WO2001036838A1 - Mecanisme de retour de plaque de friction - Google Patents

Mecanisme de retour de plaque de friction Download PDF

Info

Publication number
WO2001036838A1
WO2001036838A1 PCT/CA2000/001362 CA0001362W WO0136838A1 WO 2001036838 A1 WO2001036838 A1 WO 2001036838A1 CA 0001362 W CA0001362 W CA 0001362W WO 0136838 A1 WO0136838 A1 WO 0136838A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake shoe
link member
pin
housing
rotor disk
Prior art date
Application number
PCT/CA2000/001362
Other languages
English (en)
Inventor
Jean-Pierre Crevier
Benoit Raymond
Original Assignee
Newtech Brake Corporation 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 Newtech Brake Corporation Inc. filed Critical Newtech Brake Corporation Inc.
Priority to AU16830/01A priority Critical patent/AU1683001A/en
Priority to CA002427951A priority patent/CA2427951A1/fr
Publication of WO2001036838A1 publication Critical patent/WO2001036838A1/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
    • 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
    • F16D55/28—Brakes with only one rotating disc
    • F16D55/32—Brakes with only one rotating disc actuated by a fluid-pressure device arranged in or on the brake
    • F16D55/34—Brakes with only one rotating disc actuated by a fluid-pressure device arranged in or on 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/14—Mechanical
    • F16D2121/16—Mechanical for releasing a normally applied brake

