WO2020255973A1 - Unité d'embrayage - Google Patents

Unité d'embrayage Download PDF

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Publication number
WO2020255973A1
WO2020255973A1 PCT/JP2020/023632 JP2020023632W WO2020255973A1 WO 2020255973 A1 WO2020255973 A1 WO 2020255973A1 JP 2020023632 W JP2020023632 W JP 2020023632W WO 2020255973 A1 WO2020255973 A1 WO 2020255973A1
Authority
WO
WIPO (PCT)
Prior art keywords
output shaft
rotational torque
side clutch
clutch
input
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2020/023632
Other languages
English (en)
Japanese (ja)
Inventor
恭兵 笹沼
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
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 Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2020255973A1 publication Critical patent/WO2020255973A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C7/00—Parts, details, or accessories of chairs or stools
    • A47C7/02—Seat parts
    • 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
    • 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
    • F16D15/00—Clutches with wedging balls or rollers or with other wedgeable separate clutching members
    • 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

Definitions

  • the present invention is a clutch unit including an input side clutch part to which a rotation torque is input and an output side clutch part which transmits the rotation torque from the input side clutch part to the output side and cuts off the rotation torque from the output side. Regarding.
  • a clutch portion is arranged between an input member and an output member.
  • the clutch portion is configured to control transmission and disconnection of rotational torque by engaging and disengaging the engaging element between the input member and the output member.
  • the clutch unit disclosed in Patent Document 1 transmits the rotational torque from the lever-side clutch portion to which the rotational torque is input by lever operation and the lever-side clutch portion to the output side, and shuts off the rotational torque from the output side. It is equipped with a clutch on the brake side.
  • the main part of the lever side clutch part is the outer ring to which the rotational torque is input by lever operation, the inner ring that transmits the rotational torque from the outer ring to the brake side clutch part, and the engagement and disengagement between the outer ring and the inner ring to the wedge gap. It is composed of a cylindrical roller that controls the transmission and interruption of rotational torque from the outer ring.
  • the main parts of the brake side clutch part are the inner ring to which the rotation torque from the lever side clutch part is input, the output shaft to which the rotation torque from the inner ring is output, the side plate and outer ring whose rotation is restricted, and the output shaft. It consists of a cylindrical roller that controls the interruption of rotational torque from the output shaft and the transmission of rotational torque from the inner ring by engaging and disengaging the outer ring to the wedge gap, and a friction ring that imparts rotational resistance to the output shaft. ing.
  • the seat height of the seat can be adjusted by rotating the output shaft.
  • the wedge clearance between the output shaft and the outer ring is composed of a cam surface formed on the large diameter portion of the output shaft (see FIG. 5 of Patent Document 1). Further, the large diameter portion of the output shaft has an annular recess into which the friction ring is press-fitted (see FIG. 1 of Patent Document 1).
  • an object of the present invention is a clutch unit capable of stabilizing the locked state of the output shaft and suppressing deterioration of braking performance at the brake side clutch portion. Is to provide.
  • the clutch unit according to the present invention has an input side clutch unit that controls transmission and disconnection of input rotational torque, and a rotational torque that transmits rotational torque from the input side clutch unit to the output side and is reversely input from the output side. It is provided with an output side clutch portion that shuts off.
  • the output-side clutch portion in the present invention includes an output shaft having a large-diameter portion in which an annular recess is formed, and a side plate arranged outside the large-diameter portion of the output shaft in the axial direction.
  • the present invention provides a guide portion on the side plate for guiding the inner peripheral surface of the annular recess of the large diameter portion so that the guide portion is in contact with the inner peripheral surface of the annular recess. It is characterized by being arranged.
  • the inner peripheral surface of the annular recess is guided by a guide portion arranged so as to be in contact with the inner peripheral surface of the annular recess of the large diameter portion.
  • the guide portion in the present invention is a recess formed on the inner side surface in the axial direction of the side plate, and a structure in which the axial end portion of the large diameter portion is fitted into the recess is desirable.
  • the guide portion in the present invention is a convex portion formed on the inner side surface in the axial direction of the side plate, and a structure in which the convex portion is fitted into the annular concave portion of the large diameter portion is desirable.
  • the input side clutch portion and the output side clutch portion in the present invention have a structure incorporated in the automobile seat lifter portion.
