WO2018037848A1 - 電動ブレーキ装置 - Google Patents

電動ブレーキ装置 Download PDF

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Publication number
WO2018037848A1
WO2018037848A1 PCT/JP2017/027836 JP2017027836W WO2018037848A1 WO 2018037848 A1 WO2018037848 A1 WO 2018037848A1 JP 2017027836 W JP2017027836 W JP 2017027836W WO 2018037848 A1 WO2018037848 A1 WO 2018037848A1
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WO
WIPO (PCT)
Prior art keywords
shaft
force
outer ring
axial direction
rotation
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/JP2017/027836
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English (en)
French (fr)
Japanese (ja)
Inventor
山崎　達也
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.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co 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 NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2018037848A1 publication Critical patent/WO2018037848A1/ja
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
    • B60T7/00—Brake-action initiating means
    • B60T7/02—Brake-action initiating means for personal initiation
    • B60T7/04—Brake-action initiating means for personal initiation foot actuated
    • B60T7/06—Disposition of pedal
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/069—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags
    • F16D41/07—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags between two cylindrical surfaces
    • 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

Definitions

  • the present invention relates to an electric brake device that generates a braking force by a rotational driving force of an electric motor.
  • the electric brake device transmits the rotational driving force of the electric motor to the rotating shaft through a gear, converts the rotation of the rotating shaft into the axial movement of the linear motion member by the motion conversion mechanism, and the shaft along with the linear motion member.
  • the braking force is exerted by pressing the friction pad moving in the direction against the brake disc.
  • the electric motor used in this electric brake device is driven by receiving electric power supplied from a battery mounted on the vehicle, so when troubles such as abnormal decrease in the charge amount of the battery, sensor failure, disconnection of electric wiring, etc. occur, There is a problem that the brake function cannot be exhibited.
  • an electric brake device having a fail-safe function when the above trouble occurs may be employed (see FIG. 4 of Patent Document 1).
  • an outer ring member disposed so as to surround the rotation shaft is employed as the linear motion member.
  • the motion conversion mechanism a plurality of planetary rollers circumscribing the rotating shaft and inscribed in the outer ring member, a carrier for supporting these planetary rollers so as to rotate and revolve, and an inner periphery of the outer ring member are provided.
  • a planetary roller screw mechanism having a spiral ridge and a circumferential groove provided on the outer periphery of the planetary roller so as to engage with the spiral ridge can be employed.
  • a collar portion is formed that supports the carrier from the rear in the axial direction.
  • the rotational driving force of the electric motor is transmitted to the rotating shaft through the reduction mechanism, and the rotating shaft rotates around the shaft.
  • the planetary roller circumscribing the rotating shaft revolves around the rotating shaft while rotating around the roller shaft by rolling contact with the rotating shaft. Since the spiral ridge provided on the outer ring member and the circumferential groove provided on the planetary roller are engaged, the outer ring member and the planetary roller relatively move in the axial direction as the planetary roller rotates.
  • the movement of the carrier supporting the planetary roller in the axial direction is restricted, and as a result of the rotation of the planetary roller, the outer ring member moves to the front side in the axial direction and is integrated with the outer ring member.
  • a friction pad provided so as to be movable in the axial direction is pressed against the brake disc.
  • the pressing mechanism includes a cam member, a slide member provided in front of the cam member in the axial direction, and a link member provided between the cam member and the slide member.
  • the cam member rotates around the axis.
  • the cam surface formed on the cam member moves the slide member forward in the axial direction via the link member corresponding to the rotation angle. And this slide member presses a rotating shaft to the axial direction front via a spherical body.
  • the drive shaft is rotated by the operation of the parking brake, and this rotation is transmitted to the screw mechanism via the one-way clutch, and the cylindrical rotating member of the screw mechanism
  • the fail-safe function is exhibited by converting the rotational force into the axial movement of the linear motion member (screw shaft).
  • the screw shaft can be made to stand by near the pressing position by the wear compensation function (see paragraph [0037] of Patent Document 3).
