WO1998006608A2 - Mecanisme d'actionnement electromecanique pour ensemble de freins a disques - Google Patents

Mecanisme d'actionnement electromecanique pour ensemble de freins a disques Download PDF

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Publication number
WO1998006608A2
WO1998006608A2 PCT/US1997/014462 US9714462W WO9806608A2 WO 1998006608 A2 WO1998006608 A2 WO 1998006608A2 US 9714462 W US9714462 W US 9714462W WO 9806608 A2 WO9806608 A2 WO 9806608A2
Authority
WO
WIPO (PCT)
Prior art keywords
piston
disc brake
spindle
lever
motor
Prior art date
Application number
PCT/US1997/014462
Other languages
English (en)
Inventor
Thomas Weigert
Andrew Kingston
Salvatore Oliveri
Original Assignee
Kelsey Hayes Company
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 Kelsey Hayes Company filed Critical Kelsey Hayes Company
Priority to AU39846/97A priority Critical patent/AU3984697A/en
Publication of WO1998006608A2 publication Critical patent/WO1998006608A2/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
    • F16D65/14—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
    • 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
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • 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
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • 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
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/26—Cranks
    • 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
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • 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

Definitions

  • This invention relates in general to vehicle disc brake assemblies and in particular to an improved electro-mechanical actuation mechanism adapted for use in such a vehicle disc brake assembly.
  • Most vehicles are equipped with a brake system for retarding or stopping movement of the vehicle in a controlled manner.
  • a typical brake system for .an automobile or light truck includes a disc brake assembly for each of the front wheels and either a drum brake assembly or a disc brake assembly for each of the rear wheels.
  • the brake assemblies are actuated by hydraulic, pneumatic, or electrical mechanisms when an operator of the vehicle depresses a brake pedal.
  • the structures of these drum brake assemblies and disc brake assemblies, as well as the actuators therefor, are well known in the art.
  • a typical disc brake assembly includes a rotor that is secured to the wheel of the vehicle for rotation therewith. Pins secured to an anchor plate slidably support a caliper assembly.
  • the anchor plate is secured to a non-rotatable component of the vehicle, such as the vehicle frame.
  • the caliper assembly includes a pair of brake shoes that are disposed on opposite sides of the rotor.
  • the brake shoes are operatively connected to one or more hydraulically, pneumatically, or electrically actuated pistons for movement between a non- braking position, wherein they are spaced apart from opposed axial sides or braking surfaces of the rotor, and a braking position, wherein they are moved into frictional engagement with the opposed braking surfaces of the rotor.
  • the piston urges the brake shoes from the non-braking position to the braking position so as to frictionally engage the opposed braking surfaces of the rotor and thereby slow or stop the rotation of the associated wheel of the vehicle.
  • the electro-mechanical disc brake caliper assembly includes an electro-mechanical actuation mechanism, a piston unit, and a freewheeling clutch.
  • the electro-mechanical actuation mechanism includes an electrical actuating unit, an eccentric actuating lever, a mechanically actuated piston unit, and an automatic adjustment mechanism.
  • the electrical actuating unit includes an electric motor and a motor spindle operatively coupled to the motor so as to convert rotary motion of the motor into axial movement of the motor spindle.
  • the motor spindle operatively engages the lever so as to cause the lever to pivot relative to a lever pivot axis.
  • the piston unit is operatively coupled to the lever and includes a piston spindle and a piston.
  • the piston spindle is operatively coupled to the lever so as to be axially moved during actuation of the lever.
  • the piston spindle is operatively coupled to the automatic adjustment mechanism so as to cause adjustment of the piston spindle during actuation of the electro-mechanical actuation mechanism if the piston moves more than a predetermined brake clearance distance.
  • the freewheeling clutch is adapted to limit the adjustment provided by the automatic adjustment mechanism.
  • FIG. 1 is a sectional view of a portion of an electro-mechanical disc brake caliper assembly in accordance with this invention.
  • Fig. 2 is a top plan view, partially in section, of a portion of the electro- mechanical disc brake caliper assembly.
  • Fig. 3 is an elevational view of an adjusting pin and adjusting lever of the electro-mechanical actuation mechanism taken along line 3-3 of Fig. 2.
