JP2020002996A - Disc brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disc brake device capable of downsizing a power generation source. A disc brake device (100) is rotatably supported by a brake body (11), and a pair of brake arms (13) that pinch a brake rotor (35) by a pad assembly (33) of the other end (25) and air that moves a rod (47) forward and backward. The chamber 43 is rotatably connected to the cam holder 57 having one end 55 connected to the one end 23, and the other end 59 is rotatably connected to the lever pin 53 connected to the rod 47. The force transmitted by the rotation of the pair of cam levers 15 and the rotation of the cam levers 15 rotatably held by the cam holder 57 and rotatably connected via the rotation center shaft 61 provided at the one end 55 is boosted. The eccentric cam 17 for rotating the brake arm 13 and the rotation center shaft 61 on the straight line X along the expansion direction of the pair of one ends 23 respectively. It comprises a lever holding member 19, the. [Selection diagram] Figure 2

Description

  The present invention relates to a disc brake device.

  2. Description of the Related Art Disc brake devices mainly used in railway vehicles and the like are generally of a lever type using pneumatic pressure (Patent Documents 1 and 2 and the like) and rotation of a servomotor (Patent Document 3 and the like) as a power source. . Many disk brake devices of this type use a booster mechanism such as a wedge in order to reduce the size of the caliper.

JP 2008-151167 A JP 2008-151168 A Japanese Patent No. 4629980

  However, even if a boosting mechanism such as a wedge is used, the power generation source (actuator) has been relatively large due to the required axial force.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a disk brake device capable of reducing the power generation source by making the booster mechanism compact.

The above object according to the present invention is achieved by the following configurations.
(1) A brake body supported by a vehicle body and a support portion between one end and the other end are rotatably supported by the brake body, and a pad assembly attached to the other end is provided. A pair of brake arms for clamping the brake rotor from both sides, an actuator attached to the brake body for moving the output member forward and backward, and one end rotatably connected to a cam holder connected to the one end. A pair of cam levers each of which has the other end rotatably connected to an input member connected to the output member; and a rotation center shaft provided at the one end and rotatably held by the cam holder. The force transmitted by the rotation of the cam lever rotatably connected via the shaft is boosted to rotate the brake arm about the support portion as a rotation fulcrum. A disc brake device comprising: an eccentric cam to be moved; and a lever holding member that guides the rotation center axis on a straight line along a direction in which the pair of the one end portions expands.

According to the disk brake device having the configuration of the above (1), the support portion between the one end and the other end is provided at one end of a pair of brake arms rotatably supported by the brake body. , A pair of cam holders are respectively connected. One end of the pair of brake arms is expanded when the respective cam holders are separated from each other, and the pad assembly at the other end pivoted about the supporting portion presses the brake rotor.
One end (outer end) of each of a pair of cam levers is rotatably connected to each cam holder. The other ends (inner ends) of the pair of cam levers are rotatably connected by input members such as lever pins. An output member is connected to the input member. The output member allows the input member to be pressed in a direction orthogonal to the axis.
Further, an eccentric cam is rotatably held in each cam holder. A rotation center shaft is provided at one end of each of the pair of cam levers. The cam lever is rotatably connected to each of the cam holders by the pivot center shaft being supported by the eccentric cam. Each rotation center axis supported by the pair of eccentric cams is guided by a lever holding member on a straight line along the expanding direction of one end of the brake arm.
When the input member is pressed in the direction orthogonal to the axis, the pair of cam levers move in a direction away from each other on a straight line along the expanding direction. The pair of rotation center axes move the pair of cam holders in the separating direction via the respective eccentric cams (first amplification mechanism). The eccentric cam eccentrically supports the rotation center axis with respect to the rotation center line of the cam itself. The eccentric cam can reflect the displacement at one end of the cam lever due to the eccentricity to the feed amount for moving the cam holder in the separating direction (second amplification mechanism). Therefore, the eccentric cam can expand one end of the brake arm via the cam holder by boosting the force transmitted to the cam lever by the feed amount reflecting the displacement in the separating direction.
As described above, in the disc brake device of the present configuration, the eccentric cam is incorporated and held in the cam holder that connects the cam lever and one end of the brake arm. Since the cam lever is connected to the cam holder via the eccentric cam, the booster mechanism can be made compact. Further, in the disc brake device of this configuration, the adjustment of the boost can be easily performed by changing the amount of eccentricity of the rotation center axis of the eccentric cam with respect to the rotation center line of the cam. Further, in the disk brake device of this configuration, a large boost ratio can be set by the pair of cam levers and the eccentric cam, and an actuator having a small maximum output can be used.

(2) The disc brake device according to (1), wherein the eccentric cam is rotatably connected to the rotation center axis at a position offset from a rotation center line of the cam with respect to the cam holder. A disc brake device, wherein a rotation center line of the cam is rotated in an arc around the rotation center axis by rotation of a cam lever.

According to the disc brake device having the configuration (2), the eccentric cam is rotatable around the rotation center line of the cam and is held by the cam holder. One end of a cam lever is rotatably connected to the eccentric cam via a rotation center axis parallel to the rotation center line of the cam. The rotation center axis is disposed at a position (eccentric position) offset from the rotation center line of the eccentric cam. Further, the eccentric cam is fixed with its relative rotation restricted with respect to the cam lever. And, as described above, the rotation center axis is guided by the lever holding member on a straight line along the expanding direction of one end of the brake arm.
When the input member at the other end is pressed by the output member, the pair of cam levers move in a direction in which the pair of rotation center axes connected to the respective one ends are separated on a straight line along the expanding direction. At this time, since the relative rotation of the eccentric cam with respect to the cam lever is regulated, in addition to the linear movement of the rotation center axis, the rotation center line of the cam forms an arc-shaped locus about the rotation center axis. Draw and displace. That is, for the eccentric cam, this displacement is reflected in the feed amount for moving the cam holder in the separating direction.

(3) The disc brake device according to (2), wherein the eccentric cam formed in a cylindrical shape having a rotation axis of the cam as a central axis is a cylindrical cam holding formed in the cam holder. A disc brake device rotatably held in a hole.

  According to the disk brake device having the above configuration (3), the eccentric cam is formed in a cylindrical shape having the rotation center line of the cam as the center of rotation. The cylindrical eccentric cam is rotatably held coaxially in a cylindrical cam holding hole formed in the cam holder. Since the eccentric cam is fixed to one end of the cam lever with its relative rotation regulated, the eccentric cam is rotated in the cam holding hole of the cam holder when the input member is pressed and the cam lever swings. According to this disc brake device, since the eccentric cam is housed in the cam holder and the cam lever is connected to the eccentric cam via the rotation center shaft, a compact boosting mechanism is provided at the connecting portion between the cam lever and the cam holder. Can be incorporated.

(4) The disc brake device according to any one of (2) to (3), wherein the rotation center axis is guided by a guide groove formed in the lever holding member via a bearing. A disc brake device.

