WO2002066852A1 - Compensateur d'usure de freins - Google Patents

Compensateur d'usure de freins Download PDF

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Publication number
WO2002066852A1
WO2002066852A1 PCT/CA2002/000217 CA0200217W WO02066852A1 WO 2002066852 A1 WO2002066852 A1 WO 2002066852A1 CA 0200217 W CA0200217 W CA 0200217W WO 02066852 A1 WO02066852 A1 WO 02066852A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake shoe
brake
disc
axially
annular
Prior art date
Application number
PCT/CA2002/000217
Other languages
English (en)
Inventor
Yvon Rancourt
Original Assignee
Group Newtech International Inc.
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 Group Newtech International Inc. filed Critical Group Newtech International Inc.
Priority to CA002475452A priority Critical patent/CA2475452A1/fr
Priority to EP02702190A priority patent/EP1409885A1/fr
Priority to US10/468,650 priority patent/US20040112688A1/en
Publication of WO2002066852A1 publication Critical patent/WO2002066852A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • 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
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
    • F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake
    • F16D55/42—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake comprising an expansible fluid-filled flexible member coaxial with the brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F16D65/186—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with full-face force-applying member, e.g. annular
    • 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
    • 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
    • F16D65/44—Slack adjusters mechanical non-automatic by means of direct linear adjustment
    • 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
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/1304—Structure
    • F16D2065/1328—Structure internal cavities, e.g. cooling channels
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/14—Fluid-filled flexible members, e.g. enclosed air bladders

