an electric back door device, and receives rotational torque reversely input from an output-side opening / closing mechanism on the input side. The drive motor has a function not to be refluxed.

  In such a reverse input shut-off clutch, for example, as indicated by the solid line arrow in FIG. 8, when a clockwise rotational torque is input to the input outer ring 111, it is input from the input outer ring 111 due to the engagement of the cylindrical rollers 116. Is transmitted to the output shaft 112, and the output shaft 112 rotates in the clockwise direction.

  On the other hand, even if the input of the rotational torque from the input outer ring 111 is stopped, residual torque remains in the input outer ring 111 in the torque transmission state with the output shaft 112 connected to, for example, the output side opening / closing mechanism comprising a hydraulic system. There may be. This residual torque is a large torque based on, for example, a hydraulic system. When the residual torque is applied to the input outer ring 111, the elastic restoring force of the centering spring 137 is insufficient as the torque necessary to release the cylindrical roller 116 engaged with the wedge clearance 115.

  For this reason, it is difficult to reversely rotate the input outer ring 111 to a position where the rotational phase difference from the cage 117 is eliminated, and the cylindrical roller 116 remains engaged with the wedge clearance 115. If counterclockwise rotational torque is reversely input to the output shaft 112 in this state, the input outer ring 111 may also rotate with the output shaft 112 even if the drive motor is stopped.

  That is, if the residual torque as described above remains, when the rotational torque from the output shaft 112 is reversely input, the output shaft 112 does not idle and it is difficult to block the rotational torque from the output shaft 112. This may return to the input outer ring 111 and damage input side devices such as a drive motor.

  In order to solve such a problem, it is conceivable to provide means for reversely rotating the input outer ring 111 with an input side device such as a drive motor. However, when such a means is adopted, since reverse rotation control is required to reversely rotate the input outer ring 111 by the input side device, there arises a problem that the equipment cost for realizing the reverse rotation control increases.

  Accordingly, the present invention has been proposed in view of the above-described improvements, and the object of the present invention is to release the residual torque applied to the input outer ring by simple means when the input of the rotational torque from the input outer ring is stopped. An object of the present invention is to provide a reverse input cutoff clutch that can be used.

  The reverse input cutoff clutch according to the present invention includes an input side member to which rotational torque is input, an output side member to which rotational torque is output, a stationary side member to which rotation is constrained, an input side member, and an output side member. A plurality of engagement elements for controlling the interruption of the rotational torque input from the output side member and the transmission of the rotational torque input from the input side member by the engagement and disengagement between the input side member and the output side It is premised on a structure including a retainer that holds an engagement member with a member.

  As technical means for achieving the above-described object, the present invention provides a braking member that is slidably and rotatably attached to a stationary side member, and an elastic member provided between the input side member and the braking member. The elastic member is elastically deformed by the rotation of the input side member with respect to the braking member, and the braking member is rotated integrally with the input side member with respect to the stationary side member while maintaining the elastic deformation of the elastic member. The input side member is reversely rotated by the elastic restoring force of the elastic member when the input of the rotational torque from the side member is stopped.

  In the present invention, after the rotational torque input from the input side member is transmitted to the output side member, when the input of the rotational torque from the input side member is stopped, the residual torque from the output side member is loaded on the input side member. However, the residual torque can be easily released by reverse rotation of the input side member by the elastic member.

  That is, when the rotational torque is transmitted from the input side member, the elastic member is elastically deformed by the rotation of the input side member with respect to the braking member, and the braking member is integrated with the input side member while maintaining the elastic deformation of the elastic member. Rotate relative to stationary member. Thereafter, when the input of the rotational torque from the input side member is stopped, the input side member is directly reversely rotated by the elastic restoring force of the elastic member. In this manner, the input side member can be easily rotated in the reverse direction by using the elastic member provided on the input side of the reverse input cutoff clutch.

  In the present invention, the elastic member has a C-shape and is a return spring having protrusions whose both ends are bent radially outward. The braking member has a ring shape, and the return spring protrusion is locked. It is desirable that the friction plate have a first protrusion that has a second protrusion that contacts the input-side member by rotation of the input-side member. Thus, if the elastic member is used as the return spring and the braking member is used as the friction plate, it is possible to easily realize a structure in which the input side member is directly reversely rotated on the input side of the reverse input cutoff clutch. it can.

