JP6676989B2 - Electric brake device for vehicles - Google Patents

Description

  The present invention relates to an electric brake device for a vehicle.

  2. Description of the Related Art Conventionally, there has been known a vehicular electric brake device that generates a braking force by a hydraulic pressure when a vehicle runs and generates a braking force by a driving force of a motor when the vehicle is parked. In a configuration in which a braking force is generated by hydraulic pressure, an operation of bleeding brake fluid is performed (for example, Patent Document 1).

JP 2007-186140 A

  In this type of vehicle electric brake device, it is meaningful if a new configuration that facilitates the air bleeding operation is obtained.

  An electric brake device for a vehicle according to the present invention has a motor, a rotation member, and a linear motion member, a motion conversion mechanism that converts rotation of the rotation member by the motor into linear motion of the linear motion member, a cylinder, and A housing provided with a hydraulic chamber, and the cylinder is housed in the cylinder so as to be movable in a first direction and a second direction opposite to the first direction, and the cylinder is operated by the pressure of the hydraulic chamber. Can move in the first direction to press the brake pad, and can be pressed by the linear motion member moving in the first direction to press the brake pad, and move in the second direction. And a piston that is pushed by the linear moving member and moves in the second direction to increase the pressure of the hydraulic chamber. Therefore, for example, in the air bleeding operation of the brake system including the electric brake device for a vehicle, the piston is pushed by the linear moving member moving in the second direction and moves in the second direction to increase the pressure of the hydraulic pressure chamber. By doing so, there is no need for the operator to depress the brake pedal to increase the pressure in the hydraulic chamber. Therefore, for example, the number of workers required for the air bleeding operation can be reduced, so that the air bleeding operation is easily performed.

  Further, in the vehicle electric brake device, as an example, the piston includes, in the piston, an accommodation chamber that accommodates the linear motion member movably in the first direction and the second direction, and a first protrusion or A first concave portion, and the translation member is provided with a second pressing portion that presses the piston in the second direction, and a second concave portion or a second convex portion, A first surface facing the circumferential direction of the rotation axis of the rotating member in the first convex portion or the first concave portion, and a second surface facing the circumferential direction in the second concave portion or the second convex portion. A rotation limiting mechanism that limits rotation of the linear motion member about the rotation axis by contact with the surface, wherein the second pressing portion is the second concave portion or the second convex portion. Provided in the department. Therefore, since the second pressing portion is provided in the second concave portion or the second convex portion, when the second pressing portion is provided in a portion other than the second concave portion or the second convex portion. In comparison, the configuration of the vehicular electric brake device is easily simplified.

  Further, in the electric brake device for a vehicle, the linear moving member includes a first pressing portion that presses the piston in the first direction, and a second pressing portion that presses the piston in the second direction. Having a first receiving portion pressed from the first pressing portion in the first direction, and a second receiving portion pressed from the second pressing portion in the second direction. And, a first distance in the first direction between the first pressing portion and the first receiving portion, and the second pressing portion and the second receiving portion The first total value of the second distance in the first direction and the second distance in the first direction constitutes the movement distance of the piston in the second direction due to the decrease in the pressure of the hydraulic chamber and the brake pad. It is larger than the second sum of the initial thickness of the friction material and the friction material. Therefore, even when the friction material is worn, the piston moves in the cylinder in the first direction by the action of the pressure of the hydraulic chamber, pushes the brake pad, and moves in the first direction. To push the brake pad, and pushed by the linear motion member moving in the second direction to move in the second direction to increase the pressure in the hydraulic chamber.

FIG. 1 is a schematic and exemplary perspective view showing an electric brake device for a vehicle according to an embodiment. FIG. 2 is a schematic and illustrative cross-sectional view showing the caliper in the traveling mode of the electric brake device for a vehicle according to the embodiment, and is a diagram showing a cross-section of the caliper along the axial direction of the rotating shaft of the disk rotor. . FIG. 3 is a schematic and exemplary diagram showing a part of a cross section taken along line III-III of FIG. FIG. 4 is a schematic and exemplary cross-sectional view showing the caliper of the electric brake device for a vehicle in the parking mode in the embodiment, and is a view corresponding to FIG. 2. FIG. 5 is a schematic and exemplary sectional view showing the caliper of the electric brake device for a vehicle in the air release mode in the embodiment, and is a view corresponding to FIG. 2. FIG. 6 is a schematic and exemplary sectional view showing the caliper of the electric brake device for a vehicle in the traveling mode in the embodiment, and is a diagram corresponding to FIG. 2 and showing a state in which the brake pad is worn.

