GB1592109A - Creación de Inventos y Patentes con Inteligencia Artificial

GB1592109A – Bidirectional clearance sensing brake adjuster
– Google Patents

GB1592109A – Bidirectional clearance sensing brake adjuster
– Google Patents
Bidirectional clearance sensing brake adjuster

Download PDF
Info

Publication number
GB1592109A

GB1592109A
GB9652/78A
GB965278A
GB1592109A
GB 1592109 A
GB1592109 A
GB 1592109A
GB 9652/78 A
GB9652/78 A
GB 9652/78A
GB 965278 A
GB965278 A
GB 965278A
GB 1592109 A
GB1592109 A
GB 1592109A
Authority
GB
United Kingdom
Prior art keywords
clearance
clutch
gear
adjuster
rotation
Prior art date
1977-03-31
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.)

Expired

Application number
GB9652/78A
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.)

Eaton Corp

Original Assignee
Eaton Corp
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.)
1977-03-31
Filing date
1978-03-10
Publication date
1981-07-01

1978-03-10
Application filed by Eaton Corp
filed
Critical
Eaton Corp

1981-07-01
Publication of GB1592109A
publication
Critical
patent/GB1592109A/en

Status
Expired
legal-status
Critical
Current

Links

Espacenet

Global Dossier

Discuss

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

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

Description

PATENT SPECIFICATION
( 11) 1592109 ( 21) Application No 9652/78 ( 22) Filed 10 March 1978 ( 19) ( 31) Convention Application No 783258 ( 32) Filed 31 March 1977 in ( 33) United States of America (US) ( 44) Complete Specification published 1 July 1981 ( 51) INT CL 3 F 16 D 65/62 ( 52) Index at acceptance F 2 E LX ( 54) BIDIRECTIONAL CLEARANCE SENSING BRAKE ADJUSTER ( 71) We, EATON CORPORATION, a Corporation organized and existing under the laws of the State of Ohio, USA, of 100 Erieview Plaza, Cleveland, Ohio 44114, USA, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in
and by the following statement:-
The invention relates to an automatic clearance adjuster and more specifically to such an adjuster having a two-way torque limiting ratchet clutch The invention is related to the invention of our co-pending application No 9653/78 (Serial No 1592110) In a brake system wear of the brake frictional shoe-surfaces and drum increases the running clearances therebetween Uncorrected, the increasing clearance will require an increased brake stroke to move the brake shoes into frictional engagement with the brake drum The disadvantages of not correcting the increasing clearance are well known and include: ( 1) loss of effective brake actuating force due to over stretching of the air motor diaphragm, ( 2) unbalanced vehicle braking should the brakes on different wheels and/or on different axles wear at different rates, ( 3) increased amounts of pressurised air to apply the brake, ( 4) increased time to move the brake shoes into contact with the drum.
Many brake adjusters have been devised which automatically decrease the clearance between the brake shoes and the brake drum if the total brake stroke exceeds a predetermined amount Such adjusters, commonly called stroke sensing adjusters, can over adjust the brakes unless they provide for a relatively large amount of normal or running clearance to allow for elastic deformation in the brake system during severe brake applications and to allow for thermal expansion of a hot brake drum.
Several automatic adjusters have been devised which sense the two parts of any total brake stroke, i e, a first part requiring a relatively small brake actuating force to move the brake shoes into contact with the brake drum and a second part requiring a relatively large amount of brake actuating force for stopping the vehicle after the shoes have contacted the drum The second part of the brake stroke is responsible for the men 55 tioned elastic deformation and is often larger than the first part of the brake stroke These clearance sensing adjusters employ either a disengaging clutch or torque limiting clutch in the adjuster mechanism, which clutches 60 respectively disengage or slip in response to the relatively large actuating forces in the second part of the brake stroke to prevent over-adjustment due to the said elastic deformation, that is to prevent clearance adjust 65 ment when the shoes are in contact with the drum Such adjusters include or have built therein a predetermined amount of lost motion for establishing the running or normal clearance of the brake In such adjusters, 70 clearance is decreased if the lost motion is taken up before the shoes contact the drum.
The adjusting mechanism in such an adjuster automatically makes a clearance decreasing adjustment when the first part of 75 the stroke exceeds a predetermined amount.
