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WO2018003191A1 - Frein à disque - Google Patents

Frein à disque Download PDF

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Publication number
WO2018003191A1
WO2018003191A1 PCT/JP2017/010135 JP2017010135W WO2018003191A1 WO 2018003191 A1 WO2018003191 A1 WO 2018003191A1 JP 2017010135 W JP2017010135 W JP 2017010135W WO 2018003191 A1 WO2018003191 A1 WO 2018003191A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
diameter
ball
cover member
axial direction
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/010135
Other languages
English (en)
Japanese (ja)
Inventor
坂下　貴康
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
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 Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Publication of WO2018003191A1 publication Critical patent/WO2018003191A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • 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
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts

Definitions

  • the present invention relates to a disc brake used for braking a vehicle.
  • a conventional disc brake is provided with a parking brake mechanism for propelling and holding a piston at a braking position at the time of parking brake, and the parking brake mechanism includes a ball and ramp mechanism and a screw mechanism.
  • the ball and ramp mechanism and the screw mechanism are operated by the rotation of the electric motor to move the piston to the braking position, and the piston is held at the braking position by the screw mechanism (Patent Document). 1).
  • the volume of brake fluid in the cylinder fluctuates, and the hydraulic pulsation caused by the volume fluctuation causes the brake pedal to vibrate finely through the hydraulic circuit, causing an uncomfortable kickback to the driver. There is a risk of feeling.
  • An object of the present invention is to provide a disc brake that achieves downsizing and improves pedal feeling when the parking brake is operated.
  • a disc brake includes a bottomed cylindrical piston that moves one of a pair of pads arranged on both sides in the axial direction of the rotor across the rotor in the axial direction of the rotor,
  • a caliper main body having a cylinder in which the piston is movably disposed, an electric motor provided in the caliper main body, and provided in the caliper main body, and propelling the piston by a ball-and-ramp mechanism to hold it in a braking position.
  • a parking brake mechanism includes: an input member having a disk-like portion that is rotated by the rotation from the electric motor and rotates on the bottom side of the cylinder; and the disk-like portion of the input member on one end side in the axial direction.
  • a cylindrical cover member connected to the outer periphery of the cylinder and extending into the piston on the other end side in the axial direction.
  • the cover member is rotatable together with the input member, and the ball and ramp mechanism is accommodated therein.
  • a cylindrical cover member, a shaft member that is screwed to the ball and ramp mechanism, is rotatable by the operation of the ball and ramp mechanism, and is linearly movable, and is screwed to the shaft member, and the shaft member
  • a pressing member that linearly moves by rotating relative to and presses the piston in the axial direction
  • the ball and ramp mechanism is disposed inside the cover member on the one end side in the axial direction of the cover member, engages with the cover member, and rotates with the cover member.
  • the rotary linear motion lamp is biased toward the input member by a biasing member supported by the cover member on the other end side in the axial direction of the cover member. Is.
  • Sectional drawing which shows the disc brake which concerns on this embodiment.
  • the disassembled perspective view of the parking brake mechanism employ
  • the disc brake 1 includes a pair of inner brake pads 2 and outer brake pads 3 disposed on both sides in the axial direction with a disc rotor D attached to a rotating portion of the vehicle, and a caliper 4. And are provided.
  • the disc brake 1 is configured as a caliper floating type.
  • the pair of inner brake pad 2, outer brake pad 3, and caliper 4 are supported by a bracket (not shown) fixed to a non-rotating part such as a knuckle of the vehicle so as to be movable in the axial direction of the disk rotor D. ing.
  • the right side of the drawing will be described as one end side, and the left side will be appropriately described as the other end side.
  • the caliper body 6 that is the main body of the caliper 4 includes a cylinder portion 7 that is disposed on the base end side facing the inner brake pad 2 on the vehicle inner side, and a claw that is disposed on the distal end side facing the outer brake pad 3 on the vehicle outer side.
  • Part 8 The cylinder portion 7 is formed with a bottomed cylinder 15 that is a large-diameter opening 9 a that is open on the inner brake pad 2 side and is closed by a bottom wall 11 having a hole 10 on the opposite side.
  • the bottom wall 11 side in the cylinder 15 is formed with a small-diameter opening 9b that is continuous with the large-diameter opening 9a and has a smaller diameter than the large-diameter opening 9a.
  • a piston seal 16 is disposed on the inner wall surface of the large-diameter opening 9 a of the cylinder 15.
  • the piston 18 is formed in a bottomed cup shape including a bottom portion 19 and a cylindrical portion 20.
  • the piston 18 is accommodated in the cylinder 15 so that the bottom portion 19 faces the inner brake pad 2.
  • the piston 18 is housed in the large-diameter opening 9a of the cylinder 15 so as to be movable in the axial direction in contact with the piston seal 16.
  • a plurality of rotation restricting longitudinal grooves 22 are formed on the inner wall surface of the piston 18 at intervals along the circumferential direction.
  • a space between the piston 18 and the bottom wall 11 of the cylinder 15 is defined by a piston seal 16 as a hydraulic chamber 21.
  • the fluid pressure chamber 21 is supplied with fluid pressure from a fluid pressure source (not shown) such as a master cylinder or a fluid pressure control unit through a port (not shown) provided in the cylinder portion 7.
  • a recess 25 is provided on the outer peripheral side of the other end surface of the bottom portion 19 of the piston 18 facing the inner brake pad 2.
  • the concave portion 25 is engaged with a convex portion 26 formed on the back surface of the inner brake pad 2, and the piston 18 is prevented from rotating with respect to the cylinder 15 and eventually the caliper body 6 by this engagement.