  Hereinafter, exemplary embodiments of the present invention will be disclosed. A configuration of the embodiment described below, and an operation and a result (effect) provided by the configuration are examples. The present invention can be implemented by configurations other than those disclosed in the following embodiments. Further, according to the present invention, at least one of various effects (including derivative effects) obtained by the configuration can be obtained.

  As shown in FIGS. 1 and 2, a vehicle electric brake device 1 according to the present embodiment includes a disk rotor 2 that is assembled to an axle hub (not shown) and rotates integrally with wheels (not shown). And a caliper 3 that is disposed across the periphery of the disk rotor 2. Hereinafter, the axial direction of the rotation center axis of the disk rotor 2 is also referred to as a rotor axial direction, the radial direction of the disk rotor 2 is also referred to as a rotor radial direction, and the circumferential direction of the disk rotor 2 is also referred to as a rotor circumferential direction. The rotor circumferential direction intersects the rotor axial direction and the rotor radial direction.

  The vehicle electric brake device 1 has a plurality of modes including a running mode, a parking mode, and an air release mode. The mode is switched by an operation unit (not shown). In the traveling mode, the vehicular electric brake device 1 generates a braking force by pressing the pair of brake pads 13A, 13B (FIG. 2) of the caliper 3 against the disk rotor 2 by the hydraulic pressure of the brake fluid. In the parking mode, the vehicle electric brake device 1 generates a braking force by pressing the pair of brake pads 13A and 13B against the disk rotor 2 by the driving force of the motor 21. The air release mode will be described later.

  As shown in FIGS. 1 and 2, the caliper 3 includes a mounting 11 fixed to a support member provided on the vehicle body, a housing 12 supported by the mounting 11 so as to be movable in the rotor axial direction, and a caliper 3 in the rotor axial direction. The vehicle includes a pair of brake pads 13A and 13B movably supported by the mounting 11, a piston 15 movably supported in the axial direction of the rotor by a housing 12, and a moving mechanism 16 supported by the housing 12. .

  As shown in FIG. 1, the housing 12 is attached to the mounting 11 by a pair of slide pins 14 so as to be movable in the rotor axial direction. The housing 12 extends from the vehicle body side so as to straddle the disk rotor 2 in the rotor axial direction. As shown in FIGS. 1 and 2, the housing 12 has a cylinder 12a and a pair of claws 12b. Housing 12 may also be referred to as a body.

  The cylinder 12a is arranged on one side (the right side in FIG. 2) of the disk rotor 2 in the rotor axis direction. The cylinder 12a is arranged at a distance from the disk rotor 2 in the rotor axis direction. The cylinder 12a has a cylindrical surface 12c and an end surface 12d. The cylindrical surface 12c is formed in a cylindrical shape centered on the central axis Ax. The central axis Ax extends along the rotor axis direction. The end surface 12d is connected to one end of the cylindrical surface 12c in the rotor axial direction, and closes an opening at the end. The cylindrical surface 12c can also be referred to as an inner peripheral surface.

  The pawl 12b is disposed on the other side (left side in FIG. 2) of the disk rotor 2 in the rotor axis direction. The pair of claws 12b are arranged at intervals on the disk rotor 2 in the rotor axis direction.

