WO2019189654A1

WO2019189654A1 - Brake device

Info

Publication number: WO2019189654A1
Application number: PCT/JP2019/013782
Authority: WO
Inventors: 陽平小溝; 健一明城
Original assignee: 株式会社アドヴィックス
Priority date: 2018-03-29
Filing date: 2019-03-28
Publication date: 2019-10-03
Also published as: JP2019173952A

Abstract

A motion conversion mechanism of this brake device includes a rotation member, and a linear motion member which moves linearly with rotation of the rotation member. The rotation member is driven to rotate through a third gear. A male screw and a female screw mesh on the side of the third gear opposite of a brake shoe. One end of an actuating member receives a force for actuating the brake shoe from the linear motion member, and the other end actuates the brake shoe. The actuating member has a rod-shape member that extends inside of a through-hole.

Description

Brake device

The present invention relates to a brake device.

2. Description of the Related Art Conventionally, a motion conversion mechanism having a rotating member that rotates in conjunction with an output shaft of a motor and a linear motion member that moves linearly according to the rotation of the rotational member is provided, and a cable is pulled by the linear motion member. A brake device that moves and brakes a brake shoe is known (for example, Patent Document 1 and Patent Document 2). In Patent Document 1, a linear motion member having a male screw is linearly moved according to the rotation of a rotating member having a female screw. In Patent Literature 2, a member that transmits the rotation of the output shaft of the motor is connected to the shaft end surface of the rotating member that is far from the brake shoe.

Special table 2014-504711 gazette Germany DE102007002907A1

In a brake device in which a linear motion member having a male screw moves linearly according to the rotation of a rotary member having a female screw as in Patent Document 1, the diameter of a bearing that supports the rotary member is likely to increase. In some cases, the apparatus was enlarged.

Further, in a brake device in which a motor output shaft or a member that rotates in conjunction with the output shaft is connected to an axial end surface of a rotation member of a motion conversion mechanism, as in Patent Document 2, the brake device is axially In some cases, the size was increased.

Therefore, one of the problems of the present invention is to obtain a brake device having a novel configuration with less inconvenience, for example, it becomes possible to further reduce the size.

The brake device of the present invention includes, for example, a braking member that brakes the drum rotor by being pressed by a drum rotor that rotates integrally with a wheel, a backing plate that supports the braking member, and the backing plate that is provided on the backing plate. An electric actuator for operating a braking member, wherein the electric actuator includes a motor having a rotating output shaft, a male screw, and an axis around the male screw in conjunction with the output shaft. A motion converting mechanism including a rotating member that rotates in rotation, a linearly moving member that has a female screw that meshes with the male screw, and that moves linearly as the rotating member rotates, and a force that operates the braking member from the linearly moving member An operating member that receives the rotation member, and the rotating member is provided on an outer periphery of the rotating member and rotates in conjunction with the output shaft. The male screw and the female screw mesh with each other on the opposite side of the driven member from the braking member, and one end of the actuating member extends from the linear motion member to the braking member. The other end is configured to operate the braking member, and the rotating member is provided with a through hole along the axial direction of the shaft center,
The one end of the actuating member is located on the opposite side of the through hole from the braking member, and the actuating member has a rod-like member extending in the through hole.

According to such a configuration, for example, a bearing that supports the rotating member as compared to a mode in which the linearly moving member having the male screw linearly moves according to the rotation of the rotating member having the female screw as in Patent Document 1. Since the diameter of the actuator is likely to be smaller, it is possible to reduce the size of the electric actuator in the radial direction, and the smaller the diameter of the bearing, the lower the sliding speed of the bearing at the same rotational speed. There is an advantage that durability such as property is easily improved. Further, for example, compared with an aspect in which an output shaft of a motor or a member that rotates in conjunction with the output shaft is connected to an axial end surface of a rotation member of a motion conversion mechanism as in Patent Document 2, the electric actuator There is an advantage that the total length tends to be shorter. Therefore, there are obtained an advantage that it is easy to secure an in-vehicle space by reducing the size of the electric actuator as described above, and an advantage that durability can be improved. In addition, for example, the driven portion can be disposed closer to the braking member as compared with a mode in which the male screw and the female screw are engaged with each other on the braking member side with respect to the driven portion. Therefore, for example, it is not necessary to provide a relatively large part for housing the driven part of the body or case on the side far from the braking member of the brake device, so that the brake device can be configured more compactly, The advantage that the vibration energy at the time of vibration can be made smaller can be obtained. And, for example, the operating member is arranged in a state of extending linearly near the axis of the rotating member as compared with an aspect in which the operating member is arranged so as to bypass the radially outer side of the driven part. Therefore, it is possible to suppress the reaction force applied to the operation of the braking member from acting in the direction intersecting the axis. Furthermore, since the rod-shaped member has high rigidity and is difficult to bend compared to a flexible member such as a cable, for example, the assembly workability when inserting the operating member into the through hole of the rotating member is improved, or the rotating operation with the operating member is performed. Effects such as wear and torque loss due to contact with the member are suppressed.

FIG. 1 is an exemplary and schematic rear view of the brake device according to the embodiment from the rear of the vehicle. FIG. 2 is an exemplary and schematic side view of the brake device according to the embodiment from the outside in the vehicle width direction. FIG. 3 is an exemplary schematic side view of the operation of the braking member by the moving mechanism of the brake device of the embodiment, and is a diagram in a non-braking state. FIG. 4 is an exemplary and schematic side view of the operation of the braking member by the moving mechanism of the brake device of the embodiment, and is a diagram in a braking state. FIG. 5 is an exemplary schematic cross-sectional view of the electric actuator according to the embodiment and is a diagram in a braking state. FIG. 6 is an exemplary schematic cross-sectional view in which a part of the motion conversion mechanism of FIG. 5 is enlarged, and is a diagram in a braking state. FIG. 7 is an exemplary schematic perspective view of the linear motion member of the embodiment. FIG. 8 is an exemplary schematic perspective view of the rotation stopper member of the embodiment. FIG. 9 is an exemplary schematic cross-sectional view of the cable end of the embodiment. FIG. 10 is an exemplary schematic cross-sectional view enlarging a part of FIG. 9. FIG. 11 is an exemplary schematic cross-sectional view in which a part of the motion conversion mechanism in FIG. 5 is enlarged, and is a view in a non-braking state. FIG. 12 is an exemplary schematic cross-sectional view of a cable end of a first modification. FIG. 13 is an exemplary schematic cross-sectional view of a cable end of a second modified example. FIG. 14 is a cross-sectional view showing the connecting portion in a state where the cable end of FIG. 13 is rotated by 90 ° around the axis. FIG. 15 is an exemplary schematic cross-sectional view of a part of a cable end of a third modification. FIG. 16 is an exemplary schematic cross-sectional view of a part of a cable end of a fourth modified example. FIG. 17 is an exemplary schematic cross-sectional view of a part of a linear motion member and a transmission member according to a fifth modification.

