JP2020159401A - Brake for vehicle - Google Patents

Abstract

To obtain a reduction gear having a further-improved novel constitution which can easily perform assembling work while securing, for example, a buffer action, and a brake device.SOLUTION: In a brake for a vehicle, a reduction gear has a second end face adjoining an external peripheral face, separating from a first end face in a first peripheral direction, and oriented in a second peripheral direction opposite to the first peripheral direction, and the reduction gear is accommodated in a housing in a state that the second end face is limited to separate from the first end face by a prescribed interval or longer in the first peripheral direction. A whirl-stop member has an elastic deformation part which is interposed between the first end face and the second end face in a state of contacting with the first end face and the second end face, and elastically deformed according to a relative approach of the first end face and the second end face to each other, and a movement limit part interposed between the first end face and the second end face with an interval along the first peripheral direction, and limiting the relative approach of the first end face and the second end face by supporting the first end face and the second end face while being interposed therebetween when a clearance is disappeared due to the relative approach of the first end face to the second end face in the first peripheral direction.SELECTED DRAWING: Figure 10

Description

The present disclosure relates to vehicle brakes.

Conventionally, a vehicle brake having an electric motor, a speed reducing device, and a rotation linear motion conversion mechanism is known (for example, Patent Document 1). In this vehicle brake, the reduction gear decelerates the rotation of the electric motor, and the rotation linear motion conversion mechanism converts the rotation of the rotating member interlocking with the gear of the reduction gear into the linear motion of the linear motion member. The braking member moves in response to the direct movement of the wheel to brake the wheel. Sound and vibration are reduced by interposing an elastic member between the speed reducing device and the housing accommodating the speed reducing device.

Japanese Unexamined Patent Publication No. 2004-129374

However, in such a configuration, if the relative movement amount between the speed reducing device and the housing increases with the elastic deformation of the elastic member, the transmission efficiency of rotation decreases. Therefore, it may be difficult to set the specifications of the elastic member.

Therefore, one of the problems of the present disclosure is, for example, for a vehicle having a new configuration with less inconvenience, which can reduce sound and vibration and can suppress a significant decrease in rotation transmission efficiency. Get the brakes.

The vehicle brake of the present disclosure includes a motor having a rotating rotor, a speed reducing device having a plurality of gears rotating in conjunction with the rotor, a housing accommodating the speed reducing device, and the speed reducing device for the housing. A rotary linear motion having a detent member that limits the relative rotation of the housing, a rotary member that rotates in conjunction with the gear of the speed reducer, and a linear motion member that linearly rotates according to the rotation of the rotary member. The housing includes a conversion mechanism and a braking member that switches between a braking state in which the wheel is braked by moving in response to the linear motion of the linear motion member and a braking state in which the braking of the wheel is released. And a first end surface that is adjacent to the inner peripheral surface and faces the first circumferential direction of the inner peripheral surface, and the speed reducing device has an outer peripheral surface facing the inner peripheral surface and adjacent to the outer peripheral surface. The second end surface is separated from the first one end surface in the first circumferential direction and faces the second circumferential direction opposite to the first circumferential direction, and the second end surface is from the first end surface to the first one. It is housed in the housing in a state where it is restricted from being separated by a predetermined distance or more in the circumferential direction, and the detent member is in contact with the first end surface and the second end surface between the first end surface and the second end surface. The first circumferential direction is between the elastically deformed portion that is intervened in the housing and elastically deforms as the first end surface and the second end surface come relatively close to each other, and the first end surface and the second end surface. When the first end surface is relatively close to the second end surface in the first circumferential direction and the gap disappears, the first end surface is interposed between the first end surface and the second end surface. It has a movement restricting portion that restricts the first end surface from relatively approaching the second end surface by supporting the first end surface.

In the vehicle brake described above, the effect of reducing noise and vibration due to the elastic deformation of the elastically deformed portion can be obtained until the gap is closed, and after the gap is eliminated, the movement limiting portion is relative to the speed reducer and the housing. Since the movement is restricted, it is possible to suppress a decrease in the transmission efficiency of rotation. Therefore, according to the vehicle brake, for example, sound and vibration can be reduced, and it is possible to suppress a significant decrease in rotation transmission efficiency.

FIG. 1 is a schematic and exemplary cross-sectional view of the vehicle brake of the embodiment. FIG. 2 is a schematic and exemplary cross-sectional view of a portion of the vehicle brake caliper of the embodiment. FIG. 3 is a schematic and exemplary perspective view of the gear assembly of the embodiment. FIG. 4 is a schematic and exemplary exploded perspective view of a portion of the vehicle brake of the embodiment, showing a state before the gear assembly is attached to the housing. FIG. 5 is a schematic and exemplary exploded perspective view of a part of the vehicle brake of the embodiment, showing a state before the detent member is attached to the housing. FIG. 6 is a schematic and exemplary disassembled side view of a portion of the housing and gear assembly of the embodiment, showing a state before the gear assembly is inserted into the recess of the housing. FIG. 7 is a schematic and exemplary disassembled side view of a portion of the housing and gear assembly of the embodiment, showing a state in which the gear assembly is located at the mounting position. FIG. 8 is a schematic and exemplary disassembled side view of a portion of the housing, a portion of the gear assembly, and the detent member of the embodiment, before the detent member is inserted into the recess of the housing. It is a figure which shows. FIG. 9 is a schematic and exemplary side view of a part of the housing, a part of the gear assembly, and the detent member of the embodiment, showing a mounted state of the detent member. FIG. 10 is a schematic and exemplary side view of a portion of the housing, a portion of the gear assembly, and the detent member of the embodiment, wherein the movement restrictor limits the relative movement of the housing and the gear assembly. It is a figure which shows the state. FIG. 11 is a schematic and exemplary side view of the detent member of the first modification in a free state. FIG. 12 is a schematic and exemplary side view of a part of the housing, a part of the gear assembly, and the detent member of the first modification, and is a view showing a mounted state of the detent member. FIG. 13 is a schematic and exemplary side view of a part of the housing, a part of the gear assembly, and the detent member of the first modification, in which the relative movement between the housing and the gear assembly is caused by the movement restriction portion. It is a figure which shows the restricted state. FIG. 14 is a schematic and exemplary side view of the detent member of the second modification in a free state. FIG. 15 is a schematic and exemplary side view of a part of the housing, a part of the gear assembly, and the detent member of the second modification, and is a view showing a mounted state of the detent member. FIG. 16 is a schematic and exemplary side view of a part of the housing, a part of the gear assembly, and the detent member of the second modification, in which the relative movement between the housing and the gear assembly is caused by the movement restriction portion. It is a figure which shows the restricted state. FIG. 17 is a schematic and exemplary side view of the detent member of the third modification in a free state. FIG. 18 is a schematic and exemplary side view of a part of the housing, a part of the gear assembly, and the detent member of the third modification, and is a view showing a mounted state of the detent member. FIG. 19 is a schematic and exemplary side view of a part of the housing, a part of the gear assembly, and the detent member of the third modification, in which the relative movement between the housing and the gear assembly is caused by the movement restriction portion. It is a figure which shows the restricted state. FIG. 20 is a schematic and exemplary side view when viewed in the circumferential direction of the detent member of the third modification. FIG. 21 is a schematic and exemplary side view of the detent member of the fourth modification in a free state. FIG. 22 is a schematic and exemplary side view of the fourth modified example with the detent member mounted. FIG. 23 is a schematic and exemplary cross-sectional view when viewed in the circumferential direction of the movement-restricted portion in the movement-restricted state of the detent member of the fourth modification. FIG. 24 is a schematic and exemplary side view of the detent member of the fifth modification in a free state.

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

Further, the brakes for a plurality of vehicles according to the following embodiments and modifications have similar components. Therefore, according to the brakes for the plurality of vehicles, the same effect based on the same components can be obtained. In the following, common or similar reference numerals will be given to these similar components, and duplicate description will be omitted.