  • the guide portion arranged so as to be in contact with the inner peripheral surface of the annular recess of the large diameter portion guides the inner peripheral surface of the annular recess, so that when the output shaft is locked, the output shaft rotates greatly. Even if torque is applied, elastic deformation due to an excessive load on the large diameter portion can be suppressed.
  • FIG. 1 is a cross-sectional view showing the overall configuration of the clutch unit
  • FIG. 2 is a cross-sectional view taken along the line PP of FIG. 1
  • FIG. 3 is a cross-sectional view taken along the line QQ of FIG.
  • the clutch unit 10 of this embodiment has a structure in which a lever-side clutch portion 11 as an input-side clutch portion and a brake-side clutch portion 12 as an output-side clutch portion are unitized.
  • the lever-side clutch portion 11 controls transmission and disconnection of rotational torque input by lever operation.
  • the brake side clutch portion 12 transmits the rotational torque from the lever side clutch portion 11 to the output side, and shuts off the rotational torque that is reversely input from the output side.
  • the main part of the lever-side clutch portion 11 includes a side plate 13, an outer ring 14, an inner ring 15, a plurality of cylindrical rollers 16, a cage 17, an inner centering spring 18, and an inner centering spring 18. It is composed of an outer centering spring 19.
  • a claw portion 13a extending in the axial direction is formed on the outer periphery of the side plate 13, and a notch recess 14a is formed on the outer periphery of the outer ring 14.
  • the side plate 13 and the outer ring 14 are integrated by fitting the claw portion 13a into the notch recess 14a and crimping it.
  • the rotational torque is input to the outer ring 14 by the operating lever 43 (see FIG. 4) attached to the side plate 13.
  • the inner ring 15 has a tubular portion 15a through which the output shaft 22 is inserted, a diameter-expanded portion 15b in which the brake side end portion of the tubular portion 15a extends radially outward, and the outer circumference of the diameter-expanded portion 15b in the axial direction. It is composed of a plurality of pillar portions 15c (see FIG. 3) extending to the above.
  • the inner ring 15 transmits the rotational torque input from the outer ring 14 to the brake side clutch portion 12.
  • a plurality of cam surfaces 14b are formed on the inner circumference of the outer ring 14 at equal intervals in the circumferential direction.
  • a wedge clearance 20 is formed between the cam surface 14b of the outer ring 14 and the cylindrical surface 15d of the tubular portion 15a of the inner ring 15.
  • the cylindrical roller 16 is arranged between the outer ring 14 and the inner ring 15.
  • the cylindrical roller 16 controls transmission and disconnection of rotational torque from the outer ring 14 by engaging and disengaging at a wedge clearance 20 formed between the cam surface 14b of the outer ring 14 and the cylindrical surface 15d of the inner ring 15.
  • pockets 17a for accommodating the cylindrical rollers 16 are formed at a plurality of locations in the circumferential direction at equal intervals.
  • the cage 17 holds the cylindrical roller 16 by the pocket 17a in the wedge gap 20 between the cam surface 14b of the outer ring 14 and the cylindrical surface 15d of the inner ring 15.
  • the inner centering spring 18 is a C-shaped elastic member having a circular cross section arranged between the cage 17 and the cover 24 of the brake side clutch portion 12, and both ends thereof are part of the cage 17 and the cover 24. It is locked.
  • the outer centering spring 19 located on the radial outer side of the inner centering spring 18 is a C-shaped strip elastic member arranged between the outer ring 14 and the cover 24 of the brake side clutch portion 12, and both ends thereof are formed. It is locked to a part of the outer ring 14 and the cover 24.
  • the main portion of the brake side clutch portion 12 includes a pillar portion 15c of the inner ring 15 extending from the lever side clutch portion 11, an output shaft 22, an outer ring 23 as a stationary system, a cover 24, and the cover 24. It is composed of a side plate 25, a plurality of pairs of cylindrical rollers 27, a leaf spring 28 having an N-shaped cross section, and a friction ring 29.
  • the output shaft 22 includes a shaft portion 22a to which the tubular portion 15a of the inner ring 15 is extrapolated, a cup-shaped large diameter portion 22b extending radially outward from a substantially central portion of the shaft portion 22a, and an output side of the shaft portion 22a. It is composed of a pinion gear portion 22d formed coaxially with the above. The rotation torque from the lever-side clutch portion 11 is output to the output shaft 22.
  • a plurality of (six in FIG. 3) flat cam surfaces 22e are formed on the outer periphery of the large diameter portion 22b at equal intervals in the circumferential direction.
  • a wedge clearance 26 is formed between the cam surface 22e of the large diameter portion 22b and the cylindrical surface 23a of the outer ring 23.
  • Two cylindrical rollers 27 and one leaf spring 28 inserted between them are arranged in the wedge clearance 26.
  • the cylindrical roller 27 controls the interruption of the rotational torque input back from the output shaft 22 and the transmission of the rotational torque input from the pillar portion 15c of the inner ring 15 by engaging and disengaging at the wedge clearance 26.
  • the leaf spring 28 urges the cylindrical rollers 27 to separate from each other in the circumferential direction.
  • a plurality of pairs (6 pairs in FIG. 3) of cylindrical rollers 27 and leaf springs 28 are arranged at equal intervals in the circumferential direction by the pillar portions 15c of the inner ring 15.
