JP2018112277A - Clutch unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a cam surface from being enlarged and to suppress an adverse effect due to temperature in a use environment. A lever-side clutch portion 11 that controls transmission and interruption of input rotational torque, and rotational torque from the lever-side clutch portion 11 is transmitted to an output side and reversely input from the output side. The brake side clutch portion 12 is configured to be attached to and fixed to the side plate 25, the output shaft 22 from which rotation is output, and the side plate 25. A braking member that imparts rotational resistance, and the braking member is in pressure contact with the axial end surface 22h of the output shaft 22, and a metal friction plate that imparts rotational resistance to the output shaft 22 with a sliding torque generated by the pressure contact. 29. [Selection] Figure 1

Description

  The present invention includes an input-side clutch portion to which rotational torque is input, and an output-side clutch portion that transmits the rotational torque from the input-side clutch portion to the output side and blocks the rotational torque from the output side. It relates to the clutch unit.

  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).

  The clutch unit disclosed in Patent Document 1 transmits a lever-side clutch portion as an input-side clutch portion to which rotational torque is input by lever operation and the rotational torque from the lever-side clutch portion to the output side, A brake-side clutch portion serving as an output-side clutch portion that cuts off rotational torque from the output side.

  The lever side clutch part is separated from the outer ring by engaging and disengaging the outer ring to which rotational torque is input by lever operation, the inner ring that transmits the rotational torque from the outer ring to the brake side clutch part, and the wedge clearance between the outer ring and the inner ring. A cylindrical roller that controls transmission and interruption of the rotational torque of the motor, and a centering spring that accumulates elastic force with the rotational torque from the outer ring and returns the outer ring to the neutral state with the accumulated elastic force when the rotational torque is no longer input. The main part is composed of.

  The brake-side clutch unit includes a side plate and an outer ring that are restricted in rotation, an output shaft that outputs rotational torque, and an interruption and release of the rotational torque from the output shaft by engaging and disengaging the wedge between the outer ring and the output shaft. A plurality of cylindrical rollers and leaf springs that control transmission of rotational torque from the lever side clutch, a cage that holds the cylindrical rollers and leaf springs at equal intervals in the circumferential direction, and rotational resistance to the output shaft The main part is composed of a resin friction ring. The cage is formed integrally with the inner ring of the lever side clutch portion.

  In the lever side clutch portion, when rotational torque is input to the outer ring by lever operation, the cylindrical roller engages with the wedge clearance between the outer ring and the inner ring. Due to the engagement of the cylindrical rollers up to the wedge clearance, rotational torque is transmitted to the inner ring, and the inner ring rotates. At this time, an elastic force is accumulated in the centering spring as the outer ring rotates.

  When there is no input of rotational torque by lever operation, the outer ring returns to the neutral state by the elastic force of the centering spring. On the other hand, the inner ring maintains the given rotational position as it is. Therefore, the inner ring rotates in a jog by repeating the rotation of the outer ring, that is, by the pumping operation of the operation lever.

  In the brake side clutch portion, when rotational torque is reversely input to the output shaft by sitting on the seat, the cylindrical roller engages with the wedge clearance between the output shaft and the outer ring, and the output shaft is locked to the outer ring. . Due to the locking of the output shaft, the rotational torque reversely input from the output shaft is cut off. Thereby, the seat surface height of the seat is maintained.

  On the other hand, when rotational torque is input from the inner ring of the lever side clutch portion to the cage of the brake side clutch portion, the cage rotates and abuts against the cylindrical roller to press against the elastic force of the leaf spring, The cylindrical roller is detached from the wedge clearance between the outer ring and the output shaft. With the separation of the cylindrical roller, the locked state of the output shaft is released, and the output shaft can be rotated. When the locked state is released, rotational resistance is applied to the output shaft by the friction ring.

  Then, when the cage of the brake side clutch portion further rotates, the rotational torque from the cage is transmitted to the output shaft, and the output shaft rotates. That is, when the retainer is joggingly rotated with the inner ring of the lever side clutch portion, the output shaft is also joggingly rotated. The seat surface height of the seat can be adjusted by the inching rotation of the output shaft.

Japanese Patent No. 5207777

  By the way, in the brake side clutch part of the conventional clutch unit disclosed in Patent Document 1, the friction ring is fixed to the side plate as a stationary member, and the outer peripheral surface of the friction ring with respect to the inner peripheral surface of the annular recess of the output shaft. A tightening allowance is provided, and a structure is adopted in which the friction ring is press-fitted into the annular recess of the output shaft with the allowance.

