Clutch unit including an elastic member configured to apply an elastic force toward a direction of releasing a meshing state between a gear member and a stationary member

Abstract

A clutch unit includes a lever-side clutch part that controls transmission and interruption of rotational torque input through a lever operation, and a brake-side clutch part that transmits the rotational torque from the lever-side clutch part to an output side, and interrupts rotational torque reversely input from the output side. The brake-side clutch part includes an outer ring, which is constrained in rotation, an output shaft that outputs the rotation, and a cylindrical roller that controls the interruption of the rotational torque reversely input from the output shaft and the transmission of the rotational torque input from the lever-side clutch part through engagement and disengagement between the outer ring and the output shaft. The output shaft includes a slide gear, which meshes with a side plate during interruption of the rotational torque and does not mesh with the side plate during transmission of the rotational torque.

Claims

1. A clutch unit, comprising: a lever-side clutch part, which is provided on an input side, and is configured to control transmission and interruption of a rotational torque to be input through a lever operation; and a brake-side clutch part, which is provided on an output side, and is configured to transmit the rotational torque from the lever-side clutch part to the output side, and interrupt a rotational torque to be reversely input from the output side, wherein the brake-side clutch part comprises: a stationary member, which is constrained in rotation; an output member configured to output the rotation; and an engaging element configured to control the interruption of the rotational torque to be reversely input from the output member and the transmission of the rotational torque to be input from the lever-side clutch part through engagement and disengagement between the stationary member and the output member, wherein the output member comprises a gear member mounted thereto, which meshes with the stationary member during interruption of the rotational torque and is released from the meshing state with the stationary member during transmission of the rotational torque, and wherein an elastic member configured to apply an elastic force toward a direction of releasing the meshing state between the gear member and the stationary member is interposed between the stationary member and the gear member.

2. The clutch unit according to claim 1, wherein the gear member is arranged so as to be movable in an axial direction relative to the stationary member, and wherein a cam mechanism configured to move the gear member in the axial direction to control the meshing with the stationary member and the release of the meshing state is interposed between the gear member and an input member configured to receive the rotational torque to be input from the lever-side clutch part.

3. The clutch unit according to claim 1, wherein the lever-side clutch part and the brake-side clutch part are assembled to a seat lifter part for an automobile.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1 is a sectional view for illustrating an overall configuration of a clutch unit according to an embodiment of the present invention.

(2) FIG. 2 is a sectional view taken along the line P-P in FIG. 1.

(3) FIG. 3 is a sectional view taken along the line Q-Q in FIG. 1.

(4) FIG. 4 is an assembly exploded perspective view for illustrating the clutch unit of FIG. 1.

(5) FIG. 5 is a partial enlarged sectional view for illustrating a cam mechanism in a neutral state in the clutch unit of FIG. 1.

(6) FIG. 6 is a partial enlarged sectional view for illustrating the cam mechanism in an operation state in the clutch unit of FIG. 1.

(7) FIG. 7 is a sectional view for illustrating an operation state of the clutch unit of FIG. 1.

(8) FIG. 8 is a configuration view for illustrating a seat for an automobile and a seat lifter part.

DESCRIPTION OF EMBODIMENTS

(9) Detailed description is now given of a clutch unit according to an embodiment of the present invention with reference to the drawings. FIG. 1 is a sectional view for illustrating an overall configuration of the clutch unit according to this embodiment. FIG. 2 is a sectional view taken along the line P-P in FIG. 1. FIG. 3 is a sectional view taken along the line Q-Q in FIG. 1. Before description of a characteristic configuration of this embodiment, description is now given of the overall configuration of the clutch unit.

(10) As illustrated in FIG. 1, a clutch unit 10 according to this embodiment has a unit structure integrally comprising a lever-side clutch part 11 and a brake-side clutch part 12. The lever-side clutch part 11 is provided on an input side, and the brake-side clutch part 12 is provided on an output side. The lever-side clutch part 11 is configured to control transmission and interruption of a rotational torque to be input through a lever operation. The brake-side clutch part 12 has a reverse input interrupting function of transmitting the rotational torque from the lever-side clutch part 11 to the output side and interrupting the rotational torque to be reversely input from the output side.

