JP2018119658A - Reverse input blocker - Google Patents

Abstract

PROBLEM TO BE SOLVED: To surely hold a lock state of a clutch plate even if excessive rotation torque is reversely inputted from an output shaft.SOLUTION: A reverse input blocker comprises: an input shaft 11; an output shaft 12 which is arranged coaxially with the input shaft 11; a housing 13 for rotatably supporting the input shaft 11 and the output shaft 12; a clutch member 16 arranged between the input shaft 11 and the output shaft 12 so as to be movable in an axial direction; a conical clutch 15 which can make a movable friction face 38 of the clutch member 16 engaged with and released from a fixed friction face 37 of a fixed ring 36 by the axial movement of the clutch member 16. An axial end face of the clutch member 16 and an axial end face of the fixed ring 36 are made to oppose each other, face splines 55, 56 are formed at the axial end faces of the clutch member 16 and the fixed ring 36, and by the axial movement of the clutch member 16, rotation torque which is reversely inputted from the output shaft 12 can be blocked by the engagement of the face splines 55, 56.SELECTED DRAWING: Figure 1

Description

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

  The present applicant was disclosed in Patent Document 1 as a reverse input blocking device having a function of transmitting rotational torque input from the input shaft to the output shaft while blocking rotational torque input reversely from the output shaft. Propose something first.

  The reverse input shut-off device disclosed in Patent Document 1 includes an input shaft, an output shaft arranged coaxially with the input shaft, and a clutch disk arranged to be movable in the axial direction between the input shaft and the output shaft. An input side torque cam means provided between the input shaft and the clutch disk, an output side torque cam means provided between the output shaft and the clutch disk, and a cone provided between the housing and the clutch disk The main part is composed of the clutch.

  The input side torque cam means is composed of a cam groove formed on the opposing surfaces of the input shaft and the clutch disk, and a ball interposed between the two cam grooves. The output side torque cam means is composed of a cam groove formed on the opposed surfaces of the output shaft and the clutch disk, and a ball interposed between the two cam grooves. In the conical clutch, the conical movable friction surface provided in the clutch disc can be engaged and disengaged with respect to the conical fixed friction surface provided in the housing.

  In this reverse input shut-off device, when the rotational torque is reversely input from the output shaft, the output shaft and the clutch disk rotate relative to each other. Due to this relative rotation, in the output side torque cam means, the cam groove of the output shaft and the cam groove of the clutch disk are out of phase in the circumferential direction. The clutch disk moves to the axial direction input side with the axial force generated by this phase shift.

  Due to the axial movement of the clutch disc, in the conical clutch, the movable friction surface of the clutch disc engages with the fixed friction surface of the housing. The clutch disc is locked by the engagement of the movable friction surface with the fixed friction surface. The rotational torque reversely input from the output shaft is cut off by the locked state of the clutch disk.

  On the other hand, when rotational torque is input from the input shaft, the input shaft and the clutch disk rotate relative to each other. Due to this relative rotation, in the input side torque cam means, the cam groove of the input shaft and the cam groove of the clutch disc are out of phase in the circumferential direction. With the axial force generated by this phase shift, the clutch disk moves to the axial direction output side opposite to that described above.

  Due to the axial movement of the clutch disc, in the conical clutch, the movable friction surface of the clutch disc separates from the fixed friction surface of the housing. The clutch disk is unlocked by the separation of the movable friction surface from the fixed friction surface. By releasing the lock state of the clutch disk, the rotational torque from the input shaft is transmitted to the output shaft through the clutch disk.

JP 2006-57804 A

  By the way, in the conventional reverse input shut-off device disclosed in Patent Document 1, in the conical clutch, when the rotational torque reversely inputted from the output shaft is cut off, the movable friction surface of the clutch disk engages with the fixed friction surface of the housing. As a result, the clutch disk is locked.

  The locked state of the clutch disk is held only by the frictional resistance between the movable friction surface of the clutch disk and the fixed friction surface of the housing.

  For this reason, when an excessive rotational torque is reversely input from the output shaft, the movable friction surface of the clutch disk easily slips with respect to the fixed friction surface of the housing. As a result, it becomes difficult to maintain the clutch disk locked state only by the frictional resistance between the movable friction surface of the clutch disk and the fixed friction surface of the housing.

