JP6324749B2 - Clutch unit - Google Patents

Description

  The present invention includes a lever-side clutch portion to which rotational torque is input by lever operation, a brake-side clutch portion that transmits rotational torque from the lever-side clutch portion to the output side, and interrupts rotational torque from the output side. It is related with the clutch unit provided with.

  In general, in a clutch unit using an engagement element such as a cylindrical roller or a ball, a clutch portion is disposed between an input member and an output member. The clutch portion is configured to control transmission and interruption of rotational torque by engaging and disengaging an engaging member such as a cylindrical roller or a ball between the input member and the output member.

  The present applicant has previously proposed a clutch unit incorporated in an automobile seat lifter that adjusts the seat seat up and down by lever operation (see, for example, Patent Document 1). As shown in FIG. 13, the conventional clutch unit 110 disclosed in Patent Document 1 outputs a lever-side clutch portion 111 to which rotational torque is input by lever operation and the rotational torque from the lever-side clutch portion 111. And a brake side clutch portion 112 that cuts off rotational torque from the output side.

  As shown in FIGS. 13 and 14, the lever-side clutch portion 111 is composed mainly of a side plate 113 and an outer ring 114, an inner ring 115, a plurality of cylindrical rollers 116, a cage 117, an inner centering spring 118 and an outer centering spring 119. Has been. A side plate 113 that constitutes an input member together with the outer ring 114 is integrally attached to the outer side in the axial direction of the outer ring 114 by caulking. As shown in FIG. 16, an operation lever 142 that can swing in the vertical direction is attached to the side plate 113 by screws.

  Rotational torque is input to the side plate 113 and the outer ring 114 by lever operation. The inner ring 115 transmits the rotational torque from the outer ring 114 to the brake side clutch unit 112. The cylindrical roller 116 controls transmission and interruption of rotational torque from the outer ring 114 by engagement and disengagement at a wedge clearance 120 formed between the outer ring 114 and the inner ring 115. The cage 117 holds the plurality of cylindrical rollers 116 at equal intervals in the circumferential direction. The inner centering spring 118 accumulates an elastic force with the rotational torque from the outer ring 114, and releases the rotational torque to return the cage 117 to the neutral state with the accumulated elastic force. The outer centering spring 119 accumulates an elastic force with the rotational torque from the outer ring 114, and returns the outer ring 114 to a neutral state with the accumulated elastic force by releasing the rotational torque.

  As shown in FIGS. 13 and 15, the brake-side clutch unit 112 includes an outer ring 123, a cover 124 and a side plate 125, which are stationary members restricted in rotation, an output shaft 122 that outputs rotational torque, and an outer ring 123. A plurality of pairs that control transmission of rotational torque from the inner ring 115 of the lever side clutch portion 111 and interruption of rotational torque from the output shaft 122 by engagement and disengagement with a wedge clearance 126 formed between the output shaft 122 and the output shaft 122. The main part is composed of a cylindrical roller 127 and a leaf spring 128 having an N-shaped cross section that is inserted between each pair of cylindrical rollers 127 and biases the separating force between the cylindrical rollers 127.

  A cover 124 and a side plate 125 that constitute a stationary member together with the outer ring 123 are integrally attached to the inner side and the outer side in the axial direction of the outer ring 123 by caulking. A friction ring 139 that gives rotational resistance to the output shaft 122 is attached to the side plate 125. The inner ring 115 functions as a cage by accommodating the cylindrical rollers 127 and the leaf springs 128 and holding them at equal intervals in the circumferential direction. One shaft end portion of the output shaft 122 has a structure in which the components of the lever side clutch portion 111 are prevented from coming off by press-fitting a washer 131 through a wave washer 130.

  In the lever-side clutch portion 111 having the above-described configuration, when rotational torque is input to the outer ring 114 by lever operation, the cylindrical roller 116 engages with the wedge clearance 120 between the outer ring 114 and the inner ring 115, and the cylindrical roller Rotational torque is transmitted to the inner ring 115 via 116 and the inner ring 115 rotates. At this time, an elastic force is accumulated in the centering springs 118 and 119 as the outer ring 114 and the cage 117 rotate. When the rotational torque is no longer input, the retainer 117 and the outer ring 114 are returned to the neutral state by the elastic force of the centering springs 118 and 119, while the inner ring 115 maintains the given rotational position as it is. Therefore, the inner ring 115 rotates in a jog by repeating the rotation of the outer ring 114, that is, by the pumping operation of the operation lever 142.