  In the present invention, it is desirable that the restoring torque of the input side member and the braking member by the elastic member is set to be equal to or less than the sliding torque of the braking member with respect to the stationary side member. With such a configuration, when the rotational torque is transmitted from the input side member, the elastic member is elastically deformed by the rotation of the input side member with respect to the braking member, and the braking member is input while maintaining the elastic deformation of the elastic member. A series of operations of rotating with respect to the stationary side member integrally with the side member can be easily realized.

  According to the present invention, after the rotational torque input from the input side member is transmitted to the output side member, the residual torque from the output side member is loaded on the input side member when the input of the rotational torque from the input side member is stopped. However, the residual torque can be easily released by the reverse rotation of the input side member by the elastic member.

  As a result, when the rotational torque from the output side member is reversely input, the rotational torque from the output side member can be reliably cut off, so that damage to the input side device can be reliably prevented, and safety and reliability are improved. Can be planned. Moreover, since the reverse rotation control of the input side member by the input side device is not required, the equipment cost is not increased.

It is sectional drawing which shows the whole structure of a reverse input interruption | blocking clutch in embodiment of this invention. It is sectional drawing which follows the AA line of FIG. It is an assembly exploded perspective view showing the whole reverse input interception clutch composition. It is an expansion perspective view which shows an input outer ring | wheel, a return spring, and a friction board. It is sectional drawing which follows the BB line of FIG. FIG. 6 is a cross-sectional view showing a state where the input outer ring is rotated by an angle θ from the state of FIG. 5. It is sectional drawing which shows the whole structure of the conventional reverse input interruption | blocking clutch. It is sectional drawing which follows the CC line of FIG.

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

  In the following embodiments, a reverse input cutoff clutch incorporated in an electric slide door device or an electric back door device that performs door opening / closing operation by inputting rotational torque in the forward / reverse direction input from the drive motor to the output side opening / closing mechanism. Is illustrated. In addition, this reverse input interruption | blocking clutch is applicable also to various apparatuses other than an electric slide door apparatus and an electric back door apparatus.

  The reverse input cutoff clutch in this embodiment is of a type that transmits rotational torque input from the input side member to the output side member, while interrupting rotational torque input reversely from the output side member by idling of the output side member. It is.

  Before describing the characteristic configuration of this embodiment, the basic configuration as a premise of the reverse input cutoff clutch will be described in detail below with reference to FIGS. This basic configuration is the same as that of the conventional reverse input cutoff clutch shown in FIGS.

  As shown in FIGS. 1 to 4, the reverse input cutoff clutch includes an input outer ring 11 that is an input side member to which rotational torque is input, an output shaft 12 that is an output side member to which rotational torque is output, and rotation. Rotational torque that is reversely input from the output shaft 12 due to engagement and disengagement at the wedge plate 15 formed between the input outer ring 11 and the output shaft 12 and the side plate 13 and the cover 14 that are restrained stationary members. Cylindrical rollers 16 that are a plurality of engagement elements that control the interruption of the rotation and transmission of rotational torque input from the input outer ring 11, and a cage 17 that holds the cylindrical rollers 16 between the input outer ring 11 and the output shaft 12. The main part is composed of.

  The input outer ring 11 includes an input shaft portion 18 on which a motor shaft (not shown) of a drive motor that is a drive source is coaxially mounted, and a cylindrical shape that is integrally expanded from the input shaft portion 18. It is comprised with the outer ring | wheel part 19. FIG. The inner peripheral surface of the shaft hole 20 of the input shaft portion 18 is formed with a two-plane width composed of two parallel planes, and has a structure capable of transmitting torque with the motor shaft inserted into the shaft hole 20. . Cam surfaces 21 inclined in opposite directions are alternately provided on the inner peripheral surface of the outer ring portion 19 in the circumferential direction, and the wedge gradually narrows on both sides in the circumferential direction between the output shaft 12 and the arc-shaped outer peripheral surface 22. A plurality of gaps 15 are formed.

  The output shaft 12 includes a shaft portion 23 that is connected to an output-side opening / closing mechanism, and an inner ring portion 24 that is provided with an enlarged diameter integrally with the shaft portion 23. The outer peripheral surface of the shaft portion 23 has a two-plane width formed of two parallel planes, and has a structure capable of transmitting torque with an opening / closing mechanism that is inserted into the shaft portion 23. The arc-shaped outer peripheral surface 22 of the inner ring portion 24 and the cam surface 21 formed on the inner peripheral surface of the outer ring portion 19 of the input outer ring 11 constitute a plurality of wedge clearances 15.