  According to the disk brake device having the above configuration (4), each of the pivot shafts moving in the separating direction on the straight line along the expanding direction is guided to the guide groove of the lever holding member through the bearing with low friction. Is done. Thereby, the transmission loss until the force input to the input member is output from the cam holder as the expanding force of the brake arm on a straight line along the expanding direction is reduced.

(5) The disc brake device according to any one of (2) to (4), wherein the cam lever is configured to connect the eccentric cam rotatably connected via the rotation center axis to the eccentric cam. A disc brake device comprising a pair of lever members sandwiched from a rotation center line direction of a cam.

  According to the disk brake device having the configuration (5), each of the pair of cam levers includes a pair of lever members. The cam lever has a configuration in which the pair of lever members sandwich the eccentric cam from the direction of the rotation center line of the cam, so that the allowable stress is larger than that of a single cam lever. In addition, it is possible to suppress the falling deformation of the rotation center axis perpendicular to the cam lever, which is likely to occur when only one cam lever is used.

(6) The disc brake device according to any one of (2) to (5), wherein the cam holder is provided with the cam holder with respect to a rotation center line of the cam in accordance with a wear amount of a lining of the pad assembly. A disc brake device provided with an adjuster mechanism for extending a connection position of one end.

  According to the disc brake device having the above configuration (6), the cam holder is connected to one end of the brake arm via the adjuster mechanism. The adjuster mechanism enables automatic adjustment by extending the connection position of one end of the brake arm with respect to the rotation center line of the cam according to the amount of wear of the lining.

(7) The disc brake device according to any one of (1) to (6), wherein the brake body supported by an attachment member attached to the vehicle body is configured to rotate the pair of brake arms. The mounting member is rotatably held by a suspension shaft of the mounting member that is sandwiched between dynamic shafts and extends in a direction orthogonal to these, and is provided between the brake body and the mounting member to swing the brake body. A disc brake device, wherein a spring member that urges in a suppressing direction is fixed to the brake body together with the actuator.

  According to the disc brake device having the configuration (7), the brake main body is held so as to freely swing (roll) around a suspension shaft fixed to the vehicle body side. A spring member is fixed to the brake body together with the actuator between the mounting member fixed to the vehicle body and the brake body that is swingable with respect to the suspension shaft fixed to the mounting member. The spring member biases the brake body in a direction to suppress the swing of the brake body.

  ADVANTAGE OF THE INVENTION According to the disc brake device which concerns on this invention, a power-generation source can be miniaturized by making a boost mechanism compact.

  The present invention has been specifically disclosed. Further, the present invention will be more clearly and sufficiently read from the following description of embodiments for carrying out the invention (hereinafter, referred to as "embodiments").

It is a perspective view showing the whole disc brake device structure concerning a 1st embodiment of the present invention. FIG. 2 is a horizontal sectional view of the disc brake device shown in FIG. 1. FIG. 2 is a side sectional view of the disc brake device shown in FIG. 1. FIG. 4 is a vertical cross-sectional view in a direction orthogonal to a suspension axis shown in FIG. 3. FIG. 3 is an exploded perspective view of the lever mechanism shown in FIG. FIG. 3 is an operation diagram of the lever mechanism shown in FIG. 2. It is a horizontal sectional view of a disc brake device concerning a 2nd embodiment of the present invention. FIG. 8 is a side sectional view of the disc brake device shown in FIG. 7. FIG. 9 is a longitudinal sectional view in a direction orthogonal to the suspension axis shown in FIG. 8. (A) is a perspective view of the power unit shown in FIG. 7, (b) is an exploded perspective view of the power unit shown in (a). (A) is a perspective view of the lever mechanism shown in FIG. 7, (b) is an exploded perspective view of the lever mechanism shown in (a). FIG. 12 is a perspective view of a main part in which the lever mechanism shown in FIG. 11 is further disassembled. (A) is a horizontal sectional view of the power unit shown in FIG. 10, and (b) is a schematic configuration diagram of the lever mechanism shown in (a). (A) is an operation explanatory diagram of the disc brake device shown in FIG. 7 when the disc brake device is released, and (b) is an operational explanatory diagram of the disc brake device shown in FIG. 7 during normal braking. (A) is an operation explanatory diagram of the disk brake device shown in FIG. 14 when the brake rotor is tilted, and (b) is an operational explanatory diagram of the disk brake device shown in FIG. 14 when an up / down phase occurs. It is a perspective view showing the whole disc brake device structure concerning a 3rd embodiment of the present invention. FIG. 17 is a horizontal sectional view of the disc brake device shown in FIG. 16. FIG. 18 is a side sectional view of the disc brake device shown in FIG. 17. It is a longitudinal cross-sectional view in the direction orthogonal to the suspension axis shown in FIG. (A) is a perspective view of the power unit shown in FIG. 17, and (b) is an exploded perspective view of the power unit shown in (a). (A) is a perspective view of the lever mechanism shown in FIG. 17, (b) is an exploded perspective view of the lever mechanism shown in (a). FIG. 22 is a perspective view of a main part in which the lever mechanism shown in FIG. 21 is further disassembled. FIG. 18 is a horizontal sectional view of the power unit shown in FIG. 17. (A) is an operation explanatory diagram of the disc brake device shown in FIG. 17 when the disc brake device is released, and (b) is an operational explanatory diagram of the disc brake device shown in FIG. 17 during normal braking. 17A is an explanatory diagram of the operation of the disc brake device shown in FIG. 17 when the brake rotor is tilted, and FIG. 18B is an explanatory diagram of the operation of the disc brake device shown in FIG.

Hereinafter, embodiments according to the present invention will be described with reference to the drawings.
[First Embodiment]
FIG. 1 is a perspective view showing the entire structure of a disc brake device 100 according to a first embodiment of the present invention.
The disc brake device 100 according to the first embodiment can be suitably used for a disc brake for a railway vehicle, for example.

The disc brake device 100 has a brake main body 11, a brake arm 13, a cam lever 15, an eccentric cam 17, and a lever holding member 19 as main members.
The brake body 11 is supported by a mounting member 21 fixed to the vehicle body.

FIG. 2 is a horizontal sectional view of the disc brake device 100 shown in FIG.
In the pair of brake arms 13, a support 27 between one end 23 and the other end 25 is rotatably supported by a rotation shaft 29 with respect to the brake body 11. A pad assembly 33 having a plurality of linings 31 is attached to the other end 25 of each of the pair of brake arms 13. The pair of brake arms 13 are expanded in the direction in which the one end portions 23 are separated from each other, and press the brake rotors 35 arranged on both surfaces of the wheel with the pair of pad assemblies 33 from both sides.

FIG. 3 is a side sectional view of the disc brake device 100 shown in FIG.
In the disc brake device 100, the brake main body 11 is rotatably held by the suspension shaft 37. Thus, the brake body 11 is supported by the mounting member 21 mounted on the vehicle body via the suspension shaft 37. The suspension shaft 37 is sandwiched between the rotation shafts 29 of the pair of brake arms 13 and extends in a direction perpendicular to these and along the wheel track.

