WO2017150401A1 - Unité d'embrayage - Google Patents

Unité d'embrayage Download PDF

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Publication number
WO2017150401A1
WO2017150401A1 PCT/JP2017/007295 JP2017007295W WO2017150401A1 WO 2017150401 A1 WO2017150401 A1 WO 2017150401A1 JP 2017007295 W JP2017007295 W JP 2017007295W WO 2017150401 A1 WO2017150401 A1 WO 2017150401A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
output shaft
lever
side clutch
rotational torque
Prior art date
Application number
PCT/JP2017/007295
Other languages
English (en)
Japanese (ja)
Inventor
尚弘 岡田
直嗣 北山
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 WO2017150401A1 publication Critical patent/WO2017150401A1/fr

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Classifications

    • 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
    • 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
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F16D41/066—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical
    • F16D41/067—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical and the members being distributed by a separate cage encircling the axis of rotation
    • 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
    • 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
    • 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
    • F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
    • 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
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • 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
    • F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
    • F16D67/02—Clutch-brake combinations

Definitions

  • the present invention includes a lever-side clutch portion to which rotational torque is input by lever operation, a brake-side clutch portion that transmits rotational torque from the lever-side clutch portion to the output side, and interrupts rotational torque from the output side. It is related with the clutch unit provided with.
  • a clutch portion is disposed between an input member and an output member.
  • the clutch portion is configured to control transmission and interruption of rotational torque by engaging and disengaging an engaging member such as a cylindrical roller or a ball between the input member and the output member.
  • the present applicant has previously proposed a clutch unit incorporated in an automobile seat lifter that adjusts the seat seat up and down by lever operation (see, for example, Patent Document 1).
  • the clutch unit disclosed in Patent Document 1 transmits a rotational torque from the lever side clutch portion to which the rotational torque is input by lever operation, and the rotational torque from the lever side clutch portion to the output side, and the rotational torque from the output side.
  • a brake-side clutch portion that shuts off.
  • the lever side clutch part is engaged with the outer ring to which rotational torque is input by lever operation, the inner ring that transmits the rotational torque input from the outer ring to the brake side clutch part, and the wedge clearance between the outer ring and the inner ring.
  • a plurality of cylindrical rollers that control transmission and interruption of rotational torque from the outer ring by separation, a cage that holds the cylindrical rollers at equal intervals in the circumferential direction, and elastic torque is accumulated by rotational torque from the outer ring, and rotational torque
  • the main part is composed of two centering springs that return the cage and the outer ring to the neutral state by the accumulated elastic force.
  • the brake-side clutch section is configured to reduce the rotational torque from the output shaft by engaging and disengaging the side plate and outer ring whose rotation is restricted, the output shaft from which the rotational torque is output, and the wedge clearance between the outer ring and the output shaft.
  • a plurality of pairs of cylindrical rollers that control the interruption and transmission of rotational torque from the lever side clutch, a leaf spring that urges a separation force between each pair of cylindrical rollers, and a pair of cylindrical rollers and leaf springs
  • the main part is comprised by the holder
  • the inner ring that transmits the rotational torque from the outer ring to the brake side clutch portion, and in the brake side clutch portion, each pair of cylinders disposed between the outer ring and the output shaft.
  • the rollers and the leaf springs are integrally formed with a cage that holds the rollers at regular intervals in the circumferential direction.
  • the cage and outer ring return to the neutral state due to the elastic force of both centering springs, while the inner ring maintains the given rotational position. Therefore, the inner ring rotates in a jog by repeating the rotation of the outer ring, that is, by the pumping operation of the operation lever.
  • the cage of the brake side clutch portion further rotates, the rotational torque from the cage is transmitted to the output shaft, and the output shaft rotates.
