JP2010216575A - Caliper brake device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a caliper brake device in which the partial wear of a brake block due to the thermal deformation of a disk is suppressed. <P>SOLUTION: This caliper brake device in which a brake block 42 is pressed against the disk 6 of a wheel 5 includes a caliper arm 12 which is moved forward and backward relative to the disk 6 by an actuator and a bearing 23 which rotatably supports the rear surface 48 of the brake block 42 on the caliper arm 12. The brake block 42 which is pressed against the disk 6 during the braking is deflected and deformed through the bearing 23. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a structure for supporting a control member in a caliper brake device that brakes rotation of a wheel.

  In general, a caliper brake device for a railway vehicle is configured such that a pair of restrictors sandwich a wheel disk to apply a brake.

  Conventionally, the caliper brake devices for railway vehicles disclosed in Patent Documents 1 and 3 are provided with a restrictor that is driven by a hydraulic piston with respect to the caliper body, and a pair of restrictors that are fixed to the caliper body. At the time of braking, one of the brakes is pressed against the disk by the hydraulic piston, and the caliper main body is moved by a reaction force received by the brake, and the other brake fixed to the caliper main body is pressed against the disk.

  The caliper brake device disclosed in Patent Document 3 supports the hydraulic piston so as to be rotatable with respect to the caliper main body. When the caliper arm of the caliper main body is bent during braking, the hydraulic piston rotates to displace the brake member on the disc. As a configuration that is maintained in parallel to the rotating surface, the control member is prevented from being unevenly worn in the rotational radius direction of the disk.

  The control device disclosed in Patent Document 2 is configured such that a disc-shaped lining is supported on a substrate via a flat spring and a lining that slides on the disc during braking tilts following the disc, and the control device is subject to uneven wear. It comes to prevent.

JP-A-8-226467 JP 2006-207625 A JP 2008-267479 A

  However, in such a conventional caliper brake device for a railway vehicle, there is a problem that the control device fixed to the caliper body cannot follow the thermal deformation of the disk and the control device is unevenly worn. there were.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a caliper brake device that can suppress uneven wear of the control wheel in response to thermal deformation of a disk.

  The present invention relates to a caliper brake device in which a brake is pressed against a disk of a wheel, and a caliper arm that moves forward and backward with respect to the disk by an actuator, and a bearing that rotatably supports the back surface of the brake on the caliper arm. And a structure in which the brake member that is pressed against the disk during braking is bent and deformed through a bearing.

  According to the present invention, since the brake is bent and deformed through the bearing following the thermal deformation of the disk, the brake can suppress a local increase in the surface pressure against the disk and suppress uneven wear of the lining. In addition, the effective contact area of the lining with the disk can be increased to increase the braking force.

The side view of the caliper brake device which shows embodiment of this invention. FIG. Similarly front view. The schematic side view and sectional drawing which similarly show a caliper arm and a restrictor. FIG. 5 is a cross-sectional view of the caliper arm and the restrictor showing the state during braking. The schematic side view and sectional drawing which show the caliper arm and restrictor which show other embodiment. The schematic side view and sectional drawing which show the caliper arm and restrictor which show other embodiment. The schematic side view and sectional drawing which show the caliper arm and restrictor which show other embodiment. The schematic side view and sectional drawing which show the caliper arm and restrictor which show other embodiment.

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

  1 to 3 are three views of the caliper brake device 1. Here, three axes of X, Y, and Z that are orthogonal to each other are set, the X-axis extends in the horizontal horizontal direction, the Y-axis extends in the horizontal front-rear direction, and the Z-axis extends in the vertical direction. To do.

  The caliper brake device 1 for a railway vehicle sandwiches the disk 6 of the wheel 5 on which the pair of restrictors 41 and 42 rotates, and brakes the rotation of the wheel 5.

