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WO2021026720A1 - Système de libération d'embrayage - Google Patents

Système de libération d'embrayage Download PDF

Info

Publication number
WO2021026720A1
WO2021026720A1 PCT/CN2019/100187 CN2019100187W WO2021026720A1 WO 2021026720 A1 WO2021026720 A1 WO 2021026720A1 CN 2019100187 W CN2019100187 W CN 2019100187W WO 2021026720 A1 WO2021026720 A1 WO 2021026720A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
spring
release system
clutch release
retaining ring
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/CN2019/100187
Other languages
English (en)
Chinese (zh)
Inventor
康嘉瑞
安德森·索雷斯·拉波索
张波
郑飞翔
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to PCT/CN2019/100187 priority Critical patent/WO2021026720A1/fr
Priority to CN201980097576.5A priority patent/CN113994115A/zh
Publication of WO2021026720A1 publication Critical patent/WO2021026720A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types

Definitions

  • the present invention relates to the field of clutches, and more specifically to clutch release systems.
  • the centered auxiliary cylinder includes a housing, a piston, a spring retaining ring, and a coil spring.
  • the piston is located inside the housing and abuts against the inner ring of the release bearing. Under the action of the high pressure medium, the piston can push the inner ring of the release bearing axially to push the entire release bearing, so that the outer ring of the release bearing and the clutch
  • the diaphragm spring abuts.
  • the spring retaining ring is fixedly installed on the inner ring, and the axial ends of the coil spring are pressed against the spring retaining ring and the housing respectively, so as to apply a predetermined axial preloading force to the release bearing.
  • the piston pushes the inner ring of the release bearing in the axial direction under the action of the high pressure medium, the torque from the clutch is transmitted from the outer ring of the release bearing to the ball and inner ring of the release bearing, and then the torque is transferred from the release bearing's inner ring.
  • the inner ring is transferred to the spring retaining ring. Since the coil spring as an axial preload spring generally does not have sufficient torsion resistance to withstand the torque, the coil diameter of the coil spring becomes larger.
  • the spring retaining ring mainly provides radial force to limit the coil spring, but when the coil spring is deformed to a certain extent, it may fall out of its installation position, causing the clutch release system to malfunction.
  • the purpose of the present invention is to overcome or at least alleviate the above-mentioned shortcomings of the prior art, and provide a new type of clutch release system, which can prevent the axial preload spring from being deformed due to the torque from the clutch and then escaping from its installation position.
  • the present invention provides a clutch release system including a release bearing and a centering auxiliary cylinder assembled with each other, the centering auxiliary cylinder including a housing and a piston located inside the housing , The piston abuts against the inner ring of the release bearing in the axial direction to be able to push the release bearing in the axial direction,
  • the clutch release system further includes a spring retaining ring and a pre-loaded spring, the spring retaining ring is fixedly installed on the inner ring, and an axial side end of the pre-loaded spring abuts against the spring retaining ring to press Abutting against the inner ring and the other axial end of the preload spring abuts against the housing, and the axial one end of the preload spring is at least in both axial and radial directions The upper part is restricted by the spring retaining ring.
  • the preload spring is a coil spring.
  • the spring retaining ring includes a first annular portion extending in the axial direction as a whole and a hook portion extending radially inward with respect to the first annular portion, and one turn of the coil spring is at least Partly located at the radial inner side of the first annular portion and the turn is restricted by the hook portion.
  • the spring retaining ring further includes a stopper portion protruding toward the radially inner side relative to the first annular portion, and the stopper portion is used to stop the circumferential end of the turn for the The turns are limited in the circumferential direction.
  • the hook portion and the stop portion are opposed to each other via the central axis of the first annular portion.
  • a part of the turns of the coil spring is sleeved on the casing from the radially outer side.
  • the spring retaining ring further includes a second annular portion extending entirely in the axial direction and an annular connecting portion extending entirely in the radial direction.
  • the diameter of the second annular portion is smaller than that of the first annular portion.
  • the diameter of a ring portion and the second ring portion are fixedly mounted on the inner ring, the connecting portion connects the first ring portion and the second ring portion to each other, the spiral One end of the spring in the axial direction is pressed against the connecting portion, thereby applying pressure to the inner ring.
  • the second annular portion is fixedly installed on the radially inner side of the inner ring through interference fit.
  • the second annular portion is formed with a plurality of mounting protrusions protruding toward the radially outer side, the plurality of mounting protrusions are evenly distributed along the circumferential direction, and the plurality of mounting protrusions and the The inner ring realizes the interference fit.
  • the connecting portion and the hook portion of the spring retaining ring are arranged to sandwich a turn of the coil spring located radially inward of the first annular portion of the spring retaining ring in the axial direction. At least a part of, so that the connecting portion and the spring retaining ring limit the turn in the axial direction.
  • the present invention provides a new type of clutch release system, which can use the spring retaining ring to perform the axial end of the preloaded spring at least in the axial and radial directions. Limit, so that even if the pre-loaded spring is deformed to a certain extent under the action of the torque from the clutch, it will not come out of the spring retaining ring and will not come out of its installation position.