  • the output shaft is also joggingly rotated.
  • the seat seat height can be adjusted without any discomfort for the passenger.
  • the friction ring is made of resin, and both are made of different materials and have different linear expansion coefficients. For this reason, especially during expansion due to a high temperature, the friction ring press-fit state with respect to the annular recess of the output shaft, that is, the friction ring tightening force (tightening force) is remarkably increased.
  • the resin material constituting the friction ring tends to reduce the rotational resistance imparted to the output shaft by the friction ring when the service period is extended due to the effect of creep. As a result, when the brake side clutch part is unlocked, there is a possibility that abnormal noise or fine vibration may occur in the brake side clutch part.
  • the present invention has been proposed in view of the above-described improvements, and the object of the present invention is to always stably provide an appropriate rotational resistance to the output shaft when the brake side is unlocked. To provide a clutch unit.
  • the clutch unit according to the present invention is provided on the input side, and is provided on the output side with a lever side clutch portion that controls transmission and interruption of the rotational torque input by lever operation, and the rotational torque from the lever side clutch portion.
  • a basic configuration including a brake-side clutch portion that transmits to the output side and blocks rotational torque that is reversely input from the output side is provided.
  • the brake side clutch portion of the present invention includes a stationary member whose rotation is restricted, an output member from which rotation is output, a stationary member attached to the stationary member, And a braking member that imparts rotational resistance to the output member with sliding torque generated by press-fitting, and the braking member is formed of a metal coil spring.
  • the braking member is a metal coil spring
  • the coil spring and the output member can be made of a material having substantially the same linear expansion coefficient. From this, it is possible to suppress an increase in the tightening force of the coil spring due to press-fitting into the output member due to a temperature rise.
  • the braking member in the present invention has a structure in which both ends of the coil spring are extended in the radial direction, the stationary member has a structure having protrusions protruding in the axial direction, and both ends of the coil spring are stationary. A configuration in which the projection is locked to the projection is desirable.
  • the braking member according to the present invention has a structure in which both ends of the coil spring are extended in the axial direction, the stationary member has a structure having a recess recessed in the axial direction, and both ends of the coil spring are stationary. It is desirable to have a configuration that is locked in the recess.
  • Such a configuration is effective as another means for reducing the diameter of the coil spring with the rotation of the output member and making the output member rotatable when the brake side clutch is unlocked.
  • 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 braking member is a metal coil spring
  • the coil spring and the output member can be made of a material having a substantially equivalent linear expansion coefficient. From this, it is possible to suppress an increase in the tightening force of the coil spring due to press-fitting into the output member due to a temperature rise.
  • 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. 2 is an exploded perspective view showing a side plate and a brake spring of FIG. 1. It is a fragmentary sectional view which shows the operation state (at the time of the stop of an output shaft) of a braking spring. It is a fragmentary sectional view which shows the operation state (at the time of rotation of an output shaft) of a braking spring. It is a characteristic view which shows the relationship of the operation torque with respect to the operation angle of an input shaft.
  • FIG. 6 is an exploded perspective view showing a side plate and a brake spring in another embodiment of the present invention. It is a block diagram which shows the seat seat and seat lifter part of a motor vehicle.
  • FIG. 1 is a cross-sectional view showing the overall configuration of the clutch unit of this embodiment
  • FIG. 2 is a cross-sectional view taken along line AA in FIG. 1
  • FIG. 3 is a cross-sectional view taken along line BB in FIG.
  • the clutch unit 10 of this embodiment has a structure in which a lever side clutch portion 11 provided on the input side and a brake side clutch portion 12 provided on the output side are unitized.
  • the lever side clutch part 11 controls transmission and interruption of rotational torque input by lever operation.
  • the brake-side clutch unit 12 has a reverse input blocking function for transmitting the rotational torque from the lever-side clutch unit 11 to the output side and blocking the rotational torque that is reversely input from the output side.