  • Fig. 4 is an outboard view of the electro-mechanical disc brake caliper assembly.
  • Fig. 5 is an enlarged sectional view of a portion of the electro-mechanical disc brake caliper assembly illustrated in Fig. 1.
  • the disc brake caliper assembly 10 includes a caliper, indicated generally at 11.
  • the caliper 11 includes an inboard leg portion 12 and an outboard leg portion 13 that are interconnected by an intermediate bridge portion 14.
  • the inboard leg portion 12 of the caliper 11 includes an annular recess 12A for receiving an electro-mechanical actuating mechanism, indicted generally at 40, for effecting the operation of the disc brake assembly 10 under normal operating conditions.
  • the caliper 11 is slidably supported on a pair of pins
  • the pins 15 which are secured to an anchor plate indicated generally at 16.
  • the pins 15 extend through respective non-threaded apertures (not shown) formed through the inboard leg 12 of the caliper 11.
  • the pins 15 have threaded ends (not shown) which are received in respective threaded apertures (not shown) formed through the anchor plate 16.
  • the pins 15 permit the caliper 11 to slide in both the outboard direction (toward the left when viewing Figs. 1 and 2) and the inboard direction (toward the right when viewipg Figs. 1 and 2). Such sliding movement of the caliper 11 occurs when the disc brake assembly 10 is actuated, as will be explained below.
  • a pair of bolts 17 extend through respective non-threaded apertures (not shown) formed through the anchor plate 16 to secure the anchor plate 16 to a stationary component of the vehicle, such as the steering knuckle (not shown) in a front wheel drive vehicle.
  • the anchor plate 16 includes a pair of outwardly extending arms 18 and 19 having upstanding guide rails 18A and 19A, respectively formed thereon.
  • the guide rails 18A and 19A extend transverse to the arms 18 and 19 and parallel to one another.
  • the guide rails 18A and 19A are provided to slidably support an inboard brake shoe, indicated generally at 20, and an outboard brake shoe, indicated generally at 21, of the disc brake caliper assembly 10.
  • the inboard brake shoe 20 includes a backing plate 22 and a friction pad 23 (Fig. 1).
  • the opposed ends of the inboard backing plate 22 have notches 22A and 22B formed therein for supporting the inboard brake shoe 20 on the guide rails 18A and 19A of the anchor plate 16.
  • the outboard brake shoe 21 includes a backing plate 24 and a friction pad 25.
  • the opposed ends of the outboard backing plate 24 have notches (not shown) formed therein for supporting the outboard brake shoe 21 on the guide rails 18A and 19A of the anchor plate 16.
  • the inboard brake shoe 20 can be supported on a brake piston 63, while the outboard brake shoe 21 can be supported on the outboard leg portion 13 of the caliper 11.
  • the disc brake assembly 10 further includes a rotor, indicated generally at 26, which is connected to a hub, indicated generally at 32, and a wheel (not shown) of the vehicle for rotation therewith.
  • the illustrated rotor 26 is ventilated and includes a pair of opposed friction plates 27 and 28 which are spaced apart from one another by a plurality of intermediate ribs or posts 29 in a known manner.
  • the rotor 26 extends radially outwardly between the inboard friction, pad 23 and the outboard friction pad 25.
  • the rotor 26 further includes an inner mounting flange portion 30 connected to the friction plate 27 by a circumferential wall or hat portion 31.
  • the inner mounting flange portion 30 includes a centrally located pilot hole 30A that defines an axis of rotation for the rotor 26.
  • a plurality of lug bolt receiving holes 30B (only one of such plurality of lug bolt receiving holes 30B is shown in Fig. 1) are equally spaced circumferentially on the rotor 26 about the pilot hole 30a.
  • a lug bolt (not shown) extends through a respective one of a plurality of lug bolt receiving holes 32 A provided in the hub 32, and through each of the lug bolt receiving holes 30B for mounting and securing the rotor 26 to the hub 32 and vehicle wheel for rotation therewith.
  • the disc brake caliper assembly 10 also includes a dust boot seal 33 and a pair of retractor clips 34 and 35.
  • the dust boot seal 33 is formed from a flexible material and has a first end that engages an outboard end of the recess 12 A.
  • a second end of the dust boot seal 33 engages an annular groove formed in an outer side wall of the piston 63.
  • a plurality of flexible convolutions are provided in the dust boot seal 33 to permit relative movement between the first and second ends thereof.
  • the dust boot seal 33 is provided to prevent water, dirt, and other contaminants from entering into the recess 12A.
  • the retractor clips 34 and 35 are supported on and secured to the guide rails 18A and 19 A, respectively of the anchor plate 16.
  • the retractor clips 34 and 35 are operative to spread the brake shoes 20 and 21 apart from one another when the disc brake caliper assembly 10 is not actuated.
