JP2008296843A - Vehicular parking brake device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vehicular parking brake device capable of smoothly distributing tensile force to an inner wire connected to both parking brakes and preventing operational sound from becoming higher because of aging. <P>SOLUTION: Preparing sun gears 21, 21C, annular internal gears 23, 23B, 23C, carriers 25, 25C, and planet gear mechanisms 20, 20C composed of planet gears 22, 22C eccentric to the carrier and supported to freely rotate, turning force is given to the sun gears by electric motors 15, 15C for generating turning force in the annular internal gears and the carriers. The turning force generated in the carriers is converted to the tensile force of first brake wires 41, 41B, 41C by first conversion mechanisms 30, 30B, 30C. The turning force generated in the annular internal gears is converted to the tensile force of second brake wires 46, 46B, 46C by second conversion mechanisms 35, 35B, 35C. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a vehicle parking brake device that uses an electric motor as a power source to place a parking brake in a braking state by rotating the electric motor in the forward direction and release the parking brake by rotating in the reverse direction.

  As an electric parking brake device in which an equalizer is provided in an operation force transmission path connecting the operation unit of the parking brake and each wheel so that the braking force of each wheel becomes equal, there is a technology disclosed in Patent Document 1, for example. The equalizer of Patent Document 1 is of the balance type, and the central portion of a lever-like equalizer is pivotally supported by a nut engaged with a screw shaft rotated by an electric motor, and is connected to a parking brake. One end of each inner wire is connected to both ends of the equalizer. If the screw shaft is rotated in the forward direction by the electric motor, the equalizer is attracted by the nut and each parking brake is operated with the same force, and if the screw shaft is rotated in the opposite direction, the equalizer is returned to each parking brake. Is released.

Moreover, as a parking brake apparatus provided with the equalizer of the format different from patent document 1, there exists the technique disclosed by FIGS. 5-9 of patent document 2, for example. In this technology, the screw shaft that slidably passes coaxially through the wheel rotated by the electric motor has a square cross section at the center and is rotated together with the wheel, and the right and left screw portions on both sides of the screw shaft are rotated. One end of each inner wire is connected to each nut that is screw-engaged and restricted in rotation, and the other end of each inner wire is connected to each parking brake. When the wheel is rotated in one direction by the electric motor, the screw shaft that is slidable with respect to the wheel is also rotated, the nuts are attracted to each other, the parking brakes are operated with equal force, and the wheel is rotated in the opposite direction. Then, each nut is returned and each parking brake is released. In addition, there is a technique disclosed in Patent Document 3 as a technique similar to Patent Document 2. In this technique, each end portion of a spline shaft and a spindle that are screw-engaged with each other is connected to one end of each inner wire, and The end is connected to each parking brake, and the spline shaft is rotated by a motor through a spline fitting gear.
JP 2007-092601 (paragraphs [0017] to [0018], FIG. 1). JP-A-08-295210 (paragraphs [0024] to [0038], FIGS. 5 to 9). JP-T-2001-513179 (page 8, line 21 to page 9, line 26, FIGS. 2 to 5).

  In the technique of Patent Document 1 described above, if the wear of each parking brake or the elongation of each inner wire is not the same, the inclination angle of the balance with respect to the screw shaft becomes excessive, and there is a problem that it cannot function as an equalizer. In the equalizer described in Patent Document 2, an equalizer action is performed in which the central portion of the screw shaft slides in the axial direction with respect to the wheel so that the magnitude of the force applied to both inner wires is the same. However, since the screw shaft slides with respect to the wheel in a state in which rotational torque is applied from the wheel to the screw shaft, the sliding frictional force in the axial direction of the sliding portion between the screw shaft central portion and the wheel increases, and the equalizer action In addition, the sliding portion between the screw shaft central portion and the wheel is worn with the passage of time of use, and there is a problem that the sliding portion becomes loose and the operating noise becomes high. In the technique of Patent Document 3, as in Patent Document 2, the equalizer action is insufficient due to the frictional force in the axial direction between the gear rotated by the motor and the spline shaft, and the spline fitting portion is worn. Increases the operating noise.

  An object of the present invention is to provide a vehicle parking brake device that can smoothly distribute a tensile force to an inner wire connected to both parking brakes and can prevent an increase in operating noise due to changes over time. .

  In order to solve the above-mentioned problem, the structural feature of the invention according to claim 1 is that a housing (10) and a sun gear (21, 21) supported in the housing (10) so as to be coaxial with each other and relatively rotatable. 21C), an annular internal gear (23, 23B, 23C), a carrier (25, 25C), and a support shaft (24, 24C) provided eccentrically on the carrier and rotatably supported by the sun gear A planetary gear mechanism (20, 20B, 20C) comprising planetary gears (22, 22C) meshed with both of the annular internal gears and the annular internal gear by applying a rotational force to the sun gears (21, 21C). (23, 23B, 23C) and the electric motor (15, 15C) that generates the rotational force on the carrier (25, 25C), and the first and second parking brakes (50, 50) provided on different wheels. 1) The first brake wire (41) and the second brake wire (46) that generate the braking force in 1) and the rotational force generated in the carrier (25, 25C) are converted into the tensile force of the first brake wire (41). And a second conversion mechanism (30, 30B, 30C) that converts the rotational force generated in the annular internal gear (23, 23B, 23C) into a tensile force of the second brake wire (46). 35, 35B, 35C).

  The structural feature of the invention according to claim 2 is that in the parking brake device for a vehicle according to claim 1, each conversion of the first and second conversion mechanisms (30, 30B, 30C, 35, 35B, 35C). The characteristic is that when the brake wire (41, 46) is pulled by the electric motor (15) and the parking brake (50, 51) is in a braking state, the tensile force distributed to each brake wire is the first. It is set to the characteristic which generates the braking force equal to the 1st and 2nd parking brakes (50, 51).

  The structural feature of the invention according to claim 3 is that, in the vehicle parking brake device according to claim 2, the conversion mechanisms (30, 30B, 35, 35B) are male screw members (30, 30B, 35, 35B) that are screwed into each other in a freely rotatable manner. 31, 36, 32 B, 37 B) and female screw members (32, 37, 31 B, 36 B), respectively, and each conversion characteristic is set by making the lead of each screw pair different. .