Further, in the present specification, ordinal numbers are given for convenience in order to distinguish parts, parts, directions, etc., and do not indicate priorities or orders.

[Embodiment]
FIG. 1 is a cross-sectional view of the brake 1 for a vehicle. As illustrated in FIG. 1, the brake 1 includes a motor 20, a rotation transmission mechanism 100, and a caliper 200 (FIG. 2) incorporating a rotation linear motion conversion mechanism 50. The brake 1 can operate not only as a hydraulic brake but also as an electric brake. The caliper 200 constitutes a hydraulic brake, and the motor 20, the rotation transmission mechanism 100, the rotation linear motion conversion mechanism 50, and the caliper 200 constitute an electric brake. The electric brake is a so-called electric parking brake. That is, the brake 1 is configured so that the braking state by the electric brake function is maintained at the time of parking. However, the electric brake may be activated during running or pausing. The motor 20 is an electric motor and is an example of a drive source.

The motor 20 and the rotation transmission mechanism 100 are housed in the housing 10. The housing 10 includes a casing 11, an inner cover 12, and an outer cover 13.

The casing 11 is provided with an accommodating portion 11a for accommodating the motor 20. The accommodating portion 11a is a bottomed cylindrical hole. The motor 20 is housed in the housing portion 11a in a posture in which one end 21a of the shaft 21 is exposed from the opening end 11b of the housing portion 11a. The side surface (peripheral surface) and the bottom surface of the motor 20 are covered with the wall portion 11c of the casing 11. The casing 11 is made of an insulating synthetic resin material. The shaft 21 is an example of a rotor.

The motor 20 is covered with an inner cover 12 from the side opposite to the casing 11. The inner cover 12 covers the opening end 11b of the accommodating portion 11a. The inner cover 12 is provided with a through hole 12a, and the shaft 21 of the motor 20 penetrates the through hole 12a and is on the opposite side of the motor 20 (body 20a), that is, with the accommodating portion 11a of the inner cover 12. It is exposed on the other side. The inner cover 12 extends in a direction intersecting (orthogonal) with the rotation center Ax1. The inner cover 12 is connected to the casing 11 by a connector 14 such as a screw. The body 20a of the motor 20 is covered with a casing 11 and an inner cover 12. The inner cover 12 is attached to the motor 20. The inner cover 12 is made of an insulating synthetic resin material. The inner cover 12 is an example of a motor bracket.

The rotation transmission mechanism 100 includes an intermediate gear 41, a first planetary gear mechanism 42, and a second planetary gear mechanism 46. The rotation transmission mechanism 100 transmits the rotation of the shaft 21 of the motor 20 to the rotation linear motion conversion mechanism 50 (FIG. 2). In the rotation transmission mechanism 100, the rotation of the shaft 21 is transmitted to the rotation linear motion conversion mechanism 50 via the intermediate gear 41, the first planetary gear mechanism 42, and the second planetary gear mechanism 46. The rotation transmission mechanism 100 is an example of a speed reducing device for operating the brake.

The intermediate gear 41 is rotatably provided around the rotation center Ax2 parallel to the rotation center Ax1, and has an input gear 41a and an output gear 41b. The input gear 41a meshes with the pinion 22 fixed to the shaft 21 of the motor 20. The output gear 41b drives the first planetary gear mechanism 42. The number of teeth of the output gear 41b is smaller than the number of teeth of the input gear 41a. Therefore, the rotation of the motor 20 is decelerated by the intermediate gear 41.

The first planetary gear mechanism 42 has a first sun gear 43, a first planetary carrier 44, and a ring gear 45. The first planetary gear mechanism 42 is an example of the first gear set.

The first sun gear 43 and the first planetary carrier 44 rotate around a rotation center Ax3 parallel to the rotation centers Ax1 and Ax2. The ring gear 45 is fixed to the casing 11. The center of the ring gear 45 coincides with the rotation center Ax3.

The first sun gear 43 has an input gear 43a and an output gear 43b. The input gear 43a meshes with the output gear 41b of the intermediate gear 41. The output gear 43b drives the first planetary carrier 44. The first sun gear 43 is provided with a through hole centered on the rotation center Ax3, and the shaft 49 is press-fitted into the through hole.

The first planetary carrier 44 includes a first carrier base 44a, a plurality of first pinion shafts 44b integrally provided with the first carrier base 44a, and a plurality of rotatably supported first pinion shafts 44b, respectively. It has the first pinion gear 44c of the above. The first pinion gear 44c rotates about the axis (center of rotation) of the first pinion shaft 44b parallel to the center of rotation Ax3. In the present embodiment, as an example, the number of the first pinion shafts 44b is 4, and the number of the first pinion gears 44c is 4, but the present invention is not limited to this.

The first pinion gear 44c meshes with the output gear 43b of the first sun gear 43 in the radial direction of the rotation center Ax3, and meshes with the ring gear 45 (internal teeth) in the radial direction of the rotation center Ax3. The first pinion gear 44c revolves around the first sun gear 43. The first carrier base 44a has a second sun gear 44d as an output unit. In such a configuration, the rotation of the intermediate gear 41 is decelerated by the first planetary gear mechanism 42 and output from the second sun gear 44d.

In the first planetary gear mechanism 42, a part of the first sun gear 43, the first carrier base 44a, and the first pinion shaft 44b are made of a synthetic resin material. On the other hand, the first pinion gear 44c and the ring gear 45 are made of a metal material.

The second planetary gear mechanism 46 has a second sun gear 44d, a second planetary carrier 47, and a ring gear 45. The second planetary gear mechanism 46 is an example of a second gear set. The ring gear 45 is shared by the first planetary gear mechanism 42 and the second planetary gear mechanism 46.

The second sun gear 44d and the second planetary carrier 47 rotate around the rotation center Ax3. The second sun gear 44d and the second planetary carrier 47 are rotatably supported by a shaft 49 fixed to the first sun gear 43 and extending along the rotation center Ax3.

The second planetary carrier 47 includes a second carrier base 47a, a plurality of second pinion shafts 47b fixed to the second carrier base 47a, and a plurality of second pinion shafts 47b rotatably supported by the second pinion shaft 47b. It has a two-pinion gear 47c. The second pinion gear 47c rotates around the axis (center of rotation) of the second pinion shaft 47b parallel to the center of rotation Ax3. In the present embodiment, as an example, the number of the second pinion shaft 47b is 4, and the number of the second pinion gear 47c is also 4, but the number is not limited to this.

The second pinion gear 47c meshes with the second sun gear 44d in the radial direction of the rotation center Ax3, and meshes with the ring gear 45 (internal tooth) in the radial direction of the rotation center Ax3. The second pinion gear 47c revolves around the second sun gear 44d. The second carrier base 47a has a protruding portion 47d as an output portion. The rotation of the first planetary gear mechanism 42 is decelerated by the second planetary gear mechanism 46, and is output from the protrusion 47d.

In the second planetary gear mechanism 46, the second sun gear 44d and the second planetary carrier 47 are made of a metal material such as an iron-based material.

The rotating member 51 (FIG. 2) of the rotary linear motion conversion mechanism 50 is coupled to the protruding portion 47d of the second planetary gear mechanism 46 and rotates integrally with the protruding portion 47d. Therefore, the rotating member 51 rotates in conjunction with the shaft 21 of the motor 20.

Further, the second pinion shaft 47b is coupled to the second carrier base 47a by being press-fitted into a hole provided in the second carrier base 47a. The density of the second carrier base 47a is set higher than the density of the second pinion shaft 47b. The second carrier base 47a is an example of a support member. The rotation transmission mechanism 100 may be a speed reduction device having a plurality of gears, and is not limited to the configuration as in this embodiment.