  • the clutch spring idles during braking, so that the adjustment nut does not rotate in the piston retraction direction, and the piston (brake pad) cannot be retreated more than a predetermined amount. Also, since the protrusion provided on the rotating disk that can be rotated from the outside and the locking pin provided integrally with the rotor of the motor are locked, the piston can be moved backward greatly even if the adjustment nut is directly rotated. I can't. Therefore, when the brake pad is greatly worn and replaced with a new one, it is necessary to disassemble the pressing mechanism.
  • an object of the present invention is to reduce the weight of the electric brake device and to easily retract the piston when replacing the friction pad without hindering the brake operation by the motor.
  • an electric motor a rotating shaft that rotates around the shaft by the rotational driving force of the electric motor, and a linearly-moving member that is movable in the axial direction of the rotating shaft.
  • a motion conversion mechanism that converts the rotation of the rotary shaft into an axial movement of the linear motion member; and an axial direction along with the axial movement of the linear motion member.
  • a friction pad that moves to the center, a rotation mechanism that rotates around an axis by the driver's operating force, and an intermediate amount disposed between the rotation shaft and the rotation mechanism.
  • the transmission of the operation force from the rotation mechanism to the rotation shaft is cut off when smaller than a predetermined threshold value, while the rotation mechanism moves from the rotation mechanism to the rotation shaft when the operation amount is equal to or greater than the threshold value.
  • Clutch machine that allows transmission of the operating force to If, to constitute a electric braking apparatus having a.
  • the clutch mechanism rotates the rotating shaft around the shaft, thereby preventing the reaction force in the axial rearward direction via the rotating shaft. be able to. For this reason, it is not necessary to increase the thickness of the gear box (cover) so much, and it is possible to use a non-metallic material such as a non-ferrous material or a resin as the material. Become.
  • shut-off mechanism it is possible to prevent the rotational drive of the rotary shaft by the electric motor from competing with the rotational drive of the rotary shaft by the driver's operating force, so that the electric motor can be driven normally. It is possible to achieve both stable rotational driving of the rotating shaft when the motor is in operation and quick operation of the fail-safe mechanism when the electric motor fails.
  • the clutch mechanism can transmit the operation force in a direction in which the friction pad is pressed against the brake disc from the rotation mechanism to the rotating shaft, while the friction pad is transmitted from the brake disc. It is preferable that the one-way clutch is configured to prevent transmission of the operating force in the separating direction from the rotating mechanism to the rotating shaft.
  • the clutch mechanism has an outer peripheral surface of the rotating shaft that is inclined in the same circumferential direction with a predetermined circumferential interval from the inner peripheral surface with the rotating shaft inserted through the shaft center.
  • An outer ring formed with a cam surface that forms a wedge space, a return spring that urges the outer ring in one direction around the axis, a wedge spring, and the rotation shaft and the cam surface.
  • a plurality of engagement elements that can be engaged with each other, a pocket that holds the plurality of engagement elements at a predetermined interval, a retainer that is formed with a locking pin that rises radially outward, and the holding against the outer ring.
  • a switch spring capable of urging the retainer in the circumferential direction, and a protrusion that abuts against the locking pin and prevents the retainer from rotating beyond a predetermined angle by the urging force of the return spring. It is preferable to have a configuration.
  • the electric brake device is configured such that when the operation amount of the rotation mechanism is smaller than a predetermined threshold between the rotation mechanism that rotates around the axis by the driver's operation force and the rotation axis, the rotation is performed.
  • a clutch mechanism that interrupts transmission of the operating force from the moving mechanism to the rotating shaft, and permits transmission of the operating force from the rotating mechanism to the rotating shaft when the operation amount is equal to or greater than the threshold value. It was adopted. By doing so, the electric brake device can be reduced in weight, and the piston can be easily retracted when replacing the friction pad without hindering the brake operation by the motor.
  • Sectional view along the line II-II in FIG. 1 is a longitudinal sectional view showing a main part of the electric brake device shown in FIG. Sectional view along line IV-IV in FIG. Partial sectional view taken along line VV in FIG. Sectional view along line VI-VI in FIG.