The adjusting mechanism is blocked out or prevented from making a clearance decreasing adjustment during the second part of the stroke The second part of the stroke is often 80 larger than the first part due to the high actuating forces causing deformation in the brake system and therefore can quickly over adjust the brake if the adjusting mechanism is not blocked out One clearance sensing 85 adjuster, disclosed in U S Reissue Patent No 26,965, employs a disengaging clutch which physically disengages an adjusting mechanism in response to the high brake actuating forces Another such adjuster, dis 90 closed in U S Patent No 3,507,369, employs a spring clutch which slips in response to the high brake actuating forces The clutches employed in the adjusters require a rather high degree of quality control in manufac 95 ture and assembly.
Further, the mentioned adjusters provide only for clearance decreasing adjustments in response to the first part of the stroke exceeding a predetermined amount How 100 0 W) 1,592,109 ever, the first part of the brake stroke, i e, the running clearance, may be temporarily increased when the brake drum thermally expands, whereby the mentioned clearance sensing adjusters will over adjust the brake.
An adjuster for automatically increasing and decreasing the clearance of an improperly adjusted brake is disclosed in U S Patent No 3,990,546 However, this adjuster can not distinguish between the two parts of the brake stroke as do the previously mentioned adjusters employing either the disengaging clutch or the spring clutch.
An object of the invention is to provide an automatic clearance adjuster having an improved two-way torque limiting clutch.
According to one aspect of the invention there is provided a clearance adjuster for automatically controlling clearance between a movable friction member and a rotating member, the adjuster comprising a lever defining a housing having first and second intermeshed gears disposed therein, adjusting means, means operative to apply a force for inhibiting rotation of the gears by the adjusting means in at least one direction relative to the lever and a two-way torque limiting ratchet clutch having torque transmitting capacity in both drive directions; the first gear being adapted for driving connection with the movable member; the second gear being operative to adjustably lock the first gear to the lever and to transmit forces between the lever and the first gear for moving the friction member into engagement and disengagement with the rotating member; the adjusting means being operative to apply a torque to rotate the second gear relative to the lever and effect a clearance adjusting rotation of the gear in response to pivotal movement of the lever; the said clutch being operative in one drive direction to resist slipping and to allow a clearance decreasing rotation of the second gear while the forces transmitted are below a first predetermined level; the said clutch being operative in the one drive direction to slip and prevent the said clearance decreasing rotation in response to the forces transmitted exceeding the said first predetermined level; the said clutch operative in the other drive direction to slip and prevent a clearance increasing rotation in response to the transmitted forces exceeding a second predetermined level; and the said clutch operative in the other drive direction to slip and prevent the said clearance increasing rotation in response to the inhibiting force exceeding the said second predetermined level.
According to another aspect of the invention there is provided a clearance adjuster for automatically controlling clearance between a movable friction member and a rotating member, the adjuster comprising a lever defining a housing having first and second intermeshed gears disposed therein, adjusting means, means operative to apply a force for inhibiting rotation of the gears by the adjusting means in at least one direction and a two-way torque limiting ratchet clutch; the 70 first gear being adapted for driving connection with the movable friction member; the second gear operative to adjustably lock the first gear to the lever, whereby pivotal movement of the lever moves the friction 75 member into engagement and disengagement with the rotating member; the adjusting means operative to apply a torque to rotate the second gear relative to the lever to effect a clearance adjusting rotation of the gears in 80 response to the pivotal movement; the said clutch having a torque transmitting capacity in one drive direction allowing a clearance decreasing rotation of the second gear by the adjusting means while the movable member 85 moves through the said clearance in one direction; the said clutch being operative to slip and prevent rotation of the second gear by the adjusting means while the movable friction member is in contact with the rotat 90 ing member; and the said clutch being operative in the other drive direction to slip and prevent clearance increasing rotation of the second gear by the adjusting means in response to the inhibiting force while the 95 movable friction member moves through the said clearance in the other direction.
