WO2015004696A1 - Disc brake device - Google Patents

Disc brake device Download PDF

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Publication number
WO2015004696A1
WO2015004696A1 PCT/JP2013/004283 JP2013004283W WO2015004696A1 WO 2015004696 A1 WO2015004696 A1 WO 2015004696A1 JP 2013004283 W JP2013004283 W JP 2013004283W WO 2015004696 A1 WO2015004696 A1 WO 2015004696A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
positioning
pad
rotor
shaft
Prior art date
Application number
PCT/JP2013/004283
Other languages
French (fr)
Japanese (ja)
Inventor
誠人 大澤
浩忠 吉谷
Original Assignee
株式会社Tbk
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 株式会社Tbk filed Critical 株式会社Tbk
Priority to PCT/JP2013/004283 priority Critical patent/WO2015004696A1/en
Publication of WO2015004696A1 publication Critical patent/WO2015004696A1/en

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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
    • F16D65/56—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
    • F16D65/568—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake for synchronous adjustment of actuators arranged in parallel
    • 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
    • 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
    • F16D2125/28—Cams; Levers with cams
    • 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

Definitions

  • the present invention relates to a disc brake device mounted on an automobile or the like.
  • a disc brake device As such a disc brake device, a disc rotor that rotates with a wheel of an automobile, etc., a pair of brake pads arranged so as to sandwich the disc rotor, and a rotor surface of the disc rotor provided across the outer periphery of the disc rotor
  • a floating type brake device including a caliper provided so as to be movable in a direction perpendicular to the vertical direction (see, for example, Patent Documents 1 and 2).
  • a brake actuator is provided only on one brake pad side, and one brake pad is pressed against the rotor surface by the operation of the brake actuator, and the other brake pad is passed through the caliper using the reaction force.
  • the disc rotor is sandwiched from both sides by a pair of brake pads, and the rotation of the disc rotor and wheels is braked by the frictional force between them.
  • the disc brake device as described above has a pad pressing device for pressing the brake pad against the rotor surface of the disc rotor by the operation of the brake actuator.
  • This pad pressing device has a brake shaft arranged substantially parallel to the rotor surface, and the brake pad is pressed against the rotor surface by rotating the brake shaft in the brake operating direction by the operation of the brake actuator. It is configured. Further, when the brake operation is released, the brake shaft is rotated in the brake release direction by the urging force of the spring to separate the brake pad from the rotor surface.
  • the brake shaft rotates while drawing a complicated turning locus combining movement in the disc rotor direction (left-right direction) and up-down direction, and presses the brake pad against the rotor surface of the disc rotor.
  • This method has an advantage that the frictional resistance is lower than the method in which the brake shaft is supported by the slide bearing.
  • the rotation position of the brake shaft varies, there is a problem that the components may interfere with each other during the operation of the brake and may be damaged.
  • the present invention has been made in view of such a problem, and provides a disc brake device that can suppress variations in the rotational position of the brake shaft and prevent components from interfering with each other and breaking during braking.
  • the purpose is to provide.
  • a disc brake device includes a disc rotor that rotates together with a wheel, a brake pad that is provided to face the rotor surface of the disc rotor, and the brake pad that is disposed on the rotor surface.
  • a pad pressing device for pressing, and a brake housing (for example, caliper 6 in the embodiment) that accommodates the pad pressing device therein, and the brake pad is pressed against the rotor surface by the pad pressing device;
  • the disc rotor and the wheel are braked by the frictional force generated in the wheel.
  • the pad pressing device includes a brake actuator that operates when a brake operation is performed, and a brake shaft that is disposed substantially parallel to the rotor surface and rotates in the brake operation direction by the operation of the brake actuator (for example, the operating shaft 20) in the embodiment, a pad pushing mechanism that moves the brake pad in a direction approaching the rotor surface by turning the brake shaft, and the pad pushing mechanism when the brake operation is released. And a brake release spring (for example, the return spring 15 in the embodiment) that moves the brake shaft in the brake release direction.
  • the brake shaft abuts against the inner surface of the positioning recess formed in the brake housing at all rotation positions from the position before the brake operation start to the position rotated in the brake operation direction. It has a positioning pin for positioning the shaft.
  • the positioning pin is formed in a substantially trapezoidal shape with a cross section having an involute curve at a portion contacting the inner surface of the positioning recess, and the positioning recess is a portion contacting the positioning pin.
  • the cross section in is composed of a trapezoidal depression.
  • the positioning pin is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, and the positioning recess has a substantially conical shape having a trapezoidal cross section on the entire periphery. It is preferable to consist of a dent.
  • the outer peripheral surface of the portion where the positioning pin is provided in the brake shaft is formed in a curved surface shape having a radius equal to the meshing pitch circle radius of the positioning pin and the positioning recess. It is preferable.
  • At least two positioning pins are provided in the axial direction on the brake shaft.
  • the brake shaft comes into contact with the inner surface of the positioning recess of the brake housing at all the rotational positions between the position before the brake operation is started and the brake operation position. It has a positioning pin for positioning. Therefore, the brake shaft can be positioned at all the rotation positions, and variations in the rotation positions of the brake shaft can be suppressed. Therefore, it is possible to prevent the component parts from interfering with each other during the brake operation, and to exhibit a stable braking force with respect to the brake operation.
  • the positioning pin is formed in a substantially trapezoidal shape in which the cross section at the portion contacting the inner surface of the positioning recess has an involute curve, and the positioning recess is configured by a trapezoidal recess in the portion contacting the positioning pin.
  • the positioning pins and the positioning recesses can be easily manufactured, and the manufacturing cost can be reduced.
  • the positioning pin is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, and the positioning recess is formed of a substantially conical recess having a trapezoidal cross section on the entire circumference, the positioning pin Since the assembling direction of the pin can be eliminated, it is possible to prevent the positioning pin from being damaged due to an assembly error.
  • the outer peripheral surface of the portion where the positioning pin is provided on the brake shaft is formed in a curved surface shape having a radius equal to the engagement pitch circle radius of the positioning pin and the positioning recess, and the pressure angle of the positioning pin (involute) is positioned If the pressure angle is set to be larger than the pressure angle of the recess, the positioning pin and the positioning recess are kept substantially constant (precisely slightly increased) while the brake shaft rotates, and the positioning pin is not loaded. It is possible to prevent the positioning pin from being damaged even in a high load state during brake operation.
  • the pressure angle of the positioning pin is set to be larger than the pressure angle of the positioning recess as described above, the clamping force is lost and shifted while the brake shaft is rotating, and the clamping force is restored again. Even in this case, the positional deviation is only slight, and the positioning pin is rotated in the direction in which the clearance from the positioning recess slightly increases with this position as the initial position, so that no load is applied to the positioning pin. Can do.
  • the two positioning pins can prevent the axis of the brake shaft from being inclined.
  • FIG. 1 is a vertical cross-sectional view at a substantially central portion of a disc brake device according to the present invention. It is a horizontal sectional view in the position of arrow II-II shown in FIG.
  • FIG. 3 is a vertical sectional view at the position of arrow III-III shown in FIG. 2.
  • FIG. 4 is a horizontal sectional view at the position of arrow IV-IV shown in FIG. 3. It is a figure which shows a positioning pin, (a) is a front view, (b) is sectional drawing in the position of arrow bb shown to (a).
  • FIG. 2 is an enlarged view around a positioning pin in FIG. 1.
  • FIG. 5 is an enlarged view around the adjuster mechanism in FIG. 4. It is sectional drawing in the position of arrow VIII-VIII shown in FIG.
  • the directions of the up and down, left and right and front and rear arrows shown in the figure will be referred to as the up and down direction, the left and right direction, and the front and rear direction, respectively.
  • the disc brake device 1 includes a disc-like disc rotor 2 that rotates together with a wheel of an automobile or the like, a carrier 3 that is fixed to an axle (a case that receives an axle), and the disc rotor 2 in the carrier 3.
  • This is a floating type disc brake device.
  • the guide sleeves 9a and 9b extending in a direction substantially orthogonal to the rotor surfaces 2L and 2R (surfaces against which the brake pads are pressed) of the disc rotor 2 are attached to the carrier 3 by bolts (see FIG. 4).
  • the caliper 6 is guided by the guide sleeves 9a and 9b and is provided so as to be movable in a direction (right and left direction) substantially orthogonal to the rotor surfaces 2L and 2R.
  • the caliper 6 is connected to the guide sleeves 9a and 9b and includes a pressing mechanism accommodating portion 6a that accommodates the pad pressing device 10 therein, a pad supporting portion 6b that supports the left brake pad 4, and the accommodating portion 6a and the supporting portion 6b. And a connecting portion 6c to be connected.
  • the left and right brake pads 4 and 5 are attached to the pad members 4a and 5a that are in contact with the rotor surfaces 2L and 2R of the disc rotor 2, and the back surfaces of the pad members 4a and 5a (the non-contact surface side with the disc rotor 2).
  • the metal plate members 4b and 5b are formed.
  • the pad pressing device 10 includes a brake actuator (not shown) that operates when a brake operation is performed, an operating shaft 20, a slide block 30, a return spring 15, a pad pushing mechanism 40, and an adjuster mechanism 50. Is done.
  • the operating shaft 20 includes a shaft main body 21 that extends substantially parallel to the rotor surface of the disc rotor 2 and extends in the front-rear direction, and a lever portion 22 that extends upward from a substantially central portion of the shaft main body 21. At the upper end portion of the lever portion 22, a concave portion 22 a to which the tip of the operating portion of the brake actuator is connected is formed.
  • the shaft body 21 has a substantially semicircular first curved surface 23 having a radius R ⁇ b> 1 on the side facing the disc rotor 2, and the surface opposite to the disc rotor 2 (the right inner surface of the caliper 6).
  • the second curved surface 24 having a substantially semicircular shape with a radius R2 (R2 ⁇ R1).
  • the center of curvature P1 of the first curved surface 23 and the center of curvature P2 of the second curved surface 24 are shifted in the vertical direction.
  • the first curved surface 23 is provided on the front and rear sides so as to sandwich the lever portion 22.
  • the second curved surface 24 is provided with positioning pins 25 and 25 at the center portion and the rear end portion in the front-rear direction, respectively.
  • the positioning pin 25 is attached to the shaft main body 21, and the protrusion 25a protruding from the shaft main body 21 at that time is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface as shown in FIG. That is, the protrusion 25a has an involute curve as shown in FIG. 5 (b) in any cross section passing through the central axis C and perpendicular to the paper surface in the front view shown in FIG. 5 (a). It is formed in a substantially trapezoidal shape.
  • a support plane 18 that is substantially parallel to the rotor surface of the disk rotor 2 is provided on the right inner surface of the caliper 6 (pressing mechanism accommodating portion 6a).
  • a substantially conical positioning recess 19 corresponding to the shape of the protrusion 25 a of the positioning pin 25 is formed in the support plane 18.
  • the second curved surface 24 and the protruding portion 25a of the shaft body 21 and the support plane 18 on which the positioning recess 19 is formed are involute gears (external gears) in the cross section. The relationship is similar to that of racks.
  • the radius R2 (shaft rolling surface radius) of the second curved surface 24 is set to be equal to the meshing pitch circle radius, and the pressure angle of the protrusion 25a (involute) is larger than the pressure angle of the positioning recess 19.
  • the relationship is similar to the relationship between the involute gear of such specifications and the rack.
  • the slide block 30 is provided adjacent to the operating shaft 20 on the side closer to the disc rotor 2 than the operating shaft 20.
  • the slide block 30 is guided by a first bearing 35 provided in the caliper 6 (pressing mechanism accommodating portion 6a), and is provided so as to be movable in a direction (right and left direction) substantially orthogonal to the rotor surface of the disk rotor 2.
  • the slide block 30 has a substantially semicircular concave curved surface 31 corresponding to the first curved surface 23 on the surface facing the first curved surface 23 of the shaft body 21.
  • the concave curved surface 31 is provided with a second bearing 32 (for example, a needle bearing).
  • Shaft support portions 33 and 33 are provided at the front end portion and the rear end portion of the slide block 30 to support the front and rear end portions of the shaft main body 21 and restrict the front and rear movement of the shaft main body 21 (see FIG. 2). ).
  • the return spring 15 is compressed between the wall portion 17 provided at the position on the left end side inside the caliper 6 (pressing mechanism accommodating portion 6a) and the spring support recess portion 34 formed at the left end portion of the slide block 30. Is provided.
  • the slide block 30 is biased toward the operating shaft 20 by the elastic force of the return spring 15.
  • the concave curved surface 31 of the slide block 30 is in contact with the first curved surface 23 of the shaft body 21 via the second bearing 32.
  • the second curved surface 24 of the shaft body 21 is in contact with the support plane 18 in the caliper 6.
  • the protruding portion 25 a of the positioning pin 25 provided on the second curved surface 24 is inserted into the positioning recess 19 formed in the support plane 18.
  • the operating shaft 20 is pressed against the support plane 18 via the slide block 30 by the return spring 15 so as to be restricted from moving in the left-right direction, and moved in the front-rear direction by the shaft support portions 33, 33 of the slide block 30. Is supported in a regulated state.
  • the operating shaft 20 is also restricted from moving in the vertical direction by the contact of the concave curved surface 31 of the slide block 30 with the first curved surface 23 and the fitting of the protruding portion 25a of the positioning pin 25 and the positioning concave portion 19 of the support plane 18. Supported by the state.
  • the operating shaft 20 is supported by a second bearing 32 provided on the concave curved surface 31 of the slide block 30 in a state where the first curved surface 23 can be rotationally moved along the concave curved surface 31.
  • the pad pushing mechanism 40 includes a pair of front and rear nut members 41 and 42 connected to the slide block 30, and screw members 43 and 42 attached to the front and rear nut members 41 and 42, respectively. 44 and a head member 45 attached to the tip end portions (left end portions) of the screw members 43 and 44.
  • the nut members 41 and 42 are substantially cylindrical members and are configured to be connected to the slide block 30 so as to be movable together with the slide block 30 in a direction (left-right direction) substantially perpendicular to the rotor surface of the disk rotor 2. Screws are cut on the inner peripheral surfaces of the nut members 41 and 42.
  • the screw members 43 and 44 are substantially cylindrical members, and the screw members 43 and 44 are threaded on the outer peripheral surfaces.
  • the screw members 43 and 44 are screwed into the nut members 41 and 42, respectively.
  • a head member 45 is attached to the tip of the screw members 43 and 44.
  • the head member 45 is a substantially flat plate-like member, and the right brake pad 5 (plate member 5 b) is in contact with the left side surface of the head member 45.
  • the adjuster mechanism 50 includes an adjuster pin 51, a first wheel 52, a second wheel 53, a lap spring 54, a cone member 55, a clutch spring 56, and an interlocking gear train 57. Is done.
  • the adjuster pin 51 is fixed to the front end surface of the operating shaft 20 (shaft body 21), and moves in the vertical direction as the operating shaft 20 rotates.
  • the first wheel 52 is a cylindrical member, and is provided on the outer peripheral portion of the nut member 41 so as to be rotatable relative to the nut member 41.
  • the first wheel 52 is formed with an insertion hole 52a into which the tip of the adjuster pin 51 is inserted.
  • the inner diameter of the insertion hole 52a is formed larger than the outer shape of the adjuster pin 51, and a predetermined gap (gap) is provided between the inner surface of the insertion hole 52a and the adjuster pin 51.
  • the first wheel 52 rotates relative to the nut member 41 when the adjuster pin 51 moves up and down with the rotation of the operating shaft 20 and the adjuster pin 51 presses the inner surface of the insertion hole 52a. ing.
  • the second wheel 53 is also a cylindrical member, and is provided to be rotatable relative to the nut member 41 at the outer peripheral portion of the nut member 41 (a position on the right side of the first wheel 52).
  • a first tapered surface 53 a that narrows toward the left is formed on the inner surface of the right end portion of the second wheel 53.
  • a second tapered surface 53b that extends toward the left is formed at a position on the left side of the first tapered surface 53a on the inner surface of the second wheel.
  • the wrap spring 54 has one end attached to the first wheel 52 and the other end attached to the second wheel 53, and is provided so as to wrap the outer periphery of the first and second wheels 52, 53.
  • the lap spring 54 is configured to transmit only rotation in one direction of the first wheel 52 to the second wheel 53 based on the rotation direction of the first wheel 52 and the winding direction of the lap spring 54. More specifically, when the first wheel 52 is rotated in the winding direction of the lap spring 54, the inner diameter of the lap spring 54 tends to be reduced, so that the first and second wheels 52 and 53 are clamped by the lap spring 54. The rotation of the first wheel 52 is transmitted to the second wheel 53.
  • the cone member 55 includes a disc-shaped main body portion 55a disposed outside the nut member 41, and an attachment hole 41a formed in the nut member 41 extending leftward from the central portion of the main body portion 55a. It has an insertion portion 55b to be inserted into.
  • the outer peripheral portion of the insertion portion 55b and the mounting hole 41a are each formed in a hexagonal shape, so that the cone member 55 can move relative to the nut member 41 in the left-right direction and can rotate integrally with the nut member 41.
  • the member 41 is provided.
  • a washer 58 is attached to the left end of the insertion portion 55b with a bolt.
  • a clutch spring 56 is provided in a compressed state between the inner surface of the right end of the nut member 41 and the washer 58.
  • the cone member 55 is urged to the left by the elastic force of the clutch spring 56, and the outer peripheral end portion of the main body portion 55 a is held between the first tapered surface 53 a of the second wheel 53. At this time, the second tapered surface 53 b of the second wheel 53 is in contact with the outer peripheral end of the nut member 41.
  • the interlocking gear train 57 is fixed to the left end portion of the nut member 41 and is rotatably provided at a position on the left end side of the slide block 30 and a first gear 57 a that rotates integrally with the nut member 41.
  • the tip of the lever portion 22 of the operating shaft 20 is moved in the brake operating direction (the direction of arrow A in FIG. 1) by the brake actuator according to the operation amount. ) And is swung.
  • the lever portion 22 is swung in this manner, the shaft body 21 is rotated counterclockwise in FIG. 1 by the lever principle.
  • the shaft main body 21 is arranged such that the center of curvature P ⁇ b> 1 of the first curved surface 23 and the center of curvature P ⁇ b> 2 of the second curved surface 24 are offset (offset).
  • the shaft body 21 is rotated counterclockwise, the first curved surface 23 is rotated counterclockwise along the concave curved surface 31 of the slide block 30 via the second bearing 32, and the slide block It is moved in the direction of pressing 30 (the direction against the urging force of the return spring 15). Further, as shown in FIG. 6, the second curved surface 24 is rolled downward on the support plane 18 in the caliper 6. At this time, the protruding portion 25a of the positioning pin 25 and the positioning recess 19 of the support plane 18 are in a state of being engaged at a predetermined pressure angle, similarly to the relationship between the involute gear and the rack. Therefore, the operating shaft 20 is positioned at all the rotational positions from the position before the start of the brake operation to the position rotated in the brake operation direction (brake operation position).
  • the slide block 30 resists the urging force of the return spring 15 and the pad pressing mechanism 40 (nut members 41, 42).
  • the screw members 43 and 44 and the bed member 45) are moved together in a direction approaching the right rotor surface 2R of the disc rotor 2.
  • the right brake pad 5 in contact with the head member 45 is pressed against the right rotor surface 2R.
  • the caliper 6 is moved in the right direction in FIG. 1 using the reaction force when the right brake pad 5 is pressed against the right rotor surface 2R.
  • the left brake pad 4 supported by the pad support portion 6 b of the caliper 6 is pressed against the left rotor surface 2 ⁇ / b> L of the disc rotor 2.
  • the disc rotor 2 is sandwiched from the left and right sides by the left and right brake pads 4 and 5, and the disc rotor 2 and the wheels are braked by the frictional force generated between them.
  • the adjuster pin 51 fixed to the shaft main body 21 moves downward as shown by a two-dot chain line in FIG. Is done.
  • the adjuster pin 51 presses the inner surface of the insertion hole 52a, and the first wheel 52 moves in the direction shown in FIG. It is rotated relative to the nut member 41 in the clockwise direction.
  • the winding direction of the wrap spring 54 is provided so as to be the same direction as the rotation direction (counterclockwise) of the first wheel 52.
  • the inner diameter of the lap spring 54 tends to be reduced, so that the first and second wheels 52 and 53 are sandwiched by the lap spring 54, and the first wheel 52 The rotation is transmitted to the second wheel 53, and the second wheel 53 is rotated counterclockwise.
  • the cone member 55 (main body portion 55a) whose rotational force is sandwiched between the first tapered surfaces 53a of the second wheel 53 as shown in FIG.
  • the cone member 55 and the nut member 41 are integrally rotated counterclockwise in FIG. 8 as a result of being transmitted to the nut member 41 in contact with the second tapered surface 53b.
  • the screw cut on the inner peripheral surface of the nut member 41 and the outer peripheral surface of the screw member 43 is a direction in which the screw member 43 approaches the right rotor surface 2R of the disc brake 2 when the nut member 41 is rotated counterclockwise.
  • the nut member 41 is relatively moved. Therefore, when the nut member 41 is rotated counterclockwise, the screw member 43 is moved relative to the nut member 41 in a direction approaching the right rotor surface 2R.
  • the counterclockwise rotation of the nut member 41 is transmitted to the rear nut member 42 via the interlocking gear train 57 (first to third gears 57a to 57c), and the nut member 42 is also rotated counterclockwise. Rotated (see FIG. 4).
  • the screws cut in the rear nut member 42 and the screw member 44 are also configured in the same manner as the nut member 41 and the screw member 43. Therefore, the screw member 44 is also moved relative to the nut member 42 in the direction approaching the right rotor surface 2R by the same amount of movement as the screw member 43.
  • the right brake pad 5 is moved in a direction approaching the right rotor surface 2R via the head member 45 attached to the screw members 43, 44.
  • the first curved surface 23 of the shaft main body 21 is rotated clockwise in FIG. 1 along the concave curved surface 31 of the slide block 30 via the second bearing 32. While rotating, it is moved in a direction away from the right rotor surface 2R (right direction). Further, as shown in FIG. 6, the second curved surface 24 is rolled upward on the support plane 18 in the caliper 6. At this time, the protrusion 25a of the positioning pin 25 and the positioning recess 19 of the support plane 18 are in mesh with each other at a predetermined pressure angle, as in the relationship between the involute gear and the rack.
  • the first and second curved surfaces 23, 24 move, the shaft body 21 is rotated clockwise, and the lever portion 22 is swung in the brake release direction (the direction opposite to the arrow A in FIG. 1).
  • the second curved surface 24 rolls upward on the support plane 18, and the protrusion 25 a of the positioning pin 25 and the positioning recess 19 of the support plane 18 are engaged with each other.
  • the lever portion 22 swings in the brake release direction until the position becomes the reference position in the brake release state.
  • the adjuster pin 51 fixed to the shaft body 21 is moved upward as shown by the solid line in FIG.
  • the adjuster pin 51 presses the inner surface of the insertion hole 52a, and the first wheel 52 is It is rotated relative to the nut member 41 around.
  • the winding direction of the lap spring 54 is as described above, when the first wheel 52 is rotated clockwise, the inner diameter of the lap spring 54 tends to increase, so In addition, the coupling force between the second wheels 52 and 53 is reduced, and the rotation of the first wheel 52 is not transmitted to the second wheel 53.
  • the nut member 41 is not rotated clockwise, and the screw member 43 is not moved relative to the nut member 41 in the direction away from the right rotor surface 2R. Therefore, an appropriate distance between the right brake pad 5 and the right rotor surface 2R adjusted when the brake is operated is maintained as it is.
  • the operating shaft 20 is positioned in the positioning recess 19 of the support plane 18 provided on the inner surface of the caliper 6 at all rotational positions between the position before the brake operation is started and the brake operation position. It has a positioning pin 25 (projecting portion 25a) that is inserted into the gear and meshed at a predetermined pressure angle as in the relationship between the involute gear and the rack. Therefore, the operating shaft 20 can be positioned at all the rotational positions by the positioning pins 25 and the positioning recesses 19, and variations in the rotational positions of the operating shaft 20 can be suppressed. Therefore, it is possible to prevent the component parts from interfering with each other during the brake operation, and to exhibit a stable braking force with respect to the brake operation.
  • the positioning pin 25 since the portion of the positioning pin 25 that contacts the inner surface of the positioning recess 19 is formed by an involute curve, the positioning pin and the positioning recess can be easily manufactured, and the manufacturing cost can be reduced. Further, since the positioning pin 25 is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, the assembling direction of the positioning pin 25 can be eliminated, and the positioning pin 25 is damaged due to an assembly error. Can be prevented. Further, the radius R2 (shaft rolling surface radius) of the second curved surface 24 of the operating shaft 20 is set to be equal to the meshing pitch circle radius of the positioning pin 25 and the positioning recess 19 and the pressure of the positioning pin (involute) is set.
  • the positioning pin 25 Since the angle is set to be larger than the pressure angle of the positioning recess, the positioning pin 25 is held while the gap between the positioning pin 25 and the positioning recess 19 is kept substantially constant (exactly slightly increased) when the operating shaft 20 rotates.
  • the positioning pin 25 can be prevented from being damaged even in a high load state during the operation of the brake.
  • the positioning pins 25 are provided at the center portion and the rear end portion in the front-rear direction on the second curved surface 24 of the operating shaft 20, the axis of the operating shaft 20 is moved vertically by the two positioning pins 25. Tilt can be prevented.
  • the portion of the positioning pin 25 (projecting portion 25a) that contacts the inner surface of the positioning recess 19 is formed by an involute curve, but other than an involute curve, other than an Icroid curve, a trochoid curve, etc. It may be formed by the following curve.
  • the configuration is formed by an involute curve, the positioning pins and the positioning recesses can be easily manufactured, and the manufacturing cost can be reduced.
  • the positioning pin 25 (projecting portion 25a) is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, but is not substantially conical and contacts the inner surface of the positioning recess 19. Another shape in which the portion is formed by an involute curve may be used. Further, the positioning pins 25 are provided at the center portion and the rear end portion in the front-rear direction on the second curved surface 24 of the operating shaft 20, respectively, but may be provided at positions other than the center portion and the rear end portion. . Furthermore, the number of positioning pins 25 may be one.
  • the two positioning recesses 19 are provided corresponding to the two positioning pins 25.
  • the positioning recesses 19 are formed in a single groove shape, that is, a so-called rack shape in which the two recesses are connected in the front-rear direction. May be.