  • the disc brake caliper assembly 10 further includes an electro-mechanical actuation mechanism, indicated generally at 40, for effecting the operation of the disc brake caliper assembly 10 under normal operating conditions.
  • the electro-mechanical actuation mechanism 40 includes an electrical actuating unit 41, an eccentric actuating lever 55, a mechanically actuated piston unit 60, and an automatic adjustment mechanism 70.
  • the electrical actuating unit 41 is disposed in a separate housing 39 which is secured to the inboard leg 12 of the caliper 11 by suitable means.
  • the electrical actuating unit 41 includes an electric motor 42 and a spindle 43 operatively coupled to the motor 42 by an output shaft 44.
  • the illustrated electrical motor 42 is preferably a brushless DC motor and includes a pair of coils 42A and 42B, and magnets 42C.
  • the spindle 43 is operatively coupled to motor 42 so as to move axially relative thereto to cause the eccentric lever 55 to pivot relative to a lever pivot axis A.
  • the output shaft 44 is supported in the opening inboard leg 12 of the caliper 1 1 by a pair of bearings 45 and 46.
  • the output shaft 44 is coupled to the magnets 42C by suitable means, such as for example, by an adhesive or a binding band, to thereby effectively couple the output shaft 44 to the motor 42 for rotary motion when the motor 42 is actuated.
  • the output shaft 44 also includes an outboard portion 44A provided with internal threads 47.
  • a plurality of planetary rollers 48 are interposed between the outboard portion 44A of the output shaft 44 and the spindle 43.
  • a pair of roller guides 49 and 50 are disposed within and secured to the output shaft 44 between the opposed ends of the planetary rollers 48.
  • the planetary rollers 48 are provided with external threads 51, which are effective to operatively engage the internal threads 47 of the outboard portion 44A of the output shaft 44, and internal threads 52, which are effective to operatively engage external threads 53 provided on the outer surface of the spindle 43.
  • the planetary rollers 48 are effective to operatively couple the motor output shaft 44 to the spindle 43 to thereby convert the rotary motion of the output shaft 44 of the motor 42 into axial movement of the spindle 43.
  • the piston unit 60 includes a spindle 61, an adjustment nut 62 (which also is a part of the automatic adjustment mechanism 70), and a piston 63.
  • the spindle 61 includes an inboard end 61 A having a recess 64 formed therein, and an outboard end 6 IB having an opening 65 formed therein.
  • the recess 64 is adapted to receive an end of a thrust pin 66.
  • the other end of the thrust pin 66 is disposed in an opening 55A formed in the eccentric lever 55.
  • the spindle 61 further includes external threads 67 provided on an outer end portion thereof.
  • the external threads 67 are effective to operatively engage internal threads 68 provided on the adjustment nut 62 so as to cause rotation of the nut 62 relative to the spindle 61 during actuation of the electro-mechanical actuation mechanism 40.
  • the inboard end 61A of the spindle 61 is secured to the inboard leg 12 of the caliper 11 by a suitable means to prevent rotation thereof.
  • the means for preventing rotation is a generally rectangular shaped pin 69.
  • a spring 37 is provided for biasing the spindle 61 to the normal brake position (to the left in Fig. 5) when the brake is released.
  • the adjustment nut 62 further includes an inboard end 62A and an outboard end 62B.
  • the outboard end 62A of the nut 62 is disposed in a recess 63 A formed in the piston 63, and engages an inner end surface of the recess 63 A.
  • An elastomeric member 38 is disposed in an annular recess formed in the piston 63, and engages an outer surface of the adjustment nut 62.
  • the elastomeric member 38 allows rotation of the adjustment nut 62 relative to the piston 63, and may function as a roll back member to move the piston 63 to its normal unactuated position (not shown) when the electro-mechanical actuation mechanism 40 is released from the actuated position, as shown in Fig. 1.
  • the automatic adjustment mechanism 70 includes the adjustment nut 62, a generally hollow cylindrical sleeve 71, a clutch device 72, a driven ring, 73, and a spring 74.
  • the sleeve 71 is rotatably supported in the recess 12A of the inboard leg 12 of the caliper 1 1.
  • an inboard end 71A of the sleeve 71 is disposed adjacent a retaining ring 75
  • an outboard end 7 IB of the sleeve 71 is disposed adjacent a shoulder 12B provided in the recess 12A.
  • an air gap 76 is defined between a portion of the outer surface of the sleeve 71 and the inner surface of the recess 12 A.
  • the outer diameter of the sleeve 71 can be reduced so that it can be installed from the left side of the recess 12A (not shown). This would allow the diameter of the recess 12A in the region of the lever 55 to be smaller thereby improving the mounting of the lever 55 on lever pivot axis A.