Hereinafter, exemplary embodiments of the present invention will be disclosed. The configurations of the embodiments and modified examples shown below, and the operations and results (effects) brought about by the configurations are examples. The present invention can be realized by configurations other than those disclosed in the following embodiments and modifications. According to the present invention, it is possible to obtain at least one of various effects (including derivative effects) obtained by the configuration.

In the following embodiments and modifications, similar components are included. Therefore, in the following, the same reference numerals are given to the same components, and redundant description may be omitted. Moreover, in this specification, the ordinal number is given for convenience in order to distinguish parts, parts, and the like, and does not indicate priority or order.

Also, in each figure, the direction of the axial direction of the third rotation center Ax3 and the end portion 150a of the cable 150 (one end of the actuating member 200) is separated from the braking member and is in a braking state is indicated by an arrow D1. An arrow D2 indicates an axial direction of the rotation center Ax3 and a direction in which the end 150a approaches the braking member and enters a non-braking state. Hereinafter, unless otherwise stated, the axial direction of the third rotation center Ax3 is simply referred to as the axial direction, the radial direction of the third rotation center Ax3 is simply referred to as the radial direction, and the circumferential direction of the third rotation center Ax3. Is simply referred to as the circumferential direction.

[Embodiment]
[Configuration of brake device]
FIG. 1 is a rear view of a vehicle brake device 2 from the rear of the vehicle. FIG. 2 is a side view of the brake device 2 from the outside in the vehicle width direction. FIG. 3 is a side view showing the operation of the brake shoe 3 (braking member) by the moving mechanism 8 of the brake device 2 and is a view in a non-braking state. FIG. 4 is a side view showing the operation of the brake shoe 3 by the moving mechanism 8 of the brake device 2 and is a diagram in a braking state.

As shown in FIG. 1, the brake device 2 is accommodated inside the peripheral wall 1 a of the cylindrical wheel 1. The brake device 2 is a so-called drum brake. As shown in FIG. 2, the brake device 2 includes two brake shoes 3 that are separated from each other in the front-rear direction. As shown in FIGS. 3 and 4, the two brake shoes 3 extend in an arc shape along the inner peripheral surface 4 a of the cylindrical drum rotor 4. The drum rotor 4 rotates integrally with the wheel 1 around a rotation center C extending in the vehicle width direction (Y direction). The two brake shoes 3 move so as to contact the inner peripheral surface 4 a of the cylindrical drum rotor 4. As a result, the drum rotor 4 and thus the wheel 1 are braked by the friction between the brake shoe 3 and the drum rotor 4. The brake shoe 3 is an example of a braking member.

The brake device 2 includes a wheel cylinder 51 (see FIG. 2) that operates by hydraulic pressure, and a motor 120 that operates by energization as an actuator that moves the brake shoe 3. Each of the wheel cylinder 51 and the motor 120 can move the two brake shoes 3. The wheel cylinder 51 is used, for example, for braking while traveling, and the motor 120 is used, for example, for braking during parking. That is, the brake device 2 is an example of an electric parking brake. The motor 120 may be used for braking during traveling.

The brake device 2 includes a disc-shaped backing plate 6 as shown in FIGS. The backing plate 6 is provided in a posture intersecting with the rotation center C. That is, the backing plate 6 extends substantially along the direction intersecting the rotation center C, specifically, substantially along the direction orthogonal to the rotation center C. As shown in FIG. 1, the components of the brake device 2 are provided on both the outer side and the inner side of the backing plate 6 in the vehicle width direction. The backing plate 6 supports each component of the brake device 2 directly or indirectly. That is, the backing plate 6 is an example of a support member. The backing plate 6 is connected to a connection member (not shown) with the vehicle body. The connection member is, for example, a part of the suspension (for example, an arm, a link, an attachment member, etc.). The opening 6b provided in the backing plate 6 shown in FIG. 2 is used for coupling with the connection member. The brake device 2 can be used for both driving wheels and non-driving wheels. In addition, when the brake device 2 is used for driving wheels, an axle shaft (not shown) passes through an opening 6c provided in the backing plate 6 shown in FIG.

[Brake shoe operation by wheel cylinder]
The wheel cylinder 51, the brake shoe 3 and the like shown in FIG. 2 are disposed outside the backing plate 6 in the vehicle width direction. The brake shoe 3 is movably supported by the backing plate 6. Specifically, as shown in FIG. 3, the lower end portion 3a of the brake shoe 3 is supported by the backing plate 6 (see FIG. 2) so as to be rotatable around the rotation center C11. The rotation center C11 extends substantially parallel to the rotation center C of the wheel 1. As shown in FIG. 2, the wheel cylinder 51 is supported on the upper end portion of the backing plate 6. The wheel cylinder 51 has two movable parts (pistons) (not shown) that can project in the vehicle front-rear direction (left-right direction in FIG. 2). That is, the wheel cylinder 51 causes the two movable parts to protrude in response to the pressurization. The two projecting movable parts push the upper end 3b of the brake shoe 3, respectively. Due to the protrusion of the two movable parts, the two brake shoes 3 rotate around the rotation center C11 (see FIGS. 3 and 4), respectively, so that the upper end parts 3b move away from each other in the vehicle front-rear direction. As a result, the two brake shoes 3 move outward in the radial direction of the rotation center C of the wheel 1. A belt-like lining 31 along the cylindrical surface is provided on the outer periphery of each brake shoe 3. Therefore, as shown in FIG. 4, the lining 31 and the inner peripheral surface 4 a of the drum rotor 4 come into contact with each other by the movement of the two brake shoes 3 radially outward of the rotation center C. The drum rotor 4 and thus the wheel 1 (see FIG. 1) are braked by the friction between the lining 31 and the inner peripheral surface 4a. As shown in FIG. 2, the brake device 2 includes a return member 32. The return member 32 is a position where the two brake shoes 3 come into contact with the inner peripheral surface 4a of the drum rotor 4 when the operation of pushing the brake shoes 3 by the wheel cylinder 51 is released (braking position Psb, see FIG. 4). To a position that does not contact the inner peripheral surface 4a of the drum rotor 4 (non-braking position Psn, initial position, see FIG. 3). The return member 32 is an elastic member such as a coil spring, for example. The return member 32 gives one of the two brake shoes 3 a force in a direction approaching the other brake shoe 3, that is, a force in a direction away from the inner peripheral surface 4 a of the drum rotor 4.