  As shown in FIG. 2, the piston 15 is arranged on one side of the disk rotor 2 in the rotor axis direction, and is arranged at an interval from the disk rotor 2 in the rotor axis direction. The piston 15 is accommodated in the cylinder 12a so as to be movable in a first direction X1 and a second direction X2 opposite to the first direction X1. The first direction X1 and the second direction X2 are along the central axis Ax. The piston 15 moves toward the disk rotor 2 (in the first direction X <b> 1) by hydraulic pressure, and presses the brake pad 13 </ b> A interposed between the piston 15 and the disk rotor 2. The housing 12 moves in the second direction X2 due to the pressing reaction force, and the claw 12b of the housing 12 presses the brake pad 13B interposed between the disk rotor 2 and the claw 12b toward the disk rotor 2. That is, the pair of brake pads 13A and 13B are pressed against the disk rotor 2 by the piston 15 and the claw 12b, which are pressing members, respectively.

  A gap (not shown) is provided between the outer peripheral surface 15h of the piston 15 and the cylindrical surface 12c of the cylinder 12a. An annular seal member 20 is interposed between the outer peripheral surface 15h of the piston 15 and the cylindrical surface 12c of the cylinder 12a. The seal member 20 is made of rubber or the like, and is elastically deformable. The seal member 20 is placed in a concave portion 12f provided on the cylindrical surface 12c of the cylinder 12a. The seal member 20 restricts rotation of the piston 15 around the central axis Ax by a frictional force.

  In addition, a concave portion 15j that is concave in the second direction X2 is provided on an end surface of the piston 15 in the first direction X1. The convex portion 19a provided on the back plate 19 of the brake pad 13A is inserted into the concave portion 15j. The protrusion 19a protrudes from the end face of the back plate 19 in the second direction X2 toward the piston 15. The engagement between the concave portion 15j and the convex portion 19a restricts the rotation of the piston 15 around the central axis Ax. That is, in the present embodiment, the rotation of the piston 15 around the central axis Ax is limited by the engagement between the concave portion 15j and the convex portion 19a in addition to the frictional force of the seal member 20. Note that the concave portion 15j and the convex portion 19a are not essential and may not be provided.

  The piston 15 is provided with a storage chamber 15a. The storage chamber 15a is formed in a concave shape extending in the first direction X1 from the end surface of the piston 15 in the second direction X2 (end surface 12d side). An end of the accommodation room 15a in the second direction X2 is open. That is, the piston 15 is formed in a cylindrical shape in which an end in the first direction X1 is closed and an end in the second direction X2 is open. As shown in FIG. 3, a plurality of recesses 15d (first recesses) are provided on the inner peripheral surface 15f of the piston 15. The plurality of recesses 15d are arranged at intervals in the circumferential direction of the central axis Ax. Each recess 15d extends along the first direction X1. Each recess 15d is provided with a pair of surfaces 15e spaced from each other in the circumferential direction of the central axis Ax. The surface 15e faces in the circumferential direction of the central axis Ax. A receiving portion 15b is provided at an end of the inner peripheral surface 15f of the piston 15 in the first direction X1. The receiving portion 15b is formed in a ring shape centered on the central axis Ax, and is formed in a surface shape (conical surface shape) whose diameter decreases in the first direction X1. A projection 15g is provided at an end of the piston 15 in the second direction X2. The convex portion 15g is provided on the inner peripheral surface 15f of the piston 15 in a convex shape toward the central axis Ax. The projection 15g is formed in an annular shape around the central axis Ax. The receiving part 15c is provided in the convex part 15g. The receiving portion 15c faces in the first direction X1 and is configured as an annular surface centered on the central axis Ax. The surface 15e is an example of a first surface, the receiving portion 15b is an example of a first receiving portion, and the receiving portion 15c is an example of a second receiving portion.

  A hydraulic chamber 17 is formed between the accommodation chamber 15a of the piston 15 inside the cylinder 12a and the end face 12d of the cylinder 12a. The hydraulic chamber 17 includes a storage chamber 15a. The hydraulic chamber 17 communicates with a brake fluid passage (not shown) provided in the housing 12, and brake fluid such as oil flows into and out of the hydraulic chamber 17 through the brake fluid passage.