  The cage 17 includes a flange portion 25 and a cylindrical portion 26 that extends integrally from the flange portion 25 in the axial direction. In the tubular portion 26, pockets 27 for accommodating the cylindrical rollers 16 are formed in a cutout shape at a plurality of locations in the circumferential direction. The cylindrical portion 26 is accommodated in the outer ring portion 19 of the input outer ring 11, and the inner ring portion 24 of the output shaft 12 is accommodated in the cylindrical portion 26, whereby the cam surface 21 of the input outer ring 11 and the outer periphery of the output shaft 12 are arranged. A cylindrical roller 16 is disposed in a wedge clearance 15 formed between the surface 22 and the surface 22. In this embodiment, the number of cylindrical rollers 16 is eight, but the number is arbitrary.

  The inner ring portion 24 of the output shaft 12 is provided with a hole 28 into which a cylindrical portion (not shown) at the tip of the motor shaft is fitted. As a result, the input outer ring 11 and the output shaft 12 can rotate about the same axis via the motor shaft.

  The side plate 13 has a disk shape, and integrally includes a cylindrical portion 29 protruding in the axial direction at a central portion thereof. In the cylindrical portion 29, the input shaft portion 18 of the input outer ring 11 is rotatably inserted. The outer peripheral edge of the side plate 13 is provided with three flange portions 30 extending outward in the radial direction and a plurality of claw portions 31 bent in the axial direction. The flange portion 30 is formed with an attachment hole 32 for an electric slide door device or an electric back door device. In this embodiment, the number of the flange portions 30 is three, but the number is arbitrary.

  The cover 14 has a cup shape, and includes a large diameter portion 33 in which the outer ring portion 19 of the input outer ring 11, the cage 17, the cylindrical roller 16 and the inner ring portion 24 of the output shaft 12 are accommodated, and the large diameter portion 33 extends in the axial direction. It is comprised by the small diameter part 34 extended integrally. A sintered oil-impregnated bearing 35 is fitted into the small diameter portion 34, and the shaft portion 23 of the output shaft 12 is rotatably supported by the sintered oil-impregnated bearing 35. A plurality of cutout recesses 36 are formed on the outer peripheral edge of the large diameter portion 33.

  The claw portion 31 of the side plate 13 has a bifurcated tip, and is inserted into a corresponding notch recess 36 of the large-diameter portion 33 of the cover 14, and the bifurcated tip protruding from the notch recess 36 is outward. The side plate 13 and the cover 14 are integrated by caulking. In this embodiment, the claw portions 31 of the side plate 13 are formed at two positions between the adjacent flange portions 30, and the number of the claw portions 31 is six in total. However, the number is arbitrary.

  This reverse input shut-off clutch is arranged between the input outer ring 11 and the cage 17 in addition to the input outer ring 11, the output shaft 12, the side plate 13, the cover 14, the cylindrical roller 16 and the cage 17 that constitute the main parts described above. A centering spring 37 provided and a sliding spring 38 disposed between the cage 17 and the cover 14 are provided.

  The centering spring 37 is a U-shaped leaf spring, and both end portions 39 thereof are inserted into the holes 40 of the outer ring portion 19 of the input outer ring 11, and the bent portion 41 is notched concave portion 42 of the cylindrical portion 26 of the cage 17. It is assembled by inserting it into. Thereby, the input outer ring 11 and the cage 17 are connected via the centering spring 37, and the cage 17 holds the cylindrical roller 16 at the center position of the wedge clearance 15. In this embodiment, the number of centering springs 37 is two, but the number is arbitrary.

  The sliding spring 38 is a C-shaped spring made of a wire having a circular cross section, and has a shape in which both end portions 43 are bent radially inward. The sliding spring 38 is disposed on the outer peripheral side of the flange portion 25 of the cage 17, and is assembled by inserting both end portions 43 into the cutout holes 44 of the flange portion 25 and engaging them in the circumferential direction. As a result, the sliding spring 38 is brought into contact with the inner end face of the large-diameter portion 33 of the cover 14, and the rotational resistance is applied to the cage 17 by sliding with respect to the cover 14 when rotating integrally with the cage 17. .

  The basic configuration as a premise of the reverse input cutoff clutch in this embodiment is as described above, and a characteristic configuration added to the basic configuration will be described in detail below.

  As shown in FIGS. 1, 3, and 4, the reverse input cutoff clutch of this embodiment includes a friction plate 45 that is a braking member that is slidably and rotatably attached to the side plate 13, and friction between the input outer ring 11 and the friction plate 45. A return spring 46, which is an elastic member, is provided between the plate 45 and the plate 45.