(11) As illustrated in FIG. 1 and FIG. 2, the lever-side clutch part 11 comprises a side plate 13, an outer ring 14, an inner ring 15, a plurality of cylindrical rollers 16, a cage 17, an inner centering spring 18, and an outer centering spring 19. The side plate 13 and the outer ring 14 are configured to receive the rotational torque to be input through the lever operation. The inner ring 15 is configured to transmit the rotational torque to be input from the outer ring 14 to the brake-side clutch part 12. The plurality of cylindrical rollers 16 are configured to control transmission and interruption of the rotational torque from the outer ring 14 through engagement and disengagement between the outer ring 14 and the inner ring 15. The cage 17 is configured to retain the cylindrical rollers 16 at equal intervals in a circumferential direction. The inner centering spring 18 is configured to return the cage 17 to a neutral state. The outer centering spring 19 is configured to return the outer ring 14 to a neutral state.

(12) In the lever-side clutch part 11, the side plate 13 is fixed to the outer ring 14 by inserting claw parts 13a formed on an outer peripheral edge portion of the side plate 13 into cutout recessed parts 14a formed in an outer peripheral edge portion of the outer ring 14, and crimping the claw parts 13a, thereby forming an integrated input member of the lever-side clutch part 11. A plurality of cam surfaces 14b are formed at equal intervals in the circumferential direction on an inner periphery of the outer ring 14. The input of the rotational torque to the outer ring 14 is performed through an operation lever 43 (see FIG. 8), which is mounted to the side plate 13 by screwing or the like and is swingable in a vertical direction.

(13) The inner ring 15 comprises a tubular part 15a, a radially expanded part 15b, and a plurality of pillar parts 15c. The tubular part 15a is configured to receive an output shaft 22 inserted therethrough. The radially expanded part 15b is formed by extending an end portion of the tubular part 15a on a brake side radially outward. The plurality of pillar parts 15c are formed so as to protrude by bending an outer peripheral end portion of the radially expanded part 15b in an axial direction (see FIG. 3). A wedge gap 20 is formed between a cylindrical surface 15d formed on an outer periphery of the tubular part 15a of the inner ring 15 and each of the cam surfaces 14b formed on the inner periphery of the outer ring 14. The cylindrical rollers 16 are arranged in the wedge gaps 20 at the equal intervals in the circumferential direction by the cage 17.

(14) The inner centering spring 18 is a C-shaped elastic member having a circular cross section and is provided between the cage 17 and a cover 24, which is a stationary member of the brake-side clutch part 12. Both end portions of the inner centering spring 18 are locked to parts of the cage 17 and the cover 24. When the rotational torque to be input from the outer ring 14 through the lever operation is applied, the inner centering spring 18 is spread outward as the cage 17 following the outer ring 14 rotates relative to the cover 24 in a stationary state, and an elastic force is thus accumulated. When the rotational torque to be input from the outer ring 14 is released, the inner centering spring 18 returns the cage 17 to the neutral state by the elastic force.

(15) The outer centering spring 19 positioned on a radially outer side with respect to the inner centering spring 18 is a C-shaped band-plate elastic member arranged between the outer ring 14 and the cover 24. Both end portions of the outer centering spring 19 are locked to parts of the outer ring 14 and the cover 24. When the rotational torque to be input from the outer ring 14 through the lever operation is applied, the outer centering spring 19 is spread outward as the outer ring 14 rotates relative to the cover 24 in a stationary state, and an elastic force is thus accumulated. When the rotational torque to be input from the outer ring 14 is released, the outer centering spring 19 returns the outer ring 14 to the neutral state by the elastic force.

(16) The cage 17 is a cylindrical member made of resin in which a plurality of pockets 17a configured to receive the cylindrical rollers 16 are formed at the equal intervals in the circumferential direction. Both of the end portions of the inner centering spring 18 are locked to one end portion of the cage 17 in the axial direction, that is, an end portion of the brake-side clutch part 12 on the cover 24 side in the axial direction. The cage 17 is arranged 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 part 12 in the axial direction.

