WO2010059422A1 - Plongeur de réglage du frein automatique avec came de relâchement d'embrayage - Google Patents

Plongeur de réglage du frein automatique avec came de relâchement d'embrayage Download PDF

Info

Publication number
WO2010059422A1
WO2010059422A1 PCT/US2009/063237 US2009063237W WO2010059422A1 WO 2010059422 A1 WO2010059422 A1 WO 2010059422A1 US 2009063237 W US2009063237 W US 2009063237W WO 2010059422 A1 WO2010059422 A1 WO 2010059422A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
worm shaft
adaptor
housing
worm
Prior art date
Application number
PCT/US2009/063237
Other languages
English (en)
Inventor
Mark J. Kromer
John Louis
Zoltan Tormasi
Original Assignee
Bendix Spicer Foundation Brake Llc
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 Bendix Spicer Foundation Brake Llc filed Critical Bendix Spicer Foundation Brake Llc
Priority to CN200980154774.7A priority Critical patent/CN102449341B/zh
Priority to RU2011124930/11A priority patent/RU2517638C2/ru
Priority to MX2011005104A priority patent/MX2011005104A/es
Priority to AU2009317919A priority patent/AU2009317919B2/en
Priority to EP09827997.9A priority patent/EP2352931B1/fr
Priority to CA2743831A priority patent/CA2743831C/fr
Priority to PL09827997T priority patent/PL2352931T3/pl
Publication of WO2010059422A1 publication Critical patent/WO2010059422A1/fr

Links

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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/04—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting mechanically
    • B60T11/06—Equalising arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T7/00—Brake-action initiating means
    • B60T7/02—Brake-action initiating means for personal initiation
    • B60T7/08—Brake-action initiating means for personal initiation hand actuated
    • B60T7/10—Disposition of hand control
    • B60T7/108—Disposition of hand control with mechanisms to take up slack in the linkage to the brakes
    • 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
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/42—Slack adjusters mechanical non-automatic
    • F16D65/50—Slack adjusters mechanical non-automatic for angular adjustment of two concentric parts of the brake control system
    • 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
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/58—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with eccentric or helical body
    • 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
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/60—Slack adjusters mechanical self-acting in one direction for adjusting excessive play for angular adjustment of two concentric parts of the brake control systems