[Configuration of moving mechanism and operation of brake shoe by moving mechanism]
Moreover, the brake device 2 includes a moving mechanism 8 shown in FIGS. The moving mechanism 8 moves the two brake shoes 3 from the non-braking position Psn (FIG. 3) to the braking position Psb (FIG. 4) based on the operation of the electric actuator 100 (see FIG. 5) including the motor 120. The moving mechanism 8 is provided outside the backing plate 6 in the vehicle width direction. The moving mechanism 8 includes a lever 81, a cable 150, and a strut 83. The lever 81 is located between one of the two brake shoes 3, for example, the left brake shoe 3 L in FIGS. 3 and 4 and the backing plate 6. It is provided so as to overlap in the axial direction. The lever 81 is supported by the brake shoe 3L so as to be rotatable around the rotation center C12. The rotation center C12 is located at the end of the brake shoe 3L on the side away from the rotation center C11 (upper side in FIGS. 3 and 4), and is substantially parallel to the rotation center C11. The cable 150 moves the lower end 81a of the lever 81 on the side far from the rotation center C12 in a direction approaching the right brake shoe 3R shown in FIGS. 3 and 4 (see the arrow in FIG. 4). The cable 150 moves substantially along the backing plate 6. The strut 83 is interposed between the lever 81 and the brake shoe 3R different from the brake shoe 3L on which the lever 81 is supported, and stretches between the lever 81 and the other brake shoe 3R. The connection position P1 between the lever 81 and the strut 83 is set between the rotation center C12 and the connection position P2 between the end 150b of the cable 150 (the other end E2 of the operating member 200) and the lever 81. Yes. The end 150b of the cable 150 is an example of the other end E2 of the operating member 200. The operation member 200 will be described later in detail.

In such a moving mechanism 8, when the lever 150 moves toward the brake shoe 3 R by pulling the cable 150 and moving it to the right in FIG. 4 (arrow a), the lever 81 is braked via the strut 83. The shoe 3R is pushed rightward in FIG. 4 (arrow b). Accordingly, the brake shoe 3R rotates around the rotation center C11 from the non-braking position Psn (FIG. 3) (arrow c in FIG. 4), and the braking position Psb (FIG. 4) in contact with the inner peripheral surface 4a of the drum rotor 4. Move to. In this state, the connection position P2 between the cable 150 and the lever 81 corresponds to the power point, the rotation center C12 corresponds to the fulcrum, and the connection position P1 between the lever 81 and the strut 83 corresponds to the action point. Further, when the lever 81 moves to the right in FIG. 4, that is, in the direction in which the strut 83 pushes the brake shoe 3R (arrow b) with the brake shoe 3R in contact with the inner peripheral surface 4a, the strut 83 is stretched. The lever 81 rotates in the direction opposite to the direction in which the lever 81 moves, that is, counterclockwise in FIGS. 3 and 4 with the connection position P1 with the strut 83 as a fulcrum (arrow d). As a result, the brake shoe 3L rotates around the rotation center C11 from the non-braking position Psn (FIG. 3) and moves to the braking position Psb (FIG. 4) in contact with the inner peripheral surface 4a of the drum rotor 4. In this manner, the

brake shoes

3L and 3R are both moved from the non-braking position Psn (FIG. 3) to the braking position Psb (FIG. 4) by the operation of the moving mechanism 8. In the state after the brake shoe 3R comes into contact with the inner peripheral surface 4a of the drum rotor 4, the connection position P1 between the lever 81 and the strut 83 serves as a fulcrum. The amount of movement of the

brake shoes

3L, 3R is very small, for example, 1 mm or less.

[Electric actuator]
As shown in FIG. 1, the electric actuator 100 is fixed to the backing plate 6 in a state of protruding from the inner surface 6 a in the vehicle width direction of the backing plate 6 to the side opposite to the brake shoe 3.

FIG. 5 is an exemplary schematic cross-sectional view of the electric actuator 100 of the embodiment, and is a diagram in a braking state. As described with reference to FIG. 4, the electric actuator 100 pulls the brake shoe 3 (braking member) via the cable 150 (flexible member) and moves the brake shoe 3 from the non-braking position to the braking position. The cable 150 is an example of a flexible member.

As shown in FIG. 5, the electric actuator 100 includes a housing 110, a motor 120, a speed reduction mechanism 130, a motion conversion mechanism 140, and an operation member 200.

The housing 110 supports the motor 120, the speed reduction mechanism 130, and the motion conversion mechanism 140. The housing 110 includes a body 112 (base), a lower case 113, an inner cover 114, and an upper case 115. These are integrated by, for example, a coupling tool (not shown) such as a screw or insert molding. A housing chamber R surrounded by a wall 111 of the housing 110 is provided in the housing 110. The motor 120, the speed reduction mechanism 130, and the motion conversion mechanism 140 are each accommodated in the accommodation chamber R and covered with the wall portion 111. The housing 110 may be referred to as a base, a support member, a casing, or the like. In addition, the structure of the housing 110 is not limited to what was illustrated here.

The body 112 can be made of a metal material such as an aluminum alloy, for example. In this case, the body 112 can be manufactured by die casting, for example. The lower case 113, the inner cover 114, and the upper case 115 can be made of, for example, a synthetic resin material.

The motor 120 is an example of an actuator. For example, the motor 120 includes housing parts such as a stator, a rotor, a coil, and a magnet (not shown) in addition to the output shaft 122. The output shaft 122 protrudes in the direction D2 which is the direction along the first rotation center Ax1 of the motor 120 and to the right of FIG.

The speed reduction mechanism 130 includes a plurality of gears that are rotatably supported by the housing 110. The plurality of gears are, for example, a first gear 131, a second gear 132, and a third gear 133. Deceleration mechanism 130 can be referred to as a rotation transmission mechanism.