  • a dust boot 27 is interposed between the outer wall surface of the bottom 19 of the piston 18 and the inner wall surface of the large-diameter opening 9 a of the cylinder 15 to prevent foreign matter from entering the cylinder 15.
  • One end surface of the bottom portion 19 of the piston 18 facing the parking brake mechanism 43 is a circular recess 30 provided in the central portion in the radial direction, and continuously extends from one end of the circular recess 30 toward the inner wall surface of the piston 18. And an annular inclined portion 31 extending so as to expand in diameter.
  • the inner diameter of the circular recess 30 is formed larger than that of a large-diameter male screw portion 186 of a spindle rod 83 described later.
  • a housing 35 is attached to the bottom wall 11 side of the cylinder 15 in an airtight manner.
  • a cover 36 is airtightly attached to one end opening of the housing 35.
  • the housing 35 and the cylinder part 7 are kept airtight by a seal member 37.
  • the housing 35 and the cover 36 are kept airtight by a seal member 38.
  • An electric motor 40 is hermetically attached to the housing 35 via a seal member 41 so as to be aligned with the caliper body 6.
  • the electric motor 40 is disposed outside the housing 35, but the housing 35 may be formed so as to cover the electric motor 40 and the electric motor 40 may be accommodated in the housing 35.
  • the sealing member 41 becomes unnecessary, and the number of assembling steps can be reduced.
  • the housing 35 and the cover 36 may be welded and joined. In this case, the seal member 38 becomes unnecessary, and the number of assembling steps can be reduced.
  • a spur multi-stage reduction mechanism 44 and a planetary gear reduction mechanism 45 that increase the rotation by the electric motor 40, and the rotational movement from the spur multi-stage reduction mechanism 44 and the planetary gear reduction mechanism 45 are converted into a linear movement.
  • a parking brake mechanism 43 for propelling the piston 18 and holding it at the braking position.
  • the flat-tooth multistage reduction mechanism 44 and the planetary gear reduction mechanism 45 are accommodated in the housing 35.
  • the spur multi-stage reduction mechanism 44 has a pinion gear 46, a first reduction gear 47, and a second reduction gear 48.
  • the pinion gear 46 is formed in a cylindrical shape, and has a hole 50 that is press-fitted and fixed to the rotating shaft 40 a of the electric motor 40, and a gear 51 that is formed on the outer wall surface.
  • the first reduction gear 47 is integrally formed with a large-diameter large gear 53 that meshes with the gear 51 of the pinion gear 46 and a small-diameter small gear 54 that extends from the large gear 53 in the axial direction. .
  • the first reduction gear 47 is rotatably supported by a shaft 55 having one end supported by the housing 35 and the other end supported by the cover 36.
  • the second reduction gear 48 is integrally formed with a large-diameter large gear 56 that meshes with the small gear 54 of the first reduction gear 47 and a small-diameter sun gear 57 that extends from the large gear 56 in the axial direction. Yes.
  • the sun gear 57 constitutes a part of the planetary gear reduction mechanism 45.
  • the second reduction gear 48 is rotatably supported by a shaft 58 supported by the cover 36.
  • the planetary gear speed reduction mechanism 45 includes a sun gear 57, a plurality of (for example, three) planetary gears 60, an internal gear 61, and a carrier 62.
  • the planetary gear 60 has a gear 63 meshed with the sun gear 57 of the second reduction gear 48 and a hole portion 64 through which a pin 65 erected from the carrier 62 is inserted.
  • the three planetary gears 60 are arranged at equal intervals on the circumference of the carrier 62.
  • the carrier 62 is formed in a disk shape, and a polygonal hole 68 into which the polygonal shaft portion 92 of the input shaft 80 is fitted is formed at the center in the radial direction.
  • the polygonal shaft portion 92 of the input shaft 80 is fitted into the polygonal hole 68, so that rotational torque can be transmitted between the carrier 62 and the input shaft 80.
  • a plurality of pin holes 69 are formed on the outer peripheral side of the carrier 62.
  • a pin 65 for rotatably supporting each planetary gear 60 is press-fitted and fixed in each pin hole 69.
  • the carrier 62 and each planetary gear 60 are constituted by a wall surface 35b projecting from the periphery of the opening 35a of the housing 35 to one end side, and an annular wall portion 72 integrally provided on the second reduction gear 48 side of the internal gear 61. Axial movement is restricted.
  • the relative rotation with the input shaft 80 is restricted by the polygonal hole 68 provided in the carrier 62, but a mechanical element capable of transmitting rotational torque such as a spline or a key may be employed.
  • the internal gear 61 is integrally provided on the second reduction gear 48 side continuously from the internal teeth 71 with which the gears 63 of the respective planetary gears 60 are engaged, and moves in the axial direction of the planetary gear 60. It is formed from an annular wall portion 72 to be regulated.
  • the internal gear 61 is press-fitted and fixed in the housing 35.
  • a spur multi-stage reduction mechanism 44 and a planetary gear reduction mechanism 45 are provided as a reduction mechanism that increases the rotation by the electric motor 40. Any one or both of the reduction mechanisms may be omitted as long as the rotational torque can be output.
  • the parking brake mechanism 43 converts the rotational movement from the spur multi-stage reduction mechanism 44 and the planetary gear reduction mechanism 45, that is, the rotation from the electric motor 40 into linear movement (hereinafter referred to as linear movement), and thrusts the piston 18. To hold the piston 18 in the braking position. As shown in FIGS. 1 and 2, the parking brake mechanism 43 is disposed between the bottom wall 11 of the cylinder 15 and the bottom portion 19 of the piston 18.
  • the parking brake mechanism 43 has an input shaft 80 as an input member, a cover member 81, a ball and ramp mechanism 82, a spindle rod 83 as a shaft member, and an adjuster nut 84 as a pressing member. .