  A spring member 39 shown in FIG. 1 is provided between the brake body 11 and the mounting member 21. The spring member 39 urges the brake main body 11 in a direction for suppressing the swing.

  A power unit 41 as a power generation source is fixed to the brake body 11. The power unit 41 includes an air chamber 43 as an actuator and a lever mechanism unit 45. The air chamber 43 includes a rod 47 that is an output member in the same direction as the suspension shaft 37. When the compressed air is supplied to the air chamber 48 on the rear end side of the air piston 46 incorporated in the air chamber 43, the rod 47 advances in the direction along the axis against the return spring 49. That is, the air chamber 43 is attached to the brake main body 11 and operates with the rod 47 capable of moving forward and backward.

  The lever mechanism unit 45 is fixed integrally with the air chamber 43, and is inserted so that the rod 47 from the air chamber 43 can move forward and backward in a direction approaching and separating from the pad assembly 33. The lever mechanism unit 45 houses the lever mechanism 51. The lever mechanism unit 45 is configured such that, when the rod 47 advances, the lever pin 53 which is an input member of the lever mechanism 51 shown in FIG. 2 is pressed.

FIG. 4 is a longitudinal sectional view in a direction perpendicular to the suspension shaft 37 shown in FIG.
The lever mechanism 51 has a pair of cam levers 15. The cam lever 15 has one end 55 shown in FIG. 2 rotatably connected to a cam holder 57 connected to the one end 23 of the brake arm 13. As shown in FIG. 2, the other ends 59 of the pair of cam levers 15 are rotatably connected to lever pins 53 connected to rods 47.

  As shown in FIG. 2, the cam holder 57 holds the eccentric cams 17 rotatably. The eccentric cam 17 is rotatably connected to the cam lever 15 via a rotation center shaft 61 provided at one end 55 of the cam lever 15. The eccentric cam 17 boosts the force transmitted by the rotation of the cam lever 15 to rotate the brake arm 13 about the support portion 27 as a rotation fulcrum.

  The lever mechanism unit 45 is provided with the lever holding member 19 shown in FIGS. The lever holding member 19 guides the rotation center shaft 61 on a straight line X along the expanding direction of the one end 23 of the pair of brake arms 13.

  As shown in FIG. 2, the eccentric cam 17 is rotatably connected to the rotation center shaft 61 at a position offset from the rotation center line 63 of the cam with respect to the cam holder 57. The eccentric cam 17 rotates (moves) the rotation center line 63 of the cam along an arc-shaped trajectory around the rotation center axis 61 by the rotation of the cam lever 15.

FIG. 5 is an exploded perspective view of the lever mechanism 51 shown in FIG.
The eccentric cam 17 is formed in a cylindrical shape with the rotation center line 63 of the cam as a central axis. The eccentric cam 17 is rotatably held in a cylindrical cam holding hole 65 formed in the cam holder 57. A cylindrical bearing bush 67 is inserted between the eccentric cam 17 and the cam holding hole 65. The bearing bush 67 reduces friction between the eccentric cam 17 and the cam holding hole 65.

  The rotation center shaft 61 is guided by a guide groove 71 formed in the lever holding member 19 via a bearing 69. The inner ring of the bearing 69 is fixed to the rotation center shaft 61. The bearing 69 has an outer ring rotatably provided on the inner ring via a plurality of rolling elements. The outer periphery of the outer ring of the bearing 69 is guided by the guide groove 71.

  In the eccentric cam 17, a lock pin 73 penetrates the opposite side of the rotation center axis 61 with respect to the rotation center line 63 of the cam. Further, the lock pin 73 penetrating the eccentric cam 17 penetrates the cam lever 15. That is, the cam lever 15 and the eccentric cam 17 are connected to each other so that the rotation center shaft 61 and the lock pin 73 penetrate therethrough so that they cannot rotate relative to each other.

  The cam lever 15 is constituted by a pair of lever members 75 that sandwich the eccentric cam 17 connected via the rotation center shaft 61 from the direction of the rotation center line 63 of the cam. Therefore, the cam lever 15 is constituted by a total of four lever members 75 in two pairs with the eccentric cam 17 interposed therebetween. One end 55 of each of the lever members 75 is fixed to the eccentric cam 17 by fastening a washer 77 and a nut 79 to a distal end of a rotation center shaft 61 that passes through a bearing 69. The eccentric cams 17 are rotatable at cam holding holes 65 of the respective cam holders 57.

  An adjuster mechanism 81 is provided on the cam holder 57. The adjuster mechanism 81 has a link rod 85 serving as an output shaft that enables the connection position of the one end 23 of the brake arm 13 to the rotation center line 63 of the cam to be extended by rotation. The link rod 85 includes an adjustment gear 87. An adjuster lever 91 biased by an adjuster spring 89 meshes with the teeth of the adjustment gear 87. When the wear amount of the lining 31 becomes equal to or more than a predetermined value, the adjuster lever 91 sends out the link rod 85 at a position where the adjustment gear 87 is rotated by one peak, and then meshes with the adjustment gear 87 to rotate the adjustment gear 87. regulate.

Next, the operation of the disc brake device 100 will be described.
In the disc brake device 100 according to the first embodiment, the support portions 27 between the one end 23 and the other end 25 of the pair of brake arms 13 are rotatably supported by the brake body 11. . The brake arm 13 is provided at its other end 25 with a pad assembly 33 for clamping the brake rotor 35 from both sides. An air chamber 43 for moving the rod 47 forward and backward is attached to the brake body 11. A pair of cam holders 57 are respectively connected to one end portions 23 of the pair of brake arms 13. When the respective cam holders 57 are separated from each other, one end 23 of the pair of brake arms 13 is expanded, and the pad assemblies 33 of the other end 25 rotated around the support portion 27 are arranged on both surfaces of the wheel. The brake rotor 35 is pressed.

  One end 55 (outer end) of each of the pair of cam levers 15 is rotatably connected to each cam holder 57. The other ends 59 (inner ends) of the pair of cam levers 15 are rotatably connected by lever pins 53. A rod 47 is connected to the lever pin 53. The rod 47 enables the lever pin 53 to be pressed in a direction orthogonal to the axis.

  Furthermore, the eccentric cam 17 is rotatably held by each cam holder 57. A rotation center shaft 61 is provided at one end 55 of each of the pair of cam levers 15. The cam lever 15 is rotatably connected to each of the cam holders 57 by the rotation center shaft 61 being pivotally supported by the eccentric cam 17. Each rotation center shaft 61 pivotally supported by the pair of eccentric cams 17 is guided by the lever holding member 19 on a straight line X along the expanding direction of the one end 23 of the brake arm 13.