(17) As illustrated in FIG. 1 and FIG. 3, the brake-side clutch part 12, which is of a type called lock type and has the reverse input interrupting function, mainly comprises the inner ring 15, the output shaft 22, an outer ring 23, the cover 24, a side plate 25, a plurality of pairs of cylindrical rollers 27, and plate springs 28. The inner ring 15 serves as an input member configured to receive the rotational torque to be input from the lever-side clutch part 11. The output shaft 22 serves as an output member configured to output the rotational torque from the lever-side clutch part 11. The outer ring 23, the cover 24, and the side plate 25 serve as a stationary member which is constrained in rotation. The plurality of pairs of cylindrical rollers 27 are configured to control interruption of the rotational torque to be reversely input from the output shaft 22 and transmission of the rotational torque to be input from the inner ring 15 through engagement and disengagement between the outer ring 23 and the output shaft 22. The plate springs 28 each have an N-shaped cross section, and are configured to apply a separating force in the circumferential direction to the pairs of cylindrical rollers 27.

(18) In the output shaft 22, a large-diameter part 22b extending outward in the radial direction so as to have a larger diameter is formed integrally with a center portion of a shaft part 22a in the axial direction on which the tubular part 15a of the inner ring 15 is externally inserted. A pinion gear 22d configured to be coupled to a seat lifter part 41 (see FIG. 8) is coaxially formed at an end portion of the shaft part 22a on an output side. Moreover, a washer 31 is press-fitted to an end portion of the shaft part 22a on an input side through intermediation of a wave washer 30, thereby preventing removal of the components of the lever-side clutch part 11.

(19) A plurality of flat cam surfaces 22e are formed at equal intervals in the circumferential direction on an outer periphery of the large-diameter part 22b of the output shaft 22. The two cylindrical rollers 27 and the one plate spring 28 interposed between the two cylindrical rollers 27 are arranged in each of wedge gaps 26 formed between each of the cam surfaces 22e of the large-diameter part 22b and a cylindrical inner peripheral surface 23a of the outer ring 23. The cylindrical rollers 27 and the plate springs 28 are arranged at the equal intervals in the circumferential direction by the pillar parts 15c of the inner ring 15.

(20) In this case, the inner ring 15 has a function as an input member of the brake-side clutch part 12 by transmitting the rotational torque to be input from the outer ring 14 of the lever-side clutch part 11 to the output shaft 22 through the radially expanded part 15b, and a function as a cage by receiving the cylindrical rollers 27 and the plate springs 28 in pockets 15h and retaining the cylindrical rollers 27 and the plate springs 28 at the equal intervals in the circumferential direction by the pillar parts 15c. Hereinafter, the pillar parts 15c of the inner ring 15 are referred to as a cage 15c.

(21) The outer ring 23, the cover 24, and the side plate 25 are integrated as a stationary member of the brake-side clutch part 12 by inserting claw parts 25a formed on an outer peripheral edge portion of the side plate 25 into cutout recessed parts 23b formed in an outer peripheral edge portion of the outer ring 23 in a thick plate shape and cutout recessed parts 24a (see FIG. 4) formed in an outer peripheral edge portion of the cover 24, and crimping the claw parts 25a, thereby fixing the side plate 25 to the outer ring 23 and the cover 24 (see FIG. 3).

(22) Description is now given of an operation example of the lever-side clutch part 11 and the brake-side clutch part 12 having the configuration described above.

(23) In the lever-side clutch part 11, when the rotational torque is input to the outer ring 14 through the lever operation, the cylindrical rollers 16 are engaged with the wedge gaps 20 between the outer ring 14 and the inner ring 15. The rotational torque is transmitted to the inner ring 15 thorough the engagement of the cylindrical rollers 16 in the wedge gaps 20, thereby rotating the inner ring 15. On this occasion, as the outer ring 14 and the cage 17 rotate, the elastic forces are accumulated in both of the centering springs 18 and 19.

(24) When the input of the rotational torque is lost, the cage 17 and the outer ring 14 return to the respective neutral states by the elastic forces of both of the centering springs 18 and 19. Meanwhile, the inner ring 15 maintains a given rotational position. Thus, the inner ring 15 rotates in an inching manner by repetition of the rotation of the outer ring 14, that is, a pumping operation on the operation lever 43.

(25) In the brake-side clutch part 12, even when a rotational torque is reversely input to the output shaft 22 by seating on a seat 40, the cylindrical rollers 27 are engaged with the wedge gaps 26 between the output shaft 22 and the outer ring 23, and the output shaft 22 is thus locked to the outer ring 23. In such a manner, the rotational torque to be reversely input from the output shaft 22 is locked by the brake-side clutch part 12, and reverse transmission to the lever-side clutch part 11 is interrupted. As a result, the seat 40 is fixed, and cannot thus be vertically adjusted.