  • the input shaft 80 is rotatably supported by the cylinder 15, and the rotational motion from the electric motor 40 is transmitted through the spur multi-stage reduction mechanism 44 and the planetary gear reduction mechanism 45.
  • the input shaft 80 includes a disk-shaped portion 90 having an outer diameter smaller than the inner diameter of the small-diameter opening 9b in the cylinder 15, and torque transmission extending integrally from the radial center of the disk-shaped portion 90 to one end side. And a shaft portion 91.
  • a small-diameter disk-shaped portion 93 is provided so as to protrude from the radial center of one end surface of the disk-shaped portion 90 toward the one end side.
  • a torque transmission shaft portion 91 extends integrally from the radial center of one end surface of the small-diameter disk-shaped portion 93 toward one end side.
  • the tip of the torque transmission shaft portion 91 is formed in a polygonal shaft portion 92 that is chamfered in a polygonal shape.
  • An annular groove 99 is formed between the torque transmission shaft portion 91 and the polygon shaft portion 92.
  • An accommodating concave portion 95 is formed at a substantially central portion of the other end surface of the disk-shaped portion 90.
  • An annular ball groove 96 extending in the circumferential direction around the accommodation recess 95 is formed on the other end surface of the disk-shaped portion 90.
  • a plurality of rotation restricting protrusions 97 are formed on the outer wall surface of the disk-shaped portion 90 at intervals in the circumferential direction.
  • the rotation restricting projection 97 of the input shaft 80 is engaged with each locking recess 177 provided at one end of a large diameter cover 175 of the cover member 81 described later. Thereby, the relative rotation of the input shaft 80 and the cover member 81 is restricted.
  • a locking step portion 98 extending in the circumferential direction is formed between the rotation restricting projections 97 on the outer peripheral portion of one end of the disk-shaped portion 90.
  • the first washer 100 is disposed so as to contact the bottom wall 11 of the cylinder 15.
  • the torque transmission shaft portion 91 of the input shaft 80 is inserted through the insertion hole 100 a of the first washer 100 and the hole portion 10 provided in the bottom wall 11 of the cylinder 15.
  • the polygon shaft 92 is inserted through the opening 35 a of the housing 35 and fitted into the polygon hole 68 of the carrier 62.
  • the polygonal shaft portion 92 is formed as a hexagonal shaft portion
  • the polygonal hole 68 is formed as a hexagonal hole.
  • the polygon shaft portion 92 may be a hexagon, a polygon such as a triangle, a quadrangle, a pentagon, a heptagon, an octagon, or a two-sided shape.
  • a seal member 105 and a sleeve 106 are provided between the outer wall surface of the torque transmission shaft portion 91 of the input shaft 80 and the inner wall surface of the hole 10 of the bottom wall 11 of the cylinder 15.
  • the sleeve 106 is disposed on one end side, and the seal member 105 is disposed on the other end side.
  • the seal member 105 and the sleeve 106 are provided to maintain the liquid tightness of the hydraulic chamber 21.
  • a retaining ring 107 is attached to the annular groove 99 of the input shaft 80. The retaining ring 107 restricts the axial movement of the input shaft 80 into the cylinder 15.
  • a second washer 110 is disposed on one end surface of the disk-shaped portion 90 of the input shaft 80 around the small-diameter circular portion 93.
  • a first thrust bearing 113 is disposed between the first washer 100 and the second washer 110.
  • the disk-shaped portion 90 of the input shaft 80 is supported on the bottom wall 11 of the cylinder 15 so as to be rotatable by the first thrust bearing 113.
  • a ball and ramp mechanism 82 is arranged on the other end side of the disk-shaped portion 90 of the input shaft 80.
  • the ball-and-ramp mechanism 82 includes a support lamp 120 located on one end side, a rotary linear motion lamp 121 located on the other end side, and each ball 122 interposed between the support lamp 120 and the rotational linear motion lamp 121. And have.
  • the support lamp 120 includes an annular support plate-shaped portion 125 and a support cylindrical portion 126 that protrudes integrally from the radial center of one end surface of the support plate-shaped portion 125 to one end side.
  • On the inner wall surface of the support plate-like portion 125 On the inner wall surface of the support plate-like portion 125, a small-diameter female screw portion 127 into which a small-diameter male screw portion 185 of a spindle rod 83 described later is screwed is formed.
  • the other end surface of the support plate-like portion 125 that is, the surface facing the rotation-linear motion plate-like portion 140 of the rotary linear motion lamp 121, extends in an arc shape with a predetermined inclination angle along the circumferential direction and has a diameter.
  • a plurality of ball grooves 128 (for example, three or four locations) having an arcuate cross section in the direction are formed.
  • annular ball groove 130 is formed around the support cylindrical portion 126 on one end surface of the support plate-like portion 125, that is, a surface facing the disc-like portion 90 of the input shaft 80.
  • a second thrust bearing 132 is disposed between the annular ball groove 130 of the support plate-like portion 125 and the annular ball groove 96 of the disc-like portion 90 of the input shaft 80.
  • the second thrust bearing 132 extends in an annular shape and is rotatably supported by a holding plate 133 having a plurality of openings 133a formed at intervals in the circumferential direction, and each opening 133a of the holding plate 133. And a plurality of balls 134.
  • a stopper wall portion (not shown) that abuts against a stopper portion 196 of a stopper member 195 fixed to one end of a spindle rod 83 (described later) protrudes inwardly from the inner wall surface of the support cylindrical portion 126.
  • the rotary linear motion lamp 121 is disposed so as to face the other end side of the support lamp 120.
  • the rotary linear motion lamp 121 includes an annular rotational linear motion plate-like portion 140, and a plurality of rotation restricting projections that protrude from the outer wall surface of the rotary linear motion plate-like portion 140 along the circumferential direction. 141.