  • the sleeve 71 further includes an opening formed in an inner surface thereof adjacent the inboard end 71 A.
  • an adjusting pin 77 (shown in Figs. 2 and 3) is disposed in the opening of the sleeve 71 and is effective to operatively couple the sleeve 71 to an adjusting lever 78 for rotation therewith.
  • the adjusting lever 78 is operatively coupled to the eccentric lever 55 and located on the lever axis A. As shown in Fig. 3, the mouth of the adjusting lever 78 is normally separated from the adjusting pin 77 by a predetermined gap G.
  • a predetermined normal brake clearance which is defined as the clearance between the friction pads 2.3 and 25 and the rotor friction plates 28 and 27, respectively
  • the sleeve 71 is rotated by the adjusting lever 78 via the adjusting pin 77 to thereby accommodate for the wear of the friction pads 23 and 25.
  • the clutch 72 is disposed in the sleeve 71 about the adjusting nut 62 between a retaining ring 79 and an inboard end 73 A of the driven ring 73.
  • the driven ring 73 is disposed in the sleeve 71 about the adjusting nut 62.
  • a key 73B couples the driven ring 73 to the adjusting nut 62 to prevent relative rotation therebetween, but permitting the driven ring 73 to move axially relative to the adjusting nut 62.
  • the driven ring 73 is urged against an outboard end 72 A of the clutch 72 by an outboard end of the spring 74.
  • the inboard end of the spring 74 engages an inner end surface of the sleeve 71.
  • the outboard end 72A of the clutch 72 and the inboard end 73 A of the driven ring 73 are coupled together by a friction coupling, or other suitable means, to thereby limit the torque transmitted by the sleeve 71 to the adjusting nut 62 via the ring 73.
  • the driver of the vehicle depresses the brake pedal (not shown).
  • the depression of the brake pedal generates an electrical signal that is operative to actuate the electro-mechanical actuation mechanism 40.
  • the signal actuates the electric motor 42 which rotates the output shaft 44 and imparts rotary motion to the rollers 48 which in turn, axially move the spindle 43 (toward the left when viewing Figs. 1 and 2) causing the end of the spindle to rotate the eccentric lever 55 in a clockwise direction, as indicated by arrow R in Figs. 1 and 3.
  • This movement of the lever 55 causes axial movement of the thrust pin 66 (toward the left when viewing Figs. 1 and 2) causing axial movement of the spindle 61 and the piston 63 (toward the left when viewing Figs. 1 and 2).
  • the piston 63 engages the backing plate 22 of the inboard brake shoe 20 and moves the friction pad 23 of the inboard brake shoe 20 into frictional engagement with the inboard friction plate 28 of the rotor 26.
  • the caliper 11 slides on the pins 15 in the inboard direction (toward the right when viewing Figs. 1 and 2) such that the outboard leg 13 thereof moves the friction pad 25 of the outboard brake shoe 21 into frictional engagement with the outboard friction plate 27 of the rotor 26.
  • the friction pads 23 and 25 frictionally engage the opposed friction plates 27 and 28 of the rotor 26.
  • the adjusting lever 78 rotates in the direction of the arrow R more than the width of the gap G and engages the adjusting pin 77 (as shown in Fig. 3).
  • the adjusting pin 77 causes the sleeve 71 to rotate in the recess 12A.
  • the rotation of the sleeve 71 is operative to rotate the ring 73 via the clutch connection therewith and cause the adjusting nut 62 to rotate relative to the spindle 61 to thereby accommodate for brake wear.
  • the sleeve 71 rotates back to its normal position and defines the gap G between the mouth of the adjusting lever 78 and the adjusting pin 77 as shown in Fig. 3.
  • One advantage of this invention is that any lever 55 ratio can be realized so that optimal torque-speed characteristics of the motor 42 can be used. Also, the direction of the axis A can be varied by rotating the axis A and moving the contact point between the lever 55 and the spindle 43 so that the position of the actuating unit 41 can be changed relative to the space in the wheel area of the vehicle.
  • the lever 55 can be actuated by a cable (not shown) which is operatively connected to an electrical actuating unit (not shown) located remote from the disc brake caliper assembly 10, or by a motor gear or planetary gear unit which directly transmits the torque from the motor to the lever 55.
  • a cable not shown
  • an electrical actuating unit not shown
  • a motor gear or planetary gear unit which directly transmits the torque from the motor to the lever 55.
  • the invention has been described and illustrated in the context with a sliding caliper disc brake assembly 10, it will be appreciated that this invention may be used with other types of brake assemblies.
  • this invention may be used in a fixed caliper disc brake assembly (not shown), and in a dmm-in-hat type of disc brake assembly (not shown), wherein the brake assembly includes a «disc type service brake and a drum type parking and emergency brake.