  • the lever side clutch unit 11 transmits to the brake side clutch unit 12 the side plate 13 and the outer ring 14 to which rotational torque is input by lever operation, and the rotational torque input from the outer ring 14.
  • a retainer 17 for holding, an inner centering spring 18 for returning the retainer 17 to a neutral state, and an outer centering spring 19 for returning the outer ring 14 to a neutral state are provided.
  • the claw part 13a formed in the outer peripheral edge part of the side plate 13 is inserted into the notch recess 14a formed in the outer peripheral edge part of the outer ring 14, and the side plate 13 is tightened by tightening. And is integrated as an input member of the lever side clutch portion 11.
  • the input of the rotational torque to the outer ring 14 is performed by an operation lever 43 (see FIG. 9) that is swingable in the vertical direction and is attached to the side plate 13 by screwing or the like.
  • the inner ring 15 includes a cylindrical portion 15a through which the output shaft 22 is inserted, a diameter-enlarged portion 15b in which a brake side end portion of the cylindrical portion 15a extends radially outward, and an outer peripheral end of the diameter-enlarged portion 15b. It consists of a plurality of pillars 15c (see FIG. 3) protruding by bending the part in the axial direction.
  • a wedge clearance 20 is formed between a cylindrical surface 15d formed on the outer periphery of the cylindrical portion 15a of the inner ring 15 and a cam surface 14b formed on the inner periphery of the outer ring 14, and the above-described cylindrical roller is formed in the wedge clearance 20.
  • 16 are arranged at equal intervals in the circumferential direction by a cage 17.
  • the inner centering spring 18 is a C-shaped elastic member having a circular cross section disposed between the retainer 17 and a cover 24 that is a stationary member of the brake side clutch portion 12. Both ends of the inner centering spring 18 are disposed on the retainer 17 and the cover 24. It is locked to a part of.
  • the inner centering spring 18 is elastically expanded by the rotation of the cage 17 following the outer ring 14 with respect to the cover 24 in a stationary state when the rotational torque input from the outer ring 14 is applied by lever operation. When the rotational torque input from the outer ring 14 is released, the cage 17 is returned to the neutral state by the elastic force.
  • the outer centering spring 19 positioned on the radially outer side of the inner centering spring 18 is a C-shaped strip elastic member disposed between the outer ring 14 and the above-described cover 24, and both ends thereof are arranged on the outer ring 14 and the cover 24. It is locked to a part of.
  • the outer centering spring 19 is expanded with the rotation of the outer ring 14 with respect to the cover 24 in a stationary state when the rotational torque input from the outer ring 14 by the lever operation is applied, and an elastic force is accumulated. When the rotational torque input from is released, the outer ring 14 is returned to the neutral state by the elastic force.
  • the cage 17 is a resin-made cylindrical member in which a plurality of pockets 17a for accommodating the cylindrical rollers 16 are formed at equal intervals in the circumferential direction. Note that both end portions of the inner centering spring 18 are locked to one axial end portion of the cage 17, that is, the axial end portion on the cover 24 side of the brake side clutch portion 12.
  • the cage 17 is disposed between the outer ring 14 and the inner ring 15 in the radial direction, and is sandwiched between the outer ring 14 and the cover 24 of the brake side clutch portion 12 in the axial direction.
  • the brake-side clutch portion 12 having a reverse input blocking function which is called a lock type, has a pillar portion 15 c of the inner ring 15 to which the rotational torque from the lever-side clutch portion 11 is input.
  • An output shaft 22 as an output member from which the rotational torque from the lever side clutch portion 11 is output, an outer ring 23, a cover 24 and a side plate 25 as stationary members whose rotation is restricted, an outer ring 23 and an output shaft 22.
  • a plurality of pairs of cylindrical rollers 27 for controlling the interruption of the rotational torque reversely input from the output shaft 22 and the transmission of the rotational torque input from the column portion 15c of the inner ring 15 by engagement and disengagement between
  • the main part de ne and referred to) and is configured.
  • the output shaft 22 is integrally formed with a large-diameter portion 22b that extends radially outward and expands in the axial central portion of the shaft portion 22a into which the cylindrical portion 15a of the inner ring 15 is extrapolated.
  • a pinion gear 22d for connecting to the seat lifter portion is coaxially formed at the output side end portion of the shaft portion 22a.