  • the rotation translation plate-like portion 140 is formed with an insertion hole 140a through which the spindle rod 83 is inserted in the center portion in the radial direction.
  • the inner diameter of the insertion hole 140a is formed larger than the outer diameter of a small-diameter male thread portion 185 of a spindle rod 83 described later.
  • One end surface of the rotary linear plate-like portion 140 that is, the surface facing the support plate-like portion 125 of the support lamp 120, has a predetermined inclination angle along the circumferential direction and extends in an arc shape and in the radial direction.
  • a plurality of ball grooves 142 (for example, three or four) having an arcuate cross section are formed.
  • each ball groove 142 of the rotation linear motion lamp 121 and each ball groove 128 of the support lamp 120 are configured such that a depression is provided in the middle of the inclination along the circumferential direction or the inclination is changed in the middle. Also good.
  • the rotation linear motion lamp 121 is engaged with the cover member 81 by engaging each rotation regulating projection 141 of the rotation linear motion lamp 121 with each slit 180 provided in a small diameter cover portion 176 of the cover member 81 described later. On the other hand, it is supported so as not to be relatively rotatable and movable in the axial direction.
  • the ball 122 is interposed between each ball groove 128 of the support lamp 120 (support plate-like portion 125) and each ball groove 142 of the rotation / linear motion ramp 121 (rotation / linear motion plate-like portion 140). .
  • the ball-and-ramp mechanism 82 when rotational torque is applied to the rotation / linear motion ramp 121, the ball grooves 128 of the support plate-shaped portion 125 and the ball grooves 142 of the rotation / linear motion plate-shaped portion 140 As the balls 122 roll between the support plate-like portion 125 and the rotation-linear motion plate-like portion 140, the rotation difference between the support plate-like portion 125 and the rotation-linear motion plate-like portion 140 causes The relative distance in the axial direction varies.
  • a third thrust bearing 145 is disposed on the other end side of the rotary linear motion lamp 121 of the ball and ramp mechanism 82 so as to contact the other end surface of the rotary linear motion plate-like portion 140.
  • a rotating annular body 146 is disposed so as to contact the other end surface of the third thrust bearing 145.
  • the outer diameter of the third thrust bearing 145 is smaller than the outer diameter of the first thrust bearing 113 disposed between the first washer 100 and the second washer 110.
  • the outer diameter of the third thrust bearing 145 is formed smaller than the inner diameter of the piston 18, and more specifically, smaller than the inner diameter of a small diameter cover portion 176 of the cover member 81 described later.
  • the rotating annular body 146 is rotatably supported by the ball and ramp mechanism 82 via the third thrust bearing 145.
  • the rotating annular body 146 is formed to have a smaller diameter than the inner diameter of the small diameter cover portion 176 of the cover member 81 described later.
  • the rotating annular body 146 includes a large-diameter annular portion 147 having a spline hole 150 and a small-diameter cylindrical portion 148 that protrudes integrally from the other end surface of the large-diameter annular portion 147 to the other end side.
  • the other end of the small diameter cylindrical portion 148 is brought into contact with the spring seat 157.
  • An annular groove 149 is formed on the outer wall surface of the small diameter cylindrical portion 148.
  • the large-diameter annular portion 147 of the rotating annular body 146 is formed in the spline hole 150.
  • the spline hole 150 is splined to the spline shaft 187 of the spindle rod 83.
  • the rotary annular body 146 and the spindle rod 83 are able to slide relative to each other in the axial direction while receiving mutual rotational torque.
  • spline engagement is employed to couple the spindle rod 83 and the rotating annular body 146 so that they cannot be rotated relative to each other.
  • other known machines such as key fitting and D-hole that cannot be rotated relative to each other are used. Elements may be used.
  • the first spring clutch 155 is wound around the annular groove 149 provided in the small diameter cylindrical portion 148 of the rotating annular body 146.
  • the first spring clutch 155 has a distal end portion 155a facing outward in the radial direction and a coil portion 155b wound from the distal end portion 155a in a single layer.
  • the front end portion 155a is engaged with a slit 180 of a small diameter cover portion 176 of the cover member 81 described later, and the coil portion 155b is wound around an annular groove 149 provided on the outer wall surface of the small diameter cylindrical portion 148 of the rotating annular body 146.
  • the first spring clutch 155 rotates between the cover member 81 and the rotating annular body 146 in any one of the applying directions, the first spring clutch 155 is caused by friction between the coil portion 155 b and the annular groove 149 of the rotating annular body 146. Due to the force (clamping force), a rotational resistance torque is generated between the cover member 81 and the rotating annular body 146, and the rotational torque in the apply direction is transmitted between the cover member 81 and the rotating annular body 146. Is.
  • the first spring clutch 155 rotates between the cover member 81 and the rotating annular body 146 in one of the release directions, the coil portion 155b is opened and the tightening force is reduced. Rotational resistance torque is not generated between the cover member 81 and the rotating annular body 146, and the rotational torque is not transmitted in the release direction between the cover member 81 and the rotating annular body 146, allowing mutual rotation.
  • the spring seat 157 is formed in an annular shape.
  • the spring seat 157 is formed to have a smaller diameter than the inner diameter of a small diameter cover portion 176 of the cover member 81 described later.
  • On the outer wall surface of the spring seat 157 a plurality of rotation restricting protrusions 158 are formed to protrude in the circumferential direction. These rotation restricting projections 158 engage with respective slits 180 provided in a small diameter cover portion 176 of the cover member 81 to be described later, so that the spring seat 157 cannot rotate relative to the cover member 81, and It is supported so as to be movable in the axial direction.