Definitions

  • the present invention relates to a disk brake for vehicles and more particularly to improvements in friction plate return mechanisms for disengaging brake shoe from frictional contact with a rotor disk in the disk brake assembly.
  • the disk brake assembly for a vehicle as described in the applicant's PCT publication WO98/29671 generally includes a housing mounted to the vehicle, an annular rotor disk within the housing, and means mounting the disk to the wheel.
  • the disk has at least a first radial planar annular friction surface and the housing includes a first annular brake shoe provided adjacent the first friction surface of the disk.
  • the brake shoe is axially movable towards and away from the first friction surface and is restrained from rotating with the disk.
  • An annular fluid expandable bladder extends between the first annular brake shoe and a radial wall of the housing, so that upon expansion of the bladder the first brake shoe moves axially to frictionally engage the first friction surface of the disk.
  • means for disengaging the first brake shoe from frictional contact with the first friction surface of the rotor disk which is a rolling seal provided between an axially generated surface of the brake shoe and an axially generated cylindrical surface of the first radial wall of the housing such that the rolling seal can store energy when force is being applied on the brake shoe to frictionally engage the frictional surface of the rotor disk, and the stored energy is sufficient to retract the brake shoe from the first friction surface of the rotor disk when the applied force is removed from the brake shoe.
  • the disk brake works well. Improvements regarding the disengaging means, however, are desired because adjustment has to be done to compensate for the increasing of the travel distance of the brake shoe during a break action.
  • the increasing of the travel distance is a result of the wearing of the friction surface of the disk.
  • the rolling seal is more resiliently deformed to store more energy so that more braking force is needed to overcome the resistance from the deformed rolling seal.
  • a brake shoe return apparatus for a disk brake assembly wherein a rotor disk rotates in a housing about an axis and a brake shoe moves towards the rotor disk for frictional engagement therewith
  • the brake shoe return comprising: a link member slidable relative to the housing and in a to and fro direction parallel to the axis of rotation of the rotor disk and associatd with the brake shoe; resilient means associated with the link member for urging the link member away from the rotor disk; a connecting member to link the brake shoe with the link member and frictionally connected with the moving member to move the link member together with the brake shoe in a forward movement towards the rotor disk during a braking action when a forward pressure is applied to the brake shoe until the resilient means overcomes the forward pressure and returns the link member and the brake shoe to a position where the brake shoe is disengaged from the rotor disk.
  • a brake shoe return apparatus for a disk brake assembly wherein a rotor disk rotates in a housing about an axis and a brake shoe moves towards the rotor disk for frictional engagement therewith
  • the brake shoe return comprising: a link member slidable relative to the housing and in a to and fro direction parallel to the axis of rotation of the rotor disk and associatd with the brake shoe; resilient means associated with the link member for urging the link member away from the rotor disk; a friction device associated with the housing and slidable relative to the housing in the forward and rearward direction within a predetermined travel; the friction device being frictionally connected to the link member, the link member and the friction device permitting the link member to move together with the brake shoe in the forward direction during a brake action with little frictional resistance from the friction device when the friction device is restrained, while a maximum friction force in the opposite direction between the friction device and the link member prevents the link member from moving in the rearward direction relative to the friction device so that
  • the other retaining washer acting as the friction device surrounds the exterior of the pin and is contained within a chamber of the housing.
  • the periphery of the chamber is defined by a circumferentially extending groove, which receives the flat ring of the retaining washer.
  • the retaining washer is axially movable within the chamber and the axial movement is limited by the width of the groove. The retaining washer is moved together with the pin in the forward direction in a brake action until the flat ring abuts a front side of the groove, and permits the pin to slide through the retaining washer to continue the forward movement.
  • the retaining washer When the braking force is removed and the pin moves in the rearward direction under the spring force, the retaining washer is moved together with the pin in the rearward direction until the flat ring abuts the rear side of the groove to stop the rearward movement of the pin.
  • the spring force is never greater than the friction force between the finger members and the exterior of the pin and therefore, the finger members are able to grip the pin firmly and to stop the rearward movement.
  • Figure 1 is a partial sectional view of a disk brake incorporating a preferred embodiment of the invention
  • Figure 2 is an exploded perspective view of the embodiment in Figure 1 ;
  • Figure 3 is a front view of the retaining washer used in the embodiment in Figure 1 ;
  • Figure 4 is a cross-sectional view taken along line 4-4 in Figure 3;
  • Figure 5 is a perspective view, partly in cross- section of another embodiment of the present invention. Mode for Carrying Out the Invention
  • a friction plate return mechanism 10 is installed to a disk brake 14 for an automobile.
  • the disk brake 14 is not a part of the invention and many different types of disk brakes may incorporate the embodiment of the invention. Therefore, the disk brake is described merely with its basic structure to illustrate the braking operation of the disk brake using the friction plate return mechanism 10.
  • the disk brake 14 generally includes a housing 16 mounted to the automobile, an annular rotor disk 18 within the housing, and mounting member 20 for mounting the disk 18 to the wheel 22 of the automobile.
  • the disk 18 has at least a radial planar annular frictional surface 24 and the housing includes an annular brake shoe 26 provided adjacent the friction surface 18 of the disk.
  • the friction plate return mechanism 10 includes a cylindrical casing 34 and a pin 36 which are more clearly illustrated in Figure 2.
  • the cylindrical casing 34 is closed at the rear end 38 and has a central opening 40 at the front end 42.
  • the pin 36 is slidably received within the casing 34 and a front portion of the pin 36 protrudes forwardly from the central opening 40.
  • a spiral spring 44 is contained within a bigger chamber 46, and positioned between a front wall 48 of the chamber 46 and an enlarged pin head 50 such that the pin 36 is biased to a rear position in which the pin head 50 contacts the closed end 38 of the cylindrical housing.
  • An enlarged rear portion 52 of the pin 36 prevents the pin 36 from overprotruding forwardly from the cylindrical casing when it abuts the front wall 48 of the chamber 46.
  • a smaller chamber 54 is defined within the cylindrical casing 34 near the front end 42, and the central opening 40 extends axially through the chamber 54.
  • the retaining washer 56 or 58 is made from an integral metal plate having a central aperture.
  • the metal plate includes an annular outer section forming a flat ring 60 and an annular inner portion forming a plurality of finger members 62 which are circumferentially spaced apart from one another by a plurality of radially extending cuts 64.
  • the finger members 62 are bent in permanent deformation in one direction, which is referred to as a forward direction hereinafter.
  • the final opening 66 defined by the ends of the finger members 62 is slightly smaller than the exterior of the pin 36.
  • the finger members 36 are enabled to be resiliently deformed slightly to permit the pin 36 to be inserted from the rear side of the retaining washer 56 therethrough. However, if the pin 36 is to be moved in the rearward direction rela- tive to the retaining washer 56, the friction force between the exterior of the pin 36 of the finger members 62 is in a trend to move the ends of the finger members 62 together with the pin 36 to further grip the pin 36 and stop the movement thereof. When the pin 36 is moved in the rearward direction by a force greater than or equal to the maximum friction force between the exterior of the pin and the finger members, the retaining washer 56 or 58 is no longer able to stop the rearward movement of the pin 36.
  • the retaining washer 58 abuts the brake shoe backing plate 26a and engages a front portion of the pin 36 extending therethrough as shown in Figure 1.
  • the retaining washer 58 grips the pin 36 to move together with the backing plate 26a in the forward direction against the spring force applied on the pin head 50.
  • the spring force acting on the pin head 50 moves the pin 36 with retaining washer 58 to move the backing plate 26a rearwardly in order to disengage the brake lining 26b from frictional contact with the frictional surface 24.
  • the brake shoe 26 has to travel a longer distance from its original position to engage the frictional surface 24. That means the pin 36 would have to travel together with the backing plate 26a over a longer distance and the spring 44 would be more compressed to produce greater spring forces acting on the pinhead 50. Practically, the spring forces acting on the pin head 50 will never be greater than the maximum friction force between the retaining washer 58 and the pin 36 and therefore, the spring force is able to move the pin 36 together with the backing plate 26a in the rearward direction for disengagement from the friction surface 24.
  • the retention washers 156a, 156b, and 156c are located on pin 136 (at the place of the pin head 50 in the embodiment of Figure 1 to 4).
  • washers 156a serve both the purpose of the former pinhead 50 and the retaining washer 56.
  • the washers 156a, 156b and 156c are spaced apart by spacers 157a, 157b, 157c which in turn are contained within a cylindrical cage 151 with an annular radial wall 152.
  • the spring 144 abuts against the radial wall 152.
  • the multiple retaining washers 156a, 156b, 156c have limited axial travel within the cylindrical recess portion 168 in the housing 134.
  • the pin 136 When the brakes are released, the pin 136 will be withdrawn under the urging of the spring 144 thereby pulling back the backing plate and thus the brake liner from the friction surface of the disk brake. However, the pin will have advanced slightly in relation to the washers 156 and thus will not return fully to its initial position in the housing 134. Thus the pin 136 is in a position with the backing plate for travel with compensation for wear.

