WO2017090734A1

WO2017090734A1 - Brake device

Info

Publication number: WO2017090734A1
Application number: PCT/JP2016/084991
Authority: WO
Inventors: 鈴木　努
Original assignee: Ｋｙｂ株式会社
Priority date: 2015-11-26
Filing date: 2016-11-25
Publication date: 2017-06-01
Also published as: JP6609171B2; JP2017096436A

Abstract

A brake device (100) that comprises: a pair of link arms (30) that are respectively provided to face either side of a brake disc (1a) and that have a support part (32) that is between one end part (31) and another end part (33) and that is rotatably supported on a brake main body (10), the one end parts (31) being connected to each other by a connection member (35), and the other end parts (33) each supporting a brake lining (2) that is in sliding contact with and applies friction to the brake disc (1a); an actuator (20) that is provided to the connection member (35) and that makes an output member (21) move back and forth; a lever (40) that moves rotationally as a result of the back and forth movement of the output member (21); an eccentric cam (51) that is provided to the one end part (31) of one of the pair of link arms (30) and that rotates around a rotational axis (A1) as a result of the rotational movement of the lever (40); and a pressing member (61) that moves back and forth in association with the rotation of the eccentric cam (51), presses the other one end part (31), and increases/decreases the distance between the one one end part (31) and the other one end part (31).

Description

Brake device

The present invention relates to a brake device.

Conventionally, the force of an actuator is applied to the force point of a pair of link arms that can rotate around a fulcrum, and the brake lining supported by the point of action of the link arm is brought into sliding contact with the brake disc to brake the rotation of the wheel. A brake device is used.

In JP10-505038A, one end of a caliper lever is connected to each other, and the other end is pivotally attached to each brake pad. An eccentric transmission device provided at a fulcrum between both ends of the caliper lever includes a caliper lever. A brake caliper unit that pivots is disclosed. The eccentric body transmission device has an eccentric pin that rotates in response to a force generated by a brake force generator, and rotates the caliper lever around one end by the rotation of the eccentric pin.

However, in the caliper brake unit of JP10-505038A, the circumferential tangential force that acts on the brake pad from the brake disk during braking when the brake pad slides on the brake disk acts on the eccentric pin of the eccentric body transmission device. Therefore, a large force is required to rotate the eccentric pin during braking, and it has been difficult to improve mechanical efficiency.

This invention aims at improving the mechanical efficiency of a brake device.

According to an aspect of the present invention, a brake device that clamps and brakes a brake disk that rotates with a wheel includes a brake main body supported by a vehicle body or a carriage, and one end and the other end with respect to the brake main body. A support portion is rotatably supported and provided on both sides of the brake disc, the one end portions are connected by a connecting member, and the other end portions are slidably contacted with the brake disc and rubbed. A pair of link arms that support a brake lining that applies force; an actuator that is provided on the connecting member to move the output member forward and backward; and a lever that is pivotally connected to the output member and that is rotated by the forward and backward movement of the output member. And an eccentric cam that is provided at one end of one of the pair of link arms and rotates about a rotation axis by rotation of the lever; And forward and backward with the rotation of the serial eccentric cam presses the other of the one end, and a pressing member for scaling the distance between one of the end portion and the other of the one end.

FIG. 1 is a plan view of a brake device according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the periphery of the connecting member in the brake device. FIG. 3 is a diagram for explaining the positional relationship between the lever and the adjuster in the height direction.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

First, the configuration of the brake device 100 according to the embodiment of the present invention will be described with reference to FIGS. 1 to 3.

The brake device 100 is mainly applied to a railway vehicle. The brake device 100 brakes the wheel 1 by sandwiching a brake disc 1 a that rotates together with the wheel 1. Specifically, as shown in FIG. 1, the brake device 100 sandwiches the brake disc 1 a from both sides with a pair of brake linings 2, and the friction force between the brake disc 1 a and the brake lining 2 causes the wheels 1 to move. Brakes rotation.