(26) Meanwhile, when the rotational torque is input from the inner ring 15 of the lever-side clutch part 11 to the cage 15c through the lever operation, the cage 15c rotates to be brought into abutment against the cylindrical rollers 27, and presses the cylindrical rollers 27 against the elastic forces of the plate springs 28. With this, the cylindrical rollers 27 are disengaged from the wedge gaps 26. As a result of the disengagement of the cylindrical rollers 27 from the wedge gaps 26, the locked state of the output shaft 22 is released, and the output shaft 22 thus becomes rotatable.

(27) When the cage 15c further rotates, the rotational torque from the lever-side clutch part 11 is transmitted to the output shaft 22 through abutment of stopper surfaces 15g of cam grooves 15e in a cam mechanism 33 described later against protrusions 32b of a slide gear 32 (see FIG. 6), thereby rotating the output shaft 22. In other words, when the cage 15c rotates in the inching manner, the output shaft 22 also rotates in the inching manner. As a result, the seat 40 can be vertically adjusted.

(28) The overall configuration of the clutch unit 10 according to this embodiment is as described above. Detailed description is now given of the characteristic configuration of the clutch unit 10.

(29) While the output shaft 22 is locked in the brake-side clutch part 12, when a vertical vibration is generated during travelling of a vehicle on a rough road or the like in a seating state on the seat 40 (see FIG. 8), a rotational torque in a forward direction and a rotational torque in a backward direction are reversely input in an alternate and continuous manner to the output shaft 22. In order to reliably lock the output shaft 22 even when the rotational torques in the forward and backward directions are reversely input in a continuous manner to the output shaft 22, the following structure is provided.

(30) As illustrated in FIG. 1, FIG. 3, and FIG. 4, the brake-side clutch part 12 in this embodiment has such a structure that the output shaft 22 comprises the slide gear 32 being a gear member mounted thereto, which meshes with the side plate 25 during interruption of the rotational torque and is released from the meshing state with the side plate 25 during transmission of the rotational torque. The slide gear 32 is arranged so as to be movable in the axial direction relative to the side plate 25 under a state in which the slide gear 32 is accommodated in an annular recessed part 22c formed in the large-diameter part 22b of the output shaft 22.

(31) The slide gear 32 is a ring-shaped member having, on an inner periphery thereof, a teeth part 32a (hereinafter referred to as internal teeth). In correspondence to this configuration, a teeth part 25b (hereinafter referred to as external teeth) corresponding to the internal teeth 32a of the slide gear 32 is formed on an inner periphery of the side plate 25. The internal teeth 32a of the slide gear 32 and the external teeth 25b of the side plate 25 can mesh with each other.

(32) Meanwhile, the cam mechanism 33 (see FIG. 1) configured to move the slide gear 32 in the axial direction, to thereby control the meshing of the slide gear 32 with the side plate 25 and the release of the meshing state is interposed between the slide gear 32 and the radially expanded part 15b of the inner ring 15 configured to function as an input member of the brake-side clutch part 12.

(33) The cam mechanism 33 comprises the protrusions 32b formed on an end surface of the slide gear 32 so as to extend in the axial direction, and the cam grooves 15e formed in the circumferential direction in an end surface of the radially expanded part 15b of the inner ring 15 (see FIG. 4).

(34) The protrusions 32b are formed at a plurality of locations in the circumferential direction at equal intervals on the end surface of the slide gear 32. Moreover, the cam grooves 15e are formed at a plurality of locations in the circumferential direction at equal intervals in the radially expanded part 15b of the inner ring 15 so as to correspond to the protrusions 32b of the slide gear 32. The four protrusions 32b and the four cam grooves 15e are exemplified in this embodiment, but the numbers are suitably set.

(35) Holes 22f through which the protrusions 32b of the slide gear 32 are to be inserted are formed through the large-diameter part 22b of the output shaft 22. The holes 22f are formed at a plurality of locations in the circumferential direction at equal intervals in the large-diameter part 22b of the output shaft 22 so as to correspond to the protrusions 32b of the slide gear 32.