Preferably, the ratchet clutch includes two sets of mating ratchet teeth having inclined drive faces in both drive directions of the 100 clutch and circumferentially arrayed on mating frusto-conical end surfaces of two annular clutch members, thereby providing self aligning of the clutch members.
In order that the invention may be more 105 readily understood, a specific embodiment thereof will now be described with reference to the accompanying drawing, in which:
Figure 1 illustrates a cam actuated brake and an actuating means therefor including 110 an adjuster according to the invention; Figure 2 is a partially broken away view of the actuating means and adjuster of Figure 1; Figure 3 and 3 A illustrate further details of the adjuster of Figure 2, Figure 3 being in the 115 direction of the arrow III in Figure 2, and Figure 4 is a section view taken along line 4-4 of Figure 2.
Referring now to Figure 1, therein is shown a brake actuating means 10 and 120 automatic clearance adjuster 11 for a brake assembly 12 of a truck type vehicle Actuating means 10 includes an L-shaped lever 14 which is pivotally connected to a clevis 16 via a pin 18 Clevis 16 is in turn connected to a 125 rod 19 which moves axially to the left to apply the brake in response to pressurised fluid acting on an unshown diaphragm in an air motor 20.
The brake assembly 12 includes a pair of 130 1,592,109 friction members or brake shoes 22 which are moved radially outward into frictional contact with a brake drum 24 in response to counterclockwise rotation of an s-cam 26 which may be formed on or fixed to one end of a shaft 28 The other end of shaft 28 is connected to the actuating means 10 Hence, pressurised fluid in motor 20 providing a force for moving rod 19 to the left and effects a counterclockwise rotation of lever 14 and scam 26 about the axis of shaft 28 A spring 30 applies a force for retracting the brake shoes and an unshown spring in air motor 20 provides a force for retracting rod 19 when the pressurised fluid is removed Brake assembly 12 as thus far described, except the automatic clearance adjuster 11, is well known.
The automatic clearance adjuster 11 employs an improved torque limiting clutch for sensing the two parts of the brake stroke and a roller clutch The roller clutch allows the clearance to be increased should the clearance become too small for any reason.
The structure and operation of actuating means 10 and clearance adjuster 11 is more clearly shown in the partially broken away view of lever 14 in Figure 2 and Figures 3 and 3 A, the details shown in Figure 3 being rotated through 90 with respect to Figure 2.
Lever 14 includes through-bores 32 and 34 for housing portions of the clearance adjuster Bore 32 rotatably supports a worm gear 38 which is splined to shaft 28 Bore 34 is defined by coaxial bore portions 34 a, 34 b, 34 c and 34 d Bore portion 34 a houses an adjusting assembly 40 and a two-way torque limiting ratchet clutch 42 Bore portion 34 b provides rotational support for one end portion 44 a of a worm shaft 44 The inner end of portion 44 a has a square drive portion 44 b Bore portion 34 c houses a worm 46 in mesh with worm gear 38 and fixed to rotate with worm shaft 44 Bore portion 34 d houses a roller clutch 48 which is fixed to the other end of worm shaft 44; this has an enlarged round portion 44 c, a squared portion 44 d and necked down round portion 44 e.
Adjusting assembly 40 includes a cylindrical sleeve member 50 having a slotted end a and a pair of internal helical grooves 50 b which drivingly but loosely receive the ends of a pin 52 pressed through a hole 54 a in a drive member 54 Sleeve 50 is rotatably supported by bore 34 a and is retained therein against axial movement by snap rings 56 and 58 Drive members 54 includes a head portion 54 b pivotally secured to clevis 16 by a pin 60 which also loosely retains member 54 against rotation about its axis Pivotal movement of lever 14 in a counterclockwise direction, to apply the brake, axially moves drive member 54 further into sleeve 50 and effects a rotation of the sleeve in one direction due to the co-operation between pin 52 and helical grooves 50 b Pivotal movement of lever 14 in a clockwise direction, to release the brake, axially retracts the drive member and effects a rotation of sleeve in the opposite direction The adjusting 70 assembly is sealed against foreign matter by a rubber boot 62 which is secured to lever 14 and drive member 54 by clamps 64 and 66.