  • An adjuster nut 84 is disposed on the other end side of the spring seat 157, and the nut portion 163 of the adjuster nut 84 can be advanced and retracted in the insertion hole 159 of the spring seat 157.
  • the inner diameter of the insertion hole 159 of the spring seat 157 and the inner diameter of the small-diameter cylindrical portion 148 of the rotating annular body 146 are substantially the same diameter.
  • a coil spring 203 is disposed between the spring seat 157 and a receiving portion 182 of a small diameter cover portion 176 of the cover member 81 described later.
  • the spring seat 157 prevents the rotational torque of the rotating annular body 146 from being transmitted to the coil spring 203.
  • the adjuster nut 84 is formed in a cylindrical shape and is disposed in the piston 18.
  • the adjuster nut 84 includes a flange portion 162 located on the other end side in the piston 18 and a nut portion 163 that integrally extends from the substantially central portion in the radial direction of the flange portion 162 to the one end side.
  • a spherical surface 164 is formed that contacts the annular inclined portion 31 provided on the bottom portion 19 of the piston 18.
  • a plurality of rotation restricting protrusions 165 are formed on the outer wall surface of the flange portion 162 so as to protrude in the circumferential direction at intervals.
  • Each of these rotation restricting protrusions 165 is engaged with each rotation restricting vertical groove 22 provided on the inner wall surface of the piston 18.
  • the adjuster nut 84 is supported so as not to rotate relative to the piston 18 and to be movable in the axial direction.
  • a large-diameter female screw portion 166 is formed on the inner wall surface of the nut portion 163 to which a large-diameter male screw portion 186 of a spindle rod 83 described later is screwed.
  • a plurality of locking groove portions 167 are formed on one end surface of the nut portion 163 at intervals in the circumferential direction.
  • the tip end portion 200 a of the second spring clutch 200 is engaged with any one of the locking groove portions 167.
  • On the outer wall surface of the nut portion 163, a plurality of vertically long protrusions 168 are provided protruding at intervals in the circumferential direction. Each vertically long protrusion 168 extends a predetermined length from the flange portion 162 toward one end side.
  • the outer diameter of the nut portion 163 is smaller than the inner diameter of the insertion hole 159 of the spring seat 157 and the inner diameter of the small-diameter cylindrical portion 148 of the rotating annular body 146.
  • the cover member 81 is formed in a cylindrical shape.
  • the cover member 81 extends from the vicinity of the bottom wall 11 of the cylinder 15 into the piston 18.
  • the cover member 81 includes a large-diameter cover portion 175 located on one end side, and a small-diameter cover portion 176 provided continuously from the large-diameter cover portion 175 to the other end side.
  • the outer diameter of the large diameter cover portion 175 is larger than the inner diameter of the piston 18 and smaller than the small diameter opening 9 b of the cylinder 15.
  • the outer diameter of the small diameter cover portion 176 is smaller than the inner diameter of the piston 18.
  • a plurality of locking recesses 177 are formed on one end surface of the large-diameter cover portion 175 at intervals in the circumferential direction.
  • the rotation restricting protrusions 97 of the input shaft 80 are engaged with the respective locking recesses 177. Thereby, the relative rotation between the cover member 81 and the input shaft 80 becomes impossible. In other words, the rotational torque from the input shaft 80 is transmitted to the cover member 81.
  • a plurality of protrusion claw portions 178 are formed that protrude from the one end side at intervals in the circumferential direction.
  • a plurality of circular openings 179 are formed in the circumferential wall portion of the large diameter cover portion 175 at intervals in the circumferential direction.
  • a plurality of slits 180 extending in the axial direction are formed in the circumferential wall portion of the small diameter cover portion 176 at intervals in the circumferential direction.
  • a substantially rectangular opening 181 is formed between adjacent slits 180 in the peripheral wall portion of the small diameter cover portion 176.
  • a receiving portion 182 that is bent inward is formed at the other end of the small diameter cover portion 176.
  • the inner diameter of the receiving portion 182 is formed larger than the outer diameter of the nut portion 163 of the adjuster nut 84.
  • a plurality of notches 183 are formed in the receiving portion 182 at intervals in the circumferential direction. Each notch 183 is formed by notching the inner wall surface of the receiving part 182. Each notch 183 is configured to engage with each longitudinal projection 168 provided on the adjuster nut 84, so that the adjuster nut 84 is prevented from excessively moving to one end side when released. I have to.
  • the spindle rod 83 has a small-diameter male screw portion 185 that is screwed into the small-diameter female screw portion 127 of the support lamp 120 on one end side, and a large-diameter male screw portion 186 that is screwed into the large-diameter female screw portion 166 of the adjuster nut 84. Is integrally formed on the other end side.
  • the spindle rod 83 corresponds to a shaft member.
  • a spline shaft 187 is provided between the small-diameter male screw portion 185 and the large-diameter male screw portion 186 so as to be continuous with the large-diameter male screw portion 186.
  • the outer diameter of the spline shaft 187 is formed smaller than the outer diameter of the large-diameter male screw portion 186. In other words, the outer diameter of the large-diameter male screw portion 186 is larger than the inner diameter of the spline hole 15 of the rotating annular body 146. Between the spline shaft 187 and the small diameter male screw portion 185, a minimum diameter shaft portion 188 having a smaller diameter than the outer diameter of the small diameter male screw portion 185 is formed. When the parking brake is not operated, the rotation linear motion lamp 121 is positioned around the minimum diameter shaft portion 188. One end surface of the spindle rod 83 is opposed to the bottom surface of the housing recess 95 of the input shaft 80.
  • a stopper member 195 is fixed to one end of the spindle rod 83.
  • the stopper member 195 is formed in a cylindrical shape.