Definitions

  • the present invention relates to disc brakes and more particularly to improvements for wear compensation in large area contact disc brakes for vehicles.
  • the disc brake of the present invention is a disc brake of the type described in United States patent No. 5,330,034 issued July 19, 1994 and United States patent RE 35055 issued October 10, 1995 referring to full annular disc brakes for large vehicles such as trucks.
  • the concept of the full annular disc brake is also proposed for automobiles and light trucks and the applicant describes a structure of a full annular disc brake for such vehicles in the applicant's PCT patent application PCT/CA97/01014, entitled IMPROVED DISC BRAKE ASSEMBLY and published as WO98/29671 in the inventor's name, Rancourt on July 9, 1998.
  • the disc brake assembly for a vehicle as described in the applicant's PCT application WO98/29671 generally includes a housing mounted to the vehicle, an annular rotor disc within the housing, and means for mounting the disc to the wheel.
  • the disc has at least a first radial planar annular friction surface and the housing includes a first annular brake shoe provided adjacent to the first friction surface of the disc.
  • the brake shoe is axially moveable towards and away from the first friction surface and is restrained from rotating with the disc.
  • An annular fluid expandable bladder extends between the first annular brake shoe and a radial wall ofthe housing, so that upon expansion of the bladder the first brake shoe moves axially to frictionally engage the first friction surface of the disc.
  • the travel distance ofthe brake shoe increases as a result ofthe wearing ofthe friction surface of the disc and the brake shoe. The longer distance the brake shoe travels, the more time is needed to react to a brake action and fully stop the vehicle. Therefore, the travel distance of the brake shoe must be adjusted to an acceptable range when the wearing exceeds the range.
  • a disc brake assembly for a vehicle wheel generally includes a housing, at least first and second annular brake shoes, and at least a rotor disc co-axially mounted to the wheel and axially moveable with respect to the wheel.
  • the second brake shoe is adapted to move axially towards the rotor disc and further press the rotor disc against the first brake shoe, resulting in respective frictional engagement between the rotor disc and the first brake shoe, and between the rotor disc and the second brake shoe.
  • the disc brake housing of the assembly comprises an annular radial wall for supporting the first annular brake shoe thereto, and a plurality of link members extending axially from an external periphery of the annular radial wall for detachably connecting an annular radial support structure mounted to the vehicle and housing the rotor disc and the brake shoes.
  • the securing means preferably comprises an elongated aperture defined in the distal end of each link member and extending radially therethrough.
  • a plurality of elongated mounting keys each having a mounting bore extending therethrough for receiving a mounting screw.
  • the mounting bore is offset from a center of the key and the elongated mounting keys are adapted for insertion into the respective elongated apertures in either one of opposite orientations so that the mounting bores are adapted to be selectively located in two different axial positions with respect to the housing.
  • the disc brake housing is originally assembled with the mounting bores more distal from the annular radial wall of the housing. After the rotor disc and the brake shoes or the brake pads attached thereto become thinner as a result of wear, leaving a longer axial distance for moving parts to travel, the elongated mounting keys, therefore, are reinserted into the respective elongated apertures in the opposite orientation to have the mounting bores located less far away from the annular radial wall so that the axial space between the annular radial wall and the annular radial support structure is smaller. The smaller axial space between the annular radial wall and the radial support structure makes the travel distance of the moving parts shorter and therefore the adjustment is achieved.
  • a disc brake assembly for a vehicle wheel includes a housing; at least first and second annular brake shoes; at least a rotor disc having first and second annular radial planar friction surfaces substantially parallel to each other, the rotor disc being co-axially mounted to the wheel and axially moveable with respect to the wheel; means for restraining the first brake shoe from rotating with the rotor disc; means for restraining the second brake shoe from rotating with the rotor disc; and an annular fluid expandable bladder, whereby upon expansion ofthe bladder the second brake shoe moves axially towards the rotor disc and further presses the rotor disc against the first brake shoe, resulting in respective frictional engagement between the first friction surface of the rotor disc and the first brake shoe, and between the second friction surface of the rotor disc and the second brake shoe.
  • the housing comprises an annular radial wall operatively supporting the first annular brake shoe adjacent to the first friction surface of the rotor disc; an annular radial support wall adapted to be mounted to a frame of the vehicle and operatively supporting the bladder and the second annular brake shoe adjacent to the second friction surface ofthe rotor disc; and means for connecting the annular radial wall to the annular radial support wall in an axially and selectively spaced relationship.