Landscapes

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

Abstract

La présente invention concerne un mécanisme de retour de patin de frein (10, 110) servant à dégager un patin de frein (26a, 26b) d'un contact de frottement avec un disque rotor dans un système de freinage de véhicule. Le mécanisme comprend un axe (36, 136) reçu de manière à pouvoir coulisser dans un boîtier (34, 134) qui est monté sur le véhicule. L'axe (36, 136) est placé dans une position arrière au moyen d'un ressort (44, 144) et est relié du point de vue des frottements au patin de frein (26) au moyen d'une rondelle d'arrêt (58, 158) permettant de déplacer le patin de frein (26) dans une direction arrière en s'éloignant du disque rotor (18) lorsqu'une force de freinage cesse de s'exercer à partir du patin de frein (26). Une autre rondelle d'arrêt (56, 156) est reçue à l'intérieur du boîtier et peut se déplacer axialement sur une distance prédéterminée. La rondelle d'arrêt (56, 156) est également reliée à l'axe (36, 136) du point de vue des frottements et permet à l'axe (36, 136) de se déplacer librement dans la direction frontale avec le patin de frein (26) durant une action de freinage, mais provoque l'arrêt de l'axe (36, 136) dans un mouvement arrière avec le patin de frein (26) excepté le mouvement avec la rondelle d'arrêt (56, 156) sur la distance prédéterminée.
PCT/CA2000/001362 1999-11-15 2000-11-15 Mecanisme de retour de plaque de friction WO2001036838A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU16830/01A AU1683001A (en) 1999-11-15 2000-11-15 Friction plate return mechanism
CA002427951A CA2427951A1 (fr) 1999-11-15 2000-11-15 Mecanisme de retour de plaque de friction