  In the brake-side clutch portion 112 having the above-described configuration, when rotational torque is reversely input to the output shaft 122, the cylindrical roller 127 engages with the wedge clearance 126 between the output shaft 122 and the outer ring 123, and the output shaft 122 is locked to the outer ring 123. In this manner, the rotational torque reversely input from the output shaft 122 is locked by the brake side clutch portion 112 and the return to the lever side clutch portion 111 is blocked.

  On the other hand, in the brake side clutch portion 112, when rotational torque is input from the lever side clutch portion 111 to the inner ring 115, the inner ring 115 rotates and comes into contact with the cylindrical roller 127 and presses against the elastic force of the leaf spring 128. As a result, the cylindrical roller 127 is released from the wedge clearance 126 between the outer ring 123 and the output shaft 122 to release the locked state, and the output shaft 122 can be rotated. As the inner ring 115 further rotates, rotational torque from the inner ring 115 is transmitted to the output shaft 122, and the output shaft 122 rotates.

JP 2012-67793 A

  As described above, in the lever side clutch portion 111 of the conventional clutch unit 110 incorporated in the vehicle seat lifter portion, the side plate 113 that constitutes the input member together with the outer ring 114 is integrally fixed to the outer ring 114 by caulking. An operation lever 142 is fixed to the side plate 113 by screws. On the other hand, as shown in FIG. 17, when the rotational torque from the outer ring 114 is released, the cylindrical roller 116 is interposed between the outer ring 114 and the inner ring 115 when the outer ring 114 is returned to the neutral state by the elastic force of the outer centering spring 119. A gap m is set between the outer ring 114 and the cylindrical roller 116 so as to reliably return to the center position without biting.

  Thus, if there is a gap m between the outer ring 114 and the cylindrical roller 116, circumferential play occurs in the outer ring 114 when the lever is operated. That is, the play in the circumferential direction is generated in the operation lever 142 fixed to the outer ring 114 via the side plate 113. If there is such a backlash, abnormal noise may be generated from the operation lever 142 due to minute vibrations during idling of the automobile.

  Therefore, in order to reduce the backlash in the circumferential direction generated in the operation lever 142, conventionally, as shown in FIG. 18, in the press-fitting structure of the washer 131 that prevents the component parts of the lever-side clutch portion 111, An axial preload is applied to the outer ring 114 by the elastic force of the wave washer 130 disposed between the washer 131 and the washer 131.

  However, such a retaining structure by press-fitting the washer 131 requires a component part called the wave washer 130, which increases the number of parts. Further, since the wave washer 130 needs to be assembled, the assembling work becomes complicated.

  Therefore, the present invention has been proposed in view of the above-described problems, and an object of the present invention is to provide a clutch unit that can easily reduce the number of parts and improve the assembly workability.

As a technical means for achieving the above-mentioned object, a clutch unit according to the present invention is provided on the input side, and a lever side clutch portion that controls transmission and interruption of rotational torque input by lever operation, and an output side And the brake side clutch part that transmits the rotational torque from the lever side clutch part to the output side and cuts off the rotational torque reversely input from the output side. The lever side clutch part is rotated by lever operation. An input member to which torque is input, a connecting member that transmits rotational torque input from the input member to the brake side clutch, and rotation from the input member by engagement and disengagement between the input member and the connecting member A plurality of engagement elements that control transmission and interruption of torque, and an input member and a stationary member of the brake side clutch portion are sandwiched in the axial direction, And a cage for holding the zygote, the cage, by energizing elastic force in the axial direction between the input member and the stationary member, the peripheral of the input member with application of axial preload to the input member The elastic force generating portion for reducing the direction play is integrally formed on either the input member side or the stationary member side axial end surface.

  In the present invention, an elastic force generating portion that urges an elastic force in the axial direction between the input member and the stationary member is integrally formed on either the axial end surface of the input member side or the stationary member side. By providing the cage, it is possible to apply an axial preload to the input member with the elastic force generating portion of the cage. By applying this axial preload, it is possible to reduce circumferential backlash generated in the operation lever attached to the input member. As described above, by providing the elastic force generating portion integrally on the axial end surface of the cage, the axial preload is applied to the input member in the washer press-fitting structure that prevents the components of the lever side clutch portion from coming off. Therefore, the wave washer that has been conventionally used is not necessary.