  • the stopper member 195 is formed with a stopper portion 196 that protrudes radially outward.
  • the relative rotation range (ball and ramp mechanism) between the spindle rod 83 and the support lamp 120 is determined by the stopper portion 196 of the stopper member 195 and the stopper wall portion provided on the inner wall surface of the support cylindrical portion 126 of the support lamp 120.
  • the rotation angle corresponding to the amount of movement 82 in the axial direction) is limited.
  • a first small-diameter screw fitting portion 191 is formed between the small-diameter female screw portion 127 of the support lamp 120 and the small-diameter male screw portion 185 of the spindle rod 83.
  • the first small-diameter screw fitting portion 191 has a reverse efficiency of 0 or less, that is, irreversible so that the support lamp 120 does not rotate due to the axial load transmitted from the piston 18 to the spindle rod 83. It is comprised as a screw fitting part with.
  • a second large-diameter screw fitting portion 192 is formed between the large-diameter female screw portion 166 of the adjuster nut 84 and the large-diameter male screw portion 186 of the spindle rod 83.
  • the second large-diameter screw fitting portion 192 has a reverse efficiency of 0 or less so that the spindle rod 83 does not rotate due to an axial load transmitted from the piston 18 to the adjuster nut 84, that is, irreversible. It is comprised as a screw fitting part with.
  • the second spring clutch 200 has a tip portion 200a facing outward in the radial direction and a coil portion 200b wound in a single layer from the tip portion 200a. Then, the tip end portion 200 a is fitted into one of the locking groove portions 167 of the adjuster nut 84, and the coil portion 200 b is wound around one end side outer periphery of the large-diameter male screw portion 186 of the spindle rod 83. With respect to the rotation of the spindle rod 83 in the apply direction, the second spring clutch 200 does not generate rotational resistance torque with the adjuster nut 84 because the coil portion 200b is opened and the tightening force is reduced.
  • the rotational torque is not transmitted in the apply direction between the adjuster nut 84 and the spindle rod 83, and the mutual rotation is allowed.
  • the second spring clutch 200 rotates the spindle rod 83 in the release direction by a frictional force (tightening force) generated by tightening the coil portion 200b and the large-diameter male screw portion 186 of the spindle rod 83.
  • a rotational resistance torque is generated between the control nut 83 and the adjuster nut 84.
  • the ball-and-ramp mechanism 82 (rotary linear lamp 121, each ball 122, support lamp 120), the second thrust bearing 132, and the disk-shaped portion 90 of the input shaft 80 are arranged in this order, and each of the cover members 81 is arranged.
  • the protruding claw portions 178 By bending the protruding claw portions 178 inwardly, the protruding claw portions 178 are engaged with the respective locking step portions 98 provided on the disk-shaped portion 90 of the input shaft 80 so as to be integrally configured.
  • the electric motor 40 is connected to an ECU 210 composed of an electronic control device that is a control means for driving and controlling the electric motor 40.
  • the ECU 210 is connected to a parking switch 211 that is operated to instruct the operation / release of the parking brake.
  • the ECU 210 can also operate without operating the parking switch 211 based on a signal from the vehicle (not shown).
  • the operation of the disc brake 1 according to this embodiment will be described.
  • the action at the time of braking of the disc brake 1 as a normal hydraulic brake by the operation of a brake pedal (not shown) will be described.
  • the hydraulic pressure corresponding to the depressing force of the brake pedal is supplied from the master cylinder to the hydraulic chamber 21 in the caliper 4 via a hydraulic circuit (both not shown).
  • the piston 18 moves forward (moves in the left direction in FIG. 1) from the original position during non-braking while pressing the piston seal 16 against the disc rotor D while elastically deforming the piston seal 16.
  • the caliper body 6 moves to the right in FIG.
  • FIGS. 1 to 3 show stepwise actions when the parking brake is operated (applied), and FIGS. 7 to 9 show stepwise actions when the parking brake is released (released). It is shown in.
  • the ECU 210 drives the electric motor 40 and the sun gear of the planetary gear reduction mechanism 45 via the spur multi-stage reduction mechanism 44. 57 is rotated. Due to the rotation of the sun gear 57, the carrier 62 is rotated through each planetary gear 60. Then, the rotational torque from the carrier 62, that is, the rotation of the electric motor 40 is transmitted to the input shaft 80.
  • the cover member 81 rotates in the same direction by the rotation of the input shaft 80 in the apply direction. Then, by the rotation of the cover member 81 in the apply direction, the rotation / linear motion ramp 121, the first spring clutch 155, and the spring seat 157 rotate in the same direction. At the initial stage of the application, the rotational torque transmitted to the cover member 81 is smaller than the rotational resistance torque obtained by adding the frictional resistance between the rotating annular body 146 and the spring seat 157 to the rotational resistance of the first spring clutch 155. The rotation of the cover member 81 in the apply direction is transmitted to the spindle rod 83 via the rotating annular body 146. Subsequently, as shown in FIG.
  • the rotation resistance torque is not transmitted to the adjuster nut 84 by the second spring clutch 200 due to the rotation of the spindle rod 83 (the adjuster nut 84 is rotated in the apply direction of the spindle rod 83).
  • the adjuster nut 84 since the adjuster nut 84 is restricted from rotating relative to the piston 18, the adjuster nut 84 moves in the axial direction toward the bottom 19 of the piston 18.
  • the rotational torque from the input shaft 80 (cover member 81) is increased so that the rotational torque becomes the rotational resistance torque by the first spring clutch 155, and the frictional resistance between the rotating annular body 146 and the spring seat 157 is increased. If the rotation torque is larger than the applied rotational resistance torque, the rotation of the spindle rod 83 and the rotating annular body 146 stops and starts to rotate relative to the cover member 81 and the rotary linear motion lamp 121.