  The structural feature of the invention according to claim 4 is the parking brake device for a vehicle according to claim 2, wherein the first conversion mechanism (30, 30B) is a male screw member (31, 32B) into which the first conversion mechanism (30, 30B) is screwed so as to be rotatable. ) And a female screw member (32, 31B), and the second conversion mechanism (35, 35B) is a pair of gears (23a, 38, 23Bb, 38B)) that mesh with each other, Shift of the pair of gears (23a, 38, 23Bb, 38B) having a second screw pair consisting of a male screw member (36, 37B) and a female screw member (37, 36B) to be screwed movably and meshing with each other That is, the conversion characteristics of the respective conversion mechanisms (30, 30B, 35, 35B) are set by adjusting the ratio.

  The structural feature of the invention according to claim 5 is that the housing (10), the sun gear (21) and the annular internal gear (23) supported in the housing (10) coaxially with each other and relatively rotatable. ) And a carrier (25), and a planetary gear (22) that is rotatably supported by a support shaft (24) provided eccentrically on the carrier and meshes with both the sun gear and the annular internal gear. A planetary gear mechanism (20), an electric motor (15) that applies rotational force to the sun gear (21) to generate rotational force on the annular internal gear (23) and the carrier (25), and different wheels A first brake wire (41) and a second brake wire (46) for generating a braking force on the first and second parking brakes (50, 51) provided, and the carrier (25) are coaxially integrated. A first screw shaft (31) that is connected and protrudes on the opposite side of the electric motor (15), and the housing (10) is concentrically slidable in the axial direction and constrained to rotate. And a female screw portion formed at one end includes a first screw pair made of a first sliding member (32) screw-engaged with the first screw shaft, and a rotational force generated in the carrier (25). A first conversion mechanism (30) for converting the tensile force of the first brake wire (41), one end of which is connected to the other end of the first sliding member in the axial direction; the first screw shaft (31); A second external gear (not shown) that is supported by the housing (10) so as to be rotatable about a parallel axis and is meshed with a first external gear (23a) that is coaxially formed integrally with the annular internal gear (23). 38) and the second external gear are coaxially and integrally connected. A second screw shaft (36) projecting to the opposite side of the first screw shaft, and an end portion supported coaxially with the second screw shaft so as to be axially slidable and rotationally restrained and supported by the housing. And a second screw pair formed by a second sliding member (37) screw-engaged with the second screw shaft, and a rotational force generated in the annular internal gear is generated by the second sliding member. The first and second external gears which are provided with a second conversion mechanism (35) for converting into a tensile force of the second brake wire (46) whose one end is connected to the other end of the member from the axial direction and meshed with each other. By adjusting the transmission ratio of (23a, 38), the conversion characteristics of the first and second conversion mechanisms (30, 35) are pulled by the brake wires (41, 46) by the electric motor (15). The parking brake (50, 51) is braked In this state, the tensile force distributed to each brake wire is set to a characteristic that generates a braking force equal to the first and second parking brakes (50, 51).

  The structural feature of the invention according to claim 6 is that the housing (10), the sun gear (21) and the annular internal gear (23) supported in the housing (10) coaxially with each other and relatively rotatable. ) And a carrier (25), and a planetary gear (22) that is rotatably supported by a support shaft (24) provided eccentrically on the carrier and meshes with both the sun gear and the annular internal gear. A planetary gear mechanism (20), an electric motor (15) that applies rotational force to the sun gear (21) to generate rotational force on the annular internal gear (23) and the carrier (25), and different wheels A first brake wire (41) and a second brake wire (46) for generating a braking force on the first and second parking brakes (50, 51) provided, and the carrier (25) are coaxially integrated. A first screw shaft (31) that is connected and protrudes on the opposite side of the electric motor (15), and the housing (10) is concentrically slidable in the axial direction and constrained to rotate. A female screw portion supported at one end and provided with a first screw pair made of a first sliding member (32) screw-engaged with the first screw shaft includes a rotational force generated in the carrier. A first conversion mechanism (30) for converting the tensile force of the first brake wire (41) having one end connected in the axial direction to the other end of the sliding member, and an axis parallel to the first screw shaft (31) A second external gear (38) meshed with a first external gear (23a) that is supported by the housing (10) so as to be rotatable around and is coaxially formed integrally with the annular internal gear (23); The front is connected to the second external gear coaxially and integrally. A second screw shaft (36) projecting on the same side as the first screw shaft, and axially slidable and concentric with the second screw shaft and supported by the housing and formed at one end. A second screw pair consisting of a second sliding member (37) screw-engaged with the second screw shaft, and the rotational force generated in the annular internal gear other than the second sliding member. The first and second external gears (23a, 23a, 23) provided with a second conversion mechanism (35) for converting into a tensile force of the second brake wire (46) whose one end is connected to the end from the axial direction. 38), the respective conversion characteristics of the first and second conversion mechanisms (30, 35) can be obtained by pulling the brake wires (41, 46) by the electric motor (15). The parking brake (50, 51) is in the braking state. When this is done, the tensile force distributed to each brake wire is set to a characteristic that generates a braking force equal to the first and second parking brakes (50, 51).

  A structural feature of the invention according to claim 7 is the parking brake device for a vehicle according to claim 5 or 6, wherein the conversion characteristics of the conversion mechanisms (30, 35) are the first and second conversion characteristics. In addition to or instead of adjusting the gear ratio of the external gears (23a, 38), the conversion characteristics of the conversion mechanisms are set by making the leads of the screw pairs different.

  The structural feature of the invention according to claim 8 is the vehicle parking brake device according to any one of claims 5 to 7, wherein the first and second screw shafts (31, 36) are Instead of the first and second screw cylinders (31B, 36B) coaxially and integrally connected to the carrier (25) and the second external gear (38), respectively, the first and second sliding members ( 32, 37) are axially slidable on the same axis as the first and second screw cylinders and supported by the housing (10) so as to be slidable in the axial direction. The first and second sliding members (32B, 37B) that are screw-engaged with the second screw cylinder are respectively replaced.

  The structural feature of the invention according to claim 9 is the vehicle parking brake device according to any one of claims 5 to 8, wherein the annular internal gear (23B) has a small diameter on one side in the axial direction. The cylindrical portion (23Bb) is integrally formed on the same axis, and the first external gear (23Ba) is formed on the outer periphery of the cylindrical portion.

  A structural feature of the invention according to claim 10 is the parking brake device for a vehicle according to any one of claims 2 to 9, wherein the first and second conversion mechanisms (30, 30B, 30C, 35, 35B, 35C), the first and first conversion characteristics when the brake wire (41, 46) is pulled by the electric motor (15) to bring the parking brake (50, 51) into a braking state. That is, the characteristic is set to distribute the tensile force equal to each brake wire (41, 46) so that the brake force equal to the two parking brakes (50, 51) is generated.