FIG. 2 is a cross-sectional view of the caliper 200. The caliper 200 has a body 201 and a piston 203. The body 201 is provided with a cylinder 202. The cylinder 202 is a bottomed cylindrical hole opened downward in FIG. 2 with the rotation center Ax3 as the center. The piston 203 is housed in the cylinder 202 so as to be reciprocating along the rotation center Ax3. The cylinder 202 is provided with a hydraulic chamber R. As the hydraulic pressure in the hydraulic chamber R rises, the piston 203 pushes the back plate 204a of the pad 204 downward in FIG. 2 and the lining 204b against the disc D. As a result, a braking state by the hydraulic brake is obtained in which the wheel (not shown) of the vehicle rotating integrally with the disc D is braked. Specifically, the piston 203 has a cylindrical outer surface outer peripheral surface 203b and an end surface 203c on the side opposite to the hydraulic chamber R (lower side in FIG. 2). A minute gap (clearance) is set between the outer peripheral surface 203b of the piston 203 and the inner peripheral surface 202a of the cylinder 202, and the outer peripheral surface 203b has an inner circumference in a lubricated state in which the hydraulic fluid exists in the gap. It slides on the surface 202a. The seal 62 is interposed between the outer peripheral surface 203b and the inner peripheral surface 202a, and suppresses leakage of the hydraulic fluid from the hydraulic chamber R through the gap. Further, the seal 62 has a retract function of pulling the piston 203 toward the hydraulic chamber R side (upper in FIG. 2) by elastic force as the hydraulic pressure in the hydraulic chamber R decreases, and separating the end surface 203c of the piston 203 from the pad 204. have. That is, when the pressure on the back plate 204a of the piston 203 is released as the hydraulic pressure in the hydraulic chamber R decreases, the pressing of the lining 204b on the disc D by the piston 203 is released, whereby the hydraulic brake is released. The braking release state can be obtained. In this way, the caliper 200 can operate as a hydraulic brake. The pad 204 is an example of a braking member, and the disc D is an example of a brake rotor.

Further, a rotation / linear motion conversion mechanism 50 is provided in the caliper 200. The rotary linear motion conversion mechanism 50 has a rotary member 51 and a linear motion member 52. The rotating member 51 has a coupling portion 51a, a flange 51b, and a shaft 51c, and is rotatably supported by the body 201 around the rotation center Ax3. The coupling portion 51a is coupled to the protruding portion 47d as an output portion of the second planetary gear mechanism 46 (rotation transmission mechanism 100). A thrust bearing 61 is provided between the flange 51b and the body 201 of the caliper 200. The shaft 51c projects from the flange 51b to the side opposite to the joint portion 51a (downward in FIG. 2). A male screw 51d is provided on the outer peripheral surface of the shaft 51c. The rotating member 51 is an example of the first rotating member.

The linear motion member 52 has a tubular portion 52a and a protrusion 52b. The shape of the tubular portion 52a is a cylindrical shape centered on the rotation center Ax3. A female screw 52c is provided on the inner surface of the tubular portion 52a, and the female screw 52c and the male screw 51d of the rotating member 51 mesh with each other. The protrusion 52b protrudes outward in the radial direction of the rotation center Ax3 from the tubular portion 52a.

The rotation linear motion conversion mechanism 50 is housed in a recess 203a provided in the piston 203. The recess 203a is open toward the hydraulic chamber R side (upper side of FIG. 2). The linear motion member 52 is provided so as to be movable in the axial direction (vertical direction in FIG. 2) of the rotation center Ax3 in the recess 203a. The recess 203a is provided with a groove 203d extending in the axial direction of the rotation center Ax3, and the protrusion 52b of the linear motion member 52 is movably accommodated in the groove 203d along the groove 203d. That is, the side surface of the groove 203d and the protrusion 52b of the linear motion member 52 form a detent mechanism for the linear motion member 52. Further, in the present embodiment, the rotation of the piston 203 around the rotation center Ax3 is restricted by the friction between the piston 203 and the seal 62 or the pad 204.

As described above, in the present embodiment, the male screw 51d of the rotating member 51 and the female screw 52c of the linear motion member 52 mesh with each other, and the rotation of the protrusion 52b of the linear motion member 52 is restricted by the groove 203d of the piston 203. The linear motion member 52 linearly moves in the axial direction of the rotation center Ax3 according to the rotation of the rotary member 51. Due to the unidirectional rotation of the rotating member 51 based on the rotation of the shaft 21 of the motor 20 (hereinafter, this is referred to as normal rotation), the linear motion member 52 moves downward in FIG. 2, and the piston 203 maps the back plate 204a. When pressed downward of 2, the piston 203 presses the lining 204b of the pad 204 against the disc D. As a result, a braking state is obtained by the electric braking function in which the wheel (not shown) of the vehicle rotating integrally with the disc D is braked. On the other hand, when the linear motion member 52 moves upward in FIG. 2 due to the reverse rotation of the rotating member 51 based on the reversal of the shaft 21 of the motor 20, and the pressure of the piston 203 on the back plate 204a is released, the piston The pressing of the lining 204b against the disc D by the 203 is released, whereby the braking released state by the electric braking function is obtained. In this way, the motor 20, the rotation transmission mechanism 100, the rotation linear motion conversion mechanism 50, and the caliper 200 can operate as an electric brake.

FIG. 3 is a perspective view of the gear assembly 40. In the following, for convenience of explanation, regarding the axial direction of the rotation center Ax3, the upper part in FIGS. 1 and 3 is referred to as the first axial direction and is represented by an arrow Da1, and the lower part in FIGS. 1 and 3 is the second axis. It is called the direction and is represented by the arrow Da2. Further, as shown in FIG. 3, with respect to the circumferential direction of the rotation center Ax3, the direction of the right-handed screw in the first axial direction Da1 is referred to as the second circumferential direction and is represented by an arrow Dp2, which is the second circumferential direction Dp2. The opposite direction is referred to as the first circumferential direction and is represented by the arrow Dp1. The arrows indicating the first axial direction Da1, the second axial direction Da2, the first circumferential direction Dp1, and the second circumferential direction Dp2 are appropriately shown in figures other than FIGS. 1 and 3.

The gear assembly 40 has a portion of the first planetary gear mechanism 42 excluding the first sun gear 43 (FIG. 1) and a second planetary gear mechanism 46. That is, the gear assembly 40 has a first planetary carrier 44, a ring gear 45, a second sun gear 44d, and a second planetary carrier 47.

The ring gear 45 has an outer peripheral surface 40a, an end surface 45b in the first axial direction Da1, and an end surface 45c in the second axial direction Da2. The outer peripheral surface 40a has a cylindrical shape. The end faces 45b and 45c are along the radial direction and the circumferential direction of the rotation center Ax3, respectively, and intersect and are orthogonal to the axial direction of the rotation center Ax3. The end faces 45b and 45c may also be referred to as end portions. The axial direction of the rotation center Ax3 is the axial direction of the outer peripheral surface 40a, the circumferential direction of the rotation center Ax3 is the circumferential direction of the outer peripheral surface 40a, and the radial direction of the rotation center Ax3 is the radial direction of the outer peripheral surface 40a. ..

As shown in FIG. 3, a protrusion 40b is provided on the outer peripheral surface 40a of the ring gear 45. A plurality of protrusions 40b are provided on the outer peripheral surface 40a at intervals in the circumferential direction of the rotation center Ax3. In the example of FIG. 3, three protrusions 40b having the same shape are arranged at equal intervals in the circumferential direction of the rotation center Ax3, in other words, at every 120 ° of the central angle of the rotation center Ax3.

The protrusion 40b protrudes outward in the radial direction of the rotation center Ax3 from the outer peripheral surface 40a. The protrusion 40b has a substantially constant width in the circumferential direction of the rotation center Ax3 and a substantially constant height in the radial direction of the rotation center Ax3, and extends in the axial direction of the rotation center Ax3.