The first gear 131 rotates integrally with the output shaft 122 of the motor 120. The first gear 131 can be referred to as a drive gear.

The second gear 132 rotates around the second rotation center Ax2 parallel to the first rotation center Ax1. The second gear 132 includes an input gear 132a and an output gear 132b. The input gear 132a meshes with the first gear 131. The number of teeth of the input gear 132a is larger than the number of teeth of the first gear 131. Therefore, the second gear 132 is decelerated to a lower rotational speed than the first gear 131. The output gear 132b is located closer to the backing plate 6 side (right side in FIG. 5) than the input gear 132a. The second gear 132 can be referred to as an idler gear.

The third gear 133 rotates around the third rotation center Ax3 parallel to the first rotation center Ax1. The third gear 133 meshes with the output gear 132b of the second gear 132. The number of teeth of the third gear 133 is larger than the number of teeth of the output gear 132b. Therefore, the third gear 133 is decelerated to a lower rotational speed than the second gear 132. The third gear 133 can be referred to as a driven gear or a ring gear. The third gear 133 is an example of a driven part. Here, the ring gear is an annular gear, which is an external tooth in this embodiment. Note that the configuration of the speed reduction mechanism 130 is not limited to that illustrated here. The speed reduction mechanism 130 may be a rotation transmission mechanism other than a gear mechanism, such as a rotation transmission mechanism using a belt, a pulley, or the like.

The motion conversion mechanism 140 includes a rotating member 141 and a linearly moving member 142.

FIG. 6 is an enlarged cross-sectional view of a part of the motion conversion mechanism 140 of FIG. 5, and is a diagram in a braking state. As shown in FIG. 6, the rotating member 141 has a peripheral wall 141a and a flange 141b. The shape of the peripheral wall 141a is a cylindrical shape centered on the third rotation center Ax3. A through hole 141c along the axial direction is provided inside the peripheral wall 141a.

The shape of the flange 141b is annular and plate-shaped. The flange 141b projects radially outward from the peripheral wall 141a. A third gear 133 is provided on the outer periphery of the flange 141b.

The peripheral wall 141a has a first extending portion 141a1 extending in the direction D1 from the flange 141b and a second extending portion 141a2 extending in the direction D2 from the flange 141b. The length of the first extension 141a1 is longer than the length of the second extension 141a2.

The external thread 141d is provided in the outer periphery of the 1st extension part 141a1. The center of the male screw 141d in the radial direction is the third rotation center Ax3. The third rotation center Ax3 is an example of an axis.

A radial bearing 161 such as a slide bush or a roller bearing is provided between the outer periphery of the second extending portion 141a2 and the inner peripheral surface of the through hole 112a of the body 112. Further, a thrust bearing 162 such as a roller bearing is provided between the end surface 141b1 in the direction D2 of the flange 141b and the end surface 112b in the direction D1 of the body 112, for example. The rotating member 141 is supported by the body 112 via the radial bearing 161 and the thrust bearing 162 so as to be rotatable around the third rotation center Ax3. The rotating member 141 is rotationally driven by the second gear 132 by the meshing of the second gear 132 and the third gear 133.

The third gear 133 is made of, for example, a synthetic resin material, and the disk 141b2 excluding the third gear 133 of the peripheral wall 141a and the flange 141b can be made of a metal material such as iron or aluminum alloy. In the present embodiment, iron is used as an example. In this case, the rotating member 141 can be configured by insert molding, for example. The rotating member 141 may be integrally formed of a metal material including the third gear 133.

The linear motion member 142 has a side wall 142a and a flange 142b. The side wall 142a is located radially outward with respect to the rotating member 141 and extends in the axial direction. The side wall 142a surrounds the third rotation center Ax3 and the rotation member 141. The end of the rotating member 141 in the direction D1 is located in the through hole 142c. The side wall 142a has a first extension 142a1 extending in the direction D1 from the flange 142b and a second extension 142a2 extending in the direction D2 from the flange 142b. The length of the first extension 142a1 is longer than the length of the second extension 142a2.

A female screw 142d that meshes with the male screw 141d of the rotating member 141 is provided on the inner surface of the through hole 142c. The female screw 142d is provided in a section from the end in the direction D2 of the through hole 142c to the position aligned with the flange 142b in the radial direction, and is not provided in the end in the direction D1 of the through hole 142c. Further, the flange 142b is surrounded by an anti-rotation member 143 extending in the axial direction.

As shown in FIG. 6, the detent member 143 has a side wall 143a. The side wall 143a is located radially outward with respect to the flange 142b and extends in the axial direction. The side wall 143a surrounds the third rotation center Ax3 and the periphery of the rotation member 141, and the shape of the side wall 143a is tubular or cylindrical. The side wall 143a may also be referred to as a peripheral wall.

FIG. 7 is a perspective view of the linear motion member 142 of the embodiment. As shown in FIG. 7, the shape of the side wall 142a of the linear motion member 142 is a cylindrical shape centered on the third rotation center Ax3. The side wall 142a may also be referred to as a peripheral wall. A through hole 142c along the axial direction is provided inside the side wall 142a. The shape of the flange 142b provided in the linear motion member 142 is a hexagonal plate shape. Each of the six outer surfaces 142b1 of the flange 142b has a planar shape extending in the axial direction. The linear motion member 142 can be formed by forging a metal material such as an aluminum alloy, for example.

FIG. 8 is a perspective view of the detent member 143 of the embodiment. As shown in FIG. 8, the anti-rotation member 143 can be configured by press-molding or bending a plate material made of a metal material such as an iron-based material. The side wall 143a is configured in a hexagonal cylindrical shape. Each of the six inner surfaces 143a1 of the side wall 143a is a plane extending in the axial direction.

Also, six protrusions 143b bent in an L shape from the end in the direction D1 of the side wall 143a are provided. The protrusion 143b has a base portion 143b1 extending in the axial direction from the side wall 143a and a bent portion 143b2 bent from the tip of the base portion 143b1 toward the radial center. As shown in FIGS. 6 and 8, the end surface 143b3 in the direction D1 in the bent portion 143b2 is formed in a planar shape. In the present embodiment, the anti-rotation member 143 has six protrusions 143b, but may have two protrusions 143b or may have six or more protrusions 143b.