The brake disc 1a is formed on both front and back surfaces of the wheel 1 and rotates integrally with the wheel 1. Instead of the structure in which the brake disk 1a is formed integrally with the wheel 1, a separate brake disk 1a that rotates together with the wheel 1 may be provided.

The brake lining 2 is opposed to the brake disk 1a with a predetermined interval (state shown in FIG. 1) when not braking. During braking, the brake lining 2 moves toward the brake disc 1a and is pressed against the brake disc 1a in parallel.

The brake lining 2 includes a back plate portion 2a supported by the lining holding portion 3 of the brake device 100, and a friction member 2b that contacts the brake disc 1a during braking. The friction member 2b includes a plurality of segments and is fixed to the surface of the back plate portion 2a. The brake lining 2 brakes the rotation of the wheel 1 by the frictional force generated by the contact between the friction member 2b and the brake disc 1a.

The lining holding part 3 has a dovetail groove (not shown) into which the back plate part 2a of the brake lining 2 is inserted. Anchor blocks 4 that are fixed to the lining holder 3 by a pair of anchor bolts 5 are respectively provided at the upper and lower ends of the lining holder 3. The anchor block 4 fixes the end of the back plate portion 2a of the brake lining 2 in the longitudinal direction (the direction perpendicular to the paper surface in FIG. 1). Thereby, the brake lining 2 inserted in the dovetail is held by the lining holding part 3.

As shown in FIG. 1, the brake device 100 includes a pair of link arms on which a brake body 10 and a support portion 32 between one end portion 31 and the other end portion 33 are rotatably supported with respect to the brake body 10. 30, a connecting member 35 that connects the end portions 31 of the link arm 30, an actuator 20 that is provided on the connecting member 35 and advances and retracts the rod 21 as an output member, and the rod 21 that is rotatably connected to the rod 21. The link arm 30 is provided at one of the lever 40 and the one end portion 31 of the pair of link arms 30 which are rotated by advancing and retreating, and the force transmitted by the rotation of the lever 40 is boosted to support the support 32 as a fulcrum. Adjuster that maintains a constant clearance between the brake unit 1a and the brake disc 1a when wear of the brake lining 2 proceeds. Including 0 and, the.

The brake body 10 is supported by a carriage (not shown) when the brake device 100 is applied to a railway vehicle. The brake body 10 is supported by a vehicle body (not shown) when the brake device 100 is applied to a vehicle other than a railway vehicle.

As shown in FIG. 2, the actuator 20 is a fluid pressure actuator that is actuated by the pressure of the working fluid such as hydraulic pressure such as hydraulic pressure or air pressure. Actuator 20 operates based on a driver's braking operation, and moves rod 21 forward and backward. The actuator 20 may be other types such as a mechanical actuator that operates by rotation of an electric motor.

The actuator 20 includes a diaphragm 22 as an elastic film that elastically deforms due to the pressure of the working fluid and moves the rod 21 back and forth, and a return spring 23 that biases the rod 21 against the pressure of the working fluid.

The diaphragm 22 is sandwiched between the case 20a and the cover 20b, and defines a pressure chamber (not shown) between the cover 20b. The diaphragm 22 is deformed when the working fluid is supplied to and discharged from the pressure chamber.

The rod 21 advances and retreats with the deformation of the diaphragm 22. Specifically, when the working fluid is supplied to the pressure chamber, the rod 21 retreats in the direction in which the brake device 100 enters a braking state, and when the working fluid is discharged from the pressure chamber, the rod device 100 Enter in the direction of the non-braking state. The rod 21 has a flat portion 21 a that is in surface contact with the diaphragm 22.

The rod 21 advances and retreats with respect to the brake body 10 and can swing in the direction in which the brake lining 2 can move (left and right in FIG. 1). The center of the brake disc 1a is located on the extension line of the central axis along which the rod 21 reciprocates.