  • the connecting means preferably comprises a plurality of link members extending axially from an external periphery of the annular radial wall.
  • the link members are preferably equally and circumferentially spaced apart from one another.
  • Each link member preferably includes a distal end having a mounting bore radially extending therethrough for receiving a mounting screw. An axial position of the mounting bore is selectively determined when the link members are connected to the annular radial support wall.
  • a disc brake assembly for a vehicle wheel comprises a first annular brake shoe; a first rotor disc co-axially mounted to the wheel, axially spaced apart from the first brake shoe and axially moveable with respect to the wheel; a second annular brake shoe axially spaced apart from the first rotor disc; a second rotor disc co-axially mounted to the wheel, axially spaced apart from the second brake shoe and axially moveable with respect to the wheel; and a third annular brake shoe axially spaced apart form the second rotor.
  • An annular expandable bladder is provided and adapted to move the third brake shoe, second rotor, second brake shoe and second rotor axially towards the first brake shoe upon expansion of the bladder during a brake action, resulting in frictional engagement between the first brake shoe and the first rotor, the first rotor and the second brake shoe, the second brake shoe and the second rotor and the second rotor and the third brake shoe respectively.
  • a housing is provided to house the brake shoes and rotor discs. The housing has an annular radial wall for operatively supporting the first brake shoe and an annular radial support wall adapted to be mounted to a frame of the vehicle for operatively supporting the third brake shoe.
  • Also included in the housing is a means for connecting the annular radial wall to the annular radial support wall in an axially and selectively spaced relationship to adjust an axial space between the annular radial wall and the annular radial support wall so that the travel distance of the axially moveable brake shoes and rotor discs of the disc assembly is adapted to be reduced in order to compensate for wear of friction surfaces ofthe brake shoes.
  • the connecting means preferably comprises a plurality of link members extending axially from an external periphery of the annular radial wall and equally and circumferentially space apart from one another.
  • Each link member has an elongated aperture defined at a distal end thereof and extending radially therethrough.
  • a plurality of elongated mounting keys each having a mounting bore extending through the key for receiving a mounting screw are adapted for insertion into the respective elongated apertures.
  • the mounting bore is offset from a center of the key so that the mounting bores are adapted to be selectively located in two different axial positions with respect to the housing when each key is inserted in the bore in opposite orientations.
  • the disc brake assembly further, preferably comprises means for inhibiting relative rotation between the third brake shoe and the annular radial support wall, and between the third and second brake shoes while permitting relative and axial movement therebetween respectively.
  • a means is also preferably provided for inhibiting the first brake shoe from rotation with respect to the housing.
  • the present invention advantageously provides a very simple structure of the housing to enable the housing to have selective axial spaces for adjusting the travel distance of the axially moving parts of the disc brake assembly to compensate for wear.
  • the adjustment structure is very reliable because there are no moving parts needed for the adjustment.
  • the adjusted length is dependent on the distance between the center of the bore and the center of the elongated key which can be predetermined within a wide range with no restrictions. This is particularly good for a multiple disc brake assembly which has more than one rotor disc because the more friction surfaces the disc brake assembly has, the longer distance might be necessarily adjusted.
  • the cost to incorporate the adjustable feature for wear compensation is inexpensive.
  • Fig. 1 is a partial, longitudinally cross-sectional view of a disc brake assembly incorporating a preferred embodiment ofthe invention
  • Fig. 2 is a perspective view of a disc brake housing in accordance with the preferred embodiment in Fig 1 ;
  • Fig. 3 is a partial front view of Fig. 1, showing the supportive relationship between the first brake shoe and an annular radial wall ofthe housing;
  • Fig. 4 is a partial rear view of Fig. 1 , showing the connection of link members of the housing to an annular radial support wall and the supportive relationship between the annular radial support wall and the second and third brake shoes;
  • Fig. 5 is a partial view taken from a direction indicated by arrow P in Fig. 3, showing an original axial location ofthe mounting bores;
  • Fig. 6 is the same view illustrated in Fig. 5, showing the adjusted axial location ofthe mounting bores to compensate for wear;
  • Fig. 7 is a partial cross-sectional view of a key inserted into the aperture of the link member according to another embodiment ofthe invention.
  • Fig. 8 is a partial, longitudinally cross-sectional view of a disc brake assembly incorporating another preferred embodiment ofthe invention.
  • Fig. 9 is a partial top view of Fig. 8, showing the engagement of a fork member ofthe second brake shoe with an axial member ofthe third brake shoe;
  • Fig. 10 is a partial cross-sectional view taken along lines B-B in Fig. 9, appearing on the sheet of Fig. 8;