The anti-rotation member 143 is fixed to the housing 110 such as the body 112 and the upper case 115, for example. As shown in FIG. 6, a minute gap is provided between the outer surface 142b1 of the flange 142b and the inner surface 143a1 of the side wall 143a in a parallel state, and both the outer surface 142b1 and the inner surface 143a1 are circumferential. It extends in the direction that intersects.

Therefore, the rotation of the outer surface 142b1 around the third rotation center Ax3 is limited by the inner surface 143a1, and thereby the rotation of the linear motion member 142 is limited by the rotation preventing member 143. On the other hand, since both the outer surface 142b1 and the inner surface 143a1 extend in the axial direction, the inner surface 143a1 does not become an obstacle to the movement of the outer surface 142b1 in the axial direction. That is, the rotation preventing member 143 can guide the linear motion member 142 along the axial direction while restricting the rotation of the linear motion member 142 around the third rotation center Ax3. The inner surface 143a1 is an example of a guide part.

Next, the operation member 200 will be described.
As shown in FIG. 5, the operating member 200 includes a cable end 210 and a cable 150 (flexible member).

FIG. 9 is a cross-sectional view of the cable end 210 of the embodiment. FIG. 10 is an enlarged cross-sectional view of a part of FIG. As shown in FIG. 9, the cable end 210 includes a transmission member 220, a rod-like member 230, and a connecting portion 240. The transmission member 220, the rod-like member 230, and the connecting portion 240 are configured as an integral part.

The connecting portion 240 is connected to the end portion 150b of the cable 150. Specifically, the connecting portion 240 is a cylindrical body having a diameter larger than that of the rod-shaped member 230, and a columnar concave portion 241 is provided inside the cylindrical body. The recess 241 extends along the third rotation center Ax3, and the inner diameter of the recess 241 is substantially the same as the outer diameter of the rod-shaped member 230. As shown in FIG. 5, after the end portion 150 a of the cable 150 is inserted into the recess 241, the connecting portion 240 is crimped from the outside, so that the cable 150 and the connecting portion 240 are coupled.

As shown in FIG. 9, the rod-shaped member 230 is a columnar member that extends from the connecting portion 240 in the direction D1 to the transmission member 220. As shown in FIGS. 5 and 6, the rod-shaped member 230 extends through the through hole 141c of the rotating member 141 along the axial direction, that is, along the third rotation center Ax3 shown in FIG. The rod-shaped member 230 has a characteristic that it is more rigid and difficult to bend than the cable 150 having the same diameter.

As shown in FIG. 9, a disc-shaped transmission member 220 (one end E 1 of the operating member 200) is provided at the end of the rod-shaped member 230 in the direction D 1. As shown in FIGS. 9 and 10, the rod-shaped member 230 and the transmission member 220 are configured as an integral part. Further, as shown in FIG. 10, the transmission member 220 has a disk shape with the third rotation center Ax3 as an axis. A central portion in the radial direction of the inner side surface 221 facing the direction D2 is integrally coupled to the rod-shaped member 230.

As shown in FIG. 10, the inner side surface 221 has a first plane part 222, a taper part 223, and a second plane part 224. The first flat surface portion 222 extends in an annular shape along the circumferential direction outward in the radial direction on the inner side surface. The first plane portion 222 extends orthogonally to the third rotation center Ax3. As shown in FIG. 10, the tapered portion 223 is inclined toward the center in the radial direction from the first inner peripheral end 222 a which is the inner peripheral end edge of the first flat portion 222. The tapered portion 223 extends so as to intersect with the third rotation center Ax3. Specifically, the taper portion 223 is inclined toward the direction D2 from the first inner peripheral end 222a toward the third rotation center Ax3 (the radial center of the through hole 141c of the rotation member 141). Here, the direction D2 is also a direction approaching the end 150b of the cable 150 (the other end E2 of the operating member 200). The second flat surface portion 224 extends from the second inner peripheral end 223a, which is an inner peripheral end edge of the tapered portion 223, toward the center in the radial direction. The second plane portion 224 extends in an annular shape orthogonal to the third rotation center Ax3. A third inner peripheral end 224 a that is an edge on the inner peripheral side in the second plane portion 224 is an intersection between the inner side surface 221 and the rod-shaped member 230. Moreover, the outer side surface 225 of the transmission member 220 is comprised in the 3rd plane part 226 which is a circular flat surface, as shown in FIG. The transmission member 220 and the linear motion member 142 are not integrated, and are configured to be separated in the axial direction. The transmission member 220 is an example of one end E1 of the operation member 200.

The following is a brief description of the procedure for operating the brake device. FIG. 11 is an enlarged cross-sectional view of a part of the motion conversion mechanism 140 of FIG. 5 and is a diagram in a non-braking state. The rotation of the output shaft 122 of the motor 120 is transmitted to the rotating member 141 via the speed reduction mechanism 130. In the non-braking state shown in FIG. 11, when the rotating member 141 rotates, the external thread 142d of the rotating member 141 meshes with the external thread 142d of the rotating member 141 and the internal thread 143a1 of the rotation preventing member 143, and the outer surface 142b1 of the linearly moving member 142 The linear movement member 142 moves in the direction D1 from the position Pn1 in FIG.

At the position Pn2, the end surface 142e of the linear motion member 142 presses the first flat surface portion 222 provided on the inner surface of the transmission member 220, and pushes the transmission member 220 in the direction D1. Then, the transmission member 220, the rod-shaped member 230, and the cable 150 move in the direction D1, and as shown in FIG. 4, the end portion 150b of the cable 150 moves to the right in FIG. The brake device 2 is braked. In FIG. 11, the movement of the transmission member 220 in the direction D 2 is limited by the first flat surface portion 222 contacting the end surface 143 b 3. In other words, the end surface 143b3 has a function of a stopper of the operating member 200, and the state of FIG.

At the position P2n, when the radial center of the linear motion member 142 is at the same position as the third rotation center Ax3 in the radial direction, the radially outer end 142f of the end surface 142e contacts the first flat surface portion 222 of the transmission member 220. . However, if vibration due to the rotation of the rotating member 141 or vibration generated when the vehicle travels is transmitted to the transmission member 220, the transmission member 220 and the linear motion member 142 may be relatively misaligned. That is, the radial center of the transmission member 220 may be displaced in the radial direction with respect to the third rotation center Ax3, and the tapered portion 223 may come into contact with the end surface 142e. At this time, as described above, the tapered portion 223 is inclined toward the direction D2 toward the third rotation center Ax3, so that the radial center of the transmission member 220 is guided toward the third rotation center Ax3. Move while. As described above, when the transmission member 220 and the linear motion member 142 abut on each other in the axial direction, the taper is a guide mechanism that guides the transmission member 220 and the linear motion member 142 to a position where the relative axial deviation is relatively reduced. A portion 223 is provided on the transmission member 220. The tapered portion 223 is an example of a guide mechanism.