  • Fig. 1 is a schematic partial cross-sectional view of the clutch release system according to the present invention taken along the central axis.
  • FIG. 2 shows a three-dimensional schematic diagram of the spring retaining ring in the clutch release system in FIG. 1.
  • axial refers to the axial direction of the clutch release system (spring retaining ring)
  • one side in the axial direction refers to the upper side in FIG. 1
  • the other side in the axial direction Refers to the lower side in Figure 1
  • radial refers to the radial direction of the clutch release system (spring retaining ring)
  • circumferential refers to the circumferential direction of the clutch release system (spring retaining ring).
  • Fig. 1 is a schematic partial cross-sectional view of the clutch release system according to the present invention taken along the central axis.
  • the clutch release system includes a release bearing 1 and a centering auxiliary cylinder 2 assembled with each other.
  • the release bearing 1 has an annular shape as a whole.
  • the release bearing 1 includes an outer ring 11, an inner ring 12, and a plurality of balls 13 installed between the outer ring 11 and the inner ring 12.
  • the outer ring 11 includes an outer ring axial portion 112 extending substantially along the axial direction A and an outer ring radial portion 111 extending from an axial side end of the outer ring axial portion 112 toward the radially inner side.
  • the inner ring 12 is located on the radially inner side of the outer ring 11, and the inner ring 12 includes an inner ring axial portion 122 extending substantially along the axial direction A and extending from an axial side end of the inner ring axial portion 122 toward the radial inner side The inner ring radial portion 121.
  • the inner ring axial portion 122 and the outer ring axial portion 112 substantially overlap in the radial direction R, and a plurality of balls 13 are installed between the inner ring axial portion 122 and the outer ring axial portion 112.
  • the inner ring radial portion 121 and the outer ring radial portion 111 partially overlap in the axial direction A, and the inner ring radial portion 121 and the outer ring radial portion 111 are spaced apart from each other in the axial direction A by a predetermined gap.
  • the plurality of balls 13 are evenly distributed in the circumferential direction and held in a predetermined position by a cage.
  • the release bearing 1 further includes a seal for sealing the gap between the outer ring 11 and the inner ring 12.
  • the centering type sub-cylinder 2 includes a housing 21, a piston 22, a spring retaining ring 23 and a coil spring 24 assembled with each other.
  • the housing 21 has a substantially cylindrical shape, and the outer peripheral wall of the housing 21 is formed with a shoulder 21s against which the coil spring 24 abuts.
  • the piston 22 is mounted on the radially inner side of the housing 21 and can move along the axial direction A.
  • the end on the axial side of the piston 22 abuts against the inner ring radial portion 121 of the inner ring 12 of the release bearing 1.
  • the piston 22 can push the inner ring radial portion 121 of the inner ring 12, thereby pushing the entire release bearing 1 toward the axial side.
  • the movement allows the outer ring radial portion 111 of the outer ring 11 of the release bearing 1 to be pressed against the diaphragm spring (not shown) of the clutch.
  • the spring retaining ring 23 is fixedly mounted on the inner ring axial portion 122 of the inner ring 12 of the release bearing 1. As shown in FIG. 2, the spring retaining ring 23 includes a first annular portion 231, a second annular portion 232 and a connecting portion 233 which are integrally formed.
  • the first annular portion 231 is formed in an annular shape extending in the circumferential direction and extends in the axial direction A as a whole.
  • the spring retaining ring 23 includes a hook portion 231h that extends and bends radially inward with respect to the first ring portion 231, so that one turn 24c of the coil spring 24 is partially located in the first ring shape.
  • the loop 24c is hooked by the hook 231h while being radially inside of the portion 231.
  • the hook portion 231h is formed by bending a part of the first annular portion 231.
  • the spring retaining ring 23 also includes a stopper portion 231s protruding toward the radially inner side relative to the first annular portion 231, and the circumferential end of the turn 24c can be pressed against the stopper portion 231s along the circumferential direction, so that The stopper 231s can stop the turn 24c in the circumferential direction.
  • the hook portion 231h is formed by bending a part of the first annular portion 231 and the connecting portion 233 inwardly, for example, by pressing.
  • the hook portion 231h and the stopper portion 231s are opposed to each other with the center axis of the first annular portion 231 interposed therebetween. That is, the center of the hook portion 231h in the circumferential direction and the center of the stopper portion 231s in the circumferential direction are separated by a center angle of approximately 180 degrees.
  • the second annular portion 232 is formed in an annular shape extending in the circumferential direction and extends in the axial direction A as a whole.
  • the diameter of the second annular portion 232 is smaller than the diameter of the first annular portion 231 and the second annular portion 232 is fixedly installed on the radially inner side of the inner ring axial portion 122 of the inner ring 12 by interference fit.
  • the second annular portion 232 is formed with a plurality of mounting protrusions 232p protruding toward the radially outer side, the plurality of mounting protrusions 232p are evenly distributed along the circumferential direction, and interference is achieved by the plurality of mounting protrusions 232p and the inner ring 12 Cooperate.
  • the connecting portion 233 is formed in an annular shape extending in the circumferential direction and extending in the radial direction R as a whole, and the connecting portion 233 connects the first annular portion 231 and the second annular portion 232 to each other.
