JP2018030437A - Electric brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve weight reduction, and to make a piston easily retreat at the exchange of a brake pad without hindering a brake operation by a motor.SOLUTION: An electric brake device comprises: an electric motor 10; a rotating shaft 23 which positively rotates around an axis by the motor 10, and to which an axial peripheral reverse rotation force acts at braking; a direct-acting member 24 which can move to an axial direction of the rotating shaft 23; a motion conversion mechanism 25 for converting the rotation of the rotating shaft 23 to the movement of the direct-acting member 24 in the axial direction; a friction pad 13 which moves to the axial direction together with the direct-acting member 24; a turning mechanism 15 which turns by an operation force of a driver; and a clutch mechanism 43 which is interposed between the rotating shaft 23 and the turning mechanism 15, blocks the transmission of the operation force to the rotating shaft 23 from the turning mechanism 15 when an operation amount of the turning mechanism 15 is smaller than a preset threshold, and on the other hand, when the operation amount is not smaller than the threshold, permits the transmission of the operation force to the rotating shaft 23 from the turning mechanism 15.SELECTED DRAWING: Figure 3

Description

  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.

  Therefore, for example, as shown in Patent Document 1, an electric brake device having a fail-safe function when the above trouble occurs may be employed (see FIG. 4 in Patent Document 1). In this electric brake device, an outer ring member disposed so as to surround the rotation shaft is employed as the linear motion member. Further, as 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. On the outer periphery of the rotating shaft, a collar portion is formed that supports the carrier from the rear in the axial direction.

  When the electric motor is normally driven by the electric power supplied from the battery, 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. When the rotating shaft rotates around the axis, 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. Here, 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.

  On the other hand, when troubles such as the electric motor failing to drive normally due to abnormal decrease in battery charge, etc., the driver's operating force (for example, brake pedal depression force) Is transmitted via a wire cable to a pressing mechanism held inside. 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.

  When the driver's operating force is applied, the cam member rotates about the axis. When the cam member rotates, 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.

  When the rotating shaft is pressed by the slide member and moves forward in the axial direction, the flange provided on the outer periphery of the rotating shaft comes into contact with the carrier and moves forward in the axial direction together with the planetary roller supported by the carrier. When the planetary roller is moved forward in the axial direction, the outer ring member engaged through the spiral protrusion and the circumferential groove is also moved forward in the axial direction. As the outer ring member moves, the friction pad also moves forward in the axial direction, and the friction pad is pressed against the brake disc.

  In the electric disc brake according to Patent Document 2, external input is mechanically transmitted to the rotor of the motor, the rotor is rotated by a predetermined angle in the piston propulsion direction, and the rotor is rotated by a predetermined angle or more. A mechanism provided with permissible rotation support means is employed. According to this configuration, when the electric motor fails or the like, the fail safe function can be exhibited by directly rotating the rotor by the rotation assisting means. When the brake pad is worn, the adjustment nut moves forward in the axial direction as the rotor rotates, and the brake pad is pressed against the disc rotor (see paragraph [0023] of Patent Document 2).

  Further, in the electric brake device according to Patent Document 3, the drive shaft is rotated by operating 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 is used. The fail-safe function is exhibited by converting the rotational force into the axial movement of the linear motion member (screw shaft). Further, when the brake pad is worn, 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).

JP2015-137667A Japanese Patent No. 4399754 Japanese Patent No. 4357385

  In the electric brake device according to Patent Document 1, when the friction pad is pressed against the brake disk by the pressing force of the fail-safe mechanism, the reaction force in the rearward direction in the axial direction acts on the pressing mechanism via the rotating shaft. To do. This pressing mechanism is held by the gear box as described above. For this reason, the sufficient thickness of the gear box (cover) is secured so that the reaction force acting on the pressing mechanism can be received, or high strength steel is selected as the material, There is a problem that it is necessary to ensure a sufficient strength and it is difficult to reduce the weight.

  Further, in the electric disc brake according to Patent Document 2, the clutch spring idles during braking, so that the adjustment nut does not rotate in the piston retracting direction, and the piston (brake pad) cannot be retracted beyond 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.