It is.

  According to the first aspect of the present invention, the planetary gear mechanism has an equalizer function, and the rotational force applied to the sun gear of the planetary gear mechanism is distributed at a predetermined ratio and transmitted to the carrier and the annular internal gear. The transmitted rotational forces are converted into the tensile forces of the first brake wire and the second brake wire by the first conversion mechanism and the second conversion mechanism, and each parking brake is operated. As a result, even if the lengths of the two brake wires are considerably different, the rotational force applied to the sun gear of the planetary gear mechanism has a desired ratio to the first brake wire and the second brake wire via the carrier and the annular internal gear. In addition, it is possible to prevent the operating sound from becoming high due to backlash caused by the change over time.

  According to the invention of claim 2, in addition to the effect of the invention of claim 1, the conversion characteristics of the first and second conversion mechanisms are such that the tensile force distributed to each brake wire is the first and second parking brakes. Therefore, the braking force generated on each wheel during parking can be made equal.

  According to the invention of claim 3, since the lead of each screw pair of each conversion mechanism is made different, the rotational force applied to the sun gear of the planetary gear mechanism is transmitted via the carrier, the annular internal gear and each conversion mechanism. Thus, it can be distributed and transmitted to the first brake wire and the second brake wire at a desired ratio.

  According to the invention of claim 4, the first conversion mechanism has a first screw pair, and the second conversion mechanism has a pair of gears and a second screw pair that mesh with each other. By adjusting the gear ratio, the rotational force applied to the sun gear of the planetary gear mechanism is distributed to the first brake wire and the second brake wire at a desired ratio via the carrier, the annular internal gear and each conversion mechanism. Can communicate.

  According to the fifth aspect of the invention, in addition to the effect of the second aspect of the invention, the second screw shaft of the second conversion mechanism is protruded on the opposite side of the first screw shaft of the first conversion mechanism. One brake wire can be pulled out from each side.

  According to the invention of claim 6, in addition to the effect of the invention of claim 2, the second screw shaft of the second conversion mechanism protrudes on the same side as the first screw shaft of the first conversion mechanism. Two brake wires can be pulled out from the same side.

  According to the seventh aspect of the present invention, in addition to or instead of adjusting the gear ratio of the first and second external gears of the second conversion mechanism, each screw pair of the first and second conversion mechanisms. The rotational force applied to the sun gear of the planetary gear mechanism is distributed to the first brake wire and the second brake wire at a desired ratio via the carrier, the annular internal gear and each conversion mechanism. Can communicate.

  According to the eighth aspect of the invention, the first and second screw shafts of the first and second conversion mechanisms are the first and second screws coaxially and integrally connected to the carrier and the second external gear. The first and second sliding members are replaced by cylinders, and the male and female screws formed at one end are supported by the housing and are slidable in the axial direction and coaxially with the first and second screw cylinders. Since the first and second sliding members are screw-engaged with the first and second screw cylinders, the rotational force applied to the sun gear of the planetary gear mechanism is converted into the carrier, the annular internal gear and each conversion. It can be distributed and transmitted to the first brake wire and the second brake wire in a desired ratio via the mechanism.

  According to the ninth aspect of the present invention, the first external gear is formed on the outer periphery of the small-diameter cylindrical portion integrally formed on one side in the axial direction of the annular internal gear, whereby the first screw shaft and By reducing the distance between the second screw shafts or between the first screw cylinder and the second screw cylinder, the vehicle parking brake device can be reduced in size.

  According to the invention which concerns on Claim 10, since the tensile force distributed to each brake wire becomes mutually equal, the parking brake of the same specification can be provided in each wheel.

  First, a first embodiment of a vehicle parking brake device according to the present invention will be described with reference to FIGS. In the first embodiment, as shown mainly in FIG. 1, a planetary gear mechanism 20 including a sun gear 21, an annular internal gear 23, a carrier 25, and three planetary gears 22, and the sun gear 21 are given a rotational force. Thus, the electric motor 15 for generating the rotational force on the annular internal gear 23 and the carrier 25, the first and second control cables 40 and 45, and the rotational force generated on the carrier 25 and the annular internal gear 23 are respectively the first and the first. 2 Consists of first and second conversion mechanisms 30 and 35 that convert the tensile force of the inner wires (brake wires) 41 and 46 of the control cables 40 and 45, and the housing 10 that covers and holds them.

  As shown in FIG. 1, the housing 10 of the first embodiment has a box shape having first and second partition walls 10 a and 10 b, and includes a plurality of parts integrally connected to each other. A planetary gear mechanism 20 is provided in the first chamber R1 between the partition walls 10a and 10b, and the first conversion is performed in the second chamber R2 opposite to the first chamber R1 across the first partition wall 10a. A mechanism 30 is provided, and a second conversion mechanism 35 and an electric motor 15 are provided in a third chamber R3 opposite to the first chamber R1 across the second partition wall 10b.

  Next, the planetary gear mechanism 20 will be described. A first screw shaft (first male screw member) 31 of the first conversion mechanism 30 passes through the first partition wall 10 a and is supported by a ball bearing 34. A carrier 25 of the planetary gear mechanism 20 is integrally formed coaxially at the tip of the first screw shaft 31 protruding into the first chamber R1. As shown in FIGS. 1 and 2, planetary gears 22 are rotatably supported on three support shafts 24 that are erected on the carrier 25 by the same distance from the rotation axis thereof and are erected at equal angular intervals. Yes. A one-way clutch 16 is mounted coaxially with the carrier 25 on the first chamber R1 side of the second partition wall 10b, and the sun gear 21 of the planetary gear mechanism 20 fixed to the output shaft 16a is meshed with each planetary gear 22. ing. The annular internal gear 23 of the planetary gear mechanism 20 is provided coaxially with the sun gear 21 and the carrier 25, and the internal gears on the inner periphery thereof mesh with the planetary gears 22. A first external gear 23a is formed. Each of the meshed gears in FIGS. 1 and 2 represents only the mesh pitch circle according to the simplified drawing method defined in JIS.