(36) As illustrated in FIG. 5 and FIG. 6, a distal-end curve forming part 32c of each of the protrusions 32b of the slide gear 32 is brought into abutment against a cam surface 15f of each of the cam grooves 15e of the inner ring 15 via each of the holes 22f of the large-diameter part 22b of the output shaft 22 in the cam mechanism 33. The cam surface 15f comprises a crest portion positioned at the center in the cam groove 15e, inclined portions extending from the crest portion toward both sides in the circumferential direction, and groove bottom portions extending from the inclined portions toward the both sides in the circumferential direction.

(37) Moreover, stopper surfaces 15g are formed at both ends in a circumferential direction of the cam groove 15e so as to rise in the axial direction from the groove bottom portions of the cam surface 15f. The stopper surface 15g has a function of transmitting the rotational torque from the inner ring 15 of the lever-side clutch part 11 to the output shaft 22 through abutment against the protrusion 32b of the slide gear 32.

(38) In other words, when the inner ring 15 is rotated by the rotational torque from the lever-side clutch part 11, in a rotation direction, the stopper surface 15g of each of the cam grooves 15e of the inner ring 15 is brought into abutment against each of the protrusions 32b of the slide gear 32 protruding from each of the holes 22f of the large-diameter part 22b of the output shaft 22 in the cam mechanism 33. The rotational torque of the inner ring 15 is transmitted to the output shaft 22 through abutment between the stopper surfaces 15g of the cam grooves 15e and the protrusions 32b of the slide gear 32, and the output shaft 22 thus rotates.

(39) The slide gear 32 is assembled to the output shaft 22 by accommodating the slide gear 32 in the annular recessed part 22c of the output shaft 22. On this occasion, as a result of the insertion of the protrusions 32b of the slide gear 32 through the holes 22f of the large-diameter part 22b of the output shaft 22, the movement of the slide gear 32 in the axial direction relative to the side plate 25 is permitted, and the movement (rotation) of the slide gear 32 in the circumferential direction relative to the output shaft 22 is prevented.

(40) Moreover, as illustrated in FIG. 1 and FIG. 4, an elastic member 34 configured to apply an elastic force toward a direction of releasing the meshing state between the slide gear 32 and the side plate 25 is interposed between the side plate 25 and the slide gear 32. As the elastic member 34, for example, a wave spring having a ring shape as illustrated in FIG. 4 is preferred (see FIG. 4).

(41) The elastic member 34 is configured to apply its elastic force to the side plate 25 and the slide gear 32, to thereby press the slide gear 32 toward the output shaft 22 side with respect to the side plate 25 in the stationary state. As a result, the internal teeth 32a of the slide gear 32 are reliably disengaged from the external teeth 25b of the side plate 25 when the locked state of the output shaft 22 is released.

(42) Moreover, the elastic member 34 has a function of applying the rotational resistance to the output shaft 22 via the slide gear 32 through friction forces generated respectively between the elastic member 34 and the side plate 25 and between the elastic member 34 and the slide gear 32. As a result, the state in which the cylindrical rollers 27 are locked to the outer ring 23 and the output shaft 22 can smoothly be released.

(43) As illustrated in FIG. 5, in the clutch unit 10 according to this embodiment, under a state in which the rotational torque is not input from the outer ring 14 of the lever-side clutch part 11, the distal-end curve forming parts 32c of the protrusions 32b of the slide gear 32 are at neutral positions at which each of the distal-end curve forming parts 32c is brought into abutment against the crest portion of the cam surface 15f of each of the cam grooves 15e of the inner ring 15 in the cam mechanism 33 of the brake-side clutch part 12.

(44) Under the state in which the protrusions 32b of the slide gear 32 are at the neutral positions of the cam grooves 15e, the slide gear 32 is pressed toward the side plate 25 side in the axial direction against the elastic force of the elastic member 34, and the internal teeth 32a of the slide gear 32 and the external teeth 25b of the side plate 25 mesh with each other (see FIG. 1). As a result, the output shaft 22 is brought into the locked state.

(45) In this locked state of the output shaft 22, even when the vertical vibration is generated during travelling of a vehicle on a rough road or the like in the seating state on the seat 40 (see FIG. 8), and a rotational torque in the forward direction and a rotational torque in the backward direction are reversely input in an alternate and continuous manner to the output shaft 22 as a result of the vertical vibration, the internal teeth 32a of the slide gear 32 mesh with the external teeth 25b of the side plate 25, and the output shaft 22 can thus reliably be locked.