In this configuration, as shown in FIG. 5, the transmission member 220 (one end E 1 of the operating member 200) receives a force for operating the brake shoe 3 (braking member) from the linear motion member 142 and transmits the force to the rod-shaped member 230. . Further, the transmission member 220 is located on the direction D1 side (left side in FIG. 5) with respect to the through hole 141c of the rotating member 141, and the connecting portion 240 is located on the direction D2 side (right side in FIG. 5). positioned. That is, the transmission member 220 is located on the opposite side of the through hole 141c from the braking member. The connecting portion 240 is located on the opposite side of the through hole 141c from the transmission member 220. The transmission member 220 is an example of one end E1 of the operation member 200.

Furthermore, the rod-shaped member 230 of the operating member 200 is positioned in a state extending in the through hole 141c. Here, the actuating member 200 moves in the directions D1 and D2, but the linearly moving member 142 is at the tip position in the direction D1, in other words, the linearly moving member 142 is the most along the axial direction from the rotating member 141. In the state of being separated from each other, the connecting portion 240 is located on the opposite side to the transmission member 220 (one end E1 of the operating member 200) with respect to the through hole 141c. That is, when the operation member 200 moves in the directions D1 and D2, the connecting portion 240 is not positioned in the through hole 141c, and the connecting portion 240 is always positioned outside the through hole 141c.

As described above, in the present embodiment, the brake device 2 includes the brake shoe 3 (braking member) and the electric actuator 100. The electric actuator 100 has a motion conversion mechanism 140 including a motor 120, a rotating member 141 having a male screw 141d, and a linear motion member 142 having a female screw 142d, and an actuating member 200. The rotating member 141 is rotationally driven via a third gear 133 (driven portion), and the male screw 141d and the female screw 142d are engaged with each other on the opposite side of the brake shoe 3 of the third gear 133, and one end of the actuating member 200 is engaged. E1 is configured to receive a force for operating the brake shoe 3 from the linear motion member 142, and the other end E2 is configured to operate the brake shoe 3. The rotating member 141 is provided with a through hole 141c along the axial direction, one end E1 of the operating member 200 is located on the opposite side of the through hole 141c from the brake shoe 3, and the operating member 200 is located in the through hole 141c. It has the rod-shaped member 230 extended by.

According to such a configuration, for example, the rotating member 141 is supported as compared with a mode in which the linearly moving member having the male screw linearly moves according to the rotation of the rotating member having the female screw as in Patent Document 1. Since the diameter of the bearing tends to be small, the electric actuator 100 can be made smaller in the radial direction, and the bearing sliding speed at the same rotational speed becomes lower due to the smaller diameter of the bearing. There is an advantage that durability such as wear resistance is easily improved. Further, for example, the electric actuator 100 is compared with an aspect in which a motor output shaft or a member that rotates in conjunction with the output shaft is connected to an axial end surface of the rotation member of the motion conversion mechanism as in Patent Document 2. There is an advantage that the total length of the is easily shortened. Therefore, there are obtained an advantage that it is easy to secure an in-vehicle space by reducing the size of the electric actuator 100 as described above, and an advantage that durability can be improved. Further, for example, the third gear 133 is made more of the brake shoe 3 than the aspect in which the male screw 141d and the female screw 142d are engaged with each other on the brake shoe 3 side (braking member side) with respect to the third gear 133 (driven portion). Can be placed nearby. Therefore, for example, since it is not necessary to provide a relatively large portion for housing the third gear 133 of the body 112 on the side far from the brake shoe 3 of the brake device 2, the brake device 2 can be configured more compactly, There is an advantage that the vibration energy when the brake device 2 vibrates can be further reduced. And, for example, compared with the mode in which the operating member 200 is arranged so as to bypass the radially outer side of the third gear 133, the operating member 200 is more linearly extended near the axis of the rotating member. Since it can arrange | position, it can suppress that the reaction force concerning the action | operation of the brake shoe 3 acts in the direction which cross | intersects an axial center. Furthermore, since the rod-shaped member 230 has a high rigidity and is difficult to bend as compared with a flexible member such as a cable, for example, the assembly workability when the operating member 200 is inserted into the through hole 141c of the rotating member 141 is improved. Effects such as wear and torque loss due to contact between the actuating member 200 and the rotating member 141 are suppressed.

The actuating member 200 is connected to the rod-shaped member 230 via a connecting portion 240 located on the opposite side of the rod-shaped member 230 and one end E1 of the through-hole 141c of the rotating member 141, and transmits a force for operating the braking member. Cable 150 (flexible member). According to such a configuration, for example, the inner diameter of the through-hole 141c is set by positioning the connecting portion 240 whose outer diameter is likely to be larger than the rod-shaped member 230 or the cable 150 (flexible member) outside the through-hole 141c. The outer diameter of the rotating member 141 can be reduced.

Furthermore, in a state where one end E1 of the actuating member 200 is located farthest from the rotating member 141 in the axial direction, the connecting portion 240 is located on the opposite side to the one end E1 of the through hole 141c. According to such a structure, the size reduction effect by having arrange | positioned the connection part 240 out of the through-hole 141c in all the sections of the through-hole 141c, for example can be acquired.

The actuating member 200 is configured to be axially separable from the linear motion member 142, and the transmission member 220 and the rod-shaped member 230 are configured as an integral part. According to such a configuration, for example, the linear motion member 142 can be moved independently of the operation member 200. In a more specific example, the overrun of the linear motion member 142 can be permitted without moving the operating member 200 and hence the brake shoe 3. Therefore, the control accuracy when controlling the movement amount of the linear motion member 142 can be relaxed. In addition, for example, the electric actuator 100 can be configured to be smaller by the amount that the components for connecting the transmission member 220 and the rod-shaped member 230 can be omitted.

Furthermore, when the transmission member 220 and the linear motion member 142 abut on each other in the axial direction, the transmission member 220 is configured to guide the transmission member 220 and the linear motion member 142 to a position where the relative axial displacement is relatively reduced. Have.