Definitions

  • the present invention relates to brakes used on, for example, commercial truck or trailer axles, and in particular to automatic slack adjusters which eliminate excess motion in a brake actuator mechanism used to apply the brake.
  • Such adjusters typically are: (i) located on a portion of a brake camshaft which is outside of the brake (typically splined to the camshaft); and (ii) coupled to a pushrod of a brake actuator such that when the brake actuator push rod is extended or retracted, the slack adjuster rotates about the longitudinal axis of the brake camshaft.
  • a brake and slack adjuster arrangement is shown in Fig. 1 of U.S. Patent No. 4,380,276.
  • the slack adjuster causes the brake camshaft to rotate about its longitudinal axis, which in turn rotates a brake actuation cam affixed to the end of the brake camshaft located within the drum brake.
  • the rotation of the cam either presses the brake linings into engagement with the brake drum inner friction surface or allows the brake linings to withdraw radially inward, away from the friction surface.
  • the brake camshaft is also known as the brake cam.
  • Automatic slack adjusters can be designed to transmit brake actuator force to the brake camshaft in the brake application direction with no relative motion between the adjuster and the brake camshaft.
  • the slack adjuster is permitted to rotate relative to the brake camshaft an angular distance sufficient to remove some or all of this undesired slack, i.e., limiting the distance the brake linings withdraw from the brake drum friction surface so that the lining-drum clearance is maintained at a desired minimum.
  • the brake application cam thus stops in a corresponding new rest position at which the brake linings are maintained closer to the brake drum friction surface, at which the brake linings are maintained closer to the brake drum friction surface.
  • the worm shaft of the worm gear set rotates about is longitudinal axis, causing the worm shaft to move relative to the worm gear in a circumferential direction about the circumference of the worm gear.
  • This relative movement of the worm shaft and gear creates corresponding relative motion between the slack adjuster body and the brake camshaft.
  • the brake actuator pushrod returns to its rest position the brake camshaft does not return to its original rest position.
  • the brake camshaft only rotates through a smaller angle to a new rest position.
  • the brake application cam thus stops in a corresponding new rest position at which the brake linings are maintained closer to the brake drum friction surface.
  • the automatic slack adjuster compensates for brake lining and drum wear.
  • the one-way clutch is coupled to the worm shaft through a toothed clutch, which may conically shaped.
  • a heavy coil spring or disc-spring pack is positioned at the opposite end of the worm shaft to keep the conical clutch engaged and to provide adequate torque to turn the worm shaft.
  • the worm shaft turns the worm wheel, which is coupled to brake camshaft, in order to decrease the brake lining clearance and thus compensate for lining wear.
  • Examples of such arrangements are shown in prior art Figs. 1-3, corresponding respectively to Fig. 4 of U.S. Patent No. 4,380,276 (toothed clutch teeth 63), Fig. 3 of U.S. Patent No. 5,327,999 (toothed clutch 8), and Fig. 1 of U.S. Patent No. 5,664,647 (toothed clutch 14).
  • an external extension of the worm shaft projects outside the automatic slack adjuster housing to permit manual brake lining clearance adjustment during the installation of the slack adjuster or of new brake linings (in Fig.
  • extension 57 in Fig. 2, extension 4'; in Fig. 3, extension 15
  • the extension usually is shaped as a square or hexagon to facilitate gripping and turning with a wrench or other tool.
  • the worm shaft In order to advance the brake lining, the worm shaft must be rotated in a first direction (designated the clockwise direction for the purpose of this description). In order to retract the brake lining, the worm shaft must be rotated in the opposite, or counter-clockwise, direction. [0009] When the external extension is rotated in the clockwise (advance) direction, the toothed clutch remains engaged, and the worm shaft rotates with little resistance from the one-way clutch permitting the worm shaft to rotate with little resistance.
  • the adaptor part and an adjacent end of the automatic slack adjuster's worm shaft are provided with corresponding axially-oriented lugs which permit the adaptor part to drive rotation of the worm shaft in the clockwise and counter-clockwise directions. Between the lugs, ramps are provided which, when the lugs are displaced circumferentially relative to one another, cause the adaptor part to push the worm shaft to move axially away from the adapter part.
  • This axial displacement of the worm shaft axially lifts the output part of the one-way clutch out of engagement with the input part, disengaging the one-way clutch's one-way teeth and thereby permitting the worm shaft to smoothly rotate within the automatic slack adjuster housing without damaging the engagement teeth within the oneway clutch.
  • a similar camming action may be obtained by the interaction of camming surfaces of the adaptor part and a rod which extends through a bore in the worm shaft and is fixed to the output part of the one-way clutch.
  • the axial displacement of the cam rod pushes the one-way clutch output part out of engagement with the input part, freeing the worm shaft to be smoothly turned.
  • FIGs. 1-3 are views of prior art slack adjuster worm gear and one-way adjustment clutch arrangements.
  • Fig. 4a is an oblique partial cut-away view of an automatic slack adjuster in accordance with an embodiment of the present invention