The return spring 23 pushes the rod 21 back in the direction in which the brake device 100 is in a non-braking state. When the working fluid is supplied to the pressure chamber, and the force by which the working fluid in the pressure chamber pushes the rod 21 overcomes the urging force of the return spring 23, the rod 21 is pushed out in the direction in which the brake device 100 enters the braking state.

The link arms 30 are respectively provided facing both surfaces of the brake disc 1a. One end portions 31 of the pair of link arms 30 are connected by a connecting member 35. The other end portion 33 of the link arm 30 supports the brake lining 2 slidably in contact with the brake disc 1a to apply a frictional force so as to be swingable. The link arm 30 has a pair of arm portions 30a provided at the top and bottom.

As shown in FIG. 1, one end 31 of one link arm 30 is provided with a connecting shaft 31 a that penetrates and connects the connecting member 35 and the link arm 30. One end 31 of the other link arm 30 is connected through the connecting member 35, the link arm 30, and the pair of levers 40 so as to boost the force generated by the advancement and retraction of the rod 21 of the actuator 20. Is provided. The booster unit 50 will be described later in detail.

The support portion 32 of the link arm 30 is provided with an arm shaft 32 a that penetrates and connects the link arm 30 and the brake body 10. The link arm 30 is rotatably supported by the brake body 10 by an arm shaft 32a. A circumferential tangential force acting on the brake lining 2 from the brake disc 1a during braking of the brake device 100 acts on the brake body 10 from the support portion 32 via the arm shaft 32a.

The other end portion 33 of the link arm 30 is provided with a lining shaft 33 a that penetrates and connects the link arm 30 and the lining holding portion 3. The lining holding part 3 is rotatably supported by the link arm 30 by the lining shaft 33a. As a result, the brake lining 2 can swing with respect to the link arm 30 and can always abut against the brake disc 1a in parallel during braking.

As shown in FIG. 2, the lever 40 transmits the force generated by the forward / backward movement of the rod 21 of the actuator 20 to the booster unit 50. One end 41 of the lever 40 is rotatably connected to the rod 21. The other end portion 42 of the lever 40 is connected to a small diameter portion 52 as a rotating portion described later of the booster unit 50. The lever 40 rotates between the rod 21 and the small diameter portion 52 when the rod 21 advances and retreats with respect to the brake body 10. As shown in FIG. 3, a pair of levers 40 are provided vertically so as to avoid other members such as the adjuster 60.

The booster unit 50 includes an eccentric cam 51 that is provided at one end portion 31 of the pair of link arms 30 and rotates about the rotation axis A <b> 1 by the rotation of the lever 40. The eccentric cam 51 presses a sleeve 61 as a pressing member described later of the adjuster 60. The sleeve 61 advances and retreats with the rotation of the eccentric cam 51, presses the other end portion 31 of the pair of link arms 30, and expands or contracts the distance between the one end portion 31 and the other end portion 31. In the present embodiment, the sleeve 61 of the adjuster 60 functions as a pressing member. However, an independent pressing member may be provided separately from the adjuster 60.

The eccentric cam 51 has a pair of small diameter portions 52 that are rotatably connected to one end portion 31 of the link arm 30 and rotate around the rotation axis A1, and a center axis A2 that is offset from the rotation axis A1. , And an eccentric portion 53 formed to have a larger diameter than the small diameter portion 52. The rotational axis A1 of the eccentric cam 51 is provided such that the position with respect to the link arm 30 is the same position as the central axis of the connecting shaft 31a.

The small diameter portion 52 is formed to have a smaller diameter than the eccentric portion 53. The central axis of the small diameter portion 52 is the rotation axis A1 of the eccentric cam 51. The other end portion 42 of the lever 40 is connected to each of the pair of small diameter portions 52 so as not to be relatively rotatable. Therefore, when the rod 21 moves back and forth and the lever 40 rotates, the small diameter portion 52 rotates around the rotation axis A1.