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

Abstract

A disk brake device (1) according to the present invention is configured so that a brake shaft (20) that constitutes a pad pressing device (10) for pressing brake pads (4, 5) against rotor surfaces (2L, 2R) comprises a positioning pin (25) that: is in contact with the inner surface of a positioning recess (19) that is formed on a brake housing (6) between all rotation positions from a pre-brake operation start position to a position that is reached by rotating in the brake operation direction; and that performs positioning of the brake shaft (20).

Description

ディスクブレーキ装置Disc brake device
　本発明は、自動車等に搭載されるディスクブレーキ装置に関する。 The present invention relates to a disc brake device mounted on an automobile or the like.
　このようなディスクブレーキ装置として、自動車等の車輪とともに回転するディスクロータと、このディスクロータを挟むように対向配置された一対のブレーキパッドと、ディスクロータの外周を跨いで設けられディスクロータのロータ面に垂直な方向に移動可能に設けられたキャリパとを備えた構成のフローティングタイプのブレーキ装置が知られている（例えば、特許文献１および２を参照）。このディスクブレーキ装置では、一方のブレーキパッド側だけにブレーキアクチュエータを有し、このブレーキアクチュエータの作動により一方のブレーキパッドをロータ面に押し付けるとともに、その反力を用いてキャリパを介して他方のブレーキパッドを引き寄せて反対側のロータ面に押し付け、一対のブレーキパッドによってディスクロータを両側から挟み、両者の間の摩擦力によりディスクロータおよび車輪の回転を制動するように構成されている。 As such a disc brake device, a disc rotor that rotates with a wheel of an automobile, etc., a pair of brake pads arranged so as to sandwich the disc rotor, and a rotor surface of the disc rotor provided across the outer periphery of the disc rotor There is known a floating type brake device including a caliper provided so as to be movable in a direction perpendicular to the vertical direction (see, for example, Patent Documents 1 and 2). In this disc brake device, a brake actuator is provided only on one brake pad side, and one brake pad is pressed against the rotor surface by the operation of the brake actuator, and the other brake pad is passed through the caliper using the reaction force. Are pushed against the rotor surface on the opposite side, the disc rotor is sandwiched from both sides by a pair of brake pads, and the rotation of the disc rotor and wheels is braked by the frictional force between them.
　上記のようなディスクブレーキ装置は、ブレーキアクチュエータの作動によりブレーキパッドをディスクロータのロータ面に押し付けるためのパッド押圧装置を有している。このパッド押圧装置は、ロータ面に略平行に配置されたブレーキシャフトを有しており、このブレーキシャフトをブレーキアクチュエータの作動によりブレーキ作動方向に回動させることでブレーキパッドをロータ面に押し付けるように構成されている。また、ブレーキ操作が解除されると、ブレーキシャフトはスプリングの付勢力によりブレーキ解除方向に回動されてブレーキパッドをロータ面から離すように構成されている。 The disc brake device as described above has a pad pressing device for pressing the brake pad against the rotor surface of the disc rotor by the operation of the brake actuator. This pad pressing device has a brake shaft arranged substantially parallel to the rotor surface, and the brake pad is pressed against the rotor surface by rotating the brake shaft in the brake operating direction by the operation of the brake actuator. It is configured. Further, when the brake operation is released, the brake shaft is rotated in the brake release direction by the urging force of the spring to separate the brake pad from the rotor surface.
特許第３８８１７１０号Japanese Patent No. 3881710 特許第３９６０３９６号Japanese Patent No. 3960396
　ところで、従来のディスクブレーキ装置において、ブレーキシャフトが、ディスクロータ方向（左右方向）および上下方向の移動を組み合わせた複雑な回動軌跡を描きながら回動し、ブレーキパッドをディスクロータのロータ面に押し付けるように構成されたものがある。この方式は、すべり軸受によりブレーキシャフトを支持する方式に比べて摩擦抵抗が低いという利点がある。しかしながら、ブレーキシャフトを、ブレーキ作動開始前の位置からブレーキ作動位置までの間の全ての回動位置において位置決めすることが難しいという課題があった。そして、ブレーキシャフトの回動位置がばらつくと、ブレーキ作動中に構成部品が干渉し、破損する可能性があるという課題があった。 By the way, in a conventional disc brake device, the brake shaft rotates while drawing a complicated turning locus combining movement in the disc rotor direction (left-right direction) and up-down direction, and presses the brake pad against the rotor surface of the disc rotor. There is something configured as follows. This method has an advantage that the frictional resistance is lower than the method in which the brake shaft is supported by the slide bearing. However, there is a problem that it is difficult to position the brake shaft at all the rotational positions between the position before the brake operation is started and the brake operation position. And if the rotation position of the brake shaft varies, there is a problem that the components may interfere with each other during the operation of the brake and may be damaged.
　本発明は、このような課題に鑑みてなされたものであり、ブレーキシャフトの回動位置のばらつきを抑え、ブレーキ作動中に構成部品が干渉して破損することを防ぐことができるディスクブレーキ装置を提供することを目的とする。 The present invention has been made in view of such a problem, and provides a disc brake device that can suppress variations in the rotational position of the brake shaft and prevent components from interfering with each other and breaking during braking. The purpose is to provide.
　前記課題を解決するために、本発明に係るディスクブレーキ装置は、車輪とともに回転するディスクロータと、前記ディスクロータのロータ面に対向して設けられたブレーキパッドと、前記ブレーキパッドを前記ロータ面に押し付けるためのパッド押圧装置と、前記パッド押圧装置を内部に収容するブレーキハウジング（例えば、実施形態におけるキャリパ６）とを備え、前記パッド押圧装置により前記ブレーキパッドを前記ロータ面に押し付け、両者の間に発生する摩擦力により前記ディスクロータおよび前記車輪の制動を行うように構成される。その上で、前記パッド押圧装置は、ブレーキ操作が行われたときに作動するブレーキアクチュエータと、前記ロータ面に略平行に配置されて前記ブレーキアクチュエータの作動によりブレーキ作動方向に回動するブレーキシャフト（例えば、実施形態におけるオペレーティングシャフト２０）と、前記ブレーキシャフトの回動により前記ブレーキパッドを前記ロータ面に近づく方向に移動させるパッド押動機構と、ブレーキ操作が解除されたときに前記パッド押動機構を前記ロータ面から離れる方向に移動させるとともに前記ブレーキシャフトをブレーキ解除方向に回動させるブレーキ解除スプリング（例えば、実施形態におけるリターンスプリング１５）とを備える。そして、前記ブレーキシャフトは、ブレーキ作動開始前の位置からブレーキ作動方向に回動された位置までの間の全ての回動位置において前記ブレーキハウジングに形成された位置決め凹部の内面と当接して前記ブレーキシャフトの位置決めを行う位置決めピンを有して構成される。 In order to solve the above problems, a disc brake device according to the present invention includes a disc rotor that rotates together with a wheel, a brake pad that is provided to face the rotor surface of the disc rotor, and the brake pad that is disposed on the rotor surface. A pad pressing device for pressing, and a brake housing (for example, caliper 6 in the embodiment) that accommodates the pad pressing device therein, and the brake pad is pressed against the rotor surface by the pad pressing device; The disc rotor and the wheel are braked by the frictional force generated in the wheel. In addition, the pad pressing device includes a brake actuator that operates when a brake operation is performed, and a brake shaft that is disposed substantially parallel to the rotor surface and rotates in the brake operation direction by the operation of the brake actuator ( For example, the operating shaft 20) in the embodiment, a pad pushing mechanism that moves the brake pad in a direction approaching the rotor surface by turning the brake shaft, and the pad pushing mechanism when the brake operation is released. And a brake release spring (for example, the return spring 15 in the embodiment) that moves the brake shaft in the brake release direction. The brake shaft abuts against the inner surface of the positioning recess formed in the brake housing at all rotation positions from the position before the brake operation start to the position rotated in the brake operation direction. It has a positioning pin for positioning the shaft.
　なお、上記構成のディスクブレーキ装置において、前記位置決めピンは、前記位置決め凹部の内面に当接する部分における断面がインボリュート曲線を有した略台形状に形成され、前記位置決め凹部は、前記位置決めピンと当接する部分における断面が台形状の凹みからなることが好ましい。また、このように構成された場合において、前記位置決めピンは、外周面全体においてインボリュート曲線を有した略円錐状に形成され、前記位置決め凹部は、全周において断面が台形状となる略円錐状の凹みからなることが好ましい。さらに、このように構成された場合において、前記ブレーキシャフトにおける前記位置決めピンが設けられた部分の外周面は、前記位置決めピンと前記位置決め凹部の噛み合いピッチ円半径と等しい半径を有する曲面形状に形成されることが好ましい。 In the disc brake device having the above-described configuration, the positioning pin is formed in a substantially trapezoidal shape with a cross section having an involute curve at a portion contacting the inner surface of the positioning recess, and the positioning recess is a portion contacting the positioning pin. It is preferable that the cross section in is composed of a trapezoidal depression. Further, in this case, the positioning pin is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, and the positioning recess has a substantially conical shape having a trapezoidal cross section on the entire periphery. It is preferable to consist of a dent. Further, in this case, the outer peripheral surface of the portion where the positioning pin is provided in the brake shaft is formed in a curved surface shape having a radius equal to the meshing pitch circle radius of the positioning pin and the positioning recess. It is preferable.
　また、上記構成のディスクブレーキ装置において、前記位置決めピンは、前記ブレーキシャフトにおいて軸方向に少なくとも２つ設けられていることが好ましい。 In the disc brake device having the above-described configuration, it is preferable that at least two positioning pins are provided in the axial direction on the brake shaft.
　本発明に係るディスクブレーキ装置によれば、ブレーキシャフトが、ブレーキ作動開始前の位置からブレーキ作動位置までの間の全ての回動位置において、ブレーキハウジングの位置決め凹部の内面と当接してブレーキシャフトの位置決めを行う位置決めピンを有して構成される。そのため、ブレーキシャフトを全ての回動位置において位置決めすることができ、ブレーキシャフトの回動位置のばらつきを抑えることができる。従って、ブレーキ作動中に構成部品が干渉して破損することを防ぐことができ、ブレーキ操作に対して安定した制動力を発揮することができる。 According to the disc brake device of the present invention, the brake shaft comes into contact with the inner surface of the positioning recess of the brake housing at all the rotational positions between the position before the brake operation is started and the brake operation position. It has a positioning pin for positioning. Therefore, the brake shaft can be positioned at all the rotation positions, and variations in the rotation positions of the brake shaft can be suppressed. Therefore, it is possible to prevent the component parts from interfering with each other during the brake operation, and to exhibit a stable braking force with respect to the brake operation.
