WO2012039253A1 - Clutch unit - Google Patents

Clutch unit Download PDF

Info

Publication number
WO2012039253A1
WO2012039253A1 PCT/JP2011/069884 JP2011069884W WO2012039253A1 WO 2012039253 A1 WO2012039253 A1 WO 2012039253A1 JP 2011069884 W JP2011069884 W JP 2011069884W WO 2012039253 A1 WO2012039253 A1 WO 2012039253A1
Authority
WO
WIPO (PCT)
Prior art keywords
lever
input
brake
clutch
torque
Prior art date
Application number
PCT/JP2011/069884
Other languages
French (fr)
Japanese (ja)
Inventor
川合 正浩
佐藤 光司
康二 磯田
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2012039253A1 publication Critical patent/WO2012039253A1/en

Links

Images

Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60NSEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/02Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
    • B60N2/04Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable
    • B60N2/16Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable height-adjustable
    • B60N2/1635Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable height-adjustable characterised by the drive mechanism
    • B60N2/167Ratchet mechanism
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60NSEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/90Details or parts not otherwise provided for
    • B60N2/919Positioning and locking mechanisms
    • B60N2/933Positioning and locking mechanisms rotatable
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00Freewheels or freewheel clutches
    • F16D41/06Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/086Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate members being of circular cross-section and wedging by rolling
    • F16D41/088Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate members being of circular cross-section and wedging by rolling the intermediate members being of only one size and wedging by a movement not having an axial component, between inner and outer races, one of which is cylindrical
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00Freewheels or freewheel clutches
    • F16D41/06Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/10Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing
    • F16D41/105Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing the intermediate members being of circular cross-section, of only one size and wedging by rolling movement not having an axial component between inner and outer races, one of which is cylindrical