  • Fig. 11 is a partial, longitudinally cross-sectional view of a disc brake assembly incorporating a further preferred embodiment ofthe invention.
  • Fig. 12 is a partial top view of Fig. 11, appearing on the sheet of Fig. 9 and showing the engagement between the axial members of the second and third brake shoes.
  • the disc brake assembly 10 for an automobile wheel (not shown) is illustrated having a housing 12.
  • the housing 12 has an annular radial wall 14 and a plurality of link members 16 extending axially from an external periphery of the annular radial wall 14.
  • the link members 16 are equally and circumferentially spaced apart from one another.
  • Supportive portions 18 are provided between adjacent link members 16, connecting the external periphery of the annular radial wall 14 to increase the strength and solidity of the connection between the link members 16 and the annular radial wall 14.
  • the housing 12 including the annular radial wall 14, the link members 16 and the supportive portions 18 is integrally made from casting metal.
  • the annular radial wall 14 has a substantially flat inner surface 20 and a smoothly curved outer surface 22.
  • a plurality of openings 24 axially extending through the annular radial wall 14 and equally, circumferentially spaced apart from one another.
  • Each link member 16 includes a distal end 26 having an elongated aperture 28 (shown in Fig. 2) radially extending therethrough.
  • the elongated apertures 28 are axially oriented, each having an axially extending longitudinal axis.
  • a first annular brake shoe 30 includes an annular axial section 32 and an annular radial section 34 extending outwardly from the axial section 32.
  • a plurality of axially protruding members 34 that are equally and circumferentially spaced apart from one another and received in the respective openings 24 (see Fig. 3) when the first annular brake shoe 30 is supported to the annular radial wall 14 with the axial section 32 resting on an inner edge 36 of the annular radial wall 14.
  • a plurality of radially extending grooves 38 and 40 are provided on the outer surfaces of the respective axial section 32 and the axially protruding members 34 to increase the air contacting surfaces of the first brake shoe 30 for a better cooling solution.
  • the radial section 34 of the first annular brake shoe 30 has an annular inner planar surface 42 on which an annular brake pad 44 is securely attached by any well known mechanism.
  • a rotor disc 46 Adjacent to the first brake shoe 30 is a rotor disc 46 which is co-axially mounted to the wheel of the vehicle and axially moveable with respect to the wheel, which is well known.
  • the rotor disc 46 includes first and second annular planar friction surfaces 48 and 50 that are parallel to each other and perpendicular to the rotation axis ofthe wheel.
  • the brake pad 44 is also perpendicular to the rotation axis of the wheel so that the first annular radial planar friction surface 48 is parallel to the first annular brake pad 44 while slightly and axially spaced apart therefrom.
  • a circumferentially extending groove 52 is provided around the rotor disc 46 to improve the cooling condition of the rotor disc.
  • a second or intermediate annular brake shoe 54 includes a radial section 56 having first and second annular radial planar surfaces 58 and 60, parallel to each other.
  • a pair of annular brake pads 62 and 64 are securely attached to the surfaces 58 and 60 respectively, by any well-known means.
  • the second or intermediate annular brake shoe 54 is positioned adjacent to the first rotor disc 46 at the side opposite to the first brake shoe 30 so that the annular brake pad 62 is parallel to and slightly spaced apart from the annular radial planar friction surface 50 of the first rotor disc.
  • a plurality of axial legs 66 extend axially from the external periphery of the radial section 56 and are equally and circumferentially spaced apart from one another as shown in Figs. 1 and 4.
  • a second rotor disc 68 Adjacent to the second or intermediate annular brake shoe 54 and at the side opposite to the first rotor disc 46 is a second rotor disc 68. Similarly to the first rotor disc 46, the second rotor disc 68, is co-axially mounted to the wheel of the vehicle and axially moveable with respect to the wheel.
  • Parallel annular radial planar friction surfaces 70 and 72 are perpendicular to the rotation axis of the wheel and a circumferentially extending groove 74 is provided around the rotor disc to improve the cooling condition of the second rotor disc 68.
  • the annular radial planar friction surface 70 is parallel to the brake pad 64 and slightly spaced apart therefrom.
  • a third annular brake shoe 76 is placed adjacent to the second rotor disc 68, at the side opposite to the second or intermediate annular brake shoe 54.
  • the third annular brake shoe 76 includes a radial section 78 having at opposite sides, two parallel annular radial planar surfaces 80 and 82.
  • An annular brake pad 84 is securely attached to the surface 80 by any well-known means so that the brake pad 84 is parallel to the annular radial planar friction surface 72 of the second rotor disc 68 and slightly spaced apart therefrom.
  • a plurality of axial members 84 radially protrude, axially extend from an external periphery of the radial section 78 and are equally and circumferentially spaced apart, as shown in Figs. 1 and 4.
  • a recess 86 is provided on an external surface of each axial member 84 and axially extends through the entire axial member.