  As shown in FIGS. 1 to 3, the caliper body 10 supports the left and right control members 41 and 42. The support frame 30 is fixed to a carriage (not shown) of the railway vehicle. The caliper body 10 is slidably connected to the support frame 30 via two support pins 31 and 32, and is supported so as to be relatively movable in the X-axis direction (the rotation axis direction of the disk 6).

  As shown in FIG. 2, the caliper body 10 includes left and right caliper arms 11 and 12 that extend so as to sandwich the wheel 5.

  A support rail 51 is attached to the right caliper arm 11. The right restrictor 41 is supported by the caliper arm 11 via the support rail 51.

  As shown in FIGS. 1 and 3, the right caliper arm 11 is provided with three hydraulic pistons (actuators) 8.

  As shown in FIG. 1, the caliper body 10 is provided with an inlet portion 20, and a hydraulic pipe (not shown) is connected to the inlet portion 20.

  At the time of braking, each hydraulic piston 8 moves in the X-axis direction by the pressurized hydraulic fluid guided through the inlet portion 20, presses the support rail 51, and the support rail 51 moves in the X-axis direction. As a result, the right restrictor 41 supported by the support rail 51 is pressed against the disk 6, and the caliper body 10 is moved in the X-axis direction by the reaction force received by the restrictor 41, so that the restrictor 42 is pressed against the disk 6. It is done.

  As shown in FIG. 1, adjusters 61 and 62 are fastened to the upper and lower ends of the right caliper arm 11, respectively. The adjusters 61 and 62 have anchor pins 16 and 17 that engage with the support rail 51, adjust the stroke of the anchor pins 16 and 17 that are pulled in by the urging force of a spring (not shown), and control the brake at the time of non-braking. The gap between the discs 41 and 42 with respect to the disk 6 is kept constant.

  As shown in FIG. 3, anchor blocks 75 and 77 having anchor pins 18 and 19 on the upper and lower ends of the left caliper arm 12 are fastened through anchor bolts 76 and 78, respectively. The upper and lower ends of the restrictor 42 are supported by the caliper arm 12 by engaging the anchor pins 18 and 19 respectively.

  FIG. 4B is a schematic side view showing the left caliper arm 12 and the restrictor 42, and FIG. 4A is a cross-sectional view taken along line AA in FIG.

  The restrictor 42 has a metal back plate 43 and a lining 44 fixed to the back plate 43.

  Support recesses 45 and 46 are formed at both ends of the back plate 43, and the anchor pins 18 and 19 engage with the support recesses 45 and 46, respectively. During braking, when the brake member 42 slides on the disk 6 to brake the rotation of the wheel 5, the braking reaction force acting on the brake member 42 is supported by the caliper arm 12 via the anchor pins 18 and 19.

  The lining 44 is provided as a friction material in sliding contact with the disk 6. The lining 44 is divided into, for example, three blocks and is fixed to the mounting surface 47 of the back plate 43.

  As shown in FIG. 4B, the linings 44 are arranged along the arc-shaped disc center line S so as to be in sliding contact with the ring-shaped disc 6 at the same site. The disk center line S is a disk center line that extends in the rotational circumferential direction of the disk 6 through the center of the ring-shaped disk 6.

  The back plate 43 is formed of a metal plate having appropriate rigidity, and is bent and deformed by the surface pressure received from the disk 6 by the control device 42 as will be described later.

  The caliper arm 12 has an arm surface 22 that faces the back surface 48 of the control wheel 42 with a gap 49.

  The caliper arm 12 is provided with a plurality of bearings 23 that rotatably support the back plate 43 of the control wheel 42.

  As shown in FIG. 4A, the bearing 23 includes a semi-cylindrical roller 24 and a roller support member 26 that slidably supports a roller back surface 25 of the roller 24. The roller support member 26 is embedded in the arm surface 22 of the caliper arm 12.

  The roller 24 includes a roller body 29 having a roller back surface 25 that is in sliding contact with the roller support member 26, and a heat insulating plate 28 attached to the roller body 29. The heat insulating plate 28 comes into contact with the back surface 48 of the brake device 42, and heat from the brake device 42 is prevented from being transmitted to the bearing 23.