　また、位置決めピンを、位置決め凹部の内面に当接する部分における断面がインボリュート曲線を有した略台形状に形成し、位置決め凹部を、位置決めピンと当接する部分における断面が台形状の凹みからなる構成とすれば、位置決めピンおよび位置決め凹部の製造が容易となり、製造コストも抑えることができる。またこのとき、位置決めピンを、外周面全体においてインボリュート曲線を有した略円錐状に形成し、位置決め凹部を、全周において断面が台形状となる略円錐状の凹みからなる構成とすれば、位置決めピンの組立方向性を無くすことができるので、組立誤差により位置決めピンが破損するようなことを防ぐことができる。さらにこのとき、ブレーキシャフトにおける位置決めピンが設けられた部分の外周面を、位置決めピンと位置決め凹部の噛み合いピッチ円半径と等しい半径を有する曲面形状に形成し、且つ位置決めピン（インボリュート）の圧力角を位置決め凹部の圧力角より大きく設定する構成とすれば、ブレーキシャフトが回動するときに位置決めピンと位置決め凹部の隙間を略一定（正確には微増）に保持しつつ、位置決めピンに負荷がかからないようにすることができ、ブレーキ作動中の高い荷重状態でも位置決めピンの破損を防ぐことができる。なお、位置決めピンおよび位置決め凹部の圧力角が一致していると、噛み合いによる挙動が生じ、制作誤差により位置決めピンと位置決め凹部の接触による挙動と、ピッチ線上の転がりによる挙動との間には誤差が生じる。また、ブレーキシャフトが回動途中に何らかの原因によってブレーキのクランプ力が失われた状態になると、ブレーキシャフトの前記外周面（転動面）にかかっていた押付力が失われるので、この転動面は容易にずれてしまう。このずれた状態で再びクランプ力が復活すると、本来と違う位置でピッチ円の転がりが始まるので、ブレーキ装置の内部機構にブレーキ作動による干渉などが発生する可能性がある。そこで、上記のように位置決めピンの圧力角を位置決め凹部の圧力角より大きく設定する構成とすれば、ブレーキシャフトが回動中にクランプ力が喪失されてずれた状態となり、再びクランプ力が復活した場合でも、その位置ずれは僅かなずれですみ、またこの位置を初期位置として位置決めピンが位置決め凹部との隙間が微増する方向に回動していくため、位置決めピンに負荷がかからないようにすることができる。 Further, the positioning pin is formed in a substantially trapezoidal shape in which the cross section at the portion contacting the inner surface of the positioning recess has an involute curve, and the positioning recess is configured by a trapezoidal recess in the portion contacting the positioning pin. Thus, the positioning pins and the positioning recesses can be easily manufactured, and the manufacturing cost can be reduced. Further, at this time, if the positioning pin is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, and the positioning recess is formed of a substantially conical recess having a trapezoidal cross section on the entire circumference, the positioning pin Since the assembling direction of the pin can be eliminated, it is possible to prevent the positioning pin from being damaged due to an assembly error. Further, at this time, the outer peripheral surface of the portion where the positioning pin is provided on the brake shaft is formed in a curved surface shape having a radius equal to the engagement pitch circle radius of the positioning pin and the positioning recess, and the pressure angle of the positioning pin (involute) is positioned If the pressure angle is set to be larger than the pressure angle of the recess, the positioning pin and the positioning recess are kept substantially constant (precisely slightly increased) while the brake shaft rotates, and the positioning pin is not loaded. It is possible to prevent the positioning pin from being damaged even in a high load state during brake operation. If the pressure angles of the positioning pin and the positioning recess are the same, a behavior due to meshing occurs, and an error occurs between the behavior due to contact between the positioning pin and the positioning recess due to production errors and the behavior due to rolling on the pitch line. . In addition, if the brake clamping force is lost due to some reason during the rotation of the brake shaft, the pressing force applied to the outer peripheral surface (rolling surface) of the brake shaft is lost. Is easily displaced. When the clamping force is restored again in this shifted state, the pitch circle starts rolling at a position different from the original position, which may cause interference due to brake operation in the internal mechanism of the brake device. Therefore, if the pressure angle of the positioning pin is set to be larger than the pressure angle of the positioning recess as described above, the clamping force is lost and shifted while the brake shaft is rotating, and the clamping force is restored again. Even in this case, the positional deviation is only slight, and the positioning pin is rotated in the direction in which the clearance from the positioning recess slightly increases with this position as the initial position, so that no load is applied to the positioning pin. Can do.
　また、位置決めピンをブレーキシャフトにおいて軸方向に少なくとも２つ設ける構成とすれば、この２つの位置決めピンによりブレーキシャフトの軸が傾くことを防ぐことができる。 Further, if at least two positioning pins are provided in the axial direction of the brake shaft, the two positioning pins can prevent the axis of the brake shaft from being inclined.
本発明に係るディスクブレーキ装置の略中央部における垂直断面図である。1 is a vertical cross-sectional view at a substantially central portion of a disc brake device according to the present invention. 図１に示す矢印II-IIの位置における水平断面図である。It is a horizontal sectional view in the position of arrow II-II shown in FIG. 図２に示す矢印III-IIIの位置における垂直断面図である。FIG. 3 is a vertical sectional view at the position of arrow III-III shown in FIG. 2. 図３に示す矢印IV-IVの位置における水平断面図である。FIG. 4 is a horizontal sectional view at the position of arrow IV-IV shown in FIG. 3. 位置決めピンを示す図であり、(ａ)は正面図、(ｂ)は(ａ)に示す矢印ｂ-ｂの位置における断面図である。It is a figure which shows a positioning pin, (a) is a front view, (b) is sectional drawing in the position of arrow bb shown to (a). 図１における位置決めピン周辺の拡大図である。FIG. 2 is an enlarged view around a positioning pin in FIG. 1. 図４におけるアジャスタ機構周辺の拡大図である。FIG. 5 is an enlarged view around the adjuster mechanism in FIG. 4. 図４に示す矢印VIII‐VIIIの位置における断面図である。It is sectional drawing in the position of arrow VIII-VIII shown in FIG.
　以下、本発明の実施形態について図面を参照して説明する。本発明の一実施形態に係るディスクブレーキ装置を図１～図４に示している。なお、以下では、説明の便宜上、図中に示す上下、左右および前後の矢印の方向をそれぞれ、上下方向、左右方向、前後方向と称して説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. A disc brake device according to an embodiment of the present invention is shown in FIGS. In the following, for convenience of explanation, the directions of the up and down, left and right and front and rear arrows shown in the figure will be referred to as the up and down direction, the left and right direction, and the front and rear direction, respectively.
　ディスクブレーキ装置１は、図１に示すように、自動車等の車輪とともに回転する円盤状のディスクロータ２と、アスクル（車軸を受けるケース）に固定されたキャリア３と、キャリア３においてディスクロータ２を左右に挟むように対向配置された一対のブレーキパッド４，５と、キャリア３においてディスクロータ２に対して左右方向に移動可能に設けられたキャリパ６と、エアもしくは油圧により作動するブレーキアクチュエータ（図示せず）と、ブレーキアクチュエータの作動により左右のブレーキパッド４，５をディスクロータ２の左右側面２Ｌ，２Ｒ（以下、ロータ面２Ｌ，２Ｒと称する）にそれぞれ押し付けるためのパッド押圧装置１０とを有して構成されるフローティングタイプのディスクブレーキ装置である。 As shown in FIG. 1, the disc brake device 1 includes a disc-like disc rotor 2 that rotates together with a wheel of an automobile or the like, a carrier 3 that is fixed to an axle (a case that receives an axle), and the disc rotor 2 in the carrier 3. A pair of brake pads 4 and 5 disposed so as to be sandwiched between the right and left, a caliper 6 provided on the carrier 3 so as to be movable in the left-right direction with respect to the disc rotor 2, and a brake actuator (FIG. And a pad pressing device 10 for pressing the left and right brake pads 4 and 5 against the left and right side surfaces 2L and 2R (hereinafter referred to as rotor surfaces 2L and 2R) of the disc rotor 2 by the operation of the brake actuator. This is a floating type disc brake device.
　キャリア３には、ディスクロータ２のロータ面２Ｌ，２Ｒ（ブレーキパッドが押し付けられる面）に略直交する方向に延びるガイドスリーブ９ａ，９ｂがボルトによって取り付けられている（図４を参照）。キャリパ６は、ガイドスリーブ９ａ，９ｂにガイドされてロータ面２Ｌ，２Ｒに略直交する方向（左右方向）に移動可能に設けられている。キャリパ６は、ガイドスリーブ９ａ，９ｂに接続され内部にパッド押圧装置１０を収容する押圧機構収容部６ａと、左ブレーキパッド４を支持するパッド支持部６ｂと、これら収容部６ａおよび支持部６ｂを連結する連結部６ｃとを有して構成されている。 The guide sleeves 9a and 9b extending in a direction substantially orthogonal to the rotor surfaces 2L and 2R (surfaces against which the brake pads are pressed) of the disc rotor 2 are attached to the carrier 3 by bolts (see FIG. 4). The caliper 6 is guided by the guide sleeves 9a and 9b and is provided so as to be movable in a direction (right and left direction) substantially orthogonal to the rotor surfaces 2L and 2R. The caliper 6 is connected to the guide sleeves 9a and 9b and includes a pressing mechanism accommodating portion 6a that accommodates the pad pressing device 10 therein, a pad supporting portion 6b that supports the left brake pad 4, and the accommodating portion 6a and the supporting portion 6b. And a connecting portion 6c to be connected.
　左右のブレーキパッド４，５は、ディスクロータ２のロータ面２Ｌ，２Ｒに接触されるパッド部材４ａ，５ａと、パッド部材４ａ，５ａの裏面側（ディスクロータ２との非接触面側）に取り付けられた金属製のプレート部材４ｂ，５ｂとを有して構成される。 The left and right brake pads 4 and 5 are attached to the pad members 4a and 5a that are in contact with the rotor surfaces 2L and 2R of the disc rotor 2, and the back surfaces of the pad members 4a and 5a (the non-contact surface side with the disc rotor 2). The metal plate members 4b and 5b are formed.
　パッド押圧装置１０は、ブレーキ操作が行われたときに作動するブレーキアクチュエータ（図示せず）、オペレーティングシャフト２０、スライドブロック３０、リターンスプリング１５、パッド押動機構４０およびアジャスタ機構５０を有して構成される。オペレーティングシャフト２０は、ディスクロータ２のロータ面に略平行且つ前後方向に延びるシャフト本体２１と、シャフト本体２１の略中央部から上方に延びるレバー部２２と有して構成される。レバー部２２の上端部には、ブレーキアクチュエータの作動部の先端が接続される凹部２２ａが形成されている。 The pad pressing device 10 includes a brake actuator (not shown) that operates when a brake operation is performed, an operating shaft 20, a slide block 30, a return spring 15, a pad pushing mechanism 40, and an adjuster mechanism 50. Is done. The operating shaft 20 includes a shaft main body 21 that extends substantially parallel to the rotor surface of the disc rotor 2 and extends in the front-rear direction, and a lever portion 22 that extends upward from a substantially central portion of the shaft main body 21. At the upper end portion of the lever portion 22, a concave portion 22 a to which the tip of the operating portion of the brake actuator is connected is formed.
　シャフト本体２１は、図３に示すように、ディスクロータ２に向いた側面において半径Ｒ１の略半円形状の第１曲面２３を有し、ディスクロータ２と反対側の面（キャリパ６の右側内面に向いた側面）において半径Ｒ２（Ｒ２＜Ｒ１）の略半円形状の第２曲面２４を有して構成されている。第１曲面２３の曲率中心Ｐ１と第２曲面２４の曲率中心Ｐ２とは上下方向にずれた配置となっている。図２に示すように、第１曲面２３は、レバー部２２を挟むように前後にそれぞれ設けられている。第２曲面２４には、前後方向における中央部および後端部にそれぞれ位置決めピン２５，２５が設けられている。 As shown in FIG. 3, the shaft body 21 has a substantially semicircular first curved surface 23 having a radius R <b> 1 on the side facing the disc rotor 2, and the surface opposite to the disc rotor 2 (the right inner surface of the caliper 6). The second curved surface 24 having a substantially semicircular shape with a radius R2 (R2 <R1). The center of curvature P1 of the first curved surface 23 and the center of curvature P2 of the second curved surface 24 are shifted in the vertical direction. As shown in FIG. 2, the first curved surface 23 is provided on the front and rear sides so as to sandwich the lever portion 22. The second curved surface 24 is provided with positioning pins 25 and 25 at the center portion and the rear end portion in the front-rear direction, respectively.
　位置決めピン２５がシャフト本体２１に取り付けられ、その時にシャフト本体２１から突出する突出部２５ａは、図５に示すように、外周面全体においてインボリュート曲線を有した略円錐状に形成されている。すなわち、突出部２５ａは、図５（ａ）に示す正面図において中心軸Ｃを通り且つ紙面に垂直ないずれの断面においても、その断面は図５（ｂ）に示すようにインボリュート曲線を有した略台形状に形成されている。 The positioning pin 25 is attached to the shaft main body 21, and the protrusion 25a protruding from the shaft main body 21 at that time is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface as shown in FIG. That is, the protrusion 25a has an involute curve as shown in FIG. 5 (b) in any cross section passing through the central axis C and perpendicular to the paper surface in the front view shown in FIG. 5 (a). It is formed in a substantially trapezoidal shape.