According to such a configuration, for example, even when the transmission member and the linear motion member are eccentric, the taper portion 223 (guide mechanism) reduces the shaft misalignment, and thus the vibration of the electric actuator 100 is suppressed. Or wear and torque loss due to contact between the actuating member 200 and the rotating member 141 can be suppressed.

[First Modification]
Next, a first modification will be described. FIG. 12 is a cross-sectional view of the cable end 210A of the first modification. As shown in FIG. 12, in the cable end 210 A according to the first modification, the connecting portion 240 A may be configured by two members, and one may be fastened to the other. The connecting portion 240 A includes a coupled portion 250 that is integrally provided with the rod-shaped member 230 at an end portion in the direction D 2 of the rod-shaped member 230, and a coupling member 260 that can be coupled to the coupled portion 250. The coupled portion 250 has a larger diameter than the rod-shaped member 230, and is provided with a first recess 251 extending inward along the third rotation center Ax3. The coupling member 260 includes a small-diameter portion 261 that can be fastened to the first recess 251 of the coupled portion 250 and a large-diameter portion 262 that is larger in diameter than the small-diameter portion 261 and integrated with the small-diameter portion 261. The large-diameter portion 262 is provided with a second recess 263 in which the end 150a (see FIG. 5) of the cable 150 is caulked. The transmission member 220, the rod-like member 230, and the coupled portion 250 are configured as an integral part. The coupling member 260 can be assembled to the coupled portion 250 by fastening the small diameter portion 261 of the coupling member 260 to the first recess 251 of the coupled portion 250.

According to such a configuration, for example, when only the coupling member 260 is damaged, the coupling member 260 may be removed from the coupled portion 250 and replaced with another coupling member 260, and the entire cable end 210A needs to be replaced. Therefore, labor and manufacturing costs can be reduced.

[Second Modification]
Next, a second modification will be described. FIG. 13 is a cross-sectional view of the cable end 210B of the second modification. FIG. 14 is a cross-sectional view showing the connecting portion 240B in a state where the cable end 210B of FIG. 13 is rotated by 90 ° around the axis.

As shown in FIGS. 13 and 14, in the cable end 210B according to the second modification, the connecting portion 240B may be constituted by two members, and one of them may be coupled to the other via a pin (not shown).

The connecting portion 240 B includes a coupled portion 350 provided integrally with the rod-shaped member 230 at an end in the direction D 2 of the rod-shaped member 230, and a coupling member 360 that can be coupled to the coupled portion 350. As shown in FIG. 14, the coupled portion 350 has a pair of legs 351 that face each other while being spaced apart in a direction orthogonal to the third rotation center Ax3. A recess 352 is provided. Each leg 351 is provided with a through hole 353 into which a pin (not shown) can be inserted. As shown in FIG. 13, the height of the leg portion 351 in the direction orthogonal to the third rotation center Ax3 is larger than the diameter of the rod-shaped member, and as shown in FIG. 14, the side surfaces 351a of the pair of leg portions 351. The separation distance in the direction orthogonal to the third rotation center Ax3 is configured to be larger than the diameter of the rod-shaped member 230.

As shown in FIGS. 13 and 14, the coupling member 360 includes a protruding portion 361 that can be inserted between the pair of leg portions 351 of the coupled portion 350, and a second recessed portion 363 provided inwardly. And a cylindrical portion 362 integrated with each other. The projecting portion 361 is provided with a through hole 364 having the same diameter as the through hole 353 of the leg portion 351. A cable end 150a (see FIG. 5) is caulked in the second recess 363. These transmission member, rod-shaped member, and coupled portion 350 are configured as an integral part. Note that the coupling member 360 can be assembled to the coupled portion 350 by inserting the protruding portion 361 of the coupling member 360 into the first recess 352 of the coupled portion 350 and inserting pins (not shown) into the through

holes

353 and 364. .

According to such a configuration, for example, the coupling member 360 is coupled to the coupled portion 350 by a simple procedure of inserting the protruding portion 361 of the coupling member 360 into the first recess 352 of the coupled portion 350 and inserting the pin into the through hole. Therefore, labor saving can be achieved.

[Third Modification]
Next, a third modification will be described. FIG. 15 is a cross-sectional view of a part of the cable end 210C of the third modification. As shown in FIG. 15, a disc-shaped transmission member 220 A is integrally provided at the end of the rod-shaped member 230 in the direction D 1. The entire inner surface 221A of the transmission member 220A on the rotating member 141 side is configured as a tapered portion 223A. The taper portion 223A is inclined toward the direction D2 from the outer peripheral end 223Aa toward the third rotation center Ax3 that is the center in the radial direction. Further, the protrusion 143Ab of the anti-rotation member 143A is configured as a tapered portion in which an end surface 143Ab3 provided at the tip in the direction D1 extends in parallel with the inner surface 221A of the transmission member 220A. That is, the end surface 143Ab3 is inclined toward the direction D2 as it goes from the outer peripheral end 143Ab4 to the center in the radial direction. Further, the tapered portion 223A of the transmission member 220A can contact the end surface 143Ab3.

According to such a configuration, for example, when the tapered portion 223A of the transmission member 220A comes into contact with the end surface 143Ab3, the radial center of the transmission member 220A moves toward the third rotation center Ax3. Here, since the end surface 143b3 is located on the outer side in the radial direction with respect to the linear motion member 142, the radial position adjustment can be stably performed on the outer peripheral portion of the transmission member 220A. Note that the end surface 143Ab3 and the tapered portion 223A are examples of a guide mechanism.

[Fourth Modification]
Next, a fourth modification will be described. FIG. 16 is a cross-sectional view of a part of the cable end 210D of the fourth modified example.

As shown in FIG. 16, in the cable end 210D according to the fourth modification, the connecting portion 240C has a tubular member 400, and the end portion 230Aa of the rod-like member 230A and the end portion 150a of the cable may be combined. Good.

The rod-shaped member 230A is configured to have the same diameter over the entire length, and a male screw is provided at the end 230Aa in the direction D2. The diameter of the end portion in the direction D2 and the end portion 150a of the cable are substantially the same. The tubular member 400 is provided with a through hole 401 along the third rotation center Ax3, and an internal thread is provided on the inner peripheral surface. An end 230Aa in the direction D2 of the rod-shaped member 230A is fastened to one side of the through hole 401 of the tubular member 400, and the end 150a of the cable 150 is inserted and crimped to the other side.