Definitions

  • the present invention includes a lever-side clutch portion that transmits rotational torque from the input side to the output side, a brake-side clutch portion that transmits rotational torque from the input side to the output side, and blocks reverse input torque from the output side, It is related with the clutch unit which has.
  • a clutch portion is disposed between an input side member and an output side member.
  • the clutch portion is configured to control transmission / cutoff of input torque by engaging / disengaging an engagement element such as a cylindrical roller or a ball in a wedge clearance formed between the input side member and the output side member. It has become.
  • the present applicant for example, is incorporated in an automobile seat lifter that adjusts the seat seat up and down by lever operation, and transmits a rotational torque from the input side to the output side, and outputs a rotational torque from the input side.
  • a clutch unit having a brake side clutch portion that transmits to the side and interrupts reverse input torque from the output side has been previously proposed (for example, see Patent Document 1).
  • FIG. 29 is a longitudinal sectional view showing the entire configuration of the conventional clutch unit disclosed in the above-mentioned Patent Document 1
  • FIG. 30 is a sectional view taken along the line DD of FIG. 29, and
  • FIG. 31 is a line EE of FIG. FIG.
  • the lever-side clutch unit 111 includes a lever-side outer ring 114 as an input-side member to which torque is inputted by lever operation, and torque from the lever-side outer ring 114 as a brake-side clutch unit 112. And a cylindrical roller 116 as a plurality of engagement elements for controlling transmission / interruption of input torque from the lever-side outer ring 114 by engagement / disengagement between the lever-side outer ring 114 and the inner ring 115.
  • a retainer 117 that holds each cylindrical roller 116 at a predetermined interval in the circumferential direction, a brake-side outer ring 123 as a stationary side member that is constrained to rotate, and a cover 124 that will be described later as a retainer 117 and a stationary side member.
  • the elastic force is accumulated by the input torque from the lever side outer ring 114, and the accumulated elastic force is obtained by releasing the input torque.
  • the inner centering spring 118 as the first elastic member for returning the cage 117 to the neutral state
  • the lever-side outer ring 114 and the cover 124 Provided between the inner centering spring 118 as the first elastic member for returning the cage 117 to the neutral state, the lever-side outer ring 114 and the cover 124, and stores the elastic force by the input torque from the lever-side outer ring 114.
  • the main part is composed of the outer centering spring 119 as a second elastic member that returns the lever-side outer ring 114 to the neutral state by the accumulated elastic force by
  • 113 is a lever side plate that is fixed to the lever side outer ring 114 by caulking and constitutes an input side member together with the lever side outer ring 114
  • 131 is a washer attached to the output shaft 122 via a wave washer 130.
  • the brake side clutch portion 112 is a brake side outer ring 123 as a stationary side member whose rotation is restricted, and a connecting member to which torque from the lever side clutch portion 111 is input.
  • the main part is constituted by a plurality of pairs of cylindrical rollers 127 that control transmission of input torque from the output shaft and interruption of reverse input torque from the output shaft 122.
  • the enlarged diameter portion 115c that extends radially outward from the axial end of the inner ring 115 and bends in the axial direction functions as a cage that holds the cylindrical rollers 127 at predetermined intervals in the circumferential direction.
  • reference numerals 124 and 125 denote a cover and a brake side plate that form a stationary member together with the brake side outer ring 123.
  • the brake side outer ring 123 and the cover 124 are integrally crimped and fixed by the brake side plate 125.
  • Reference numeral 128 denotes a leaf spring having an N-shaped cross section, for example, disposed between each pair of cylindrical rollers 127, and 129 is a friction ring as a braking member attached to the brake side plate 125.
  • the wave-side washer 130 is inserted into the outer periphery of the output shaft 122 and the washer 131 is press-fitted into the outer periphery of the output shaft 122, whereby the lever-side clutch unit 111.
  • the components such as the lever-side outer ring 114 and the brake-side clutch portion 112, such as the inner ring 115, are prevented from coming off. That is, the wave washer 130 is sandwiched between the lever side outer ring 114 and the inner ring 115 and the washer 131. Thereby, the lever side outer ring 114 and the inner ring 115 are prevented from coming off by applying a pressing load to the lever side outer ring 114 and the inner ring 115.
  • the output shaft 122 needs to have an axial dimension for fixing the washer 131, and the axial direction of the output shaft 122 There is a possibility that it becomes difficult to reduce the size of the entire clutch unit by increasing the size.
  • an object of the present invention is to provide a compact clutch unit capable of reducing the number of parts and simplifying assembly in the retaining structure. is there.
  • the clutch unit according to the present invention is provided on the input side, and controls the transmission / cut-off of rotational torque to the output side by lever operation, and the input side torque from the lever side clutch unit provided on the output side. Is transmitted to the output side and the brake side clutch part that cuts off the reverse input torque from the output side.
  • An annular groove is provided in the shaft part of the output side member of the brake side clutch part, and is assembled to the output side member. Further, an annular locking member for preventing the component part of the lever side clutch part and the component part of the brake side clutch part from fitting is fitted in the concave groove of the shaft part.
  • the structure in which the annular locking member is fitted in the concave groove of the shaft part is used.
  • the locking member can be fitted and fixed in the groove so that it can be configured with a single locking member, reducing the number of parts and simplifying assembly. Can be achieved.
  • the output side member does not require an axial dimension for fixing a washer which is one of the conventional retaining parts by press fitting, the axial dimension of the output side member can be made shorter than before. This makes it easy to downsize the entire clutch unit.
  • a wave spring or a disc spring is desirable as the locking member of the present invention. If such a wave spring or a disc spring is used, a reliable retaining can be realized by the elastic force of the wave spring or the disc spring itself fitted in the concave groove of the shaft portion of the output side member.
  • the disc spring preferably has a structure in which cutout portions are formed at a plurality of locations on the inner periphery thereof. If the disc spring having such a structure is used, the portions that fit into the concave grooves of the shaft portion of the output side member are dispersed in a plurality of locations in the circumferential direction, so the disc spring is extrapolated to the shaft portion. Assembly work is easy.
  • the lever side clutch portion in this clutch unit includes an input side member to which torque is input by lever operation, a connecting member that transmits torque from the input side member to the brake side clutch portion, and between the input side member and the connecting member.
  • a plurality of engagement elements that control transmission / cutoff of input torque from the input side member by engagement / disengagement, a cage that holds the engagement elements at predetermined intervals in the circumferential direction, and a stationary side member that is restricted in rotation
  • an elastic force that is provided between the cage and the stationary member, accumulates an elastic force with an input torque from the input side member, and releases the input torque to return the cage to a neutral state with the accumulated elastic force.
  • One elastic member provided between the input side member and the stationary side member, accumulates the elastic force with the input torque from the input side member, and releases the input torque to cause the input side member to move with the accumulated elastic force.
  • Neutral Configurations are possible in which a second elastic member to return to.
  • the engaging member of the lever side clutch portion is a cylindrical roller.
  • the brake side clutch portion in the clutch unit includes a connecting member to which torque from the lever side clutch portion is input, an output side member to which torque is output, a stationary side member in which rotation is constrained, and a stationary side member thereof.
  • a plurality of pairs of engagement elements disposed in the wedge clearance between the output side members and controlling transmission of input torque from the connecting member and blocking of reverse input torque from the output side member by engagement / disengagement between both members;
  • a configuration with The engaging member of the brake side clutch is preferably a cylindrical roller.
  • 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.
  • the input side member is coupled to the lever
  • the output side member is connected to the link mechanism of the automobile seat lifter unit.
  • the annular concave groove is provided in the shaft portion of the output side member of the brake side clutch portion, and the components of the lever side clutch portion and the components of the brake side clutch portion that are assembled to the output side member are retained.
  • the annular locking member By fitting the annular locking member to be fitted into the concave groove of the shaft portion, it is possible to configure a retaining component with one locking member, and it is possible to reduce the number of components and simplify the assembly.
  • the output side member does not require an axial dimension for fixing a washer, which is one of the conventional retaining parts, by press-fitting, the entire clutch unit can be reduced in size. As a result, it is possible to provide a clutch unit that is easy to assemble, low in cost, and compact.
  • FIG. 2 is a cross-sectional view taken along line AA in FIG.
  • FIG. 3 is a sectional view taken along line BB in FIG. 1.
  • FIG. 6b is a left side view of FIG. 6a.
  • FIG. 7b is a left side view of FIG. 7a.
  • FIG. 7b is a right side view of FIG. 7a.
  • FIG. 8b is a left side view of FIG. 8a.
  • FIG. 10b is a left side view of FIG. 10a.
  • Fig. 10b is a cross-sectional view of Fig. 10a.
  • FIG. 14b is a left side view of FIG. 14a.
  • FIG. 14b is a right side view of FIG. 14a. It is sectional drawing which shows a brake side outer ring
  • FIG. 14b is a left side view of FIG. 14a.
  • FIG. 14b is a right side view of FIG. 14a.
  • FIG. 15b is a left side view of FIG. 15a. It is sectional drawing which shows a cover.
  • FIG. 16b is a left side view of FIG. 16a.
  • FIG. 17b is a right side view of FIG. 17a.
  • FIG. 17b is a front view which shows a friction ring.
  • FIG. 18b is a left side view of FIG. 18a.
  • FIG. 18b is a right side view of FIG. 18a.
  • FIG. 20b is a right side view of FIG. 20a.
  • FIG. 2 is a cross-sectional view which shows the clutch unit which comprised the retaining structure by the disc spring of FIG. 20a. It is a perspective view which shows the state before attaching a brake side outer ring
  • FIG. 2 is a cross-sectional view taken along the line CC of FIG.
  • FIG. 30 is a transverse sectional view taken along line DD of FIG. 29.
  • FIG. 30 is a transverse sectional view taken along line EE of FIG. 29.
  • FIG. 1 is a longitudinal sectional view showing an overall configuration of a clutch unit X according to an embodiment of the present invention
  • FIG. 2 is a right side view of the clutch unit X shown in FIG. 1
  • FIG. 3 is a left side view of the clutch unit X shown in FIG. 4
  • FIG. 5 is a cross-sectional view taken along line BB in FIG. 6 to 20
  • FIG. 21 is a longitudinal sectional view showing the overall configuration of the clutch unit X according to another embodiment of the present invention
  • FIGS. 22 to 26 are views showing an assembled state of main components of the clutch unit X.
  • the clutch unit X is incorporated in an automobile seat lifter (see FIGS. 27, 28a, and 28b) that adjusts the height of the seat by operating a lever, for example.
  • the clutch unit X is a unit of a lever side clutch portion 11 provided on the input side and a brake side clutch portion 12 having a reverse input cutoff function provided on the output side. It has a configuration.
  • the lever-side clutch unit 11 includes, for example, a lever-side plate 13 and a lever-side outer ring 14 as input-side members to which an operation lever (not shown) is coupled, A wedge clearance formed between an inner ring 15 as a connecting member that transmits torque from the lever-side outer ring 14 to the brake-side clutch portion 12, and an outer peripheral surface 15a of the inner ring 15 and an inner peripheral surface 14a of the lever-side outer ring 14.
  • a plurality of cylindrical rollers 16 serving as engagement elements disposed at 20 a cage 17 that holds the cylindrical rollers 16 at equal intervals in the circumferential direction, and a first for returning the cage 17 to a neutral state
  • An inner centering spring 18 that is an elastic member and an outer centering spring 19 that is a second elastic member for returning the lever-side outer ring 14 to a neutral state are provided.
  • the brake side clutch portion 12 having a reverse input blocking function as a lock type is used as a connecting member to which torque from the lever side clutch portion 11 is input.
  • a cylindrical spring 27 interposed between each pair of cylindrical rollers 27, and a plate spring 28 having an N-shaped cross section for biasing the separating force between the cylindrical rollers 27 constitutes a main part.
  • the output shaft 22 is provided with a protrusion 22f, and a hole 15d into which the protrusion 22f is inserted with a clearance is provided in the inner ring 15 (see FIG. 1).
  • FIGS. 6 a and 6 b show the lever side plate 13 of the lever side clutch portion 11.
  • the lever side plate 13 has a hole 13a through which the output shaft 22 and the inner ring 15 are inserted at a central portion thereof, and a plurality of (for example, five) claw portions 13b project from the outer peripheral edge. These claw portions 13b are bent in the axial direction to have a bifurcated tip, and are inserted into a notch recess 14e (see FIG. 7c) of the lever-side outer ring 14 described later to expand the bifurcated tip outward.
  • the lever side plate 13 is fixed by caulking to the lever side outer ring 14.
  • symbol 13c in a figure is the several (for example, four) hole for attaching the operation lever for operating the height adjustment of a seat to the lever side side board 13.
  • FIG. 1 the code
  • FIG. 7a to 7c show the lever side outer ring 14.
  • the lever-side outer ring 14 is formed by pressing a single plate-shaped material into a cup shape, and a hole 14b through which the output shaft 22 and the inner ring 15 are inserted is formed in the center part 14c.
  • a plurality of cam surfaces 14a are formed at equal intervals in the circumferential direction on the inner periphery of the cylindrical portion 14d extending in the axial direction (see FIG. 4).
  • a plurality (for example, three) of claw portions 14f and 14g project from the outer peripheral edge portion of the lever side outer ring 14 and are bent in the axial direction.
  • one claw portion 14f is inserted and disposed between two locking portions 19a (see FIG. 12) of an outer centering spring 19 to be described later, and the remaining two claw portions 14g.
  • a plurality of (five in the figure) cutout recesses 14e into which the claw portions 13b (see FIGS. 6a and 6b) of the lever side side plate 13 are inserted are formed.
  • the lever side plate 13 and the lever side outer ring 14 are connected by crimping the claw portion 13b of the lever side plate 13 inserted into the notch recess 14e.
  • the lever side outer ring 14 and the lever side plate 13 fixed by crimping to the lever side outer ring 14 constitute an input side member of the lever side clutch portion 11.
  • FIG. 8a and 8b show the inner ring 15.
  • FIG. The inner ring 15 includes an outer peripheral surface 15a that forms a wedge clearance 20 (see FIG. 4) between the outer diameter of the cylindrical portion 15b through which the output shaft 22 is inserted and the cam surface 14a of the lever-side outer ring 14. .
  • an enlarged diameter portion 15c extending radially outward from the end of the cylindrical portion 15b and bent in the axial direction is integrally formed, and the enlarged diameter portion 15c functions as a cage for the brake side clutch portion 12. Therefore, pockets 15e for accommodating the cylindrical rollers 27 and the leaf springs 28 are formed at equal intervals in the circumferential direction.
  • symbol 15d in a figure is a hole into which the protrusion 22f (refer FIG. 1) of the output shaft 22 is inserted with a clearance.
  • the cage 17 is a cylindrical member in which a plurality of pockets 17a for accommodating the cylindrical rollers 16 are formed at equal intervals in the circumferential direction.
  • Two notch recesses 17b are formed at one end of the retainer 17, and a locking part 18a of an inner centering spring 18 (described later) is locked to two adjacent end surfaces 17c of each notch recess 17b. (See FIG. 25).
  • FIG. 11 shows the inner centering spring 18.
  • the inner centering spring 18 is formed of a C-shaped spring member having a circular cross section having a pair of engaging portions 18a bent radially inward, and is located on the inner diameter side of the outer centering spring 19 (see FIG. 25).
  • the inner centering spring 18 is disposed between the cage 17 and a cover 24 that is a stationary side member of the brake side clutch portion 12, and both locking portions 18 a are two end surfaces 17 c (FIG. 9, FIG. 9). 10b) and a claw portion 24b (see FIGS. 16a and 16b) provided on the cover 24 (see FIGS. 25, 26a and 26b).
  • the inner centering spring 18 when the input torque from the lever side outer ring 14 is applied, one locking portion 18 a is on one end surface 17 c of the cage 17, and the other locking portion 18 a is on the claw portion 24 b of the cover 24.
  • the inner centering spring 18 As the lever-side outer ring 14 rotates, the inner centering spring 18 is pushed and expanded to accumulate elastic force.
  • the elastic restoring force causes the cage 17 to move. Is returned to the neutral state.
  • FIG. 12 shows the outer centering spring 19.
  • the outer centering spring 19 is a strip-shaped spring member having a C-shape and having a pair of locking portions 19a whose both ends are bent radially outward, and is located on the outer diameter side of the inner centering spring 18 ( FIG. 25).
  • the outer centering spring 19 is disposed between the lever-side outer ring 14 of the lever-side clutch portion 11 and the cover 24 of the brake-side clutch portion 12, and both locking portions 19 a are claw portions 14 f provided on the lever-side outer ring 14. (See FIGS. 7a to 7c) and is also locked to a claw portion 24d (see FIGS. 16a and 16b) provided on the cover 24 (see FIGS. 26a and 26b).
  • the locking portion 19a is arranged with a circumferential phase (180 °) shifted from the locking portion 18a of the inner centering spring 18 (see FIG. 25).
  • FIGS. 13 a, 13 b, and 14 a to 14 c show the output shaft 22.
  • the output shaft 22 has a large-diameter portion 22d that extends radially outward from the shaft portion 22c and is integrally formed at a substantially central portion in the axial direction.
  • a pinion gear 41g for connecting to the seat lifter portion 41 is coaxially formed at the tip of the shaft portion 22c.
  • a plurality of (for example, six) flat cam surfaces 22a are formed on the outer peripheral surface of the large-diameter portion 22d at equal intervals in the circumferential direction, and a wedge clearance 26 provided between the inner peripheral surface 23b of the brake-side outer ring 23 and the like.
  • Two cylindrical rollers 27 and a leaf spring 28 are arranged on each (see FIG. 5).
  • An annular recess 22b in which the friction ring 29 is accommodated is formed on one end face of the large diameter portion 22d.
  • Reference numeral 22f in the figure is a protrusion formed on the other end face of the large-diameter portion 22d and is inserted into the hole 15d of the inner ring 15 with a clearance (see FIGS. 1, 8a, and 8b).
  • FIG. 15a, 15b, 16a and 16b show the brake side outer ring 23 and its cover 24.
  • FIG. 17a and 17b show the brake side plate 25.
  • FIG. The brake side outer ring 23 and the cover 24 are caulked and fixed integrally by the brake side plate 25.
  • the brake-side outer ring 23 is a thick plate-like member obtained by punching one material with a press, and the cover 24 is formed by pressing another material with a press.
  • reference numerals 24c and 25b denote holes through which the output shaft 22 is inserted
  • reference numeral 25c denotes a hole into which a projection 29a of a friction ring 29 described later is fitted.
  • a plurality (three) of cutout recesses 23a are formed on the outer periphery of the brake side outer ring 23, and a plurality (three) of cutout recesses 24a are also formed on the outer periphery of the cover 24 so as to correspond to the cutout recesses 23a.
  • the claw portion 25a of the brake side plate 25 is inserted into the notch recess 23a of the brake side outer ring 23, and the brake side plate is inserted into the notch recess 24a of the cover 24 as shown in FIG. 25 claw portions 25a are inserted.
  • Crimp claw portion 25a of the brake-side side plate 25 By tightening the claw portion 25a of the brake side plate 25 inserted into the notches 23a and 24a, the brake side outer ring 23 and the cover 24 are connected and integrated with the brake side plate 25 to constitute a stationary member. Crimp claw portion 25a of the brake-side side plate 25, by utilizing crimping jig (not shown), it is carried out by expanding the bifurcated distal end portion 25a 1 of the claw portion 25a to the outside (See FIG. 24).
  • a wedge clearance 26 is formed between the inner peripheral surface 23b of the brake side outer ring 23 and the cam surface 22a of the output shaft 22 (see FIG. 5).
  • the cover 24 is formed with a claw portion 24b protruding in the axial direction, and the claw portion 24b is disposed between the two locking portions 18a of the inner centering spring 18 of the lever side clutch portion 11 (FIGS. 11 and 26a). , See FIG. 26b).
  • the claw part 24b of the cover 24 is formed by raising the outer diameter side of the claw part forming position.
  • a claw portion 24 d that protrudes in the axial direction is formed on the outer periphery of the cover 24.
  • the claw portion 24d is disposed between the two locking portions 19a of the outer centering spring 19 of the lever side clutch portion 11 (see FIGS. 12, 26a, and 26b).
  • Two sets of locking portions 24e and 24f are formed on the outer periphery of the cover 24 by step processing (see FIGS. 26a and 26b).
  • the engaging portions 24e and 24f can be contacted in the rotation direction when the claw portion 14g of the lever-side outer ring 14 rotates in a state of being in contact with the end surface of the brake-side outer ring 23, whereby the operating angle of the operating lever It functions as a rotation stopper that regulates That is, when the lever side outer ring 14 is rotated by the operation of the operation lever, the claw portion 14g moves along the outer periphery of the cover 24 between the locking portions 24e and 24f of the cover 24.
  • the outer periphery of the brake side plate 25 is provided with one flange portion 25e and two flange portions 25f as clutch attachment portions to the seat lifter portion (see FIGS. 2 to 4). At the tips of these three flange portions 25e and 25f, holes 25g and 25h for attachment to the seat lifter portion are formed so that the cylindrical portions 25i and 25j are axially bent so as to surround and bend the attachment holes 25g and 25h. Projected.
  • a friction ring 29 made of resin shows a friction ring 29 made of resin.
  • a plurality of circular protrusions 29a are provided on the end face of the friction ring 29 at equal intervals along the circumferential direction thereof, and the protrusions 29a are press-fitted into the holes 25c of the brake side plate 25 to be fitted to the brake side. It adheres to the side plate 25 (refer FIG. 1, FIG. 3).
  • the fitting state with the hole 25c is obtained by elastic deformation of the projection 29a by the resin material.
  • the friction ring 29 is press-fitted with an allowance to the inner peripheral surface 22e of the annular recess 22b formed in the large diameter portion 22d of the output shaft 22 (see FIGS. 13a, 14a, and 14b).
  • a rotational resistance is applied to the output shaft 22 by a frictional force generated between the outer peripheral surface 29 c of the friction ring 29 and the inner peripheral surface 22 e of the annular recess 22 b of the output shaft 22.
  • a plurality of concave grooves 29b are formed on the outer peripheral surface 29c of the friction ring 29 at equal intervals in the circumferential direction (see FIG. 5).
  • the setting range of the rotational resistance provided by the frictional force generated between the outer peripheral surface 29c of the friction ring 29 and the inner peripheral surface 22e of the annular recess 22b of the output shaft 22 can be reduced, and the magnitude of the rotational resistance can be reduced. Can be set appropriately. Further, since the slit 29b becomes a grease reservoir, it is possible to suppress the outer peripheral surface 29c of the friction ring 29 from being worn by sliding with the inner peripheral surface 22e of the annular recess 22b of the output shaft 22.
  • 19a to 19c show a wave spring 30 as a locking member.
  • the wave spring 30 is formed by, for example, coiling.
  • an annular groove 22g is provided in the shaft portion 22c of the output shaft 22 of the brake clutch portion 12 (see FIGS. 13a, 13b, and 14a), and the lever side assembled to the output shaft 22 is provided.
  • the structure is such that a wave spring 30 for retaining the component parts of the clutch portion 11 such as the lever-side outer ring 14 and the brake-side clutch portion 12 such as the inner ring 15 is fitted in the concave groove 22g of the shaft portion 22c.
  • the wave spring 30 is fitted into the concave groove 22g of the shaft portion 22c. 2), the wave spring 30 can be fixed by being fitted into the concave groove 22g, so that the single wave spring 30 can be used as a retaining part. Can be reduced and the assembly can be simplified. Further, the output shaft 22, since the washer 131 which is one of the conventional retaining part axial dimension L 1 to press-fitted (see FIG. 29) becomes unnecessary, the axial direction of the output shaft 22 it is possible to shorten the dimension L 2 than the conventional (L 2 ⁇ L 1), the overall size of the clutch unit is facilitated.
  • a disc spring 31 as shown in FIGS. 20a and 20b may be used as a locking member for preventing the lever-side outer ring 14 and the inner ring 15 from coming off.
  • a concave groove 22g is provided in the shaft portion 22c of the output shaft 22, and a disc spring 31 is fitted in the concave groove 22g.
  • the disc spring 31 prevents the lever-side outer ring 14 and the inner ring 15 from coming off.
  • the leaf spring 28 urges the pair of cylindrical rollers 27 so that the cylindrical rollers 27 are braked with the output shaft 22.
  • the output shaft 22 is locked to the brake side outer ring 23 by engaging with the wedge clearance 26 between the side outer rings 23. Accordingly, the reverse input torque 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.
  • the input torque from the lever-side outer ring 14 is input to the inner ring 15 via the lever-side clutch portion 11, and the inner ring 15 comes into contact with the cylindrical roller 27 and presses against the elastic force of the leaf spring 28.
  • the cylindrical roller 27 is removed from the wedge clearance 26, the locked state of the output shaft 22 is released, and the output shaft 22 becomes rotatable.
  • the inner ring 15 further rotates, the clearance between the hole 15d of the inner ring 15 and the protrusion 22f of the output shaft 22 is clogged, and the inner ring 15 comes into contact with the protrusion 22f of the output shaft 22 in the rotation direction, so that the input torque from the inner ring 15 is increased.
  • the output shaft 22 is transmitted to the output shaft 22 through the protrusion 22f, and the output shaft 22 rotates.
  • FIG. 27 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 41a of the seat lifter 41.
  • FIG. 28 a conceptually shows one structural example of the sheet lifter unit 41.
  • Seat slide adjuster 41b of the slide moving member 41b 1 to the link member 41c, one end of 41d are respectively rotatably hinged.
  • 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.
  • Sector gear 41f is pivotally rotatably sitting seat 40a, a swingable fulcrum 41f 1 around.
  • the other end of the link member 41d is pivotally attached to the seating seat 40a.
  • the clutch unit X of the above-described embodiment is fixed to an appropriate part of the seating seat 40a.
  • the clutch unit X is fixed to the seating seat 40a by plastically deforming the three flange portions 25e and 25f of the brake side plate 25 so that the distal end portions of the cylindrical portions 25i and 25j are expanded outward. It is fixed by caulking to a seat frame (not shown) of the seat 40a.
  • the operation lever 41a is coupled to the lever side plate 13 of the lever side clutch portion 11, and the output shaft 22 of the brake side clutch portion 12 is provided with a pinion gear 41g that meshes with the sector gear 41f that is a rotating member.
  • the pinion gear 41g is integrally formed at the tip of the shaft portion 22c of the output shaft 22 as shown in FIGS. 1, 13a, 13b, 14a, and 14b.