  • the washer 31 is press-fitted into the input side end portion of the shaft portion 22a via the wave washer 30 to prevent the component parts of the lever side clutch portion 11 from coming off.
  • a plurality of (for example, six) flat cam surfaces 22e are formed on the outer periphery of the large-diameter portion 22b of the output shaft 22 at equal intervals in the circumferential direction.
  • One leaf spring interposed between the two cylindrical rollers 27 and the cylindrical rollers 27 in a wedge clearance 26 provided between the cam surface 22e of the large diameter portion 22b and the cylindrical inner peripheral surface 23a of the outer ring 23. 28 are arranged.
  • the cylindrical roller 27 and the leaf spring 28 are arranged at equal intervals in the circumferential direction by the pillar portion 15 c of the inner ring 15.
  • the column portion 15c of the inner ring 15 transmits a rotational torque input from the outer ring 14 of the lever side clutch portion 11 to the output shaft 22, thereby functioning as an input member of the brake side clutch portion 12, and the cylindrical roller 27 and the leaf spring. 28 is accommodated in the pocket 15f and held at equal intervals in the circumferential direction to function as a cage.
  • the column portion 15c of the inner ring 15 is referred to as a cage 15c.
  • the large-diameter portion 22b of the output shaft 22 is provided with a protrusion 22f for transmitting the rotational torque from the inner ring 15 to the output shaft 22.
  • the protrusion 22f is inserted and disposed in a hole 15e formed in the enlarged diameter portion 15b of the inner ring 15 with a circumferential clearance.
  • the outer ring 23, the cover 24, and the side plate 25 are divided into a notch recess 23 b formed in the outer peripheral edge of the thick plate-like outer ring 23 and a notch recess 24 a formed in the outer peripheral edge of the cover 24.
  • the side plate 25 is fixed to the outer ring 23 and the cover 24 and is integrated as a stationary member of the brake side clutch portion 12 by inserting and crimping the claw portion 25a formed on the outer peripheral edge of the brake.
  • the cage 17 and the outer ring 14 are returned to the neutral state by the elastic force of the centering springs 18 and 19.
  • the inner ring 15 maintains the given rotational position as it is. Therefore, the inner ring 15 rotates in a jog by repeating the rotation of the outer ring 14, that is, by the pumping operation of the operation lever 43 (see FIG. 9).
  • the cylindrical roller 27 engages with the wedge clearance 26 between the output shaft 22 and the outer ring 23 even when rotational torque is reversely input to the output shaft 22 due to seating on the seat. 22 is locked to the outer ring 23. In this way, the rotational torque reversely input from the output shaft 22 is locked by the brake side clutch portion 12 and the return of the rotational torque reversely input to the lever side clutch portion 11 is blocked. Thereby, the seat seat cannot be adjusted up and down.
  • the overall configuration of the clutch unit 10 in this embodiment is as described above, and the brake spring 29 that is a characteristic configuration thereof will be described in detail below.
  • the brake spring 29 is attached to the side plate 25 as an alternative to the resin friction ring (see Patent Document 1) in the conventional clutch unit, and is connected to the output shaft 22.
  • This is a metal coil spring that imparts rotational resistance to the output shaft 22 with a sliding torque generated by the press-fitting of.
  • both ends 29a and 29b of the brake spring 29 are extended radially inward, and a pair of protrusions 25b and 25c protruding inward in the axial direction are formed on a part of the side plate 25 by cutting and raising.
  • the braking spring 29 is elastically deformed by expanding both the extending end portions 29a and 29b in the circumferential direction by arranging one extending end portion 29a and the other extending end portion 29b in an overlapping manner in the circumferential direction. The diameter is reduced.
  • the brake spring 29 is attached to the side plate 25 by disposing and locking the both extended end portions 29a and 29b on the outer side in the circumferential direction of the protrusions 25b and 25c of the side plate 25, and is attached to the large diameter portion 22b of the output shaft 22.
  • the inner circumferential surface 22g of the formed annular recess 22c is press-fitted with a tightening margin (tight force).
  • a rotational resistance (sliding torque) is applied to the output shaft 22 when the lever is operated by the frictional force generated between the outer peripheral portion 29c of the brake spring 29 and the inner peripheral surface 22g of the annular recess 22c of the output shaft 22.
  • both ends 29a and 29b of the brake spring 29 are slightly expanded in the circumferential direction, whereby the brake spring 29 is reduced in diameter by elastic deformation. Due to the reduced diameter of the brake spring 29, a minute gap is formed between the outer peripheral portion 29c of the brake spring 29 and the inner peripheral surface 22g of the annular recess 22c of the output shaft 22, and the output shaft 22 becomes rotatable. Thereafter, while the brake spring 29 remains in the reduced diameter state shown in FIG. 6, the output shaft 22 rotates while the inner peripheral surface 22 g of the annular recess 22 c of the output shaft 22 slides with respect to the outer peripheral portion 29 c of the brake spring 29.