  In the present invention, the elastic force generating portion is formed at a plurality of locations on the spring piece formed over the entire circumference of the axial end surface of the cylindrical cage, or on the axial end surface of the cylindrical cage. A spring piece is desirable. Thus, if the elastic force generating part of the cage is formed on the entire circumference or a part of its axial end face, a structure for applying axial preload to the input member can be easily provided as an alternative structure of the conventional wave washer. it can.

  The clutch unit according to the present invention is suitable for automobile use by incorporating the lever side clutch part and the brake side clutch part into the automobile seat lifter part.

  According to the present invention, the elastic force generating portion that urges the elastic force in the axial direction between the input member and the stationary member is integrally formed on the axial end surface of either the input member side or the stationary member side. By providing the cage, it is possible to apply an axial preload to the input member with the elastic force generating portion of the cage, thereby reducing circumferential backlash generated on the operation lever attached to the input member. it can. As a result, the washer press-in structure that prevents the lever-side clutch components from coming off eliminates the need for wave washers that were previously used to apply axial preload to the input member, reducing the number of parts and assembling workability. Can be improved.

In embodiment of this invention, it is sectional drawing which shows the whole structure of a clutch unit. It is sectional drawing which follows the AA line of FIG. It is sectional drawing which follows the BB line of FIG. It is a right view which shows the operation lever attached to the side plate of FIG. (A) is a perspective view which shows the holder | retainer of FIG. 1, (B) is sectional drawing of (A). It is a principal part expanded sectional view of FIG. (A) is a perspective view which shows the modification of a holder | retainer, (B) is sectional drawing of (A). (A) is a perspective view which shows the modification of a holder | retainer, (B) is sectional drawing of (A). (A) is a perspective view which shows the modification of a holder | retainer, (B) is sectional drawing of (A). It is a perspective view which shows the seat seat of a motor vehicle. It is a conceptual diagram which shows one structural example of a sheet lifter part. It is a principal part enlarged view of FIG. It is sectional drawing which shows the whole structure of the conventional clutch unit. It is sectional drawing which follows the CC line of FIG. It is sectional drawing which follows the DD line | wire of FIG. It is a right view which shows the operation lever attached to the side plate of FIG. It is a principal part expanded sectional view of FIG. It is a principal part expanded sectional view of FIG.

  As shown in FIG. 1, the clutch unit 10 according to the embodiment of the present invention has a structure in which a lever side clutch portion 11 provided on the input side and a brake side clutch portion 12 provided on the output side are unitized. ing. The lever side clutch part 11 controls transmission and interruption of rotational torque input by lever operation. The brake-side clutch unit 12 has a reverse input blocking function for transmitting the rotational torque from the lever-side clutch unit 11 to the output side and blocking the rotational torque that is reversely input from the output side.

  As shown in FIGS. 1 and 2, the lever side clutch unit 11 receives the side plate 13 and the outer ring 14 as input members to which rotational torque is input by lever operation, and the rotational torque input from the outer ring 14 to the brake side clutch. An inner ring 15 as a connecting member that transmits to the portion 12, a plurality of cylindrical rollers 16 that control transmission and interruption of rotational torque from the outer ring 14 by engagement and disengagement between the outer ring 14 and the inner ring 15, and a plurality of cylindrical rollers 16 A cage 17 for holding the cylindrical rollers 16 at equal intervals in the circumferential direction, an inner centering spring 18 for returning the cage 17 to a neutral state, and an outer centering spring 19 for returning the outer ring 14 to a neutral state, It comprises.

  In the lever side clutch portion 11, the claw portion 13 a formed on the outer peripheral edge portion of the side plate 13 is inserted into the notched recess portion 14 a formed on the outer peripheral edge portion of the outer ring 14, and the side plate 13 is tightened. 14 and is integrated as an input member of the lever side clutch portion 11. On the inner periphery of the outer ring 14, a plurality of cam surfaces 14b are formed at equal intervals in the circumferential direction. As shown in FIG. 4, the rotational torque is input to the outer ring 14 by an operation lever 42 that is swingable in the vertical direction (see the arrow in the figure) attached to the side plate 13 by screwing.