(46) In the brake-side clutch part 12, even when contact positions of the cylindrical rollers 27 are slightly displaced between the outer ring 23 and the output shaft 22, or hysteresis of an elastic deformation is present in the output shaft 22, the outer ring 23, and the cylindrical rollers 27 which bear the rotational torque, a gradual rotation of the output shaft 22 can be prevented through the meshing between the internal teeth 32a of the slide gear 32 and the external teeth 25b of the side plate 25.

(47) As a result, occurrence of a phenomenon in which the seat 40 is slightly lowered can be prevented. Moreover, the meshing between the internal teeth 32a of the slide gear 32 and the external teeth 25b of the side plate 25 enables bearing of a high torque on the brake-side clutch part 12.

(48) Meanwhile, when the rotational torque is input from the outer ring 14 of the lever-side clutch part 11, a phase shift occurs between the protrusions 32b of the slide gear 32 and the cam grooves 15e of the inner ring 15 in the cam mechanism 33 of the brake-side clutch part 12.

(49) In other words, when, as indicated by the solid arrow of FIG. 6, the cam surface 15f of each of the cam grooves 15e of the inner ring 15 moves in the circumferential direction relative to the distal-end curve forming part 32c of each of the protrusions 32b of the slide gear 32 as a result of the rotation of the inner ring 15, as indicated by the broken arrow of FIG. 6, each of the protrusions 32b of the slide gear 32 moves axially toward a direction of protruding from each of the holes 22f of the output shaft 22 by the elastic force of the elastic member 34.

(50) Each of the protrusions 32b of the slide gear 32 moves from the crest portion of each of the cam surfaces 15f to the groove bottom portion via the inclined portion as a result of the movement of the cam grooves 15e of the inner ring 15 in the circumferential direction and the movement of the protrusions 32b of the slide gear 32 in the axial direction. In this way, each of the protrusions 32b of the slide gear 32 is brought into abutment against the groove bottom portion of the cam surface 15f of each of the cam grooves 15e.

(51) As described above, as illustrated in FIG. 7, the slide gear 32 moves in the axial direction (see the outlined arrow of FIG. 7) so as to be separated from the side plate 25 by the elastic force of the elastic member 34 as a result of the phase shift between each of the protrusions 32b of the slide gear 32 and each of the cam grooves 15e of the inner ring 15.

(52) As a result of this movement of the slide gear 32 in the axial direction, the internal teeth 32a of the slide gear 32 are disengaged from the external teeth 25b of the side plate 25, and the meshing state between the internal teeth 32a of the slide gear 32 and the external teeth 25b of the side plate 25 is thus released. As a result, the locked state of the output shaft 22 is released, and the output shaft 22 is brought into a rotatable state relative to the outer ring 23.

(53) In this embodiment, there is employed a structure in which the elastic member 34 configured to apply the elastic force toward the direction of releasing the meshing state between the slide gear 32 and the side plate 25 is interposed between the side plate 25 and the slide gear 32 of the brake-side clutch part 12. With this configuration, the internal teeth 32a of the slide gear 32 can reliably be disengaged from the external teeth 25b of the side plate 25 by the elastic force of the elastic member 34 when the locked state of the output shaft 22 is released.

(54) Moreover, when the locked state of the output shaft 22 is released, the rotational resistance can be applied to the output shaft 22 via the slide gear 32 through the friction forces generated respectively between the elastic member 34 and the side plate 25 and between the elastic member 34 and the slide gear 32. As a result, the locked state of the output shaft 22 can smoothly be released through the lever operation.

(55) Then, when the inner ring 15 further rotates, the stopper surface 15g of each of the cam grooves 15e of the inner ring 15 is brought into abutment against each of the protrusions 32b of the slide gear 32 in the rotation direction. When each of the stopper surfaces 15g presses each of the protrusions 32b in the rotation direction as a result of the abutment between the stopper surfaces 15g and the protrusions 32b, the rotational torque to be input from the inner ring 15 is transmitted to the output shaft 22 via the protrusions 32b of the slide gear 32, thereby rotating the output shaft 22.