　図１および図６に示すように、キャリパ６（押圧機構収容部６ａ）の右側内面には、ディスクロータ２のロータ面と略平行な支持平面１８が設けられている。この支持平面１８には、位置決めピン２５の突出部２５ａの形状に対応した略円錐状の位置決め凹部１９が形成されている。この位置決め凹部１９に突出部２５ａが挿入された状態において、シャフト本体２１の第２曲面２４および突出部２５ａと位置決め凹部１９が形成された支持平面１８とが、その断面においてインボリュート歯車（外接歯車）とラックの関係と同様の関係になっている。さらに、第２曲面２４の半径Ｒ２（シャフト転動面半径）は、噛み合いピッチ円半径に等しくなるように設定され、且つ突出部２５ａ（インボリュート）の圧力角が位置決め凹部１９の圧力角より大きくなるように設定されており、このような諸元のインボリュート歯車とラックの関係と同様の関係になっている。 As shown in FIGS. 1 and 6, a support plane 18 that is substantially parallel to the rotor surface of the disk rotor 2 is provided on the right inner surface of the caliper 6 (pressing mechanism accommodating portion 6a). A substantially conical positioning recess 19 corresponding to the shape of the protrusion 25 a of the positioning pin 25 is formed in the support plane 18. In a state where the protruding portion 25a is inserted into the positioning recess 19, the second curved surface 24 and the protruding portion 25a of the shaft body 21 and the support plane 18 on which the positioning recess 19 is formed are involute gears (external gears) in the cross section. The relationship is similar to that of racks. Further, the radius R2 (shaft rolling surface radius) of the second curved surface 24 is set to be equal to the meshing pitch circle radius, and the pressure angle of the protrusion 25a (involute) is larger than the pressure angle of the positioning recess 19. Thus, the relationship is similar to the relationship between the involute gear of such specifications and the rack.
　スライドブロック３０は、図１～図４に示すように、オペレーティングシャフト２０よりもディスクロータ２に近い側においてオペレーティングシャフト２０に隣接して設けられている。スライドブロック３０は、キャリパ６（押圧機構収容部６ａ）内に設けられた第１ベアリング３５によりガイドされてディスクロータ２のロータ面に略直交する方向（左右方向）に移動可能に設けられている。スライドブロック３０は、シャフト本体２１の第１曲面２３と対向する面において第１曲面２３に対応する略半円形状の凹曲面３１を有している。この凹曲面３１には第２ベアリング３２（例えばニードルベアリング）が設けられている。スライドブロック３０の前端部および後端部には、シャフト本体２１の前後端部をそれぞれ支持してシャフト本体２１の前後移動を規制するシャフト支持部３３，３３が設けられている（図２を参照）。 1 to 4, the slide block 30 is provided adjacent to the operating shaft 20 on the side closer to the disc rotor 2 than the operating shaft 20. The slide block 30 is guided by a first bearing 35 provided in the caliper 6 (pressing mechanism accommodating portion 6a), and is provided so as to be movable in a direction (right and left direction) substantially orthogonal to the rotor surface of the disk rotor 2. . The slide block 30 has a substantially semicircular concave curved surface 31 corresponding to the first curved surface 23 on the surface facing the first curved surface 23 of the shaft body 21. The concave curved surface 31 is provided with a second bearing 32 (for example, a needle bearing). Shaft support portions 33 and 33 are provided at the front end portion and the rear end portion of the slide block 30 to support the front and rear end portions of the shaft main body 21 and restrict the front and rear movement of the shaft main body 21 (see FIG. 2). ).
　リターンスプリング１５は、キャリパ６（押圧機構収容部６ａ）内部の左端側の位置に設けられた壁部１７とスライドブロック３０の左端部に形成されたバネ支持凹部３４との間において圧縮された状態で設けられている。このリターンスプリング１５の弾性力によりスライドブロック３０はオペレーティングシャフト２０側に付勢されている。そして、スライドブロック３０の凹曲面３１が第２ベアリング３２を介してシャフト本体２１の第１曲面２３に当接されている。さらに、シャフト本体２１の第２曲面２４がキャリパ６内の支持平面１８に当接されている。このとき、第２曲面２４に設けられた位置決めピン２５の突出部２５ａが支持平面１８に形成された位置決め凹部１９に挿入された状態となっている。 The return spring 15 is compressed between the wall portion 17 provided at the position on the left end side inside the caliper 6 (pressing mechanism accommodating portion 6a) and the spring support recess portion 34 formed at the left end portion of the slide block 30. Is provided. The slide block 30 is biased toward the operating shaft 20 by the elastic force of the return spring 15. The concave curved surface 31 of the slide block 30 is in contact with the first curved surface 23 of the shaft body 21 via the second bearing 32. Further, the second curved surface 24 of the shaft body 21 is in contact with the support plane 18 in the caliper 6. At this time, the protruding portion 25 a of the positioning pin 25 provided on the second curved surface 24 is inserted into the positioning recess 19 formed in the support plane 18.
　このようにオペレーティングシャフト２０は、リターンスプリング１５によりスライドブロック３０を介して支持平面１８に押し付けられて左右方向の移動が規制されるとともに、スライドブロック３０のシャフト支持部３３，３３により前後方向の移動が規制された状態で支持されている。また、オペレーティングシャフト２０は、スライドブロック３０の凹曲面３１と第１曲面２３の当接および位置決めピン２５の突出部２５ａと支持平面１８の位置決め凹部１９の嵌合により上下方向の移動も規制された状態で支持されている。さらに、オペレーティングシャフト２０は、スライドブロック３０の凹曲面３１に設けられた第２ベアリング３２により第１曲面２３が凹曲面３１に沿って回転移動可能な状態で支持されている。 As described above, the operating shaft 20 is pressed against the support plane 18 via the slide block 30 by the return spring 15 so as to be restricted from moving in the left-right direction, and moved in the front-rear direction by the shaft support portions 33, 33 of the slide block 30. Is supported in a regulated state. The operating shaft 20 is also restricted from moving in the vertical direction by the contact of the concave curved surface 31 of the slide block 30 with the first curved surface 23 and the fitting of the protruding portion 25a of the positioning pin 25 and the positioning concave portion 19 of the support plane 18. Supported by the state. Further, the operating shaft 20 is supported by a second bearing 32 provided on the concave curved surface 31 of the slide block 30 in a state where the first curved surface 23 can be rotationally moved along the concave curved surface 31.
　パッド押動機構４０は、図２および図４に示すように、スライドブロック３０に連結された前後一対のナット部材４１，４２と、前後のナット部材４１，４２にそれぞれ取り付けられたスクリュー部材４３，４４と、スクリュー部材４３，４４の先端部（左端部）に取り付けられたヘッド部材４５とを有して構成される。ナット部材４１，４２は、略円筒形状の部材であり、スライドブロック３０に連結されてスライドブロック３０とともにディスクロータ２のロータ面に略直交する方向（左右方向）に移動可能に構成されている。ナット部材４１，４２の内周面にはネジが切られている。 2 and 4, the pad pushing mechanism 40 includes a pair of front and rear nut members 41 and 42 connected to the slide block 30, and screw members 43 and 42 attached to the front and rear nut members 41 and 42, respectively. 44 and a head member 45 attached to the tip end portions (left end portions) of the screw members 43 and 44. The nut members 41 and 42 are substantially cylindrical members and are configured to be connected to the slide block 30 so as to be movable together with the slide block 30 in a direction (left-right direction) substantially perpendicular to the rotor surface of the disk rotor 2. Screws are cut on the inner peripheral surfaces of the nut members 41 and 42.
　スクリュー部材４３，４４は、略円柱形状の部材であり、スクリュー部材４３，４４の外周面にはネジが切られている。スクリュー部材４３，４４は、ナット部材４１，４２内にそれぞれ螺合されて取り付けられている。スクリュー部材４３，４４の先端部にヘッド部材４５が取り付けられている。ヘッド部材４５は、略平板状の部材であり、ヘッド部材４５の左側面に右ブレーキパッド５（プレート部材５ｂ）が接している。 The screw members 43 and 44 are substantially cylindrical members, and the screw members 43 and 44 are threaded on the outer peripheral surfaces. The screw members 43 and 44 are screwed into the nut members 41 and 42, respectively. A head member 45 is attached to the tip of the screw members 43 and 44. The head member 45 is a substantially flat plate-like member, and the right brake pad 5 (plate member 5 b) is in contact with the left side surface of the head member 45.
　アジャスタ機構５０は、図７および図８に示すように、アジャスタピン５１、第１ホイール５２、第２ホイール５３、ラップスプリング５４、コーン部材５５、クラッチスプリング５６および連動ギヤ列５７を有して構成される。アジャスタピン５１は、オペレーティングシャフト２０（シャフト本体２１）の前端面に固定され、オペレーティングシャフト２０の回動に伴って上下方向に移動するようになっている。 7 and 8, the adjuster mechanism 50 includes an adjuster pin 51, a first wheel 52, a second wheel 53, a lap spring 54, a cone member 55, a clutch spring 56, and an interlocking gear train 57. Is done. The adjuster pin 51 is fixed to the front end surface of the operating shaft 20 (shaft body 21), and moves in the vertical direction as the operating shaft 20 rotates.
　第１ホイール５２は、円筒形状の部材であり、ナット部材４１の外周部においてナット部材４１に対して相対回転可能に設けられている。第１ホイール５２には、アジャスタピン５１の先端部が挿入される挿入孔５２ａが形成されている。挿入孔５２ａの内径寸法はアジャスタピン５１の外形よりも大きく形成されており、挿入孔５２ａの内面とアジャスタピン５１との間には所定のギャップ（隙間）を有している。第１ホイール５２は、オペレーティングシャフト２０の回動に伴ってアジャスタピン５１が上下移動し、アジャスタピン５１が挿入孔５２ａの内面を押圧することにより、ナット部材４１に対して相対回転するようになっている。 The first wheel 52 is a cylindrical member, and is provided on the outer peripheral portion of the nut member 41 so as to be rotatable relative to the nut member 41. The first wheel 52 is formed with an insertion hole 52a into which the tip of the adjuster pin 51 is inserted. The inner diameter of the insertion hole 52a is formed larger than the outer shape of the adjuster pin 51, and a predetermined gap (gap) is provided between the inner surface of the insertion hole 52a and the adjuster pin 51. The first wheel 52 rotates relative to the nut member 41 when the adjuster pin 51 moves up and down with the rotation of the operating shaft 20 and the adjuster pin 51 presses the inner surface of the insertion hole 52a. ing.
　第２ホイール５３も、円筒形状の部材であり、ナット部材４１の外周部（第１ホイール５２よりも右方側の位置）においてナット部材４１に対して相対回転可能に設けられている。第２ホイール５３の右端部内面には、左方に向かって狭まる第１テーパ面５３ａが形成されている。また、第２ホイールの内面における第１テーパ面５３ａより左方側の位置には、左方に向かって広がる第２テーパ面５３ｂが形成されている。 The second wheel 53 is also a cylindrical member, and is provided to be rotatable relative to the nut member 41 at the outer peripheral portion of the nut member 41 (a position on the right side of the first wheel 52). A first tapered surface 53 a that narrows toward the left is formed on the inner surface of the right end portion of the second wheel 53. A second tapered surface 53b that extends toward the left is formed at a position on the left side of the first tapered surface 53a on the inner surface of the second wheel.
　ラップスプリング５４は、一端部が第１ホイール５２に取り付けられるとともに他端部が第２ホイール５３に取り付けられ、第１および第２ホイール５２，５３の外周部を包むように設けられている。ラップスプリング５４は、第１ホイール５２の回転方向とラップスプリング５４の巻き方向に基づいて、第１ホイール５２の一方向の回転だけを第２ホイール５３に伝達するように構成されている。より詳細には、第１ホイール５２がラップスプリング５４の巻き方向に回転されたときには、ラップスプリング５４の内径が小さくなろうとするため、ラップスプリング５４により第１および第２ホイール５２，５３が挟持され、第１ホイール５２の回転が第２ホイール５３に伝達される。一方、第１ホイール５２がラップスプリング５４の巻き方向と反対方向に回転されたときには、ラップスプリング５４の内径が大きくなろうとするため、ラップスプリング５４により第１および第２ホイール５２，５３が挟持されず、第１ホイール５２の回転が第２ホイール５３に伝達されないように構成されている。なお、第１ホイール５２の回転方向とラップスプリング５４の巻き方向の関係については後述する。 The wrap spring 54 has one end attached to the first wheel 52 and the other end attached to the second wheel 53, and is provided so as to wrap the outer periphery of the first and second wheels 52, 53. The lap spring 54 is configured to transmit only rotation in one direction of the first wheel 52 to the second wheel 53 based on the rotation direction of the first wheel 52 and the winding direction of the lap spring 54. More specifically, when the first wheel 52 is rotated in the winding direction of the lap spring 54, the inner diameter of the lap spring 54 tends to be reduced, so that the first and second wheels 52 and 53 are clamped by the lap spring 54. The rotation of the first wheel 52 is transmitted to the second wheel 53. On the other hand, when the first wheel 52 is rotated in the direction opposite to the winding direction of the lap spring 54, the inner diameter of the lap spring 54 tends to increase, so that the first and second wheels 52 and 53 are clamped by the lap spring 54. Therefore, the rotation of the first wheel 52 is not transmitted to the second wheel 53. The relationship between the rotation direction of the first wheel 52 and the winding direction of the lap spring 54 will be described later.