  As shown in FIG. 2, the brake pad 13A is disposed between the disk rotor 2 and the piston 15, and the brake pad 13B is disposed between the disk rotor 2 and the pawl 12b. Each of the brake pads 13A and 13B has a friction material 18 facing the disk rotor 2 and a back plate 19 disposed on the side of the friction material 18 opposite to the disk rotor 2. The friction material 18 and the back plate 19 are overlapped with each other in the rotor axial direction and fixed to each other. The friction material 18 contacts the disk rotor 2 to generate a frictional force.

  The moving mechanism 16 includes a motor 21, a speed reduction mechanism 22, and a motion conversion mechanism 23. The motor 21, the speed reduction mechanism 22, and the motion conversion mechanism 23 are mounted on the housing 12 and supported by the housing 12. The motor 21, the speed reduction mechanism 22, and the motion conversion mechanism 23 move integrally with the housing 12 in the rotor axial direction. The motor 21 generates a driving force (rotational force) when energized. The driving force of the motor 21 is reduced by the reduction mechanism 22 and transmitted to the motion conversion mechanism 23. The motor 21 is controlled by a control unit (not shown).

  The motion conversion mechanism 23 has a rotating member 24 and a linear moving member 25. The motion conversion mechanism 23 converts the rotation of the rotating member 24 by the motor 21 into the linear motion of the linear member 25.

  The rotating member 24 extends along the central axis Ax in a state where a part thereof is disposed in the cylinder 12a. The rotating member 24 is supported by the housing 12 so as to be rotatable around the central axis Ax while being inserted into a through hole 12g that penetrates through the end face 12d of the housing 12. The rotating member 24 has a male screw part 24a and a flange part 24b. The external thread portion 24a is disposed inside the cylinder 12a. Further, at least a part of the male screw portion 24a is arranged in the housing chamber 15a of the piston 15. The flange portion 24b overlaps the end surface 12d of the cylinder 12a. A retaining ring 27 (clip) is fitted to a portion of the rotating member 24 protruding from the housing 12 to prevent the rotating member 24 from coming off from the housing 12. The contact between the retaining ring 27 and the flange portion 24b with the housing 12 restricts the movement of the rotating member 24 in the first direction X1 and the second direction X2. The rotating member 24 is connected to the reduction mechanism 22 outside the housing 12, and rotates around the central axis Ax by the driving force of the motor 21 transmitted via the reduction mechanism 22. The flange portion 24b and the retaining ring 27 can also be referred to as a movement restricting portion.

  The translation member 25 is accommodated in the accommodation chamber 15a of the piston 15 so as to be movable in the first direction X1 and the second direction X2. The translation member 25 is formed in a substantially cylindrical shape (annular shape) centered on the central axis Ax. A female screw portion 25 a is provided on the inner peripheral surface of the linear motion member 25. The female screw portion 25a is connected to the male screw portion 24a of the rotating member 24. Further, as shown in FIG. 3, a plurality of convex portions 25 b protruding in the radial direction of the central axis Ax are provided on the outer peripheral surface 25 f of the linear motion member 25. The plurality of convex portions 25b are arranged at intervals in the circumferential direction of the central axis Ax. The protrusion 25b extends along the first direction X1. A pair of surfaces 25c is provided on both sides of the protrusion 25b in the circumferential direction of the central axis Ax. The surface 25c faces in the circumferential direction of the central axis Ax. The protrusion 25b is inserted into the recess 15d of the piston 15. The surface 25c of the convex portion 25b faces the surface 15e of the concave portion 15d in the circumferential direction of the central axis Ax. The contact between the surface 25c and the surface 15e limits the rotation of the linear motion member 25 about the central axis Ax which is the rotation axis of the rotation member 24. The surface 25c and the surface 15e constitute a rotation limiting mechanism 26. The protrusion 25b is an example of a second protrusion, and the surface 25c is an example of a second surface. The translation member 25 can also be called a nut member.

  When the rotation member 24 rotates in a state where the rotation of the translation member 25 is restricted by the rotation restricting mechanism 26, the rotation of the rotation member 24 by the motor 21 causes the translation of the translation member 25 by the male screw portion 24 a and the female screw portion 25 a. Is converted. When the motor 21 (rotating member 24) rotates in one direction (forward direction), the translation member 25 is moved in the first direction X1, and the motor 21 (rotating member 24) moves in the opposite direction (reverse direction). ), The translation member 25 is moved in the second direction X2.