  • Fig. 4b is an elevation partial cut-away view of the Fig. 4a automatic slack adjuster
  • Fig. 4c is an enlarged view of a detail of the one-way clutch of Figs. 4a and 4b.
  • Fig. 5a is a enlarged view of the components shown in section A of the partial cross-section in Fig. 4a
  • Fig. 5b is a transverse cut-away view of the Fig. 5a embodiment viewed from the one-way clutch end of the automatic slack adjuster.
  • Fig. 6 is cross-section view of an automatic slack adjuster in accordance with an alternative embodiment of the present invention.
  • FIGS. 4a-4c are partial cut-away views of a clearance-sensing automatic slack adjuster of the self-setting type 100
  • Figures 5a-5b provide enlarged views of the cut-away areas of Figs. 4a-4c.
  • the automatic slack adjuster 100 has a main gear set comprising a worm shaft 110 meshing with a worm gear 120, a brake actuator pushrod receiving hole 130 for coupling the automatic slack adjuster 100 to a brake actuator pushrod (not illustrated), and a splined coupling 140 either integrally formed with or otherwise coupled to the worm gear 120 to receive an end of a brake camshaft (not illustrated).
  • the worm shaft 110 is provided with a heavy coil spring or a disc spring pack 150 preloaded to bias the worm shaft load face 155 away from its corresponding housing mating face 156 by a designed gap.
  • worm gear 120 Concentrically located adjacent to worm gear 120 is a reference wheel 125, which is non-rotationally fixed to stationary reference arm 137, the reference arm being secured to a fixed point, such as the axle of the vehicle.
  • the reference wheel 125 meshes with adjustment wheel 135, which through a worm shaft extension 136 drives the control worm wheel 180, coupled via one-way clutch 170 to the worm shaft 110.
  • the control worm wheel 180 is formed with saw-tooth teeth 185 on an end face.
  • the control worm wheel teeth 185 which function as the input part to the one-way clutch 170, cooperates with corresponding saw-tooth teeth 186 on the output side of the one-way clutch.
  • the output part of the one-way clutch is a ratchet wheel 190, keyed to the worm shaft 110 by a polygon section 115 (or another alternate feature, such as a roll pin or other component sufficient to preclude rotation of the output side of the one-way clutch relative to the worm shaft 110).
  • the output part of the one-way clutch (ratchet wheel 190) is held axially against a step 195 on the worm shaft 110 by a light spring 200.
  • the brake actuator pushrod pushes on the automatic slack adjuster in the brake application direction 160.
  • the automatic slack adjuster begins to rotate about the brake cam shaft in the brake application direction, and this movement is transferred via the power spring 150 to worm shaft 110 and onward through the teeth of the worm shaft 110 and the worm gear 120 to splined coupling 140 to begin rotating the brake camshaft to apply the brake.
  • a reaction force acting on the brake linings is transmitted back through the brake cam and worm wheel to the worm shaft 110, pushing it axially to counteract the force of the power spring 150 biasing the worm shaft 110 in the brake application direction.
  • the reaction force by the worm screw pushes the worm shaft 110 backward until its load face 155 contacts housing mating face 156.
  • the braking application force applied by the brake actuator is transferred from the housing mating face to the worm shaft 110, and from the worm shaft 110 to worm gear 120.
  • the wheel of adjuster screw 135 rests in the slack adjuster housing a predetermined distance a from the outer cover 137. This distance corresponds to the desired brake lining clearance.
  • the adjuster screw 135 begins to climb along the circumference of fixed reference wheel 125, driven by the engagement of its worm threads 136 with the control worm wheel 180.
  • the adjuster screw 135 begins to move axially outward toward the outer cover 137.
  • An alternate variant to the preferred embodiment is of the "Adjust on Release type" in which prior to application of a braking force, as shown in Fig. 5b the wheel of adjuster screw 135 rests against the outer cover, a predetermined distance a from the housing. This distance corresponds to the desired brake lining clearance.
  • the adjuster screw 135 begins to climb along the circumference of fixed reference wheel 125, driven by the engagement of its worm threads 136 with the control worm wheel 180.
  • the adjuster screw 135 begins to move axially inward toward the housing.
  • the adjuster wheel 135 Prior to application of a braking force, as shown in Fig. 5b the adjuster wheel 135 rests in the slack adjuster housing a predetermined distance a from the outer cover 137. This distance corresponds to the desired brake lining clearance.
  • the adjuster screw 135 begins to climb along the circumference of fixed reference wheel 125, driven by the engagement of its worm threads 136 with the control worm wheel 180.
  • the adjuster screw 135 begins to move axially outward toward the outer cover 137. If there is no excessive wear in the brake, the linings will touch the brake drum when the adjuster screw 135 closes the predetermined distance a, and thus the adjuster wheel 135 will not rotate control worm wheel 180.
  • the adjuster screw can alternately be embodied as a two piece assembly comprising the Wheel part rotationally coupled to the worm part with an angular play built in which corresponds to the axial movement in the present embodiment.
  • the brake actuator pushrod will cause the automatic slack adjuster to continue to rotate in brake application direction 160, and adjuster wheel 135 will continue to climb reference wheel 125 until the brake linings come into full contact with the brake drum.