  The friction plate 45 is a ring-shaped band plate member. The friction plate 45 is formed with first protrusions 47 extending in the axial direction at two locations in the circumferential direction of the outer peripheral edge portion thereof, and extending in the axial direction at one circumferential position of the outer peripheral edge portion. Two protrusions 48 are formed. The second protrusion 48 is provided at a position 180 ° opposite to the circumferential center position between the two first protrusions 47.

  The friction plate 45 is fitted into the tubular portion 29 of the side plate 13 by fitting a wave spring 50 into the annular groove 49 of the tubular portion 29. Due to the spring load of the wave spring 50, the friction plate 45 is elastically pressed against the side plate 13 so as to be able to slide and rotate. In this embodiment, the wave spring 50 is illustrated as an attachment means for the friction plate 45, but another structure using a disc spring or the like may be used.

  The return spring 46 is a C-shaped elastic member made of a wire having a circular cross section, and has a pair of projecting pieces 51 whose both ends are bent outward in the radial direction. The return spring 46 is attached to a spring holding portion 52 provided on the axial end surface of the outer ring portion 19 of the input outer ring 11. The spring holding portion 52 is composed of an annular convex portion 53 that is integrally projected on the axial end surface of the outer ring portion 19. A concave groove 54 is formed on the inner peripheral end surface of the spring retaining portion 52, and notches 55 are formed in two circumferential directions. 56 is formed.

  The return spring 46 is attached to the spring holding portion 52 as follows. That is, as shown in FIG. 5, the return spring 46 is fitted into the groove 54 of the annular convex portion 53 of the outer ring portion 19, and the pair of projecting pieces 51 are disposed in the circumferentially outer side in one notch 55 of the annular convex portion 53. Fits in a position-controlled state. The tip end portion of the projecting piece 51 of the return spring 46 is inserted between the first projections 47 of the friction plate 45 arranged on the radially outer side of the notch 55 of the annular convex portion 53. The first protrusion 47 of the friction plate 45 abuts on the outer side in the circumferential direction of the protrusion 51 of the return spring 46.

  Thus, the friction plate 45 and the input outer ring 11 are centered by the return spring 46. Further, the second protrusion 48 of the friction plate 45 is disposed in the other notch 56 of the annular convex portion 53. In the centering state by the return spring 46, the second protrusion 48 of the friction plate 45 is disposed at the circumferential center position of the notch 56 of the annular convex portion 53.

  An example of operation of the reverse input cutoff clutch having the above basic configuration and characteristic configuration will be described in detail below.

  When rotational torque is input from the input outer ring 11 by the operation of the drive motor, in the basic configuration, the centering spring 37 is inserted into the hole 40 of the outer ring portion 19 of the input outer ring 11 and the notch recess 42 of the cylindrical portion 26 of the cage 17. Therefore, the centering spring 37 is elastically deformed between the input outer ring 11 and the cage 17 that receives rotational resistance from the sliding spring 38 that slides on the cover 14.

  Here, the sliding torque necessary for sliding the sliding spring 38 with respect to the cover 14 is set to be larger than the force necessary for elastically deforming the centering spring 37. Therefore, due to the elastic deformation of the centering spring 37, the rotation of the cage 17 is delayed with respect to the rotation of the input outer ring 11, and a rotational phase difference is generated between the cage 17 and the input outer ring 11.

  As a result, the cylindrical roller 16 relatively moves in the circumferential direction in the wedge clearance 15 between the input outer ring 11 and the output shaft 12 and engages with the wedge clearance 15. Due to the engagement of the cylindrical rollers 16, the rotational torque input from the input outer ring 11 is transmitted to the output shaft 12.

  Then, when the input of the rotational torque from the input outer ring 11 is stopped, the input outer ring 11 is reversely rotated to a position where the rotational phase difference from the cage 17 is eliminated by the elastic restoring force of the centering spring 37. As a result, the cylindrical roller 16 disengages from the wedge clearance 15 between the input outer ring 11 and the output shaft 12 and returns to the center position of the wedge clearance 15.

  On the other hand, when rotational torque is reversely input from the output shaft 12, the cylindrical roller 16 located at the center of the wedge clearance 15 between the output shaft 12 and the input outer ring 11 is detached from the output shaft 12 and the input outer ring 11. Since the output shaft 12 is held idle, the rotational torque from the output shaft 12 is cut off so as not to return to the input outer ring 11.