  • the radially outer peripheral edge of the connecting portion 233 is connected to the axially one side peripheral edge of the first annular portion 231, and the radially inner peripheral edge of the connecting portion 233 is connected to the other axially side of the second annular portion 232.
  • the first annular portion 231 and the second annular portion 232 are located on both sides of the connecting portion 233 in the axial direction. As shown in FIG.
  • the connecting portion 233 abuts against the other axial end of the inner ring axial portion 122 from the other axial side, so that the connecting portion 233 is abutted by the axial end of the coil spring 24.
  • the coil spring 24 exerts a pressure along the axial direction A on the axial portion 122 of the inner ring.
  • a part of the coil 24c of the coil spring 24 is interposed between the connecting portion 233 and the hook portion 231h in the axial direction A.
  • the connecting portion 233 and the hook portion 231h can oppose the coil spring 24 in the axial direction A.
  • the turn 24c located on the radial inner side of the first annular portion 231 is limited; a part of the turn 24c of the coil spring 24 is located between the first annular portion 231 and the hook portion 231h in the radial direction R, passing The first ring portion 231 and the hook portion 231h can limit the turn 24c of the coil spring 24 located radially inward of the first ring portion 231 in the radial direction R; due to the circumferential end of the turn 24c of the coil spring 24 Since it is stopped by the stopper 231s in the circumferential direction, the coil 24c of the coil spring 24 located on the radially inner side of the first annular portion 231 can be restricted by the stopper 231s in the circumferential direction.
  • the spring retaining ring 23 can limit the turns 24c of the coil spring 24 in the three directions of the axial direction A, the radial direction R, and the circumferential direction, thereby effectively preventing the coil spring 24 from the clutch. After a certain deformation under the action of the torque, it will not come out of the spring retaining ring 23 and will not come out of its installation position.
  • the coil spring 24 includes a plurality of turns spirally wound in the circumferential direction.
  • the turn 24c of the coil spring 24 located on the most axial side abuts against the connecting portion 233 of the spring retaining ring 23 and then presses against the inner ring 12 of the release bearing 1.
  • the first annular portion 231 and the connecting portion 233 of the spring retaining ring 23 limit the turn 24c in the axial direction A, radial direction R, and circumferential direction, so that the turn 24c is fixed relative to the spring retaining ring 23, thereby The coil spring 24 is prevented from falling out of the spring retaining ring 23 after the coil spring 24 is deformed due to torque.
  • the turn of the coil spring 24 on the other side most in the axial direction abuts on the shoulder 21 s of the housing 21.
  • the coil spring 24 can apply a predetermined axial preload force (pressure) to the release bearing 1 via the spring retaining ring 23.
  • the turns of the coil spring 24 between the turns on both sides of the axial direction are sleeved on the housing 21 from the radial outside, and the radial dimension of these turns is smaller than that of the turns on both sides of the axial direction. size.
  • the hook 231h extends and bends toward the radial inner side. It can be understood that, in order to ensure the retention effect of the hook 231h, the hook 231h may face the axial direction after extending toward the radial inner side. One side (the second ring portion 232) is bent.
  • the hook portion 231h is formed by a part of the first ring-shaped portion 231 extending and bending toward the radial inner side
  • the present invention is not limited to this.
  • the hook portion 231h may be formed by a part of the connecting portion 233, or a separately formed hook portion may be fixed to the first annular portion 231 or the connecting portion 233 by welding, as long as it is satisfied that the hook portion and the connecting portion 233 can move in the axial direction.
  • a part of the coil 24c of the coil spring 24 may be restricted from both sides in the axial direction.
  • the length of the hook portion 231h extending in the circumferential direction should not be too short, and furthermore, a plurality of separated hook portions 231h may be provided.
  • notches on both sides of the hook portion 231h shown in FIG. 2 are provided to facilitate processing and are not a necessary feature of the technical solution of the present invention.
  • the stopper 231s is formed by bending a part of the first annular portion 231 and the connecting portion 233 inward by, for example, punching. It should be understood that the stopper formed in this way The portion 231s should ensure that the circumferential end of the coil 24c of the coil spring 24 can be abutted without allowing the coil spring 24 to pass through.
  • the present invention is not limited to this.
  • the center angle The angle can be set as required.
  • portion of the coil spring 24 mounted on the radially inner side of the first annular portion 231 may be the entire turn or part of the turn. It can be changed as needed.
  • the centering sub-cylinder 2 according to the present invention may include other various known components.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un système de libération d'embrayage, le système de libération d'embrayage étant apte à utiliser une bague de retenue de ressort (23) pour limiter l'extrémité latérale axiale d'un ressort hélicoïdal (24) au moins dans la direction axiale (A) et la direction radiale (R), de telle sorte que le ressort hélicoïdal (24) ne se dégage pas de la bague de retenue de ressort (23) même si le ressort hélicoïdal (24) se déforme dans une certaine mesure sous l'action d'un couple provenant de l'embrayage.
PCT/CN2019/100187 2019-08-12 2019-08-12 Système de libération d'embrayage Ceased WO2021026720A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/CN2019/100187 WO2021026720A1 (fr) 2019-08-12 2019-08-12 Système de libération d'embrayage
CN201980097576.5A CN113994115A (zh) 2019-08-12 2019-08-12 离合器分离系统