  An electric motor 15 is mounted coaxially with the one-way clutch 16 on the third chamber R3 side of the second partition wall 10b. The output shaft of the electric motor 15 is connected to the input shaft of the one-way clutch 16, and the one-way clutch 16 A sun gear 21 of the planetary gear mechanism 20 is coaxially fixed to the output shaft. For example, the one-way clutch 16 described in Patent Document 1 may be used, and the rotation of the one-way clutch 16 from the input shaft to the output shaft is transmitted in either the forward or reverse direction. The rotation toward the input shaft is prevented in both forward and reverse directions.

  The first conversion mechanism 30 includes the above-described first screw shaft 31 and the first support cylinder portion 11 that protrudes inward coaxially with the first screw shaft 31 from the outer wall of the housing 10 facing the first partition wall 10a. The first sliding member (first female screw member) 32 is supported. The first sliding member 32 is in the shape of a rectangular tube, and is supported by the square inner hole of the first supporting cylindrical portion 11 so that the rotation is restricted and slidable in the axial direction. The screw shaft 31 is screw-engaged. The first screw pair consisting of the first screw shaft 31 and the first sliding member 32 that are screw-engaged with each other is a right-hand thread. One end of the middle portion in the longitudinal direction of the first sliding member 32 that is the back side in the direction orthogonal to the paper surface in FIG. Enters the first sliding member 32 and rotatably supports the tip of the first screw shaft 31.

  The second conversion mechanism 35 has substantially the same structure as the first external gear 23 a formed on the outer periphery of the annular internal gear 23, the second external gear 38 that meshes with the first external gear 23 a, and the first conversion mechanism 30. The second screw shaft 36 and the second sliding member 37 are used. Similar to the first conversion mechanism 30, the second screw shaft (second male screw member) 36 penetrates the second partition 10b and is supported by a ball bearing 39, and the tip of the second screw shaft 36 protrudes into the first chamber R1. The second external gear 38 is integrally formed on the same axis. Similarly to the first conversion mechanism 30, the second sliding member 37 is supported by the second support cylinder portion 12 so that its rotation is restricted and slidable in the axial direction, and the female screw portion 37 a at the tip thereof is a second screw shaft. 36 is threadedly engaged. The second screw pair composed of the second screw shaft 36 and the second sliding member 37 that are screw-engaged with each other is a left-hand screw opposite to the first screw pair, but the lead is the same.

  The first control cable 40 composed of the first inner wire 41 and the first outer tube 42 has an end of the first outer tube 42 at the center of the mounting portion of the first support cylinder portion 11 on the outer wall of the housing 10 via a mounting bracket 42a. One end of the first inner wire 41 that is attached and extends through the first outer tube 42 enters the first support cylinder portion 11, and the connecting fitting 41 a at the tip thereof is the first sliding that is opposite to the female screw portion 32 a. The member 32 is locked at one end. Similarly, in the second control cable 45, one end of the second outer tube 47 is attached to the outer wall of the housing 10 via the mounting bracket 47a, and one end of the second inner wire 46 is locked to one end of the second sliding member 37. ing. The other ends of the inner wires 41 and 46 of the control cables 40 and 45 are respectively connected to the operating portions of the parking brakes 50 and 51 of different wheels, and the other ends of the outer tubes 42 and 47 are attached to the fixing portions of the parking brakes 50 and 51. It has been.

  Next, the operation of the above-described first embodiment will be described. In FIG. 2, when the sun gear 21 is rotated clockwise by the electric motor 15, both the carrier 25 and the second external gear 38 are rotated clockwise, and the first and second inner wires 41, 46 are both Each of the parking spaces is pulled by the first screw pair made of the first screw shaft 31 and the first sliding member 32 and the second screw pair made of the second screw shaft 36 and the second sliding member 37 and pulled to the end. The brakes 50 and 51 generate the same braking force. If the sun gear 21 is rotated counterclockwise by the electric motor 15, both the first and second inner wires 41 and 46 are returned and the parking brakes 50 and 51 are released.

The rotational force applied to the sun gear 21 by the electric motor 15 in the state where the parking brakes 50 and 51 are operated as described above, the inner wires 41 and 46 are pulled and stopped to the end, and the planetary gear mechanism 20 is also stopped. Is T _b (= F · b / 2; b is the meshing pitch circle diameter of the sun gear 21), the force of F as shown in FIG. Works. For simplicity, the description will be made assuming that the number of planetary gears 22 is one. Each meshing position of the planetary gear 22 with the annular internal gear 23, the center of the support shaft 24 of the carrier 25 that pivotally supports the planetary gear 22, and the meshing position of the second external gear 38 with the first external gear 23a. The forces acting on F are F, 2F, and c · F / d, respectively. Thereby, the rotational force T _a generated in the carrier 25 and the first screw shaft 31, the rotational force T _c generated in the annular internal gear 23, and the clockwise rotational force generated in the second external gear 38 and the second screw shaft 36. T _d is as follows.

T _a = 2F (c + b) / 4 = F (c + b) / 2

T _c = −c · F / 2

T _d = (c · F / d) (e / 2) = c · e · F / 2d

  However,

    a: meshing pitch circle diameter of the planetary gear 22

    c: meshing pitch circle diameter of the internal teeth of the annular internal gear 23

    d: meshing pitch circle diameter of the first external gear 23a

    e: meshing pitch circle diameter of the second external gear 38

    (C + b) / 4: the amount of eccentricity at the center of the support shaft 24

Here, if T a ₌ T _d, in the state in which the planetary gear mechanism 20 is stopped, the rotational force generated in the first screw shaft 31 T _a and the rotational force T _d generated in the second screw shaft 36 is equal . In this case, the speed increasing ratio (e / d) by the first and second external gears 23a and 38 is 1 + b / c.

A set of numerical examples is shown below.
a = 17.5, b = 5, c = 40, d = 48, e = 54, e / d = 1.125

  The first and second inner wires 41, 46 pulled by the sun gear 21 rotated by the electric motor 15 via the carrier 25, the annular internal gear 23, and the first and second conversion mechanisms 30, 35 have a small resistance. The rotation of the carrier 25 or the annular internal gear 23 corresponding to the inner wires 41 and 46 drawn to the end is stopped. When the other inner wire 46 or 41 is drawn to the end by the rotation of the remaining annular internal gear 23 or the carrier 25, the rotational force applied from the electric motor 15 to the sun gear 21 is a predetermined ratio by the equalizer action of the planetary gear mechanism 20. It is distributed to the carrier 25 and the annular internal gear 23, converted into the same tensile force by the first conversion mechanism 30 and the second conversion mechanism 35, and transmitted to the first inner wire 41 and the second inner wire 46, and each parking brake 50, 51 is activated. Accordingly, the first and second inner wires 41 and 46 are pulled with almost equal force.