(56) In this embodiment, there is employed a structure in which the cam mechanism 33 (the protrusions 32b of the slide gear 32 and the cam grooves 15e of the inner ring 15) configured to move the slide gear 32 in the axial direction to control the meshing between the slide gear 32 and the side plater 25 and the release of the meshing state is interposed between the slide gear 32 and the inner ring 15. Thus, the meshing between the slide gear 32 and the side plater 25 and the release of the meshing state can thus easily be performed.

(57) Moreover, immediately after the internal teeth 32a of the slide gear 32 are disengaged from the external teeth 25b of the side plate 25, there is given the state in which the cylindrical rollers 27 are engaged with the wedge gaps 26 between the outer ring 23 and the output shaft 22 in the brake-side clutch part 12. Therefore, even when the rotational torque is reversely input to the output shaft 22 at this time point, the output shaft 22 is reliably locked.

(58) After that, when the internal teeth 32a of the slide gear 32 are completely disengaged from the external teeth 25b of the side plate 25 as a result of the movement of the slide gear 32 in the axial direction, the cylindrical rollers 27 are disengaged from the wedge gaps 26 between the outer ring 23 and the output shaft 22. Thus, noise such as gear rattle is not generated between the slide gear 32 and the side plate 25 during the lever operation.

(59) As described above, in the brake-side clutch part 12, the structure in which the cylindrical rollers 27 are engaged with the wedge gaps 26 between the outer ring 23 and the output shaft 22 is required in addition to the structure in which the internal teeth 32a of the slide gear 32 and the external teeth 25b of the side plate 25 mesh with each other.

(60) Finally, description is given of an application example of the clutch unit 10 according to this embodiment. The clutch unit 10 having the structure described above in detail is used after being assembled to the seat lifter part 41 for an automobile, which is configured to adjust a height of the seat through the lever operation. FIG. 8 is a view for illustrating the seat 40 installed in a cabin of an automobile.

(61) As illustrated in FIG. 8, the seat 40 comprises a seating seat 48 and a backrest seat 42, and a height of a seat surface of the seating seat 48 is adjusted by the seat lifter part 41. The height adjustment of the seating seat 48 is performed through the operation lever 43 mounted to the side plate 13 of the lever-side clutch part 11 (see FIG. 1) in the clutch unit 10.

(62) The seat lifter part 41 has the following structure. One ends of link members 45 and 46 are pivotably mounted to a slidable member 44. Another ends of the link members 45 and 46 are pivotably mounted to the seating seat 48. A sector gear 47 is provided integrally with another end of the link member 45. The sector gear 47 meshes with the pinion gear 22d of the output shaft 22 of the clutch unit 10.

(63) For example, when the seating surface of the seating seat 48 is to be lowered, the locked state of the brake-side clutch part 12 (see FIG. 1) is released by a lever operation in the lever-side clutch part 11, in other words, by swinging the operation lever 43 downward. The seating surface of the seating seat 48 can smoothly be lowered by applying the appropriate rotational resistance to the output shaft 22 through the elastic member 34 upon the unlocking of the brake-side clutch part 12.

(64) As a result of the unlocking of the brake-side clutch part 12, the pinion gear 22d of the output shaft 22 of the brake-side clutch part 12 is turned clockwise (in a direction indicated by the arrow of FIG. 8) by a rotational torque transmitted from the lever-side clutch part 11 to the brake-side clutch part 12. Then, the sector gear 47 meshing with the pinion gear 22d swings counterclockwise (in a direction indicated by the arrow of FIG. 8). As a result, both of the link member 45 and the link member 46 thus tilt, and the seating surface of the seating seat 48 is consequently lowered.

(65) In such a manner, when the operation lever 43 is released after the height of the seat surface of the seating seat 48 is adjusted, the operation lever 43 swings upward by the elastic forces of both of the centering springs 18 and 19, and returns to an original position (neutral state). When the operation lever 43 is swung upward, the seating surface of the seating seat 48 is raised through an operation opposite to the operation described above. When the operation lever 43 is released after the height adjustment of the seating seat 48, the operation lever 43 swings downward, and returns to the original position (neutral state).

(66) The present invention is not limited to the above-mentioned embodiment. As a matter of course, the present invention may be carried out in various modes without departing from the spirit of the present invention. The scope of the present invention is defined in claims, and encompasses equivalents described in claims and all changes within the scope of claims.