  • the number of the axial members 84 and the size of the recesses 86 correspond to those of the axial legs 66 of the second or intermediate annular brake shoe 54 so that the axial legs 66 are slidably engaged in the respective recesses of the third annular brake shoe 76. Therefore, the second brake shoe 54 is radially supported to the third brake shoe 76 and a relative axial movement therebetween is permitted but relative rotation is restrained.
  • a plurality of axial grooves 88 and 90 are provided on the external surface of each axial leg 66 and each axial member 84 (see Fig. 4) to increase air contacting surfaces of the second and third annular brake shoe, resulting in a better cooling solution.
  • annular radial support wall 92 is provided in order to hold the disc brake assembly 10 together.
  • the annular radial support wall 92 is adapted to be mounted on a frame of the vehicle and have a first group of grooves 94 extending axially on the external periphery thereof and equally circumferentially spaced apart from one another, as shown in Fig. 4, to receive the respective axial legs 16 of the housing 12.
  • Each axial leg 16 of the housing 12 has an elongated aperture 96 having its longitudinal axis extending axially, as shown in Fig. 5.
  • An elongated key 98, sized and shaped correspondingly to the elongated aperture 96 is inserted into the aperture 98.
  • a mounting bore 100 is defined in the elongated key 98, radially extending through the key for receiving a mounting screw 102 (shown in Figs. 1 and 4) that is threadably secured to the annular radial support wall 92.
  • the position ofthe center ofthe mounting bore 100 is on the longitudinal central line ofthe key 98, and offset a distance marked A in Fig. 5 from the center of the elongated key 98.
  • the key 98 is oriented so that the mounting bore 100 is offset from the center of the key 98 towards the distal edge of the axial leg 16.
  • the annular radial support wall 92 includes a second group of grooves 104 extending axially on the external periphery of the annular radial support wall 92 and equally circumferentially spaced apart to slidably receive the respective axial members 84 of the third annular brake shoe 76 with the respective axial legs 66 of the second or intermediate annular brake shoe 54 slidably engaged thereto (see Fig. 4). Therefore, the second and third brake shoes 54 and 76 are radially supported to the annular radial support wall 92.
  • An annular expandable bladder 106 is placed between the annular radial support wall 92 and the radial section 78 of the third annular brake shoe 76.
  • the bladder 106 moves the third annular brake shoe towards the second rotor disc 68.
  • the second rotor disc 68 begins to move towards the second or intermediate annular brake shoe 54 when the second rotor disc is pressed by the third annular brake shoe 76.
  • the second or intermediate annular brake shoe 54 and the first rotor disc 46 are pressed to move towards the first annular brake shoe 30 until a complete frictional engagement occurs between the brake pad 44 and the annular radial planar friction surface 48, the annular radial planar friction surface 50 and the brake pad 62, the brake pad 64 and the annular radial planar friction surface 70, the annular radial planar friction surface 72 and the brake pad 84 while the first brake shoe is firmly pressed against the inner surface 20 of the annular radial wall 14 of the housing 12.
  • the first brake shoe 30 is inhibited from rotation by the annular radial wall 14 through the axially protruding members 34, and the second and third brake shoes are restrained from rotation by the annular radial support wall 92 through the respective axial legs 16 and axial members 84 so that the frictional engagement between the brake shoes and rotor discs will eventually stop the rotation of the rotor discs and bring the vehicle to a full stop.
  • the complete frictional engagement is achieved, relative frictional movement exists between each brake pad and the corresponding friction surface of the rotor discs which produces heat energy and causes wearing of the break pads. Therefore, each brake pad will become thinner and leave more axial distance for the moving parts of the brake to travel after a certain extent of the brake wearing is done. That means, more time is needed to bring the vehicle to a full stop when the driver applies the brakes.
  • the disc brake assembly 10 is adapted to adjust the travel distance of the moving parts of the brake. After the travel distance reaches a predetermined extent, the mounting screws 102 are removed. Therefore, the elongated keys 98 can be removed from the elongated apertures 96 and reinserted into the apertures 96 with an opposite orientation so that the mounting bores 100 are located on the other end of the elongated apertures 96, located a longer distance away from the distal edge of the axial leg 16 as shown in Fig. 6. As indicated in Figs. 5 and 6, the distance between the center of the mounting bore 100 and the center of the key 98 is A, and therefore, the axial position of the mounting bore 100 is moved a distance 2A inwardly from its original position.
  • the annular radial support wall 92 must be moved a distance 2 A inwardly in order to align the mounting bores 100 with the corresponding mounting bores (not shown) in the annular radial support walls 92 to reattach the mounting screws 102 so that the axial distance between the annular radial wall 14 and the annular radial support wall 92 is reduced by 2 A.
  • the distance A is predetermined when the disc brake assembly 10 is designed and manufactured.
  • Fig. 7 illustrates an alternative embodiment of the key 98 that is indicated as 98a and includes a top portion greater than the elongated aperture 96 to form a shoulder 106 around the key 98a.