FIG. 6 is an operation diagram of the lever mechanism 51 shown in FIG.
When the lever pin 53 is pressed in the direction orthogonal to the axis, the pair of cam levers 15 move in the direction away from each other on the straight line X along the expanding direction. The pair of rotation center shafts 61 move the pair of cam holders 57 in the separating direction via the respective eccentric cams 17 (first amplification mechanism). The eccentric cam 17 supports the rotation center shaft 61 eccentrically with respect to the rotation center line 63 of the cam itself. The eccentric cam 17 can reflect the displacement δ at one end 55 of the cam lever 15 to the feed amount Δ for moving the cam holder 57 in the separating direction due to the eccentricity (second amplification mechanism). The feed amount Δ is the amount of movement from the lever rotation center 93. Therefore, the eccentric cam 17 can expand the one end 23 of the brake arm 13 via the cam holder 57 by boosting the force transmitted to the cam lever 15 by the feed amount Δ reflecting the displacement δ in the separating direction.

  As described above, in the disc brake device 100 according to the first embodiment, the eccentric cam 17 is incorporated and held in the cam holder 57 that connects the cam lever 15 and the one end 23 of the brake arm 13. Since the cam lever 15 is connected to the cam holder 57 via the eccentric cam 17, the boosting mechanism can be made compact. Further, the disc brake device 100 of the first embodiment can easily adjust the boosting force by changing the amount of eccentricity of the rotation center shaft 61 with respect to the rotation center line 63 of the eccentric cam 17. It becomes. Further, in the disc brake device 100 of the first embodiment, a large boost ratio can be set by the pair of cam levers 15 and the eccentric cam 17, and the air chamber 43 having a small maximum output can be used.

  Further, in the disc brake device 100 according to the first embodiment, the eccentric cam 17 is rotatable around the rotation center line 63 of the cam and is held by the cam holder 57. One end 55 of the cam lever 15 is rotatably connected to the eccentric cam 17 via a rotation center axis 61 parallel to the rotation center line 63 of the cam. The rotation center shaft 61 is disposed at a position (eccentric position) offset from the rotation center line 63 of the eccentric cam 17. The eccentric cam 17 is fixed with its relative rotation restricted with respect to the cam lever 15. Then, the rotation center shaft 61 is guided by the lever holding member 19 on the straight line X along the expanding direction of the one end 23 of the brake arm 13 as described above.

  When the lever pin 53 at the other end 59 is pressed by the rod 47, the pair of cam levers 15 move in a direction in which the pair of rotation center shafts 61 connected to the respective one ends 55 separate on a straight line X along the expanding direction. Moving. At this time, since the relative rotation of the eccentric cam 17 with respect to the cam lever 15 is restricted, in addition to the movement of the rotation center axis 61 on the straight line X, the rotation center line 63 of the cam is centered on the rotation center axis 61. Displaces in a circular arc-shaped trajectory. That is, the displacement δ of the eccentric cam 17 is reflected on the feed amount Δ for moving the cam holder 57 in the separating direction.

  Further, in the disc brake device 100 according to the first embodiment, the eccentric cam 17 is formed in a cylindrical shape having the rotation center line 63 of the cam as the center of rotation. The cylindrical eccentric cam 17 is rotatably held coaxially in a cam holding hole 65 also formed in the cam holder 57. Since the eccentric cam 17 is fixed to one end 55 of the cam lever 15 with its relative rotation being regulated, the eccentric cam 17 is rotated in the cam holding hole of the cam holder 57 by the lever pin 53 being pressed and the cam lever 15 swinging. According to the disc brake device 100, the eccentric cam 17 is housed in the cam holder 57, and the cam lever 15 is connected to the eccentric cam 17 via the rotation center shaft 61, so that the connecting portion between the cam lever 15 and the cam holder 57 A compact booster mechanism can be incorporated.

  In the disc brake device 100 according to the first embodiment, a bearing 69 is coaxially attached to the end of the rotation center shaft 61. The respective rotation center shafts 61 which move in the separating direction on the straight line X along the expanding direction along the guide groove 71 while rotating, have low friction by the relative rotation of the inner ring and the outer ring of the bearing 69. It is guided by the guide groove 71. Thereby, the transmission loss until the force input to the lever pin 53 is output from the cam holder 57 as the expanding force of the brake arm 13 on the straight line X along the expanding direction is reduced.

  In the disc brake device 100 according to the first embodiment, each of the pair of cam levers 15 includes a pair of lever members 75. That is, four lever members 75 are used. The cam lever 15 has a configuration in which the pair of lever members 75 sandwich the eccentric cam 17 from the direction of the rotation center line 63 of the cam, so that the allowable stress is larger than that of a single cam member. In addition, it is possible to suppress the tilting deformation of the rotation center shaft 61 perpendicular to the cam lever 15 that is likely to occur when only one cam lever 15 is used.

  Further, in the disc brake device 100 according to the first embodiment, the cam holder 57 is connected to the one end 23 of the brake arm 13 via the adjuster mechanism 81. The adjuster mechanism 81 includes an adjustment gear 87 that enables the connection position of the one end 23 of the brake arm 13 to the rotation center line 63 of the cam to be extended by rotation. An adjuster lever 91 biased by an adjuster spring 89 meshes with the teeth of the adjustment gear 87. When the wear amount of the lining 31 exceeds a certain level, the adjuster lever 91 feeds the adjusting gear 87 at a position rotated by one mountain, meshes with the adjusting gear 87, and regulates the rotation of the adjusting gear 87. Accordingly, the adjuster mechanism 81 can perform automatic adjustment by extending the connection position of the one end 23 of the brake arm 13 with respect to the rotation center line 63 of the cam according to the amount of wear of the lining 31.

  In the disc brake device 100 according to the first embodiment, the mounting member 21 is fixed to the vehicle body. The suspension shaft 37 is fixed to the mounting member 21. The suspension shaft 37 is sandwiched between the rotation shafts 29 of the pair of brake arms 13 and extends in a direction orthogonal to these and along the wheel track. The suspension shaft 37 holds the brake body 11 rotatably around the shaft. The brake body 11 is held so as to freely swing (roll) around a suspension axis fixed to the vehicle body. A spring member 39 is provided between the mounting member 21 fixed to the vehicle body and the brake body 11 that is swingable with respect to a suspension shaft 37 fixed to the mounting member 21. Together with the brake body 11. The spring member 39 urges the brake body 11 in a direction to suppress the swing of the brake body 11. Thus, the brake body 11 is configured such that the linings 31 of the pad assemblies 33 on both sides are arranged with an equal clearance with respect to the brake rotor 35 after the swing return. Further, by fixing the power unit 41 to the brake body 11, the number of parts can be reduced by eliminating the use of spherical bearings or the like.

[Second embodiment]
Next, a disc brake device 200 according to a second embodiment of the present invention will be described.
FIG. 7 is a horizontal cross section of a disc brake device 200 according to a second embodiment of the present invention. In the second embodiment, the same members and portions as those in the first embodiment are denoted by the same reference numerals and described.
The disc brake device 200 has as main members a brake body 11, a brake arm 13, an air chamber 43 as an actuator, a lever mechanism 95 as a drive direction changing mechanism, and a follow-up mechanism 97.
The brake body 11 is supported by a mounting member 21 fixed to the vehicle body.