  With such a press-fit structure, the outer periphery of the friction ring is caused by the friction force generated between the outer peripheral surface of the friction ring and the inner peripheral surface of the annular recess of the output shaft when the output shaft is unlocked in the brake side clutch portion. The inner peripheral surface of the annular recess slides on the surface. Thereby, an appropriate rotational resistance (sliding torque) is applied to the output shaft.

  By applying this rotational resistance, the locked state of the output shaft can be released smoothly during lever operation, improving the operational feeling and adjusting the seat surface height of the seat without causing a sense of incongruity to the passenger. ing.

  However, since the outer peripheral surface of the friction ring is in pressure contact with the inner peripheral surface of the annular recess of the output shaft, the cam surface located on the radially outer side of the annular recess is expanded by the pressing force. Further, the amount of expansion of the cam surface also varies depending on the tightening allowance of the friction ring.

  Therefore, it becomes difficult to manage the dimensions of the cam surface, and the engagement and disengagement between the outer ring and the output shaft up to the wedge clearance stably shuts off the rotational torque from the output shaft and transmits the rotational torque from the lever side clutch. It becomes difficult to control.

  Further, since the friction ring is made of resin, the friction ring expands or contracts depending on the usage environment of the clutch unit, that is, the temperature at the brake side clutch portion. Due to the expansion or contraction of the friction ring, the rotational resistance applied to the output shaft by the friction ring is likely to change.

  As a result, it becomes difficult to give a stable rotational resistance to the output shaft. When unlocking the output shaft of the brake side clutch portion by lever operation, it becomes difficult to stably unlock the output shaft, resulting in instability of lever operation.

  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 prevent the cam surface from expanding and suppress the adverse effects of temperature in the usage environment. It is in.

  The clutch unit according to the present invention transmits an input-side clutch portion that controls transmission and cutoff of input rotational torque, and transmits rotational torque from the input-side clutch portion to the output side, and is reversely input from the output side. The basic structure which consists of an output side clutch part which interrupts | blocks rotational torque is comprised.

  As technical means for achieving the above-mentioned object, the output-side clutch portion of the present invention includes a stationary member whose rotation is constrained, an output member from which rotation is output, and a stationary member attached and fixed to the output member. A braking member that imparts rotational resistance, and the braking member is a metal friction plate that presses against the axial end surface of the output member and provides rotational resistance to the output member with sliding torque generated by the pressure contact It is characterized by.

  In the present invention, the braking member is a metal friction plate, and the friction plate is brought into pressure contact with the axial end surface of the output member, and rotational resistance is applied to the output member with a sliding torque generated by the pressure contact. In this way, by pressing the friction plate against the axial end surface of the output member, it is possible to prevent the cam surface located on the radially outer side of the output member from expanding. Moreover, since the friction plate is made of metal, adverse effects due to temperature in the use environment can be suppressed.

  The brake member in the present invention preferably has a structure in which the elastic member attached to the output member is in elastic contact with the axial end surface of the output member.

  If such a structure is adopted, the braking member can be brought into pressure contact with the output member by a simple means called an elastic member, and rotational resistance can be easily applied to the output member with the sliding torque generated by the pressure contact. it can.

  The brake member according to the present invention preferably has a structure that is fixedly attached to the stationary member by concave-convex fitting in the circumferential direction.

  If such a structure is adopted, the braking member can be attached to and fixed to the stationary member by a simple means such as a concave-convex fitting in the circumferential direction, and the braking member can be easily integrated with the stationary member.

  The clutch unit according to the present invention preferably has a structure in which the input-side clutch portion and the output-side clutch portion are incorporated in the vehicle seat lifter portion.

  If such a structure is adopted, the input side clutch part is a lever side clutch part to which rotational torque is input by lever operation, and the output side clutch part is a brake side clutch part, so that it can be easily added to an automobile seat lifter part. Can be applied.

  According to the present invention, the braking member is made of a metal friction plate, the friction plate is brought into pressure contact with the axial end surface of the output member, and rotational resistance is applied to the output member with the sliding torque generated by the pressure contact. In this way, by pressing the friction plate against the axial end surface of the output member, it is possible to prevent the cam surface located on the radially outer side of the output member from expanding. Moreover, since the friction plate is made of metal, adverse effects due to temperature in the use environment can be suppressed.

