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WO2005038287A1 - Systeme de compensation d'usure destine a un ensemble de frein a disque - Google Patents

Systeme de compensation d'usure destine a un ensemble de frein a disque Download PDF

Info

Publication number
WO2005038287A1
WO2005038287A1 PCT/CA2004/001863 CA2004001863W WO2005038287A1 WO 2005038287 A1 WO2005038287 A1 WO 2005038287A1 CA 2004001863 W CA2004001863 W CA 2004001863W WO 2005038287 A1 WO2005038287 A1 WO 2005038287A1
Authority
WO
WIPO (PCT)
Prior art keywords
disk brake
sprocket
wear compensation
push plate
assembly
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CA2004/001863
Other languages
English (en)
Inventor
Alain Constans
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.)
GROUPE NEWTECH INTERNATIONAL Inc
Original Assignee
GROUPE 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 GROUPE NEWTECH INTERNATIONAL Inc filed Critical GROUPE NEWTECH INTERNATIONAL Inc
Publication of WO2005038287A1 publication Critical patent/WO2005038287A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16D65/58—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with eccentric or helical body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—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
    • 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
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/66—Wedges

Definitions

  • This invention is concerned with a wear compensation system for a full contact annular disk brake assembly. It also relates to a method for compensating the wear in a full contact annular disk brake assembly.
  • a wear compensation system for a full contact annular disk brake assembly, the disk brake assembly comprising an annular actuator and an annular disk brake pad support, both coaxially located around a central axis, the wear compensation system comprising an annular push plate to be coaxially mounted around the central axis and set between the annular actuator and the annular disk brake pad support, the push plate comprising at least two ramps projecting towards the disk brake support; a wear compensation assembly having a cavity rigidly connected to a fixed location, and a second end operatively engaged to the push plate; characterized in that the wear compensation assembly comprises a sprocket located in the casing, the sprocket having a plurality of oblique teeth, and a spring-biased follower including a plurality of teeth in mesh with the oblique teeth of the sprocket, the sprocket being operatively connected to the push plate, whereby the sprocket rotates and causes the push plate
  • FIG. 1 is a perspective view of a full contact annular disk. brake assembly in accordance with a preferred embodiment of the present invention
  • FIG. 2 is an exploded view showing half of the disk brake assembly shown in Fig. 1 ;
  • FIG. 3 is a partial schematic view of a rack and pinion arrangement used in the preferred embodiment for the wear compensation assembly
  • FIG. 4 is an enlarged and partially exploded view of the wear compensation assembly, including the wear compensation plate;
  • FIG. 5 is a view similar to Fig. 4, showing the parts from another perspective;
  • FGI 6. is a view similar to Fig. 4, showing the parts from yet another perspective;
  • FIG. 7 is the perspective side view of the wear compensation assembly
  • FIG. 8 is a view similar to Fig. 7, taken from another perspective.
  • FIG. 1 shows a disk brake assembly (10) in accordance with one possible embodiment of the present invention.
  • the illustrated disk brake assembly (10) is designed to be used on a large truck or bus with a pneumatic braking system. Slightly different versions can be designed for other kinds of vehicles, including vehicles with a hydraulic braking system.
  • the disk brake assembly (10) comprises a central hub (14). This central hub (14) includes a side flange (12) which supports a number of mounting bolts (18) provided to secure the corresponding wheel or wheels to the vehicle (not shown).
  • the disk brake assembly (10) also comprises an external housing (22), which includes an external cover (20).
  • a rotor disk (30) is slidably mounted around the hub (14) between the external cover (20) and the bottom of the remainder of the housing (22).
  • the rotor disk (30) is essentially a radial disk or, preferably, a pair of disks between which ventilation channels are provided.
  • Rotational engagement between the hub (14) and the rotor (30) is preferably through a set of axial splines (not shown) provided on the hub (14) and corresponding inner teeth (not shown) provided on the interior of the rotor disk (30). Other arrangements are possible as well.
  • the disk brake assembly (10) comprises rotating parts and fixed parts.
  • the rotating parts are rotating with reference to the fixed parts.
  • the fixed parts are the ones that are directly or indirectly rigidly attached to the axle of the vehicle.
  • One of the rotating parts of the disk brake assembly (10) is the hub (14) to which the rotor disk (30) is connected.
  • Non-rotating parts include sets of brake pads (40).
  • One set of brake pads (40) is attached to the external cover (20).
  • the second set of brake pads (50) is attached to a slidable inner carrier (52) actuated by means of an annular air bellows (80) in fluid communication with the pneumatic braking system of the vehicle, as shown in FIG. 2.
  • the air bellows (80) pushes a piston (81 ), itself pushing the inner carrier (52).