  Further, as shown in FIG. 2, the linear motion member 25 is provided with a pressing portion 25d and a pressing portion 25e. The pressing portion 25d is provided at an end of the linear motion member 25 in the first direction X1. The pressing portion 25d is formed in an annular surface shape centered on the central axis Ax, and is formed in a surface shape (conical surface shape) whose diameter decreases in the first direction X1. The pushing portion 25e faces the receiving portion 15b of the piston 15, and pushes the receiving portion 15b (piston 15) in the first direction X1. Further, the pressing portion 25e is provided on the outer peripheral portion of the linear motion member 25, and is formed in an annular planar shape facing the second direction X2. The pushing part 25e faces the receiving part 15c of the piston 15, and pushes the receiving part 15c (piston 15) in the second direction X2.

  In the above configuration, in the traveling mode, when the brake pedal (not shown) is pressed from the state where the piston 15 is located at the non-braking position (initial position, FIG. 2), the pressure in the hydraulic pressure chamber 17 increases. Then, the piston 15 moves in the cylinder 12a in the first direction X1 by the action of the pressure of the hydraulic chamber 17 and presses the brake pad 13A. As a result, the brake pads 13A and 13B sandwich the disk rotor 2, and a braking force is applied to the disk rotor 2. At this time, the seal member 20 is elastically deformed by the frictional force with the piston 15. When the pushing operation of the brake pedal is released, the pressure in the hydraulic chamber 17 is reduced, and the piston 15 moves in the cylinder 12a in the second direction X2 due to the restoring force of the seal member 20, and moves to the non-braking position. (FIG. 2). As a result, the piston 15 does not press the brake pad 13A. In this traveling mode, the receiving portions 15b and 15c of the piston 15 and the pushing portions 25d and 25e of the linear motion member 25 are separated from each other. Therefore, in the traveling mode, the linear motion member 25 does not hinder the movement of the piston 15.

  Further, for example, when the driving mode is changed from the traveling mode to the parking mode, the rotation member 24 rotates in one direction by rotating the motor 21 in one direction, and the linear motion member 25 moves in the first direction X1. Moving. In the course of this movement, the pushing part 25d of the linear member 25 comes into contact with the receiving part 15b of the piston 15, and the piston 15 is pushed by the linear member 25 moving in the first direction X1 and pushes the brake pad 13A ( (Fig. 4). As a result, the brake pads 13A and 13B sandwich the disk rotor 2, and a braking force is applied to the disk rotor 2. At this time, the seal member 20 is elastically deformed by the frictional force with the piston 15. At this time, the pressing portion 25d presses the receiving portion 15b to adjust the position of the central axis Ax of the piston 15 in the radial direction. When the movement of the brake pad 13A, the piston 15, and the translation member 25 in the first direction X1 is restricted by the disk rotor 2, the load (power consumption) of the motor 21 increases. When the power consumption of the motor 21 reaches the specified amount, the rotation of the motor 21 stops. Further, when the mode is changed from the parking mode to the traveling mode, the rotation of the motor 21 by the predetermined amount in the other direction causes the rotation member 24 to rotate by the predetermined amount in the other direction, and the linear motion member 25 to move in the second direction. It moves to X2 and returns to the non-braking position (initial position, FIG. 2). At this time, the piston 15 moves in the second direction X1 in the cylinder 12a by the restoring force of the seal member 20, and returns to the non-braking position (FIG. 2).