  • the rotational torque transmitted from the cover member 81 is transmitted from the rotary linear motion lamp 121 to the support lamp 120 via each ball 22, so that the rotational linear motion lamp 121 is caused by the action of the ball and ramp mechanism 82.
  • a propulsive force toward the other end is generated, and the spindle rod 83 is directly moved to the other end via the rotating annular body 146.
  • the rotational torque transmitted from the support lamp 120 is transmitted from the small-diameter female screw portion 127 to the small-diameter male screw portion 185 of the spindle rod 83, so that the first small-diameter screw fitting portion 191 acts on the spindle rod 83.
  • a thrust obtained by adding the thrust generated in the ball and ramp mechanism 82 to the thrust generated in the first small diameter screw fitting portion 191 is applied to the piston 18 via the adjuster nut 84.
  • the second large-diameter screw fitting portion 192 between the large-diameter male screw portion 186 of the spindle rod 83 and the large-diameter female screw portion 166 of the adjuster nut 84 is relatively rotated at the initial stage of applying.
  • the adjuster nut 84 is moved to the other end side, and the piston 18 is moved to the other end side to obtain a pressing force to the disk rotor D.
  • the piston 18 Even if the position of the piston 18 with respect to the cylinder 11 changes due to wear of the pair of inner and outer brake pads 2 and 3 due to the operation of the second large-diameter screw fitting portion 192, the piston 18 The original position of the adjuster nut 84 can be adjusted.
  • the ECU 210 is electrically operated until the pressing force (braking force) from the pair of inner and outer brake pads 2 and 3 to the disc rotor D reaches a predetermined value, for example, until the current value of the electric motor 40 reaches a predetermined value.
  • the motor 40 is driven. Thereafter, when the ECU 210 detects that the pressing force to the disc rotor D has reached a predetermined value by the fact that the current value of the electric motor 40 has reached a predetermined value, the ECU 210 stops energization of the electric motor 40. Then, since the rotation of the cover member 81 in the apply direction is stopped, the rotation of the rotation linear motion lamp 151 of the ball and ramp mechanism 82 is stopped.
  • the large-diameter screw fitting portion 192 is configured by a screw fitting portion that does not reversely operate between the spindle rod 83 and the adjuster nut 84 as described above.
  • a first small-diameter screw fitting portion 191 between the small-diameter male screw portion 185 of the spindle rod 83 and the small-diameter female screw portion 127 of the support lamp 120 of the ball and ramp mechanism 82 is also between the spindle rod 83 and the support lamp 120. It is configured as a screw fitting part that does not operate reversely. Further, the second spring clutch 200 applies a rotational resistance torque to the spindle rod 83 with respect to rotation in the release direction with respect to the adjuster nut 84. As a result, the stop state of the adjuster nut 84 is maintained, the piston 18 is held at the braking position, and the operation of the parking brake is completed.
  • the reaction force of the pressing force from the disk rotor D is adjusted by the adjuster nut 84, the spindle rod 83, the support ramp 120 of the ball and ramp mechanism 82, the second thrust bearing 132, the input shaft. It is transmitted to the bottom wall 11 (see FIG. 2) of the cylinder 15 through the 80 disk-shaped portion 90 and the first thrust bearing 113, and serves as a holding force for the piston 18.
  • the thrust generated by the ball and ramp mechanism 82 acts on the third thrust bearing 145 that is disposed on the radially inner side of the piston 18 and has to be used with a small diameter. The durability of the brake 1 is improved.
  • first thrust bearing 113 and the second thrust bearing 132 on which the reaction force of the pressing force from the disk rotor D acts are arranged on the outer side in the radial direction of the piston 18 and can be employed with a large diameter.
  • the durability of the disc brake 1 can be improved.
  • the ECU 210 returns the piston 18 based on the parking release operation of the parking switch 211, that is, in the release direction in which the piston 18 is separated from the disk rotor D. Is driven to rotate. As a result, the spur multi-stage reduction mechanism 44 and the planetary gear reduction mechanism 45 rotate in the release direction to return the piston 18, and the rotation is transmitted to the input shaft 80 via the carrier 62.
  • the rotation resistance torque and the rotation resistance torque in the release direction of the spindle rod 83 with respect to the adjuster nut 84 by the second spring clutch 200 are applied, and the total rotation resistance torque is determined by the spring seat 157 and the rotating annular body.
  • the spindle rod 83 and the rotating annular body 146 do not rotate while stopped and rotate relative to the cover member 81 because the torque is larger than the rotational resistance torque due to the frictional resistance between the cover member 146 and the cover member 81.
  • each vertically long protrusion 168 of the adjuster nut 84 is formed on each notch 183 of the cover member 81.
  • the relative rotation between the adjuster nut 84 and the cover member 81 is restricted, and the rotation of the cover member 81 in the release direction is stopped. The movement of is stopped. Thereby, at the time of release, it can suppress that adjuster nut 84 moves to one end side excessively.
  • the ball and ramp mechanism 82 is first returned to the initial position, the spindle rod 83 is retracted, and then the adjuster nut 84 is retracted. The holding force to 18 is released.
  • the first thrust bearing 113 and the first thrust bearing 132 to which the reaction force of the pressing force from the disc rotor D acts are arranged on the radially outer side of the piston 18. Therefore, the outer diameter can be formed as large as possible, and the durability of the disc brake 1 can be improved.
  • the third thrust bearing 145 disposed on the radially inner side of the piston 18 has a structure in which the reaction force of the pressing force from the disk rotor D does not act, so that the outer diameter can be reduced, Miniaturization can be achieved.
  • the ball and ramp mechanism 82 is not disposed inside the piston 18 but is disposed closer to the bottom wall 11 of the cylinder 15 than the piston 18 in the axial direction.