The eccentric part 53 is provided between the pair of small diameter parts 52. That is, the small diameter portion 52 is provided on each side of the eccentric portion 53 in the axial direction. The eccentric portion 53 rotates in an arc shape with the distance between the rotation axis A1 and the center axis A2 as a radius around the rotation axis A1 by the rotation of the lever 40, and moves the sleeve 61 forward and backward.

The eccentric cam 51 has an eccentric portion 53 at the center in the axial direction, and has a small diameter portion 52 having a smaller diameter than the eccentric portion 53 at both ends thereof. Therefore, since the eccentric cam 51 has a small diameter from the center toward both ends, it is easy to process and assemble.

The adjuster 60 includes a sleeve 61 that is rotatably provided around the central axis in the case 20a, and a rod 62 that is inserted into the sleeve 61. The rod 62 has a threaded portion 62 a that is threadedly engaged with the sleeve 61.

When the wear of the brake lining 2 progresses beyond a specified amount, the sleeve 61 rotates through a link (not shown). As a result, the rod 62 moves out of the sleeve 61 by a size corresponding to the amount of wear of the brake lining 2. Thereby, the adjuster 60 always maintains the clearance between the brake disc 1a and the brake lining 2 at a constant size.

As shown in FIG. 2, the adjuster 60 is provided as a single assembly together with the actuator 20 and the booster unit 50, so that the degree of freedom in design is high.

Next, the operation of the brake device 100 will be described.

When the actuator 20 is actuated based on the driver's braking operation, the brake device 100 changes from the non-braking state (the state shown in FIG. 1) to the braking state.

When the actuator 20 is operated to supply the working fluid to the pressure chamber and the rod 21 is retracted, the lever 40 is rotated. The force by which the actuator 20 retracts the rod 21 is transmitted to the small diameter portion 52 of the eccentric cam 51 through the lever 40.

In the eccentric cam 51, the small-diameter portion 52 rotates around the rotation axis A1 by the force transmitted through the lever 40, and the eccentric portion 53 rotates in an arc shape around the rotation axis A1 in one direction ( It rotates counterclockwise in FIG. Thereby, the eccentric part 53 presses the sleeve 61, presses the other end part 31 of the pair of link arms 30, and enlarges the distance between the one end part 31 and the other end part 31.

Since the link arm 30 is rotatably supported by the brake body 10 by the support portion 32, when the one end portion 31 moves in a direction away from each other, the other end portion 33 moves in a direction close to each other. Therefore, the brake lining 2 moves toward the brake disc 1a and is pressed in contact with the brake disc 1a in parallel, so that the rotation of the wheel 1 is braked.

At this time, as shown in FIG. 2, the eccentric cam 51 is moved from the rod 21 to the lever 21 by the lever ratio between the length L3 of the lever 40 and the distance L4 between the rotation axis A1 and the center axis A2 of the eccentric portion 53. The force transmitted through 40 is doubled by L3 / L4 and transmitted to the link arm 30. Therefore, a large braking force can be obtained without providing a large actuator. Therefore, the brake device 100 can be reduced in size and weight.

Further, as shown in FIG. 1, the link arm 30 is supported such that the support portion 32 between the one end portion 31 and the other end portion 33 is rotatable with respect to the brake body 10. An eccentric cam 51 that rotates the link arm 30 by boosting the force transmitted to the rod 21 by the rotation of the lever 40 is provided at one end 31 of the link arm 30. Therefore, the circumferential tangential force that acts on the brake lining 2 from the brake disc 1 a during braking of the brake device 100 acts on the arm shaft 32 a of the support portion 32 and does not act on the eccentric cam 51. Therefore, since the frictional resistance when the eccentric cam 51 rotates does not increase, the mechanical efficiency during braking of the brake device 100 can be improved.