  The inner ring 15 includes a cylindrical portion 15a through which the output shaft 22 is inserted, a diameter-enlarged portion 15b in which a brake side end portion of the cylindrical portion 15a extends radially outward, and an outer peripheral end of the diameter-enlarged portion 15b. It consists of a plurality of protruding portions 15c (see FIG. 3) protruding by bending the portion in the axial direction. A wedge clearance 20 is formed between the outer peripheral surface 15d of the cylindrical portion 15a of the inner ring 15 and the cam surface 14b of the outer ring 14, and the cylindrical roller 16 is inserted into the wedge clearance 20 by the cage 17 at equal intervals in the circumferential direction. It is arranged.

  The inner centering spring 18 is a C-shaped elastic member having a circular cross section disposed between the retainer 17 and a cover 24 that is a stationary member of the brake side clutch portion 12. Both ends of the inner centering spring 18 are disposed on the retainer 17 and the cover 24. It is locked to a part of. The inner centering spring 18 is elastically expanded by the rotation of the cage 17 following the outer ring 14 with respect to the cover 24 in a stationary state when the rotational torque input from the outer ring 14 is applied by lever operation. When the rotational torque input from the outer ring 14 is released, the cage 17 is returned to the neutral state by the elastic force.

  The outer centering spring 19 located on the outer diameter side of the inner centering spring 18 is a C-shaped strip elastic member disposed between the outer ring 14 and the above-described cover 24, and both ends of the outer centering spring 19 are disposed on the outer ring 14 and the cover 24. It is locked to a part of. The outer centering spring 19 is expanded with the rotation of the outer ring 14 with respect to the cover 24 in a stationary state when the rotational torque input from the outer ring 14 by lever operation is applied, and an elastic force is accumulated. When the rotational torque input from 14 is released, the outer ring 14 is returned to the neutral state by its elastic force.

  As shown in FIGS. 5A and 5B, the cage 17 is a resin-made cylindrical member in which a plurality of pockets 17a for accommodating the cylindrical rollers 16 are formed at equal intervals in the circumferential direction. A notch for locking both end portions of the inner centering spring 18 described above at one axial end portion of the retainer 17, that is, the axial end portion on the cover 24 side of the brake side clutch portion 12. A recess 17b is formed. The cage 17 is disposed between the outer ring 14 and the inner ring 15 in the radial direction, and is sandwiched between the outer ring 14 and the cover 24 of the brake side clutch portion 12 in the axial direction.

  5 (A) and 5 (B), the spring piece 17e as an elastic force generating portion that urges the elastic force in the axial direction between the outer ring 14 and the cover 24 is integrated with the axial end surface 17c on the outer ring 14 side. The retainer 17 formed in FIG. The spring piece 17e has an annular shape formed over the entire circumference of the axial end surface 17c of the retainer 17, and has a thin plate shape that is inclined so as to incline from the outer peripheral edge of the axial end surface 17c toward the inner diameter side. Eggplant. Since the cage 17 is made of resin, and the spring piece 17e formed integrally with the cage 17 has a thin plate shape, the spring piece 17e can easily bias an elastic force in the axial direction. .

  Although the spring piece 17e is made of resin, the spring piece 17e can be configured by integrally forming a steel disc spring in the cage 17. The spring piece 17e extends from the outer peripheral edge of the axial end face 17c to the inner diameter side, but extends so as to incline from the inner peripheral edge of the axial end face 17c to the outer diameter side. It is also possible to do.

  As shown in FIGS. 1 and 3, the brake side clutch portion 12 having a reverse input blocking function of a type called a lock type has an inner ring 15 as a connecting member to which rotational torque from the lever side clutch portion 11 is input. An output shaft 22 as an output member from which the rotational torque from the lever side clutch portion 11 is output, an outer ring 23, a cover 24 and a side plate 25 as stationary members whose rotation is restricted, an outer ring 23 and an output shaft 22. A plurality of pairs of cylindrical rollers 27 for controlling the interruption of the rotational torque reversely input from the output shaft 22 and the transmission of the rotational torque input from the inner ring 15 by engagement and disengagement between them, and each pair of cylindrical rollers The main part is composed of a leaf spring 28 having an N-shaped cross section that urges a separation force in a circumferential direction between the members 27.