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CA 2289812 CA2289812A1 (fr) 1999-11-15 1999-11-15 Mecanisme de retour de lamelle de friction
CA2,289,812 1999-11-15

Publications (1)

Publication Number Publication Date
WO2001036838A1 true WO2001036838A1 (fr) 2001-05-25

Family

ID=4164620

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2000/001362 WO2001036838A1 (fr) 1999-11-15 2000-11-15 Mecanisme de retour de plaque de friction

Country Status (3)

Country Link
AU (1) AU1683001A (fr)
CA (1) CA2289812A1 (fr)
WO (1) WO2001036838A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008080962A1 (fr) * 2007-01-05 2008-07-10 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein à disque, notamment pour un véhicule utilitaire
WO2013143991A1 (fr) * 2012-03-26 2013-10-03 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein a disque

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1207766A (fr) * 1957-07-10 1960-02-18 Dunlop Sa Dispositif de réglage par accroissements infiniment petits et frein muni d'un tel dispositif
US3815716A (en) * 1973-03-19 1974-06-11 Gen Motors Corp Automatic piston adjuster
US4382491A (en) * 1980-08-11 1983-05-10 Hurst Performance, Inc. Drag free disc brake assembly having automatically adjusting caliper
EP0478947A1 (fr) * 1990-10-04 1992-04-08 Knorr-Bremse Ag Frein à disque, notamment frein à disque multiples pour véhicules ferroviaires
US5465816A (en) * 1994-07-20 1995-11-14 Westinghouse Air Brake Company Slack adjusting brake cylinder for a brake unit on a railway transit vehicle
WO1998029671A1 (fr) 1996-12-31 1998-07-09 Yvon Rancourt Ensemble frein a disque ameliore
WO1998032989A1 (fr) * 1997-01-24 1998-07-30 John Woollams Dispositif de reglage automatique pour mecanismes utilisant l'energie de ressort

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1207766A (fr) * 1957-07-10 1960-02-18 Dunlop Sa Dispositif de réglage par accroissements infiniment petits et frein muni d'un tel dispositif
US3815716A (en) * 1973-03-19 1974-06-11 Gen Motors Corp Automatic piston adjuster
US4382491A (en) * 1980-08-11 1983-05-10 Hurst Performance, Inc. Drag free disc brake assembly having automatically adjusting caliper
EP0478947A1 (fr) * 1990-10-04 1992-04-08 Knorr-Bremse Ag Frein à disque, notamment frein à disque multiples pour véhicules ferroviaires
US5465816A (en) * 1994-07-20 1995-11-14 Westinghouse Air Brake Company Slack adjusting brake cylinder for a brake unit on a railway transit vehicle
WO1998029671A1 (fr) 1996-12-31 1998-07-09 Yvon Rancourt Ensemble frein a disque ameliore
WO1998032989A1 (fr) * 1997-01-24 1998-07-30 John Woollams Dispositif de reglage automatique pour mecanismes utilisant l'energie de ressort

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008080962A1 (fr) * 2007-01-05 2008-07-10 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein à disque, notamment pour un véhicule utilitaire
US8944221B2 (en) 2007-01-05 2015-02-03 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Disk brake for a commercial vehicle
WO2013143991A1 (fr) * 2012-03-26 2013-10-03 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein a disque
US9382957B2 (en) 2012-03-26 2016-07-05 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Disc brake

Also Published As

Publication number Publication date
CA2289812A1 (fr) 2001-05-15
AU1683001A (en) 2001-05-30

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