As shown in FIG. 1, the force transmitted from the eccentric cam 51 to the one end portion 31 of the link arm 30 is the distance L1 between the one end portion 31 and the support portion 32, and the support portion 32 and the other end portion 33. It is boosted to L1 / L2 times by the lever ratio with the distance L2 between them. In the brake device 100, since the distance L2 is larger than the distance L1, the force that presses the brake lining 2 against the brake disc 1a is greater than the force transmitted from the eccentric cam 51 to the one end 31 of the link arm 30. It becomes a small power.

However, in the brake device 100, the force transmitted from the rod 21 of the actuator 20 via the lever 40 by the eccentric cam 51 is boosted at a large magnification. Therefore, even if the link arm 30 is shortened to reduce the distance L1 in order to reduce the size and weight of the brake device 100, a sufficiently large braking force can be obtained.

In the brake device 100, the eccentric cam 51 is provided at the one end 31 of the link arm 30, so that the design freedom of the position of the arm shaft 32 a of the support portion 32 is increased. Therefore, it is possible to arrange the arm shaft 32 a at a position facing the side surface of the wheel 1. Therefore, the distance L1 can be made larger than the distance L2, and the force boosted by the eccentric cam 51 can be further boosted to press the brake lining 2 against the brake disc 1a.

Brake device 100 changes from a braking state to a non-braking state (the state shown in FIG. 1) when actuator 20 operates in a direction opposite to that during braking based on a driver's braking release operation.

When the actuator 20 is operated, the working fluid is discharged from the pressure chamber, and the rod 21 enters by the biasing force of the return spring 23, the lever 40 is pulled by the rod 21 and rotates. The force that causes the actuator 20 to enter the rod 21 is transmitted to the small diameter portion 52 of the eccentric cam 51 through the lever 40.

The eccentric cam 51 rotates in the other direction (clockwise in FIG. 1) when the eccentric portion 53 rotates in an arc shape around the rotation axis A1 by the force transmitted through the lever 40. Thereby, the one end part 31 of a pair of link arm 30 moves to the direction which adjoins mutually. Accordingly, the other end portions 33 of the pair of link arms 30 move in directions away from each other. As a result, the brake lining 2 is separated from the brake disc 1a, and the braking of the wheel 1 is released.

At this time, if the amount of wear of the brake lining 2 advances beyond the specified amount, the adjuster 60 functions and the rod 62 retracts from the sleeve 61. Thereby, the clearance between the brake disc 1a and the brake lining 2 is always maintained at a constant size.

According to the above embodiment, the following effects are obtained.

The link arm 30 is supported such that a support portion 32 between one end portion 31 and the other end portion 33 is rotatable with respect to the brake body 10. An eccentric cam 51 that rotates the link arm 30 by boosting the force transmitted to the rod 21 by the rotation of the lever 40 is provided at one end 31 of the link arm 30. Therefore, the circumferential tangential force that acts on the brake lining 2 from the brake disc 1 a during braking of the brake device 100 acts on the arm shaft 32 a of the support portion 32 and does not act on the eccentric cam 51. Therefore, since the frictional resistance when the eccentric cam 51 rotates does not increase, the mechanical efficiency during braking of the brake device 100 can be improved.

Hereinafter, the configuration, operation, and effect of the embodiment of the present invention will be described together.

In the present embodiment, a brake device 100 that clamps and brakes a brake disc 1a that rotates with a wheel 1 includes a brake body 10 supported by a vehicle body or a carriage, and one end 31 and the other end 33 with respect to the brake body 10. The support portions 32 are rotatably supported and are respectively provided on both sides of the brake disc 1a. One end portions 31 are connected to each other by a connecting member 35, and the other end portions 33 are connected to the brake disc 1a. A pair of link arms 30 that support the brake lining 2 that slides and applies a frictional force, an actuator 20 that is provided on the connecting member 35 and moves the rod 21 back and forth, and is pivotally connected to the rod 21 so that the rod 21 moves forward and backward. Is provided at one end 31 of one of the pair of link arms 30 and the lever 40 rotated by the rotation of the lever 40. The eccentric cam 51 that rotates about the rotation axis A1, and advances and retreats with the rotation of the eccentric cam 51 to press the other end portion 31, and the distance between the one end portion 31 and the other end portion 31 is increased. And a sleeve 61 that expands and contracts.