  In the pair of brake arms 13, a support 27 between one end 23 and the other end 25 is rotatably supported by a rotation shaft 29 with respect to the brake body 11. A pad assembly 33 having a plurality of linings 31 is attached to the other end 25 of each of the pair of brake arms 13. The pair of brake arms 13 are expanded in the direction in which the one end portions 23 are separated from each other, and press the brake rotors 35 arranged on both surfaces of the wheel with the pair of pad assemblies 33 from both sides.

FIG. 8 is a side sectional view of the disc brake device 200 shown in FIG.
In the disc brake device 200, the brake main body 11 is rotatably held by the suspension shaft 37. Thus, the brake body 11 is supported by the mounting member 21 mounted on the vehicle body via the suspension shaft 37. The suspension shaft 37 is sandwiched between the rotation shafts 29 of the pair of brake arms 13 and extends in a direction perpendicular to these and along the wheel track.

  A spring member 39 is provided between the brake body 11 and the mounting member 21 (see FIG. 1). The spring member 39 urges the brake main body 11 in a direction for suppressing the swing.

  A power unit 99 as a power generation source is fixed to the brake body 11. The power unit 99 includes an air chamber 43 as an actuator and a lever mechanism unit 101. The air chamber 43 includes a rod 47 that is an output member in the same direction as the suspension shaft 37. When the compressed air is supplied to the air chamber 48 on the rear end side of the air piston 46 incorporated in the air chamber 43, the rod 47 advances in the direction along the axis against the return spring 49. That is, the air chamber 43 is attached to the brake main body 11 and operates with the rod 47 capable of moving forward and backward.

  The lever mechanism unit 101 is fixed integrally with the air chamber 43, and is inserted so that the rod 47 from the air chamber 43 can move forward and backward in a direction approaching and separating from the pad assembly 33. The lever mechanism unit 101 houses a lever mechanism 95. The lever mechanism unit 101 is configured such that when the rod 47 advances, the lever pin 53 as an input member of the lever mechanism 95 shown in FIG. 7 is pressed.

FIG. 9 is a longitudinal sectional view in a direction orthogonal to the suspension shaft 37 shown in FIG.
The lever mechanism 95 has a pair of cam levers 15. The cam lever 15 has one end 55 shown in FIG. 7 rotatably connected to a cam holder 57 connected to the one end 23 of the brake arm 13. As shown in FIG. 7, the other end 59 of each of the pair of cam levers 15 is rotatably connected to a lever pin 53 connected to a swing joint member 105 into which the rod 47 is inserted.

  As shown in FIG. 7, the cam holder 57 holds the eccentric cams 17 rotatably. The eccentric cam 17 is rotatably connected to the cam lever 15 via a rotation center shaft 61 provided at one end 55 of the cam lever 15. The eccentric cam 17 boosts the force transmitted by the rotation of the cam lever 15 to rotate the brake arm 13 about the support portion 27 as a rotation fulcrum.

  The lever mechanism unit 101 is provided with a lever holding member 19 shown in FIG. The lever holding member 19 guides the rotation center shaft 61 on a straight line X along the expanding direction of the one end 23 of the pair of brake arms 13.

  As shown in FIG. 7, the eccentric cam 17 is rotatably connected to the rotation center shaft 61 at a position offset from the rotation center line 63 of the cam with respect to the cam holder 57. The eccentric cam 17 rotates (moves) the rotation center line 63 of the cam along an arc-shaped trajectory around the rotation center axis 61 by the rotation of the cam lever 15.

FIG. 10A is a perspective view of the power unit 99 shown in FIG. 7, and FIG. 10B is an exploded perspective view of the power unit 99 shown in FIG.
In the power unit 99, the link rod 85 protrudes from both sides of the lever mechanism unit 101 through the cover member 103. The link rod 85 presses the one end 23 of the brake arm 13 in the expanding direction. The lever mechanism unit 101 houses a lever mechanism 95. The lever mechanism 95 constitutes a drive direction conversion mechanism.

FIG. 11A is a perspective view of the lever mechanism 95 shown in FIG. 17, and FIG. 11B is an exploded perspective view of the lever mechanism 95 shown in FIG.
The lever mechanism 95 converts the moving force of the rod 47 in the reciprocating direction into a driving force in the expanding direction for expanding and swinging the one end 23 of the pair of brake arms 13.

  A follow-up mechanism 97 is provided between the rod 47 and the lever pin 53 of the lever mechanism 95. The follow-up mechanism 97 operates to cause the lever pin 53 to follow the rod 47 in response to a position change of the lever mechanism 95 with respect to the rod 47.

FIG. 12 is a perspective view of a main part of the lever mechanism 95 shown in FIG.
The eccentric cam 17 is formed in a cylindrical shape with the rotation center line 63 (see FIG. 7) of the cam as a central axis. The eccentric cam 17 is rotatably held in a cylindrical cam holding hole 65 formed in the cam holder 57. A cylindrical bearing bush 67 is inserted between the eccentric cam 17 and the cam holding hole 65. The bearing bush 67 reduces friction between the eccentric cam 17 and the cam holding hole 65.

  The rotation center shaft 61 is guided via a bearing 69 to a guide groove 71 (see FIG. 11) formed in the lever holding member 19. The inner ring of the bearing 69 is fixed to the rotation center shaft 61. The bearing 69 has an outer ring rotatably provided on the inner ring via a plurality of rolling elements. The outer periphery of the outer ring of the bearing 69 is guided by the guide groove 71.

  In the eccentric cam 17, a lock pin 73 penetrates the opposite side of the rotation center axis 61 with respect to the rotation center line 63 of the cam. Further, the lock pin 73 penetrating the eccentric cam 17 penetrates the cam lever 15. That is, the cam lever 15 and the eccentric cam 17 are connected to each other so that the rotation center shaft 61 and the lock pin 73 penetrate therethrough so that they cannot rotate relative to each other.

  The cam lever 15 is constituted by a pair of lever members 75 that sandwich the eccentric cam 17 connected via the rotation center shaft 61 from the direction of the rotation center line 63 of the cam. Therefore, the cam lever 15 is constituted by a total of four lever members 75 in two pairs with the eccentric cam 17 interposed therebetween. One end 55 of each of the lever members 75 is fixed to the eccentric cam 17 by fastening a washer 77 and a nut 79 to a distal end of a rotation center shaft 61 that passes through a bearing 69. The eccentric cams 17 are rotatable at cam holding holes 65 of the respective cam holders 57.

  An adjuster mechanism 81 is provided on the cam holder 57. The adjuster mechanism 81 has a link rod 85 serving as an output shaft that enables the connection position of the one end 23 of the brake arm 13 to the rotation center line 63 of the cam via the connection member 83 by rotation. The link rod 85 includes an adjustment gear 87. An adjuster lever 91 biased by an adjuster spring 89 meshes with the teeth of the adjustment gear 87. When the wear amount of the lining 31 becomes equal to or more than a certain amount, the adjuster lever 91 sends out the link rod 85 at a position where the adjustment gear 87 is rotated by one peak, and then meshes with the adjustment gear 87 to rotate the adjustment gear 87. regulate.