  Next, the second embodiment shown in FIG. 3 will be described. In the first embodiment described above, the first and second control cables 40 and 45 are drawn from the opposite side of the housing 10, but the second embodiment is different in that it is drawn from the same side of the housing 10A. Since the other structure of the second embodiment is almost the same as that of the first embodiment, this difference will be mainly described.

  The housing 10A of the second embodiment has a box shape having a partition wall 10Aa near one outer wall, and is constituted by a plurality of parts that are integrally connected to each other, as in the first embodiment. A planetary gear mechanism 20 is provided in the first chamber R1A between the partition wall 10Aa and the outer wall close to the partition wall 10Aa, and the second chamber R2A on the opposite side to the first chamber R1A across the first partition wall 10Aa. The first and second conversion mechanisms 30 and 35 are provided, and the electric motor 15 is provided outside the housing 10A.

  The planetary gear mechanism 20 has substantially the same structure as that of the first embodiment, and includes a sun gear 21, three planetary gears 22, an annular internal gear 23, a support shaft 24, and a carrier 25. Similar to the first embodiment, it is integrally formed at the tip of the first screw shaft 31 that penetrates the partition wall 10Aa and protrudes into the first chamber R1A. A one-way clutch 16 is mounted coaxially with the carrier 25 on the inner surface of the outer wall of the housing 10A forming a part of the wall of the first chamber R1A, and the sun gear of the planetary gear mechanism 20 provided on the output shaft 16a. 21 is meshed with each planetary gear 22. An electric motor 15 similar to that of the first embodiment is provided on the outer side of the outer wall to which the one-way clutch 16 is attached.

  The first conversion mechanism 30 has the same structure as that of the first embodiment described above, and includes a first screw shaft 31 and a first sliding member 32 that is screw-engaged with the first screw shaft 31. The second conversion mechanism 35 is the same as in the first embodiment except that the second screw shaft 36 is supported by the partition wall 10Aa and protrudes to the same side as the first screw shaft 31. The first and second control cables 40 and 45 are exactly the same as in the first embodiment, and are attached to the housing 10A and the first and second sliding members 32 and 37 in the same manner. The other ends of the inner wires 41 and 46 of the control cables 40 and 45 are respectively connected to the operating portions of the parking brakes 50 and 51 of different wheels, and the other ends of the outer tubes 42 and 47 are attached to the fixing portions of the parking brakes 50 and 51. It has been.

  This second embodiment is also operated in the same manner as the first embodiment, and when the sun gear 21 is rotated in one direction by the electric motor 15, the first and second inner wires 41, 46 are attracted to each parking brake 50, When the sun gear 21 is rotated in the reverse direction, the inner wires 41 and 46 are returned and the parking brakes 50 and 51 are released.

  In the second embodiment, as in the first embodiment, the meshing pitch circle diameter of each gear is set so that the rotational force generated in the first screw shaft 31 and the rotational force generated in the second screw shaft 36 are equal. In addition, the equalizer action in which the rotational force applied to the sun gear 21 is converted so as to generate an equal tensile force to the first inner wire 41 and the second inner wire 46 is not hindered, and play due to wear is extremely small. It is.

  In the first embodiment, the first and second inner wires 41 and 46 are pulled out from both sides of the housing 10, respectively, whereas in the second embodiment, the first and second inner wires 41 and 46 are pulled out from the same side of the housing 10A. be able to.

  Next, the third embodiment shown in FIG. 4 will be described. In the first embodiment described above, the first and second conversion mechanisms 30 and 35 are coupled to the planetary gear mechanism 20 side and rotated by the first and second screw shafts 31 and 36, respectively, and are screw-engaged therewith. The first external gear 23a has an annular shape, and includes first and second sliding members 32 and 37 that have internal thread portions 32a and 37a that are supported by the housing 10 so as to be slidable in the axial direction. It is formed on the outer periphery of the internal gear 23. On the other hand, in the third embodiment, the first and second conversion mechanisms 30B and 35B are respectively connected to the planetary gear mechanism 20B side and rotated by the first and second screw cylinders 31B and 36B, and the screw engagement with them. The first and second sliding members (male screw members) 32B and 37B, which have male screw portions 32Bb and 37Bb to be joined, are supported by the housing 10B so as to be freely slidable in the axial direction. The tooth gear 23Ba is different in that it is formed on the outer periphery of a small-diameter cylindrical portion 23Bb integrally formed on one side in the axial direction of the annular internal gear 23B. Since the other structure of the third embodiment is almost the same as that of the first embodiment, this difference will be mainly described.

  Similar to the first screw shaft 31 of the first embodiment, the first screw cylinder (first female screw member) 31B of the first conversion mechanism 30B penetrates the first partition 10Ba and is supported by the ball bearing 34, and the first chamber R1B. A carrier 25 of the planetary gear mechanism 20B is integrally formed coaxially at the tip of the first screw cylinder 31B protruding inward. A first cylindrical support member 33B is attached to the distal end portion of the first support cylinder portion 11B that protrudes inward coaxially with the first screw cylinder 31B from the outer wall of the housing 10B facing the first partition wall 10Ba. Yes. The first cylindrical support member 33B is composed of a small-diameter rectangular tube portion 33Ba and a large-diameter cylindrical portion 33Bb, and the small-diameter square tube portion 33Ba is fitted and attached to a square inner hole of the first support cylindrical portion 11B. The tip of one screw cylinder 31B is rotatably supported by the inner circumference of a large diameter cylindrical portion 33Bb. In the first sliding member (first male screw member) 32B, the male screw portion 32Bb at one end is screw-engaged into the first screw cylinder 31B, and the remaining square bar portion 32Ba is the rectangular tube portion 33Ba of the first cylindrical support member 33B. Is supported so as to be slidable in the axial direction and restricted in rotation. One end of the first inner wire 41B of the first control cable 40B enters the square bar portion 32Ba, and the connecting fitting 41Ba at the tip thereof is locked in the male screw portion 32Bb.

