WO2012039253A1 - Unité d'embrayage - Google Patents

Unité d'embrayage Download PDF

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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
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WO
WIPO (PCT)
Prior art keywords
lever
input
brake
clutch
torque
Prior art date
Application number
PCT/JP2011/069884
Other languages
English (en)
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/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
    • B60N2/04—Seats 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
    • B60N2/16—Seats 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
    • B60N2/1635—Seats 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
    • B60N2/167—Ratchet mechanism
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/90—Details or parts not otherwise provided for
    • B60N2/919—Positioning and locking mechanisms
    • B60N2/933—Positioning and locking mechanisms rotatable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/086—Freewheels 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
    • F16D41/088—Freewheels 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/10—Freewheels 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
    • F16D41/105—Freewheels 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)
  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)
  • Seats For Vehicles (AREA)

Abstract

La présente invention comporte : une section d'embrayage côté levier (11) qui est mise en œuvre du côté admission et qui commande, par le fonctionnement du levier, la transmission du couple de rotation au côté sortie et le blocage de la transmission de celui-ci ; et une section d'embrayage côté frein (12) mise en œuvre du côté sortie, la section d'embrayage côté frein (12) transmettant le couple d'entrée, qui est transmis en provenance de la section d'embrayage côté levier (11), au côté sortie et bloquant une entrée de couple inverse en provenance du côté sortie. Un conduit annulaire (22g) est mis en œuvre dans la section arbre (22c) de l'arbre de sortie (22) de la section d'embrayage côté frein (12). Un ressort ondulé annulaire (30) est placé dans le conduit (22g) dans la section arbre (22c), et le ressort ondulé (30) retient la bague extérieure côté levier (14) de la section d'embrayage côté levier (11) et la bague intérieure (15) de la section d'embrayage côté frein (12), la section d'embrayage côté levier (11) et la section d'embrayage côté frein (12) étant montées sur l'arbre de sortie (22).
PCT/JP2011/069884 2010-09-21 2011-09-01 Unité d'embrayage WO2012039253A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010-210814 2010-09-21
JP2010210814A JP2012067792A (ja) 2010-09-21 2010-09-21 クラッチユニット

Publications (1)

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

Family

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Application Number Title Priority Date Filing Date
PCT/JP2011/069884 WO2012039253A1 (fr) 2010-09-21 2011-09-01 Unité d'embrayage

Country Status (2)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3875797A4 (fr) * 2018-10-31 2022-07-27 NTN Corporation Unité d'embrayage

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6653565B2 (ja) * 2015-12-18 2020-02-26 シロキ工業株式会社 車両用クラッチユニット
KR20220046890A (ko) * 2020-10-08 2022-04-15 현대트랜시스 주식회사 펌핑 디바이스용 편심 방지기구

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006226366A (ja) * 2005-02-16 2006-08-31 Ntn Corp 回転伝達装置
JP2009156283A (ja) * 2007-12-25 2009-07-16 Ntn Corp 回転伝達装置
JP2009210114A (ja) * 2008-03-06 2009-09-17 Ntn Corp クラッチユニット

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006226366A (ja) * 2005-02-16 2006-08-31 Ntn Corp 回転伝達装置
JP2009156283A (ja) * 2007-12-25 2009-07-16 Ntn Corp 回転伝達装置
JP2009210114A (ja) * 2008-03-06 2009-09-17 Ntn Corp クラッチユニット

Cited By (2)

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

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