  • the pillar portion 15c has a function of transmitting the rotational torque input from the outer ring 14 to the output shaft 22 and a function of accommodating the cylindrical roller 27 and the leaf spring 28 in the pocket 15f and holding them at equal intervals in the circumferential direction.
  • the large diameter portion 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 arranged in the hole 15e formed in the enlarged diameter portion 15b of the inner ring 15 with a clearance in the circumferential direction.
  • the pinion gear portion 22d of the output shaft 22 is connected to the seat lifter portion 39 (see FIG. 4).
  • the washer 31 By press-fitting the washer 31 to the input side of the shaft portion 22a via the wave washer 30, the component parts of the lever-side clutch portion 11 are prevented from coming off.
  • Notch recesses 23b and 24a are formed on the outer periphery of the outer ring 23 and the cover 24, and a claw portion 25a extending in the axial direction is formed on the outer periphery of the side plate 25.
  • the outer ring 23, the cover 24, and the side plate 25 are integrated by fitting the claw portion 25a into the notch recesses 23b and 24a and crimping them.
  • the friction ring 29 is, for example, a resin member and is fixed to the side plate 25.
  • the friction ring 29 is press-fitted into the inner peripheral surface 22g of the annular recess 22c formed in the large diameter portion 22b of the output shaft 22 with a fitting allowance.
  • the output shaft 22 slides on the friction ring 29 fixed to the side plate 25 in a stationary state when the lever is operated by the frictional force generated between the outer peripheral surface 29a of the friction ring 29 and the inner peripheral surface 22g of the annular recess 22c. Is given rotational resistance.
  • the cylindrical roller 27 engages with the wedge clearance 26 between the output shaft 22 and the outer ring 23 even if the rotational torque is reversely input to the output shaft 22 due to seating on the seat 40 (see FIG. 4). The output shaft 22 is then locked to the outer ring 23.
  • the cylindrical roller 27 is separated from the wedge clearance 26.
  • the locked state of the output shaft 22 is released and the output shaft 22 can rotate.
  • the friction ring 29 imparts rotational resistance to the output shaft 22.
  • the rotational torque from the lever-side clutch portion 11 is transmitted to the output shaft 22 via the protrusion 22f, and the output shaft 22 rotates. That is, when the inner ring 15 oscillates, the output shaft 22 also oscillates. As a result, the seat height of the seat 40 can be adjusted.
  • FIG. 4 shows a seat 40 installed in the passenger compartment of an automobile.
  • the seat height of the seat 40 in the seat lifter portion 39 is adjusted by the operation lever 43 attached to the side plate 13 (see FIG. 1) of the lever side clutch portion 11.
  • the seat lifter portion 39 has the following structure.
  • link members 45 and 46 are rotatably pivotally attached to the slide movable member 44.
  • the other ends of the link members 45 and 46 are rotatably pivotally attached to the seat 40.
  • 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 portion 22d of the output shaft 22.
  • the seat surface of the seat 40 can be smoothly lowered by applying an appropriate rotational resistance to the output shaft 22 by the friction ring 29 (see FIG. 1).
  • the overall configuration of the clutch unit 10 in this embodiment is as described above, but the large diameter portion 22b and the side plate 25 of the output shaft 22 in the brake side clutch portion 12, which are characteristic configurations thereof, will be described in detail below. ..
  • a guide portion (recessed portion 25b in FIG. 1, convex portion 25d in FIG. 5) for guiding the inner peripheral surface 22g of the annular concave portion 22c of the large diameter portion 22b having a cup shape is provided on the side plate 25.
  • the guide portion is provided so as to be in contact with the inner peripheral surface 22g of the annular recess 22c.
  • the guide portion in the embodiment of FIG. 1 is a recess 25b formed on the inner side surface in the axial direction of the side plate 25.
  • the recess 25b is formed in an annular shape so as to face the axial end 22h of the large diameter portion 22b.
  • the axial end 22h of the large diameter portion 22b is fitted into the recess 25b of the side plate 25.
  • the inner peripheral surface 22g of the annular recess 22c is guided by the recess 25b arranged so as to be in contact with the inner peripheral surface 22g of the annular recess 22c. That is, the stepped surface 25c of the recess 25b is brought into contact with the inner peripheral surface 22g of the annular recess 22c.
  • the guide portion in the embodiment of FIG. 5 is a convex portion 25d formed on the inner side surface in the axial direction of the side plate 25.
  • the convex portion 25d is formed in a tubular shape so as to correspond to the axial end portion 22h of the large diameter portion 22b.
  • the convex portion 25d of the side plate 25 is fitted into the annular concave portion 22c of the large diameter portion 22b.
  • the convex portion 25d arranged so as to be in contact with the inner peripheral surface 22g of the annular recess 22c guides the inner peripheral surface 22g of the annular recess 22c. That is, the outer peripheral surface 25e of the convex portion 25d is brought into contact with the inner peripheral surface 22g of the annular recess 22c.
  • the friction ring 29 is fixed to the convex portion 25d of the side plate 25 and slidable with the shaft portion 22a of the output shaft 22 or fixed to the shaft portion 22a of the output shaft 22.
  • the structure may be slidable with the convex portion 25d of the side plate 25.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Transportation (AREA)
  • Seats For Vehicles (AREA)
  • Braking Arrangements (AREA)