  • FIG. 5 is a partial cross-sectional view showing a brake pedal operating force blocking mechanism in a state where the operating force is blocked. It is a partial cross-sectional view showing a brake pedal operating force blocking mechanism, the operating force can be transmitted
  • the electric brake device includes an electric motor 10, a rotary shaft 23 that rotates around the axis by the rotational driving force of the electric motor 10, a linear motion member 24 that is movable in the axial direction of the rotary shaft 23, and the rotation of the rotary shaft 23. Is converted to an axial movement of the linear motion member 24, a friction pad 13 provided in front of the linear motion member 24 in the axial direction and moved in the axial direction along with the axial movement of the linear motion member 24, The rotating mechanism 15 that rotates about the axis by the driver's operating force, and the rotating mechanism 23 is disposed between the rotating mechanism 15 and the operation amount of the rotating mechanism 15 is greater than a predetermined threshold value. Is smaller, the transmission of the operation force from the rotation mechanism 15 to the rotation shaft 23 is interrupted, while the operation force from the rotation mechanism 15 to the rotation shaft 23 is greater than the threshold value. Clutch mechanism 4 that allows transmission of The are a major component.
  • This electric brake device normally exerts a braking force by driving the electric motor 10 in accordance with a driver's brake operation.
  • a fail-safe mechanism is provided that obtains braking force by the driver's operating force.
  • the electric brake device includes a brake disk 11 that rotates integrally with a wheel (not shown), and a pair of friction pads 12 that are opposed to each other in the axial direction with the brake disk 11 in between. 13 and an electric motor 10 for moving the friction pads 12 and 13, and the braking force is generated by pressing the friction pads 12 and 13 against the brake disk 11 with the power transmitted from the electric motor 10.
  • this electric brake device can generate a braking force even in a state where the braking force by the electric motor 10 cannot be exerted due to some trouble, so that the wire cable 14 provided so as to be pulled by the operating force of the driver, And a rotation mechanism 15 connected to one end of the wire cable 14.
  • This electric brake device has a caliper body 19 having a shape in which a pair of facing portions 16 and 17 facing each other in the axial direction with the brake disc 11 in between are connected by a bridge 18 positioned on the outer diameter side of the brake disc 11.
  • the friction pad 12 is disposed between one facing portion 16 of the caliper body 19 and the brake disk 11, and the friction pad 13 is disposed between the other facing portion 17 and the brake disk 11.
  • the friction pads 12 and 13 are guided by pad pins (not shown) attached to the caliper body 19 and slide parts (not shown) provided on the caliper bracket 21 so as to be movable in the axial direction of the brake disc 11. Has been.
  • the caliper body 19 is moved in the axial direction of the brake disc 11 by a pair of slide pins 22 attached to a caliper bracket 21 fixed to a knuckle (not shown) that supports a wheel by bolts 20. Supported as possible. Accordingly, when the friction pad 13 shown in FIG. 2 or the like moves forward in the axial direction and is pressed against the brake disc 11, the caliper body 19 moves rearward in the axial direction due to the reaction force received from the brake disc 11, and the caliper The friction pad 12 on the opposite side is also pressed against the brake disk 11 by the movement of the body 19.
  • the other facing portion 17 of the caliper body 19 includes a cylindrical caliper housing 17A that is open at both front and rear ends in the axial direction, and a right angle with respect to the axial direction from the axially rear end of the caliper housing 17A.
  • the caliper flange 17B extends in a direction (a direction parallel to the brake disc 11).
  • the caliper housing 17A has a rotation shaft 23, an outer ring member functioning as a linear motion member 24 disposed so as to surround the rotation shaft 23 (hereinafter, the same reference numeral as the linear motion member 24), and the rotation shaft 23.
  • a planetary roller screw mechanism that functions as a motion conversion mechanism 25 that converts the rotation of the outer ring member 24 into an axial movement of the outer ring member 24 (hereinafter, the same reference numeral as that of the motion conversion mechanism 25 is attached).
  • the friction pad 13 is disposed in front of the outer ring member 24 in the axial direction.
  • the electric motor 10 is attached to the caliper flange 17B.
  • a reduction mechanism 26 is provided between the electric motor 10 and the rotary shaft 23 to reduce and transmit the rotation of the electric motor 10 to the rotary shaft 23.