  • the worm shaft 110 is displaced axially until its load face 155 rests again the mating face 156 of the housing. This same axial motion also axially separates the toothed faces of the one-way clutch 170, disengaging the control worm wheel 180) from the worm shaft 110.
  • any further motion of the adjuster wheel 135 about reference wheel 2 will cause the adjuster wheel worm shaft threads 136 to rotate control wheel 180 about the worm shaft 110, but will not result in adjustment of the worm shaft 110.
  • a rotational input is given to one-way clutch 170 through a control worm and wheel pair (the worm wheel 180 is illustrated in Figs. 4a, 4b and 5).
  • the rotational input to the one-way clutch 170 is in the free-wheel direction, and thus as the input part teeth 185 tend to slide lout of engagement with the teeth 186 of the ratchet wheel 190, the output part effectively pushes the ratchet wheel 190 against the light spring 200. If the force pushing the ratchet wheel is sufficiently high, the one-way clutch skips forward by a tooth. Then, during the brake return stroke, as the input part rotates in the brake release direction, the teeth 185 re-engage teeth 186. The rotation of the output part 190 thus also rotates the input part 190 in the brake release direction.
  • the output part 190 is held in a rotationally-fixed relationship to the worm shaft 110 by polygon-shaped region 115, the worm shaft 110 is rotationally displaced relative to the worm wheel 120, such that the worm wheel 120 does not return to its original rest position, but instead comes to rest in a position corresponding to the brake cam shaft and the brake shoe being closer to the brake drum, i.e., in a position which reduces excess clearance.
  • worm shaft 110 initially moves backward until it reaches housing mating face 156. In doing so, the worm shaft pushes the output part 190 of the one-way clutch out of engagement with the teeth 185 of the input part, with no further adjustment. In this way a clearance sensing function is realized, by disengagement of the one-way clutch.
  • an adaptor part 210 projects out of the automatic slack adjuster housing and is provided with a hexagonal end for applying a wrench or similar tool.
  • the adaptor part and worm shaft are rotationally coupled by corresponding driving lugs 225, 226.
  • the openings 227 between the lugs are wider than the lugs, so that in each direction of rotation one set of lug side faces are in contact with one another, and there is a gap between the opposite lug side faces.
  • the adaptor part 210 also is provided with a feature which has a slit to hold a leaf spring.
  • the leaf spring is positioned such it exerts a force on the worm shaft lugs 226 to bias the lugs 226 into contact with the corresponding side faces of adaptor part lugs 225 which are engaged when turning in the brake shoe advance direction (in this embodiment, clockwise). It may be noted that the function of the leaf spring may alternately be accomplished by the use of a torsion spring.
  • the opening between adjacent lugs is constructed so that when brake shoes are to be manually advanced, one set of drive faces of the adjuster part lugs 225 are in contact with the corresponding faces of the lugs 226 of the worm shaft. In this condition there is no axial contact between the adaptor and worm shaft.
  • the worm shaft lugs 226 encounter a ramp construction 228 provided in the webbing between the adaptor lugs 225.
  • the ramps 228 are arranged such that as soon as the adaptor part 210 starts to turn counter-clockwise, the ramps contact the end faces of the worm shaft lugs 226.
  • the ramps 228 affect a cam action which pushes the worm shaft 110 axially away from the adaptor part 210.
  • This axial motion of the worm shaft 110 results in a corresponding axial motion of the one-way clutch output part 190.
  • the clutch output part 150 is pushed by worm shaft step 195 axially a distance sufficient to disengage it from the input part 180.
  • the ramps 228 cause the worm shaft to automatically take the teeth 186 of output part 190 out of engagement with the teeth 185 of the input part so that the worm shaft 110 is may turn freely, thereby permitting brake back-off to be accomplished in smooth manner without any forced slippage of clutch teeth.
  • an output part disengaging actuator here in the form of a slender coaxial rod 300 slidingly positioned within a hole running through the length of the worm shaft 100, is used to axially displace the output part of the one-way clutch to disengage the output part from the input part.
  • the inner end 310 the rod may rest against an actuating surface of the output part 190 of the one-way clutch, or as shown in Fig. 6, may be coupled to the output part.
  • the output part 190 is biased into engagement with control worm wheel 180 by a light spring 150.
  • the manual adjustment adaptor part 320 in this embodiment is constructed with a cam surface 330 on inside surface.
  • the cam surface 330 engages with a mating cam 340 on the adaptor part end of the coaxial rod 300.
  • the adaptor part 320 which is also arranged to engage and rotate the worm shaft 110, is thereby free to turn the worm shaft in a smooth manner without any forced slippage of clutch teeth.
  • the foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. For example, in the Fig. 5 embodiment, it does not matter whether the ramp is provided between the adaptor part lugs or between the worm shaft lugs, as long as the required camming action is provided to lift the one-way clutch output part axially out of engagement with the control worm wheel's one-way teeth. Because such modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and equivalents thereof.