Abstract

The present invention comprises: a lever-side clutch section (11) which is provided on the input side and which controls, by means of lever operation, the transmission of rotational torque to the output side and the blocking of the transmission thereof; and a brake-side clutch section (12) provided on the output side, the brake-side clutch section (12) transmitting input torque, which is transmitted from the lever-side clutch section (11), to the output side and blocking a reverse torque input from the output side. An annular groove (22g) is provided in the shaft section (22c) of the output shaft (22) of the brake-side clutch section (12). An annular wave spring (30) is fitted in the groove (22g) in the shaft section (22c), and the wave spring (30) retains the lever-side outer ring (14) of the lever-side clutch section (11) and the inner ring (15) of the brake-side clutch section (12), the lever-side clutch section (11) and the brake-side clutch section (12) being mounted on the output shaft (22).

Description

クラッチユニットClutch unit
 本発明は、入力側からの回転トルクを出力側へ伝達するレバー側クラッチ部と、入力側からの回転トルクを出力側へ伝達すると共に出力側からの逆入力トルクを遮断するブレーキ側クラッチ部とを有するクラッチユニットに関する。 The present invention includes a lever-side clutch portion that transmits rotational torque from the input side to the output side, a brake-side clutch portion that transmits rotational torque from the input side to the output side, and blocks reverse input torque from the output side, It is related with the clutch unit which has.
 一般に、円筒ころやボール等の係合子を用いるクラッチユニットにおいては、入力側部材と出力側部材との間にクラッチ部が配設される。このクラッチ部は、前述の入力側部材と出力側部材間に形成される楔すきまに円筒ころやボール等の係合子を係合・離脱させることによって、入力トルクの伝達・遮断を制御する構成になっている。 Generally, in a clutch unit using an engagement element such as a cylindrical roller or a ball, a clutch portion is disposed between an input side member and an output side member. The clutch portion is configured to control transmission / cutoff of input torque by engaging / disengaging an engagement element such as a cylindrical roller or a ball in a wedge clearance formed between the input side member and the output side member. It has become.
 本出願人は、例えば、レバー操作により座席シートを上下調整する自動車用シートリフタ部に組み込まれ、入力側からの回転トルクを出力側へ伝達するレバー側クラッチ部と、入力側からの回転トルクを出力側へ伝達すると共に出力側からの逆入力トルクを遮断するブレーキ側クラッチ部とを具備したクラッチユニットを先に提案している(例えば、特許文献1参照)。 The present applicant, for example, is incorporated in an automobile seat lifter that adjusts the seat seat up and down by lever operation, and transmits a rotational torque from the input side to the output side, and outputs a rotational torque from the input side. A clutch unit having a brake side clutch portion that transmits to the side and interrupts reverse input torque from the output side has been previously proposed (for example, see Patent Document 1).
 図29は前述の特許文献1に開示された従来のクラッチユニットの全体構成を示す縦断面図、図30は図29のD-D線に沿う断面図、図31は図29のE-E線に沿う断面図である。 29 is a longitudinal sectional view showing the entire configuration of the conventional clutch unit disclosed in the above-mentioned Patent Document 1, FIG. 30 is a sectional view taken along the line DD of FIG. 29, and FIG. 31 is a line EE of FIG. FIG.
 図29、図30に示すように、レバー側クラッチ部111は、レバー操作によりトルクが入力される入力側部材としてのレバー側外輪114と、そのレバー側外輪114からのトルクをブレーキ側クラッチ部112に伝達する連結部材としての内輪115と、レバー側外輪114と内輪115間での係合・離脱によりレバー側外輪114からの入力トルクの伝達・遮断を制御する複数の係合子としての円筒ころ116と、各円筒ころ116を円周方向に所定間隔で保持する保持器117と、回転が拘束された静止側部材としてのブレーキ側外輪123と、保持器117と静止側部材としての後述のカバー124との間に設けられ、レバー側外輪114からの入力トルクで弾性力を蓄積し、その入力トルクの開放により、蓄積された弾性力で保持器117を中立状態に復帰させる第一の弾性部材としての内側センタリングばね118と、レバー側外輪114とカバー124との間に設けられ、レバー側外輪114からの入力トルクで弾性力を蓄積し、その入力トルクの開放により、蓄積された弾性力でレバー側外輪114を中立状態に復帰させる第二の弾性部材としての外側センタリングばね119とで主要部が構成されている。 As shown in FIGS. 29 and 30, the lever-side clutch unit 111 includes a lever-side outer ring 114 as an input-side member to which torque is inputted by lever operation, and torque from the lever-side outer ring 114 as a brake-side clutch unit 112. And a cylindrical roller 116 as a plurality of engagement elements for controlling transmission / interruption of input torque from the lever-side outer ring 114 by engagement / disengagement between the lever-side outer ring 114 and the inner ring 115. A retainer 117 that holds each cylindrical roller 116 at a predetermined interval in the circumferential direction, a brake-side outer ring 123 as a stationary side member that is constrained to rotate, and a cover 124 that will be described later as a retainer 117 and a stationary side member. The elastic force is accumulated by the input torque from the lever side outer ring 114, and the accumulated elastic force is obtained by releasing the input torque. Provided between the inner centering spring 118 as the first elastic member for returning the cage 117 to the neutral state, the lever-side outer ring 114 and the cover 124, and stores the elastic force by the input torque from the lever-side outer ring 114. The main part is composed of the outer centering spring 119 as a second elastic member that returns the lever-side outer ring 114 to the neutral state by the accumulated elastic force by releasing the input torque.
 なお、図中、113はレバー側外輪114に加締め固定されてレバー側外輪114と共に入力側部材を構成するレバー側側板、131はウェーブワッシャ130を介して出力軸122に取り付けられたワッシャである。 In the figure, 113 is a lever side plate that is fixed to the lever side outer ring 114 by caulking and constitutes an input side member together with the lever side outer ring 114, and 131 is a washer attached to the output shaft 122 via a wave washer 130. .
 一方、図29、図31に示すように、ブレーキ側クラッチ部112は、回転が拘束された静止側部材としてのブレーキ側外輪123と、レバー側クラッチ部111からのトルクが入力される連結部材としての内輪115と、トルクが出力される出力軸122と、ブレーキ側外輪123と出力軸122間の楔すきまに配設され、ブレーキ側外輪123と出力軸122間での係合・離脱により内輪115からの入力トルクの伝達と出力軸122からの逆入力トルクの遮断を制御する複数対の係合子としての円筒ころ127とで主要部が構成されている。 On the other hand, as shown in FIGS. 29 and 31, the brake side clutch portion 112 is a brake side outer ring 123 as a stationary side member whose rotation is restricted, and a connecting member to which torque from the lever side clutch portion 111 is input. The inner ring 115, the output shaft 122 for outputting torque, the wedge clearance between the brake side outer ring 123 and the output shaft 122, and the inner ring 115 by engagement / disengagement between the brake side outer ring 123 and the output shaft 122. The main part is constituted by a plurality of pairs of cylindrical rollers 127 that control transmission of input torque from the output shaft and interruption of reverse input torque from the output shaft 122.
 なお、内輪115の軸方向端部から径方向外側に延在して軸方向に屈曲した拡径部115cは、円筒ころ127を円周方向に所定間隔で保持する保持器として機能する。図中、124,125はブレーキ側外輪123と共に静止側部材を構成するカバーおよびブレーキ側側板で、ブレーキ側外輪123とカバー124はブレーキ側側板125により一体的に加締め固定される。128は各対の円筒ころ127間に配置された例えば断面N字形の板ばね、129はブレーキ側側板125に取り付けられた制動部材としての摩擦リングである。 The enlarged diameter portion 115c that extends radially outward from the axial end of the inner ring 115 and bends in the axial direction functions as a cage that holds the cylindrical rollers 127 at predetermined intervals in the circumferential direction. In the figure, reference numerals 124 and 125 denote a cover and a brake side plate that form a stationary member together with the brake side outer ring 123. The brake side outer ring 123 and the cover 124 are integrally crimped and fixed by the brake side plate 125. Reference numeral 128 denotes a leaf spring having an N-shaped cross section, for example, disposed between each pair of cylindrical rollers 127, and 129 is a friction ring as a braking member attached to the brake side plate 125.
特開2009-210114号公報JP 2009-210114 A
 ところで、特許文献1に開示された従来のクラッチユニットは、出力軸122の外周にウェーブワッシャ130を挿入した上で、その出力軸122の外周にワッシャ131を圧入することにより、レバー側クラッチ部111の構成部品、例えばレバー側外輪114およびブレーキ側クラッチ部112の構成部品、例えば内輪115を抜け止めした構造を具備する。つまり、レバー側外輪114および内輪115とワッシャ131との間にウェーブワッシャ130を挟み込んだ構造としている。これにより、レバー側外輪114および内輪115に押圧荷重を付与することで、レバー側外輪114および内輪115を抜け止めするようにしている。 By the way, in the conventional clutch unit disclosed in Patent Document 1, the wave-side washer 130 is inserted into the outer periphery of the output shaft 122 and the washer 131 is press-fitted into the outer periphery of the output shaft 122, whereby the lever-side clutch unit 111. The components such as the lever-side outer ring 114 and the brake-side clutch portion 112, such as the inner ring 115, are prevented from coming off. That is, the wave washer 130 is sandwiched between the lever side outer ring 114 and the inner ring 115 and the washer 131. Thereby, the lever side outer ring 114 and the inner ring 115 are prevented from coming off by applying a pressing load to the lever side outer ring 114 and the inner ring 115.
 しかしながら、前述のような抜け止め構造の場合、ウェーブワッシャ130およびワッシャ131からなる二つの抜け止め部品を必要とし、これらウェーブワッシャ130およびワッシャ131とを出力軸122に順次組み付けなければならない。また、ワッシャ131を出力軸122の外周に圧入した構造を採用していることから、出力軸122は、ワッシャ131を固定するための軸方向寸法が必要となって、その出力軸122の軸方向寸法が大きくなることでクラッチユニット全体の小型化が難しくなる可能性があった。 However, in the case of the retaining structure as described above, two retaining parts including the wave washer 130 and the washer 131 are required, and the wave washer 130 and the washer 131 must be sequentially assembled to the output shaft 122. Further, since the structure in which the washer 131 is press-fitted into the outer periphery of the output shaft 122 is adopted, the output shaft 122 needs to have an axial dimension for fixing the washer 131, and the axial direction of the output shaft 122 There is a possibility that it becomes difficult to reduce the size of the entire clutch unit by increasing the size.
 そこで、本発明は前述の改善点に鑑みて提案されたもので、その目的とするところは、抜け止め構造における部品点数の削減および組み立ての簡略化を図り得るコンパクトなクラッチユニットを提供することにある。 Accordingly, the present invention has been proposed in view of the above-described improvements, and an object of the present invention is to provide a compact clutch unit capable of reducing the number of parts and simplifying assembly in the retaining structure. is there.
 本発明に係るクラッチユニットは、入力側に設けられ、レバー操作により出力側への回転トルクの伝達・遮断を制御するレバー側クラッチ部と、出力側に設けられ、レバー側クラッチ部からの入力トルクを出力側へ伝達すると共に出力側からの逆入力トルクを遮断するブレーキ側クラッチ部とからなり、ブレーキ側クラッチ部の出力側部材の軸部に環状の凹溝を設け、出力側部材に組み付けられたレバー側クラッチ部の構成部品およびブレーキ側クラッチ部の構成部品を抜け止めする環状の係止部材を軸部の凹溝に嵌め込んだことを特徴とする。 The clutch unit according to the present invention is provided on the input side, and controls the transmission / cut-off of rotational torque to the output side by lever operation, and the input side torque from the lever side clutch unit provided on the output side. Is transmitted to the output side and the brake side clutch part that cuts off the reverse input torque from the output side. An annular groove is provided in the shaft part of the output side member of the brake side clutch part, and is assembled to the output side member. Further, an annular locking member for preventing the component part of the lever side clutch part and the component part of the brake side clutch part from fitting is fitted in the concave groove of the shaft part.
 本発明では、レバー側クラッチ部の構成部品およびブレーキ側クラッチ部の構成部品の抜け止め構造として、環状の係止部材を軸部の凹溝に嵌め込んだ構造としたことにより、従来では二つの抜け止め部品を必要としていたのに対して、係止部材を凹溝に嵌め込んで固定することができることから、一つの係止部材で抜け止め部品を構成でき、部品点数の削減および組み立ての簡略化が図れる。また、出力側部材は、従来の抜け止め部品の一つであるワッシャを圧入により固定するための軸方向寸法が不要となるので、その出力側部材の軸方向寸法を従来よりも短くすることができ、クラッチユニット全体の小型化が容易となる。 In the present invention, as a structure for preventing the component of the lever side clutch part and the component of the brake side clutch part from coming off, the structure in which the annular locking member is fitted in the concave groove of the shaft part is used. Whereas retaining parts are required, the locking member can be fitted and fixed in the groove so that it can be configured with a single locking member, reducing the number of parts and simplifying assembly. Can be achieved. Further, since the output side member does not require an axial dimension for fixing a washer which is one of the conventional retaining parts by press fitting, the axial dimension of the output side member can be made shorter than before. This makes it easy to downsize the entire clutch unit.
 なお、本発明の係止部材としては、ウェーブスプリングや皿ばねが望ましい。このようなウェーブスプリングや皿ばねを使用すれば、出力側部材の軸部の凹溝に嵌まり込んだウェーブスプリングあるいは皿ばね自身が有する弾性力でもって確実な抜け止めを実現できる。特に、皿ばねについては、その内周の複数箇所に切り欠き部が形成されている構造が好ましい。このような構造を具備した皿ばねを使用すれば、出力側部材の軸部の凹溝に嵌まり込む部位が周方向の複数箇所に分散されているので、皿ばねを軸部に外挿する組み付け作業が容易となる。 Note that a wave spring or a disc spring is desirable as the locking member of the present invention. If such a wave spring or a disc spring is used, a reliable retaining can be realized by the elastic force of the wave spring or the disc spring itself fitted in the concave groove of the shaft portion of the output side member. In particular, the disc spring preferably has a structure in which cutout portions are formed at a plurality of locations on the inner periphery thereof. If the disc spring having such a structure is used, the portions that fit into the concave grooves of the shaft portion of the output side member are dispersed in a plurality of locations in the circumferential direction, so the disc spring is extrapolated to the shaft portion. Assembly work is easy.
 このクラッチユニットにおけるレバー側クラッチ部は、レバー操作によりトルクが入力される入力側部材と、入力側部材からのトルクをブレーキ側クラッチ部に伝達する連結部材と、入力側部材と連結部材間での係合・離脱により入力側部材からの入力トルクの伝達・遮断を制御する複数の係合子と、各係合子を円周方向に所定間隔で保持する保持器と、回転が拘束された静止側部材と、保持器と静止側部材の間に設けられ、入力側部材からの入力トルクで弾性力を蓄積し、その入力トルクの開放により、蓄積された弾性力で保持器を中立状態に復帰させる第一の弾性部材と、入力側部材と静止側部材の間に設けられ、入力側部材からの入力トルクで弾性力を蓄積し、その入力トルクの開放により、蓄積された弾性力で入力側部材を中立状態に復帰させる第二の弾性部材とを備えた構成が可能である。なお、このレバー側クラッチ部の係合子は円筒ころが望ましい。 The lever side clutch portion in this clutch unit includes an input side member to which torque is input by lever operation, a connecting member that transmits torque from the input side member to the brake side clutch portion, and between the input side member and the connecting member. A plurality of engagement elements that control transmission / cutoff of input torque from the input side member by engagement / disengagement, a cage that holds the engagement elements at predetermined intervals in the circumferential direction, and a stationary side member that is restricted in rotation And an elastic force that is provided between the cage and the stationary member, accumulates an elastic force with an input torque from the input side member, and releases the input torque to return the cage to a neutral state with the accumulated elastic force. One elastic member, provided between the input side member and the stationary side member, accumulates the elastic force with the input torque from the input side member, and releases the input torque to cause the input side member to move with the accumulated elastic force. Neutral Configurations are possible in which a second elastic member to return to. In addition, it is desirable that the engaging member of the lever side clutch portion is a cylindrical roller.