Torque limiting ratchet clutch 42 includes an annular clutch member 68 rotatably 75 seated against a shoulder defined by the difference in diameter between bore portions 34 a and 34 b, an annular clutch member 70, and a spring 72 for biasing clutch members 68 and 70 into engagement with a substan 80 tially constant force Clutch member 68 includes a square opening 68 a which snugly receives square drive portion 44 b of worm shaft 44 and a convex frusto-conical face 68 b having a set of asymetric teeth 68 c circumfer 85 entially arrayed thereon, see Figure 3 Clutch member 70 includes a pair of tangs 70 a which are loosely received in slot 50 a of sleeve 50 and a concave frusto-conical face b matable with face 68 b and having a set of 90 asymetric teeth 70 c circumferentially arrayed thereon and mating with teeth 68 c, see Figure 3 Looking momentarily at Figure 3 A, each tooth 68 c includes a high torque drive face 68 d inclined at about 25 degrees with 95 respect to the rotational axis of the clutch and a low torque drive face 68 e inclined at about 55 degrees with respect to the axis.
Teeth 70 c include drive faces 70 d and 70 e which mate respectively with drive faces 68 d 100 and 68 e.
As may be seen from the configuration of ratchet teeth 68 c and 70 c, clutch 42 has a higher torque capacity or limit in the clearance decreasing direction when drive is 105 through high torque drive faces 68 d and 70 d during brake application and a lower torque limit in the clearance increasing direction when drive is through low torque drive faces 68 e and 70 e during brake release The greater 110 torque capacity in the clearance decreasing direction is needed since the teeth of worm 46 move in an up-ramp direction with respect to the teeth of worm gear 38, since s-cam 26 moves in an up-ramp direction, and since the 115 forces of shoe retraction spring 30 works through the ramps to oppose rotation of the worm The ramps and spring 30 assist worm rotation in the clearance increasing direction.
The ratchet teeth could of course be made 120 symmetrical, but this would require a higher capacity roller clutch 48 or device to prevent rotation in the clearance increasing direction.
The biasing force of spring 72 is substantially constant and independent of the pivotal 125 position of lever 14 or the axial position of drive member 54 Further, the torque capacity of the ratchet clutch is easily maintained within prescribed limits.
Looking now at Figures 2 and 4, roller 130 clutch 48 includes an outer race 73 pressed into bore portion 34 d, an inner race 74 having three cam surfaces 74 a separated by three radially extending rib portions 74 b and a squared opening 74 c which fits snugly over squared portion 44 d of worm shaft 44, three rollers 76 which wedge between the cam surfaces 74 a and the inner surface of outer race to lock-up the clutch, three springs 78 carried by ribs 74 b and biasing the rollers up the ramps of cam surfaces 74 a, and an end plate 80 rotatably unsorted on necked down portion 44 e -of wcu shaft 44 and retained thereon by a snap ring 82 It may be seen from the foregoing that clutch member 68 and inner race 74 are locked together via worm shaft 44 Hence, roller clutch lock-up prevents rotation of worm 46 and clutch member 68 Plate 80 allows manual clearance adjustment of the brakes and includes for this purpose a hexagonal head 80 a and three fingers 80 b interposed between rollers 76 and ribs 74 b to facilitate free clockwise and counterclockwise rotation of the inner race and worm 46 in response to rotation of the hexagonal head by a wrench Outer race 73 provides an end stop for worm 46 and a bearing surface for enlarged portion 44 c or worm shaft 44 Roller clutch 48 is free running when worm 46 is being turned in the clearance decreasing direction by ratchet clutch 42 and locks-up when the ratchet clutch attempts to rotate the worm in the clearance increasing direction However, inner race 74 has to rotate a few angular degrees before rollers 76 can wedge between.
the outer race and cam surfaces 74 a to lockup the roller clutch This small amount of angular rotation or hysteresis in the roller clutch allows the ratchet clutch to rotate worm 46 a predetermined amount in the clearance increasing direction each time the brakes are released, thereby providing an automatic clearance increasing adjustment of the brake.
When the shoe to drum clearance is within the predetermined limits, a clearance increasing and decreasing equilibrium will be established by the adjuster, i e, the adjuster will make a small clearance decreasing adjustment during each brake application stroke and a substantially equally small clearance increasing adjustment during each brake release stroke When the shoe to drum clearance is greater than the predetermined limits, the torque limiting clutch allows each clearance decreasing adjustment to increase relative to each clearance increasing adjustment until the clearance is within limits.