  As a result, it becomes easy to manage the dimensions of the cam surface, and it is possible to stably control the interruption of the rotational torque from the output member and the transmission of the rotational torque from the input side clutch portion. In addition, the rotational resistance applied to the output member by the friction plate is difficult to change, and when the output member of the output side clutch portion is unlocked, the locked state of the output member can be stably released.

It is sectional drawing which shows a clutch unit in embodiment of this invention. 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 a block diagram which shows the seat seat and seat lifter part of a motor vehicle. It is a perspective view which shows the side plate and friction plate of FIG. It is sectional drawing which shows the clutch unit in other embodiment of this invention.

  An embodiment of a clutch unit according to the present invention will be described in detail with reference to the drawings. 1 is a cross-sectional view showing the overall configuration of the clutch unit of this embodiment, FIG. 2 is a cross-sectional view taken along the line P-P in FIG. 1, and FIG. 3 is a cross-sectional view taken along the line Q-Q in FIG.

  In the following embodiments, a clutch unit incorporated in an automobile seat lifter is illustrated, but the present invention can be applied to other than the seat lifter. Before describing the characteristic configuration of this embodiment, the overall configuration of the clutch unit will be described.

  As shown in FIG. 1, the clutch unit 10 of this embodiment has a structure in which a lever side clutch portion 11 as an input side clutch portion and a brake side clutch portion 12 as an output side clutch portion are unitized.

  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 transmits to the brake side clutch unit 12 the side plate 13 and the outer ring 14 to which rotational torque is input by lever operation, and the rotational torque input from the outer ring 14. Inner ring 15, a plurality of cylindrical rollers 16 that control transmission and interruption of rotational torque from outer ring 14 by engagement and disengagement between outer ring 14 and inner ring 15, and each cylindrical roller 16 is held at equal intervals in the circumferential direction. A cage 17, 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 are provided.

  The side plate 13 and the outer ring 14 are inserted into a notch recess 14a formed on the outer peripheral edge of the outer ring 14 and crimped by inserting a claw portion 13a formed on the outer peripheral edge of the side plate 13, thereby tightening the side plate 13 on the outer ring 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. The input of the rotational torque to the outer ring 14 is performed by an operation lever 43 (see FIG. 4) that can swing in the vertical direction and is attached to the side plate 13 by screwing or the like.

  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 pillars 15c (see FIG. 3) that protrude by bending the part to one side in the axial direction (brake side clutch part 12 side). A wedge clearance 20 is formed between the cylindrical outer peripheral surface 15 d of the cylindrical portion 15 a of the inner ring 15 and the cam surface 14 b formed on the inner periphery of the outer ring 14. Cylindrical rollers 16 are arranged in the wedge clearance 20 by a cage 17 at equal intervals in the circumferential direction.

  The inner centering spring 18 is a C-shaped elastic member having a circular cross section disposed between the cage 17 and the cover 24 of the brake side clutch portion 12, and both ends thereof are part of the cage 17 and the cover 24. It is locked. The inner centering spring 18 is 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, and elastic force is applied. When the rotational torque 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 positioned radially outside the inner centering spring 18 is a C-shaped strip elastic member disposed between the outer ring 14 and the cover 24, and both ends of the outer centering spring 19 are located at one end of the outer ring 14 and the cover 24. It is locked to the part. 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 the lever operation is applied, and an elastic force is accumulated. When the rotational torque is released, the outer ring 14 is returned to the neutral state by the elastic force.

  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. Both end portions of the inner centering spring 18 are locked to one axial end portion of the cage 17, that is, the axial end portion on the cover 24 side of the brake side clutch portion 12. The cage 17 is disposed between the outer ring 14 and the inner ring 15.

  As shown in FIGS. 1 and 3, the brake-side clutch portion 12 of a type called a lock type includes an inner ring 15 to which rotational torque from the lever-side clutch portion 11 is input, and rotation from the lever-side clutch portion 11. The output shaft 22 serving as an output member from which torque is output, the outer ring 23, the cover 24, and the side plate 25 serving as stationary members whose rotation is restricted, and the engagement and disengagement between the outer ring 23 and the output shaft 22, thereby the output shaft 22 is applied to a plurality of pairs of cylindrical rollers 27 for controlling the interruption of the rotational torque input from 22 and the transmission of the rotational torque input from the inner ring 15, and a separation force in the circumferential direction is applied to each pair of cylindrical rollers 27. The main part is composed of a plate spring 28 having an N-shaped cross section and a friction plate 29 as a braking member for imparting rotational resistance to the output shaft 22.