  The second conversion mechanism 35B is engaged with a first external gear 23Ba formed on the outer periphery of a small-diameter cylindrical portion 23Bb coaxially and integrally formed on one side in the axial direction of the annular internal gear 23B. The second external gear 38B, the second screw cylinder 36B and the second sliding member 37B having substantially the same structure as the first conversion mechanism 30B are configured. Similar to the first conversion mechanism 30B, the second screw cylinder (second female screw member) 36B penetrates the second partition 10Bb, is supported by the ball bearing 39, and protrudes into the first chamber R1B. The second external gear 38B meshed with the first external gear 23Ba is integrally formed on the same axis. Similar to the first embodiment, the second inner wire (not shown) of the second control cable in which the second outer tube is fixed to the outer wall of the housing 10B on the opposite side of the first control cable 40B is the first conversion mechanism 30B. Similarly, it is connected to the second sliding member 37B.

  The third embodiment is also operated in the same manner as the first embodiment. When the sun gear 21 is rotated in one direction by the electric motor 15, the first inner wire 41B and the second inner wire are attracted and each parking brake is operated. If the sun gear 21 is rotated in the opposite direction, each inner wire is returned and each parking brake is released.

  In the third embodiment, as in the first embodiment, the meshing pitch circle diameter of each gear is set so that the rotational force generated in the first screw cylinder 31B is equal to the rotational force generated in the second second screw cylinder 36B. Therefore, the equalizer action that the rotational force applied to the sun gear 21 is converted so as to generate a tensile force equal to the first inner wire 41B and the second inner wire is not hindered, and the durability is reduced due to wear. There are very few.

  In the first embodiment described above, the first external gear 23a that meshes with the second external gear 38 is formed on the outer periphery of the annular internal gear 23, whereas in the third embodiment, the second external gear 23a. The first external gear 23Ba meshing with the gear 38B is formed on the outer periphery of a small-diameter cylindrical portion 23Bb integrally formed on one side in the axial direction of the annular internal gear 23B. In this way, the first screw cylinder The distance between 31B and the 2nd screw cylinder 36B can be reduced rather than the distance between the 1st screw shaft 31 and the 2nd screw shaft 36, and a vehicle parking brake apparatus can be reduced in size.

  In the first to third embodiments described above, the conversion characteristics of the first and second conversion mechanisms are such that when the brake wire is pulled by the electric motor 15 and the parking brakes 50 and 51 are brought into the braking state, each brake wire The gear ratios of the pair of gears 23a, 38, 23Bb, and 38B that mesh with each other are adjusted so that the tensile forces distributed to each other are equal to each other. Thereby, the parking brakes 50 and 51 of the same specification can be provided in each wheel.

  By adjusting the conversion characteristics of the first and second conversion mechanisms by changing the leads of the screw pair consisting of the male screw members 31, 36, 32B, and 37B and the female screw members 32, 37, 31B, and 36B, The tensile force distributed to the second inner wires 41, 41B and 46, 46B may be the same.

  Next, the fourth embodiment shown in FIGS. 5 and 6 will be described. In the fourth embodiment, the planetary gear mechanism 20C is substantially the same as the planetary gear mechanism 20 of the first embodiment except for the support portion, but the first and second conversion mechanisms 30C and 35C are the same as those of the first embodiment. Unlike the first and second conversion mechanisms 30 and 35, the driving mechanism between the electric motor 15C and the sun gear 21C of the planetary gear mechanism 20C is also completely different.

  As shown in FIGS. 5 and 6, the housing 10 </ b> C of the fourth embodiment forms a rectangular box-shaped first portion that forms the first chamber R <b> 1 </ b> C and a second chamber R <b> 2 </ b> C that protrudes from one side thereof. Like the first embodiment, it is composed of a plurality of portions that are integrally connected to each other. The planetary gear mechanism 20C and the first and second conversion mechanisms 30C and 35C are provided in the first part, the drive mechanism for the sun gear 21C is provided in the second part, and the electric motor 15C is located outside the second part. Is provided.

  The planetary gear mechanism 20C includes a sun gear 21C, three planetary gears 22C, an annular internal gear 23C, a support shaft 24C, and a carrier 25C. The annular internal gear 23C is the first part of the housing 10C. It is rotatably supported via a ball bearing 27C at a substantially central portion of the inner surface of the wall portion on the two-part side. The disc-shaped carrier 25C is rotatably supported coaxially with the planetary gear 22C via a ball bearing 26C on the wall portion of the housing 10C opposite to the second portion, and is decentered by the same distance from the rotation axis. The planetary gear 22C is rotatably supported by the three support shafts 24C that are erected at angular intervals, and meshed with the internal teeth of the annular internal gear 23C.

  In the second chamber R2C of the housing 10C, the output shaft 18Ca of the worm wheel 18C is rotatably supported via the ball bearing 19C on the same axis as the annular internal gear 23 and the carrier 25, and in the first chamber R1C. The sun gear 21C of the planetary gear mechanism 20C is fixed to the tip end of the projecting output shaft 18Ca and meshed with each planetary gear 22C. The output shaft 15Ca of the electric motor 15C attached to the second portion of the housing 10C enters the second chamber R2C at a right angle to the worm wheel 18C, and the worm 17C fixed to the output shaft 15Ca is meshed with the worm wheel 18C. The sun gear 21C is driven.

  As shown in FIGS. 5 and 6, the first conversion mechanism 30 </ b> C is a ring having a substantially constant thickness, and the outer periphery of the first pulley (first rotating member) 31 </ b> C that is coaxially fixed to the outer periphery of the carrier 25 </ b> C. A first outer peripheral groove (first arcuate portion) 31Ca is formed at a constant depth over the entire circumference, and a part of the vicinity of the outer periphery is provided with a tip of a first inner wire 41C of a first control cable 40C described later. A mounting hole 31Cb for locking the coupling fitting 41Ca is formed. The second conversion mechanism 35C has an outer periphery of a second pulley (second rotating member) 35C similar to the first conversion mechanism 30C, except that the fixing destination is the outer periphery of the annular internal gear 23C and the outer diameter is slightly smaller. A second outer peripheral groove (second arcuate portion) 36Ca is formed over the entire circumference at a constant depth, and a mounting hole 36Cb similar to the mounting hole 31Cb is formed. A needle roller bearing 28C is coaxially interposed between the annular internal gear 23C and the second pulley 36C, which are integrally fixed to each other, and between the carrier 25C and the first pulley 31C. The annular internal gear 23C and the second pulley 36C, and the carrier 25C and the first pulley 31C may be integrally formed.