When the shoe to drum clearance is less than the predetermined limits, the torque limiting clutch allows each clearance decreasing adjustment to diminish relative to each clearance increasing adjustment until the clearance is again within the limits.
During the first part of the brake-applying.
stroke, lever 14 rotates counterclockwise about the axis of shaft 28 and carries therewith worm 46 and worm gear 38 The worm reacts through a thrust bearing 84 70 against a shoulder defined by the difference in diameter between bore portions 34 b and 34 c Drive member 54 moves axially in sleeve 50, rotates clutch member 70 after small clearances defined by the loose fits between 75.
pin 60 and clevis 16, between pin 52 and grooves 50 b, and between slot 50 a and tangs a are taken up These small clearances provide a lost motion for establishing the normal or predetermined running clearance 80 between shoes 22 and drum 24 When the lost motion is taken up, sleeve 50 rotates% clutch member 70 which applies a torque.
through the high torque drive faces foirotating worm 46 relative to lever 14 and 85 decreasing the shoe to drum clearance.
During the first part of the brake-applying stroke and if the brake is adjusted within limits, the lost motion will be taken up shortly before shoes 22 contact drum 24, 90 thereby allowing a small or incremental rotation of worm 46 and clutch member 68 by clutch member 70 until the shoes contact the drum Continued counterclockwise rota tion of lever 14, i e, the second part of the 95 brake stroke, cause an abrupt increase in.
reaction forces throughout the actuating.
means and the brake assembly These forces react at the interface of the worm and worm gear teeth and quickly raise the torque 100 required to rotate the worm to a level above the torque limit of clutch 42, whereby teeth c slip over teeth 68 c during the remainder of the second part of the brake stroke If the shoe to drum clearance is greater than the 105.
predetermined limit, the length of the first part of the brake stroke increases in proportion to the excess clearance, thereby increasing the amount of each incremential clearance decreasing rotation of worm 46 If the 110.
shoe to drum clearance is less than the predetermined limit, the length of the first part of the brake stroke decreases in proportion to the insufficient clearance, thereby decreasing the amount of each incremantial 115 clearance decreasing rotation of worm 46.
During the brake release stroke, the lost motion is first taken up in the reverse direction, the low torque drive faces of teeth c then slip over the low torque drive faces 120 of teeth 68 c until the brake shoes move out of contact with the drum, clutch 42 then rotates the worm a maximum predetermined or fixed incremential amount until the hysteresis in roller clutch 48 is taken up, and the 125 roller clutch then locks-up and applies a counter torque to worm shaft 44 in excess to the low torque limit of clutch 42 in the clearance increasing direction Each fixed incremential clearance increasing rotation of 130 1,592,109 1,592,109 worm 46 will be greater than each incremential clearance decreasing rotation of the worm while the shoe to drum clearance is less than the predetermined limit, will be substantially the same as each clearance decreasing increment while the brake clearance is within limits, and will be less than each clearance decreasing increment while the shoe to drum clearance is greater than the predetermined limit Hence, adjuster 11 provides variable clearance decreasing adjustments and maximum predetermined or fixed clearance increasing adjustments in response to brake applications and releases respectively.
The preferred embodiment of the invention has been disclosed for illustration purposes Many variations and modifications of the preferred embodiment are believed to be within the scope of the invention For example, the means for effecting clearances decreasing adjustments, i e, sleeve 50 and ratchet clutch 42, may be used in combination with other means to inhibit, prevent, or control rotation of worm 46 in the clearance increasing direction Such devices could be a spring such as the Belleville spring as shown in U S Patent No 3,507,369, a spring clutch such as shown in U S Patent No 3,907,357, or a ratchet device similar to ratchet clutch 42 as shown herein Further, the roller clutch may be used in combination with other types of torque limiting devices, e g, the spring clutch as shown in U S Patent No 3,507,369.