  The output shaft 22 is integrally formed with a large-diameter portion 22b that extends radially outward and expands in the axially central portion of the shaft portion 22a into which the tubular portion 15a of the inner ring 15 is extrapolated. An annular recess 22c is formed on the end surface of the large diameter portion 22b of the output shaft 22 facing the side plate 25, and a friction ring 39 is press-fitted into the annular recess 22c with a margin. A pinion gear 22d for connecting to the seat lifter 41 (see FIGS. 10 to 12) is coaxially formed at the end of the shaft 22a extending from the large diameter portion 22b to the brake side clutch portion 12. Further, a structure is provided in which the components of the lever side clutch portion 11 are prevented from coming off by press-fitting a washer 31 into the end portion of the shaft portion 22a extending from the large diameter portion 22b to the lever side clutch portion 11.

  A plurality of (for example, six) flat cam surfaces 22e are formed on the outer peripheral surface of the large-diameter portion 22b of the output shaft 22 at equal intervals in the circumferential direction. Two wedge-shaped gaps 26 provided between the cam surface 22e of the large diameter portion 22b and the inner peripheral surface 23a of the outer ring 23 are provided with two cylindrical rollers 27 and one leaf spring 28 interposed between the cylindrical rollers 27. Are arranged. The cylindrical rollers 27 and the leaf springs 28 are arranged at equal intervals in the circumferential direction by the protruding portions 15 c of the inner ring 15 having a function of transmitting the rotational torque input from the outer ring 14 to the output shaft 22. That is, the protruding portion 15c of the inner ring 15 functions as a cage by accommodating the cylindrical roller 27 and the leaf spring 28 in the pocket 15f and holding them at equal intervals in the circumferential direction. The large diameter portion 22 b of the output shaft 22 is provided with a protrusion 22 f for transmitting the rotational torque from the inner ring 15 to the output shaft 22. The protrusion 22f is inserted into the hole 15e formed in the enlarged diameter portion 15b of the inner ring 15 with a clearance.

  The outer ring 23, the cover 24, and the side plate 25 are divided into a notch recess 23 b formed in the outer peripheral edge of the thick plate-like outer ring 23 and a notch recess 24 a formed in the outer peripheral edge of the cover 24. The side plate 25 is fixed to the outer ring 23 and the cover 24 and is integrated as a stationary member of the brake side clutch portion 12 by inserting and crimping the claw portion 25a formed on the outer peripheral edge of the brake.

  The friction ring 39 as a braking member is a member formed of a resin material in a ring shape by injection molding or the like, and is fixed to the side plate 25. The friction ring 39 is press-fitted to the inner peripheral surface 22g of the annular recess 22c formed in the large diameter portion 22b of the output shaft 22 with a tightening margin. The friction force generated between the outer peripheral surface 39b of the friction ring 39 and the inner peripheral surface 22g of the annular recess 22c of the output shaft 22 gives rotational resistance to the output shaft 22 during lever operation.

  As described above, the lever-side clutch portion 11 includes the retainer 17 in which the spring piece 17e that urges the elastic force in the axial direction between the outer ring 14 and the cover 24 is integrally formed on the axial end surface 17c. By doing so, an axial preload can be applied to the outer ring 14 by the spring piece 17e of the cage 17. That is, as shown in FIG. 6, with the axial end surface 17d of the cage 17 in contact with the cover 24, the outer ring 14 that contacts the spring piece 17e is pressed in the axial direction by elastic deformation of the spring piece 17e. The washer 31 is press-fitted into the shaft portion 22 a of the output shaft 22. By applying this axial preload, even if a gap m (see FIG. 17) is set between the outer ring 14 and the cylindrical roller 16, the circumference generated in the operation lever 42 attached to the outer ring 14 via the side plate 13. Directional play can be reduced.

  Thus, since the play in the circumferential direction generated in the operation lever 42 can be reduced, it is possible to suppress the generation of abnormal noise from the operation lever 42 due to minute vibration during idling of the automobile. In addition, by providing the spring piece 17e integrally with the axial end surface 17c of the cage 17, the axial preload is applied to the outer ring 14 in the press-fit structure of the washer 31 that prevents the components of the lever side clutch portion 11 from coming off. Therefore, the wave washer 130 (see FIG. 13) that has been conventionally used is not necessary. As a result, the number of parts can be reduced and the assembly workability can be improved.