Further, as shown in FIG. 3, the protrusion 40b has a substantially constant width in the circumferential direction of the rotation center Ax3 and a substantially constant height in the radial direction of the rotation center Ax3, and the end face 45b and the end face of the ring gear 45. It extends in the axial direction of the rotation center Ax3 with and from 45c. The protrusion 40b functions as a slider that moves along a rail or a guide provided on the casing 11 when the gear assembly 40 is attached to the casing 11. This will be described later.

Further, as shown in FIG. 1, an inward flange 45d is provided at the end of the ring gear 45 in the second axial direction Da2. The inner diameter of the inward flange 45d is smaller than the outer diameter of the second carrier base 47a. Therefore, the second carrier base 47a, the second pinion gear 47c, and the second pinion gear 47c to which the second pinion shaft 47b is attached in the cylinder of the ring gear 45 in a posture in which the central axis (rotation center Ax3) of the ring gear 45 is substantially along the direction of gravity. A gear assembly 40 in which the first carrier base 44a to which the two sun gears 44d and the first pinion shaft 44b are attached and the first pinion gear 44c are housed and temporarily assembled before mounting on the casing 11 can be configured. That is, the ring gear 45 functions as a container for accommodating parts other than the ring gear 45 in the gear assembly 40.

FIG. 4 is a diagram showing a state before the gear assembly 40 is attached to the casing 11 (housing 10), and FIG. 5 is a diagram showing a state before the detent member 70 is attached to the casing 11.

As shown in FIGS. 1 and 4, the casing 11 is provided with a recess 11d that opens in the second axial direction Da2. The gear assembly 40 is attached to the casing 11 in a state of being housed in the recess 11d. The bottom surface 11d1 of the recess 11d intersects and is orthogonal to the axial direction of the rotation center Ax3. The inner peripheral surface 11d2 of the recess 11d has a cylindrical surface shape centered on the rotation center Ax3. The gear assembly 40 is inserted into the recess 11d in the first axial direction Da1, and is housed in a posture in which the end surface 45b of the ring gear 45 and the first pinion gear 44c (FIG. 3) face the bottom surface 11d1 of the recess 11d. A minute gap is provided between the top surface of the protrusion 40b of the gear assembly 40 and the inner peripheral surface 11d2 of the recess 11d facing the top surface, and between the outer peripheral surface 40a and the inner peripheral surface 11d2 of the gear assembly 40. Is provided with a larger gap. The axial direction of the rotation center Ax3 is the axial direction of the inner peripheral surface 11d2, the circumferential direction of the rotation center Ax3 is the circumferential direction of the inner peripheral surface 11d2, and the radial direction of the rotation center Ax3 is the diameter of the inner peripheral surface 11d2. The direction.

After being inserted all the way into the recess 11d, the gear assembly 40 is moved relative to the casing 11 in the first circumferential direction Dp1 to move to a predetermined mounting position. After that, as shown in FIG. 5, the detent member 70 is directed from the introduction ports Ip provided at three locations (however, only one location is shown in FIG. 5) around the end surface 45b of the gear assembly 40. It is inserted into D1 (first axial direction Da1) and is mounted between the inner peripheral surface 11d2 of the recess 11d and the outer peripheral surface 40a (FIGS. 3 and 4) of the gear assembly 40. The detent member 70 limits the relative movement (relative rotation) of the rotation center Ax3 between the casing 11 and the gear assembly 40 in the circumferential direction.

Here, with reference to FIGS. 6 to 10, the attachment of the gear assembly 40 to the casing 11, the attachment of the detent member 70, and the limitation of the relative rotation between the casing 11 and the gear assembly 40 by the detent member 70. Explained. 6 to 8 are side views at each stage until the casing 11, the gear assembly 40, and the detent member 70 are assembled. FIG. 6 shows a state before the gear assembly 40 is inserted into the recess 11d of the casing 11, FIG. 7 shows a state where the gear assembly 40 inserted into the recess 11d is moved to the mounting position, and FIG. The state before the detent member 70 is inserted into the recess 11d is shown. 9 and 10 are side views of a part of the casing 11 and the gear assembly 40 with the detent member 70 attached. FIG. 9 shows a mounted state in which the gear assembly 40 and the detent member 70 are attached to the casing 11, and FIG. 10 shows the detent member 70 being elastic due to the relative movement of the gear assembly 40 and the casing 11 around the rotation center Ax3. Indicates a compressed state. In the following description, the axial direction of the rotation center Ax3 is simply referred to as an axial direction, the radial direction of the rotation center Ax3 is simply referred to as a radial direction, and the circumferential direction of the rotation center Ax3 is simply referred to as a circumferential direction.

In the present embodiment, the gear assembly 40 is provided with a protrusion 40b that functions as a slider, and the casing 11 (housing 10) is provided with a rail 11e that guides the slider to a predetermined mounting position. However, the configuration is not limited to this, and the housing 10 may be provided with a slider, and the gear assembly 40 may be provided with a rail. The rail may also be referred to as a guide or a guide rail. The slider can also be referred to as a guided portion or a mover.

The protrusion 40b has an end surface 40b1 in the first circumferential direction Dp1 and an end surface 40b2 in the second circumferential direction Dp2. The end face 40b1 is a plane that faces Dp1 in the first circumferential direction, is substantially along the radial direction and the axial direction, has a substantially constant height in the radial direction, and extends in the axial direction. The end face 40b2 is a plane that faces the second circumferential direction Dp2, substantially along the radial direction and the axial direction, has a substantially constant height in the radial direction, and extends in the axial direction. The end faces 40b1 and 40b2 may be oriented in the circumferential direction, and need not be continuously extended, and may have an intermittent configuration. Further, the end faces 40b1 and 40b2 are not limited to the side surfaces of the protrusions, and may be formed by, for example, the side surfaces of the recesses.

The rail 11e is a rib protruding inward in the radial direction of the rotation center Ax3 from the inner peripheral surface 11d2 of the recess 11d. The rail 11e has a first rail 11e1, a second rail 11e2, and a third rail 11e3.

The first rail 11e1 has a substantially constant width in the circumferential direction of the rotation center Ax3 and a substantially constant height in the radial direction of the rotation center Ax3, and extends in the axial direction of the rotation center Ax3. As illustrated in FIG. 9, the first rail 11e1 has the gear assembly 40 mounted on the casing 11 from a position corresponding to the end of the first axial Da1 of the gear assembly 40 to the second axial Da2. It extends to a position corresponding to the end of the, but is not limited to this.

The third rail 11e3 has a substantially constant width in the axial direction of the rotation center Ax3 and a substantially constant height in the radial direction of the rotation center Ax3, and extends in the circumferential direction of the rotation center Ax3. The third rail 11e3 extends in the first circumferential direction Dp1 from a position separated from the end of the first rail 11e1 in the second axial direction Da2 in the first circumferential direction Dp1. The end of the third rail 11e3 in the second circumferential direction Dp2 functions as the second rail 11e2 that guides the protrusion 40b as a slider in the axial direction of the rotation center Ax3. As shown in FIG. 6, the gap between the first rail 11e1 and the second rail 11e2 functions as an introduction port Ip of the movement path of the protrusion 40b formed by the rail 11e.

In the first rail 11e1, the protrusion 40b as a slider is guided by the end surface 11f1 in the first circumferential direction Dp1, and in the third rail 11e3, the protrusion 40b is guided by the end surface 11f3 in the first axial direction Da1. Is. The end face 11f1 faces the first circumferential direction Dp1, and the end face 11f2 faces the second circumferential direction DP2. The rail 11e does not have to extend continuously, and may have an intermittent configuration. Further, the rail 11e may be formed by a surface for guiding the slider, and is not limited to a protrusion such as a rib, and may be formed by, for example, a side surface of a recess.