  The roller support member 26 has a receiving surface 27 whose cross section is recessed in an arc shape. The roller 24 is rotated by being brought into sliding contact with the receiving surface 27 of the roller back surface 25.

  The roller back surface 25 is formed so as to be curved in an arc shape centering on the rotation center O located on the surface of the heat insulating plate 28. As a result, the rotation center O of the roller 24 is disposed on the back surface 48 of the restrictor 42.

  A pair of bearings 23 is provided behind each of the three linings 44 divided. The pair of bearings 23 are disposed so as to sandwich the disk center line S and the rotation center O of each roller 24 is substantially orthogonal to the radial line R extending in the rotation radial direction of the disk 6. As a result, following the thermal deformation or the like of the disk 6, the brake element 42 can be bent and deformed along the disk center line S via the bearings 23.

  At the time of braking, the left and right control members 41 and 42 are pressed against the left and right discs 6 respectively, and the rotation of the wheels 5 is braked by the frictional force applied to the discs 6. When the disk 6 becomes high temperature due to the frictional heat generated at this time, the cross section of the disk 6 may be thermally deformed into a convex shape or a concave shape, and the surface pressure against the control elements 41 and 42 may locally increase.

  FIG. 5A shows a central portion where the center line D of the cross section of the disk 6 is thermally deformed so as to bulge out convexly with respect to the restrictor 42, and the surface pressure against the restrictor 42 faces the disk center line S. FIG. 9 shows a state in which the brake element 42 is bent and deformed during braking that is locally increased. In this case, the controller 42 rotates the bearings 23 so that the central portion facing the disc center line S is bent and deformed in a concave shape with respect to the disc 6, and the surface 44 b of the lining 44 is bent along the disc 6. Therefore, it is possible to prevent the surface pressure against the disk 6 from locally increasing at the central portion facing the disk center line S, to suppress uneven wear of the lining 44, and to increase the effective contact area of the lining 44 to the disk 6. The braking force can be increased.

  FIG. 5B shows an inner peripheral portion and an outer peripheral portion where the cross-sectional center line D of the disk 6 is thermally deformed so as to be recessed in a concave shape with respect to the restrictor 42 and the surface pressure against the restrictor 42 is separated from the disc center line S. FIG. 9 shows a state in which the brake element 42 is bent and deformed during braking that is locally increased. In this case, the controller 42 rotates the bearings 23 so that the central portion along the disc center line S is bent and deformed in a convex shape with respect to the disc 6, and the surface 44 b of the lining 44 is bent along the disc 6. Therefore, it is possible to prevent the surface pressure on the disk 6 from locally increasing at the inner and outer peripheral parts away from the disk center line S, thereby suppressing uneven wear of the lining 44 and effective for the lining 44 with respect to the disk 6. The contact area is enlarged and the braking force can be increased.

  As described above, in the present embodiment, the caliper brake device 1 in which the brake member 42 is pressed against the disk 6 of the wheel 5, the caliper arm 12 that moves forward and backward with respect to the disk 6 by the actuator (hydraulic piston 8), A bearing 23 that rotatably supports the back surface 48 of the control device 42 with respect to the caliper arm 12 is provided, and the control device 42 that is pressed against the disk 6 during braking is bent and deformed through the bearing 23.

  Based on the above-described configuration, the control element 42 is bent and deformed through the bearing 23 following the thermal deformation of the disk 6, so that the control element 42 can suppress a local increase in surface pressure against the disk 6 and the lining. 44 is suppressed, and the effective contact area of the lining 44 with respect to the disk 6 is increased to increase the braking force.

  In the present embodiment, the bearing 23 includes a semi-cylindrical roller 24 and a roller support member 26 that rotatably supports the roller 24, and the roller 24 has a rotation center O that rotates the disk 6. It was set as the structure arrange | positioned so as to be substantially orthogonal with respect to the radial line R extended in a center direction.