  Further, for example, when the air release of the brake fluid (brake fluid exchange) is performed, the parking mode is changed to the air release mode. At the time of bleeding the brake fluid (replacement of the brake fluid), as an example, the brake fluid mixed with air while the plug of the bleeder portion (not shown) provided in the above-described brake fluid passage of the housing 12 is loosened. Is discharged, and new brake fluid is filled. In the air release mode, when the motor 21 rotates in the other direction, the rotating member 24 rotates in the other direction, and the translation member 25 moves in the second direction X2. In the course of this movement, the pushing part 25e of the linear member 25 comes into contact with the receiving part 15c of the piston 15, and the piston 15 is pushed by the linear member 25 moving in the second direction X2 and moves in the second direction X2. It moves to increase the pressure in the hydraulic chamber 17 (FIG. 5). At this time, as an example, the piston 15 and the linear moving member 25 are positioned such that the protrusion 15g of the piston 15 and the end of the linear moving member 25 in the second direction abut on the flange portion 24b of the rotating member 24 (the last retreat position). ). When the mode is changed from the air release mode to the parking mode, the rotation member 24 rotates in one direction by rotating the motor 21 in one direction, and the linear motion member 25 moves in the first direction X1. In the course of this movement, the pushing part 25d of the linear member 25 comes into contact with the receiving part 15b of the piston 15, and the piston 15 is pushed by the linear member 25 moving in the first direction X1 and pushes the brake pad 13A ( (Fig. 4). As a result, the brake pads 13A and 13B sandwich the disk rotor 2, and a braking force is applied to the disk rotor 2. In this air release mode, when increasing the pressure in the hydraulic pressure chamber 17, in order to efficiently release air from the hydraulic pressure chamber 17, a brake hydraulic pressure path connecting the master cylinder (not shown) and the vehicle electric brake device 1 is provided. By using a valve mechanism (not shown) provided in the middle, pressure leakage of the hydraulic chamber 17 to the master cylinder side is suppressed. Examples of the above-mentioned valve mechanism include a hydraulic control device such as an ABS and an ESC, and a shutoff unit such as a hose plier.

  In the air bleeding mode, when the pressure in the hydraulic chamber 17 increases due to the movement of the piston 15 in the second direction X2, the axial reaction force applied to the piston 15 and thus the linear motion member 25 increases, so that the rotation member 24 directly moves. The force transmitted to the moving member 25 around the central axis Ax tends to increase. On the other hand, in the present embodiment, the rotation of the piston 15 around the central axis Ax is restricted by the engagement between the concave portion 15j and the convex portion 19a in addition to the frictional force of the seal member 20, so that the piston 15 The rotation stop around the central axis Ax can be more reliably performed.

  Further, in the present embodiment, a first distance D1 (FIG. 2) in the first direction X1 between the pressing portion 25d (first pressing portion) and the receiving portion 15b (first receiving portion) is determined. The first total value of the second distance D2 (FIG. 2) in the first direction X1 between the portion 25e (second pressing portion) and the receiving portion 15c (second receiving portion) is equal to the liquid It is larger than the second sum of the moving distance D3 of the piston 15 in the second direction X2 due to the decrease in the pressure of the pressure chamber 17 and the initial thickness D4 of the friction material 18. Here, the line L1 in FIG. 2 indicates the position of the end face of the piston 15 in the first direction X1 when the piston 15 is braked (when the hydraulic pressure is increased).

  As described above, in the present embodiment, the piston 15 can move in the cylinder 12a in the first direction X1 by the action of the pressure of the hydraulic chamber 17 to press the brake pad 13A, and Is pushed by the linear moving member 25 moving in the direction X1, and the brake pad 13A can be pressed. The hydraulic pressure is moved by the linear moving member 25 moving in the second direction X2 to move in the second direction X2. The pressure in the chamber 17 is increased. Therefore, for example, in the air bleeding operation of the vehicular electric brake device 1, the piston 15 is pushed by the translation member 25 moving in the second direction X <b> 2 and moves in the second direction X <b> 2, and the pressure in the hydraulic pressure chamber 17 is increased. , The operator does not need to depress the brake pedal to increase the pressure in the hydraulic chamber 17. Therefore, for example, the number of workers required for the air bleeding operation can be reduced, so that the air bleeding operation (brake fluid replacement operation) is easily performed. At this time, for example, the brake fluid passage and the brake including the fluid pressure chamber 17 need not be driven without driving a fluid pressure source such as a master cylinder that controls the fluid pressure in the fluid pressure chamber 17 or a pump of the fluid pressure control valve block. The hydraulic pressure in the hydraulic system can be increased. Further, in the present embodiment, the air is evacuated while moving the linear member 25 and the rotating member 24, so that the air is less likely to remain between the linear member 25 and the rotating member 24, and the air bleeding is more reliable. Can be done.