Further, in the present embodiment, the gear assembly 40 is provided with a protrusion 40b that functions as a slider as described above, and the casing 11 (housing 10) restricts the movement of the slider and holds the slider at a predetermined mounting position. A stopper 11 g is provided. However, the configuration is not limited to this, and the housing 10 may be provided with a slider and the gear assembly 40 may be provided with a stopper.

The first rail 11e1 functions as a first stopper 11g1 that restricts the protrusion 40b as a slider from moving in the second circumferential direction Dp2, and the third rail 11e3 has the protrusion 40b moving in the second axial direction Da2. It functions as a third stopper 11g3 that limits.

Further, a second stopper 11g2 is provided on the inner peripheral surface 11d2 of the recess 11d of the casing 11. The second stopper 11g2 has a substantially constant width in the circumferential direction of the rotation center Ax3 and a substantially constant height in the radial direction of the rotation center Ax3, and extends in the axial direction of the rotation center Ax3. The second stopper 11g2 extends from the end of the first circumferential direction Dp1 of the third rail 11e3 in the first axial direction Da1. Further, the second stopper 11g2 is a position corresponding to the end portion of the gear assembly 40 in the first axial direction Da1 to the end portion in the second axial direction Da2 in a state where the gear assembly 40 is mounted on the casing 11. Extends to.

In the first stopper 11g1, it is the end surface 11f1 of the first circumferential direction Dp1 that restricts the movement of the protrusion 40b as a slider in the second circumferential direction Dp2, and in the second stopper 11g2, the first circumferential direction of the protrusion 40b. It is the end face 11f2 of the second circumferential direction Dp2 that limits the movement to Dp1, and it is the first axial direction Da1 that limits the movement of the protrusion 40b to the second axial direction Da2 in the third stopper 11g3. The end face is 11f3. The stopper 11g does not have to extend continuously, and may have an intermittent configuration. Further, the stopper 11g may be formed by a surface that restricts the movement of the slider, and is not limited to a protrusion such as a rib, and may be formed by, for example, a side surface of the recess. Further, the stopper 11g may limit the movement of the slider adjacent to the slider. Therefore, the surface of the stopper that restricts the movement of the slider in the circumferential direction of the center of rotation Ax3 and the surface of the slider that comes into contact with the stopper need only intersect the circumferential direction and are orthogonal to the circumferential direction. It is not necessary, and the surface of the stopper that restricts the movement of the slider in the axial direction of the center of rotation Ax3 and the surface of the slider that abuts on the stopper need only intersect the axial direction and are orthogonal to the axial direction. You don't have to.

Further, in the present embodiment, the bottom surface 11d1 (see FIGS. 1 and 4) of the recess 11d functions as a fourth guide that guides the rotation center Ax3 in the circumferential direction, and the gear assembly 40 moves in the first axial direction Da1. The inner peripheral surface 11d2 of the recess 11d may be provided with protrusions such as ribs that function as the fourth guide and the fourth stopper, although the fourth stopper functions as a fourth stopper. ..

In such a configuration, as shown in FIG. 6, as the gear assembly 40 is moved relative to the casing 11 in the first axial direction Da1 (direction D1), the protrusion 40b as a slider Is inserted into the movement path from the introduction port Ip, guided by the first rail 11e1 and the second rail 11e2, and moves to the position P1 where the gear assembly 40 shown in FIG. 7 abuts on the bottom surface 11d1 of the recess 11d.

Next, as shown in FIG. 7, as the gear assembly 40 is moved relative to the casing 11 in the first circumferential direction Dp1, the protrusion 40b is guided by the third rail 11e3. It moves from the position P1 shown in FIG. 7 to the position P2 away from the first circumferential direction Dp1. The position P2 is a mounting position of the gear assembly 40 to the casing 11 (housing 10).

As is clear from FIG. 7, when the protrusion 40b is in the position P2, the second stopper 11g2 can limit the movement of the protrusion 40b in the first circumferential direction Dp1, but the end surface 11f1 of the first stopper 11g1. Since there is a gap G between the protrusion 40b and the end surface 40b2 of the second circumferential direction Dp2 of the protrusion 40b, the movement of the protrusion 40b in the second circumferential direction Dp2 is not restricted in this state. Therefore, as shown in FIGS. 8 and 9, the detent member 70 is inserted between the end surface 11f1 of the first stopper 11g1 and the end surface 40b2 of the protrusion 40b. The detent member 70 is interposed between the first stopper 11g1 and the protrusion 40b to limit the protrusion 40b and thus the gear assembly 40 from moving (rotating) in the second circumferential direction Dp2. The detent member 70 may also be referred to as a fixing member or a spacer. The detent member 70 fills the gap G.

As shown in FIG. 8, the detent member 70 is inserted by the operator from the introduction port Ip into the movement path, that is, into the gap G, moved in the first axial direction Da1 (direction D1), and is shown in FIG. Move to the position P3. The position P3 is a mounting position of the detent member 70 to the casing 11 and the gear assembly 40.

Here, in the line of sight of FIGS. 8 and 9, the outer shape of the detent member 70 is substantially oval. The end surface 70a of the detent member 70 in the first axial direction Da1, that is, the upper end surface 70a in FIG. 8 has a curved surface shape that is convex in the first axial direction Da1, and is the first of the detent members 70. The end surface 70a in the axial direction Da2, that is, the lower end surface 70a in FIG. 8, has a curved surface shape that is convex in the second axial direction Da2. That is, the end faces 70a on both sides of the detent member 70 in the longitudinal direction have a tapered shape whose width becomes narrower toward the tip. The tapered shape is not limited to this, and can be realized as various forms. The end face 70a is an example of an end portion.

Further, the detent member 70 has elasticity and is mounted in a state of being elastically compressed between the first stopper 11g1 and the protrusion 40b. That is, the detent member 70 is press-fitted between the first stopper 11g1 and the protrusion 40b. In other words, the detent member 70 is interposed between the end surface 11f1 of the first stopper 11g1 and the end surface 40b2 of the protrusion 40b in contact with the end surface 11f1 and the end surface 40b2. Therefore, the width Wf (FIG. 8) along the lateral direction of the detent member 70 in the free state is larger than the width Ws (FIG. 9) along the circumferential direction in the mounted state.

The detent member 70 has a substantially constant thickness in the radial direction of the rotation center Ax3, that is, in the direction perpendicular to the paper surface of FIG. 9 in the mounted state shown in FIG. 9, and also has an axial direction and a circumferential direction of the rotation center Ax3. It has a shape like a flat plate extending to. Further, in the mounted state, the thickness in the radial direction (not shown) is smaller than the width W in the circumferential direction and the length L in the axial direction, and the width W is shorter than the length L. Therefore, in the present embodiment, in the mounted state, the longitudinal direction of the detent member 70 is the axial direction of the rotation center Ax3, the width direction of the detent member 70 is the circumferential direction of the rotation center Ax3, and the detent member 70 The thickness direction is the radial direction of the rotation center Ax3. 8 and 9 correspond to a view of the detent member 70 from the thickness direction.

In the free state shown in FIG. 8, the detent member 70 is plane symmetric with respect to the virtual plane perpendicular to the longitudinal direction, plane symmetric with respect to the virtual plane perpendicular to the lateral direction, and in the thickness direction. It is also plane symmetric with respect to a virtual plane perpendicular to.

The end faces 70b on both sides of the detent member 70 in the width direction are planes extending in the thickness direction and the longitudinal direction in the free state shown in FIG. 8, and in the radial direction and the axial direction in the mounting state shown in FIG. It is a plane extending to. The end face 70b does not have to be flat.

Slits 70c extending in the axial direction with a substantially constant width are provided at the central portion of the detent member 70 in the width direction in the mounted state shown in FIG. 9, and slits 70c are provided at both ends in the longitudinal direction of the slit 70c. A through hole 70d that is larger than the width of the above is provided. In the present embodiment, the slit 70c and the two through holes 70d form one large through hole.

Further, the detent member 70 has two bases 71L and 71R and two arms 72T and 72B.