  In addition to the operation of the basic configuration described above, in the reverse input cutoff clutch of this embodiment, in the characteristic configuration, when the rotational torque is transmitted from the input outer ring 11, the return is caused by the rotation of the input outer ring 11 with respect to the friction plate 45. The spring 46 is elastically deformed. Since the rotational torque by the return spring 46 is set smaller than the sliding torque by the friction plate 45, only the input outer ring 11 with respect to the friction plate 45 and the side plate 13 until the input outer ring 11 rotates by the angle θ. Rotates.

  As shown in FIG. 6, when the input outer ring 11 rotates to the angle θ in the direction of the solid line in the figure, the second protrusion 48 of the friction plate 45 contacts the notch 56 of the input outer ring 11. Accordingly, when the input outer ring 11 rotates by an angle θ or more, the friction plate 45 also slides and rotates with respect to the side plate 13 as the input outer ring 11 rotates.

  In this way, the friction plate 45 rotates with respect to the side plate 13 integrally with the input outer ring 11 while maintaining the elastic deformation of the return spring 46. The friction plate 45 is necessary to rotate the input outer ring 11 by rotating the input outer ring 11 by an angle θ to elastically deform the return spring 46 and maintain the elastic deformation.

  After the rotational torque input from the input outer ring 11 is transmitted to the output shaft 12, the residual torque from the output shaft 12 may be loaded on the input outer ring 11 when the input of the rotational torque from the input outer ring 11 is stopped. If such residual torque remains, it is difficult to release the cylindrical roller 16 in the engaged state by the wedge clearance 15 with the elastic restoring force of the centering spring 37. As a result, the rotational phase difference between the input outer ring 11 and the cage 17 remains generated, and the cylindrical roller 16 remains engaged with the wedge clearance 15.

  Therefore, in the reverse input cutoff clutch of this embodiment, in the characteristic configuration, even when residual torque is applied to the input outer ring 11 when the input torque of the rotational torque from the input outer ring 11 is stopped, the elastic restoring force of the return spring 46 is restored. Thus, the input outer ring 11 is directly reversely rotated. Since the elastic restoring force of the return spring 46 is a torque sufficient to cause the input outer ring 11 to directly reversely rotate, the wedge spring 15 is engaged by the direct reverse rotation of the input outer ring 11 by the return spring 46. The cylindrical roller 16 that is in the combined state can be easily released.

  Here, the restoring torque of the input outer ring 11 and the friction plate 45 by the return spring 46 is set to be equal to or less than the sliding torque of the friction plate 45 with respect to the side plate 13. Therefore, the input outer ring 11 can be rotated in the reverse direction with respect to the friction plate 45 in a state where the rotation of the friction plate 45 is stopped with respect to the side plate 13. Thus, the input outer ring 11 can be easily rotated in reverse by using the return spring 46 provided on the input side of the reverse input cutoff clutch.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

11 Input side member (input outer ring)
12 Output side member (output shaft)
13 Stationary side member (side plate)
16 Engagement element (cylindrical roller)
17 Cage 45 Braking member (friction plate)
46 Elastic member (return spring)
47 1st protrusion 48 2nd protrusion 51 Protrusion piece

Claims (3)

An input side member to which rotational torque is input, an output side member to which rotational torque is output, a stationary side member whose rotation is restricted, and engagement and disengagement between the input side member and the output side member Accordingly, the engagement between the input side member and the output side member is controlled between the plurality of engagement elements that control the blocking of the rotational torque that is reversely input from the output side member and the transmission of the rotational torque that is input from the input side member. A reverse input shut-off clutch comprising a cage for holding a coupling,
A braking member that is slidably rotatable with respect to the stationary side member; and an elastic member provided between the input side member and the braking member. The elastic member is elastically deformed, and the braking member is rotated integrally with the input side member with respect to the stationary side member while maintaining the elastic deformation of the elastic member, and when the input of the rotational torque from the input side member is stopped, the elastic member A reverse input shut-off clutch, wherein the input side member is reversely rotated by an elastic restoring force.   The elastic member has a C-shape and is a return spring having projecting pieces whose both ends are bent radially outward. The braking member has a ring shape, and the projecting pieces of the return spring are locked. 2. The reverse input cutoff clutch according to claim 1, which is a friction plate having a first protrusion and a second protrusion that contacts the input side member by rotation of the input side member.   The reverse input cutoff clutch according to claim 1 or 2, wherein a restoring torque of the input side member and the braking member by the elastic member is set to be equal to or less than a sliding torque of the braking member with respect to the stationary side member.

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