  In the present embodiment, as an example, the piston 15 has, as an example, an accommodation chamber 15a that accommodates the translation member 25 movably in the first direction X1 and the second direction X2, and a recess 15d (first recess). The linear motion member 25 is provided with a pressing portion 25e (second pressing portion) for pressing the piston 15 in the second direction X2 and a convex portion 25b (second convex portion). ing. The rotation restricting mechanism 26 includes a surface 15e (first surface) facing the circumferential direction in the concave portion 15d, a surface 25c (second surface) facing the circumferential direction in the convex portion 25b (second convex portion), , Restricts rotation of the translation member 25 around the central axis Ax (rotation axis) of the rotation member 24. And the pushing part 25e is provided only in the convex part 25b. As described above, since the pressing portion 25e is provided only on the convex portion 25b, for example, unlike the case where the pressing portion 25e is provided other than the convex portion 25b over the entire area in the circumferential direction of the linear motion member 25, the convex portion 25e is provided. As for the portions other than the portion 25b, it is not necessary to consider the shape and dimensional accuracy required for the contact of the piston 15 with the receiving portion 15c, so that the configuration of the vehicle electric brake device 1 is easily simplified.

  In the present embodiment, the linear motion member 25 includes a pressing portion 25d (first pressing portion) that presses the piston 15 in the first direction X1 and a pressing portion 25e (first pressing portion) that presses the piston 15 in the second direction X2. The piston 15 has a receiving portion 15b (first receiving portion) pressed from the pressing portion 25d (first pressing portion) in the first direction X1, and a second direction. X2 has a receiving portion 15c (second receiving portion) pressed from the pressing portion 25d (second pressing portion). Then, a first distance D1 in the first direction X1 between the pressing portion 25d and the receiving portion 15b, and a distance between the pressing portion 25e (second pressing portion) and the receiving portion 15c (second receiving portion). The first total value of the second distance D2 in the first direction X1 and the movement distance D3 of the piston 15 in the second direction X2 due to the decrease in the pressure of the hydraulic chamber 17 and the brake pad 13A It is larger than the second total value of the friction material 18 and the initial thickness D4. Therefore, even if the friction material 18 of the brake pad 13A shown in FIG. 6 is in a worn state, the piston 15 moves in the cylinder 12a in the first direction X1 by the action of the pressure of the hydraulic pressure chamber 17 to apply the brake. The pad 13A is pushed, pushed by the linear motion member 25 moving in the first direction X1, and pushed by the brake pad 13A, and pushed by the linear motion member 25 moved in the second direction X2, and moved in the second direction X2. Thus, the pressure in the hydraulic chamber 17 can be increased. In FIG. 6, the initial position of the direct acting member 25 when the brake pads 13A and 13B are new (FIG. 2) is indicated by a chain line.

  Note that the piston 15 is provided with a first convex portion instead of the concave portion 15d (first concave portion), and the linear motion member 25 is provided with a second convex portion instead of the convex portion 25b (second convex portion). A concave portion may be provided. In this case, the rotation restricting mechanism 26 includes a surface (first surface) facing the circumferential direction of the central axis Ax in the first convex portion and a surface (second surface) facing the circumferential direction of the central axis Ax in the second concave portion. The rotation of the translation member 25 around the central axis Ax of the rotation member 24 due to the contact between the rotation member 24 and the rotation member 24 is restricted.

  Hereinafter, a procedure of an air bleeding operation performed after replacement of the brake pads 13A and 13B will be described. First, the worker checks the remaining amount of the brake fluid in the reservoir tank attached to the master cylinder, and if the remaining amount is small, replenishes the reservoir tank with the brake fluid. Next, the operator shuts off the brake fluid passage between the master cylinder and the vehicle electric brake device 1 by the above-described valve mechanism or the like. Next, the operator sets the brake fluid collection container on the bleeder unit. Next, the worker performs the air release in the above-described air release mode. Next, the operator removes the brake fluid collection container of the bleeder section. Next, the operator replenishes the reservoir tank with the brake fluid to complete the air bleeding operation.