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

Abstract

Cette invention concerne une structure perfectionnée conçue pour un ensemble électromécanique faisant office d'étrier de frein à disques. Ledit étrier électromécanique de frein à disques comporte un mécanisme d'actionnement électromécanique, une unité piston et un embrayage à roue libre. Ledit mécanisme d'actionnement électromécanique comprend une unité d'actionnement électrique, un levier d'actionnement excentrique, une unité piston actionnée mécaniquement et un mécanisme d'ajustement automatique. Ladite unité d'actionnement électrique comporte un moteur électrique et un axe de moteur fonctionnellement couplé audit moteur de façon à transformer le mouvement rotatif du moteur en mouvement axial dudit axe. Cet axe de moteur est en contact fonctionnel avec le levier de manière à faire pivoter le levier par rapport à un axe de pivotement du levier. L'unité piston, qui est fonctionnellement couplée au levier, comporte un axe et un piston. Ledit axe du piston est fonctionnellement couplé au levier de manière à subir un déplacement axial lors de l'actionnement du levier. L'axe de piston est fonctionnellement couplé au mécanisme d'ajustement automatique de façon à provoquer l'ajustement de l'axe du piston lors de l'actionnement du mécanisme d'actionnement électromécanique si le piston se déplace sur une longueur plus importante que la distance de sécurité du frein. L'embrayage à roue libre est conçu pour limiter l'ajustement assuré par le mécanisme d'ajustement automatique.
PCT/US1997/014462 1996-08-15 1997-08-15 Mecanisme d'actionnement electromecanique pour ensemble de freins a disques WO1998006608A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU39846/97A AU3984697A (en) 1996-08-15 1997-08-15 Electro-mechanical actuation mechanism for disc brake assembly

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US2436196P 1996-08-15 1996-08-15
US60/024,361 1996-08-15

Publications (1)

Publication Number Publication Date
WO1998006608A2 true WO1998006608A2 (fr) 1998-02-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1997/014462 WO1998006608A2 (fr) 1996-08-15 1997-08-15 Mecanisme d'actionnement electromecanique pour ensemble de freins a disques