  Accordingly, the present invention has been proposed in view of the above-described problems, and the object of the present invention is to reverse the clutch disk in a reliable manner even when excessive rotational torque is reversely input from the output shaft. It is to provide an input blocking device.

  A reverse input blocking device according to the present invention includes an input shaft, an output shaft disposed coaxially with the input shaft, a stationary member that rotatably supports the input shaft and the output shaft, and an input shaft and an output shaft. A clutch member that is arranged so as to be axially movable therebetween, and a conical clutch that allows the movable friction surface of the clutch member to be engaged and disengaged with respect to the fixed friction surface of the stationary member by the axial movement of the clutch member. The structure provided.

  As a technical means for achieving the above-described object, the present invention makes the axial end surface of the clutch member and the axial end surface of the stationary member face each other, and an uneven fitting portion is provided on the axial end surfaces of the clutch member and the stationary member. It is characterized in that the rotational torque reversely input from the output shaft by the engagement of the concave-convex fitting portion can be interrupted by the axial movement of the clutch member.

  In the present invention, when the rotational torque reversely input from the output shaft is interrupted, the movable friction surface of the clutch member is pressed against the fixed friction surface of the stationary member in the conical clutch by the axial movement of the clutch member with respect to the output shaft. Due to the pressure contact between the fixed friction surface and the movable friction surface, the clutch member is engaged by engaging the fixed friction surface and the movable friction surface with the frictional force generated in the rotational direction between the fixed friction surface and the movable friction surface. Is locked. Due to the clutch member being locked, the rotational torque reversely input from the output shaft is cut off.

  Furthermore, in the present invention, the concave and convex fitting portions provided on the axial end surfaces of the clutch member and the stationary member are engaged with each other by the above-described axial movement of the clutch member. Due to the engagement of the concave and convex fitting portions, the axial end surface of the clutch member and the axial end surface of the stationary member are brought together with a rotational fitting force generated between the axial end surface of the clutch member and the axial end surface of the stationary member. Engage.

  Thus, even when excessive rotational torque is reversely input from the output shaft, in the conical clutch, not only the fixed friction surface of the stationary member and the movable friction surface of the clutch member are engaged, but also the stationary member is formed by the concave and convex fitting portion. By engaging the end face in the axial direction and the end face in the axial direction of the clutch member, the locked state of the clutch member can be reliably held.

  As for the uneven | corrugated fitting part in this invention, the structure in which the some convex part or recessed part extended in radial direction was formed along the circumferential direction is desirable.

  If such a structure is employed, rotation generated between the axial end surface of the clutch member and the axial end surface of the stationary member due to the engagement of the concave-convex fitting portion when the rotational torque reversely input from the output shaft is interrupted. The axial end face of the stationary member and the axial end face of the clutch member can be reliably engaged with each other by the direction fitting force.

  The clutch member according to the present invention includes a clutch plate having a movable friction surface and a slide gear coupled to the clutch plate so as to be movable in the axial direction, and the concave / convex fitting portion is provided on an axial end surface of the slide gear. The structure is desirable.

  If such a structure is adopted, when the rotational torque reversely inputted from the output shaft is interrupted, the fixed friction surface and the movable friction surface are engaged with each other in the conical clutch, and the axial end surface of the slide gear is stationary with the clutch member. A structure for engaging the end face in the axial direction of the member can be easily realized.

  In the present invention, it is desirable to have a structure in which an elastic member is interposed between the clutch plate and the slide gear so that the concave-convex fitting portion can be engaged against the elastic force of the elastic member by axial movement of the slide gear with respect to the clutch plate. .

  By adopting such a structure, when releasing the clutch plate lock state, the structure in which the axial end surface of the slide gear is detached from the axial end surface of the stationary member in the clutch member is easily realized by the elastic force of the elastic member. can do.

  According to the present invention, even if excessive rotational torque is reversely input from the output shaft, the conical clutch not only engages the fixed friction surface of the stationary member and the movable friction surface of the clutch member, but also the uneven fitting portion. Thus, by engaging the axial end surface of the stationary member and the axial end surface of the clutch member, the locked state of the clutch member can be reliably maintained.

  As a result, it is not necessary to enlarge the reverse input shut-off device in accordance with excessive rotational torque. This makes it possible to reduce the size of the reverse input blocking device.