 このクラッチユニットにおけるブレーキ側クラッチ部は、レバー側クラッチ部からのトルクが入力される連結部材と、トルクが出力される出力側部材と、回転が拘束された静止側部材と、その静止側部材と出力側部材間の楔すきまに配設され、両部材間での係合・離脱により連結部材からの入力トルクの伝達と出力側部材からの逆入力トルクの遮断を制御する複数対の係合子とを備えた構成が可能である。なお、このブレーキ側クラッチ部の係合子は円筒ころが望ましい。 The brake side clutch portion in the clutch unit includes a connecting member to which torque from the lever side clutch portion is input, an output side member to which torque is output, a stationary side member in which rotation is constrained, and a stationary side member thereof. A plurality of pairs of engagement elements disposed in the wedge clearance between the output side members and controlling transmission of input torque from the connecting member and blocking of reverse input torque from the output side member by engagement / disengagement between both members; A configuration with The engaging member of the brake side clutch is preferably a cylindrical roller.
 本発明に係るクラッチユニットは、レバー側クラッチ部およびブレーキ側クラッチ部を自動車用シートリフタ部に組み込むことで自動車用途として適している。その場合、入力側部材がレバーに結合され、出力側部材が自動車用シートリフタ部のリンク機構に連結された構造となる。 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. In this case, the input side member is coupled to the lever, and the output side member is connected to the link mechanism of the automobile seat lifter unit.
 本発明によれば、ブレーキ側クラッチ部の出力側部材の軸部に環状の凹溝を設け、出力側部材に組み付けられたレバー側クラッチ部の構成部品およびブレーキ側クラッチ部の構成部品を抜け止めする環状の係止部材を軸部の凹溝に嵌め込んだことにより、一つの係止部材で抜け止め部品を構成することができ、部品点数の削減および組み立ての簡略化が図れる。また、出力側部材は、従来の抜け止め部品の一つであるワッシャを圧入により固定するための軸方向寸法が不要となるので、クラッチユニット全体の小型化も図れる。その結果、組立性が良好で低コストかつコンパクトなクラッチユニットを提供できる。 According to the present invention, the annular concave groove is provided in the shaft portion of the output side member of the brake side clutch portion, and the components of the lever side clutch portion and the components of the brake side clutch portion that are assembled to the output side member are retained. By fitting the annular locking member to be fitted into the concave groove of the shaft portion, it is possible to configure a retaining component with one locking member, and it is possible to reduce the number of components and simplify the assembly. Further, since the output side member does not require an axial dimension for fixing a washer, which is one of the conventional retaining parts, by press-fitting, the entire clutch unit can be reduced in size. As a result, it is possible to provide a clutch unit that is easy to assemble, low in cost, and compact.
本発明の実施形態におけるクラッチユニットの全体構成を示す縦断面図である。It is a longitudinal section showing the whole clutch unit composition in an embodiment of the present invention. 図1の右側面図である。It is a right view of FIG. 図1の左側面図である。It is a left view of FIG. 図1のA-A線に沿う断面図である。FIG. 2 is a cross-sectional view taken along line AA in FIG. 図1のB-B線に沿う断面図である。FIG. 3 is a sectional view taken along line BB in FIG. 1. レバー側側板を示す断面図である。It is sectional drawing which shows a lever side side board. 図6aの左側面図である。FIG. 6b is a left side view of FIG. 6a. レバー側外輪の一例を示す断面図である。It is sectional drawing which shows an example of a lever side outer ring | wheel. 図7aの左側面図である。FIG. 7b is a left side view of FIG. 7a. 図7aの右側面図である。FIG. 7b is a right side view of FIG. 7a. 内輪を示す断面図である。It is sectional drawing which shows an inner ring | wheel. 図8aの左側面図である。FIG. 8b is a left side view of FIG. 8a. 保持器を示す斜視図である。It is a perspective view which shows a holder | retainer. 保持器を示す断面図である。It is sectional drawing which shows a holder | retainer. 図10aの左側面図である。FIG. 10b is a left side view of FIG. 10a. 図10aの断面図である。Fig. 10b is a cross-sectional view of Fig. 10a. 内側センタリングばねを示す斜視図である。It is a perspective view which shows an inner side centering spring. 外側センタリングばねを示す斜視図である。It is a perspective view which shows an outer side centering spring. 出力軸を一方の側から見た斜視図である。It is the perspective view which looked at the output shaft from one side. 出力軸を他方の側から見た斜視図である。It is the perspective view which looked at the output shaft from the other side. 出力軸を示す断面図である。It is sectional drawing which shows an output shaft. 図14aの左側面図である。FIG. 14b is a left side view of FIG. 14a. 図14aの右側面図である。FIG. 14b is a right side view of FIG. 14a. ブレーキ側外輪を示す断面図である。It is sectional drawing which shows a brake side outer ring | wheel. 図15aの左側面図である。FIG. 15b is a left side view of FIG. 15a. カバーを示す断面図である。It is sectional drawing which shows a cover. 図16aの左側面図である。FIG. 16b is a left side view of FIG. 16a. ブレーキ側側板を示す断面図である。It is sectional drawing which shows a brake side plate. 図17aの右側面図である。FIG. 17b is a right side view of FIG. 17a. 摩擦リングを示す正面図である。It is a front view which shows a friction ring. 図18aの左側面図である。FIG. 18b is a left side view of FIG. 18a. 図18aの右側面図である。FIG. 18b is a right side view of FIG. 18a. ウェーブスプリングを示す斜視図である。It is a perspective view which shows a wave spring. ウェーブスプリングを示す正面図である。It is a front view which shows a wave spring. 図19bの右側面図である。It is a right view of FIG. 19b. 皿ばねを示す正断面図である。It is a front sectional view showing a disc spring. 図20aの右側面図である。FIG. 20b is a right side view of FIG. 20a. 図20aの皿ばねによる抜け止め構造を具備したクラッチユニットを示す縦断面図である。It is a longitudinal cross-sectional view which shows the clutch unit which comprised the retaining structure by the disc spring of FIG. 20a. ブレーキ側側板にブレーキ側外輪を組み付ける前の状態を示す斜視図である。It is a perspective view which shows the state before attaching a brake side outer ring | wheel to a brake side side board. ブレーキ側側板にブレーキ側外輪を組み付けた後の状態を示す斜視図である。It is a perspective view which shows the state after attaching the brake side outer ring | wheel to the brake side side board. ブレーキ側側板にブレーキ側外輪およびカバーを組み付けた状態を示す斜視図である。It is a perspective view which shows the state which assembled | attached the brake side outer ring | wheel and the cover to the brake side side plate. ブレーキ側側板とブレーキ側外輪とカバーを加締めにより一体化した状態を示す斜視図である。It is a perspective view which shows the state which integrated the brake side side board, the brake side outer ring | wheel, and the cover by crimping. 図1のC-C線に沿う断面図である。FIG. 2 is a cross-sectional view taken along the line CC of FIG. ブレーキ側側板、ブレーキ側外輪、カバーおよび内側センタリングばねに対して保持器を組み付ける前の状態を示す斜視図である。It is a perspective view which shows the state before attaching a holder | retainer with respect to a brake side side board, a brake side outer ring | wheel, a cover, and an inner centering spring. ブレーキ側側板、ブレーキ側外輪、カバーおよび内側センタリングばねに対して保持器を組み付けた後の状態を示す斜視図である。It is a perspective view which shows the state after attaching a holder | retainer with respect to a brake side side board, a brake side outer ring | wheel, a cover, and an inner centering spring. 自動車の座席シートを示す概念図である。It is a conceptual diagram which shows the seat seat of a motor vehicle. シートリフタ部の一構造例を示す概念図である。It is a conceptual diagram which shows one structural example of a sheet lifter part. シートリフタ部の一構造例を示す要部拡大図である。It is a principal part enlarged view which shows one structural example of a sheet lifter part. 従来のクラッチユニットの全体構成を示す縦断面図である。It is a longitudinal cross-sectional view which shows the whole structure of the conventional clutch unit. 図29のD-D線に沿う横断面図である。FIG. 30 is a transverse sectional view taken along line DD of FIG. 29. 図29のE-E線に沿う横断面図である。FIG. 30 is a transverse sectional view taken along line EE of FIG. 29.
 図1は本発明の実施形態におけるクラッチユニットXの全体構成を示す縦断面図、図2は図1に示すクラッチユニットXの右側面図、図3は図1に示すクラッチユニットXの左側面図、図4は図1のA-Aに沿う横断面図、図5は図1のB-B線に沿う横断面図である。また、図6~図20はクラッチユニットXの主要な各構成部品を示す図である。図21は本発明の他の実施形態におけるクラッチユニットXの全体構成を示す縦断面図、図22~図26はクラッチユニットXの主要な構成部品の組み付け状態を示す図である。 1 is a longitudinal sectional view showing an overall configuration of a clutch unit X according to an embodiment of the present invention, FIG. 2 is a right side view of the clutch unit X shown in FIG. 1, and FIG. 3 is a left side view of the clutch unit X shown in FIG. 4 is a cross-sectional view taken along line AA in FIG. 1, and FIG. 5 is a cross-sectional view taken along line BB in FIG. 6 to 20 are diagrams showing main components of the clutch unit X. FIG. FIG. 21 is a longitudinal sectional view showing the overall configuration of the clutch unit X according to another embodiment of the present invention, and FIGS. 22 to 26 are views showing an assembled state of main components of the clutch unit X. FIG.
 クラッチユニットXは、例えばレバーの操作により座席シートの高さ調整を行う自動車用シートリフタ部(図27、図28a、図28b参照)に組み込まれる。このクラッチユニットXは、図1~図5に示すように、入力側に設けられたレバー側クラッチ部11と、出力側に設けられた逆入力遮断機能のブレーキ側クラッチ部12とをユニット化した構成となっている。 The clutch unit X is incorporated in an automobile seat lifter (see FIGS. 27, 28a, and 28b) that adjusts the height of the seat by operating a lever, for example. As shown in FIGS. 1 to 5, the clutch unit X is a unit of a lever side clutch portion 11 provided on the input side and a brake side clutch portion 12 having a reverse input cutoff function provided on the output side. It has a configuration.
 レバー側クラッチ部11は、図1、図2、図4に示すように、例えば、操作レバー(図示せず)が連結された入力側部材としてのレバー側側板13およびレバー側外輪14と、そのレバー側外輪14からのトルクをブレーキ側クラッチ部12に伝達する連結部材としての内輪15と、その内輪15の外周面15aとレバー側外輪14の内周面14aとの間に形成された楔すきま20に配設された係合子としての例えば複数の円筒ころ16と、円筒ころ16を円周方向等間隔に保持する保持器17と、その保持器17を中立状態に復帰させるための第一の弾性部材である内側センタリングばね18と、レバー側外輪14を中立状態に復帰させるための第二の弾性部材である外側センタリングばね19とを有する。 As shown in FIGS. 1, 2, and 4, the lever-side clutch unit 11 includes, for example, a lever-side plate 13 and a lever-side outer ring 14 as input-side members to which an operation lever (not shown) is coupled, A wedge clearance formed between an inner ring 15 as a connecting member that transmits torque from the lever-side outer ring 14 to the brake-side clutch portion 12, and an outer peripheral surface 15a of the inner ring 15 and an inner peripheral surface 14a of the lever-side outer ring 14. For example, a plurality of cylindrical rollers 16 serving as engagement elements disposed at 20, a cage 17 that holds the cylindrical rollers 16 at equal intervals in the circumferential direction, and a first for returning the cage 17 to a neutral state An inner centering spring 18 that is an elastic member and an outer centering spring 19 that is a second elastic member for returning the lever-side outer ring 14 to a neutral state are provided.
 ロック型と称されるタイプで逆入力遮断機能を有するブレーキ側クラッチ部12は、図1、図3、図5に示すように、レバー側クラッチ部11からのトルクが入力される連結部材としての内輪15と、出力側部材としての出力軸22と、回転が拘束された静止側部材としてのブレーキ側外輪23、カバー24およびブレーキ側側板25と、そのブレーキ側外輪23と出力軸22間の楔すきま26に配設され、ブレーキ側外輪23と出力軸22間での係合・離脱により内輪15からの入力トルクの伝達と出力軸22からの逆入力トルクの遮断を制御する複数対の係合子としての円筒ころ27と、各対の円筒ころ27間に介挿され、それら円筒ころ27同士に離反力を付勢する断面N字形の板ばね28とで主要部が構成されている。なお、出力軸22には突起22fが設けられ、この突起22fがクリアランスをもって挿入された孔15dが内輪15に設けられている(図1参照)。 As shown in FIGS. 1, 3, and 5, the brake side clutch portion 12 having a reverse input blocking function as a lock type is used as a connecting member to which torque from the lever side clutch portion 11 is input. Inner ring 15, output shaft 22 as an output side member, brake side outer ring 23, cover 24 and brake side side plate 25 as stationary side members restricted in rotation, and wedge between the brake side outer ring 23 and output shaft 22 A plurality of pairs of engagement elements disposed in the clearance 26 and controlling transmission of input torque from the inner ring 15 and interruption of reverse input torque from the output shaft 22 by engagement / disengagement between the brake side outer ring 23 and the output shaft 22. And a cylindrical spring 27 interposed between each pair of cylindrical rollers 27, and a plate spring 28 having an N-shaped cross section for biasing the separating force between the cylindrical rollers 27 constitutes a main part. The output shaft 22 is provided with a protrusion 22f, and a hole 15d into which the protrusion 22f is inserted with a clearance is provided in the inner ring 15 (see FIG. 1).
 次に、このクラッチユニットXにおけるレバー側クラッチ部11およびブレーキ側クラッチ部12の主要な構成部品について詳述する。 Next, the main components of the lever side clutch part 11 and the brake side clutch part 12 in the clutch unit X will be described in detail.
 図6a、図6bはレバー側クラッチ部11のレバー側側板13を示す。このレバー側側板13は、その中央部位に出力軸22および内輪15が挿通される孔13aが形成され、外周縁部に複数(例えば5つ)の爪部13bが突設されている。これらの爪部13bは、軸方向に屈曲成形されてその先端部を二股状とし、後述するレバー側外輪14の切欠き凹部14e(図7c参照)に挿入して二股状先端部を外側へ拡開させることにより、レバー側側板13をレバー側外輪14に加締め固定している。なお、図中の符号13cは、座席シートの高さ調整を操作するための操作レバーをレバー側側板13に取り付けるための複数(例えば4つ)の孔である。 FIGS. 6 a and 6 b show the lever side plate 13 of the lever side clutch portion 11. The lever side plate 13 has a hole 13a through which the output shaft 22 and the inner ring 15 are inserted at a central portion thereof, and a plurality of (for example, five) claw portions 13b project from the outer peripheral edge. These claw portions 13b are bent in the axial direction to have a bifurcated tip, and are inserted into a notch recess 14e (see FIG. 7c) of the lever-side outer ring 14 described later to expand the bifurcated tip outward. By opening, the lever side plate 13 is fixed by caulking to the lever side outer ring 14. In addition, the code | symbol 13c in a figure is the several (for example, four) hole for attaching the operation lever for operating the height adjustment of a seat to the lever side side board 13. FIG.
 図7a~図7cはレバー側外輪14を示す。このレバー側外輪14は、一枚の板状素材をプレス加工によりカップ状に成形したもので、中央部14cに出力軸22および内輪15が挿通される孔14bが形成され、その中央部14cから軸方向に延びる筒状部14dの内周には、複数のカム面14aが円周方向等間隔に形成されている(図4参照)。 7a to 7c show the lever side outer ring 14. FIG. The lever-side outer ring 14 is formed by pressing a single plate-shaped material into a cup shape, and a hole 14b through which the output shaft 22 and the inner ring 15 are inserted is formed in the center part 14c. A plurality of cam surfaces 14a are formed at equal intervals in the circumferential direction on the inner periphery of the cylindrical portion 14d extending in the axial direction (see FIG. 4).