  Based on the above configuration, the brake element 42 is bent and deformed so as to follow the thermal deformation along the disk center line S of the disk 6 via the bearing 23. For this reason, the control member 42 can suppress a local increase in the surface pressure against the disk 6, suppress uneven wear of the lining 44, and increase the braking force.

  In the present embodiment, the roller 24 is arranged so that the center of rotation O is on the back surface 48 of the restrictor 42.

  Based on the above configuration, the roller 24 can be reduced in size, and the space for the bearing 23 can be reduced.

  In the present embodiment, the roller 24 has a roller body 29 that is in sliding contact with the roller support member 26, and a heat insulating plate 28 that is attached to the roller body 29 and abuts against the back surface 48 of the brake element 42.

  Based on the above configuration, the heat insulating plate 28 is interposed between the control wheel 42 and the bearing 23, so that the bearing 23 is prevented from being overheated and the smooth operability of the bearing 23 is maintained.

  Next, another embodiment shown in FIG. 6 will be described. This basically has the same configuration as that of the embodiment of FIGS. 1 to 5, and only different portions will be described. In addition, the same code | symbol is attached | subjected to the same structure part as the said embodiment.

  FIG. 6B is a schematic side view showing the left caliper arm 12 and the restrictor 42, and FIG. 6A is a cross-sectional view taken along the line AA in FIG.

  In the present embodiment, three bearings 23 are provided at the center of each lining 44 divided into three blocks. The three bearings 23 are arranged at a predetermined interval in the rotational radius direction of the disk 6, and the bearing 23 disposed at the center thereof is disposed along the disk center line S.

  When the center line of the cross section of the disk 6 is thermally deformed to be curved in an S shape during braking, and the surface pressure against the brake element 42 is locally increased along the disk center line S, the brake element 42 is By rotating the three bearings 23 arranged in the direction of the radius of rotation, the cross-section of the bearing 23 is bent and deformed so that the surface pressure against the disk 6 is not locally increased, and uneven wear of the lining 44 is suppressed. In addition, the effective contact area of the lining 44 with respect to the disk 6 is increased, and the braking force is increased.

  Next, another embodiment shown in FIG. 7 will be described. This basically has the same configuration as that of the embodiment of FIGS. 1 to 5, and only different portions will be described. In addition, the same code | symbol is attached | subjected to the same structure part as the said embodiment.

  FIG. 7B is a schematic side view showing the left caliper arm 12 and the restrictor 42, and FIG. 7A is a cross-sectional view taken along the line AA in FIG.

  In the present embodiment, a single bearing 23 is provided at the center of each lining 44 divided into three blocks. Each bearing 23 is arranged along the disk center line S.

  When the arm surface 22 is inclined with respect to the back surface 48 of the control device 42 as the caliper arms 11 and 12 are bent so as to expand at the time of braking, the control device 42 has the arm surface 22 of the control device 42. The bearings 23 are bent and deformed so as to be parallel to the back surface 48, and uneven wear of the lining 44 can be suppressed, and the effective contact area of the lining 44 with respect to the disk 6 can be increased to increase the braking force.

  Next, another embodiment shown in FIG. 8 will be described. This basically has the same configuration as that of the embodiment of FIGS. 1 to 5, and only different portions will be described. In addition, the same code | symbol is attached | subjected to the same structure part as the said embodiment.

  FIG. 8B is a schematic side view showing the left caliper arm 12 and the restrictor 42, and FIG. 8A is a cross-sectional view taken along line AA of FIG. 8B.

  In the present embodiment, the rotation center O of the roller 24 is arranged on the wear margin 44 a of the lining 44.

  The roller back surface 25 of the bearing 23 is formed to be curved in an arc shape around a rotation center O located on a point where the wear margin 44a of the lining 44 is equally divided in the X-axis direction.