In embodiment of this invention, it is sectional drawing which shows the whole structure of a reverse input interruption | blocking apparatus. It is sectional drawing which follows the PP line | wire of FIG. It is sectional drawing which follows the QQ line of FIG. It is sectional drawing which follows the RR line | wire of FIG. It is sectional drawing which follows the SS line | wire of FIG. It is sectional drawing which shows the state which the phase shift of the cam groove generate | occur | produced in the torque cam part. It is sectional drawing which shows the state which the slide gear of FIG. 1 moves to an axial direction.

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

  FIG. 1 shows the overall configuration of a reverse input blocking device. As shown in the figure, the reverse input blocking device of this embodiment includes an input shaft 11, an output shaft 12, a housing 13 that is a stationary member, a torque cam portion 14, a conical clutch 15, and a clutch member 16. The main part is composed.

  The housing 13 accommodates main portions including the shaft end portion of the input shaft 11, the shaft end portion of the output shaft 12, the torque cam portion 14, the conical clutch 15, and the clutch member 16. The housing 13 has a half structure in which the input side case 17 and the output side case 18 are joined and integrated.

  The input shaft 11 and the output shaft 12 are coaxially arranged, and the shaft end portion of the input shaft 11 and the shaft end portion of the output shaft 12 are disposed to face each other. Flange portions 19 and 20 are integrally formed at the shaft end portions of the input shaft 11 and the output shaft 12. The input shaft 11 and the output shaft 12 are supported with respect to the housing 13 by bearings 21 and 22 so as to be rotatable forward and backward.

  A clutch member 16 is disposed between the flange portion 19 of the input shaft 11 and the flange portion 20 of the output shaft 12 so as to be movable in the axial direction. The torque cam portion 14 includes an input side cam portion 23 provided between the flange portion 19 of the input shaft 11 and the clutch member 16, and an output side cam portion 24 provided between the clutch member 16 and the output shaft 12. It consists of

  FIG. 2 is a cross-sectional view taken along the line P-P in FIG. 1 and shows an input side cam portion 23 (solid line) and an output side cam portion 24 (broken line). FIG. 5 is a cross section taken along the line S-S in FIG. 2 and shows the cam grooves 25 and 26 and the ball 27 of the input side cam portion 23. In addition, since the output side cam part 24 also has the same structure as the input side cam part 23, the cam grooves 28 and 29 of the output cam part 24 and the ball | bowl 30 are attached | subjected with the parenthesis in a figure.

  The input-side cam portion 23 is camped at equal intervals at a plurality of circumferential positions, for example, four locations (see FIG. 2) on both opposing surfaces of the flange portion 19 of the input shaft 11 and the cam plate 42 (described later) of the clutch member 16. Grooves 25 and 26 are formed. A ball 27 is interposed between the cam groove 25 of the flange portion 19 and the cam groove 26 of the cam plate 42.

  As shown in FIG. 5, the cam groove 25 of the flange portion 19 and the cam groove 26 of the cam plate 42 are cam surfaces 32 and 33 which are inclined so that the depth gradually decreases from the circumferential center to both circumferential ends. It has the circumferential cross-sectional V-groove shape with. In this embodiment, a plurality of cam grooves 25 and 26 and four balls 27 are provided (see FIG. 2), but the number thereof is arbitrary.

  The output side cam portion 24 is camped at equal intervals at a plurality of circumferential positions, for example, four locations (see FIG. 2) on both opposing surfaces of a slide gear 44 (described later) of the clutch member 16 and the flange portion 20 of the output shaft 12. Grooves 28 and 29 are formed. A ball 30 is interposed between the cam groove 28 of the slide gear 44 and the cam groove 29 of the flange portion 20.

  As shown in FIG. 5, the cam groove 28 of the slide gear 44 and the cam groove 29 of the flange portion 20 are cam surfaces 34 and 35 which are inclined so that the depth gradually decreases from the circumferential center toward both circumferential ends. It has the circumferential cross-sectional V-groove shape with. In this embodiment, the plurality of cam grooves 28 and 29 and the balls 30 are four (see FIG. 2), but the number is arbitrary.

  As shown in FIG. 1, the conical clutch 15 includes a stationary ring 36 of the housing 13 and a clutch plate 43 (described later) of the clutch member 16. The fixing ring 36 is attached to the input side case 17 of the housing 13 by an appropriate means.

  A conical fixed friction surface 37 is formed on the inner peripheral surface of the fixing ring 36. A conical movable friction surface 38 is formed on the outer peripheral surface of the clutch plate 43. In the conical clutch 15, the movable friction surface 38 of the clutch plate 43 can be pressed against the fixed friction surface 37 of the fixed ring 36.