  As shown in FIG. 11, the follow-up mechanism 97 includes a swing joint member 105. The swing joint member 105 has a pair of fitting holes 107 that rotatably support the respective lever pins 53. The swing joint member 105 has a pivot bearing hole 109 on a side surface orthogonal to the surface on which the fitting hole 107 is formed. The pivot bearing hole 109 is formed in a substantially conical shape having a small inner diameter in the depth direction. The pivot bearing hole 109 pivotally supports the distal end of the rod 47 that moves forward and backward in a direction perpendicular to the direction in which the brake arm 13 expands.

FIG. 13A is a horizontal sectional view of the power unit 99 shown in FIG. 10, and FIG. 13B is a schematic configuration diagram of the lever mechanism 95 shown in FIG.
When the compressed air is supplied to the air chamber 48 at the rear end side of the air piston 46 built in the air chamber 43, the power unit 99 advances the rod 47 to the lever mechanism unit 101. The rod 47 that has advanced to the lever mechanism unit 101 presses the swing joint member 105 of the lever mechanism 95. When the swing joint member 105 is pressed, the lever mechanism 95 presses the lever pin 53 fitted in the fitting hole 107. The lever mechanism 95 moves the cam holder 57 in the expanding direction by the cam lever 15 via the eccentric cam 17 when the lever pin 53 is pressed.

Next, the operation of the disc brake device 200 will be described.
In the disc brake device 200 according to the second embodiment, the brake body 11 is supported by the vehicle body. An air chamber 43 is fixed to the brake body 11. The air chamber 43 moves the rod 47 forward and backward. A pair of brake arms 13 are rotatably supported by the brake body 11. The support portion 27 between the one end 23 and the other end 25 of the brake arm 13 is supported by the brake main body 11 via a rotation shaft 29 and is rotatable. The lever mechanism 95 converts the moving force of the rod 47 in the advancing direction into a direction in which the one ends 23 of the pair of brake arms 13 are expanded. A pair of brake arms 13 whose one ends are expanded respectively press pad brakes 35 attached to both ends of a brake rotor 35 disposed on both surfaces of the wheel from both sides.

  A position change may occur between the rod 47 as the output member and the lever mechanism 95 due to the inclination of the brake rotor 35 or the phase difference between the sprung and unsprung portions. Due to this position change, the rod 47 and the lever pin 53 of the lever mechanism 95 are disengaged. The follow-up mechanism 97 absorbs this deviation, and maintains the rod 47 and the lever pin 53 in a connected state in which force can be transmitted even when a positional change occurs.

The boosting operation by the lever mechanism 95 of the disc brake device 200 according to the second embodiment is the same as that of the disc brake device 100 according to the first embodiment, and a description thereof will be omitted.
In the disc brake device 200 according to the second embodiment, the swing joint member 105 is formed with the fitting hole 107 that rotatably supports the input member of the lever mechanism 95. The swing joint member 105 is provided with a pivot bearing hole 109 for pivotally supporting the distal end of the rod 47 which moves forward and backward in a direction perpendicular to the direction in which the brake arm 13 expands. When the rod 47 advances, the follow-up mechanism 97 presses the pivot bearing hole 109 of the swing joint member 105. The pressed swing joint member 105 presses the lever pin 53 of the lever mechanism 95 inserted in the fitting hole 107 in the same direction.

FIG. 14A is an explanatory diagram of the operation when the disc brake device 200 shown in FIG. 7 is released, and FIG. 14B is an explanatory diagram of the operation of the disc brake device 200 shown in FIG. 7 during normal braking. .
At this time, the positional change between the rod 47 and the lever pin 53 caused by the inclination of the brake rotor 35 is absorbed by the rod 47 rotating in the fitting hole 107 of the swing joint member 105.

FIG. 15A is a diagram illustrating the operation of the disk brake device 200 shown in FIG. 14 when the brake rotor is tilted, and FIG. 15B is a diagram illustrating the operation of the disk brake device 200 shown in FIG. FIG.
In addition, the positional change between the rod 47 and the lever pin 53 caused by the phase difference between the sprung and unsprung portions is caused by the movement of the lever mechanism 95 shown in FIG. This positional fluctuation is absorbed by the pivot movement of the swing joint member 105 with respect to the distal end of the rod 47.

[Third embodiment]
Next, a disc brake device 300 according to a third embodiment of the present invention will be described.
FIG. 16 is a perspective view showing the entire structure of the disc brake device 300 according to the third embodiment of the present invention. In the third embodiment, members and portions equivalent to those in the first embodiment are denoted by the same reference numerals and described.
The disc brake device 300 has, as main members, a brake body 11, a brake arm 13, a motor gear unit 111 as an actuator, a lever mechanism 113 as a drive direction changing mechanism, and a follow-up mechanism 115.
The brake body 11 is supported by a mounting member 21 fixed to the vehicle body.

FIG. 17 is a horizontal sectional view of the disc brake device 300 shown in FIG.
In the pair of brake arms 13, a support 27 between one end 23 and the other end 25 is rotatably supported by a rotation shaft 29 with respect to the brake body 11. A pad assembly 33 having a plurality of linings 31 is attached to the other end 25 of each of the pair of brake arms 13. The pair of brake arms 13 are expanded in the direction in which the one end portions 23 are separated from each other, and press the brake rotors 35 arranged on both surfaces of the wheel with the pair of pad assemblies 33 from both sides.

FIG. 18 is a side sectional view of the disc brake device 300 shown in FIG.
In the disc brake device 300, the brake main body 11 is rotatably held by the suspension shaft 37. Thus, the brake body 11 is supported by the mounting member 21 mounted on the vehicle body via the suspension shaft 37. The suspension shaft 37 is sandwiched between the rotation shafts 29 of the pair of brake arms 13 and extends in a direction perpendicular to these and along the wheel track.

  A spring member 39 is provided between the brake body 11 and the mounting member 21 (see FIG. 1). The spring member 39 urges the brake main body 11 in a direction for suppressing the swing.

  A power unit 117 as a power generation source is fixed to the brake body 11. The power unit 117 includes an electromagnetic holding brake 119, a motor gear unit 111 as an actuator, a spring unit 121, and a lever mechanism unit 123.

  The electromagnetic holding brake 119 is provided with a solenoid 125 for electromagnetic holding. The electromagnetic holding brake 119 applies an axial force to the ball screw 127 by energizing the solenoid 125, thereby enabling the lever mechanism 113 to be driven directly.

  The motor gear unit 111 includes a ball screw 127 that passes through the spring unit 121 and reaches the lever mechanism unit 123. A ball nut 129 as an output member is screwed into the ball screw 127. When the ball screw 127 is rotated by driving the motor gear unit 111, the ball nut 129 moves forward and backward in a direction orthogonal to the expanding direction.