 このレバー側外輪14の外周縁部には複数(例えば3つ)の爪部14f,14gが突設されて軸方向に屈曲成形されている。これら爪部14f,14gのうち、一つの爪部14fは、後述する外側センタリングばね19の二つの係止部19a(図12参照)間に挿入配置されて係止され、残り二つの爪部14gは、後述するブレーキ側外輪23の端面に接触した状態でレバー側外輪14の回転によりそのブレーキ側外輪23の端面上を摺動し、カバー24の外周に設けられた回転ストッパとしての一対の係止部24e,24f(図16b参照)間で移動してその回転方向の移動端で係止部24e,24fのそれぞれに当接可能とすることで、操作レバーの操作角度を規制するようにしている。 A plurality (for example, three) of claw portions 14f and 14g project from the outer peripheral edge portion of the lever side outer ring 14 and are bent in the axial direction. Of these claw portions 14f and 14g, one claw portion 14f is inserted and disposed between two locking portions 19a (see FIG. 12) of an outer centering spring 19 to be described later, and the remaining two claw portions 14g. Is a pair of engagements as rotation stoppers provided on the outer periphery of the cover 24 by sliding on the end surface of the brake side outer ring 23 by the rotation of the lever side outer ring 14 in contact with the end surface of the brake side outer ring 23 described later. By moving between the stop portions 24e and 24f (see FIG. 16b) and making contact with each of the locking portions 24e and 24f at the moving ends in the rotational direction, the operation angle of the operation lever is regulated. Yes.
 レバー側外輪14の外周には、レバー側側板13の爪部13b(図6a、図6b参照)が挿入される複数(図では5つ)の切欠き凹部14eが形成されている。この切欠き凹部14eに挿入されたレバー側側板13の爪部13bを加締めることによりレバー側側板13とレバー側外輪14が連結されている。レバー側外輪14とそのレバー側外輪14に加締め固定されたレバー側側板13とでレバー側クラッチ部11の入力側部材を構成している。 In the outer periphery of the lever side outer ring 14, a plurality of (five in the figure) cutout recesses 14e into which the claw portions 13b (see FIGS. 6a and 6b) of the lever side side plate 13 are inserted are formed. The lever side plate 13 and the lever side outer ring 14 are connected by crimping the claw portion 13b of the lever side plate 13 inserted into the notch recess 14e. The lever side outer ring 14 and the lever side plate 13 fixed by crimping to the lever side outer ring 14 constitute an input side member of the lever side clutch portion 11.
 図8a、図8bは内輪15を示す。この内輪15は、出力軸22が挿通される筒状部15bの外径にレバー側外輪14のカム面14aとの間に楔すきま20(図4参照)を形成する外周面15aを備えている。また、筒状部15bの端部から径方向外側に延在して軸方向に屈曲した拡径部15cが一体的に形成され、その拡径部15cをブレーキ側クラッチ部12の保持器として機能させるため、円筒ころ27および板ばね28を収容するポケット15eが円周方向等間隔に形成されている。なお、図中の符号15dは、出力軸22の突起22f(図1参照)がクリアランスをもって挿入される孔である。 8a and 8b show the inner ring 15. FIG. The inner ring 15 includes an outer peripheral surface 15a that forms a wedge clearance 20 (see FIG. 4) between the outer diameter of the cylindrical portion 15b through which the output shaft 22 is inserted and the cam surface 14a of the lever-side outer ring 14. . Further, an enlarged diameter portion 15c extending radially outward from the end of the cylindrical portion 15b and bent in the axial direction is integrally formed, and the enlarged diameter portion 15c functions as a cage for the brake side clutch portion 12. Therefore, pockets 15e for accommodating the cylindrical rollers 27 and the leaf springs 28 are formed at equal intervals in the circumferential direction. In addition, the code | symbol 15d in a figure is a hole into which the protrusion 22f (refer FIG. 1) of the output shaft 22 is inserted with a clearance.
 図9、図10a~図10cは樹脂製の保持器17を示す。この保持器17は、円筒ころ16を収容する複数のポケット17aが円周方向等間隔に形成された円筒状部材である。この保持器17の一方の端部には、二つの切欠き凹部17bが形成され、それぞれの切欠き凹部17bの隣接する二つの端面17cに後述の内側センタリングばね18の係止部18aが係止される(図25参照)。 9 and 10a to 10c show a cage 17 made of resin. The cage 17 is a cylindrical member in which a plurality of pockets 17a for accommodating the cylindrical rollers 16 are formed at equal intervals in the circumferential direction. Two notch recesses 17b are formed at one end of the retainer 17, and a locking part 18a of an inner centering spring 18 (described later) is locked to two adjacent end surfaces 17c of each notch recess 17b. (See FIG. 25).
 図11は内側センタリングばね18を示す。この内側センタリングばね18は、径方向内側に屈曲させた一対の係止部18aを有する断面円形のC字状ばね部材からなり、外側センタリングばね19の内径側に位置する(図25参照)。この内側センタリングばね18は、保持器17とブレーキ側クラッチ部12の静止側部材であるカバー24との間に配設され、両係止部18aが保持器17の二つの端面17c(図9、図10b参照)に係止されると共にカバー24に設けられた爪部24b(図16a、図16b参照)に係止されている(図25、図26a、図26b参照)。 FIG. 11 shows the inner centering spring 18. The inner centering spring 18 is formed of a C-shaped spring member having a circular cross section having a pair of engaging portions 18a bent radially inward, and is located on the inner diameter side of the outer centering spring 19 (see FIG. 25). The inner centering spring 18 is disposed between the cage 17 and a cover 24 that is a stationary side member of the brake side clutch portion 12, and both locking portions 18 a are two end surfaces 17 c (FIG. 9, FIG. 9). 10b) and a claw portion 24b (see FIGS. 16a and 16b) provided on the cover 24 (see FIGS. 25, 26a and 26b).
 この内側センタリングばね18では、レバー側外輪14からの入力トルクの作用時、一方の係止部18aが保持器17の一方の端面17cに、他方の係止部18aがカバー24の爪部24bにそれぞれ係合するので、レバー側外輪14の回転に伴って内側センタリングばね18が押し拡げられて弾性力が蓄積され、レバー側外輪14からの入力トルクの開放時、その弾性復元力により保持器17を中立状態に復帰させる。 In the inner centering spring 18, when the input torque from the lever side outer ring 14 is applied, one locking portion 18 a is on one end surface 17 c of the cage 17, and the other locking portion 18 a is on the claw portion 24 b of the cover 24. As the lever-side outer ring 14 rotates, the inner centering spring 18 is pushed and expanded to accumulate elastic force. When the input torque from the lever-side outer ring 14 is released, the elastic restoring force causes the cage 17 to move. Is returned to the neutral state.
 図12は外側センタリングばね19を示す。この外側センタリングばね19はC字状をなし、その両端を径方向外側に屈曲させた一対の係止部19aを有する帯板状ばね部材であり、内側センタリングばね18の外径側に位置する(図25参照)。外側センタリングばね19は、レバー側クラッチ部11のレバー側外輪14とブレーキ側クラッチ部12のカバー24との間に配設され、両係止部19aがレバー側外輪14に設けられた爪部14f(図7a~図7c参照)に係止されると共にカバー24に設けられた爪部24d(図16a、図16b参照)に係止されている(図26a、図26b参照)。この係止部19aは、内側センタリングばね18の係止部18aに対して円周方向の位相(180°)をずらせて配置されている(図25参照)。 FIG. 12 shows the outer centering spring 19. The outer centering spring 19 is a strip-shaped spring member having a C-shape and having a pair of locking portions 19a whose both ends are bent radially outward, and is located on the outer diameter side of the inner centering spring 18 ( FIG. 25). The outer centering spring 19 is disposed between the lever-side outer ring 14 of the lever-side clutch portion 11 and the cover 24 of the brake-side clutch portion 12, and both locking portions 19 a are claw portions 14 f provided on the lever-side outer ring 14. (See FIGS. 7a to 7c) and is also locked to a claw portion 24d (see FIGS. 16a and 16b) provided on the cover 24 (see FIGS. 26a and 26b). The locking portion 19a is arranged with a circumferential phase (180 °) shifted from the locking portion 18a of the inner centering spring 18 (see FIG. 25).
 この外側センタリングばね19では、レバー操作によりレバー側側板13から入力トルクが作用してレバー側外輪14が回転した場合、一方の係止部19aがレバー側外輪14の爪部14fに、他方の係止部19aがカバー24の爪部24dにそれぞれ係合するので、レバー側外輪14の回転に伴って外側センタリングばね19が押し拡げられて弾性力が蓄積され、レバー側外輪14からの入力トルクを開放すると、その弾性復元力によりレバー側外輪14を中立状態に復帰させる。 In the outer centering spring 19, when the lever side outer plate 14 is rotated by the lever operation by the lever operation and the lever side outer ring 14 rotates, one locking portion 19 a is engaged with the claw portion 14 f of the lever side outer ring 14 and the other engagement. Since the stop portions 19a are respectively engaged with the claw portions 24d of the cover 24, the outer centering spring 19 is pushed and expanded with the rotation of the lever side outer ring 14, and the elastic force is accumulated, and the input torque from the lever side outer ring 14 is increased. When opened, the lever-side outer ring 14 is returned to the neutral state by the elastic restoring force.
 図13a、図13b、図14a~図14cは出力軸22を示す。この出力軸22は、軸部22cから径方向外側に延びて拡径した大径部22dが軸方向ほぼ中央部位に一体的に形成されている。この軸部22cの先端には、シートリフタ部41(図27、図28a、図28b参照)と連結するためのピニオンギヤ41gが同軸的に形成されている。 FIGS. 13 a, 13 b, and 14 a to 14 c show the output shaft 22. The output shaft 22 has a large-diameter portion 22d that extends radially outward from the shaft portion 22c and is integrally formed at a substantially central portion in the axial direction. A pinion gear 41g for connecting to the seat lifter portion 41 (see FIGS. 27, 28a, and 28b) is coaxially formed at the tip of the shaft portion 22c.
 大径部22dの外周面には複数(例えば6つ)の平坦なカム面22aが円周方向等間隔に形成され、ブレーキ側外輪23の内周面23bとの間で設けられた楔すきま26(図5参照)に二つの円筒ころ27および板ばね28がそれぞれ配されている。この大径部22dの一方の端面には、摩擦リング29が収容配置される環状凹部22bが形成されている。また、図中の符号22fは、大径部22dの他方の端面に形成された突起で、内輪15の孔15dにクリアランスをもって挿入される(図1、図8a、図8b参照)。 A plurality of (for example, six) flat cam surfaces 22a are formed on the outer peripheral surface of the large-diameter portion 22d at equal intervals in the circumferential direction, and a wedge clearance 26 provided between the inner peripheral surface 23b of the brake-side outer ring 23 and the like. Two cylindrical rollers 27 and a leaf spring 28 are arranged on each (see FIG. 5). An annular recess 22b in which the friction ring 29 is accommodated is formed on one end face of the large diameter portion 22d. Reference numeral 22f in the figure is a protrusion formed on the other end face of the large-diameter portion 22d and is inserted into the hole 15d of the inner ring 15 with a clearance (see FIGS. 1, 8a, and 8b).
 図15a、図15b、図16a、図16bはブレーキ側外輪23およびそのカバー24を示す。図17a、図17bはブレーキ側側板25を示す。前述のブレーキ側外輪23とカバー24は、このブレーキ側側板25により一体的に加締め固定される。ブレーキ側外輪23は、一枚の素材をプレスで打ち抜き加工した厚肉の板状部材であり、カバー24は、一枚の別素材をプレス加工により成形したものである。なお、図中の符号24c,25bは出力軸22が挿通された孔、符号25cは後述の摩擦リング29の突起29aが嵌合する孔である。 15a, 15b, 16a and 16b show the brake side outer ring 23 and its cover 24. FIG. 17a and 17b show the brake side plate 25. FIG. The brake side outer ring 23 and the cover 24 are caulked and fixed integrally by the brake side plate 25. The brake-side outer ring 23 is a thick plate-like member obtained by punching one material with a press, and the cover 24 is formed by pressing another material with a press. In the figure, reference numerals 24c and 25b denote holes through which the output shaft 22 is inserted, and reference numeral 25c denotes a hole into which a projection 29a of a friction ring 29 described later is fitted.
 ブレーキ側外輪23の外周には複数(3個)の切欠き凹部23aが形成されると共に、これら切欠き凹部23aに対応させて、カバー24の外周にも複数(3個)の切欠き凹部24aが形成されている。図22a、図22bに示すようにブレーキ側外輪23の切欠き凹部23aにブレーキ側側板25の爪部25aが挿入されると共に、図23に示すようにカバー24の切欠き凹部24aにブレーキ側側板25の爪部25aが挿入される。 A plurality (three) of cutout recesses 23a are formed on the outer periphery of the brake side outer ring 23, and a plurality (three) of cutout recesses 24a are also formed on the outer periphery of the cover 24 so as to correspond to the cutout recesses 23a. Is formed. 22a and 22b, the claw portion 25a of the brake side plate 25 is inserted into the notch recess 23a of the brake side outer ring 23, and the brake side plate is inserted into the notch recess 24a of the cover 24 as shown in FIG. 25 claw portions 25a are inserted.
 これら切欠き凹部23a,24aに挿入されたブレーキ側側板25の爪部25aを加締めることによりブレーキ側外輪23とカバー24を連結してブレーキ側側板25と共に一体化して静止側部材を構成する。このブレーキ側側板25の爪部25aの加締めは、加締め治具(図示せず)を利用することにより、その爪部25aの二股状先端部25aを外側へ拡開させることにより行われる(図24参照)。 By tightening the claw portion 25a of the brake side plate 25 inserted into the notches 23a and 24a, the brake side outer ring 23 and the cover 24 are connected and integrated with the brake side plate 25 to constitute a stationary member. Crimp claw portion 25a of the brake-side side plate 25, by utilizing crimping jig (not shown), it is carried out by expanding the bifurcated distal end portion 25a 1 of the claw portion 25a to the outside (See FIG. 24).
 ブレーキ側外輪23の内周面23bと出力軸22のカム面22aとの間に楔すきま26が形成されている(図5参照)。カバー24には軸方向に突出する爪部24bが形成され、その爪部24bをレバー側クラッチ部11の内側センタリングばね18の二つの係止部18a間に配置している(図11、図26a、図26b参照)。このカバー24の爪部24bは、その爪部形成位置の外径側を面起こしすることにより形成されている。カバー24の外周には軸方向に突出する爪部24dが形成されている。この爪部24dは、レバー側クラッチ部11の外側センタリングばね19の二つの係止部19a間に配置される(図12、図26a、図26b参照)。 A wedge clearance 26 is formed between the inner peripheral surface 23b of the brake side outer ring 23 and the cam surface 22a of the output shaft 22 (see FIG. 5). The cover 24 is formed with a claw portion 24b protruding in the axial direction, and the claw portion 24b is disposed between the two locking portions 18a of the inner centering spring 18 of the lever side clutch portion 11 (FIGS. 11 and 26a). , See FIG. 26b). The claw part 24b of the cover 24 is formed by raising the outer diameter side of the claw part forming position. A claw portion 24 d that protrudes in the axial direction is formed on the outer periphery of the cover 24. The claw portion 24d is disposed between the two locking portions 19a of the outer centering spring 19 of the lever side clutch portion 11 (see FIGS. 12, 26a, and 26b).
 カバー24の外周には二組の係止部24e,24fが段付き加工により形成されている(図26a、図26b参照)。これら係止部24e,24fは、レバー側外輪14の爪部14gがブレーキ側外輪23の端面に接触した状態で回転する際にその回転方向で当接可能とすることで、操作レバーの操作角度を規制する回転ストッパとして機能する。つまり、操作レバーの操作によりレバー側外輪14が回転すれば、その爪部14gがカバー24の係止部24eと24fとの間でカバー24の外周に沿って移動することになる。 Two sets of locking portions 24e and 24f are formed on the outer periphery of the cover 24 by step processing (see FIGS. 26a and 26b). The engaging portions 24e and 24f can be contacted in the rotation direction when the claw portion 14g of the lever-side outer ring 14 rotates in a state of being in contact with the end surface of the brake-side outer ring 23, whereby the operating angle of the operating lever It functions as a rotation stopper that regulates That is, when the lever side outer ring 14 is rotated by the operation of the operation lever, the claw portion 14g moves along the outer periphery of the cover 24 between the locking portions 24e and 24f of the cover 24.
 ブレーキ側側板25の外周には、シートリフタ部へのクラッチ取付部として、一つのフランジ部25eと二つのフランジ部25fが設けられている(図2~図4参照)。これら三つのフランジ部25e,25fの先端部には、シートリフタ部への取付用孔25g,25hが穿設されてその取付孔25g,25hを囲撓するように円筒部25i,25jが軸方向に突設されている。 The outer periphery of the brake side plate 25 is provided with one flange portion 25e and two flange portions 25f as clutch attachment portions to the seat lifter portion (see FIGS. 2 to 4). At the tips of these three flange portions 25e and 25f, holes 25g and 25h for attachment to the seat lifter portion are formed so that the cylindrical portions 25i and 25j are axially bent so as to surround and bend the attachment holes 25g and 25h. Projected.