  • the speed reduction mechanism 26 is accommodated in a cover 27 provided so as to cover the end opening of the caliper housing 17A in the axial direction and the side surface of the caliper flange 17B (see FIG. 4).
  • the speed reduction mechanism 26 includes a first gear 26A that rotates around the shaft integrally with the rotor shaft 10A of the electric motor 10, a second gear 26B that meshes with the first gear 26A, and a second gear 26B.
  • a third gear 26C that rotates about the axis integrally with the gear 26B and has a smaller number of teeth than the second gear 26B; a fourth gear 26D that meshes with the third gear 26C and rotates about the axis integrally with the rotary shaft 23;
  • Have The rotation of the electric motor 10 is transmitted through the plurality of gears 26 ⁇ / b> A, 26 ⁇ / b> B, 26 ⁇ / b> C, 26 ⁇ / b> D after being sequentially decelerated and input to the rotary shaft 23.
  • the fourth gear 26D is supported by the caliper flange 17B and the cover 27, and the movement in the axial direction is restricted.
  • the planetary roller screw mechanism 25 includes a plurality of planetary rollers 25A circumscribing the rotating shaft 23 and inscribed in the outer ring member 24, and a carrier 25B that supports the planetary rollers 25A so that they can rotate and revolve. And a spiral protrusion 25C provided on the inner periphery of the outer ring member 24, and a circumferential groove 25D provided on the outer periphery of the planetary roller 25A so as to engage with the spiral protrusion 25C.
  • the plurality of planetary rollers 25A are arranged at equal intervals in the circumferential direction.
  • Each planetary roller 25 ⁇ / b> A is in rolling contact with the outer periphery of the rotating shaft 23 and the inner periphery of the outer ring member 24.
  • the contact portion of the rotating shaft 23 with respect to the planetary roller 25A is a cylindrical surface.
  • the planetary roller 25 ⁇ / b> A rotates by the rotational force received from the outer periphery of the rotating shaft 23, and accordingly, the planetary roller 25 ⁇ / b> A rolls around the inner periphery of the outer ring member 24 and revolves.
  • the spiral ridge 25C on the inner periphery of the outer ring member 24 is a spiral ridge extending obliquely with respect to the circumferential direction.
  • the circumferential groove 25D on the outer periphery of the planetary roller 25A is a groove extending in parallel to the circumferential direction.
  • the circumferential groove 25D having a lead angle of 0 degree is provided on the outer periphery of the planetary roller 25A.
  • a spiral groove having a lead angle different from that of the spiral protrusion 25C may be provided. Good.
  • the outer ring member 24 is supported on the inner surface of the caliper housing 17A so as to be movable in the axial direction.
  • a contact portion of the inner surface of the caliper housing 17A with respect to the outer ring member 24 is a cylindrical surface.
  • the outer ring member 24 has a concave portion 29 that engages with a convex portion 28 formed on the back surface of the friction pad 13, and is prevented from rotating with respect to the caliper housing 17 ⁇ / b> A by the engagement of the convex portion 28 and the concave portion 29.
  • the inner peripheral surface of the caliper housing 17A is is provided with outer retaining ring 17A 1, the outer ring retaining ring 17A 1, moving in the axially rearward of the outer ring member 24 is restricted.
  • the carrier 25B extends in the axial direction between a pair of carrier plates 25B 1 and 25B 2 facing in the axial direction with the planetary roller 25A in between and the planetary rollers 25A adjacent in the circumferential direction, and the carrier plates 25B 1 and 25B 2. having a connecting portion 25B 3 for connecting to each other, and a roller shaft 25B 4 which rotatably supports the respective planetary rollers 25A.
  • Each carrier plate 25B 1 , 25B 2 is formed in an annular shape that penetrates the rotating shaft 23, and a bearing 30 is mounted between each carrier plate 25 B 1 , 25 B 2 and the rotating shaft 23.
  • Both end portions of the roller shaft 25B 4 is movably supported in the radial direction of the outer ring member 24 in the long hole 31 formed on a pair of carrier plate 25B 1, 25B 2. Further, at both ends of the roller shaft 25B 4, the elastic ring 32 so as to circumscribe the roller shaft 25B 4 of all of the planetary rollers 25A in the circumferential direction spaced is stretched. The elastic ring 32 prevents slippage between the planetary roller 25 ⁇ / b> A and the rotary shaft 23 by pressing each planetary roller 25 ⁇ / b> A against the outer periphery of the rotary shaft 23.