  The linear joint member 131 is fixed to the ball nut 129. The linear motion joint member 131 advances and retreats inside the lever mechanism unit 123 together with the ball nut 129. The lever mechanism unit 123 houses the lever mechanism 113. The lever mechanism unit 123 is configured such that the lever pin 53, which is an input member of the lever mechanism 113, is pressed when the ball nut 129 and the linear motion joint member 131 advance.

  The spring unit 121 includes a plurality (three in this embodiment) of coil springs 133 at equal intervals in the circumferential direction around the ball screw 127. The spring unit 121 accumulates a return urging force when the electromagnetic holding brake 119 is operated.

FIG. 19 is a longitudinal sectional view in a direction orthogonal to the suspension shaft 37 shown in FIG.
The lever mechanism 113 has a pair of cam levers 15. The cam lever 15 has one end 55 shown in FIG. 17 rotatably connected to a cam holder 57 connected to one end 23 of the brake arm 13. As shown in FIG. 17, the other ends 59 of the pair of cam levers 15 are rotatably connected to lever pins 53 connected to a linear motion joint member 131 integrally fixed to the ball screw 127.

  As shown in FIG. 17, the cam holder 57 holds the eccentric cams 17 rotatably. The eccentric cam 17 is rotatably connected to the cam lever 15 via a rotation center shaft 61 provided at one end 55 of the cam lever 15. The eccentric cam 17 boosts the force transmitted by the rotation of the cam lever 15 to rotate the brake arm 13 about the support portion 27 as a rotation fulcrum.

  The lever mechanism unit 123 is provided with a lever holding member 19 shown in FIG. The lever holding member 19 guides the rotation center shaft 61 on a straight line X along the expanding direction of the one end 23 of the pair of brake arms 13.

  As shown in FIG. 17, the eccentric cam 17 is rotatably connected to the rotation center shaft 61 at a position offset from the rotation center line 63 of the cam with respect to the cam holder 57. The eccentric cam 17 rotates (moves) the rotation center line 63 of the cam along an arc-shaped trajectory around the rotation center axis 61 by the rotation of the cam lever 15.

20A is a perspective view of the power unit 117 shown in FIG. 17, and FIG. 20B is an exploded perspective view of the power unit 117 shown in FIG.
The power unit 117 has a link rod 85 protruding from both sides of the lever mechanism unit 123 through the cover member 103. The link rod 85 presses the one end 23 of the brake arm 13 in the expanding direction. The lever mechanism unit 123 houses the lever mechanism 113. The lever mechanism 113 constitutes a drive direction conversion mechanism.

21A is a perspective view of the lever mechanism 113 shown in FIG. 17, and FIG. 21B is an exploded perspective view of the lever mechanism 113 shown in FIG.
The lever mechanism 113 converts a moving force of the ball nut 129 in the reciprocating direction into a driving force in the expanding direction for expanding and swinging the one end 23 of the pair of brake arms 13.

  A follow-up mechanism 115 is provided between the ball nut 129 and the lever pin 53 of the lever mechanism 113. The follow-up mechanism 115 is configured by a linear motion joint member 131 fixed to the ball nut 129. The linear motion joint member 131 has a slide groove 135 that supports the lever pin 53 movably in the expanding direction, and moves forward and backward in a direction perpendicular to the expanding direction.

FIG. 22 is a perspective view of a main part of the lever mechanism 113 shown in FIG.
The other end 59 of the pair of cam levers 15 is rotatably connected by lever pins 53. The lever pin 53 is inserted into the slide groove 135 of the linear motion joint member 131. The linear motion joint member 131 has a slide groove 135 on each of a pair of parallel outer surfaces. The pair of lever pins 53 are inserted into these slide grooves 135, respectively. The lever pin 53 inserted in the slide groove 135 can rotate within the slide groove and can move along the slide groove 135. In the lever mechanism 113, the other configurations of the eccentric cam 17, the rotation center shaft 61, the cam lever 15, the cam holder 57, and the lever holding member 19 are the same as those of the lever mechanism 95 described above.

FIG. 23 is a horizontal sectional view of the power unit 117 shown in FIG.
When power is supplied to the motor gear unit 111, the power unit 117 rotates the ball screw 127. The power unit 117 rotates the ball screw 127 to advance the ball nut 129 whose relative rotation is restricted, that is, the linear motion joint member 131, to the lever mechanism unit 123. The linear motion joint member 131 that has advanced to the lever mechanism unit 123 presses the lever pin 53 of the lever mechanism unit 123. The lever mechanism 113 moves the cam holder 57 in the expanding direction by the cam lever 15 via the eccentric cam 17 when the lever pin 53 is pressed.

Next, the operation of the disc brake device 300 will be described.
In the disc brake device 300 according to the third embodiment, the follow-up mechanism 115 has the direct-acting joint member 131. The linear motion joint member 131 is fixed to a ball nut 129 that moves forward and backward in a direction perpendicular to the direction in which the brake arm 13 expands. The linear motion joint member 131 has a slide groove 135 that supports the lever pin 53 of the lever mechanism 113 that is a drive direction conversion mechanism so as to be movable in the direction in which the brake arm 13 expands. When the ball nut 129 advances, the following mechanism 115 presses the lever pin 53 supported by the slide groove 135 in the direction perpendicular to the advance direction in the same direction.

  The boosting operation by the lever mechanism 113 of the disc brake device 300 according to the third embodiment is the same as that of the disc brake device 100 according to the first embodiment, and thus the description is omitted.

  A pair of brake arms 13 with one ends thereof expanded open press pad brakes 35 from both sides, on which pad assemblies 33 attached to the other end 25 are arranged on both surfaces of the wheel.

  A position change may occur between the rod 47 as the output member and the lever mechanism 113 due to the inclination of the brake rotor 35 or the phase difference between the sprung and unsprung portions. Due to this positional change, the ball nut 129 as an output member and the lever pin 53 as an input member of the lever mechanism 113 are disengaged. The follow-up mechanism 115 absorbs this deviation, and maintains the ball nut 129 and the lever pin 53 in a connected state in which force can be transmitted even when a positional change occurs.

  When the ball nut 129 advances, the follower mechanism 115 causes the slide groove 135 of the linear motion joint member 131 to press the lever pin 53 of the lever mechanism 113 in the same direction.

FIG. 24A is an operation explanatory diagram of the disc brake device 300 shown in FIG. 17 when it is released, and FIG. 24B is an operational explanatory diagram of the disc brake device 300 shown in FIG. 17 during normal braking. .
At this time, the position fluctuation between the ball nut 129 and the lever pin 53 caused by the inclination of the brake rotor 35 is absorbed by the rotation of the lever pin 53 in the slide groove 135.

FIG. 25A is a diagram illustrating the operation of the disk brake device 300 shown in FIG. 17 when the brake rotor is tilted, and FIG. 25B is a diagram illustrating the operation of the disk brake device 300 shown in FIG. 17 when a vertical phase occurs. FIG.
In addition, the position fluctuation between the ball nut 129 and the lever pin 53 caused by the phase difference between the sprung and unsprung portions is caused by the movement of the lever mechanism 113 shown in FIG. 25B in the direction of the arrow. This positional fluctuation is absorbed by the movement of the lever pin 53 along the slide groove 135.