  As described above, the embodiment of the present invention has been exemplified, but the above embodiment is merely an example, and is not intended to limit the scope of the invention. The above embodiments can be implemented in other various forms, and various omissions, replacements, combinations, and changes can be made without departing from the spirit of the invention. In addition, the specifications (structure, type, direction, shape, size, length, width, thickness, height, number, arrangement, position, material, etc.) of each configuration, shape, etc. may be changed as appropriate. Can be implemented.

  DESCRIPTION OF SYMBOLS 1 ... Electric brake device for vehicles, 13A, 13B ... Brake pad, 15 ... Piston, 15a ... Housing chamber, 15b ... Receiving part (first receiving part), 15c ... Receiving part (second receiving part), 15d ... Recess (first recess), 15e surface (first surface), 16 moving mechanism, 17 hydraulic chamber, 18 friction material, 21 motor, 23 motion conversion mechanism, 24 rotating member, 25 ... Linear motion member, 25b... Convex portion (second convex portion), 25c... Surface (second surface), 25d... Pressing portion (first pressing portion), 25e... Pressing portion (second pressing portion) , 26: rotation limiting mechanism, D1: first distance, D2: second distance, D3: moving distance, D4: initial thickness, X1: first direction, X2: second direction, Ax: central axis (Axis of rotation).

Claims (2)

Motor and
A motion converting mechanism having a rotating member and a linear moving member, and converting the rotation of the rotating member by the motor into a linear motion of the linear moving member;
A housing provided with a cylinder and a hydraulic chamber,
The cylinder is movably accommodated in a first direction and a second direction opposite to the first direction, and moves in the cylinder in the first direction by the action of the pressure of the hydraulic chamber. And the brake pad can be pressed, and the brake pad can be pressed by being pushed by the translation member moving in the first direction, and pushed by the translation member moving in the second direction. A piston that moves in the second direction to increase the pressure of the hydraulic chamber,
Bei to give a,
The piston is provided with an accommodation chamber that accommodates the translation member movably in the first direction and the second direction, and a first convex portion or a first concave portion,
The linear member is provided with a second pressing portion that presses the piston in the second direction, and a second concave portion or a second convex portion,
A first surface facing the circumferential direction of the rotation axis of the rotating member in the first convex portion or the first concave portion, and a second surface facing the circumferential direction in the second concave portion or the second convex portion. A rotation limiting mechanism that limits rotation of the linear motion member around the rotation axis by contact with the surface,
The electric brake device for a vehicle , wherein the second pressing portion is provided in the second concave portion or the second convex portion . Motor and
A motion converting mechanism having a rotating member and a linear moving member, and converting the rotation of the rotating member by the motor into a linear motion of the linear moving member;
A housing provided with a cylinder and a hydraulic chamber,
The cylinder is movably accommodated in a first direction and a second direction opposite to the first direction, and moves in the cylinder in the first direction by the action of the pressure of the hydraulic chamber. And the brake pad can be pressed, and the brake pad can be pressed by being pushed by the translation member moving in the first direction, and pushed by the translation member moving in the second direction. A piston that moves in the second direction to increase the pressure of the hydraulic chamber,
With
The translation member has a first pusher that pushes the piston in the first direction, and a second pusher that pushes the piston in the second direction,
The piston has a first receiving part pressed from the first pressing part in the first direction, and a second receiving part pressed from the second pressing part in the second direction. And
A first distance in the first direction between the first pressing portion and the first receiving portion, and a first distance between the second pressing portion and the second receiving portion. The first total value of the second distance in the direction and the movement distance of the piston in the second direction due to the decrease in the pressure of the hydraulic chamber and the initial thickness of the friction material constituting the brake pad Satono greater than the second sum, car dual electric braking apparatus.

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