Further, in the present embodiment, the eccentric cam 51 is rotatably connected to one end portion 31 of the link arm 30, the lever 40 is connected to the small diameter portion 52 that rotates about the rotation axis A1, and the rotation axis A1. It has a center axis A2 at the offset position, and an eccentric portion 53 that rotates in a circular arc shape around the rotation axis A1 by the rotation of the lever 40 and advances and retracts the sleeve 61.

In these configurations, the link arm 30 is supported such that the support portion 32 between the one end portion 31 and the other end portion 33 is rotatable with respect to the brake body 10. An eccentric cam 51 that rotates the link arm 30 by boosting the force transmitted to the rod 21 by the rotation of the lever 40 is provided at one end 31 of the link arm 30. Therefore, the circumferential tangential force that acts on the brake lining 2 from the brake disc 1 a during braking of the brake device 100 acts on the arm shaft 32 a of the support portion 32 and does not act on the eccentric cam 51. Therefore, since the frictional resistance when the eccentric cam 51 rotates does not increase, the mechanical efficiency during braking of the brake device 100 can be improved.

Further, in the present embodiment, the small-diameter portion 52 is provided with a pair of small diameter portions 52 as compared to the eccentric portion 53, and the levers 40 are provided so as not to rotate relative to each other, and the eccentric portion 53 includes the pair of small diameter portions. 52 is provided.

In this configuration, the eccentric cam 51 has a small diameter from the center toward both ends, so that it is easy to process and assemble.

The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

For example, a needle bearing (not shown) as a rolling bearing may be provided on the outer periphery of the eccentric portion 53 of the eccentric cam 51. By providing the needle bearing on the outer periphery of the eccentric portion 53, it is possible to prevent the contact portion between the eccentric portion 53 and the sleeve 61 from rubbing when the actuator 20 is actuated, so that the mechanical efficiency of the brake device 100 can be improved.

This application claims priority based on Japanese Patent Application No. 2015-230278 filed with the Japan Patent Office on November 26, 2015, the entire contents of which are incorporated herein by reference.

Claims

A brake device that holds and brakes a brake disk that rotates with a wheel,
A brake body supported by the vehicle body or the carriage,
A support portion between the one end portion and the other end portion is rotatably supported with respect to the brake main body and is provided to face both surfaces of the brake disc, and the one end portions are connected by a connecting member, A pair of link arms each supporting the brake lining in which each of the other end portions is in sliding contact with the brake disc to apply a frictional force;
An actuator provided on the connecting member for moving the output member forward and backward;
A lever that is rotatably connected to the output member and rotates by the advancement and retraction of the output member;
An eccentric cam provided at one end of one of the pair of link arms and rotating about a rotation axis by the rotation of the lever;
A brake device comprising: a pressing member that advances and retreats with the rotation of the eccentric cam and presses the other end, and expands or contracts the distance between the one end and the other end.
The brake device according to claim 1,
The eccentric cam is
A rotating part rotatably connected to the one end of the link arm, the lever being connected and rotating about the rotation axis;
A brake device having a center axis at a position offset from the rotation axis, and an eccentric portion that rotates in a circular arc shape around the rotation axis by the rotation of the lever to advance and retract the pressing member.
The brake device according to claim 2,
The rotating part is provided with a pair of small diameters compared to the eccentric part, and the levers are provided so as not to rotate relative to each other.
The eccentric portion is a brake device provided between the pair of rotating portions.