 図18a~図18cは樹脂製の摩擦リング29を示す。摩擦リング29の端面には、その円周方向に沿って等間隔に円形の突起29aが複数個設けられ、この突起29aをブレーキ側側板25の孔25cに圧入して嵌合させることによりブレーキ側側板25に固着される(図1、図3参照)。 18a to 18c show a friction ring 29 made of resin. A plurality of circular protrusions 29a are provided on the end face of the friction ring 29 at equal intervals along the circumferential direction thereof, and the protrusions 29a are press-fitted into the holes 25c of the brake side plate 25 to be fitted to the brake side. It adheres to the side plate 25 (refer FIG. 1, FIG. 3).
 この突起29aの圧入時、樹脂材による突起29aの弾性変形でもって孔25cとの嵌合状態が得られる。このように突起29aと孔25cの圧入嵌合構造を採用することにより、搬送時などの取り扱いで摩擦リング29がブレーキ側側板25から脱落することを未然に防止でき、組立時のハンドリング性を向上させることができる。 When the projection 29a is press-fitted, the fitting state with the hole 25c is obtained by elastic deformation of the projection 29a by the resin material. By adopting the press-fitting structure of the protrusions 29a and the holes 25c in this way, the friction ring 29 can be prevented from dropping off from the brake side plate 25 during handling and the like, and handling characteristics during assembly are improved. Can be made.
 この摩擦リング29は出力軸22の大径部22dに形成された環状凹部22bの内周面22eに締め代をもって圧入される(図13a、図14a、図14b参照)。摩擦リング29の外周面29cと出力軸22の環状凹部22bの内周面22eとの間に生じる摩擦力によって、出力軸22に回転抵抗が付与される。 The friction ring 29 is press-fitted with an allowance to the inner peripheral surface 22e of the annular recess 22b formed in the large diameter portion 22d of the output shaft 22 (see FIGS. 13a, 14a, and 14b). A rotational resistance is applied to the output shaft 22 by a frictional force generated between the outer peripheral surface 29 c of the friction ring 29 and the inner peripheral surface 22 e of the annular recess 22 b of the output shaft 22.
 この摩擦リング29の外周面29cには、複数の凹溝状のスリット29bが円周方向等間隔に形成されている(図5参照)。このようにスリット29bを設けることにより、摩擦リング29に弾性を持たせることができることから、出力軸22の内径公差および摩擦リング29の外径公差に対する摺動トルクの変化率が大きくなることはない。 A plurality of concave grooves 29b are formed on the outer peripheral surface 29c of the friction ring 29 at equal intervals in the circumferential direction (see FIG. 5). By providing the slit 29b in this manner, the friction ring 29 can be made elastic, so that the rate of change of the sliding torque with respect to the inner diameter tolerance of the output shaft 22 and the outer diameter tolerance of the friction ring 29 does not increase. .
 つまり、摩擦リング29の外周面29cと出力軸22の環状凹部22bの内周面22eとの間に生じる摩擦力によって付与される回転抵抗の設定範囲を小さくすることができて回転抵抗の大きさを適正に設定することが容易となる。また、そのスリット29bがグリース溜まりとなるので摩擦リング29の外周面29cが出力軸22の環状凹部22bの内周面22eとの摺動で摩耗することを抑制できる。 That is, the setting range of the rotational resistance provided by the frictional force generated between the outer peripheral surface 29c of the friction ring 29 and the inner peripheral surface 22e of the annular recess 22b of the output shaft 22 can be reduced, and the magnitude of the rotational resistance can be reduced. Can be set appropriately. Further, since the slit 29b becomes a grease reservoir, it is possible to suppress the outer peripheral surface 29c of the friction ring 29 from being worn by sliding with the inner peripheral surface 22e of the annular recess 22b of the output shaft 22.
 図19a~図19cは係止部材であるウェーブスプリング30を示す。このウェーブスプリング30は、例えばコイリング加工により成形されたものである。図1に示すように、ブレーキ側クラッチ部12の出力軸22の軸部22cに環状の凹溝22gを設け(図13a、図13b、図14a参照)、その出力軸22に組み付けられたレバー側クラッチ部11の構成部品、例えばレバー側外輪14、およびブレーキ側クラッチ部12の構成部品、例えば内輪15を抜け止めするウェーブスプリング30を軸部22cの凹溝22gに嵌め込んだ構造としている。このようなウェーブスプリング30を使用することにより、出力軸22の軸部22cの凹溝22gに嵌まり込んだウェーブスプリング30自身が有する弾性力でもって確実な抜け止めを実現できる。 19a to 19c show a wave spring 30 as a locking member. The wave spring 30 is formed by, for example, coiling. As shown in FIG. 1, an annular groove 22g is provided in the shaft portion 22c of the output shaft 22 of the brake clutch portion 12 (see FIGS. 13a, 13b, and 14a), and the lever side assembled to the output shaft 22 is provided. The structure is such that a wave spring 30 for retaining the component parts of the clutch portion 11 such as the lever-side outer ring 14 and the brake-side clutch portion 12 such as the inner ring 15 is fitted in the concave groove 22g of the shaft portion 22c. By using such a wave spring 30, it is possible to realize a reliable retaining with the elastic force of the wave spring 30 itself fitted in the concave groove 22 g of the shaft portion 22 c of the output shaft 22.
 このように、レバー側外輪14および内輪15の抜け止め構造として、ウェーブスプリング30を軸部22cの凹溝22gに嵌め込んだ構造としたことにより、従来ではウェーブワッシャ130およびワッシャ131(図29参照)からなる二つの抜け止め部品を必要としていたのに対して、ウェーブスプリング30を凹溝22gに嵌め込んで固定することができることから、一つのウェーブスプリング30で抜け止め部品を構成でき、部品点数の削減および組み立ての簡略化が図れる。また、出力軸22は、従来の抜け止め部品の一つであるワッシャ131(図29参照)を圧入により固定するための軸方向寸法Lが不要となることから、その出力軸22の軸方向寸法Lを従来よりも短くすることができ(L<L)、クラッチユニット全体の小型化が容易となる。 Thus, as a structure for preventing the lever-side outer ring 14 and the inner ring 15 from coming off, the wave spring 30 is fitted into the concave groove 22g of the shaft portion 22c. 2), the wave spring 30 can be fixed by being fitted into the concave groove 22g, so that the single wave spring 30 can be used as a retaining part. Can be reduced and the assembly can be simplified. Further, the output shaft 22, since the washer 131 which is one of the conventional retaining part axial dimension L 1 to press-fitted (see FIG. 29) becomes unnecessary, the axial direction of the output shaft 22 it is possible to shorten the dimension L 2 than the conventional (L 2 <L 1), the overall size of the clutch unit is facilitated.
 なお、レバー側外輪14および内輪15を抜け止めする係止部材としては、ウェーブスプリング30以外に、図20a、図20bに示すような皿ばね31であってもよい。このの場合も、図21に示すように、出力軸22の軸部22cに凹溝22gを設け、その凹溝22gに皿ばね31を嵌め込んだ構造とする。この皿ばね31でレバー側外輪14および内輪15を抜け止めしている。このような皿ばね31を使用することにより、出力軸22の軸部22cの凹溝22gに嵌まり込んだ皿ばね31自身が有する弾性力でもって確実な抜け止めを実現できる。 In addition to the wave spring 30, a disc spring 31 as shown in FIGS. 20a and 20b may be used as a locking member for preventing the lever-side outer ring 14 and the inner ring 15 from coming off. Also in this case, as shown in FIG. 21, a concave groove 22g is provided in the shaft portion 22c of the output shaft 22, and a disc spring 31 is fitted in the concave groove 22g. The disc spring 31 prevents the lever-side outer ring 14 and the inner ring 15 from coming off. By using such a disc spring 31, it is possible to reliably prevent the disc spring 31 from coming off with the elastic force of the disc spring 31 itself fitted into the concave groove 22 g of the shaft portion 22 c of the output shaft 22.
 この皿ばね31の場合、図20a、図20bに示すように、その内周の複数箇所に矩形状の切り欠き部31aが形成されている。このような矩形状の切り欠き部31aを形成することにより、隣接する切り欠き部31a間に舌片部31bが形成されることになる。この皿ばね31を出力軸22に組み付けるに際しては、皿ばね31の舌片部31bを出力軸22の軸部22cに外挿して凹溝22gに嵌め込む。このような構造の皿ばね31では、凹溝22gに嵌まり込む部位、つまり、舌片部31bが周方向の複数箇所に分散されているので、皿ばね31を軸部22cに外挿する組み付け作業が容易となる。 In the case of this disc spring 31, as shown in FIGS. 20a and 20b, rectangular cutout portions 31a are formed at a plurality of locations on the inner periphery thereof. By forming such a rectangular cutout 31a, the tongue piece 31b is formed between the adjacent cutouts 31a. When the disc spring 31 is assembled to the output shaft 22, the tongue portion 31b of the disc spring 31 is externally inserted into the shaft portion 22c of the output shaft 22 and is fitted into the concave groove 22g. In the disc spring 31 having such a structure, the portion that fits into the concave groove 22g, that is, the tongue piece portion 31b is dispersed at a plurality of locations in the circumferential direction, so that the disc spring 31 is extrapolated to the shaft portion 22c. Work becomes easy.
 以上の構成からなるクラッチユニットXにおけるレバー側クラッチ部11およびブレーキ側クラッチ部12の動作を説明する。 The operation of the lever side clutch portion 11 and the brake side clutch portion 12 in the clutch unit X having the above configuration will be described.
 レバー側クラッチ部11では、レバー側外輪14に入力トルクが作用すると、円筒ころ16がそのレバー側外輪14と内輪15間の楔すきま20に係合し、その円筒ころ16を介して内輪15にトルクが伝達されて内輪15が回転する。この時、レバー側外輪14および保持器17の回転に伴って両センタリングばね18,19に弾性力が蓄積される。その入力トルクがなくなると、両センタリングばね18,19の弾性力によりレバー側外輪14および保持器17が中立状態に復帰する一方で、内輪15は、与えられた回転位置をそのまま維持する。従って、このレバー側外輪14の回転繰り返し、つまり、操作レバーのポンピング操作により、内輪15は寸動回転する。 In the lever side clutch portion 11, when an input torque acts on the lever side outer ring 14, the cylindrical roller 16 engages with a wedge clearance 20 between the lever side outer ring 14 and the inner ring 15, and the inner ring 15 is engaged via the cylindrical roller 16. Torque is transmitted and the inner ring 15 rotates. At this time, an elastic force is accumulated in the centering springs 18 and 19 as the lever-side outer ring 14 and the cage 17 rotate. When the input torque is lost, the lever-side outer ring 14 and the cage 17 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 lever side outer ring 14, that is, by the pumping operation of the operation lever.
 ブレーキ側クラッチ部12では、出力軸22に逆入力トルクが入力されると、板ばね28が各対の円筒ころ27に離反力を付勢することにより、円筒ころ27がその出力軸22とブレーキ側外輪23間の楔すきま26と係合して出力軸22がブレーキ側外輪23に対してロックされる。従って、出力軸22からの逆入力トルクは、ブレーキ側クラッチ部12によってロックされてレバー側クラッチ部11への逆入力トルクの還流が遮断される。 In the brake-side clutch portion 12, when reverse input torque is input to the output shaft 22, the leaf spring 28 urges the pair of cylindrical rollers 27 so that the cylindrical rollers 27 are braked with the output shaft 22. The output shaft 22 is locked to the brake side outer ring 23 by engaging with the wedge clearance 26 between the side outer rings 23. Accordingly, the reverse input torque 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.
 一方、レバー側外輪14からの入力トルクがレバー側クラッチ部11を介して内輪15に入力され、内輪15が円筒ころ27と当接して板ばね28の弾性力に抗して押圧することにより、その円筒ころ27が楔すきま26から離脱して出力軸22のロック状態が解除され、出力軸22は回転可能となる。内輪15がさらに回転すると、内輪15の孔15dと出力軸22の突起22fとのクリアランスが詰まって内輪15が出力軸22の突起22fと回転方向で当接することにより、内輪15からの入力トルクが突起22fを介して出力軸22に伝達され、出力軸22が回転する。 On the other hand, the input torque from the lever-side outer ring 14 is input to the inner ring 15 via the lever-side clutch portion 11, and the inner ring 15 comes into contact with the cylindrical roller 27 and presses against the elastic force of the leaf spring 28. The cylindrical roller 27 is removed 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 15d of the inner ring 15 and the protrusion 22f of the output shaft 22 is clogged, and the inner ring 15 comes into contact with the protrusion 22f of the output shaft 22 in the rotation direction, so that the input torque from the inner ring 15 is increased. The output shaft 22 is transmitted to the output shaft 22 through the protrusion 22f, and the output shaft 22 rotates.
 以上で詳述した構造を具備するクラッチユニットXは、例えば自動車用シートリフタ部に組み込まれて使用される。図27は自動車の乗員室に装備される座席シート40を示す。座席シート40は着座シート40aと背もたれシート40bとで構成され、着座シート40aの高さHを調整するシートリフタ部41などを備えている。着座シート40aの高さHの調整はシートリフタ部41の操作レバー41aによって行う。 The clutch unit X having the structure described in detail above is used by being incorporated in, for example, an automobile seat lifter. FIG. 27 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 41a of the seat lifter 41.
 図28aはシートリフタ部41の一構造例を概念的に示す。シートスライドアジャスタ41bのスライド可動部材41bにリンク部材41c,41dの一端がそれぞれ回動自在に枢着される。リンク部材41c,41dの他端はそれぞれ着座シート40aに回動自在に枢着される。リンク部材41cの他端はリンク部材41eを介してセクターギヤ41fに回動自在に枢着される。セクターギヤ41fは着座シート40aに回動自在に枢着され、支点41f回りに揺動可能である。リンク部材41dの他端は着座シート40aに回動自在に枢着される。 FIG. 28 a conceptually shows one structural example of the sheet lifter unit 41. Seat slide adjuster 41b of the slide moving member 41b 1 to the link member 41c, one end of 41d are respectively rotatably hinged. 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. Sector gear 41f is pivotally rotatably sitting seat 40a, a swingable fulcrum 41f 1 around. The other end of the link member 41d is pivotally attached to the seating seat 40a.
 前述した実施形態のクラッチユニットXは、着座シート40aの適宜の部位に固定される。このクラッチユニットXの着座シート40aへの固定は、ブレーキ側側板25の三つのフランジ部25e,25fを、その円筒部25i,25jの先端部分を外側へ拡径させるように塑性変形させることで着座シート40aのシートフレーム(図示せず)に加締め固定する。 The clutch unit X of the above-described embodiment is fixed to an appropriate part of the seating seat 40a. The clutch unit X is fixed to the seating seat 40a by plastically deforming the three flange portions 25e and 25f of the brake side plate 25 so that the distal end portions of the cylindrical portions 25i and 25j are expanded outward. It is fixed by caulking to a seat frame (not shown) of the seat 40a.
 一方、レバー側クラッチ部11のレバー側側板13に操作レバー41aが結合され、ブレーキ側クラッチ部12の出力軸22に回転部材であるセクターギヤ41fと噛合するピニオンギヤ41gが設けられている。このピニオンギヤ41gは、図1、図13a、図13b、図14a、図14bに示すように出力軸22の軸部22cの先端に一体的に形成されている。 On the other hand, the operation lever 41a is coupled to the lever side plate 13 of the lever side clutch portion 11, and the output shaft 22 of the brake side clutch portion 12 is provided with a pinion gear 41g that meshes with the sector gear 41f that is a rotating member. The pinion gear 41g is integrally formed at the tip of the shaft portion 22c of the output shaft 22 as shown in FIGS. 1, 13a, 13b, 14a, and 14b.
 図28bにおいて、操作レバー41aを反時計方向(上側)に揺動操作すると、その方向の入力トルクがクラッチユニットXを介してピニオンギヤ41gに伝達され、ピニオンギヤ41gが反時計方向に回動する。そして、ピニオンギヤ41gと噛合するセクターギヤ41fが時計方向に揺動して、リンク部材41cの他端をリンク部材41eを介して引っ張る。その結果、リンク部材41cとリンク部材41dが共に起立して、着座シート40aの座面が高くなる。 28b, when the operation lever 41a is swung counterclockwise (upward), the input torque in that direction is transmitted to the pinion gear 41g via the clutch unit X, and the pinion gear 41g rotates counterclockwise. Then, the sector gear 41f that meshes with the pinion gear 41g 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.
 このようにして、着座シート40aの高さHを調整した後、操作レバー41aを開放すると、操作レバー41aが二つのセンタリングばね18,19の弾性力によって時計方向に回動して元の位置(中立状態)に戻る。なお、操作レバー41aを時計方向(下側)に揺動操作した場合は、上記とは逆の動作によって、着座シート40aの座面が低くなる。また、高さ調整後に操作レバー41aを開放すると、操作レバー41aが反時計方向に回動して元の位置(中立状態)に戻る。 In this way, after adjusting the height H of the seating seat 40a, when the operation lever 41a is opened, the operation lever 41a is rotated clockwise by the elastic force of the two centering springs 18 and 19 to return to the original position ( Return to the neutral state. When the operation lever 41a is swung clockwise (downward), the seating surface of the seating seat 40a is lowered by the reverse operation. When the operation lever 41a is released after the height adjustment, the operation lever 41a rotates counterclockwise and returns to the original position (neutral state).
 本発明は前述した実施形態に何ら限定されるものではなく、本発明の要旨を逸脱しない範囲内において、さらに種々なる形態で実施し得ることは勿論のことであり、本発明の範囲は、特許請求の範囲によって示され、さらに特許請求の範囲に記載の均等の意味、および範囲内のすべての変更を含む。 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.