Landscapes

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

Abstract

L'invention porte sur un plongeur de réglage du frein automatique à autoajustement amélioré destiné à réduire le jeu d'un frein d'un véhicule, dans lequel un élément d'actionnement externe aisément accessible permet à l'ensemble embrayage unidirectionnel du plongeur de réglage du frein automatique d'être aisément débrayé pour permettre un relâchement et un recul en douceur des semelles d'un frein de véhicule sans endommagement des dents unidirectionnelles de l'ensemble embrayage. Lorsque l'élément externe est actionné dans une direction de relâchement de frein, le déplacement de l'élément est converti en un déplacement qui déplace axialement une partie de sortie de l'embrayage unidirectionnel à l'opposé d'une partie d’entrée de l'embrayage sur une distance suffisante pour désaccoupler les dents unidirectionnelles des parties, ce qui débraye ainsi l'embrayage unidirectionnel pour permettre un recul de semelle de frein sans résistance de l'embrayage unidirectionnel.
PCT/US2009/063237 2008-11-18 2009-11-04 Plongeur de réglage du frein automatique avec came de relâchement d'embrayage WO2010059422A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
CN200980154774.7A CN102449341B (zh) 2008-11-18 2009-11-04 具有离合器释放凸轮的自动间隙调整器
RU2011124930/11A RU2517638C2 (ru) 2008-11-18 2009-11-04 Автоматический механизм регулировки зазора с кулачком разъединения муфты
MX2011005104A MX2011005104A (es) 2008-11-18 2009-11-04 Tensor automático con leva de liberación de embrague.
AU2009317919A AU2009317919B2 (en) 2008-11-18 2009-11-04 Automatic slack adjuster with clutch release cam
EP09827997.9A EP2352931B1 (fr) 2008-11-18 2009-11-04 Plongeur de réglage du frein automatique avec came de relâchement d'embrayage
CA2743831A CA2743831C (fr) 2008-11-18 2009-11-04 Plongeur de reglage du frein automatique avec came de relachement d'embrayage
PL09827997T PL2352931T3 (pl) 2008-11-18 2009-11-04 Automatyczny regulator luzu z krzywką wyłączającą sprzęgło

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US12/273,274 2008-11-18
US12/273,274 US8672101B2 (en) 2008-11-18 2008-11-18 Automatic slack adjuster with clutch release cam

Publications (1)

Publication Number Publication Date
WO2010059422A1 true WO2010059422A1 (fr) 2010-05-27

Family

ID=42171116

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2009/063237 WO2010059422A1 (fr) 2008-11-18 2009-11-04 Plongeur de réglage du frein automatique avec came de relâchement d'embrayage

Country Status (9)

Country Link
US (2) US8672101B2 (fr)
EP (1) EP2352931B1 (fr)
CN (1) CN102449341B (fr)
AU (1) AU2009317919B2 (fr)
CA (1) CA2743831C (fr)
MX (1) MX2011005104A (fr)
PL (1) PL2352931T3 (fr)
RU (1) RU2517638C2 (fr)
WO (1) WO2010059422A1 (fr)