  The shaft portion 22a of the output shaft 22 into which the cylindrical portion 15a of the inner ring 15 is extrapolated is integrally formed with a large-diameter portion 22b whose diameter is increased radially outward. A pinion gear 22d for connecting to the seat lifter 39 (see FIG. 4) is formed coaxially at the output side end of the shaft 22a. Further, the washer 31 is press-fitted into the input side end portion of the shaft portion 22a via the wave washer 30 to prevent the component parts of the lever side clutch portion 11 from coming off.

  A plurality (for example, six) of flat cam surfaces 22e are formed on the outer periphery of the large-diameter portion 22b of the output shaft 22 at equal intervals in the circumferential direction. One plate interposed between the two cylindrical rollers 27 and the two cylindrical rollers 27 in a wedge clearance 26 formed between the cam surface 22e of the large diameter portion 22b and the cylindrical inner peripheral surface 23a of the outer ring 23. Each of the springs 28 is arranged.

  The cylindrical rollers 27 and the leaf springs 28 are arranged at equal intervals in the circumferential direction by column 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 column 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 and disposed in a hole 15e formed in the enlarged diameter portion 15b of the inner ring 15 with a circumferential clearance.

  The outer ring 23, the cover 24, and the side plate 25 are formed on the outer peripheral edge portion of the side plate 25 by the notch concave portion 23 b formed on the outer peripheral edge portion of the outer ring 23 and the notched concave portion 24 a formed on the outer peripheral edge portion of the cover 24. By inserting and crimping the formed claw portion 25a, 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.

  An operation example of the lever side clutch portion 11 and the brake side clutch portion 12 having the above-described configuration will be described below.

  In the lever side clutch portion 11, 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. Due to the engagement of the cylindrical roller 16 in the wedge clearance 20, rotational torque is transmitted to the inner ring 15 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 there is no input of rotational torque by lever operation, 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. On the other hand, the inner ring 15 maintains the given rotational position as it is. 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 43 (see FIG. 4).

  In the brake-side clutch portion 12, 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 by sitting on the seat, and the output shaft 22 Locked to the outer ring 23. In this way, the rotational torque reversely input from the output shaft 22 is locked by the brake side clutch portion 12 and the return of the rotational torque reversely input to the lever side clutch portion 11 is blocked. Thereby, the seat surface height of the seat is maintained.

  On the other hand, when the rotational torque from the lever side clutch portion 11 is input to the inner ring 15 by lever operation, the column portion 15 c of the inner ring 15 comes into contact with the cylindrical roller 27 and resists the elastic force of the leaf spring 28. Press. As a result, the cylindrical roller 27 is detached from the wedge clearance 26, and the locked state of the output shaft 22 is released by the separation of the cylindrical roller 27 from the wedge clearance 26, so that the output shaft 22 can rotate. When the locked state of the output shaft 22 is released, a rotational resistance is applied to the output shaft 22 by the friction plate 29.

  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. Contact in the rotational direction. Thereby, the rotational torque from the lever side clutch part 11 is transmitted to the output shaft 22 via the protrusion 22f, and the output shaft 22 rotates. That is, when the inner ring 15 is jogged and rotated, the output shaft 22 is also jogged and rotated. Thereby, the seat surface height of the seat can be adjusted.

  The clutch unit 10 having the above-described structure is used by being incorporated in an automobile seat lifter unit 39 that adjusts the height of the seat 40 by lever operation. FIG. 4 shows a seat 40 installed in the passenger compartment of the automobile.

  As shown in FIG. 4, the seat 40 includes a seat 41 and a backrest 42, and the seat lifter 39 adjusts the height of the seat surface of the seat 41. The height of the seating seat 41 is adjusted by the operation lever 43 attached to the side plate 13 (see FIG. 1) of the lever side clutch portion 11 in the clutch unit 10.

  The sheet lifter unit 39 has the following structure. One end of each of the link members 45 and 46 is pivotally attached to the slide movable member 44 so as to be rotatable. The other ends of the link members 45 and 46 are pivotally attached to the seating seat 41, respectively. A sector gear 47 is integrally provided at the other end of the link member 45. The sector gear 47 meshes with the pinion gear 22 d of the output shaft 22 of the clutch unit 10.