The two bases 71L and 71R are provided on both sides in the circumferential direction via the slits 70c. In other words, the two bases 71L and 71R are aligned in the circumferential direction through the slit 70c. Further, the two bases 71L and 71R are located between the two through holes 70d. The two bases 71L and 71R have a substantially constant width in the circumferential direction and a substantially constant height in the radial direction, respectively, and extend along the axial direction. In the free state, the two bases 71L and 71R each have a flat rectangular parallelepiped shape. Further, in the mounted state, the cross-sectional shapes of the bases 71L and 71R that are orthogonal to the axial direction are arcuate along the outer peripheral surface 40a and the inner peripheral surface 11d2. In the present embodiment, the base 71L and the base 71R have the same shape, but the shape is not limited to such a shape. Further, the cross-sectional shapes of the bases 71L and 71R that are orthogonal to the axial direction may be arcuate along the outer peripheral surface 40a and the inner peripheral surface 11d2 in the free state.

The base 71L adjacent to the second circumferential direction Dp2 with respect to the slit 70c has an end surface 71a1 of the first circumferential direction Dp1, and the base 71R adjacent to the first circumferential direction Dp1 with respect to the slit 70c has the second circumferential direction. It has an end face 71a2 of Dp2. The end face 71a1 faces the first circumferential direction Dp1 with a gap g between the end face 71a2 and the slit 70c. Further, the end face 71a2 faces the second circumferential direction Dp2 and faces with a gap g between the end face 71a1 and the slit 70c.

The arm 72T is provided in the first axial direction between the end of the base 71L in the second circumferential direction Dp2 and the first axial direction Da1 and the end of the base 71R in the first circumferential direction Dp1 and the first axial direction Da1. It extends in a convex arch shape on Da1. The other arm 72B is located between the end of the base 71L in the second circumferential direction Dp2 and the second axial direction Da2 and the end of the base 71R in the first circumferential direction Dp1 and the second axial direction Da2. It extends in a convex arch shape in the biaxial direction Da2.

The anti-rotation member 70 can be made of an elastic material, for example, an elastomer or a synthetic resin material. As an example, the detent member 70 is made of, for example, a polyamide synthetic resin.

Further, the detent member 70 can be made of, for example, a material having a thermal deformation temperature of 60 ° C. or higher.

In such a configuration, in FIG. 9, the direction in which the end surface 11f1 of the first stopper 11g1 and the end surface 40b2 of the protrusion 40b approach each other at least one of the casing 11 having the first stopper 11g1 and the gear assembly 40 having the protrusion 40b. When the torque of the above is applied, as shown in FIG. 10, the arms 72T and 72B are elastically deformed so as to be elastically sharply curved, and accordingly, the end face 71a1 of the base 71L and the end face 71a2 of the base 71R are formed. At the end, the gap g between the base 71L and the base 71R disappears. In such a state, the bases 71L and 71R intervene and support the end face 11f1 and the end face 40b2 to prevent the first stopper 11g1 and the protrusion 40b from coming closer than in the state shown in FIG. That is, the bases 71L and 71R are examples of movement limiting portions, and the arms 72T and 72B are examples of elastically deforming portions. Further, the end face 11f1 is an example of the first end face, the end face 40b2 is an example of the second end face, the end face 71a1 is an example of the third end face, and the end face 71a2 is an example of the fourth end face.

The end faces 11f1, 11f2 of the stopper 11g, the end faces 70b of the detent member 70, and the end faces 40b1, 40b2 of the protrusion 40b, respectively, need only be able to restrict the contact target from moving in the circumferential direction of the rotation center Ax3. Therefore, the end faces 11f1, 71a1, 71a2 and the end faces 40b1 need only intersect with the circumferential direction, and need not be orthogonal to the circumferential direction, and may not be flat. Further, the end faces 11f1, 71a1, 71a2 and the end faces 40b1 do not need to be continuously extended, and may have an intermittent configuration. Each end face may also be referred to as an end.

As described above, in the present embodiment, the detent member 70 is interposed between the end face 11f1 (first end face) and the end face 40b2 (second end face), and the two arms 72T. , 72B (elastic deformation part) and two bases 71L, 71R (movement restriction part). When the end faces 11f1 and the end faces 40b2 approach each other in the circumferential direction, the arms 72T and 72B can be elastically deformed as the end faces 11f1 and the end faces 40b2 approach each other until the gap g is closed. Further, in a state where the gap g is eliminated, two bases 71L and 71R arranged in contact with each other in the circumferential direction are interposed and supported between the end face 11f1 and the end face 40b2 to support the casing 11 (housing 10) having the end face 11f1. ) And the gear assembly 40 having the end face 40b2, the relative movement in the circumferential direction is restricted. That is, in the present embodiment, for example, the effect of reducing sound and vibration due to the elastic deformation of the arms 72T and 72B can be obtained until the gap g is clogged, and after the gap g is eliminated, the gear assembly 40 and the casing can be obtained. The relative movement with the eleven is restricted, and the decrease in the transmission efficiency of rotation can be suppressed. Therefore, according to such a configuration, for example, sound and vibration can be reduced, and it is possible to suppress a significant decrease in rotation transmission efficiency.

Further, in the present embodiment, the gap g is provided between the end surface 71a1 (third end surface) of the base 71L of the detent member 70 and the end surface 71a2 (fourth end surface) of the base 71R. According to such a configuration, for example, the size of the gap g can be set more accurately by setting the specifications of the detent member 70 and manufacturing control.

Further, in the present embodiment, the end face 70a (end portion) has a tapered shape. According to such a configuration, for example, the detent member 70 is guided from the introduction port Ip to the movement path by the tapered shape of the end face 70a, so that the operator attaches the detent member 70 more easily or more quickly. be able to.

Further, in the present embodiment, the detent member 70 is made of a polyamide synthetic resin material. According to such a configuration, for example, a detent member 70 having high toughness, high impact resistance, and elasticity that can be elastically deformed can be produced more easily and at a lower cost.

Further, in the present embodiment, the detent member 70 can be made of, for example, a material having a thermal deformation temperature of 60 ° C. or higher. According to such a configuration, for example, the detent member 70 is less likely to be thermally deformed depending on the environmental temperature (for example, 50 ° C. or less) at the portion where the detent member 70 is provided in the brake 1 for a vehicle. As a result, the reliability of the detent member 70 becomes even higher.

Further, in the present embodiment, the detent member 70 is press-fitted between the end face 11f1 (first end face) and the end face 40b2 (second end face). According to such a configuration, for example, the detent member 70 is difficult to come off from between the end face 11f1 and the end face 40b2, so that there is an advantage that the structure for suppressing the coming off can be omitted or simplified. ..

Further, in the present embodiment, the detent member 70 is, for example, plane-symmetric with respect to the virtual plane perpendicular to the longitudinal direction and plane-symmetric with respect to the virtual plane perpendicular to the lateral direction in the free state. Moreover, it may be plane-symmetric with respect to a virtual plane perpendicular to the thickness direction. In this case, for example, the detent member 70 can be mounted even when its postures are switched in the longitudinal direction, the lateral direction, and the thickness direction, respectively, so that the detent member 70 can be mounted. Efficiency tends to increase.

Further, in the present embodiment, the bases 71L and 71R (movement limiting portions) are made of an elastic material. With such a configuration, even if the movement is suppressed by the bases 71L and 71R, it is possible to obtain a certain degree of effect of reducing sound and vibration due to the elasticity of the bases 71L and 71R.

[First Modified Example of Embodiment]
FIG. 11 shows the free state of the detent member 70A of this modified example, FIG. 12 shows the mounted state in which the gear assembly 40 and the detent member 70A are attached to the casing 11, and FIG. 13 shows the gear assembly 40 and the mounted state. It shows a state in which the detent member 70A is elastically compressed by the relative movement around the rotation center Ax3 with the casing 11.