  • the outer diameter and the inner diameter of 18 can be made smaller, and consequently the disc brake 1 can be reduced in size.
  • the input shaft 80 is rotated by the rotational drive from the electric motor 40 and only transmitted to the cover member 81, and moves forward and backward toward the hydraulic chamber 21. Therefore, even if the driver operates the parking brake mechanism 43 while depressing the brake pedal, it is possible to prevent the volume of the brake fluid in the hydraulic chamber 21 from fluctuating. It is possible to prevent pulsation (vibration) from being transmitted to the brake pedal. Thereby, the pedal feeling at the time of operating the parking brake mechanism 43 can be made favorable, performing a brake pedal operation.
  • the ball and ramp mechanism 82 is returned to the initial position, and then the spindle rod 83 is retracted to release the holding force to the piston 18. Yes. Therefore, the apply operation can be started immediately even if the apply operation is switched to the apply operation during the release.
  • the spur multi-stage reduction mechanism 44 and the planetary gear reduction mechanism 45 are used as the reduction mechanism, but other known reduction mechanisms such as a cycloid reduction gear and a wave reduction gear are used. May be.
  • the ball 122 is employed as the rolling element of the ball and ramp mechanism 82, a roller and ramp mechanism using a cylindrical member having excellent load resistance may be employed.
  • the parking brake mechanism 43 which is a parking brake mechanism, may be operated in the case of hill start assist or hill down assist for assisting vehicle start-up, auto stop when the vehicle is stopped with the accelerator off.
  • the first aspect of the disk brake of the embodiment described above is a bottomed cylindrical shape in which one of a pair of pads arranged on both sides in the axial direction of the rotor is moved in the axial direction of the rotor with the rotor interposed therebetween.
  • Piston a caliper body having a cylinder in which the piston is movably disposed, an electric motor provided in the caliper body, and provided in the caliper body, and propelling the piston by a ball and ramp mechanism.
  • a parking brake mechanism that is held at a braking position, and the parking brake mechanism includes an input member having a disk-like portion that is rotated by the rotation from the electric motor and rotates on the bottom side of the cylinder, and the axial direction. Is connected to the outer periphery of the disk-shaped portion of the input member on one end side of the input member, and extends into the piston on the other end side in the axial direction.
  • a Jo of the cover member is rotatable with the input member, a cylindrical cover member in which the ball-and-ramp mechanism is accommodated therein,
  • a shaft member that is screw-fitted to the ball-and-ramp mechanism, is rotatable by the operation of the ball-and-ramp mechanism, and is linearly movable, and is screw-fitted to the shaft member and rotates relative to the shaft member.
  • a pressing member that presses the piston in the axial direction includes: A rotary linear motion lamp that is disposed inside the cover member on the one end side in the axial direction of the cover member, engages with the cover member, and rotates together with the cover member, the rotational linear motion ramp, and the input A support lamp which is disposed between the member and is screwed to the shaft member and transmits the axial reaction force transmitted from the rotor to the shaft member to the input member during braking.
  • the rotary linear motion lamp is biased toward the input member by a biasing member supported by the cover member on the other end side in the axial direction of the cover member.
  • the ball and ramp mechanism is disposed closer to the bottom of the cylinder in the axial direction than the piston.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)
  • Braking Systems And Boosters (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un frein à disque qui est rendu plus compact et qui améliore une sensation sur la pédale lors de l'utilisation d'un frein de stationnement. Ce mécanisme de frein de stationnement comporte un élément d'entrée auquel est transmise la rotation en provenance d'un moteur électrique, un élément de couvercle qui est joint à l'élément d'entrée sur un côté d'extrémité dans la direction axiale, un élément d'arbre qui est assemblé par vissage avec un mécanisme à bille et rampe, et un élément de pression qui est assemblé par vissage à l'élément d'arbre. Le mécanisme à bille et rampe comporte une rampe angulaire/linéaire avec laquelle l'élément de couvercle interagit, et une rampe d'appui qui est assemblée par vissage à l'élément d'arbre. Un élément de sollicitation sollicite la rampe angulaire/linéaire en direction de l'élément d'entrée.
PCT/JP2017/010135 2016-06-28 2017-03-14 Frein à disque Ceased WO2018003191A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-127897 2016-06-28
JP2016127897A JP2019143643A (ja) 2016-06-28 2016-06-28 ディスクブレーキ

Publications (1)

Publication Number Publication Date
WO2018003191A1 true WO2018003191A1 (fr) 2018-01-04

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PCT/JP2017/010135 Ceased WO2018003191A1 (fr) 2016-06-28 2017-03-14 Frein à disque

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JP (1) JP2019143643A (fr)
WO (1) WO2018003191A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117957384A (zh) * 2021-12-20 2024-04-30 日立安斯泰莫株式会社 电动制动装置以及驱动单元

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3991859A (en) * 1976-02-27 1976-11-16 General Motors Corporation Adjusting mechanism for a disc brake caliper assembly
JP2008207679A (ja) * 2007-02-27 2008-09-11 Hitachi Ltd 電動ブレーキ装置およびその制御方法
JP2016125550A (ja) * 2014-12-26 2016-07-11 日立オートモティブシステムズ株式会社 ディスクブレーキ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3991859A (en) * 1976-02-27 1976-11-16 General Motors Corporation Adjusting mechanism for a disc brake caliper assembly
JP2008207679A (ja) * 2007-02-27 2008-09-11 Hitachi Ltd 電動ブレーキ装置およびその制御方法
JP2016125550A (ja) * 2014-12-26 2016-07-11 日立オートモティブシステムズ株式会社 ディスクブレーキ

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