  • a metal coil is used as a braking member that imparts rotational resistance to the output shaft 22 when the output shaft 22 is unlocked.
  • the brake spring 29 which is a spring
  • the brake spring 29 and the output shaft 22 can be made of a material having substantially the same linear expansion coefficient. From this, it is possible to suppress an increase in the pressing force of the braking spring 29 due to press-fitting into the output shaft 22 due to a temperature rise.
  • the braking spring 29 (product of the present invention) employed in this embodiment has a frictional force during rotation of the output shaft 22 as compared with a conventional friction ring (conventional product) due to a reduction in the coil diameter during rotation transmission. Becomes smaller. Therefore, as shown in FIG. 7, it is possible to reduce the operating torque when the output shaft 22 rotates while securing the rotational resistance (sliding torque) applied when the output shaft 22 does not rotate.
  • both end portions 29a and 29b of the brake spring 29 are extended in the radial direction, and the side plates 25 are formed with protrusions 25b and 25c protruding in the axial direction.
  • the present invention is not limited to this, and the structure shown in FIG.
  • both ends 29d and 29e of the brake spring 29 are extended in the axial direction, and a pair of through holes 25d and 25e are formed as concave portions recessed in the axial direction in a part of the side plate 25. It has.
  • the brake spring 29 is configured such that one extending end portion 29d and the other extending end portion 29e overlap with each other in the circumferential direction so that both the extending end portions 29d and 29e are arranged in the circumferential direction.
  • the diameter is reduced by elastic deformation.
  • the brake spring 29 of this embodiment is attached to the side plate 25 by inserting both extended end portions 29d and 29e into the through holes 25d and 25e of the side plate 25 and locking them at the inner end portion.
  • the inner circumferential surface 22g of the annular recess 22c is press-fitted with a tightening margin (tight force).
  • a rotational resistance (sliding torque) is applied to the output shaft 22 during lever operation by the frictional force generated between the outer peripheral portion 29c of the brake spring 29 and the inner peripheral surface 22g of the annular recess 22c of the output shaft 22.
  • the through holes 25d and 25e of the side plate 25 through which both the extended ends 29d and 29e of the brake spring 29 are inserted are the extended ends 29d and 29e of the brake spring 29 when the output shaft 22 is unlocked by lever operation. Is formed in a long hole extending in the circumferential direction so that it can move in the rotation direction.
  • the clutch unit 10 of this embodiment is used by being incorporated in an automobile seat lifter 41 that adjusts the height of a seat by lever operation.
  • FIG. 9 shows a seat 40 installed in the passenger compartment of the automobile.
  • the seat 40 is composed of a seating seat 48 and a backrest seat 42, and the seat lifter 41 adjusts the height of the seating surface of the seating seat 48.
  • the height of the seating seat 48 is adjusted by the operation lever 43 attached to the side plate 13 (see FIG. 1) of the lever side clutch portion 11 in the clutch unit 10.
  • the sheet lifter 41 has the following structure. One end of each of the link members 45 and 46 is pivotally attached to the slide movable member 44. The other ends of the link members 45 and 46 are pivotally attached to the seating seat 48, respectively. A sector gear 47 is integrally provided at the other end of the link member 45. The sector gear 47 meshes with the pinion gear 22 d of the output shaft 22 of the clutch unit 10.
  • the lever side clutch portion 11 is operated, that is, the operation lever 43 is swung downward to lock the brake side clutch portion 12 (see FIG. 1). Release the state.
  • the brake side clutch part 12 is unlocked, the seating surface of the seating seat 48 can be smoothly lowered by applying an appropriate rotational resistance to the output shaft 22 by the braking spring 29 (see FIG. 1).
  • the pinion gear 22d of the output shaft 22 of the brake side clutch portion 12 is rotated clockwise (in FIG. 9) with the rotational torque transmitted from the lever side clutch portion 11 to the brake side clutch portion 12. It rotates in the direction of the arrow. Then, the sector gear 47 meshing with the pinion gear 22d swings counterclockwise (in the direction of the arrow in FIG. 9), and both the link member 45 and the link member 46 are tilted to lower the seating surface of the seating seat 48.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