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2019/100187 WO2021026720A1 (fr) 2019-08-12 2019-08-12 Système de libération d'embrayage

Publications (1)

Publication Number Publication Date
WO2021026720A1 true WO2021026720A1 (fr) 2021-02-18

Family

ID=74569696

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2019/100187 Ceased WO2021026720A1 (fr) 2019-08-12 2019-08-12 Système de libération d'embrayage

Country Status (2)

Country Link
CN (1) CN113994115A (fr)
WO (1) WO2021026720A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0919741A1 (fr) * 1997-11-27 1999-06-02 Kongsberg Automotive ASA Dispositif d'engagement et de désengagement d'un embrayage
CN105782268A (zh) * 2014-12-16 2016-07-20 舍弗勒技术股份两合公司 离合器操纵机构、离合器系统和汽车
CN108869567A (zh) * 2017-05-08 2018-11-23 舍弗勒技术股份两合公司 保持环及离合器分离系统

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3011608A (en) * 1960-12-20 1961-12-05 Quinten A Hansen Fluid pressure operated clutch having an integral and non-rotatable cylinder and piston assembly
DE3136711A1 (de) * 1981-09-16 1983-03-31 LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl Kupplung, insbesondere kompressorkupplung
US5887692A (en) * 1997-01-10 1999-03-30 Automotive Products (Usa), Inc. Hydraulic pressure cylinder with combined boot and spring
JP5800147B2 (ja) * 2011-11-16 2015-10-28 ポップリベット・ファスナー株式会社 スプリング拘束クリップ
CN106931049B (zh) * 2015-12-29 2020-06-16 舍弗勒技术股份两合公司 离合器系统及其离合器操纵机构
CN108443350B (zh) * 2017-02-16 2021-05-14 舍弗勒技术股份两合公司 离合器分离系统

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0919741A1 (fr) * 1997-11-27 1999-06-02 Kongsberg Automotive ASA Dispositif d'engagement et de désengagement d'un embrayage
CN105782268A (zh) * 2014-12-16 2016-07-20 舍弗勒技术股份两合公司 离合器操纵机构、离合器系统和汽车
CN108869567A (zh) * 2017-05-08 2018-11-23 舍弗勒技术股份两合公司 保持环及离合器分离系统

Also Published As

Publication number Publication date
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