  • the top portion of the key 98a is left above the aperture 96 that is easily gripped for removal.
  • Figs. 8, 9 and 10 illustrate a disc brake assembly 110 according to another preferred embodiment.
  • the disc brake assembly has structures similar to the disc brake assembly 10 shown in Fig. 1.
  • the similar parts identified by the same numerals indicated in Fig. 1 are not redundantly described.
  • the disc brake assembly 110 has a different structural arrangement for inhibiting the rotation of second and third brake shoes and an improved bladder system.
  • a third annular brake shoe 112 includes an annular radial section 114 having at opposite sides, two parallel annular radial planar surfaces 116 and 118.
  • the annular brake pad 84 is securely attached to the surface 116 so that the brake pad 84 is parallel to the annular radial planar friction surface 72 of the second rotor disc 68 and slightly spaced apart therefrom.
  • the third brake shoe 112 further includes an annular axial section 120 to form an external periphery of the third brake shoe 112, which is more clearly shown in Fig. 10.
  • a plurality of axial members 122 protrude radially and axially from the annular axial section 120, being equally and circumferentially spaced apart, as shown in Figs. 9 and 10.
  • the axial members 122 at their rearward end slidably fit into the respective axial grooves 104 which are located on the periphery of the annular radial support wall 92, more clearly shown in Fig. 4, whereby the third brake shoe 112 is restrained from rotation relative to the housing 12 while permitted axial movement thereto. With such a structure, the third brake shoe 112 is radially supported on the annular radial support wall 92.
  • a plurality of axial grooves 124 are provided on the external surface of each axial member 122 for a better cooling solution.
  • a plurality of fork members 126 protrude radially, extend axially from the external periphery ofthe second brake shoe 54 and are circumferentially spaced apart from one another.
  • Each of the fork members 126 includes two axial legs 128 slidably engaging a front end of a corresponding one of the axial members 122, whereby the second brake shoe 54 is restrained from rotation relative to the third brake shoe 112 but permitted axial movement with respect to both the housing 12 and the third brake shoe 112.
  • Each fork member 126 has a width fitting in the space between two adjacent link members 16 of the housing 12 and the axial legs 128 of the fork member 126 are supported on the annular axial section 122 of the third brake shoe 112.
  • the disc brake assembly 110 incorporates an improved bladder system which is described in the applicant's co-pending patent application entitled FLEXIBLE
  • An annular expandable bladder 130 is adapted to axially compress an annular piston member 139 which has a hollow structure defining an inner annular space 134 therein, and protruding axially from the radial section 114 of the third brake shoe 112.
  • An annular thermal insulator 136 is disposed between the radial section 114 of the third brake shoe 112 and the annular piston member 132.
  • a plurality of bores are preferably provided, extending through the annular piston member 132 to communicate with the inner annular space 134 and the outside ofthe annular piston member 132.
  • Figs. 11 and 12 illustrate a further preferred embodiment ofthe invention, as indicated at numeral 210.
  • the disc brake assembly 210 is similar to the embodiment 10 shown in Fig. 1 and the identical parts indicated by the same numerals are not redundantly described.
  • the improved bladder system of the disc brake assembly 210 is identical to that of the disc brake assembly 110 shown in Fig. 8 which is indicated by the same numerals and not redundantly described.
  • the third brake shoe 112 has a plurality of axial members 138 circumferentially spaced apart from one another.
  • Each axial member 138 includes a first section 140 protruding radially and extending axially and rearwards from the annular axial section 120 of the third brake shoe 112, and a second section 142 extending axially. and forwardly from the external periphery of the third brake shoe 112.
  • a plurality of axial grooves 144 are provided on the external surface of the first section 140 of the axial member 138 to increase air contact areas for a better cooling solution.
  • the second section 142 of the axial member 138 has a recessed end as shown in Fig. 12 to reduce the weight thereof.
  • the second brake shoe 54 has a plurality of axial members 146 extending rearwards and axially from the external periphery thereof, and circumferentially spaced apart from one another to slidably engage the second sections 142 of the axial members 138 of the third brake shoe 112, whereby the relative rotation between the second and third brake shoes 54 and 112 is inhibited but axial movement therebetween is permitted.
  • the rearward end of the first section 140 of the axial member 138 of the third brake shoe 112 is slidably received in the grooves 104 of the annular radial support wall 92 to inhibit the third brake shoe 112 from rotation but permit axial movement thereof with respect to the housing 12.
  • the axial members 146 of the second brake shoe are disposed in a circumferential position having a diameter smaller than the diameter of the circumferential position of the link members 16 of the housing 12 so that the axial members 146 of the second brake shoe 54 is contained within the cylindrical space defined by the interior surface of the link members 16 of the housing 12, and radially supported on the inner surface ofthe link members 16.