L'unité d'embrayage de l'invention est constituée : d'une partie embrayage côté levier (11) qui est agencée côté entrée, et qui commande la transmission et le blocage d'un couple de rotation entré par une manipulation de levier; et d'une partie embrayage côté frein (12) qui est agencée côté sortie, et qui transmet côté sortie le couple de rotation provenant de la partie embrayage côté levier (11), et bloque le couple de rotation entrée en sens inverse par le côté sortie. La partie embrayage côté frein (12) met en œuvre : une plaque latérale (25) qui restreint la rotation; un axe de sortie (22) par lequel la rotation sort; et un ressort hélicoïdal (29) en métal qui est installé sur la plaque latérale (25), et qui sert d'élément de freinage conférant une résistance de rotation à l'axe de sortie (22) au moyen d'un couple de glissement généré par son insertion de force dans l'axe de sortie (22).
PCT/JP2017/007295 2016-03-01 2017-02-27 Unité d'embrayage WO2017150401A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016038974A JP2017155815A (ja) 2016-03-01 2016-03-01 クラッチユニット
JP2016-038974 2016-03-01

Publications (1)

Publication Number Publication Date
WO2017150401A1 true WO2017150401A1 (fr) 2017-09-08

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Application Number Title Priority Date Filing Date
PCT/JP2017/007295 WO2017150401A1 (fr) 2016-03-01 2017-02-27 Unité d'embrayage

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JP (1) JP2017155815A (fr)
WO (1) WO2017150401A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6474871B1 (ja) * 2017-09-20 2019-02-27 Ntn株式会社 クラッチユニット

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002240601A (ja) * 2001-10-09 2002-08-28 Ntn Corp 座席シート
JP2005315299A (ja) * 2004-04-27 2005-11-10 Ntn Corp クラッチユニット
JP2005344822A (ja) * 2004-06-02 2005-12-15 Ntn Corp クラッチユニット
JP2010276155A (ja) * 2009-05-29 2010-12-09 Ntn Corp 逆入力遮断ユニットおよびそれを用いた紙送り装置
JP2015190573A (ja) * 2014-03-28 2015-11-02 Ntn株式会社 クラッチユニット

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002240601A (ja) * 2001-10-09 2002-08-28 Ntn Corp 座席シート
JP2005315299A (ja) * 2004-04-27 2005-11-10 Ntn Corp クラッチユニット
JP2005344822A (ja) * 2004-06-02 2005-12-15 Ntn Corp クラッチユニット
JP2010276155A (ja) * 2009-05-29 2010-12-09 Ntn Corp 逆入力遮断ユニットおよびそれを用いた紙送り装置
JP2015190573A (ja) * 2014-03-28 2015-11-02 Ntn株式会社 クラッチユニット

Cited By (3)

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JP6474871B1 (ja) * 2017-09-20 2019-02-27 Ntn株式会社 クラッチユニット
WO2019059141A1 (fr) * 2017-09-20 2019-03-28 Ntn株式会社 Unité d'embrayage
JP2019056397A (ja) * 2017-09-20 2019-04-11 Ntn株式会社 クラッチユニット

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