  Moreover, in the electric brake device according to Patent Literature 3, unlike the electric brake devices according to Patent Literature 1 and Patent Literature 2, since an axial reaction force does not occur, it is possible to reduce the thickness and weight of the cover. On the other hand, like the electric disc brake device according to Patent Document 2, since the parking brake mechanism is connected, even if the braking force is released, the rotor cannot be rotated and the piston can be largely retracted, When replacing the brake pads, the parking brake mechanism must be disassembled.

  SUMMARY OF THE INVENTION An object of the present invention is to reduce the weight of an electric brake device and make it possible to easily retract a piston when replacing a friction pad without obstructing a brake operation by a motor.

  In order to solve this problem, in the present invention, an electric motor, a rotary shaft that rotates forward around the shaft by the rotational driving force of the electric motor, and that rotates counter-rotatingly around the shaft acts during braking, and A linear motion member provided so as to be movable in the axial direction of the rotary shaft, a motion conversion mechanism for converting rotation of the rotary shaft into axial motion of the linear motion member, and provided in front of the linear motion member in the axial direction A friction pad that moves in the axial direction along with the movement of the linear motion member in the axial direction, a turning mechanism that rotates around the axis by the operating force of the driver, and between the rotating shaft and the turning mechanism. When the operation amount of the rotation mechanism is smaller than a predetermined threshold, the transmission of the operation force from the rotation mechanism to the rotation shaft is interrupted, while the operation amount is When the value is equal to or greater than the threshold value, A clutch mechanism that allows the transmission of the operation force of the rotary shaft, to constitute a electric braking apparatus having a.

  According to this configuration, when the braking force is exerted by the driver's operation force, 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.

  In addition, when the operation amount of the rotating mechanism is small, the transmission of the operation force is cut off, so that sufficient play is ensured for the stroke of the brake pedal, for example, the driver puts his foot on the brake pedal Even if the state remains, the braking force can be prevented from acting against the driver's intention. For this reason, the operating characteristics are greatly improved.

  Further, when the operation amount of the rotation mechanism is small, transmission of the operation force is interrupted, so that the brake pad can be easily replaced by retracting the piston greatly by the motor.

  In the above-mentioned configuration, it is preferable to further include a blocking mechanism that enables the rotation mechanism to be rotated by the operation force when a failure occurs in the rotational drive of the rotation shaft by the electric motor. .

  In this way, by providing the 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.

  In each of the configurations, 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.

  In this way, while the braking force can be smoothly exerted by the driver's operating force, even if the friction pad is worn, the friction pad can be pressed against the brake disc following the wear.

  In the configuration employing the one-way clutch, 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.

  In this one-way clutch, when there is no driver's operating force, the engagement element is held with a gap in the wedge space, and the outer ring and the rotation shaft can freely rotate around each other. Here, when the outer ring is rotated by the operating force against the urging force of the return spring, a standby state is established in which the engagement element is engaged between the outer peripheral surface of the rotating shaft constituting the wedge space and the cam surface of the outer ring. . When the operating force is further increased in this standby state, the rotational force of the outer ring is transmitted to the rotating shaft via the engagement element, and the rotating shaft rotates around the axis, thereby exhibiting a fail-safe function. Between the state in which the outer ring and the rotation shaft can freely rotate around each other and the standby state, the operation force is not transmitted to the rotation shaft even though the operation force is acting. It is possible to reliably prevent the braking force from acting against the driver's intention.

  The electric brake device according to the present invention 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. And a configuration in which a reverse rotational force acts on the rotating shaft during braking. 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.

Side view showing an embodiment of an electric brake device according to the present invention Sectional drawing which follows the II-II line in FIG. 1 is a longitudinal sectional view showing a main part of the electric brake device shown in FIG. Sectional drawing which follows the IV-IV line in FIG. Partial sectional view taken along line VV in FIG. Sectional drawing which follows the VI-VI line in FIG. The longitudinal cross-sectional view which shows the clutch mechanism of the electric brake device shown in FIG. Sectional drawing which follows the VIII-VIII line in FIG. Sectional drawing which follows the IX-IX line in FIG. Sectional drawing which follows the XX line in FIG. It is a fragmentary sectional view which shows the interruption mechanism of the operating force of a brake pedal, (a) is the state which interrupted operating force, (b) is the state which enabled transmission of operating force