  • a load sensor 33 is provided behind the motion conversion mechanism 25 in the axial direction.
  • This load sensor 33 is a magnetic load sensor (hereinafter, the same reference numeral as that of the load sensor 33), and includes a flange member 33A and a flange member 33A that cause deflection when a load is input from the front in the axial direction.
  • the support member 33B is supported from the rear in the axial direction, includes a magnetic target 33C that generates magnetic flux, and a magnetic sensor 33D that detects the magnetic flux generated by the magnetic target 33C.
  • the flange member 33A is an annular plate-like member formed of a metal such as iron.
  • the support member 33B is formed of a metal such as iron and is fitted on the outer peripheral edge of the flange member 33A.
  • the outer peripheral edge of the support member 33B is supported by the inner surface of the caliper housing 17A.
  • Axial rear end of the support member 33B is in contact with the protrusion 17A 2 provided on the inner surface of the caliper housing 17A.
  • the axial front end of the flange member 33A and the support member 33B is in the outer ring retaining ring 17A 1 on the inner surface of the caliper housing 17A abuts, by axial movement of the magnetic load sensor 33 is regulated Yes.
  • a cylindrical portion 33E is continuously provided on the inner peripheral side of the support member 33B so as to face the inner diameter side of the flange member 33A.
  • a plurality of bearings 34 are mounted on the inner periphery of the cylindrical portion 33E at intervals in the axial direction, and the rotary shaft 23 and the magnetic load sensor 33 are capable of relative rotation around the axis.
  • the magnetic target 33C is fixed to the inner periphery of the flange member 33A.
  • the magnetic sensor 33D is fixed to the outer periphery of the cylindrical portion 33E of the support member 33B so as to face the magnetic target 33C in the radial direction.
  • each planetary roller 25A and the carrier plate 25B 2 of the axially rearward thrust bearing 35 which rotatably supports the planetary rollers 25A is incorporated.
  • a thrust plate 36 which revolves together with the carrier plate 25B 2 are provided.
  • a thrust bearing 37 is incorporated between the thrust plate 36 and the flange member 33A of the magnetic load sensor 33. The thrust plate 36 can be rotated relative to the magnetic load sensor 33 around the axis by the thrust bearing 37.
  • Magnetic load sensor 33 the thrust plate 36, via the thrust bearing 37, by abutting the axially rearward to the carrier plate 25B 2, and restricts the movement in the axial direction behind the carrier 25B.
  • a second retaining ring 39 is mounted on the outer periphery of the rotating shaft 23 closer to the rear in the axial direction.
  • the second retaining ring 39 is in contact with a ring member 40 provided coaxially with the rotary shaft 23 from the rear in the axial direction, and the ring member 40 is in contact with the support member 33B from the rear in the axial direction. Due to the contact between the ring member 40 and the support member 33B, the rotation shaft 23 is restricted from moving forward in the axial direction with respect to the support member 33B.
  • the carrier plate 25B 1 of the axial forward movement of the axially forward is restricted by the first stop ring 38 attached to the axial forward end of the rotary shaft 23. Therefore, relative movement of the carrier 25B and the planetary roller 25A held by the carrier 25B is restricted relative to the rotating shaft 23 in the axial front and the axial rear.
  • a seal cover 41 that closes the opening at the front end in the axial direction of the outer ring member 24 is attached to the end portion in the axial direction of the outer ring member 24.
  • the seal cover 41 prevents foreign matter from entering the outer ring member 24.
  • one end of a cylindrical bellows 42 formed so as to be expandable and contractable in the axial direction is fixed to an axially forward end of the outer ring member 24, and the other end of the bellows 42 is an opening in the axially forward direction of the caliper housing 17A. It is fixed to the edge.
  • the bellows 42 prevents foreign matter from entering between the sliding surfaces of the outer ring member 24 and the caliper housing 17A.
