WO2015004696A1 - Dispositif de frein à disque - Google Patents

Dispositif de frein à disque 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
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WO
WIPO (PCT)
Prior art keywords
brake
positioning
pad
rotor
shaft
Prior art date
Application number
PCT/JP2013/004283
Other languages
English (en)
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/fr
Publication of WO2015004696A1 publication Critical patent/WO2015004696A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—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.

Landscapes

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

Abstract

La présente invention concerne un dispositif (1) de frein à disque, conçu de telle sorte qu'un arbre (20) de frein qui constitue un dispositif (10) de pression sur plaquette pour appuyer des plaquettes (4, 5) de frein contre des surfaces (2G, 2D) de rotor, comprend une goupille (25) de serrage qui : est en contact avec la surface intérieure d'un évidement (19) de positionnement qui est pratiqué sur un logement (6) de frein entre toutes les positions de rotation allant d'une position de début d'opération de pré-freinage à une position qui est atteinte par rotation dans le sens de mise en œuvre du frein ; et effectue la mise en place de l'arbre (20) de frein.
PCT/JP2013/004283 2013-07-11 2013-07-11 Dispositif de frein à disque WO2015004696A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/004283 WO2015004696A1 (fr) 2013-07-11 2013-07-11 Dispositif de frein à disque

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/004283 WO2015004696A1 (fr) 2013-07-11 2013-07-11 Dispositif de frein à disque

Publications (1)

Publication Number Publication Date
WO2015004696A1 true WO2015004696A1 (fr) 2015-01-15

Family

ID=52279432

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/004283 WO2015004696A1 (fr) 2013-07-11 2013-07-11 Dispositif de frein à disque

Country Status (1)

Country Link
WO (1) WO2015004696A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3564552A1 (fr) * 2018-04-30 2019-11-06 Meritor Heavy Vehicle Braking Systems (UK) Limited Mécanisme d'actionnement

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59187121A (ja) * 1983-04-01 1984-10-24 ザ　ベンデイクス　コ−ポレ−シヨン デイスクブレ−キ用機械的アクチユエ−タ
JPS6065920A (ja) * 1983-09-16 1985-04-15 Akebono Brake Ind Co Ltd パ−キングブレ−キの入力機構
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 (ja) * 1983-04-01 1984-10-24 ザ　ベンデイクス　コ−ポレ−シヨン デイスクブレ−キ用機械的アクチユエ−タ
JPS6065920A (ja) * 1983-09-16 1985-04-15 Akebono Brake Ind Co Ltd パ−キングブレ−キの入力機構
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 (fr) * 2018-04-30 2019-11-06 Meritor Heavy Vehicle Braking Systems (UK) Limited Mécanisme d'actionnement
US10895296B2 (en) 2018-04-30 2021-01-19 Meritor Heavy Vehicle Braking Systems (Uk) Limited Actuation mechanism
EP3862591A1 (fr) * 2018-04-30 2021-08-11 Meritor Heavy Vehicle Braking Systems (UK) Limited Un mécanisme d'action

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