　コーン部材５５は、ナット部材４１の外側に配置される円盤状の本体部５５ａと、本体部５５ａの中央部から左方に延びてナット部材４１に形成された取付孔４１ａからナット部材４１の内部に挿入される挿入部５５ｂを有して構成される。挿入部５５ｂの外周部と取付孔４１ａはそれぞれ六角形に形成されており、これによりコーン部材５５はナット部材４１に対して左右方向に相対移動可能、且つナット部材４１と一体に回転可能にナット部材４１に設けられている。挿入部５５ｂの左端部にはワッシャ５８がボルトによって取り付けられている。ナット部材４１の右端内面とワッシャ５８の間には、クラッチスプリング５６が圧縮された状態で設けられている。このクラッチスプリング５６の弾性力によりコーン部材５５は左方に付勢され、本体部５５ａの外周端部が第２ホイール５３の第１テーパ面５３ａに挟持された状態となっている。このとき、第２ホイール５３の第２テーパ面５３ｂはナット部材４１の外周端部と当接した状態となっている。 The cone member 55 includes a disc-shaped main body portion 55a disposed outside the nut member 41, and an attachment hole 41a formed in the nut member 41 extending leftward from the central portion of the main body portion 55a. It has an insertion portion 55b to be inserted into. The outer peripheral portion of the insertion portion 55b and the mounting hole 41a are each formed in a hexagonal shape, so that the cone member 55 can move relative to the nut member 41 in the left-right direction and can rotate integrally with the nut member 41. The member 41 is provided. A washer 58 is attached to the left end of the insertion portion 55b with a bolt. A clutch spring 56 is provided in a compressed state between the inner surface of the right end of the nut member 41 and the washer 58. The cone member 55 is urged to the left by the elastic force of the clutch spring 56, and the outer peripheral end portion of the main body portion 55 a is held between the first tapered surface 53 a of the second wheel 53. At this time, the second tapered surface 53 b of the second wheel 53 is in contact with the outer peripheral end of the nut member 41.
　連動ギヤ列５７は、図４に示すように、ナット部材４１の左端部に固定されてナット部材４１と一体に回転する第１ギヤ５７ａと、スライドブロック３０の左端側の位置に回転自在に設けられて第１ギヤ５７ａと噛み合う第２ギヤ５７ｂと、後側のナット部材４２の左端部に固定されてナット部材４２と一体に回転し、第２ギヤ５７ｂと噛み合う第３ギヤ５７ｃと有して構成される。 As shown in FIG. 4, the interlocking gear train 57 is fixed to the left end portion of the nut member 41 and is rotatably provided at a position on the left end side of the slide block 30 and a first gear 57 a that rotates integrally with the nut member 41. A second gear 57b that meshes with the first gear 57a and a third gear 57c that is fixed to the left end of the rear nut member 42 and rotates integrally with the nut member 42 and meshes with the second gear 57b. Composed.
　このように構成されるディスクブレーキ装置１では、ブレーキ操作が行われると、その操作量に応じてブレーキアクチュエータによりオペレーティングシャフト２０におけるレバー部２２の先端部がブレーキ作動方向（図１における矢印Ａの方向）に押圧されて揺動される。このようにレバー部２２が揺動されると、てこの原理によってシャフト本体２１が図１における反時計回りに回動される。シャフト本体２１は、図３に示すように、第１曲面２３の曲率中心Ｐ１と第２曲面２４の曲率中心Ｐ２とが上下方向にずれた配置となっている（オフセットされている）。そのため、シャフト本体２１が反時計回りに回動されると、第１曲面２３は、第２ベアリング３２を介してスライドブロック３０の凹曲面３１に沿って反時計回りに回動しながら、スライドブロック３０を押圧する方向（リターンスプリング１５の付勢力に抗する方向）に移動される。また、第２曲面２４は、図６に示すように、キャリパ６内の支持平面１８上を下方に転動される。このとき、位置決めピン２５の突出部２５ａと支持平面１８の位置決め凹部１９とは、インボリュート歯車およびラックの関係と同様に、所定の圧力角で噛み合った状態となっている。そのため、オペレーティングシャフト２０は、ブレーキ作動開始前の位置からブレーキ作動方向に回動された位置（ブレーキ作動位置）までの全ての回動位置において位置決めされている。 In the disc brake device 1 configured as described above, when a brake operation is performed, the tip of the lever portion 22 of the operating shaft 20 is moved in the brake operating direction (the direction of arrow A in FIG. 1) by the brake actuator according to the operation amount. ) And is swung. When the lever portion 22 is swung in this manner, the shaft body 21 is rotated counterclockwise in FIG. 1 by the lever principle. As shown in FIG. 3, the shaft main body 21 is arranged such that the center of curvature P <b> 1 of the first curved surface 23 and the center of curvature P <b> 2 of the second curved surface 24 are offset (offset). Therefore, when the shaft body 21 is rotated counterclockwise, the first curved surface 23 is rotated counterclockwise along the concave curved surface 31 of the slide block 30 via the second bearing 32, and the slide block It is moved in the direction of pressing 30 (the direction against the urging force of the return spring 15). Further, as shown in FIG. 6, the second curved surface 24 is rolled downward on the support plane 18 in the caliper 6. At this time, the protruding portion 25a of the positioning pin 25 and the positioning recess 19 of the support plane 18 are in a state of being engaged at a predetermined pressure angle, similarly to the relationship between the involute gear and the rack. Therefore, the operating shaft 20 is positioned at all the rotational positions from the position before the start of the brake operation to the position rotated in the brake operation direction (brake operation position).
　シャフト本体２１の回動により第１曲面２３がスライドブロック３０を押圧する方向に移動されると、リターンスプリング１５の付勢力に抗してスライドブロック３０がパッド押動機構４０（ナット部材４１，４２、スクリュー部材４３，４４およびベッド部材４５）と一体となってディスクロータ２の右ロータ面２Ｒに近づく方向に移動される。これに伴って、ヘッド部材４５に接している右ブレーキパッド５が右ロータ面２Ｒに押し付けられる。また、右ブレーキパッド５が右ロータ面２Ｒに押し付けられた時の反力を利用してキャリパ６が図１における右方向に移動される。これによりキャリパ６のパッド支持部６ｂに支持された左ブレーキパッド４がディスクロータ２の左ロータ面２Ｌに押し付けられる。このように左右のブレーキパッド４，５によってディスクロータ２を左右両側から挟み、両者の間に発生する摩擦力によりディスクロータ２および車輪の制動を行うようになっている。 When the first curved surface 23 is moved in the direction of pressing the slide block 30 by the rotation of the shaft body 21, the slide block 30 resists the urging force of the return spring 15 and the pad pressing mechanism 40 (nut members 41, 42). The screw members 43 and 44 and the bed member 45) are moved together in a direction approaching the right rotor surface 2R of the disc rotor 2. Along with this, the right brake pad 5 in contact with the head member 45 is pressed against the right rotor surface 2R. Further, the caliper 6 is moved in the right direction in FIG. 1 using the reaction force when the right brake pad 5 is pressed against the right rotor surface 2R. As a result, the left brake pad 4 supported by the pad support portion 6 b of the caliper 6 is pressed against the left rotor surface 2 </ b> L of the disc rotor 2. In this way, the disc rotor 2 is sandwiched from the left and right sides by the left and right brake pads 4 and 5, and the disc rotor 2 and the wheels are braked by the frictional force generated between them.
　また、ブレーキ操作が行われてシャフト本体２１が図１における反時計回りに回動されると、図８において二点鎖線で示すように、シャフト本体２１に固定されたアジャスタピン５１が下方に移動される。アジャスタピン５１が第１ホイール５２の挿入孔５２ａの内面との間のギャップ以上に下方へ移動されると、アジャスタピン５１が挿入孔５２ａの内面を押圧し、第１ホイール５２が図８における反時計回りにナット部材４１に対して相対回転される。ラップスプリング５４の巻き方向は、この第１ホイール５２の回転方向（反時計回り）と同じ方向になるように設けられている。そのため、第１ホイール５２が反時計回りに回転されると、ラップスプリング５４の内径が小さくなろうとするため、ラップスプリング５４により第１および第２ホイール５２，５３が挟持され、第１ホイール５２の回転が第２ホイール５３に伝達され、第２ホイール５３が反時計回りに回転される。 When the brake operation is performed and the shaft main body 21 is rotated counterclockwise in FIG. 1, the adjuster pin 51 fixed to the shaft main body 21 moves downward as shown by a two-dot chain line in FIG. Is done. When the adjuster pin 51 is moved downward beyond a gap between the first wheel 52 and the inner surface of the insertion hole 52a of the first wheel 52, the adjuster pin 51 presses the inner surface of the insertion hole 52a, and the first wheel 52 moves in the direction shown in FIG. It is rotated relative to the nut member 41 in the clockwise direction. The winding direction of the wrap spring 54 is provided so as to be the same direction as the rotation direction (counterclockwise) of the first wheel 52. Therefore, when the first wheel 52 is rotated counterclockwise, the inner diameter of the lap spring 54 tends to be reduced, so that the first and second wheels 52 and 53 are sandwiched by the lap spring 54, and the first wheel 52 The rotation is transmitted to the second wheel 53, and the second wheel 53 is rotated counterclockwise.
　このように第２ホイール５３が反時計回りに回転されると、図７に示すように、その回転力が第２ホイール５３の第１テーパ面５３ａに挟持されたコーン部材５５（本体部５５ａ）および第２テーパ面５３ｂに当接されたナット部材４１に伝達され、コーン部材５５およびナット部材４１が一体に図８における反時計回りに回転される。ナット部材４１の内周面およびスクリュー部材４３の外周面に切られたネジは、ナット部材４１が当該反時計回りに回転されると、スクリュー部材４３をディスクブレーキ２の右ロータ面２Ｒに近づける方向にナット部材４１に対して相対移動させるように構成されている。そのため、ナット部材４１が反時計回りに回転されると、スクリュー部材４３が右ロータ面２Ｒに近づく方向にナット部材４１に対して相対移動される。 When the second wheel 53 is thus rotated counterclockwise, the cone member 55 (main body portion 55a) whose rotational force is sandwiched between the first tapered surfaces 53a of the second wheel 53 as shown in FIG. The cone member 55 and the nut member 41 are integrally rotated counterclockwise in FIG. 8 as a result of being transmitted to the nut member 41 in contact with the second tapered surface 53b. The screw cut on the inner peripheral surface of the nut member 41 and the outer peripheral surface of the screw member 43 is a direction in which the screw member 43 approaches the right rotor surface 2R of the disc brake 2 when the nut member 41 is rotated counterclockwise. The nut member 41 is relatively moved. Therefore, when the nut member 41 is rotated counterclockwise, the screw member 43 is moved relative to the nut member 41 in a direction approaching the right rotor surface 2R.
　また、ナット部材４１の反時計回りへの回転は、連動ギヤ列５７（第１～第３ギヤ５７ａ～５７ｃ）を介して後側のナット部材４２に伝達され、ナット部材４２も反時計回りに回転される（図４を参照）。後側のナット部材４２およびスクリュー部材４４に切られたネジも、ナット部材４１およびスクリュー部材４３と同様に構成されている。そのため、スクリュー部材４４も、上記スクリュー部材４３と同じ移動量だけ、右ロータ面２Ｒに近づく方向にナット部材４２に対して相対移動される。これに伴ってスクリュー部材４３，４４に取り付けられたヘッド部材４５を介して右ブレーキパッド５が右ロータ面２Ｒに近づく方向に移動される。そして、右ブレーキパッド５が右ロータ面２Ｒに当接すると、スクリュー部材４３，４４の上記相対移動に対する抵抗力が増大する。そのため、第２ホイール５３の第１テーパ面５３ａとコーン部材５５との挟持部、および第２テーパ面５３ｂとナット部材４１との当接部において滑りが生じ、右ブレーキパッド５を右ロータ面２Ｒにそれ以上に近づける移動が規制される。このようにして右ブレーキパッド５が摩耗して右ロータ面２Ｒとの間の距離が大きくなっても、ブレーキ作動時に当該距離を適正な距離に調整することができる。 Further, the counterclockwise rotation of the nut member 41 is transmitted to the rear nut member 42 via the interlocking gear train 57 (first to third gears 57a to 57c), and the nut member 42 is also rotated counterclockwise. Rotated (see FIG. 4). The screws cut in the rear nut member 42 and the screw member 44 are also configured in the same manner as the nut member 41 and the screw member 43. Therefore, the screw member 44 is also moved relative to the nut member 42 in the direction approaching the right rotor surface 2R by the same amount of movement as the screw member 43. Along with this, the right brake pad 5 is moved in a direction approaching the right rotor surface 2R via the head member 45 attached to the screw members 43, 44. And if the right brake pad 5 contact | abuts to the right rotor surface 2R, the resistance force with respect to the said relative movement of the screw members 43 and 44 will increase. As a result, slippage occurs at the holding portion between the first tapered surface 53a and the cone member 55 of the second wheel 53 and the contact portion between the second tapered surface 53b and the nut member 41, and the right brake pad 5 is moved to the right rotor surface 2R. The movement to move closer to that is restricted. Thus, even if the right brake pad 5 is worn and the distance from the right rotor surface 2R increases, the distance can be adjusted to an appropriate distance when the brake is operated.