  • the reaction force is magnetically transmitted through the outer ring member 24, the planetary roller screw mechanism 25, the thrust plate 36, and the thrust bearing 37. It is transmitted to the flange member 33A of the type load sensor 33.
  • the reaction force is transmitted to the flange member 33A, the flange member 33A bends rearward in the axial direction, and the magnetic target 33C fixed to the flange member 33A and the magnetic sensor 33D fixed to the support member 33B are moved in the axial direction. Relative displacement. Then, the output signal of the magnetic sensor 33D changes corresponding to this relative displacement.
  • the axial load applied to the flange member 33A can be determined based on the output signal of the magnetic sensor 33D. The size can be detected.
  • a clutch mechanism 43 is provided on the rear side in the axial direction of the rotating shaft 23. As shown in FIG. The clutch mechanism 43 is capable of transmitting a driver's operating force in a direction in which the friction pad 13 is pressed against the brake disk 11 from the rotation mechanism 15 that rotates about the axis to the rotation shaft 23, while the friction pad 13 13 is a one-way clutch that interrupts transmission of the operating force in the direction of releasing the pressure of 13 from the rotating mechanism 15 to the rotating shaft 23.
  • the clutch mechanism 43 is provided between an outer ring 43A in which the rotary shaft 23 is inserted in the center of the shaft, a return spring 43B that urges the outer ring 43A in one direction around the axis, and the rotary shaft 23 and the outer ring 43A.
  • the rotation mechanism 15 has a wire lever 15A to which the wire cable 14 is connected, and a lever shaft 15B that rotates around the axis together with the wire lever 15A.
  • the return spring 43B is provided around the lever shaft 15B, and the outer ring 43A and the lever shaft 15B are connected coaxially.
  • FIG. 9A As shown in FIG. 9B, on the inner peripheral surface of the outer ring 43A, with a predetermined circumferential spacing, the cam surface 43A 1 inclined in the same circumferential direction is formed. Between the cam surfaces 43A 1 and the outer peripheral surface 23A of the rotary shaft 23, is gradually narrowed wedge spaces is the distance between the cam surface 43A 1 and the outer peripheral surface 23A toward the one direction of the circumferential direction is formed Yes.
  • Engaging member 43C is an in cylindrical rollers, in the radial clearance is wide portion of the wedge spaces, while a gap between the at least one cam surface 43A 1 or the outer peripheral surface 23A, the diameter of the wedge spaces in direction gap is narrow portion, of a size to engage with both the cam surfaces 43A 1 and the outer peripheral surface 23A is employed.
  • the holder 43D has a pocket 43F in which the engaging element 43C is stored. Inside each pocket 43F and biasing member 43G is provided by the biasing member 43G, engaging elements 43C housed in the pocket 43F is, between the cam surfaces 43A 1 and the outer peripheral surface 23A of the wedge spaces The gap is biased in a direction that gradually decreases.
  • Switch spring 43E has a shape of a side view copolymers, with its base is fitted into the fitting hole 43A 2 formed on the outer ring 43A, the through hole 43D 1 in which the distal end portion is formed in the retainer 43D It is inserted. The retainer 43D, locking pin 43D 2 erected radially outward is formed. On the inner surface side of the cover 27 in which the cage 43D is accommodated, a protrusion 27A is formed that rises radially inward toward the cage 43D.
  • the outer ring 43A and the rotating mechanism 15 that rotates together with the outer ring 43A are pivoted by the biasing force of the return spring 43B. It is in a state of being biased in one direction around (see the arrow attached to the outer ring 43A in FIGS. 9A and 10A).
  • the cage 43D connected via the switch spring 43E is also urged in the same direction to rotate. Then, the locking pin 43D 2 and the cover 27 which is formed in protrusion 27A formed on the retainer 43D is the contact, the rotation of the retainer 43D is stopped.
  • the outer ring 43A stops at a position rotated by a predetermined angle from the stop position of the retainer 43D when the wire lever 15A contacts the stopper 15C provided on the cover 27. At this time, the switch spring 43E is slightly distorted from the original U-shape by the urging force of the return spring 43B (see FIGS. 9A and 10A).