Claims (1)

WHAT WE CLAIM IS:-
1 A clearance adjuster for automatically controlling clearance between a movable friction member and a rotating member, the adjuster comprising a lever defining a housing having first and second intermeshed gears disposed therein, adjusting means, means operative to apply a force for inhibiting rotation of the gears by the adjusting means in at least one direction relative to the lever and a two-way torque limiting ratchet clutch having torque transmitting capacity in both drive directions; the first gear being adapted for driving connection with the movable member; the second gear being operative to adjustably lock the first gear to the lever and to transmit forces between the lever and the first gear for moving the friction member into engagement and disengagement with the rotating member; the adjusting means being operative to apply a torque to rotate the second gear relative to the lever and effect a clearance adjusting rotation of the gear in response to pivotal movement of the lever; the said clutch being operative in one drive direction to resist slipping and to allow a clearance decreasing rotation of the second gear while the forces transmitted are below a first predetermined level; the said clutch being operative in the one drive direction to slip and prevent the said clearance decreasing rotation in response to the forces transmitted exceeding the said first predetermined level; the said clutch operative in the other drive direction 70 to slip and prevent a clearance increasing rotation in response to the transmitted forces exceeding a second predetermined level; and the said clutch operative in the other drive direction to slip and prevent the said clear 75 ance increasing rotation in response to the inhibiting force exceeding the said second predetermined level.
2 A clearance adjuster for automatically controlling clearance between a movable 80 friction member and a rotating member, the adjuster comprising a lever defining a housing having first and second intermeshed gears disposed therein, adjusting means, means operative to apply a force for inhibit 85 ing rotation of the gears by the adjusting means in at least one direction and a twoway torque limiting ratchet clutch; the first gear being adapted for driving connection with the movable friction member; the sec 90 ond gear operative to adjustably lock the first gear to the lever, whereby pivotal movement of the lever moves the friction member into engagement and disengagement with the rotating member; the adjusting means opera 95 tive to apply torque to rotate the second gear relative to the lever to effect a clearance adjusting rotation of the gears in response to the said pivotal movement; the said clutch having a torque transmitting capacity in one 100 drive direction allowing a clearance decreasing rotating of the second gear by the adjusting means while the movable member moves through the said clearance in one direction; the said clutch being operative to 105 slip and prevent rotation of the second gear by the adjusting means while the movable friction member is in contact with the rotating member; and the said clutch being operative in the other drive direction to slip 110 and prevent clearance increasing rotation of the second gear by the adjusting means in response to the said inhibiting force while the movable friction member moves through the said clearance in the other direction 115 3 An adjuster as claimed in Claim 1 or Claim 2, wherein the ratchet clutch includes a set of asymmetric ratchet teeth for providing a greater torque transmitting capacity of the ratchet clutch in one drive direction than 120 in the other drive direction.
4 An adjuster as claimed in Claim 3, wherein the greater torque transmitting capacity is in the drive direction for clearance decreasing rotation of the second gear 125 An adjuster as claimed in any preceding claim, wherein the ratchet clutch comprises a first clutch member including a first set of ratchet teeth having drive faces inclined to both drive directions of the first 130 1,592,109 clutch member; a second clutch member including a second set of ratchet teeth having drive faces inclined to both drive directions of the second clutch member and matable with the drive faces of the first tooth set; and spring means biasing the two tooth sets into engagement.
6 An adjuster as claimed in Claim 5, wherein the ratchet clutch includes a first substantially annular clutch member disposed to rotate about its axis and provided on an axially facing end thereof with a convex frusto-conical surface having the first set of circularly arrayed teeth cirumferentially disposed thereon; and a second substantially annular clutch member disposed to rotate the said axis and provided on an axially facing end thereof with a concave frusto-conical surface having the second set of circularly arrayed teeth circumferentially disposed thereon.
7 An adjuster as claimed in Claim 6, wherein the said axis is coincident with the rotational axis of the adjusting means.
8 An adjuster as claimed in Claim 5, Claim 6 or Claim 7, wherein spring means is adapted to bias the two sets of teeth into engagement with a force great enough to prevent slipping of the teeth in one drive direction of the ratchet clutch while the movable friction member moves in the said clearance for allowing a clearance decreasing rotation of the second gear by the adjusting means, with a force insufficient to prevent slipping in both drive directions of the ratchet clutch while the movable member is in substantial contact with the rotating member for preventing clearance rotation of the second gear by the adjusting means, and with a force insufficient to prevent slipping in the other drive direction of the ratchet clutch due to the said inhibiting force to prevent a clearance increasing rotation of the second gear.
9 An adjuster as claimed in Claim 7 or Claim 8, wherein the second gear is mounted to rotate with a shaft disposed to rotate about the said axis, one of the annular members being fixed to rotate with the shaft and the other being fixed to rotate with the adjusting means.
An adjuster as claimed in any of claims 5 to 9, wherein the biasing force of the spring means is independent of the pivotal position of the lever.
STEVENS, HEWLETT & PERKINS, Chartered Patent Agents, 5, Quality Court, Chancery Lane, London, W C 2.
Printed for Hcr Majesty’s Stationery Office by Burgess & Son (Abingdon) Ltd -1981 Published at The Patent Office.
Southampton Buildings London WC 2 A IAY.
from which copies may he obtained.