　そして、ブレーキ操作が解除されると、ブレーキアクチュエータによるレバー部２２への押圧力が解除され、リターンスプリング１５の弾性力によりスライドブロック３０がパッド押動機構４０と一体となってディスクロータ２の右ロータ面２Ｒから離れる方向に移動され、車輪の制動が解除されるようになっている。 When the brake operation is released, the pressing force applied to the lever portion 22 by the brake actuator is released, and the slide block 30 is integrated with the pad pushing mechanism 40 by the elastic force of the return spring 15 to the right of the disc rotor 2. The wheel is moved away from the rotor surface 2R, and the braking of the wheel is released.
　スライドブロック３０が右ロータ面２Ｒから離れる方向に移動されると、シャフト本体２１の第１曲面２３は、第２ベアリング３２を介してスライドブロック３０の凹曲面３１に沿って図１における時計回りに回動しながら、右ロータ面２Ｒから離れる方向（右方向）に移動される。また、第２曲面２４は、図６に示すように、キャリパ６内の支持平面１８上を上方に転動される。このときも、位置決めピン２５の突出部２５ａと支持平面１８の位置決め凹部１９とは、インボリュート歯車およびラックの関係と同様に、所定の圧力角で噛み合った状態となっている。このように第１および第２曲面２３，２４が移動してシャフト本体２１が時計回りに回動され、レバー部２２がブレーキ解除方向（図１における矢印Ａの逆方向）に揺動される。このとき、図６に二点鎖線で示すように、第２曲面２４が支持平面１８上を上方に転動し、位置決めピン２５の突出部２５ａと支持平面１８の位置決め凹部１９とが噛み合い終り位置になるまで、レバー部２２がブレーキ解除方向に揺動し、その揺動位置がブレーキ解除状態における基準位置になるようになっている。 When the slide block 30 is moved in a direction away from the right rotor surface 2R, the first curved surface 23 of the shaft main body 21 is rotated clockwise in FIG. 1 along the concave curved surface 31 of the slide block 30 via the second bearing 32. While rotating, it is moved in a direction away from the right rotor surface 2R (right direction). Further, as shown in FIG. 6, the second curved surface 24 is rolled upward on the support plane 18 in the caliper 6. At this time, the protrusion 25a of the positioning pin 25 and the positioning recess 19 of the support plane 18 are in mesh with each other at a predetermined pressure angle, as in the relationship between the involute gear and the rack. In this way, the first and second curved surfaces 23, 24 move, the shaft body 21 is rotated clockwise, and the lever portion 22 is swung in the brake release direction (the direction opposite to the arrow A in FIG. 1). At this time, as indicated by a two-dot chain line in FIG. 6, the second curved surface 24 rolls upward on the support plane 18, and the protrusion 25 a of the positioning pin 25 and the positioning recess 19 of the support plane 18 are engaged with each other. The lever portion 22 swings in the brake release direction until the position becomes the reference position in the brake release state.
　また、ブレーキ操作が解除されてシャフト本体２１が図１における時計回りに回動されると、図８において実線で示すように、シャフト本体２１に固定されたアジャスタピン５１が上方に移動される。アジャスタピン５１が第１ホイール５２の挿入孔５２ａの内面との間のギャップ以上に上方へ移動されると、アジャスタピン５１が挿入孔５２ａの内面を押圧し、第１ホイール５２が図８における時計回りにナット部材４１に対して相対回転される。ここで、ラップスプリング５４の巻方向が上述のようになっているため、第１ホイール５２が時計回りに回転されると、ラップスプリング５４の内径が大きくなろうとするため、ラップスプリング５４による第１および第２ホイール５２，５３の結合力が小さくなり、第１ホイール５２の回転が第２ホイール５３には伝達されない。そのため、ナット部材４１が時計回りに回転されることはなく、またスクリュー部材４３が右ロータ面２Ｒから離れる方向にナット部材４１に対して相対移動されることもない。従って、ブレーキ作動時に調整された右ブレーキパッド５と右ロータ面２Ｒの間の適正な距離がそのまま保たれる。 When the brake operation is released and the shaft body 21 is rotated clockwise in FIG. 1, the adjuster pin 51 fixed to the shaft body 21 is moved upward as shown by the solid line in FIG. When the adjuster pin 51 is moved upward beyond the gap between the first wheel 52 and the inner surface of the insertion hole 52a of the first wheel 52, the adjuster pin 51 presses the inner surface of the insertion hole 52a, and the first wheel 52 is It is rotated relative to the nut member 41 around. Here, since the winding direction of the lap spring 54 is as described above, when the first wheel 52 is rotated clockwise, the inner diameter of the lap spring 54 tends to increase, so In addition, the coupling force between the second wheels 52 and 53 is reduced, and the rotation of the first wheel 52 is not transmitted to the second wheel 53. Therefore, the nut member 41 is not rotated clockwise, and the screw member 43 is not moved relative to the nut member 41 in the direction away from the right rotor surface 2R. Therefore, an appropriate distance between the right brake pad 5 and the right rotor surface 2R adjusted when the brake is operated is maintained as it is.
　このようにディスクブレーキ装置１では、オペレーティングシャフト２０が、ブレーキ作動開始前の位置からブレーキ作動位置までの間の全ての回動位置において、キャリパ６の内面に設けられた支持平面１８の位置決め凹部１９内に挿入され、インボリュート歯車およびラックの関係と同様に所定の圧力角で噛み合った状態となる位置決めピン２５（突出部２５ａ）を有して構成される。そのため、この位置決めピン２５および位置決め凹部１９により、オペレーティングシャフト２０を全ての回動位置において位置決めすることができ、オペレーティングシャフト２０の回動位置のばらつきを抑えることができる。従って、ブレーキ作動中に構成部品が干渉して破損することを防ぐことができ、ブレーキ操作に対して安定した制動力を発揮することができる。 As described above, in the disc brake device 1, the operating shaft 20 is positioned in the positioning recess 19 of the support plane 18 provided on the inner surface of the caliper 6 at all rotational positions between the position before the brake operation is started and the brake operation position. It has a positioning pin 25 (projecting portion 25a) that is inserted into the gear and meshed at a predetermined pressure angle as in the relationship between the involute gear and the rack. Therefore, the operating shaft 20 can be positioned at all the rotational positions by the positioning pins 25 and the positioning recesses 19, and variations in the rotational positions of the operating shaft 20 can be suppressed. Therefore, it is possible to prevent the component parts from interfering with each other during the brake operation, and to exhibit a stable braking force with respect to the brake operation.
　また、位置決めピン２５における位置決め凹部１９の内面に当接する部分がインボリュート曲線により形成されているため、位置決めピンおよび位置決め凹部の製造が容易となり、製造コストも抑えることができる。また、位置決めピン２５が外周面全体においてインボリュート曲線を有した略円錐状に形成されているため、位置決めピン２５の組立方向性を無くすことができ、組立誤差により位置決めピン２５が破損するようなことを防ぐことができる。さらに、オペレーティングシャフト２０の第２曲面２４の半径Ｒ２（シャフト転動面半径）が、位置決めピン２５と位置決め凹部１９の噛み合いピッチ円半径に等しくなるように設定され、且つ位置決めピン（インボリュート）の圧力角が位置決め凹部の圧力角より大きく設定されているため、オペレーティングシャフト２０が回動するときに位置決めピン２５と位置決め凹部１９の隙間を略一定（正確には微増）に保持しつつ、位置決めピン２５に負荷がかからないようにすることができ、ブレーキ作動中の高い荷重状態でも位置決めピン２５の破損を防ぐことができる。 Further, since the portion of the positioning pin 25 that contacts the inner surface of the positioning recess 19 is formed by an involute curve, the positioning pin and the positioning recess can be easily manufactured, and the manufacturing cost can be reduced. Further, since the positioning pin 25 is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, the assembling direction of the positioning pin 25 can be eliminated, and the positioning pin 25 is damaged due to an assembly error. Can be prevented. Further, the radius R2 (shaft rolling surface radius) of the second curved surface 24 of the operating shaft 20 is set to be equal to the meshing pitch circle radius of the positioning pin 25 and the positioning recess 19 and the pressure of the positioning pin (involute) is set. Since the angle is set to be larger than the pressure angle of the positioning recess, the positioning pin 25 is held while the gap between the positioning pin 25 and the positioning recess 19 is kept substantially constant (exactly slightly increased) when the operating shaft 20 rotates. The positioning pin 25 can be prevented from being damaged even in a high load state during the operation of the brake.
　また、位置決めピン２５が、オペレーティングシャフト２０の第２曲面２４において、前後方向における中央部および後端部にそれぞれ設けられているため、この２つの位置決めピン２５によりオペレーティングシャフト２０の軸が上下方向に傾くことを防ぐことができる。 Further, since the positioning pins 25 are provided at the center portion and the rear end portion in the front-rear direction on the second curved surface 24 of the operating shaft 20, the axis of the operating shaft 20 is moved vertically by the two positioning pins 25. Tilt can be prevented.
　これまで本発明に係る実施形態について説明してきたが、本発明の範囲は上述の実施形態に示したものに限定されない。例えば、上述の実施形態では、位置決めピン２５（突出部２５ａ）における位置決め凹部１９の内面に当接する部分がインボリュート曲線により形成されているが、インボリュート曲線ではなく、アイクロイド曲線やトロコイド曲線等の他の曲線により形成されてもよい。しかしながら上述のように、インボリュート曲線により形成される構成とすれば、位置決めピンおよび位置決め凹部の製造が容易となり、製造コストも抑えることができる。 Although the embodiments according to the present invention have been described so far, the scope of the present invention is not limited to those shown in the above-described embodiments. For example, in the above-described embodiment, the portion of the positioning pin 25 (projecting portion 25a) that contacts the inner surface of the positioning recess 19 is formed by an involute curve, but other than an involute curve, other than an Icroid curve, a trochoid curve, etc. It may be formed by the following curve. However, as described above, if the configuration is formed by an involute curve, the positioning pins and the positioning recesses can be easily manufactured, and the manufacturing cost can be reduced.
　また、上述の実施形態では、位置決めピン２５（突出部２５ａ）が外周面全体においてインボリュート曲線を有した略円錐状に形成されているが、略円錐状ではなく、位置決め凹部１９の内面に当接する部分がインボリュート曲線により形成されている他の形状であってもよい。また、位置決めピン２５は、オペレーティングシャフト２０の第２曲面２４において、前後方向における中央部および後端部にそれぞれ設けられているが、中央部および後端部以外の位置に設けるようにしてもよい。さらに、位置決めピン２５は一つであってもよい。 In the above-described embodiment, the positioning pin 25 (projecting portion 25a) is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, but is not substantially conical and contacts the inner surface of the positioning recess 19. Another shape in which the portion is formed by an involute curve may be used. Further, the positioning pins 25 are provided at the center portion and the rear end portion in the front-rear direction on the second curved surface 24 of the operating shaft 20, respectively, but may be provided at positions other than the center portion and the rear end portion. . Furthermore, the number of positioning pins 25 may be one.
　また、上述の実施形態では、位置決め凹部１９は、二つの位置決めピン２５に対応して二つ設けられているが、二つの凹部を前後方向につなげた一つの凹溝状、いわゆるラック形状に形成してもよい。 In the above-described embodiment, the two positioning recesses 19 are provided corresponding to the two positioning pins 25. However, the positioning recesses 19 are formed in a single groove shape, that is, a so-called rack shape in which the two recesses are connected in the front-rear direction. May be.
１　　ディスクブレーキ装置
２　　ディスクロータ
４，５　ブレーキパッド
６　　キャリパ（ブレーキハウジング）
１０　パッド押圧装置
１５　リターンスプリング（ブレーキ解除スプリング）
１８　支持平面
１９　位置決め凹部
２０　オペレーティングシャフト（ブレーキシャフト）
２５　位置決めピン
３０　スライドブロック
４０　パッド押動機構 1 Disc brake device 2 Disc rotor 4, 5 Brake pad 6 Caliper (brake housing)
10 Pad pressing device 15 Return spring (brake release spring)
18 Support plane 19 Positioning recess 20 Operating shaft (brake shaft)
25 Positioning pin 30 Slide block 40 Pad pushing mechanism