  The first and second control cables 40C and 45C are the same as the control cables 40 and 45 of the first embodiment, except for the connecting fittings 41Ca and 46Ca of the inner wires 41C and 46C. The outer tubes 42 and 47 are attached to the housing 10C in the same manner as in the first embodiment, and the inner wires 41C and 46C are outer peripheral grooves corresponding to one end portions protruding from the fittings 42a and 47a of the outer tubes 42 and 47, respectively. The bottom surfaces of 31Ca and 36Ca are contacted in the tangential direction and guided along the bottom surfaces, and the connecting metal fittings 41Ca and 46Ca at the tips thereof are locked in the mounting holes 31Cb and 36Cb. The ratio of the radius of the first outer circumferential groove 31Ca to the radius of the second outer circumferential groove 36Ca is the speed increasing ratio (e / d) by the first and second external gears 23a and 38 in the first embodiment, that is, 1 + b / c. . Thereby, the tensile force produced in the 1st inner wire 41C and the 2nd brake wire 46C becomes equal.

  In the fourth embodiment, when the sun gear 21C is rotated by the electric motor 15C via the worm 17C and the worm wheel 18C, the first pulley 31C and the second pulley 36C are rotated in opposite directions. When the sun gear 21C is rotated in one direction by the electric motor 15C, the first and second inner wires 41C and 46C are attracted by the first and second pulleys 31C and 36C, and the parking brakes 50 and 51 are operated. If the gear 21 is rotated in the reverse direction, the inner wires 41C and 46C are returned and the parking brakes 50 and 51 are released.

  In the fourth embodiment, the meshing pitch circle diameter of each gear and the diameter of each outer circumferential groove 31Ca, 36Ca generate a tensile force in which the rotational force applied to the sun gear 21 is equal to the first inner wire 41C and the second inner wire 46C. Is set to As a result, the first and second inner wires 41C and 46C are smoothly pulled with substantially equal force, and play due to wear is very small.

  In the above embodiment, the conversion characteristics of the first and second conversion mechanisms are adjusted such that the tensile forces distributed to the first and second inner wires are equal to each other. In this case, if the characteristics of the first and second parking brakes are the same, a braking force equal to the first and second parking brakes is generated. However, when the characteristics of the first and second parking brakes are different due to, for example, the friction coefficient of the brake pad and the lever ratio of the operating part that moves the brake shoe, the parking wire is pulled by the electric motor 15 and pulled. The conversion characteristics of the first and second conversion mechanisms may be adjusted so that when the brakes 50 and 51 are in the braking state, a braking force equal to that of the first and second parking brakes is generated. In this case, the pulling force of the first and second brake wires necessary for generating the braking force equal to that of the first and second parking brakes is obtained, and the brake wires are pulled by the electric motor to brake the parking brake. When the state is set, the respective conversion characteristics of the first and second conversion mechanisms are adjusted so that the respective tensile forces distributed to the first and second inner wires become the obtained respective tensile forces.

It is sectional drawing which shows the whole structure of 1st Embodiment of the parking brake apparatus for vehicles by this invention. It is 2-2 sectional drawing of FIG. It is sectional drawing which shows the whole structure of 2nd Embodiment of the parking brake apparatus for vehicles by this invention. It is sectional drawing which shows the whole structure of 3rd Embodiment of the parking brake apparatus for vehicles by this invention. It is sectional drawing which shows the whole structure of 4th Embodiment of the parking brake apparatus for vehicles by this invention. FIG. 6 is a cross-sectional view taken along 6-6 in FIG. 5.

Explanation of symbols

10, 10A, 10B, 10C ... housing, 15, 15C ... electric motor, 20, 20B, 20C ... planetary gear mechanism, 21, 21C ... sun gear, 22, 22C ... planetary gear, 23, 23B, 23C ... annular internal teeth Gear, 23a ... First external gear, 24, 24C ... Support shaft, 25, 25C ... Carrier, 30, 30B, 30C ... First conversion mechanism, 31, 36 ... Male screw member (screw shaft), 31B, 36B ... Female screw Member (screw cylinder), 32, 37 ... Female screw member (sliding member), 32B, 37B ... Male screw member (sliding member), 35, 35B, 35C ... Second conversion mechanism, 38, 38B ... Second external gear , 41, 41B, 41C ... first brake wire, 46, 46C ... second brake wire, 50, 51 ... first and second parking brakes.

Claims (10)