  A rotation resistance applying portion 39 is provided between the clutch plate 43 and the housing 13. The rotational resistance applying portion 39 includes an annular friction plate 40 that can be pressed against the inner surface of the output side case 18 of the housing 13, and an elastic member 41 that is incorporated between the friction plate 40 and the clutch plate 43. ing.

  When the friction plate 40 is pressed against the inner surface of the output side case 18 of the housing 13 by the elastic member 41, the friction resistance acting on the pressure contact surface, the contact surface between the elastic member 41 and the clutch plate 43, or the elastic member 41 The frictional resistance acting on the contact surface with the friction plate 40 is the rotational resistance of the clutch plate 43.

  As shown in FIG. 1, the clutch member 16 described above includes a cam plate 42 positioned radially inward, a clutch plate 43 positioned radially outward, and a slide positioned between the cam plate 42 and the clutch plate 43. And a gear 44. 3 is a cross-sectional view taken along the line QQ in FIG. 1, and FIG. 4 is a cross-sectional view taken along the line RR in FIG.

  As described above, the cam plate 42 constitutes the input side cam portion 23 with the flange portion 19 of the input shaft 11. A thrust bearing 45 is disposed between the cam plate 42 and the flange portion 20 of the output shaft 12. By interposing the thrust bearing 45, the relative rotation between the output shaft 12 and the cam plate 42 is allowed, and at the same time, the axial movement of the cam plate 42 is restricted.

  Further, a flange portion 46 is integrally formed at the output shaft side end portion of the cam plate 42. As shown in FIG. 3, a face spline 47 is formed on the axial end face located on the input side of the flange portion 46. The face spline 47 is formed with a plurality of convex portions extending in the radial direction along the circumferential direction.

  As described above, the clutch plate 43 forms the conical clutch 15 with the fixing ring 36. That is, a conical movable friction surface 37 is formed on the outer peripheral surface of the clutch plate 43. As shown in FIG. 3, a slide spline 48 in which a plurality of convex portions extending in the axial direction are formed along the circumferential direction is formed on the small-diameter inner peripheral surface of the clutch plate 43. Further, an elastic member 49 such as a disc spring is attached to the large-diameter inner peripheral surface of the clutch plate 43.

  The clutch plate 43 is elastic in the axial direction so that the movable friction surface 38 is in pressure contact with the fixed friction surface 37 of the fixed ring 36 by the elastic member 50 attached to the input side end surface of the flange portion 20 of the output shaft 12. Power is energized.

  The slide gear 44 forms an output side cam portion 24 between the slide gear 44 and the flange portion 20 of the output shaft 12. An inner flange portion 51 is integrally formed on the inner periphery of the slide gear 44. As shown in FIG. 3, a face spline 52 in which a plurality of recesses extending in the radial direction are formed along the circumferential direction is formed on the axial end surface located on the output side of the inner flange portion 51.

  The face spline 52 of the slide gear 44 and the face spline 47 of the cam plate 42 mesh with each other in a state where the axial end surface of the inner flange portion 51 of the slide gear 44 and the axial end surface of the flange portion 46 of the cam plate 42 abut each other. It is in a state.

  As shown in FIG. 3, a slide spline 53 is formed on the outer peripheral surface of the slide gear 44. The slide spline 53 is formed with a plurality of recesses extending in the axial direction along the circumferential direction. The slide spline 53 of the slide gear 44 and the slide spline 48 of the clutch plate 43 are always in mesh with each other. In this state, the slide gear 44 is movable in the axial direction with respect to the clutch plate 43.

  An outer flange portion 54 is integrally formed on the outer peripheral surface of the slide gear 44. The outer flange portion 54 of the slide gear 44 is sandwiched between the axial end surface of the clutch plate 43 and the elastic member 49, and is in contact with the axial end surface of the clutch plate 43 by the elastic force of the elastic member 49. It has become.

  As shown in FIG. 4, a face spline 55 is formed on the end surface of the slide gear 44 in the circumferential direction. On the other hand, a face spline 56 is formed on the axial end surface of the fixing ring 36 (see FIG. 1). The face spline 56 is formed with a plurality of radially extending recesses along the circumferential direction.