Claims (5)

  1. 　車輪とともに回転するディスクロータと、前記ディスクロータのロータ面に対向して設けられたブレーキパッドと、前記ブレーキパッドを前記ロータ面に押し付けるためのパッド押圧装置と、前記パッド押圧装置を内部に収容するブレーキハウジングとを備え、前記パッド押圧装置により前記ブレーキパッドを前記ロータ面に押し付け、両者の間に発生する摩擦力により前記ディスクロータおよび前記車輪の制動を行うディスクブレーキ装置において、
    　前記パッド押圧装置は、ブレーキ操作が行われたときに作動するブレーキアクチュエータと、前記ロータ面に略平行に配置されて前記ブレーキアクチュエータの作動によりブレーキ作動方向に回動するブレーキシャフトと、前記ブレーキシャフトの回動により前記ブレーキパッドを前記ロータ面に近づく方向に移動させるパッド押動機構と、ブレーキ操作が解除されたときに前記パッド押動機構を前記ロータ面から離れる方向に移動させるとともに前記ブレーキシャフトをブレーキ解除方向に回動させるブレーキ解除スプリングとを備え、
    　前記ブレーキシャフトは、ブレーキ作動開始前の位置からブレーキ作動方向に回動された位置までの間の全ての回動位置において前記ブレーキハウジングに形成された位置決め凹部の内面と当接して前記ブレーキシャフトの位置決めを行う位置決めピンを有して構成されることを特徴とするディスクブレーキ装置。     A disk rotor that rotates together with the wheels, a brake pad that is provided to face the rotor surface of the disk rotor, a pad pressing device that presses the brake pad against the rotor surface, and the pad pressing device are housed inside A disc brake device comprising: a brake housing, pressing the brake pad against the rotor surface by the pad pressing device, and braking the disc rotor and the wheel by a frictional force generated between the two,
    The pad pressing device includes a brake actuator that operates when a brake operation is performed, a brake shaft that is disposed substantially parallel to the rotor surface and rotates in a brake operation direction by the operation of the brake actuator, and the brake shaft A pad pushing mechanism that moves the brake pad in a direction approaching the rotor surface by rotating the brake pad, and moves the pad pushing mechanism in a direction away from the rotor surface when the brake operation is released, and the brake shaft And a brake release spring that rotates in the brake release direction,
    The brake shaft is in contact with the inner surface of the positioning recess formed in the brake housing at all rotation positions between the position before the brake operation is started and the position rotated in the brake operation direction. A disc brake device comprising a positioning pin for positioning.
  2. 　前記位置決めピンは、前記位置決め凹部の内面に当接する部分における断面がインボリュート曲線を有した略台形状に形成され、前記位置決め凹部は、前記位置決めピンと当接する部分における断面が台形状の凹みからなることを特徴とする請求項１に記載のディスクブレーキ装置。 The positioning pin is formed in a substantially trapezoidal shape with a section in contact with the inner surface of the positioning recess having an involute curve, and the positioning recess has a trapezoidal recess in a section in contact with the positioning pin. The disc brake device according to claim 1.
  3. 　前記位置決めピンは、外周面全体においてインボリュート曲線を有した略円錐状に形成され、前記位置決め凹部は、全周において断面が台形状となる略円錐状の凹みからなることを特徴とする請求項２に記載のディスクブレーキ装置。 The positioning pin is formed in a substantially conical shape having an involute curve on the entire outer peripheral surface, and the positioning recess is formed by a substantially conical recess having a trapezoidal cross section on the entire circumference. Disc brake device according to
  4. 　前記ブレーキシャフトにおける前記位置決めピンが設けられた部分の外周面は、前記位置決めピンと前記位置決め凹部の噛み合いピッチ円半径と等しい半径を有する曲面形状に形成され、且つ前記位置決めピンの圧力角が前記位置決め凹部の圧力角より大きく設定されることを特徴とする請求項２または３に記載のディスクブレーキ装置。 The outer peripheral surface of the portion where the positioning pin is provided in the brake shaft is formed in a curved surface shape having a radius equal to the engagement pitch circle radius of the positioning pin and the positioning recess, and the pressure angle of the positioning pin is the positioning recess The disc brake device according to claim 2, wherein the disc brake device is set to be larger than a pressure angle of the disc brake.
  5. 　前記位置決めピンは、前記ブレーキシャフトにおいて軸方向に少なくとも２つ設けられていることを特徴とする請求項１～４のいずれかに記載のディスクブレーキ装置。 The disc brake device according to any one of claims 1 to 4, wherein at least two positioning pins are provided in the axial direction of the brake shaft.
PCT/JP2013/004283 2013-07-11 2013-07-11 Disc brake device WO2015004696A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3564552A1 (en) * 2018-04-30 2019-11-06 Meritor Heavy Vehicle Braking Systems (UK) Limited An actuation mechanism