Claims (9)

  1.  入力側に設けられ、レバー操作により出力側への回転トルクの伝達・遮断を制御するレバー側クラッチ部と、出力側に設けられ、前記レバー側クラッチ部からの入力トルクを出力側へ伝達すると共に出力側からの逆入力トルクを遮断するブレーキ側クラッチ部とからなり、
     前記ブレーキ側クラッチ部の出力側部材の軸部に環状の凹溝を設け、前記出力側部材に組み付けられた前記レバー側クラッチ部の構成部品およびブレーキ側クラッチ部の構成部品を抜け止めする環状の係止部材を前記軸部の凹溝に嵌め込んだことを特徴とするクラッチユニット。
    Provided on the input side and controls the transmission / cutoff of rotational torque to the output side by lever operation, and provided on the output side, transmits input torque from the lever side clutch unit to the output side It consists of a brake side clutch that cuts off the reverse input torque from the output side,
    An annular groove is provided in the shaft part of the output side member of the brake side clutch part, and an annular part that prevents the component part of the lever side clutch part and the component part of the brake side clutch part that are assembled to the output side member is provided. A clutch unit characterized in that a locking member is fitted in the concave groove of the shaft portion.
  2.  前記係止部材をウェーブスプリングとした請求項1に記載のクラッチユニット。 The clutch unit according to claim 1, wherein the locking member is a wave spring.
  3.  前記係止部材を皿ばねとした請求項1に記載のクラッチユニット。 The clutch unit according to claim 1, wherein the locking member is a disc spring.
  4.  前記皿ばねは、その内周の複数箇所に切り欠き部が形成されている請求項3に記載のクラッチユニット。 The clutch unit according to claim 3, wherein the disc spring is formed with cutout portions at a plurality of locations on an inner periphery thereof.
  5.  前記レバー側クラッチ部は、レバー操作によりトルクが入力される入力側部材と、入力側部材からのトルクをブレーキ側クラッチ部に伝達する連結部材と、前記入力側部材と連結部材間での係合・離脱により入力側部材からの入力トルクの伝達・遮断を制御する複数の係合子と、各係合子を円周方向に所定間隔で保持する保持器と、回転が拘束された静止側部材と、前記保持器と静止側部材の間に設けられ、入力側部材からの入力トルクで弾性力を蓄積し、その入力トルクの開放により、蓄積された弾性力で保持器を中立状態に復帰させる第一の弾性部材と、前記入力側部材と静止側部材の間に設けられ、入力側部材からの入力トルクで弾性力を蓄積し、その入力トルクの開放により、蓄積された弾性力で入力側部材を中立状態に復帰させる第二の弾性部材とを備えている請求項1~4のいずれか一項に記載のクラッチユニット。 The lever side clutch portion includes an input side member to which torque is input by lever operation, a connecting member that transmits torque from the input side member to the brake side clutch portion, and engagement between the input side member and the connecting member. A plurality of engagement elements that control transmission / cutoff of input torque from the input side member by detachment, a retainer that holds the engagement elements at predetermined intervals in the circumferential direction, and a stationary side member that is restricted in rotation, A first is provided between the cage and the stationary side member, accumulates an elastic force with an input torque from the input side member, and returns the cage to a neutral state with the accumulated elastic force by releasing the input torque. The elastic member is provided between the input side member and the stationary side member, and an elastic force is accumulated by an input torque from the input side member. By releasing the input torque, the input side member is moved by the accumulated elastic force. Return to neutral Clutch unit according to any one of the second elastic member and to which claims 1 to 4, comprising a.
  6.  前記ブレーキ側クラッチ部は、レバー側クラッチ部からのトルクが入力される連結部材と、トルクが出力される出力側部材と、回転が拘束された静止側部材と、その静止側部材と出力側部材間の楔すきまに配設され、両部材間での係合・離脱により前記連結部材からの入力トルクの伝達と出力側部材からの逆入力トルクの遮断を制御する複数対の係合子とを備えている請求項1~4のいずれか一項に記載のクラッチユニット。 The brake side clutch portion includes a connecting member to which torque from the lever side clutch portion is input, an output side member to which torque is output, a stationary side member in which rotation is restricted, and the stationary side member and the output side member. A plurality of pairs of engagement elements that are disposed in a wedge clearance between the members and control transmission of input torque from the connecting member and blocking of reverse input torque from the output side member by engagement / disengagement between the two members. The clutch unit according to any one of claims 1 to 4.
  7.  前記レバー側クラッチ部の係合子あるいはブレーキ側クラッチ部の係合子の少なくとも一方を円筒ころとした請求項5又は6に記載のクラッチユニット。 The clutch unit according to claim 5 or 6, wherein at least one of the engagement member of the lever side clutch portion or the engagement member of the brake side clutch portion is a cylindrical roller.
  8.  前記レバー側クラッチ部とブレーキ側クラッチ部が自動車用シートリフタ部に組み込まれている請求項1~7のいずれか一項に記載のクラッチユニット。 The clutch unit according to any one of claims 1 to 7, wherein the lever side clutch part and the brake side clutch part are incorporated in an automobile seat lifter part.
  9.  前記レバー側クラッチ部の入力側部材がレバーに結合され、前記ブレーキ側クラッチ部の出力側部材が自動車用シートリフタ部のリンク機構に連結されている請求項8に記載のクラッチユニット。 The clutch unit according to claim 8, wherein an input side member of the lever side clutch portion is coupled to a lever, and an output side member of the brake side clutch portion is connected to a link mechanism of an automobile seat lifter portion.
PCT/JP2011/069884 2010-09-21 2011-09-01 Clutch unit WO2012039253A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010-210814 2010-09-21
JP2010210814A JP2012067792A (en) 2010-09-21 2010-09-21 Clutch unit