GB9652/78A
1977-03-31
1978-03-10
Bidirectional clearance sensing brake adjuster

Expired

GB1592109A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

US05/783,258

US4094390A
(en)

1977-03-31
1977-03-31
Bidirectional clearance sensing brake adjuster

Publications (1)

Publication Number
Publication Date

GB1592109A
true

GB1592109A
(en)

1981-07-01

Family
ID=25128664
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB9652/78A
Expired

GB1592109A
(en)

1977-03-31
1978-03-10
Bidirectional clearance sensing brake adjuster

Country Status (4)

Country
Link

US
(1)

US4094390A
(en)

DE
(1)

DE2813624A1
(en)

GB
(1)

GB1592109A
(en)

SE
(1)

SE442432B
(en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

US4222310A
(en)

1978-12-04
1980-09-16
Eaton Corporation
Brake actuator fastener assembly

US4249644A
(en)

1979-05-29
1981-02-10
Eaton Corporation
Slack adjuster

ZA802145B
(en)

1979-05-29
1981-04-29
Eaton Corp
Improved slack adjuster

US4546861A
(en)

1982-05-17
1985-10-15
Lucas Industries Public Limited Company
Automatic adjuster for shoe-drum brake

DE3228796A1
(en)

1982-08-02
1984-02-02
Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover
Automatic adjustment device for the brake lever of a brake

SE502201C2
(en)

1993-11-26
1995-09-18
Haldex Ab

Brake lever for an S-chamber drum brake on a road vehicle

US20040026193A1
(en)

2002-08-08
2004-02-12
Philpott Daniel J.
Slack adjuster torque limited manual adjustment

WO2018220639A1
(en)

2017-05-31
2018-12-06
Madras Engineering Industries Private Limited
An automatic slack adjuster

Family Cites Families (7)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

US3428154A
(en)

1967-10-23
1969-02-18
Carlodge Corp
Automatic brake slack adjuster

US3507369A
(en)

1967-12-28
1970-04-21
Eaton Yale & Towne
Adjuster for cam brake

US3526303A
(en)

1969-02-12
1970-09-01
Autoset Corp
Automatic brake slack adjuster

US3901357A
(en)

1974-07-01
1975-08-26
Bendix Corp
Automatic slack adjuster

US3949840A
(en)

1975-03-03
1976-04-13
Rockwell International Corporation
Cam brake automatic slack adjusting mechanism

US3990546A
(en)

1975-07-25
1976-11-09
Midland-Ross Corporation
Automatic adjuster for brakes

US3997036A
(en)

1975-09-09
1976-12-14
Borg-Warner Corporation
Automatic brake slack adjuster

1977

1977-03-31
US
US05/783,258
patent/US4094390A/en
not_active
Expired – Lifetime

1978

1978-03-10
GB
GB9652/78A
patent/GB1592109A/en
not_active
Expired

1978-03-30
SE
SE7803583A
patent/SE442432B/en
not_active
IP Right Cessation

1978-03-30
DE
DE19782813624
patent/DE2813624A1/en
active
Granted

Also Published As

Publication number
Publication date

SE442432B
(en)

1985-12-23

US4094390A
(en)

1978-06-13

SE7803583L
(en)

1978-11-02

DE2813624A1
(en)

1978-10-05

Información de contacto