  Therefore, according to the disc brake devices 100, 200, and 300 according to the present embodiment, the power generation source can be reduced in size.

  It should be noted that the present invention is not limited to the above-described embodiment, and can be appropriately modified and improved. In addition, the material, shape, dimension, number, location, and the like of each component in the above-described embodiment are arbitrary and not limited as long as the present invention can be achieved.

Here, the features of the above-described embodiments of the disk brake device according to the present invention will be briefly summarized and listed below.
[1] a brake body (11) supported by a vehicle body;
A support (27) between one end (23) and the other end (25) is rotatably supported with respect to the brake body, and a pad assembly (33) attached to the other end is provided. A pair of brake arms (13) for pressing the brake rotor (35) from both sides;
An actuator (air chamber 43, motor gear unit 111) that is attached to the brake body and moves the output member (rod 47, ball nut 129) forward and backward;
One end (55) is rotatably connected to a cam holder (57) connected to the one end, and the other end (59) is connected to an input member (lever pin 53) connected to the output member. A pair of cam levers (15) rotatably connected to each other,
The force transmitted by the rotation of the cam lever rotatably held by the cam holders and rotatably connected via a rotation center shaft (61) provided at the one end is boosted to support the power. An eccentric cam (17) for rotating the brake arm about a portion as a rotation fulcrum;
A lever holding member (19) for guiding the rotation center axis on a straight line (X) along the expanding direction of the pair of the one end portions;
A disc brake device (100, 200, 300) comprising:
[2] The disc brake device according to the above [1],
The eccentric cam (17) is rotatably connected to the rotation center shaft (61) at a position offset from a rotation center line (63) of the cam with respect to the cam holder (57), and is connected to the cam lever (15). By rotating, the rotation center line of the cam is rotated in an arc around the rotation center axis,
Disc brake device (100, 200, 300) characterized by the above-mentioned.
[3] The disc brake device according to the above [2],
The eccentric cam (17) formed in a cylindrical shape with the rotation center line (63) of the cam as a central axis is rotatably inserted into a cylindrical cam holding hole (65) formed in the cam holder (57). Retained,
Disc brake device (100, 200, 300) characterized by the above-mentioned.
[4] The disc brake device according to any one of [2] to [3],
The rotation center shaft (61) is guided via a bearing (69) to a guide groove (71) formed in the lever holding member (19).
Disc brake device (100, 200, 300) characterized by the above-mentioned.
[5] The disc brake device according to any one of [2] to [4],
The cam lever (15) includes a pair of lever members (75) that sandwich the eccentric cam (17) rotatably connected via the rotation center shaft (61) from the direction of the rotation center line (63) of the cam. ),
Disc brake device (100, 200, 300) characterized by the above-mentioned.
[6] The disc brake device according to any one of [2] to [5],
The cam holder (57) has an adjuster mechanism (27) for extending the connecting position of the one end (23) with respect to the rotation center line (63) of the cam according to the wear amount of the lining (31) of the pad assembly (33). 81) is provided,
A disc brake device (100, 200, 300) characterized by the above-mentioned.
[7] The disc brake device according to any one of [1] to [6],
The brake body (11) supported by the mounting member (21) mounted on the vehicle body is sandwiched between the rotation shafts (29) of the pair of brake arms (13) in a direction perpendicular to the rotation axes. The hanging member (37) of the extending mounting member is rotatably held by a hanging shaft (37),
A spring member (39) provided between the brake body and the mounting member and biasing the brake body in a direction for suppressing swinging is provided together with the actuator (the air chamber 43 and the motor gear unit 111). Fixed to the body,
A disc brake device (100, 200, 300) characterized by the above-mentioned.

DESCRIPTION OF SYMBOLS 11 ... Brake body 13 ... Brake arm 15 ... Cam lever 17 ... Eccentric cam 19 ... Lever holding member 21 ... Attaching member 23 ... One end 25 ... Other end 27 ... Support part 29 ... Rotating shaft 31 ... Lining 33 ... Pad assembly 35 ... Brake rotor 37 ... Suspension shaft 39 ... Spring member 43 ... Air chamber (actuator)
47… Rod (output member)
53 ... Lever pin (input member)
55 ... one end 57 ... cam holder 59 ... other end 61 ... rotation center shaft 63 ... cam rotation center line 65 ... cam holding hole 69 ... bearing 71 ... guide groove 75 ... lever member 81 ... adjuster mechanism

Claims (7)

A brake body supported by the vehicle body,
A support portion between one end and the other end is rotatably supported with respect to the brake main body, and a pair of pad arms respectively attached to the other end are provided with a pair of brake arms for pressing the brake rotor from both sides. ,
An actuator attached to the brake body for moving the output member forward and backward;
A pair of cam levers, one end of which is rotatably connected to a cam holder connected to the one end, and the other end is rotatably connected to an input member connected to the output member; ,
Each of the cam holders is rotatably held by the cam holder, and the force transmitted by the rotation of the cam lever rotatably connected via a rotation center shaft provided at the one end is boosted to rotate the support portion. An eccentric cam for rotating the brake arm about a fulcrum,
A lever holding member that guides the rotation center axis on a straight line along the expanding direction of the pair of the one end portions,
A disc brake device comprising: The disc brake device according to claim 1, wherein
The eccentric cam is rotatably connected to the rotation center axis at a position offset from a rotation center line of the cam with respect to the cam holder, and rotation of the cam about the rotation center axis by rotation of the cam lever. Rotate the center line in an arc,
A disk brake device characterized by the above-mentioned. The disc brake device according to claim 2, wherein
The eccentric cam formed in a cylindrical shape having a rotation axis of the cam as a central axis is rotatably held in a cylindrical cam holding hole formed in the cam holder.
A disk brake device characterized by the above-mentioned. The disc brake device according to any one of claims 2 to 3,
The rotation center axis is guided by a guide groove formed in the lever holding member via a bearing,
A disk brake device characterized by the above-mentioned. The disc brake device according to any one of claims 2 to 4, wherein
The cam lever is configured by a pair of lever members that sandwich the eccentric cam rotatably connected via the rotation center shaft from the rotation center line direction of the cam.
A disk brake device characterized by the above-mentioned. The disc brake device according to any one of claims 2 to 5, wherein
The cam holder is provided with an adjuster mechanism for extending a connection position of the one end with respect to a rotation center line of the cam in accordance with a wear amount of a lining of the pad assembly.
A disk brake device characterized by the above-mentioned. The disc brake device according to any one of claims 1 to 6, wherein
The brake body supported by a mounting member mounted on the vehicle body is rotatably supported by a hanging shaft of the mounting member which is sandwiched between rotation shafts of the pair of brake arms and extends in a direction orthogonal to these. Retained
A spring member provided between the brake body and the mounting member and biasing in a direction to suppress the swing of the brake body is fixed to the brake body together with the actuator.
A disk brake device characterized by the above-mentioned.

Images