The detent member 70A of this modification has the same components as the detent member 70 of the above embodiment. Further, the detent member 70A is made of an elastic material such as an elastomer or a synthetic resin material. However, in this modification, there is no through hole 70d on the lower side of each drawing, the slit 70c extends to the end 70a1 in the second axial direction Da2, the end 70a1 is divided into two, and the detent member 70A is It has a substantially U-shaped shape. The bases 71R and 71L on both sides of the slit 70c are located between the through hole 70d and the end 70a1 and do not have the arm 72B.

Also in this modification, the detent member 70A is press-fitted between the first stopper 11g1 and the protrusion 40b. Therefore, the width Wf (FIG. 11) along the lateral direction of the detent member 70A in the free state is larger than the width Ws (FIG. 12) along the circumferential direction in the mounted state.

Even in such a configuration, in at least one of the casing 11 having the first stopper 11g1 and the gear assembly 40 having the protrusion 40b, in FIG. 12, the end face 11f1 of the first stopper 11g1 and the end face 40b2 of the protrusion 40b When torque acts in the direction of approaching each other, as shown in FIG. 13, the arm 72T elastically deforms so as to be elastically sharply curved, and accordingly, the end faces 71a1 of the base 71L and the end faces of the base 71R. The 71a2 abuts and the gap g between the base 71L and the base 71R disappears. In such a state, the bases 71L and 71R intervene and support the end face 11f1 and the end face 40b2 to prevent the first stopper 11g1 and the protrusion 40b from coming closer than in the state shown in FIG. Therefore, even with this modification, the same action and effect based on the same configuration as that of the above embodiment can be obtained.

[Second variant of the embodiment]
FIG. 14 shows the free state of the detent member 70B of this modified example, FIG. 15 shows the mounted state in which the gear assembly 40 and the detent member 70B are attached to the casing 11, and FIG. 16 shows the gear assembly 40 and the mounted state. It shows a state in which the detent member 70B is elastically compressed by the relative movement around the rotation center Ax3 with the casing 11.

The detent member 70B of this modified example has the same components as the detent members 70 and 70A of the above-described embodiment and the modified example. Further, the detent member 70B is made of an elastic material such as an elastomer or a synthetic resin material. However, in this modification, there is no slit 70c between the two through holes 70d, and one base 71 is provided instead of the two bases 71R and 71L. Further, the end surface 70b of the portion where the base 71 is provided is recessed inward in the width direction, and the width of the portion where the base 71 is provided is narrower than the maximum width (width Wf) of the detent member 70B.

Also in this modification, the detent member 70B is press-fitted between the first stopper 11g1 and the protrusion 40b. Therefore, the width Wf (FIG. 14) along the lateral direction of the detent member 70B in the free state is larger than the width Ws (FIG. 15) along the circumferential direction in the mounted state.

As shown in FIG. 15, in the mounted state of the detent member 70B, there is a gap g1 between the end surface 70b of the base 71 and the end surface 11f1 of the first stopper 11g1, and the end surface 70b of the base 71 and the protrusion 40b There is a gap g2 between the end face 40b2 and the end surface 40b2. In this modification, as an example, the width of the gap g1 along the circumferential direction and the width of the gap g2 along the circumferential direction are substantially the same, and the sum of the widths of the gap g1 and the gap g2 is the sum. The value is set to substantially the same value as the gap g of the above-described embodiment or modification, for example. The end face 70b is an example of the fifth end face.

In such a configuration, at least one of the casing 11 having the first stopper 11g1 and the gear assembly 40 having the protrusion 40b has an end surface 11f1 of the first stopper 11g1 and an end surface 40b2 of the protrusion 40b in FIG. When torques in the directions of approaching each other act, as shown in FIG. 16, the arms 72T and 72B are elastically deformed so as to be elastically sharply curved, and accordingly, the end face 70b facing the end face 11f1 and the end face thereof. 11f1 abuts and the gap g1 disappears, and the end face 70b facing the end face 40b2 and the end face 40b2 abut and the gap g2 disappears. In such a state, the base 71 is interposed and supported between the end face 11f1 and the end face 40b2 to prevent the first stopper 11g1 and the protrusion 40b from coming closer than in the state shown in FIG. Therefore, even with this modification, the same action and effect based on the same configuration as that of the above embodiment can be obtained. In addition, only one of the gap g1 and the gap g2 may be provided, or the size of the gap g1 and the size of the gap g2 may be different from each other.

[Third variant of the embodiment]
FIG. 17 shows the free state of the detent member 70C of this modified example, FIG. 18 shows the mounted state in which the gear assembly 40 and the detent member 70C are attached to the casing 11, and FIG. 19 shows the gear assembly 40 and the mounted state. It shows a state in which the detent member 70C is elastically compressed by the relative movement around the rotation center Ax3 with the casing 11. Further, FIG. 20 is a side view of the detent member 70C in the state of FIG. 19 as viewed in the circumferential direction (arrow D2 of FIG. 19).

The detent member 70C of the present modification basically has the same configuration as the detent member 70A of the first modification. That is, even in this modification, there is no lower through hole 70d in each drawing, the end portion 70a1 in the second axial direction Da2 is divided, and the detent member 70C has a substantially U-shaped shape. Further, there is no arm 72B supported at both ends, and the arm 72B is divided into two.

However, in this modification, the detent member 70C is made of a metal material such as an iron-based metal or an alumium alloy. Further, the anti-rotation member 70C can be made from a metal plate-shaped member as a whole by press molding or bending molding. The arm 72T, the two end walls 70e constituting the end face 70b, and the two divided arms 72B1 and 72B2 are made by bending a series of strip-shaped members in a substantially U-shape. The arm 72T, the two end walls 70e, and the two arms 72B1 and 72B2 all extend at substantially constant heights in the radial direction, and extend to the outer peripheral surface 40a of the gear assembly 40 and the inner peripheral surface 11d2 of the recess 11d of the casing 11. It extends while bending along. Further, from one of the radial inner and radial outer edges of the two end walls 70e, the protruding walls 70f constituting the bases 71L and 71R extend so as to approach each other along the circumferential direction, respectively.

Also in this modification, the detent member 70C is press-fitted between the first stopper 11g1 and the protrusion 40b. Therefore, the width Wf (FIG. 17) along the lateral direction of the detent member 70C in the free state is larger than the width Ws (FIG. 18) along the circumferential direction in the mounted state.

Even in such a configuration, in at least one of the casing 11 having the first stopper 11g1 and the gear assembly 40 having the protrusion 40b, in FIG. 18, the end face 11f1 of the first stopper 11g1 and the end face 40b2 of the protrusion 40b When a torque is applied in the direction of approaching each other, the arm 72T is elastically deformed so as to be elastically sharply curved, and accordingly, the tip of the base 71L and the tip of the base 71R Hits and the gap g between the base 71L and the base 71R disappears. In such a state, the bases 71L and 71R intervene and support the end face 11f1 and the end face 40b2 to prevent the first stopper 11g1 and the protrusion 40b from coming closer than in the state shown in FIG. Therefore, even with this modification, the same action and effect based on the same configuration as that of the above embodiment can be obtained.

Here, in this modification, as shown in FIG. 20, both ends of the tip of the protruding wall 70f in the axial direction are cut up in the radial direction. Then, by making the cut-up position (base end position) and the cut-up angle different between the base 71L and the base 71R, the protruding wall 70f of the base 71L and the protruding wall 70f of the base 71R are the portions C1 when viewed in the circumferential direction. Are configured to intersect each other. As a result, even when these two protruding walls 70f are slightly displaced in the radial direction, a state in which the cut-up portions of the protruding walls 70f intersect with each other can be obtained between the base 71L and the base 71R. The two protruding walls 70f, that is, the bases 71L and 71R, abut against each other and can function as a movement restricting portion.