  • the engaging element 43C is cam radial clearance wedge space is located in wide portion, which is formed on the engaging member 43C and the outer ring 43A (hereinafter, referred to as a free state.) state that the gap between the produced (the outer peripheral surface 23A in FIG. 9A and FIG. 10A) at least one surface of the outer peripheral surface 23A of the surface 43A 1 or the rotation axis 23 becomes.
  • this free state no rotational force is transmitted between the outer ring 43A and the rotating shaft 23, and the rotating shaft 23 is not affected by the rotation by the rotating mechanism 15 and is smoothly driven by the rotation of the electric motor 10. Can rotate.
  • the switch spring 43E returns to the original U-shape, and the engagement element 43C held by the retainer 43D moves to a place where the radial gap of the wedge space is narrow, and the cam surface 43A 1 and the outer peripheral surface 23A are engaged with each other to enter a state where the rotational force can be transmitted from the outer ring 43A to the rotating shaft 23 (hereinafter referred to as a standby state).
  • the amount of operation of the driver's brake pedal 44 and the like is relatively small, and the operation force is not transmitted to the rotary shaft 23.
  • the amount of play (the threshold value of the operation amount from the free state to the standby state) can be changed as appropriate by changing the positional relationship between the protrusion 27A provided on the cover 27 and the stopper 15C.
  • the normal braking operation is performed regardless of the wear amount by increasing the operation amount so that the wear pads 12 and 13 move largely by the amount corresponding to the wear amount. be able to. Even if the friction pads 12 and 13 do not come into contact with the brake disk 11 in one operation, the friction pad 13 is moved further forward in the axial direction by releasing the operation force and then applying the operation force again. Therefore, the braking force can be reliably obtained. On the other hand, similarly to the above, by releasing the operation force, the braking force can be released by separating the friction pad 13 from the brake disc 11 by the reaction force of the contact between the brake disc 11 and the friction pad 13. it can.
  • the operation force of the driver is released (the free state of the turning mechanism 15), and the motor 10 is rotated.
  • the outer ring member 24 can be largely moved rearward in the axial direction.
  • a wire pedal portion 45 to which a wire end fitting provided at an end portion of the wire cable 14 is connected and a blocking mechanism 46 are attached to a brake pedal 44 operated by a driver's foot. It has been.
  • the brake pedal 44 is supported so as to be swingable about a fulcrum shaft 47.
  • a stroke sensor 48 that detects the depression amount of the brake pedal 44 is attached to the brake pedal 44.
  • the wire connector portion 45 is supported so as to be able to swing so as to have a swing center at the same position as the fulcrum shaft 47 of the brake pedal 44.
  • the wire connector portion 45 can swing independently of the brake pedal 44 so that the brake pedal 44 can swing while being separated from the wire connector portion 45.
  • the shut-off mechanism 46 is formed on a solenoid mounting member 49 that is swingably supported around a fulcrum shaft 47, a solenoid actuator 50 that is mounted on the solenoid mounting member 49, a brake pedal 44, and a wire connector portion 45, respectively.
  • the solenoid actuator 50 has a plunger 50A that advances and retreats in parallel with the fulcrum shaft 47, and is configured such that the plunger 50A moves forward when energization stops and the plunger 50A moves backward when energization occurs.
  • the plunger engaging holes 44A and 45A are arranged so as to be located on the same line as the plunger 50A of the solenoid actuator 50 in the initial position where the brake pedal 44 is not depressed.
  • the blocking mechanism 46 advances the plunger 50 ⁇ / b> A of the solenoid actuator 50 so that the brake pedal 44 and the wire connector 45 swing together when the driver steps on the brake pedal 44.
  • the brake pedal is configured so that the operation force of the driver acting on the brake pedal 44 is blocked from being transmitted to the wire connector portion 45 by retreating the plunger 50A of the solenoid actuator 50. It can be set as the isolation
  • the shut-off mechanism 46 is in a disconnected state when energized and is connected when energization is stopped. It functions as a clutch.
  • shut-off mechanism 46 it is possible to prevent the electric motor 10 from competing with the rotational drive of the rotary shaft 23 by the electric motor 10 and the rotational drive of the rotary shaft 23 by the operating force of the driver. It is possible to achieve both stable rotation driving of the rotating shaft 23 during normal driving and quick operation of the fail-safe mechanism when the electric motor 10 fails.