  An embodiment of an electric brake device according to the present invention will be described with reference to the drawings. The electric brake device rotates in the forward direction around the axis by the electric motor 10 and the rotational driving force of the electric motor 10 and moves in the axial direction of the rotary shaft 23 and the rotary shaft 23 on which a reverse rotational force acts around the axis during braking. The linear motion member 24 that can be provided, the motion conversion mechanism 25 that converts the rotation of the rotary shaft 23 into the axial movement of the linear motion member 24, and provided in front of the linear motion member 24 in the axial direction. The friction pad 13 that moves in the axial direction along with the movement in the axial direction, the rotating mechanism 15 that rotates around the axis by the operating force of the driver, and the rotating shaft 23 and the rotating mechanism 15 are interposed. When the operation amount of the rotation mechanism 15 is smaller than a predetermined threshold value, the transmission of the operation force from the rotation mechanism 15 to the rotation shaft 23 is interrupted, while the operation amount is equal to or greater than the threshold value. Rotating from the rotation mechanism 15 A clutch mechanism 43 that allows the transmission of the operation force to 23 are the major components.

  This electric brake device normally exerts a braking force by driving the electric motor 10 in accordance with a driver's brake operation. On the other hand, when troubles such as the electric motor 10 not being driven normally occur, a fail-safe mechanism is provided that obtains braking force by the driver's operating force. Hereinafter, the electric brake device will be described in detail.

  As shown in FIGS. 1 and 2, 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. In addition, 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.

  The electric brake device includes a caliper body 19 having a shape in which a pair of opposed portions 16 and 17 that are opposed to each other in the axial direction with the brake disc 11 interposed therebetween 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.

  As shown in FIG. 4, 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.

  As shown in FIG. 2, 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).

  As shown in FIGS. 4 and 5, 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.

  As shown in FIG. 3 and the like, the fourth gear 26D is supported by the caliper flange 17B and the cover 27 and is restricted from moving in the axial direction, and also cannot move relative to the rotating shaft 23 in the axial direction. ing.

  As shown in FIG. 3, 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.

As shown in FIG. 6, 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. When the rotary shaft 23 is rotated, the planetary rollers 25A, while rotating about the roller shaft 25B _4, revolves around the rotation axis 23. That is, 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 protrusion 25C on the inner periphery of the outer ring member 24 is a spiral protrusion extending obliquely with respect to the circumferential direction. On the other hand, the circumferential groove 25D on the outer periphery of the planetary roller 25A is a groove extending in parallel to the circumferential direction. In this embodiment, the circumferential groove 25D having a lead angle of 0 degree is provided on the outer periphery of the planetary roller 25A. However, instead of the circumferential groove 25D, a spiral groove having a lead angle different from that of the spiral protrusion 25C may be provided. Good.

As shown in FIG. 3, 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. . Further, 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. Further, 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.

Between 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. Between the axially aft of the carrier plate 25B ₂ and the magnetic load sensor 33 of the planetary roller 25A (flange member 33A), 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. On the other hand, 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. In addition, 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.

  When the planetary roller screw mechanism 25 rotates the electric motor 10, the rotation of the electric motor 10 is input to the rotary shaft 23 via the speed reduction mechanism 26, and the planetary roller 25A revolves while rotating (see FIG. 3). At this time, the outer ring member 24 and the planetary roller 25A move relative to each other in the axial direction due to the difference in the lead angle between the spiral protrusion 25C and the circumferential groove 25D, but the planetary roller 25A along with the carrier 25B is axially relative to the rotating shaft 23. Since the movement is restricted, the planetary roller 25A does not move in the axial direction, and only the outer ring member 24 moves in the axial direction. Here, when the rotation in the direction in which the outer ring member 24 moves forward in the axial direction is input from the electric motor 10 to the rotation shaft 23, the outer ring member 24 presses the friction pad 13, thereby causing the friction pad shown in FIG. 12 and 13 are pressed against the brake disc 11, and a braking force is applied to the wheels that rotate integrally with the brake disc 11. Further, when rotation in the direction in which the outer ring member 24 moves rearward in the axial direction is input from the electric motor 10 to the rotary shaft 23, the friction pads 12 and 13 shown in FIG. The braking force is released.

  When the electric motor 10 is operated and the friction pads 12 and 13 are pressed against the brake disk 11, 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. When 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. By grasping in advance the relationship between the magnitude of this output signal and the magnitude of the axial load input to the flange member 33A, 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.