  • a hydraulic actuator would be used and connected to a corresponding hydraulic braking system.
  • the braking action is achieve when a force is applied by the air bellows (80). This force urges the second set of braking pads (50) against the corresponding side surface of the rotor disk (30).
  • the rotor disk (30) then moves against the first set of brake pads (40).
  • the mechanical energy of the rotation is then transformed into heat due to the friction between both side surfaces of the rotor disk (30) and the brake pads (40,50).
  • FIG. 2 shows an exploded view of the disk brake assembly (10). It shows the various components described herein. It also shows a wear compensation system, which includes a wear compensation assembly (90) and its corresponding annular push plate (92) in accordance with the present invention. This plate (92) is set near the bottom of the housing (22) and holds the back of the axially movable inner carrier (52). This will be further described herein.
  • the bottom of the housing (22) is where the air bellows (80) is located.
  • the air bellows (80) When braking, the air bellows (80) is filled with pressurized air to achieve the braking action by pushing the inner carrier (52). The braking action stops when the pressure in the air bellows (80) falls under a given value. Return springs are used to move the inner carrier (52) back to its original position.
  • FIG. 3 schematically shows the rack and pinion arrangement of the present invention.
  • the rack (94) is rigidly attached to the periphery of the wear compensation plate (92).
  • the wear compensation assembly (90) must be very precise, partly because of the relatively very small variations in thickness.
  • the ratio between the pinion (96) and the rack (94) is thus very low, which means that many rotations of the pinion (96) are required to rotate the wear compensation plate (92) significantly.
  • FIG. 4 shows the central portion of the disk brake assembly (10) in accordance with a preferred embodiment of the present invention.
  • the wear compensation plate (92) comprises a plurality of helical ramps (92a). Rotating the wear compensation plate (92) clockwise will bring the inner carrier (52) closer to the rotor disk (30). The compensation rotation direction can be anticlockwise if needed.
  • the pinion (96) is located at the end of an axle (98) and is held in position by a first bearing (100).
  • the casing of the bearing (100) is rigidly attached to the piston (81 ) of the disk brake assembly (10).
  • the opposite end of the axle (98) is attached to a cylindrical sprocket (102).
  • the sprocket (102) is slidably mounted inside a bore (104) of a support casing (106), as shown in FIG. 7.
  • the support casing (106) is rigidly attached to the housing (22) and is thus not moving with the piston (81 ).
  • the pinion (96), the axle (98) and the bearings (100,108) are designed to follow to movement of the inner carrier (52). It should be noted that there is preferably only one wear compensation assembly (90) in the disk brake assembly (10).
  • FIGS. 5, 6 and 8 show different views of the wear compensation assembly (90).
  • the sprocket (102) is provided with oblique teeth. At least one lateral follower (110) is in mesh with the sprocket (102). Two lateral followers (110) are provided in the illustrated embodiment. The followers (110) are located in respective side channels (112) and are each biased by a spring (114) towards the surface of the sprocket (102). A screw (116) maintains each follower (110) and its spring inside its side channel (112).
  • the wear compensation assembly (90) is designed so as to detect an increase in the normal length of the stroke of the inner carrier (52).
  • the stroke can be defined as the travel distance between the initial (or resting) position and the full-braking position.
  • a typical normal stroke is about 1 mm. If the stroke is within the normal value, no compensation is required. However, in the contrary, the compensation must take place.
  • the teeth of the followers (110) will move only within the same corresponding teeth of the sprocket (102).
  • the angle of the teeth is small with reference to the longitudinal axis of the sprocket. Axial movement of the sprocket (102) relative to the followers (110) will not cause a significant rotation of the sprocket (102). Also, the braking force quickly prevents the wear compensation plate (92) from rotating with reference to the inner carrier (52). The axial movement of the sprocket (102) with reference to the followers (110) will cause the teeth of the followers (110) to slide longitudinally with reference to the sprocket (102).
  • the two followers (110) are preferably offset of half the pitch of the teeth of the sprocket (102).
  • the wear compensation assembly (90) is then designed to work with only half a pitch.
  • the angle of the teeth of the sprocket (102) and the followers (110) determines if the wear compensation assembly (90) compensates when the piston goes forwards or backwards.
  • the wear compensation assembly (90) is reset to or close to its original position by removing or releasing tension in the followers (110), and manually rotating the wear compensation plate (90) back to its original position.
  • the illustrated disk brake assembly (10) is designed to be used on a large truck or bus with pneumatic braking system, slightly different versions can be designed for other kinds of vehicle, including vehicles with an hydraulic breaking system.
  • the wear compensation assembly (90) may be different from what is shown in the figures.