  • the braking force can be prevented from acting against the driver's intention. For this reason, the operating characteristics are greatly improved. Furthermore, the outer ring member 24 can be easily retracted when replacing the friction pads 12 and 13 without hindering the brake operation by the motor 10.
  • the electric brake device according to each of the embodiments described above is merely an example, and the electric brake device can be reduced in weight, and can be easily replaced when the friction pads 12 and 13 are replaced without impeding the brake operation by the motor 10.
  • the piston can be retracted can be solved, the shape, arrangement, and the like of each constituent member can be appropriately changed.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)
  • Braking Systems And Boosters (AREA)
  • Braking Elements And Transmission Devices (AREA)
PCT/JP2017/027836 2016-08-24 2017-08-01 電動ブレーキ装置 Ceased WO2018037848A1 (ja)

Applications Claiming Priority (2)

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JP2016163812A JP6739287B2 (ja) 2016-08-24 2016-08-24 電動ブレーキ装置
JP2016-163812 2016-08-24

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WO2018037848A1 true WO2018037848A1 (ja) 2018-03-01

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WO (1) WO2018037848A1 (enExample)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112298126A (zh) * 2019-08-01 2021-02-02 株式会社万都 一种车辆卡钳、车辆的制动方法及车辆
CN112443596A (zh) * 2019-08-30 2021-03-05 比亚迪股份有限公司 线控制动系统及车辆
CN112443595A (zh) * 2019-08-30 2021-03-05 比亚迪股份有限公司 线控制动系统和车辆
IT202100028913A1 (it) * 2021-11-15 2023-05-15 Brembo Spa Dispositivo di rilevazione della forza di serraggio di una pinza freno e sistema di controllo di un impianto frenante
US12497015B2 (en) 2021-11-15 2025-12-16 Brembo S.P.A. Device for detecting the clamping force of a brake caliper and control system of a braking system

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112443599B (zh) * 2019-08-30 2022-01-07 比亚迪股份有限公司 线控制动系统及车辆
JP7758943B2 (ja) * 2022-02-10 2025-10-23 株式会社椿本チエイン カムクラッチ
KR20250023556A (ko) * 2022-07-19 2025-02-18 히다치 아스테모 가부시키가이샤 액츄에이터 및 그 액츄에이터 케이스의 제조 방법 및 제조용 중자

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0522234U (ja) * 1991-09-05 1993-03-23 曙ブレーキ工業株式会社 ブレーキアクチユエータ
JP2015137667A (ja) * 2014-01-21 2015-07-30 Ntn株式会社 電動ブレーキ装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0522234U (ja) * 1991-09-05 1993-03-23 曙ブレーキ工業株式会社 ブレーキアクチユエータ
JP2015137667A (ja) * 2014-01-21 2015-07-30 Ntn株式会社 電動ブレーキ装置

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112298126A (zh) * 2019-08-01 2021-02-02 株式会社万都 一种车辆卡钳、车辆的制动方法及车辆
CN112298126B (zh) * 2019-08-01 2024-04-16 汉拿万都株式会社 一种车辆卡钳、车辆的制动方法及车辆
CN112443596A (zh) * 2019-08-30 2021-03-05 比亚迪股份有限公司 线控制动系统及车辆
CN112443595A (zh) * 2019-08-30 2021-03-05 比亚迪股份有限公司 线控制动系统和车辆
CN112443595B (zh) * 2019-08-30 2022-02-08 比亚迪股份有限公司 线控制动系统和车辆
IT202100028913A1 (it) * 2021-11-15 2023-05-15 Brembo Spa Dispositivo di rilevazione della forza di serraggio di una pinza freno e sistema di controllo di un impianto frenante
WO2023084476A1 (en) * 2021-11-15 2023-05-19 Brembo S.P.A. Device for detecting the clamping force of a brake caliper and control system of a braking system
US12497015B2 (en) 2021-11-15 2025-12-16 Brembo S.P.A. Device for detecting the clamping force of a brake caliper and control system of a braking system

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