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100206112A1 (en) * 2009-02-19 2010-08-19 Hiwin Mikrosystem Corp. Linear actuator
CN102465987B (zh) * 2010-11-08 2015-12-02 戎华庆 一种新型汽车制动自动调整臂装置
DE202011106746U1 (de) * 2011-10-14 2011-12-05 Haldex Brake Products Ab Bremshebel für eine Trommelbremse
US8973720B2 (en) * 2012-08-17 2015-03-10 Bendix Spicer Foundation Brake Llc Disc brake pad mounting and retention system and method
US8783427B2 (en) 2012-11-30 2014-07-22 Bendix Spicer Foundation Brake Llc Air disc brake adjuster for improved running clearance
CN105102844B (zh) * 2013-03-15 2017-12-22 古耐特公司 自动松隙调整器
TWI516693B (zh) * 2013-05-15 2016-01-11 第一傳動科技股份有限公司 線性致動器及其可調整速度之快速釋放結構
US9360069B2 (en) 2014-07-16 2016-06-07 Bendix Spicer Foundation Brake Llc High resolution one-way clutch using graduated engagement in a radial arrangement
CN104158346A (zh) * 2014-08-20 2014-11-19 深圳市润东来科技有限公司 一种车辆运动能量收集器及充电电路
EP3093518B2 (fr) 2015-05-11 2022-01-12 ZF CV Systems Europe BV Unité de réglage pour un régleur automatique de timonerie
JP6080066B1 (ja) * 2016-03-07 2017-02-15 パナソニックＩｐマネジメント株式会社 パンチルト駆動装置及びカメラ装置
CN106838072A (zh) * 2016-03-16 2017-06-13 倪世荣 新型斜齿轮式汽车制动间隙自动调整臂
CN106838071A (zh) * 2016-03-16 2017-06-13 倪世荣 斜齿轮蜗杆自调式汽车制动间隙自动调整臂
KR101864518B1 (ko) * 2016-04-29 2018-06-04 주식회사 에스 피 지 백래쉬 조절장치 및 이를 구비한 팬틸트 모듈
CN106050998B (zh) * 2016-07-21 2019-02-01 吴林 用于鼓式刹车系统的自动调整臂
US10197123B2 (en) 2016-08-04 2019-02-05 Tse Brakes, Inc. Vehicle braking systems with automatic slack adjusters
US10801603B2 (en) * 2016-11-23 2020-10-13 Steering Solutions Ip Holding Corporation Gear assembly with wear detection
BR112018076604A2 (pt) * 2017-05-31 2019-07-09 Madras Engineering Industries Private Ltd ajustador de folga automático
FR3069666B1 (fr) * 2017-07-27 2021-11-05 Bernard Controls Systeme de came comportant au moins un module mobile de commande d'un dispositif actionnaire
US10378604B2 (en) * 2017-12-07 2019-08-13 Bendix Spicer Foundation Brake Llc Slack adjuster for a drum brake of a vehicle air braking system
US10704630B2 (en) 2018-05-14 2020-07-07 Bendix Spicer Foundation Brake Llc Automatic slack adjuster with adjusting clutch in control train
US10808779B2 (en) 2018-08-01 2020-10-20 Bendix Commerical Vehicle Systems Llc Anti reverse ratchet mechanism for a grounded slack
DE102018216488A1 (de) * 2018-09-26 2020-03-26 Continental Teves Ag & Co. Ohg Spreizeinrichtung mit einer Nachstellvorrichtung für eine Trommelbremse
US11209062B2 (en) 2019-05-15 2021-12-28 Bendix Commercial Vehicle Systems Llc Automatic slack adjuster
CN112797120A (zh) * 2021-01-16 2021-05-14 海安市申菱电器制造有限公司 一种弧形齿面蜗杆减速机
CN114087303A (zh) * 2021-10-27 2022-02-25 瑞立集团瑞安汽车零部件有限公司 一种高强度密封性能好的自动间隙调整臂
WO2024009327A1 (fr) * 2022-07-08 2024-01-11 Madras Engineering Industries Private Limited Ensemble de réglage automatique du jeu

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB932155A (en) * 1959-12-14 1963-07-24 Dowty Rotol Ltd Improvements in or relating to drive transmissions
US3921765A (en) * 1974-02-19 1975-11-25 Aeroquip Corp Automatic brake slack adjuster
US4380276A (en) * 1980-07-21 1983-04-19 Kelsey-Hayes Co. Slack adjuster for vehicle brakes
US4440268A (en) * 1979-12-13 1984-04-03 Sab Automotive Ab Brake lever for an S-cam automotive drum brake
US5664647A (en) 1993-11-26 1997-09-09 Haldex Ab Brake drum lever for an automotive S-cam drum brake
US6450302B1 (en) 2001-05-22 2002-09-17 Crewson Brunner Inc. Automatic slack adjuster with two part lift rod
US7198138B2 (en) * 2004-06-14 2007-04-03 Ang Automotive India Private Limited Automatic slack adjuster assembly for vehicle braking system