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59187121A (en) * 1983-04-01 1984-10-24 ザ　ベンデイクス　コ−ポレ−シヨン Mechanical actuator for disk brake
JPS6065920A (en) * 1983-09-16 1985-04-15 Akebono Brake Ind Co Ltd Input mechanism of parking brake
US5400875A (en) * 1993-03-05 1995-03-28 Perrot Bremsen Gmbh Brake application mechanism for a disc brake
US5433298A (en) * 1992-09-21 1995-07-18 Deutsche Perrot-Bremse Gmbh Actuating mechanism for a sliding-caliper disc brake

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59187121A (en) * 1983-04-01 1984-10-24 ザ　ベンデイクス　コ−ポレ−シヨン Mechanical actuator for disk brake
JPS6065920A (en) * 1983-09-16 1985-04-15 Akebono Brake Ind Co Ltd Input mechanism of parking brake
US5433298A (en) * 1992-09-21 1995-07-18 Deutsche Perrot-Bremse Gmbh Actuating mechanism for a sliding-caliper disc brake
US5400875A (en) * 1993-03-05 1995-03-28 Perrot Bremsen Gmbh Brake application mechanism for a disc brake

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3564552A1 (en) * 2018-04-30 2019-11-06 Meritor Heavy Vehicle Braking Systems (UK) Limited An actuation mechanism
US10895296B2 (en) 2018-04-30 2021-01-19 Meritor Heavy Vehicle Braking Systems (Uk) Limited Actuation mechanism
EP3862591A1 (en) * 2018-04-30 2021-08-11 Meritor Heavy Vehicle Braking Systems (UK) Limited An actuation mechanism

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