  In the above description, the case where the spring pieces 17e are formed over the entire circumference of the axial end surface 17c of the cage 17 is illustrated. However, as shown in FIGS. You may make it form in the axial direction end surface 17c of the holder | retainer 17 integrally in the circumferential direction at equal intervals. The spring pieces 17f have a thin plate shape extending from the axial end surface 17c of the cage 17 so as to incline in the circumferential direction. In addition, although the six spring pieces 17f are illustrated in the figure, the number is arbitrary. In the drawing, the inclination directions of all the spring pieces 17f are the same, but the inclination directions of the spring pieces 17f may be different in the circumferential direction. The spring piece 17f has the same function as that of the spring piece 17e shown in FIGS. 5A and 5B because the function of applying the axial preload to the outer ring 14 is omitted.

  In the above description, the case where the spring pieces 17e and 17f are provided on the axial end surface 17c of the retainer 17 on the outer ring 14 side is illustrated, but the spring pieces are provided on the axial end surface 17d of the retainer 17 on the cover 24 side. You may make it provide.

  8A and 8B illustrate a cage 17 in which a spring piece 17g is integrally formed over the entire circumference (excluding the notch recess 17b) of the axial end surface 17d. This spring piece 17g is in the form of a thin plate extending so as to incline from the outer peripheral edge portion of the axial end surface 17d of the cage 17 toward the inner diameter side, similarly to the spring piece 17e shown in FIGS. . This spring piece 17g may also be provided so as to incline from the inner peripheral edge of the axial end face 17d to the outer diameter side.

  9A and 9B show a thin plate-like spring piece 17h extending from the axial end surface 17d of the retainer 17 so as to incline in the circumferential direction at a plurality of locations (notched recesses) on the axial end surface 17d. 17b) is integrally formed. The number of the spring pieces 17h is also arbitrary, and the direction of the inclination of the spring pieces 17h may be different in the circumferential direction, in addition to making the inclination directions of all the spring pieces 17h the same.

  In the cage 17 shown in FIGS. 8A and 8B and FIGS. 9A and 9B, the spring pieces 17g and 17h contacting the cover 24 are brought into contact with the axial end surface 17c of the cage 17 by elastic deformation. An axial preload is applied to the outer ring 14 by pressing the outer ring 14 in the axial direction and bringing it into contact with a washer 31 press-fitted into the shaft portion 22 a of the output shaft 22. By applying this axial preload, even if a gap m (see FIG. 17) is set between the outer ring 14 and the cylindrical roller 16, circumferential play generated in the outer ring 14 and the operation lever 42 can be reduced. it can.

  In the lever-side clutch portion 11 having the above-described configuration, when rotational torque is input to the outer ring 14 by lever operation, the cylindrical roller 16 engages with the wedge clearance 20 between the outer ring 14 and the inner ring 15 and the cylinder. Rotational torque is transmitted to the inner ring 15 via the rollers 16 and the inner ring 15 rotates. At this time, elastic force is accumulated in the centering springs 18 and 19 as the outer ring 14 and the cage 17 rotate. When the rotational torque is no longer input, the cage 17 and the outer ring 14 are returned to the neutral state by the elastic force of the centering springs 18 and 19, while the inner ring 15 maintains the given rotational position. Therefore, the inner ring 15 rotates in a jog by repeating the rotation of the outer ring 14, that is, by the pumping operation of the operation lever 42.

  In the brake-side clutch portion 12 having the above-described configuration, the cylindrical roller 27 engages with the wedge clearance 26 between the output shaft 22 and the outer ring 23 even when rotational torque is reversely input to the output shaft 22. 22 is locked to the outer ring 23. Therefore, the rotational torque reversely input from the output shaft 22 is locked by the brake side clutch portion 12 and the return of the reverse input torque to the lever side clutch portion 11 is interrupted.

  On the other hand, in the brake side clutch portion 12, as described above, when the rotational torque from the lever side clutch portion 11 is input to the inner ring 15, the inner ring 15 comes into contact with the cylindrical roller 27 and the elastic force of the leaf spring 28 is increased. By pushing against the cylindrical roller 27, the cylindrical roller 27 is detached from the wedge clearance 26, the locked state of the output shaft 22 is released, and the output shaft 22 becomes rotatable. When the inner ring 15 further rotates, the clearance between the hole 15e of the enlarged diameter portion 15b of the inner ring 15 and the projection 22f of the large diameter portion 22b of the output shaft 22 is clogged, and the enlarged diameter portion 15b of the inner ring 15 becomes the projection 22f of the output shaft 22. By abutting in the rotational direction, the rotational torque from the lever side clutch portion 11 is transmitted to the output shaft 22 via the protrusion 22f, and the output shaft 22 rotates.