  The face spline 55 of the slide gear 44 and the face spline 56 of the fixing ring 36 constitute an uneven fitting portion. The face spline 55 of the slide gear 44 and the face spline 56 of the fixed ring 36 are engaged with each other in a state where the axial end surface of the slide gear 44 and the axial end face of the fixed ring 36 are abutted.

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

  When the rotational torque reversely input from the output shaft 12 is interrupted, if the rotational torque is reversely input from the output shaft 12, the rotational resistance acting on the clutch plate 43 due to the frictional resistance at the rotational resistance applying portion 39, and the elastic member 50 However, the output shaft 12 and the clutch plate 43 rotate relative to each other with rotational resistance generated by pressing the movable friction surface 38 of the clutch plate 43 against the fixed friction surface 37 of the fixed ring 36.

  At this time, the outer flange portion 54 of the slide gear 44 abuts against the axial end surface of the clutch plate 43 by the elastic force of the elastic member 49 of the clutch plate 43, and the face spline 52 of the slide gear 44 is connected to the face spline 47 of the cam plate 42. They are engaged. On the other hand, the meshing between the face spline 56 of the fixing ring 36 and the face spline 55 of the slide gear 44 is released. As a result, the cam plate 42, the slide gear 44, and the clutch plate 43 are integrally rotated relative to the output shaft 12.

  Due to this relative rotation, in the output side cam portion 24, as shown in FIG. 6, the cam groove 29 of the flange portion 20 of the output shaft 12 and the cam groove 28 of the slide gear 44 are changed from the state of FIG. ). Due to this phase shift, the ball 30 interposed between the cam grooves 29 and 28 presses the cam surface 34 of the cam groove 28 of the slide gear 44, so that the axial force is applied to the cam plate 42, the slide gear 44 and the clutch plate 43. Occur.

  Due to this axial force, the clutch plate 43 moves in the axial direction (right side shown in FIG. 1) close to the flange portion 19 of the input shaft 11. Due to the axial movement of the clutch plate 43, the movable friction surface 38 of the clutch plate 43 is pressed against the fixed friction surface 37 of the fixed ring 36 in the conical clutch 15. At this time, a pressing force obtained by adding the axial force of the clutch plate 43 generated in the output side cam portion 24 to the elastic force of the elastic member 50 acts on the conical clutch 15.

  In this manner, the movable friction surface 38 of the clutch plate 43 is pressed against the fixed friction surface 37 of the fixed ring 36 in the axial direction, so that the conical clutch 15 has a space between the fixed friction surface 37 and the movable friction surface 38. The clutch plate 43 is locked by the frictional force generated in the rotational direction. Due to the locked state of the clutch plate 43, the rotational torque is not transmitted to the input shaft 11.

  Here, when an excessive rotational torque is reversely input to the output shaft 12, the phase shift between the cam groove 29 of the flange portion 20 of the output shaft 12 and the cam groove 28 of the slide gear 44 is further increased in the output side cam portion 24. It gets bigger. Therefore, as shown in FIG. 7, the slide gear 44 further moves in the axial direction along the slide splines 53 and 48 against the elastic force of the elastic member 49 of the clutch plate 43 (see the white arrow in the figure).

  At this time, the engagement between the face spline 52 of the slide gear 44 and the face spline 47 of the cam plate 42 is released, so that the slide gear 44 is separated from the cam plate 42 whose axial movement is restricted by the slide bearing 45. Thus, further axial movement of the slide gear 44 is possible.

  By this axial movement, the face spline 55 of the slide gear 44 and the face spline 56 of the fixing ring 36 are engaged with each other. Due to the meshing of the face spline 55 of the slide gear 44 and the face spline 56 of the fixed ring 36, the clutch is engaged with a rotational fitting force generated between the axial end surface of the clutch plate 43 and the axial end surface of the fixed ring 36. The axial end surface of the plate 43 and the axial end surface of the fixing ring 36 are engaged.

  Thus, even if excessive rotational torque is reversely input from the output shaft 12, the conical clutch 15 not only engages the fixed friction surface 37 of the fixed ring 36 and the movable friction surface 38 of the clutch plate 43. By engaging the face spline 55 of the slide gear 44 and the face spline 56 of the fixing ring 36, the axial end surface of the fixing ring 36 and the axial end surface of the clutch plate 43 are engaged, whereby the clutch plate 43 is locked. Can be securely held.

  As a result, it is not necessary to enlarge the reverse input shut-off device in accordance with excessive rotational torque. This makes it possible to reduce the size of the reverse input blocking device.