Landscapes

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

Abstract

L'invention concerne un système de compensation d'usure comprenant un ensemble de compensation d'usure et une plaque de poussage annulaire établie entre la commande de l'ensemble de frein à disque et le support mobile destiné aux garnitures du frein à disque. Le système est conçu de manière que la plaque de poussage tourne légèrement et contraigne légèrement le support des garnitures du frein à disque à distance de la commande, de manière à compenser l'usure desdites garnitures. Cette rotation est entraînée par l'ensemble de compensation d'usure, notamment un agencement de crémaillère activé quand la course de déplacement est supérieure à une valeur établie au préalable. Celle-ci est conditionnée par la relation entre une roue dentée et au moins une roue menée. Le système garantit une compensation optimale de l'ensemble de frein à disque.
PCT/CA2004/001863 2003-10-22 2004-10-22 Systeme de compensation d'usure destine a un ensemble de frein a disque Ceased WO2005038287A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US51284803P 2003-10-22 2003-10-22
US60/512,848 2003-10-22

Publications (1)

Publication Number Publication Date
WO2005038287A1 true WO2005038287A1 (fr) 2005-04-28

Family

ID=34465377

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2004/001863 Ceased WO2005038287A1 (fr) 2003-10-22 2004-10-22 Systeme de compensation d'usure destine a un ensemble de frein a disque

Country Status (1)

Country Link
WO (1) WO2005038287A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006047886A1 (fr) * 2004-11-04 2006-05-11 Groupe Newtech International Inc. Plaque intermediaire pour un ensemble de freinage a disque annulaire et a contact integral
WO2008116651A1 (fr) * 2007-03-27 2008-10-02 Pintsch Bubenzer Gmbh Élément d'écartement et dispositif de freinage
EP1925843A3 (fr) * 2006-11-27 2009-03-25 Kabushiki Kaisha Toyota Jidoshokki Dispositif de rattrapage d'usure d'un frein à disque humide
WO2009067801A1 (fr) * 2007-11-27 2009-06-04 ASTéRIA PERFORMANCE INC. Frein à disque annulaire et procédé permettant d'augmenter la force de serrage des plaquettes de frein
WO2013044397A1 (fr) * 2011-09-30 2013-04-04 ASTéRIA PERFORMANCE INC. Agencement pour compenser automatiquement l'usure des plaquettes de frein dans un frein à disque annulaire
US9091313B2 (en) 2013-08-27 2015-07-28 Akebono Brake Corporation Full contact brake

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5320205A (en) * 1992-11-12 1994-06-14 Dana Corporation Wear adjustment for a clutch
US6293371B1 (en) * 1997-06-06 2001-09-25 Meritor Automotive, Inc. Disc brake assembly
US6357570B1 (en) * 1998-11-06 2002-03-19 Valeo Friction clutch with wear take-up device for friction linings, in particular for motor vehicle, provided with means indicating degree of said wear
US6371269B1 (en) * 1999-05-18 2002-04-16 Mannesmann Sachs Ag Thrust plate assembly

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5320205A (en) * 1992-11-12 1994-06-14 Dana Corporation Wear adjustment for a clutch
US6293371B1 (en) * 1997-06-06 2001-09-25 Meritor Automotive, Inc. Disc brake assembly
US6357570B1 (en) * 1998-11-06 2002-03-19 Valeo Friction clutch with wear take-up device for friction linings, in particular for motor vehicle, provided with means indicating degree of said wear
US6371269B1 (en) * 1999-05-18 2002-04-16 Mannesmann Sachs Ag Thrust plate assembly

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006047886A1 (fr) * 2004-11-04 2006-05-11 Groupe Newtech International Inc. Plaque intermediaire pour un ensemble de freinage a disque annulaire et a contact integral
EP1925843A3 (fr) * 2006-11-27 2009-03-25 Kabushiki Kaisha Toyota Jidoshokki Dispositif de rattrapage d'usure d'un frein à disque humide
US8033364B2 (en) 2006-11-27 2011-10-11 Kabushiki Kaisha Toyota Jidoshokki Gap adjusting mechanism of a wet brake
WO2008116651A1 (fr) * 2007-03-27 2008-10-02 Pintsch Bubenzer Gmbh Élément d'écartement et dispositif de freinage
WO2009067801A1 (fr) * 2007-11-27 2009-06-04 ASTéRIA PERFORMANCE INC. Frein à disque annulaire et procédé permettant d'augmenter la force de serrage des plaquettes de frein
RU2477398C2 (ru) * 2007-11-27 2013-03-10 Астериа Перформанс Инк. Кольцевой дисковый тормоз и способ увеличения усилия схватывания тормозной колодки
US8657080B2 (en) 2007-11-27 2014-02-25 Asteria Performance Inc. Annular disk brake and method of increasing a brake pad clamping force
WO2013044397A1 (fr) * 2011-09-30 2013-04-04 ASTéRIA PERFORMANCE INC. Agencement pour compenser automatiquement l'usure des plaquettes de frein dans un frein à disque annulaire
US9091313B2 (en) 2013-08-27 2015-07-28 Akebono Brake Corporation Full contact brake

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