According to such a configuration, for example, the cylindrical member 400 is easier to manufacture than the coupled portion of the embodiment, so that it is possible to reduce manufacturing effort and cost. Moreover, the outer diameter of the connection part 240C can be made smaller by setting the thickness of the cylindrical member 400 to be smaller than the thickness of the coupled part of the embodiment.

[Fifth Modification]
Next, a fifth modification will be described. FIG. 17 is a cross-sectional view of part of the linear motion member 142A and the transmission member 220B of the fifth modification. As shown in FIG. 17, the end surface in the direction D1 of the side wall 142Aa in the linear motion member 142A of the fifth modified example is a first end surface 142Ae1 radially inward and a first end surface 142Ae1 radially outward of the first end surface 142Ae1. Two end faces 142Ae2. The first end surface 142Ae1 and the second end surface 142Ae2 are tapered portions that are inclined toward the direction D2 toward the third rotation center Ax3. However, the inclination angle with respect to the third rotation center Ax3 is set to be smaller on the first end surface 142Ae1 than on the second end surface 142Ae2. The inner surface 221B of the transmission member 220B has a first flat surface portion 222B, a peripheral surface portion 223B, and a second flat surface portion 224B. The first flat surface portion 222B and the second flat surface portion 224B extend in the radial direction, and the peripheral surface portion 223B extends in the axial direction. The peripheral surface portion 223B and the second flat surface portion 224B intersect at the corner portion 227B. The peripheral surface portion 223B is located radially inward from the inner peripheral surface of the through hole 142Ac of the linear motion member 142A. The first end surface 142Ae1 and the second end surface 142Ae2 are examples of a guide mechanism.

According to such a configuration, for example, even when the transmission member 220 B and the linear motion member 142 A are eccentric, the taper portion 223 (guide mechanism) further reduces the axial deviation, and thus the vibration of the electric actuator 100. Is more suppressed. This will be specifically described below. When the linear motion member 142A moves in the direction D1 and enters the state of FIG. 17, when the transmission member 220B is displaced in the radial direction with respect to the linear motion member 142A, the first end surface 142Ae1 or the second end surface 142Ae1 The end surface 142Ae2 is in contact with the corner portion 227B. Since the first end surface 142Ae1 and the second end surface 142Ae2 are inclined tapered portions, the transmission member 220B is connected to the linear motion member 142A so that the radial center of the transmission member 220B coincides with the radial center of the linear motion member 142A. They are guided to a position where their axial displacements are relatively reduced. Further, in a state where the transmission member 220B and the linear motion member 142A are in contact with each other in the axial direction, the circumferential surface portion 223B extending in the axial direction and the inner circumferential surface of the through hole 142Ac extending in the axial direction face each other with a gap. The relative movement of the transmission member 220B and the linear motion member 142A in the direction intersecting the axial direction is suppressed.

As mentioned above, although embodiment of this invention was illustrated, the said embodiment is an example and is not intending limiting the range of invention. The embodiment described above can be implemented in various other forms, and various omissions, replacements, combinations, and changes can be made without departing from the scope of the invention. In addition, specifications (structure, type, direction, form, size, length, width, thickness, height, number, arrangement, position, material, etc.) of each configuration, shape, etc. are changed as appropriate. Can be implemented.

For example, in the embodiment, the rod-shaped member 230 may not extend in the through hole 141c of the rotating member 141 over the entire length of the through hole 141c. In this case, the connecting portion 240 is located inside the through hole 141c. Further, the actuating member 200 may be coupled to the linear motion member 142.

Furthermore, the transmission member 220 and the rod-shaped member 230 may be configured separately. When separate members are used, the rod-shaped member 230 may be fixed to the transmission member 220 and the rod-shaped member 230 may be fastened to the transmission member 220 with a bolt. The transmission member 220 may be provided with a through-hole having a diameter larger than that of the rod-shaped member 230 and smaller than that of the connecting portion 240, and the rod-shaped member 230 is inserted into the through-hole and hooked.

In the above embodiment, the

transmission mechanism

220, 220A is provided with the guide mechanism (tapered

portion

223, 223A), but the linear motion member 142 may be provided with the guide mechanism.

Claims

A braking member that brakes the drum rotor by being pressed by a drum rotor that rotates integrally with the wheel, a backing plate that supports the braking member, an electric actuator that is provided on the backing plate and operates the braking member; A brake device comprising:
The electric actuator is
A motor having a rotating output shaft;
A rotating member that has a male screw and rotates around the axis of the male screw in conjunction with the output shaft; and a linear member that has a female screw that meshes with the male screw and moves linearly as the rotating member rotates. A motion conversion mechanism;
An actuating member for receiving a force for actuating the braking member from the linear motion member;
Have
The rotating member is rotationally driven via a driven portion that is provided on the outer periphery of the rotating member and rotates in conjunction with the output shaft,
The male screw and the female screw mesh with each other on the opposite side of the driven portion from the braking member,
The actuating member is configured such that one end receives a force to actuate the braking member from the linear motion member, and the other end actuates the braking member,
The rotating member is provided with a through hole along the axial direction of the axis,
The one end of the actuating member is disposed on the opposite side of the through hole from the braking member,
The actuating member has a rod-like member extending in the through hole,
Brake device.
The actuating member is connected to the rod-shaped member via a connecting portion disposed on the opposite side of the rod-shaped member and the one end of the through hole, and transmits a force for operating the braking member. The brake device according to claim 1, comprising:
The brake device according to claim 2, wherein the connecting portion is disposed on the side opposite to the one end of the through hole in a state where the one end is at a position farthest from the rotating member along the axial direction.
The actuating member includes a transmission member configured to be separable from the linear motion member in the axial direction and transmitting a force for operating the braking member from the linear motion member to the rod-shaped member;
The brake device according to any one of claims 1 to 3, wherein the transmission member and the rod-shaped member are configured as an integral part.
The actuating member includes a transmission member configured to be separable from the linear motion member in the axial direction and transmitting a force for operating the braking member from the linear motion member to the rod-shaped member;
When at least one of the transmission member and the linear motion member abuts the transmission member and the linear motion member in the axial direction, the axial displacement of the transmission member and the linear motion member is relatively reduced. The brake device according to any one of claims 1 to 4, further comprising a guide mechanism for guiding the position.