A housing (10);
The sun gear (21, 21C), the annular internal gear (23, 23B, 23C), the carrier (25, 25C) and the carrier (25, 25C), which are coaxially and relatively rotatably supported in the housing (10), and the carrier A planetary gear mechanism (20, 20B) comprising a planetary gear (22, 22C) rotatably supported by a support shaft (24, 24C) provided eccentrically with the sun gear and meshed with both the sun gear and the annular internal gear. 20C) and
An electric motor (15, 15C) that applies a rotational force to the sun gear (21, 21C) to generate a rotational force on the annular internal gears (23, 23B, 23C) and the carrier (25, 25C);
A first brake wire (41) and a second brake wire (46) for generating a braking force on the first and second parking brakes (50, 51) provided on different wheels;
A first conversion mechanism (30, 30B, 30C) for converting a rotational force generated in the carrier (25, 25C) into a tensile force of the first brake wire (41);
A second conversion mechanism (35, 35B, 35C) for converting a rotational force generated in the annular internal gear (23, 23B, 23C) into a tensile force of the second brake wire (46) is provided. Parking brake device for vehicles.   The parking brake device for a vehicle according to claim 1, wherein each conversion characteristic of the first and second conversion mechanisms (30, 30B, 30C, 35, 35B, 35C) is determined by the electric motor (15) by the brake wire. When the parking brake (50, 51) is brought into a braking state by pulling (41, 46), the tensile force distributed to each brake wire is equal to the first and second parking brakes (50, 51). A parking brake device for a vehicle, which is set to a characteristic that generates a braking force.   3. The parking brake device for a vehicle according to claim 2, wherein each of the conversion mechanisms (30, 30B, 35, 35B) is a male screw member (31, 36, 32B, 37B) and a female screw member (32) that are screwed into each other. , 37, 31B, 36B), and the respective conversion characteristics are set by changing the lead of each screw pair.   The vehicle parking brake device according to claim 2, wherein the first conversion mechanism (30, 30B) includes a male screw member (31, 32B) and a female screw member (32, 31B) that are rotatably screwed together. The second conversion mechanism (35, 35B) has a pair of gears (23a, 38, 23Bb, 38B)) and a male screw member (36, 37B) screwed into each other so as to be rotatable. Each of the conversion mechanisms (30, 36B) has a second screw pair made of a female screw member (37, 36B) and adjusts the gear ratio of the pair of gears (23a, 38, 23Bb, 38B) meshing with each other. 30B, 35, 35B), a parking brake device for a vehicle characterized in that the conversion characteristics are set. A housing (10);
A sun gear (21), an annular internal gear (23) and a carrier (25) supported in the housing (10) so as to be coaxial with each other and rotatable relative to each other, and a support shaft provided eccentrically to the carrier A planetary gear mechanism (20) comprising a planetary gear (22) rotatably supported by (24) and meshed with both the sun gear and the annular internal gear;
An electric motor (15) for applying a rotational force to the sun gear (21) to generate a rotational force on the annular internal gear (23) and the carrier (25);
A first brake wire (41) and a second brake wire (46) for generating a braking force on the first and second parking brakes (50, 51) provided on different wheels;
A first screw shaft (31) that is integrally connected to the carrier (25) coaxially and protrudes on the opposite side of the electric motor (15), and is axially slidable coaxially with the first screw shaft. In addition, a first screw pair comprising a first sliding member (32) in which a female screw portion formed at one end and supported by the housing (10) with its rotation restricted is engaged with the first screw shaft. A first conversion mechanism (30) that converts a rotational force generated in the carrier (25) into a tensile force of the first brake wire (41) having one end connected to the other end of the first sliding member in the axial direction. )When,
A first external gear (23a) that is supported by the housing (10) so as to be rotatable about an axis parallel to the first screw shaft (31) and is integrally formed coaxially with the annular internal gear (23); A second external gear (38) to be engaged with the second external gear, a second screw shaft (36) integrally connected to the second external gear coaxially and projecting to the opposite side of the first screw shaft; A second sliding member in which a female screw portion formed at one end and supported by the housing is axially slidable coaxially with the second screw shaft and supported by the housing and is engaged with the second screw shaft. The second brake wire (46) is provided with a second screw pair (37) and the rotational force generated in the annular internal gear is connected to the other end of the second sliding member at one end in the axial direction. A second conversion mechanism (35) for converting into force,
By adjusting the gear ratio of the first and second external gears (23a, 38) meshed with each other, the conversion characteristics of the first and second conversion mechanisms (30, 35) are changed to the electric motor ( 15), when the brake wire (41, 46) is pulled and the parking brake (50, 51) is put into a braking state, the tensile force distributed to each brake wire is changed to the first and second parking brakes ( 50, 51) is set to a characteristic that generates a braking force equal to 50, 51). A housing (10);
A sun gear (21), an annular internal gear (23) and a carrier (25) supported in the housing (10) so as to be coaxial with each other and rotatable relative to each other, and a support shaft provided eccentrically to the carrier A planetary gear mechanism (20) comprising a planetary gear (22) rotatably supported by (24) and meshed with both the sun gear and the annular internal gear;
An electric motor (15) for applying a rotational force to the sun gear (21) to generate a rotational force on the annular internal gear (23) and the carrier (25);
A first brake wire (41) and a second brake wire (46) for generating a braking force on the first and second parking brakes (50, 51) provided on different wheels;
A first screw shaft (31) that is integrally connected to the carrier (25) coaxially and protrudes on the opposite side of the electric motor (15), and is axially slidable coaxially with the first screw shaft. In addition, a first screw pair comprising a first sliding member (32) in which a female screw portion formed at one end and supported by the housing (10) with its rotation restricted is engaged with the first screw shaft. A first conversion mechanism (30) for converting a rotational force generated in the carrier into a tensile force of the first brake wire (41) having one end connected to the other end of the first sliding member in the axial direction;
A first external gear (23a) that is supported by the housing (10) so as to be rotatable about an axis parallel to the first screw shaft (31) and is integrally formed coaxially with the annular internal gear (23); A second external gear (38) to be engaged, a second screw shaft (36) which is coaxially and integrally connected to the second external gear and protrudes to the same side as the first screw shaft; A second sliding member in which a female screw portion formed at one end and supported by the housing is axially slidable coaxially with the second screw shaft and supported by the housing and is engaged with the second screw shaft. The second brake wire (46) is provided with a second screw pair (37) and the rotational force generated in the annular internal gear is connected to the other end of the second sliding member at one end in the axial direction. A second conversion mechanism (35) for converting into force,
By adjusting the gear ratio of the first and second external gears (23a, 38) meshed with each other, the conversion characteristics of the first and second conversion mechanisms (30, 35) are changed to the electric motor ( 15), when the brake wire (41, 46) is pulled and the parking brake (50, 51) is put into a braking state, the tensile force distributed to each brake wire is changed to the first and second parking brakes ( 50, 51) is set to a characteristic that generates a braking force equal to 50, 51).   The vehicle parking brake device according to claim 5 or 6, wherein the conversion characteristic of each of the conversion mechanisms (30, 35) adjusts a gear ratio of the first and second external gears (23a, 38). In addition to or in place of this, the vehicle parking brake device is characterized in that the conversion characteristic of each conversion mechanism is set by making the lead of each screw pair different.   The vehicle parking brake device according to any one of claims 5 to 7, wherein the first and second screw shafts (31, 36) are the carrier (25) and the second external gear (38). The first and second sliding members (32, 37) are replaced with the first and second screw cylinders (31B, 36B) integrally connected coaxially to each other. The first and second male screw portions, which are supported by the housing (10) and are formed at one end so as to be axially slidable and coaxially slidable, are threadedly engaged with the first and second screw cylinders. A parking brake device for a vehicle, wherein the parking brake device is replaced by a second sliding member (32B, 37B).   The parking brake device for a vehicle according to any one of claims 5 to 8, wherein the annular internal gear (23B) is integrally formed coaxially with a small-diameter cylindrical portion (23Bb) on one side in the axial direction. The parking brake device for vehicles, wherein the first external gear (23Ba) is formed on an outer periphery of the cylindrical portion.   The parking brake device for a vehicle according to any one of claims 2 to 9, wherein each conversion characteristic of the first and second conversion mechanisms (30, 30B, 30C, 35, 35B, 35C) is the electric motor. When the brake wire (41, 46) is pulled by (15) and the parking brake (50, 51) is put into a braking state, a braking force equal to the first and second parking brakes (50, 51) is obtained. A parking brake device for a vehicle, which is set to have a characteristic of distributing an equal tensile force to each brake wire (41, 46) so as to be generated.

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