  Next, there is no rotational torque reversely input from the output shaft 12 as described above, and when the rotational torque input from the input shaft 11 is transmitted to the output shaft 12, the rotational torque is input from the input shaft 11. The flange portion 19 of the input shaft 11 and the cam plate 42 of the clutch member 16 rotate relative to each other with the rotational resistance acting on the clutch plate 43 due to the frictional resistance at the rotational resistance applying portion 39. At this time, the cam plate 42 is restricted from moving in the axial direction (left side shown in FIG. 1) by a slide bearing 45 provided between the cam plate 42 and the output shaft 12.

  Therefore, the outer flange portion 54 of the slide gear 44 abuts against the axial end surface of the clutch plate 43 due to the elastic force of the elastic member 49, and the face spline 52 of the slide gear 44 meshes with the face spline 47 of the cam plate 42. It has become. On the other hand, the meshing between the face spline 56 of the fixing ring 36 and the face spline 55 of the slide gear 44 is released. As a result, the cam plate 42, the slide gear 44, and the clutch plate 43 are integrally rotated relative to the input shaft 11.

  Due to this relative rotation, in the input side cam portion 23, as shown in FIG. 6, the cam groove 25 of the flange portion 19 of the input shaft 11 and the cam groove 26 of the cam plate 42 are moved from the state of FIG. Direction). Due to this phase shift, the ball 27 interposed between the cam grooves 25 and 26 presses the cam surface 33 of the cam groove 26 of the cam plate 42, so that the axial force is applied to the cam plate 42, the slide gear 44 and the clutch plate 43. Occur.

  Due to this axial force, the clutch plate 43 moves in the axial direction (left side shown in FIG. 1) away from the flange portion 19 of the input shaft 11 against the elastic force of the elastic member 50. Although the cam plate 42 is restricted from moving in the axial direction by the slide bearing 45, the cam plate 42 is allowed to move in the axial direction to the extent that the face spline 52 of the slide gear 44 and the face spline 47 of the cam plate 42 are kept engaged. ing.

  Due to the axial movement of the clutch plate 43, the movable friction surface 38 of the clutch plate 43 is detached from the fixed friction surface 37 of the fixed ring 36 in the conical clutch 15. By releasing the movable friction surface 38 of the clutch plate 43 from the fixed friction surface 37 of the fixing ring 36, the locked state of the clutch plate 43 is released.

  By releasing the locked state of the clutch plate 43, the rotational torque from the input shaft 11 is applied to the output shaft 12 via the ball 27 between the input shaft 11 and the cam plate 42 and the ball 30 between the slide gear 44 and the output shaft 12. As a result, the output shaft 12 rotates in the same direction as the input shaft 11.

  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 shaft 12 Output shaft 13 Stationary member (housing)
15 Conical clutch 16 Clutch member 36 Stationary member (fixing ring)
37 Fixed friction surface 38 Movable friction surface 43 Clutch plate 44 Slide gear 49 Elastic member 55, 56 Concavity and convexity fitting portion (face spline)

Claims (4)

An input shaft, an output shaft disposed coaxially with the input shaft, a stationary member rotatably supporting the input shaft and the output shaft, and an axially movable between the input shaft and the output shaft. And a conical clutch capable of engaging and disengaging the movable friction surface of the clutch member with respect to the fixed friction surface of the stationary member by axial movement of the clutch member,
The axial end surface of the clutch member and the axial end surface of the stationary member are opposed to each other, and an uneven fitting portion is provided on the axial end surfaces of the clutch member and the stationary member. A reverse input blocking device characterized in that it can block rotational torque reversely input from the output shaft by meshing.   The reverse input blocking device according to claim 1, wherein the concave-convex fitting portion has a structure in which a plurality of convex portions or concave portions extending in a radial direction are formed along a circumferential direction.   The clutch member includes a clutch plate having the movable friction surface, and a slide gear coupled to the clutch plate so as to be movable in the axial direction, and the concave / convex fitting portion is provided on an axial end surface of the slide gear. The reverse input shut-off device according to claim 1 or 2.   An elastic member is interposed between the clutch plate and the slide gear, and the concave-convex fitting portion can be engaged with the elastic force of the elastic member by axial movement of the slide gear with respect to the clutch plate. Item 4. The reverse input cutoff device according to Item 3.

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