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

Abstract

Un ensemble freins à disque (10) comprend un corps (12) monté sur un véhicule et deux disques à rotor montés sur une roue du véhicule. Trois sabots de frein annulaires (30, 54, 76) sont supportés de manière fonctionnelle par le corps (12) et une structure de support du véhicule. Les disques à rotor et deux des sabots de frein annulaires sont conçus pour se déplacer axialement vers un sabot de frein limité axialement afin de venir en contact par friction lors du freinage. Le corps (12) comprend une paroi radiale annulaire (14) et une pluralité d'éléments de liaison axiaux (16) espacés les uns des autres sur la circonférence. Les éléments de liaison (16) sont fixés à la structure de support du véhicule à l'aide de vis de fixation (102) accueillies dans des trous (110). Chaque trou de fixation (100) s'étend radialement dans une clé allongée (98) et est décalé du centre de la clé. La clé allongée (98) est adaptée pour être insérée dans des orientations opposées d'un orifice allongé formé dans l'extrémité distale de l'élément de liaison axial (16) du corps (12) de sorte que la position axiale des trous de fixation (100) soit sélectionnée. La structure simple du corps (12) permet d'effectuer un réglage pour réduire le déplacement des pièces mobiles et compenser l'usure. Cette solution de compensation d'usure est fiable et bon marché.
PCT/CA2002/000217 2001-02-21 2002-02-21 Compensateur d'usure de freins WO2002066852A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CA002475452A CA2475452A1 (fr) 2001-02-21 2002-02-21 Compensateur d'usure de freins
EP02702190A EP1409885A1 (fr) 2001-02-21 2002-02-21 Compensateur d'usure de freins
US10/468,650 US20040112688A1 (en) 2002-02-21 2002-02-21 Brake wear compensator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US26986501P 2001-02-21 2001-02-21
US60/269,865 2001-02-21

Publications (1)