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3871495A (en) 1973-10-24 1975-03-18 Lloyd Raymond Devitt Automatic slack adjuster for air brakes
DE3409454A1 (de) * 1984-03-15 1985-09-26 Bergische Achsenfabrik Fr. Kotz & Söhne, 5276 Wiehl Nachstellvorrichtung fuer fahrzeugbremsen
US4621714A (en) 1985-07-12 1986-11-11 Sloan Valve Company Vehicle slack adjuster clutch
SE470526B (sv) 1992-11-18 1994-07-04 Haldex Ab Bromshävarm för en s-kambroms hos ett landsvägsfordon
US5350043A (en) 1993-03-05 1994-09-27 Crewson Brunner Inc. Automatic slack adjuster
CN2305521Y (zh) 1995-12-23 1999-01-27 韩学智 气动刹车间隙自动调整臂
US7757824B2 (en) 2004-04-07 2010-07-20 Madras Engineering Industries Private Ltd. Automatic brake adjuster for adjusting the slack between the brake lining and brake drum of a vehicular braking system
US20060163014A1 (en) * 2005-01-27 2006-07-27 Crewson Gary E Automatic slack adjuster with spring release spindle
DE102005041342B4 (de) 2005-05-20 2007-06-06 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Gestängesteller für Trommelbremse
RU76286U1 (ru) * 2008-04-28 2008-09-20 Открытое акционерное общество "Арзамасский машиностроительный завод" Автомобиль повышенной проходимости специального назначения

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB932155A (en) * 1959-12-14 1963-07-24 Dowty Rotol Ltd Improvements in or relating to drive transmissions
US3921765A (en) * 1974-02-19 1975-11-25 Aeroquip Corp Automatic brake slack adjuster
US4440268A (en) * 1979-12-13 1984-04-03 Sab Automotive Ab Brake lever for an S-cam automotive drum brake
US4380276A (en) * 1980-07-21 1983-04-19 Kelsey-Hayes Co. Slack adjuster for vehicle brakes
US5664647A (en) 1993-11-26 1997-09-09 Haldex Ab Brake drum lever for an automotive S-cam drum brake
US6450302B1 (en) 2001-05-22 2002-09-17 Crewson Brunner Inc. Automatic slack adjuster with two part lift rod
US7198138B2 (en) * 2004-06-14 2007-04-03 Ang Automotive India Private Limited Automatic slack adjuster assembly for vehicle braking system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2352931A4

Also Published As

Publication number Publication date
US8672101B2 (en) 2014-03-18
EP2352931B1 (fr) 2014-07-16
RU2517638C2 (ru) 2014-05-27
MX2011005104A (es) 2011-08-04
CA2743831C (fr) 2017-05-02
US20100122879A1 (en) 2010-05-20
EP2352931A1 (fr) 2011-08-10
EP2352931A4 (fr) 2012-08-22
CA2743831A1 (fr) 2010-05-27
AU2009317919B2 (en) 2014-11-13
MX322682B (fr) 2014-08-08
PL2352931T3 (pl) 2015-02-27
US20140209421A1 (en) 2014-07-31
CN102449341B (zh) 2015-04-29
US8973722B2 (en) 2015-03-10
CN102449341A (zh) 2012-05-09
RU2011124930A (ru) 2012-12-27
AU2009317919A1 (en) 2010-05-27

Similar Documents

Publication Publication Date Title
CA2743831C (fr) Plongeur de reglage du frein automatique avec came de relachement d'embrayage
US8302744B2 (en) Automatic slack adjuster anchor unit with a one-way clutch
EP0030766B1 (fr) Levier de frein pour frein à tambour de véhicule à came en S
CN110410439B (zh) 致动机构
CA2743835C (fr) Plongeur de reglage du frein automatique a autoreglage presentant une duree de vie accrue
CN110410431B (zh) 调节器机构
JPH0247610B2 (fr)
US4085830A (en) Automatic slack adjusters for vehicle brakes
US8453805B2 (en) Automatic slack adjuster with ball detent clutch
US4483424A (en) Automatic slack adjuster
GB2168439A (en) A disc brake actuator with slack adjustment
US20220186801A1 (en) Automatic Slack Adjuster Torque Limiting Link

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200980154774.7

Country of ref document: CN

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

Ref document number: 09827997

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: MX/A/2011/005104

Country of ref document: MX

WWE Wipo information: entry into national phase

Ref document number: 2743831

Country of ref document: CA

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2160/KOLNP/2011

Country of ref document: IN

WWE Wipo information: entry into national phase

Ref document number: 2009317919

Country of ref document: AU

WWE Wipo information: entry into national phase

Ref document number: 2009827997

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2009317919

Country of ref document: AU

Date of ref document: 20091104

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 2011124930

Country of ref document: RU