[Fourth modification of the embodiment]
21 shows the free state of the detent member 70D of this modified example, FIG. 22 shows the mounted state of the detent member 70D, and FIG. 23 shows the circumferential direction of the detent member 70D in the state of FIG. 22 (FIG. 21). It is a side view as seen in the arrow D3) of 22.

The detent member 70D of the present modification basically has the same configuration as the detent member 70A of the first modification. That is, also in this modification, the end portion 70a1 in the second axial direction Da2 is divided, and the detent member 70D has a substantially U-shaped shape.

In this modification, the detent member 70D is made of a metal material such as an iron-based metal or an alumium alloy. Further, the anti-rotation member 70D can be made from a metal plate-shaped member as a whole by press molding or bending molding.

Further, in this modification, it is made by bending a series of strip-shaped members into a substantially U-shape. However, in this modification, the arm-shaped bases 71L and 71R provided at the end portions in the longitudinal direction of the strip-shaped members facing each other with a gap g in the circumferential direction function as the movement limiting portion. At the intermediate portion between the two bases 71L and 71R, the arm 72T extends at a substantially constant height in the radial direction and bends along the outer peripheral surface 40a of the gear assembly 40 and the inner peripheral surface 11d2 of the recess 11d of the casing 11. It is extending while.

Also in this modification, the detent member 70D is press-fitted between the first stopper 11g1 and the protrusion 40b. Therefore, the width Wf (FIG. 21) along the lateral direction of the detent member 70D in the free state is larger than the width Ws (FIG. 22) along the circumferential direction in the mounted state.

Even in such a configuration, in the state of FIG. 22, at least one of the casing 11 having the first stopper 11g1 and the gear assembly 40 having the protrusion 40b has the end faces 11f1 and the protrusion 40b of the first stopper 11g1. When a torque acts in the direction in which the end faces 40b2 approach each other, the arm 72T is elastically deformed so as to be elastically sharply curved, and accordingly, the end face 71a1 of the base 71L and the end face 71a2 of the base 71R abut each other. The gap g between the end face 71a1 and the end face 71a2 is eliminated. In such a state, the bases 71L and 71R intervene and support the end face 11f1 and the end face 40b2 to prevent the first stopper 11g1 and the protrusion 40b from coming closer than in the state shown in FIG. Therefore, even with this modification, the same action and effect based on the same configuration as that of the above embodiment can be obtained.

Here, in the present modification, as shown in FIGS. 21 and 22, the end faces 71a1 and the end faces 71a2 are twisted in opposite directions to each other, whereby, as shown in FIG. 23, when viewed in the circumferential direction, A portion C2 where the end face 71a1 and the end face 71a2 intersect is generated. With such a configuration, even if the two end faces 71a1 and 71a2 are slightly displaced in the axial direction, a portion C2 where the end face 71a1 and the end face 71a2 intersect is generated when viewed in the circumferential direction, so that the end face 71a1 and the end face The 71a2 abut against each other, and the bases 71L and 71R function as movement restrictors.

[Fifth variant of the embodiment]
FIG. 24 shows a free state of the detent member 70E of this modified example. The detent member 70E of the present modification basically has the same configuration as the detent member 70D of the fourth modification. Also in this modification, the detent member 70E is made of a metal material such as an iron-based metal or an alumium alloy. Further, the anti-rotation member 70E can be made from a metal plate-shaped member as a whole by press molding or bending molding.

However, in this modification, the configuration of the end face 71a1 is different from that of the fourth modification. In this modification, the strip-shaped member is further bent in a substantially U shape along the inner peripheral surface 11d2 of the casing 11 and the outer peripheral surface 40a of the gear assembly 40 at each end surface 71a1, and the first circumference of the base 71L on the left side of FIG. 24 is formed. The end surface 71a1 as the side surface of the direction Dp1 and the end surface 71a2 as the side surface of the second circumferential direction Dp2 of the base 71R on the right side of FIG. 24 face each other with a gap g. With such a configuration, even if the two end faces 71a1 and 71a2 are slightly displaced in the axial direction, the two end faces 71a1 and 71a2 abut against each other, and the bases 71L and 71R function as movement limiting portions.

Although the embodiments of the present invention have been exemplified above, the above-described embodiments and modifications are merely examples, and the scope of the invention is not intended to be limited. The above-described embodiment and modification can be implemented in various other forms, and various omissions, replacements, combinations, and changes can be made without departing from the gist of the invention. In addition, specifications such as each configuration and shape (structure, type, direction, type, size, length, width, thickness, height, number, arrangement, position, material, etc.) are changed as appropriate. Can be carried out.

1 ... (for vehicle) brake, 11 ... casing (housing), 11d2 ... inner peripheral surface, 11f1 ... end surface (first end surface), 20 ... motor, 21 ... shaft (rotor), 40 ... gear assembly (reduction device), 40a ... outer peripheral surface, 40b2 ... end surface (second end surface), 43 ... first sun gear (gear), 44c ... first pinion gear (gear), 44d ... second sun gear (gear), 45 ... ring gear (gear), 47c ... Second pinion gear (gear), 50 ... rotary linear motion conversion mechanism, 51 ... rotary member, 52 ... linear motion member, 70, 70A to 70E ... anti-rotation member, 70a ... end face (end), 70b ... end face (fifth) End face), 70f ... Projection wall (movement restriction part), 71, 71L, 71R ... Base (movement restriction part), 71a1 ... End face (third end face), 71a2 ... End face (fourth end face), 72T, 72B ... Arm (end face) Elastic deformation part), 204 ... Pad (braking member), Dp1 ... First circumferential direction, Dp2 ... Second circumferential direction, g, g1, g2 ... Gap.

Claims (6)

A motor with a rotating rotor and
A speed reducer having a plurality of gears that rotate in conjunction with the rotor,
A housing for accommodating the speed reducer and
A detent member that limits the relative rotation of the speed reducer with respect to the housing.
A rotary linear motion conversion mechanism having a rotary member that rotates in conjunction with the gear of the reduction gear and a linear motion member that linearly rotates in response to the rotation of the rotary member.
A braking member that switches between a braking state in which the wheel is braked by moving in response to the linear motion of the linear motion member and a release state in which the wheel is released from braking.
With
The housing has an inner peripheral surface and a first end surface adjacent to the inner peripheral surface and facing the first circumferential direction of the inner peripheral surface.
The speed reducer has an outer peripheral surface facing the inner peripheral surface, a second peripheral surface adjacent to the outer peripheral surface, separated from the first one end surface in the first circumferential direction, and facing a second circumferential direction opposite to the first circumferential direction. It has two end faces, and is housed in the housing in a state in which the second end face is restricted from being separated from the first end face by a predetermined interval or more in the first circumferential direction.
The detent member is interposed between the first end surface and the second end surface in a state of being in contact with the first end surface and the second end surface, and the first end surface and the second end surface are relatively relative to each other. An elastically deformed portion that elastically deforms as it approaches and the first end surface and the second end surface are interposed with a gap along the first circumferential direction, and the first end surface is placed on the second end surface. When the gap is eliminated, the first end surface is relatively close to the second end surface by interposing and supporting the first end surface and the second end surface. Brake for vehicles, which has a movement restriction part that limits the movement. The vehicle according to claim 1, wherein the gap is provided between a third end surface provided on the detent member and a fourth end surface provided on the detent member and facing the third end surface. Brake for. A claim that the gap is provided between at least one of the first end surface and the second end surface and a fifth end surface facing the one surface and provided on the detent member. The vehicle brake according to 1. The vehicle brake according to any one of claims 1 to 3, wherein the end portion of the detent member in the axial direction of the inner peripheral surface has a tapered shape. The vehicle brake according to any one of claims 1 to 4, wherein the detent member is made of a material having a thermal deformation temperature of 60 ° C. or higher. The vehicle brake according to any one of claims 1 to 5, wherein the detent member is made of a polyamide synthetic resin material.