Country Status (2)

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WO (1) WO1998006608A2 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0995922A2 (fr) * 1998-10-24 2000-04-26 Meritor Automotive Canada, Inc. Frein de stationnement pour véhicules
DE10004058A1 (de) * 2000-02-01 2001-08-09 Daimler Chrysler Ag Bremsvorrichtung
DE10232961A1 (de) * 2002-07-19 2004-02-19 Wabco Perrot Bremsen Gmbh Scheibenbremse, insbesondere für Landfahrzeuge
EP1686281A1 (fr) * 2005-01-26 2006-08-02 KNORR-BREMSE SYSTEME FÜR NUTZFAHRZEUGE GmbH Régleur automatique de jeu pour un frein à disque
CN102069790A (zh) * 2010-12-28 2011-05-25 奇瑞汽车股份有限公司 一种电子机械制动器电控保压机构以及实现方法
DE102010004602A1 (de) * 2010-01-13 2011-07-14 IMS Gear GmbH, 78166 Antrieb zur Betätigung einer Feststellbremse
DE102012016712A1 (de) * 2012-08-22 2014-02-27 Wabco Radbremsen Gmbh Scheibenbremse, insbesondere für Nutzfahrzeuge, sowie Bremssattel für eine solche Scheibenbremse
CN112065895A (zh) * 2020-09-16 2020-12-11 中车青岛四方车辆研究所有限公司 一种电动制动器
EP4180282A1 (fr) * 2021-11-12 2023-05-17 KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH Ensemble frein et véhicule comprenant un tel ensemble frein

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0995922A2 (fr) * 1998-10-24 2000-04-26 Meritor Automotive Canada, Inc. Frein de stationnement pour véhicules
EP0995922A3 (fr) * 1998-10-24 2002-10-30 Meritor Automotive Canada, Inc. Frein de stationnement pour véhicules
DE10004058A1 (de) * 2000-02-01 2001-08-09 Daimler Chrysler Ag Bremsvorrichtung
DE10004058B4 (de) * 2000-02-01 2004-12-09 Conti Temic Microelectronic Gmbh Bremsvorrichtung
DE10232961A1 (de) * 2002-07-19 2004-02-19 Wabco Perrot Bremsen Gmbh Scheibenbremse, insbesondere für Landfahrzeuge
DE10232961B4 (de) * 2002-07-19 2007-06-14 Wabco Perrot Bremsen Gmbh Scheibenbremse, insbesondere für Landfahrzeuge
EP1686281A1 (fr) * 2005-01-26 2006-08-02 KNORR-BREMSE SYSTEME FÜR NUTZFAHRZEUGE GmbH Régleur automatique de jeu pour un frein à disque
DE102010004602A1 (de) * 2010-01-13 2011-07-14 IMS Gear GmbH, 78166 Antrieb zur Betätigung einer Feststellbremse
DE102010004602A8 (de) * 2010-01-13 2012-01-12 Ims Gear Gmbh Antrieb zur Betätigung einer Feststellbremse
US8783422B2 (en) 2010-01-13 2014-07-22 Ims Gear Gmbh Drive for actuating a parking brake
CN102069790A (zh) * 2010-12-28 2011-05-25 奇瑞汽车股份有限公司 一种电子机械制动器电控保压机构以及实现方法
CN102069790B (zh) * 2010-12-28 2013-04-10 奇瑞汽车股份有限公司 一种电子机械制动器电控保压机构以及实现方法
DE102012016712A1 (de) * 2012-08-22 2014-02-27 Wabco Radbremsen Gmbh Scheibenbremse, insbesondere für Nutzfahrzeuge, sowie Bremssattel für eine solche Scheibenbremse
CN112065895A (zh) * 2020-09-16 2020-12-11 中车青岛四方车辆研究所有限公司 一种电动制动器
CN112065895B (zh) * 2020-09-16 2022-02-01 中车青岛四方车辆研究所有限公司 一种电动制动器
EP4180282A1 (fr) * 2021-11-12 2023-05-17 KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH Ensemble frein et véhicule comprenant un tel ensemble frein

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