  The clutch unit 10 having the structure described in detail above is used by being incorporated in an automobile seat lifter 41 that adjusts the height of the seat 40 by lever operation. FIG. 10 shows a seat seat 40 installed in a passenger compartment of an automobile. The seat 40 includes a seat 40a and a backrest 40b, and includes a seat lifter 41 that adjusts the height H of the seat 40a. The height H of the seating seat 40a is adjusted by the operation lever 42 of the seat lifter 41. For example, when lowering the seating surface of the seat 40, the lever-side clutch portion 11 is unlocked, that is, the operation lever 42 is swung downward, and the brake-side clutch portion 12 is unlocked. At that time, by applying an appropriate rotational resistance to the output shaft 22, the seat surface of the seat 40 is smoothly lowered without any sense of incongruity for the passenger.

  FIG. 11 conceptually shows one structural example of the sheet lifter unit 41. One end of each of the link members 41c and 41d is pivotally attached to the slide movable member 41g of the seat slide adjuster 41b. The other ends of the link members 41c and 41d are pivotally attached to the seating seat 40a. The other end of the link member 41c is pivotally attached to the sector gear 41f via the link member 41e. The sector gear 41f is pivotally attached to the seating seat 40a and can swing around a fulcrum 41h (see FIG. 12). The other end of the link member 41d is pivotally attached to the seating seat 40a.

  In FIG. 12, when the operation lever 42 is swung upward, the input torque in that direction is transmitted to the pinion gear 22d via the clutch unit 10, and the pinion gear 22d rotates counterclockwise. Then, the sector gear 41f that meshes with the pinion gear 22d swings in the clockwise direction, and pulls the other end of the link member 41c through the link member 41e. As a result, both the link member 41c and the link member 41d stand up, and the seating surface of the seating seat 40a is raised.

  In this way, after adjusting the height H of the seating seat 40a, when the operation lever 42 is released, the operation lever 42 is rotated downward by the elastic force of the centering springs 18 and 19 to return to the original position (neutral). Return to the state. When the operation lever 42 is swung downward, the seating surface of the seating seat 40a is lowered by the reverse operation to the above. Further, when the operation lever 42 is released after the height adjustment, the operation lever 42 rotates upward and returns to the original position (neutral state).

  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 Lever side clutch part 12 Brake side clutch part 14 Input member (outer ring)
15 Connecting member (inner ring)
16 Engagement element (cylindrical roller)
17 Cage 17c, 17d Axial direction end face 17e-17h Elastic force generation part (spring piece)
24 Static member (cover)
41 Seat lifter

Claims (4)

Provided on the input side, a lever side clutch part that controls transmission and interruption of rotational torque input by lever operation, and provided on the output side, and transmits the rotational torque from the lever side clutch part to the output side, It consists of a brake side clutch part that cuts off rotational torque that is reversely input from the output side,
The lever side clutch portion includes an input member to which rotational torque is input by lever operation, a connecting member that transmits the rotational torque input from the input member to the brake side clutch portion, and between the input member and the connecting member. Between the input member and the stationary member of the brake side clutch portion in the axial direction, and each of the engagement members is A retainer for holding,
The retainer is an elastic force generator that reduces the backlash in the circumferential direction of the input member by applying an axial preload to the input member by biasing an elastic force in the axial direction between the input member and the stationary member. Is formed integrally with the axial end surface of either the input member side or the stationary member side.   2. The clutch unit according to claim 1, wherein the elastic force generating portion is a spring piece formed over the entire circumference of an axial end surface of a cylindrical cage. 3.   2. The clutch unit according to claim 1, wherein the elastic force generating portions are spring pieces formed at a plurality of locations on an axial end surface of a cylindrical cage.   The clutch unit as described in any one of Claims 1-3 in which the said lever side clutch part and the said brake side clutch part are integrated in the seat lifter part for motor vehicles.

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