  As shown in FIGS. 7 to 10, a clutch mechanism 43 is provided on the axially rear side of the rotating shaft 23. 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. A plurality of engagement elements 43C, a retainer 43D that retains the engagement elements 43C, and a switch spring 43E that can urge the retainer 43D in the circumferential direction with respect to 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.

As shown in FIG. 9, 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.

When the driver's operating force is not acting, as shown in FIGS. 9 (a) and 10 (a), the outer ring 43A and the rotation rotating integrally with the outer ring 43A by the urging force of the return spring 43B are performed. The moving mechanism 15 is biased in one direction around the axis (see the arrow attached to the outer ring 43A in FIGS. 9A and 10A). When the outer ring 43A is urged in this one direction, 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 due to the urging force of the return spring 43B (see FIGS. 9A and 10A).

Thus, in the state where the locking pin 43D ₂ and the projection 27A is in contact with, 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 in the state (hereinafter, which create a gap between the (outer peripheral surface 23A in FIG. 9 (a) and FIG. 10 (a)) at least one surface of the outer peripheral surface 23A of the surface 43A ₁ or the rotation shaft 23, and a free state Will be called). In 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.

Here, when the driver pulls the wire cable 14 by stepping on the brake pedal 44 or the like, the return is returned to the turning mechanism 15 connected to the wire cable 14 and the outer ring 43A that turns together with the turning mechanism 15. An operating force in the direction opposite to the one direction against the urging force of the spring 43B acts. When the operation force to the outer ring 43A acts, while the retainer 43D on the formed locking pin 43D ₂ and the cover 27 to the formed protrusion 27A is in contact state, only the outer ring 43A is rotated in the reverse direction . Then, as shown in FIG. 9B, the switch spring 43E returns to the original U-shape, and the engaging element 43C held by the retainer 43D moves to a position where the radial space in the wedge space is narrow. , engages with both the cam surfaces 43A ₁ and the outer peripheral surface 23A, the rotary shaft 23 twice motive power (hereinafter, referred to as a standby state.) ready transfer from the outer ring 43A becomes.

  Between the free state and the standby state, the amount of operation of the driver's brake pedal 44 and the like is relatively small, and this is an area of play where the operating force is not transmitted to the rotary shaft 23. Thus, by providing play, it is possible to reliably prevent the braking force from acting against the driver's intention. 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.

  In this standby state, when the operating force is further increased, as shown in FIG. 10B, the rotational force is transmitted from the outer ring 43A to the rotating shaft 23 via the engaging element 43C, and the operating force by the driver is increased. Correspondingly, the rotating shaft 23 rotates. As a result, the braking force is exerted by pressing the friction pads 12 and 13 against the brake disk 11 in the same manner as when the electric motor 10 is rotationally driven.

On the other hand, when the operating force is released, the outer ring 43A is rotated in the one direction by the urging force of the return spring 43B. Rotation mechanism 15, the retainer 43D on the locking pin 43D ₂ formed abuts on the projection 27A, the stopper 15C and the wire lever 15A is further provided on the cover 27 is stopped and its rotation by abutting Return to the original free state (see FIG. 9A and FIG. 10A).

  When the operating force is released, the driver's operating force from the outer ring 43A to the rotary shaft 23 is cut off. However, if the brake disc 11 and the friction pad 13 are in contact, the friction pad 13 is braked by the reaction force. The rotating shaft 23 is rotated in a direction away from the disk 11. When the friction pad 13 is retracted to a position where it does not contact the brake disc 11, the reaction force accompanying the contact disappears and the rotation of the rotary shaft 23 stops and remains at that position.

  When the friction pads 12 and 13 are worn, 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.

  When the friction pads 12 and 13 are greatly worn and need to be replaced with new ones, the operation force of the driver is released (the free state of the turning mechanism 15), and the motor 10 is rotated. Thus, the outer ring member 24 can be largely moved rearward in the axial direction.

  As shown in FIG. 1, 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. As shown in FIG. 11A, 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. Here, 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. Plunger engagement holes 44A and 45A. 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.