  Based on the above configuration, the roller 24 rotates around the rotation center O located on the wear margin 44 a of the lining 44, and deforms so that the surface 44 b of the lining 44 bends along the disk 6. For this reason, the brake member 42 can effectively suppress the local increase in the surface pressure against the disk 6, suppress uneven wear of the lining 44, and increase the braking force.

  Next, another embodiment shown in FIG. 9 will be described. This basically has the same configuration as that of the embodiment of FIGS. 1 to 5, and only different portions will be described. In addition, the same code | symbol is attached | subjected to the same structure part as the said embodiment.

  FIG. 9B is a schematic side view showing the left caliper arm 12 and the restrictor 42, and FIG. 9A is a cross-sectional view taken along line AA of FIG. 9B.

  In the present embodiment, the bearing 63 includes a hemispherical ball 64 and a ball support member 66 that slidably supports a ball back surface 65 of the ball 64. The ball support member 66 is embedded in the arm surface 22 of the caliper arm 12.

  The ball 64 includes a ball main body 69 having a ball back surface 65 that is in sliding contact with the ball support member 66, and a heat insulating plate 68 attached to the ball main body 69. The heat insulating plate 68 abuts against the back surface 48 of the brake device 42, and heat from the brake device 42 is prevented from being transmitted to the bearing 63.

  The ball support member 66 has a receiving surface 67 whose cross section is recessed in an arc shape. The ball 64 is rotated by being brought into sliding contact with the receiving surface 67 of the ball back surface 65.

  The ball back surface 65 is formed so as to be curved in an arc shape centering on the rotation center O located on the surface of the heat insulating plate 68. As a result, the rotation center O of the ball 64 is disposed on the back surface 48 of the restrictor 42.

  Three pairs of bearings 63 are provided behind each of the three linings 44 divided. The pair of bearings 63 are arranged so that the center of rotation O of each ball 64 is arranged on a radial line R extending in the radial direction of the disk 6 with the disk center line S interposed therebetween.

  Based on the above configuration, the hemispherical ball 64 rotates about a rotation center line located on a plane including the Y axis and the Z axis, and the surface 44 b of the lining 44 is deformed so as to be bent along the disk 6. For this reason, the brake member 42 can effectively suppress the local increase in the surface pressure against the disk 6, suppress uneven wear of the lining 44, and increase the braking force.

  The present invention is not limited to the above-described embodiment, and it is obvious that various modifications can be made within the scope of the technical idea.

1 Caliper brake device 5 Wheel 6 Disc 8 Hydraulic piston (actuator)
DESCRIPTION OF SYMBOLS 10 Caliper main body 16 Anchor pin 18 Anchor pin 23 Bearing 24 Roller 25 Roller back surface 26 Roller support member 27 Receiving surface 28 Insulating plate 29 Roller body 41 Control ring 42 Control ring 43 Back plate 44 Lining 47 Mounting surface 48 Back surface 63 Bearing 64 Ball 65 Ball back surface 66 Ball support member 67 Receiving surface 68 Heat insulation plate 69 Ball body

Claims (5)

A caliper brake device in which the brake is pressed against the disc of the wheel,
A caliper arm that moves forward and backward with respect to the disk by an actuator;
A bearing that supports the caliper arm so that the back surface of the control device can be rotated;
A caliper brake device characterized in that the brake member pressed against the disk during braking is bent and deformed through the bearing. The bearing is
A semi-cylindrical roller,
A roller support member that rotatably supports the roller;
2. The caliper brake device according to claim 1, wherein the roller is disposed so that a rotation center thereof is substantially orthogonal to a radial line extending in a rotation center direction of the disk.   The caliper brake device according to claim 2, wherein the roller is disposed such that a center of rotation of the roller is on the back surface of the restrictor. The bearing is
A hemispherical ball,
The caliper brake device according to claim 1, further comprising a ball support member that slidably supports the ball.   The caliper brake device according to any one of claims 1 to 4, wherein the bearing includes a heat insulating plate that abuts against the back surface of the control device.

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