  For example, when the seating surface of the seating seat 41 is lowered, the lever side clutch portion 11 is operated, that is, the operation lever 43 is swung downward to lock the brake side clutch portion 12 (see FIG. 1). Release the state. When the brake side clutch portion 12 is unlocked, the seating surface of the seating seat 41 can be lowered smoothly by applying an appropriate rotational resistance to the output shaft 22 by the friction plate 29 (see FIG. 1).

  By releasing the lock at the brake side clutch portion 12, the pinion gear 22d of the output shaft 22 of the brake side clutch portion 12 is rotated clockwise (in FIG. 4) with the rotational torque transmitted from the lever side clutch portion 11 to the brake side clutch portion 12. It rotates in the direction of the arrow. Then, the sector gear 47 that meshes with the pinion gear 22d swings counterclockwise (the arrow direction in FIG. 4), and both the link member 45 and the link member 46 are tilted to lower the seating surface of the seating seat 41.

  In this way, after adjusting the height of the seating surface of the seating seat 41, when the operation lever 43 is released, the operation lever 43 swings upward by the elastic force of the centering springs 18 and 19, and returns to its original position (neutral). Return to the state. When the operation lever 43 is swung upward, the seating surface of the seating seat 41 is raised by the reverse operation to that described above. When the operation lever 43 is released after the height of the seating seat 41 is adjusted, the operation lever 43 swings downward and returns to the original position (neutral state).

  The overall configuration of the clutch unit 10 and the seat lifter 39 in which the clutch unit 10 is incorporated in this embodiment are as described above. The friction plate 29 that is a characteristic configuration of the clutch unit 10 will be described in detail below. To do.

  In the brake-side clutch portion 12, when the output shaft 22 is unlocked, the friction plate 29 that imparts rotational resistance to the output shaft 22 is pressed against the axial end surface 22h of the annular recess 22g of the output shaft 22, as shown in FIG. And it is a metal strip ring-shaped member which gives rotational resistance to the output shaft 22 with the sliding torque which arises by the press-contact (refer FIG. 5). The friction plate 29 is provided between the large diameter portion 22 b and the wave spring 33.

  In this embodiment, as shown in FIGS. 1 and 3, an annular groove 32 is formed on the inner peripheral surface 22 i of the annular recess 22 g of the output shaft 22. A wave spring 33, which is an elastic member, is fitted in the concave groove 32. That is, the wave spring 33 is attached to the output shaft 22. The wave spring 33 brings the friction plate 29 into elastic contact with the axial end surface 22h of the annular recess 22g, and sliding force is generated by this elastic contact.

  The friction plate 29 is attached and fixed to the side plate 25 by circumferential uneven fitting. As shown in FIGS. 3 and 5, a plurality of convex portions 29 a are formed on the inner peripheral surface of the friction plate 29 along the circumferential direction, and a plurality of cylindrical portions 25 b extending in the axial direction from the inner periphery of the side plate 25 are provided. The recess 25c is formed along the circumferential direction. And the convex part 29a of the friction board 29 and the recessed part 25c of the side plate 25 are fitted. Thereby, the friction plate 29 cannot be rotated together with the side plate 25.

  Note that the convex portion 29a of the friction plate 29 is securely fitted into the concave portion 25c of the cylindrical portion 25b of the side plate 25 by slightly bending the convex portion 29a of the friction plate 29 to the side plate 25 side (see FIGS. 1 and 5). I try to let them.

  Thus, the friction plate 29 can be attached and fixed to the side plate 25 by a simple means of a fitting structure of the convex portion 29 a of the friction plate 29 and the concave portion 25 c of the side plate 25, and the friction plate 29 is integrated with the side plate 25. It becomes easy to make it. The friction plate 29 may be attached and fixed to the side plate 25 by other fixing means other than the above-described uneven fitting.

  By adopting the friction plate 29 having the above configuration, the friction plate 29 is moved by the wave spring 33 in the axial direction of the annular recess 22g of the output shaft 22 when the brake side clutch portion 12 releases the locked state of the output shaft 22. It is elastically pressed against the end face 22h.