  As shown in FIG. 11B, the blocking mechanism 46 advances the plunger 50A of the solenoid actuator 50 so that the brake pedal 44 and the wire connector 45 are integrated when the driver steps on the brake pedal 44. It can be set as the connection state which connects between the brake pedal 44 and the wire connector part 45 so that it may rock | fluctuate. Further, as shown in FIG. 11A, by retreating the plunger 50A of the solenoid actuator 50, the operation force of the driver acting on the brake pedal 44 is blocked from being transmitted to the wire connector portion 45. In this case, the brake pedal 44 and the wire connector 45 can be separated from each other. Here, since the plunger 50A of the solenoid actuator 50 moves forward when energization stops and moves backward when energization, the shut-off mechanism 46 is in a disconnected state when energized and is connected when energization is stopped. It functions as a clutch.

  Thus, by providing the 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.

  As described above, in the electric brake device, when the braking force is exerted by the operation force of the driver, the rotation shaft 23 is rotated around the axis by the clutch mechanism 43, so that the rotation shaft 23 is interposed. A reaction force in the axial rearward direction can be prevented. For this reason, it is not necessary to increase the thickness of the cover 27 of the gear box so much, and a non-metallic material such as a non-ferrous material or a resin can be adopted as the material. Therefore, the weight can be reduced. Become. Further, since the transmission of the operation force is cut off when the operation amount of the rotation mechanism 15 is small, sufficient play is ensured for the stroke of the brake pedal 44 and the like. Even in a state where the vehicle is left in place, 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. As long as the problem of the present invention that the piston can be retracted can be solved, the shape, arrangement, and the like of each constituent member can be appropriately changed.

DESCRIPTION OF SYMBOLS 10 Electric motor 13 Friction pad 15 Rotating mechanism 23 Rotating shaft 23A Outer peripheral surface 24 Linear motion member (outer ring member)
25 Motion conversion mechanism (planetary roller screw mechanism)
27A Protrusion 43 Clutch mechanism 43A Outer ring 43A ₁ Cam surface 43B Return spring 43C Engagement element 43D Retainer 43D ₂ Locking pin 43E Switch spring 43F Pocket 46 Blocking mechanism

Claims (4)

An electric motor (10);
A rotating shaft (23) that rotates forward around the axis by the rotational driving force of the electric motor (10) and that rotates in the reverse direction around the axis during braking;
A linear motion member (24) movably provided in the axial direction of the rotation shaft (23);
A motion conversion mechanism (25) that converts the rotation of the rotary shaft (23) into 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 moving in the axial direction along with the movement of the linear motion member (24) in the axial direction;
A rotation mechanism (15) that rotates around an axis by an operation force of the driver;
The rotating mechanism (15) is disposed between the rotating shaft (23) and the rotating mechanism (15), and when the operation amount of the rotating mechanism (15) is smaller than a predetermined threshold value. ) From the rotation mechanism (15) to the rotation shaft (23) when the operation amount is equal to or greater than the threshold value. A clutch mechanism (43) allowing transmission of force;
Electric brake device having   A blocking mechanism (46) that enables the turning mechanism (15) to be turned by the operating force when a failure occurs in the rotational drive of the rotating shaft (23) by the electric motor (10); The electric brake device according to claim 1.   While the clutch mechanism (43) can transmit the operation force in the direction of pressing the friction pad (13) against the brake disc (11) from the rotating mechanism (15) to the rotating shaft (23), The one-way clutch that disables transmission of the operating force in the direction of separating the friction pad (13) from the brake disc (11) from the rotating mechanism (15) to the rotating shaft (23). 2. The electric brake device according to 2. The clutch mechanism (43)
The rotary shaft (23) is inserted into the center of the shaft, and a wedge space is formed between the outer peripheral surface (23A) of the rotary shaft (23) inclined in the same circumferential direction with a predetermined circumferential interval on the inner peripheral surface. An outer ring (43A) on which a cam surface (43A ₁ ) is formed;
A return spring (43B) for urging the outer ring (43A) in one direction around the axis;
A plurality of engagement elements (43C) provided in the wedge space and engageable between the rotation shaft (23) and the cam surface (43A ₁ );
A pocket (43F) for holding the plurality of engagement elements (43C) at a predetermined interval, and a cage (43D) formed with a locking pin (43D ₂ ) standing radially outward,
A switch spring (43E) capable of urging the retainer (43D) in the circumferential direction against the outer ring (43A);
A protrusion (27A) that abuts the locking pin (43D ₂ ) and prevents the retainer (43D) from rotating beyond a predetermined angle by the biasing force of the return spring (43B);
The electric brake device according to claim 3.

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