Publication Number Publication Date
WO2002066852A1 true WO2002066852A1 (fr) 2002-08-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2002/000217 WO2002066852A1 (fr) 2001-02-21 2002-02-21 Compensateur d'usure de freins

Country Status (3)

Country Link
EP (1) EP1409885A1 (fr)
CA (1) CA2475452A1 (fr)
WO (1) WO2002066852A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1695738A2 (fr) * 2005-02-25 2006-08-30 Hitachi, Ltd. Portique rotatif pour en système de thérapie par faisceau de particules
WO2007053330A1 (fr) * 2005-10-31 2007-05-10 Warner Electric Technology Llc Ensemble frein refroidi par liquide
WO2008116651A1 (fr) * 2007-03-27 2008-10-02 Pintsch Bubenzer Gmbh Élément d'écartement et dispositif de freinage
US8776955B2 (en) 2007-02-02 2014-07-15 Warner Electric Technology Llc Liquid cooled brake with support columns
CN116890569A (zh) * 2023-09-11 2023-10-17 江苏东之宝车业股份有限公司 一种一体化鼓式刹车可调式轮毂

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1151193A (en) * 1965-05-21 1969-05-07 Verlinde Sa Improvements in or relating to Electromagnetic Disc Brakes for Electric Motors
DD148250A1 (de) * 1979-12-21 1981-05-13 Heinrich Gebers Elektromagnetisch schaltbare reibungsbremse
EP0801246A2 (fr) * 1991-06-20 1997-10-15 RANCOURT, Claude Frein
US5685398A (en) * 1996-06-28 1997-11-11 Rexnord Corporation Fast response adjustable brake
WO2000031432A1 (fr) * 1998-11-20 2000-06-02 Pintsch Bamag Antriebs- Und Verkehrstechnik Gmbh Frein pour reglage du jeu

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1151193A (en) * 1965-05-21 1969-05-07 Verlinde Sa Improvements in or relating to Electromagnetic Disc Brakes for Electric Motors
DD148250A1 (de) * 1979-12-21 1981-05-13 Heinrich Gebers Elektromagnetisch schaltbare reibungsbremse
EP0801246A2 (fr) * 1991-06-20 1997-10-15 RANCOURT, Claude Frein
US5685398A (en) * 1996-06-28 1997-11-11 Rexnord Corporation Fast response adjustable brake
WO2000031432A1 (fr) * 1998-11-20 2000-06-02 Pintsch Bamag Antriebs- Und Verkehrstechnik Gmbh Frein pour reglage du jeu

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1695738A2 (fr) * 2005-02-25 2006-08-30 Hitachi, Ltd. Portique rotatif pour en système de thérapie par faisceau de particules
EP1695738A3 (fr) * 2005-02-25 2007-04-04 Hitachi, Ltd. Portique rotatif pour en système de thérapie par faisceau de particules
US7372053B2 (en) 2005-02-25 2008-05-13 Hitachi, Ltd. Rotating gantry of particle beam therapy system
WO2007053330A1 (fr) * 2005-10-31 2007-05-10 Warner Electric Technology Llc Ensemble frein refroidi par liquide
US7591349B2 (en) 2005-10-31 2009-09-22 Warner Electric Technology Llc Liquid cooled brake assembly
US8776955B2 (en) 2007-02-02 2014-07-15 Warner Electric Technology Llc Liquid cooled brake with support columns
WO2008116651A1 (fr) * 2007-03-27 2008-10-02 Pintsch Bubenzer Gmbh Élément d'écartement et dispositif de freinage
CN116890569A (zh) * 2023-09-11 2023-10-17 江苏东之宝车业股份有限公司 一种一体化鼓式刹车可调式轮毂
CN116890569B (zh) * 2023-09-11 2023-11-28 江苏东之宝车业股份有限公司 一种一体化鼓式刹车可调式轮毂

Also Published As

Publication number Publication date
CA2475452A1 (fr) 2002-08-29
EP1409885A1 (fr) 2004-04-21

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