  The axial end surface 22h of the annular recess 22g slides with respect to the end surface 29b of the friction plate 29 by a frictional force generated between the end surface 29b of the friction plate 29 and the axial end surface 22h of the annular recess 22g by this elastic contact. . Thereby, an appropriate rotational resistance (sliding torque) is applied to the output shaft 22. By applying this rotational resistance, the seating surface of the seating seat 41 (see FIG. 4) can be adjusted smoothly.

  In this way, by pressing the friction plate 29 against the axial end surface 22h of the output shaft 22, no pressing force acts on the inner peripheral surface 22i of the annular recess 22g. Therefore, it is possible to prevent the cam surface 22e located on the radially outer side of the annular recess 22g from expanding. As a result, the dimensional management of the cam surface 22e is facilitated, and the interruption of the rotational torque from the output shaft 22 and the transmission of the rotational torque from the lever side clutch portion 11 can be controlled stably.

  Further, since the friction plate 29 is made of metal, it is possible to suppress expansion or contraction due to the temperature at the brake side clutch portion 12. For this reason, adverse effects due to temperature in the use environment can be suppressed. As a result, the rotational resistance applied to the output shaft 22 by the friction plate 29 is unlikely to change, and the locked state of the output shaft 22 can be stably released, and a stable lever operation can be realized.

  In this embodiment, the friction plate 29 is elastically brought into contact with the axial end surface 22 h of the output shaft 22 by a wave spring 33 attached to the inner peripheral surface 22 i of the annular recess 22 g of the output shaft 22. As described above, the friction plate 29 can be brought into pressure contact with the output shaft 22 by a simple means such as the wave spring 33, and the rotational resistance can be easily applied to the output shaft 22 by the sliding torque generated by the pressure contact.

  In the above embodiment, the case where the wave spring 33 is used as the elastic member has been described. However, an elastic member other than the wave spring 33 may be used. For example, as shown in FIG. 6, a structure using a disc spring 34 as an elastic member may be used. In FIG. 6, the same parts as those of FIG.

  In the embodiment shown in FIG. 6, an annular groove 35 is formed on the inner peripheral surface 22 i of the annular recess 22 g of the output shaft 22, and a retaining ring 36 is fitted in the annular groove 35. A disc spring 34 is interposed between the retaining ring 36 and the friction plate 29.

  Thus, by restricting the position of the disc spring 34 by the retaining ring 36, the disc spring 34 is brought into contact with the friction plate 29, and the disc plate spring 34 causes the friction plate 29 to end in the axial direction of the annular recess 22 g of the output shaft 22. 22h for elastic contact.

  The axial end surface 22h of the annular recess 22g slides with respect to the end surface 29b of the friction plate 29 by a frictional force generated between the end surface 29b of the friction plate 29 and the axial end surface 22h of the annular recess 22g by this elastic contact. . Thereby, an appropriate rotational resistance (sliding torque) is applied to the output shaft 22. By applying this rotational resistance, the seating surface of the seating seat 41 (see FIG. 4) can be adjusted smoothly.

  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.

10 Clutch unit 11 Input side clutch (lever side clutch)
12 Output side clutch (brake side clutch)
22 Output member (output shaft)
22h Axial end face 25 Stationary member (side plate)
25c Concave part (concave fitting)
29 Braking member (friction ring)
29a Convex part (concave unevenness)
33 Elastic member (wave spring)
34 Elastic member (Belleville spring)
39 Seat lifter

Claims (4)

An input side clutch unit that controls transmission and cutoff of input rotational torque, and an output side clutch that transmits rotational torque from the input side clutch unit to the output side and blocks rotational torque that is reversely input from the output side And consists of
The output-side clutch unit includes a stationary member whose rotation is constrained, an output member from which rotation is output, and a braking member that is attached and fixed to the stationary member and applies rotational resistance to the output member. The clutch unit is characterized in that the member is a metal friction plate that presses against an axial end surface of the output member and applies rotational resistance to the output member with a sliding torque generated by the press contact.   2. The clutch unit according to claim 1, wherein the braking member is in elastic contact with an axial end surface of the output member by an elastic member attached to the output member.   The clutch unit according to claim 1 or 2, wherein the braking member is attached and fixed to the stationary member by a concave-convex fitting in a circumferential direction.   The clutch unit as described in any one of Claims 1-3 in which the said input side clutch part and the said output side clutch part are integrated in the seat lifter part for motor vehicles.

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