Publications (1)

Publication Number Publication Date
WO2012039253A1 true WO2012039253A1 (en) 2012-03-29

Family

ID=45873743

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2011/069884 WO2012039253A1 (en) 2010-09-21 2011-09-01 Clutch unit

Country Status (2)

Country Link
JP (1) JP2012067792A (en)
WO (1) WO2012039253A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3875797A4 (en) * 2018-10-31 2022-07-27 NTN Corporation Clutch unit

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6653565B2 (en) * 2015-12-18 2020-02-26 シロキ工業株式会社 Vehicle clutch unit
KR20220046890A (en) * 2020-10-08 2022-04-15 현대트랜시스 주식회사 Eccentrictiy prevention device for pumping device

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006226366A (en) * 2005-02-16 2006-08-31 Ntn Corp Rotation transmission device
JP2009156283A (en) * 2007-12-25 2009-07-16 Ntn Corp Rotation transmitting device
JP2009210114A (en) * 2008-03-06 2009-09-17 Ntn Corp Clutch unit

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006226366A (en) * 2005-02-16 2006-08-31 Ntn Corp Rotation transmission device
JP2009156283A (en) * 2007-12-25 2009-07-16 Ntn Corp Rotation transmitting device
JP2009210114A (en) * 2008-03-06 2009-09-17 Ntn Corp Clutch unit

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3875797A4 (en) * 2018-10-31 2022-07-27 NTN Corporation Clutch unit
US11434962B2 (en) 2018-10-31 2022-09-06 Ntn Corporation Clutch unit

Also Published As

Publication number Publication date
JP2012067792A (en) 2012-04-05

Similar Documents

Publication Publication Date Title
WO2011114878A1 (en) Clutch unit
WO2012120961A1 (en) Clutch unit
WO2011102285A1 (en) Clutch unit
JP2010019343A (en) Clutch unit
WO2012039253A1 (en) Clutch unit
JP2010025206A (en) Clutch unit
JP4987604B2 (en) Clutch unit
JP2012067793A (en) Clutch unit
JP5554083B2 (en) Clutch unit
JP2009299869A (en) Clutch unit
JP5634784B2 (en) Clutch unit
JP5329056B2 (en) Clutch unit
JP5479144B2 (en) Clutch unit
JP5661305B2 (en) Clutch unit
JP2010025204A (en) Clutch unit
JP2008075766A (en) Clutch unit
JP5009075B2 (en) Clutch unit
JP2009030635A (en) Clutch unit
JP2012041943A (en) Clutch unit
JP7152869B2 (en) clutch unit
JP5465035B2 (en) Clutch unit
JP2011169403A (en) Clutch unit
JP2012052625A (en) Clutch unit
JP2012026503A (en) Clutch unit
JP5248055B2 (en) Clutch unit

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11826699

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11826699

Country of ref document: EP

Kind code of ref document: A1