Abstract

La présente invention comprend une partie d'embrayage côté levier (11) qui commande la transmission et l'interception d'un couple de rotation introduit, et une partie d'embrayage côté frein (12) qui transmet le couple de rotation de la partie d'embrayage côté levier (11) au côté de sortie et intercepte le couple de rotation introduit inversement depuis le côté de sortie. La partie d'embrayage côté frein (12) comprend un arbre de sortie (22) ayant une partie de grand diamètre (22b) dans laquelle est formé un évidement annulaire (22c), et une plaque latérale (25) disposée sur le côté externe de direction axiale de la partie de grand diamètre (22b). Un évidement (25b) qui guide la surface périphérique interne (22g) de l'évidement annulaire (22c) est formé dans la surface côté interne de direction axiale de la plaque latérale (25). La partie d'extrémité de direction axiale (22h) de la partie de grand diamètre (22b) est ajustée dans l'évidement (25b), l'évidement (25b) étant disposé de manière à être en contact avec la surface périphérique interne (22g) de l'évidement annulaire (22c).
PCT/JP2020/023632 2019-06-21 2020-06-16 Unité d'embrayage Ceased WO2020255973A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019115451A JP2021001654A (ja) 2019-06-21 2019-06-21 クラッチユニット
JP2019-115451 2019-06-21

Publications (1)

Publication Number Publication Date
WO2020255973A1 true WO2020255973A1 (fr) 2020-12-24

Family

ID=73993945

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2020/023632 Ceased WO2020255973A1 (fr) 2019-06-21 2020-06-16 Unité d'embrayage

Country Status (2)

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JP (1) JP2021001654A (fr)
WO (1) WO2020255973A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002054658A (ja) * 2000-08-08 2002-02-20 Ntn Corp クラッチユニット
JP2010025204A (ja) * 2008-07-17 2010-02-04 Ntn Corp クラッチユニット
JP2018004008A (ja) * 2016-07-06 2018-01-11 Ntn株式会社 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
JP2002054658A (ja) * 2000-08-08 2002-02-20 Ntn Corp クラッチユニット
JP2010025204A (ja) * 2008-07-17 2010-02-04 Ntn Corp クラッチユニット
JP2018004008A (ja) * 2016-07-06 2018-01-11 Ntn株式会社 クラッチユニット

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