JP2019056435A - Brake device - Google Patents

Abstract

To provide a brake device capable of adjusting a gap between a brake lining and a brake disk even when a brake body is tilted with respect to a support frame.SOLUTION: A brake device 100 includes: a brake body 10; first and second support pins 21, 22 supported by a support frame 20 movably in an axial direction and supporting the brake body 10; a pressing part 35 provided on a first caliper arm 12 of the brake boy 10, pressing a first brake lining 3 onto a brake disk 2, and moving the brake body 10 so as to press a second brake lining 4 onto the brake disk 2; and a second gap adjustment mechanism 40 for returning the brake body 10 moved to the axial direction of the first and the second support pins 21, 22 at braking to an opposite direction by a set distance at release of braking. The second gap adjustment mechanism 40 is provided on the support frame 20, and movement of the first and the second support pins 21, 22 is regulated in the axial direction, and is allowed in a radial direction.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a brake device.

  Patent Document 1 discloses a floating disc brake having a support frame attached to a carriage of a railway vehicle, and a brake body supported slidably in the axial direction of the wheel via a support pin with respect to the support frame. An apparatus is disclosed. In this disc brake device, a pair of caliper arms of the brake body is provided so as to straddle the wheels (brake discs), and a pressing mechanism for advancing and retracting the brake lining is provided only on one caliper arm.

Japanese Patent Laid-Open No. 08-226467

  In the brake device of Patent Document 1, the one caliper arm provided with the pressing mechanism is provided with a gap adjusting device that automatically adjusts the gap between the brake lining and the brake disc when the brake is released. The other caliper arm that is not provided is not provided with a gap adjusting mechanism. Therefore, when the brake device is not braked, the other brake lining and the brake disc may come into contact with each other. Therefore, the inventors of the present application have proposed that the gap between the other brake lining and the brake disk is adjusted by moving the brake body relative to the support frame.

  However, in the floating type brake device, the brake body tilts with respect to the support frame so as to follow the tilting of the traveling wheel. Therefore, when adjusting the clearance between the other brake lining and the brake disc by moving the brake body relative to the support frame, it is necessary to consider the inclination of the brake body with respect to the support frame.

  The present invention has been made in view of the above problems, and provides a brake device capable of adjusting a gap between a brake lining and a brake disc even when the brake body is inclined with respect to a support frame. With the goal.

  1st invention is a brake device, Comprising: The brake which has the 1st and 2nd caliper arm which respectively supports the 1st and 2nd brake lining which can be slidably contacted to a brake disc from both sides of a brake disc, and can provide a frictional force A main body, a support pin that is supported by the support frame attached to the vehicle body or the carriage in the axial direction and supports the brake main body, a first caliper arm that is provided on the first caliper arm and presses the first brake lining against the brake disc and the brake main body A pressing mechanism that moves the support pin in the axial direction of the support pin and presses the second brake lining against the brake disc, and a gap adjustment that returns the brake body moved in the axial direction of the support pin during braking to the opposite direction when the brake is released. A clearance adjusting mechanism provided on the support frame and moving the support pin in the axial direction. There characterized in that it is allowed to move in the radial direction while being restricted.

  In the first invention, the gap adjusting mechanism is restricted from moving in the axial direction of the support pin and is capable of moving in the radial direction. Therefore, the movement of the gap adjusting mechanism in the axial direction is restricted even when the brake body is inclined with respect to the support frame. Therefore, even when the brake body is inclined with respect to the support frame, the brake body that has moved in the axial direction of the support pin during braking is returned by a set distance in the opposite direction when braking is released.

  In the second invention, the gap adjusting mechanism has a ring body that is provided on the outer periphery of the support pin and contacts the support frame, and the support frame is formed on the inner peripheral surface of the insertion hole through which the support pin is inserted. Has an engaging groove for restricting the movement of the gap adjusting mechanism in the axial direction, and the inner diameter of the bottom of the engaging groove is formed larger than the outer diameter of the ring body. To do.

  In the second invention, since the inner diameter of the bottom of the engagement groove is formed larger than the outer diameter of the ring body, the ring body remains in the engagement groove even if the brake body is inclined with respect to the support frame. It can move and maintain the engaged state.

  According to a third aspect of the present invention, the distance between the inner diameter of the bottom of the engagement groove and the outer diameter of the ring body is formed to be larger than the displacement amount of the ring body when the maximum inclination angle with respect to the support frame of the brake body It is characterized by.

  In the third aspect of the invention, even when the brake body is tilted by the maximum tilt angle with respect to the support frame, the ring body can move in the engagement groove and maintain the engaged state.

  According to a fourth aspect of the invention, the support frame includes a support frame main body attached to the vehicle body or the carriage, and a fixing member attached to the support frame main body and having an engagement groove formed on the inner periphery.

  The fifth invention is characterized in that the fixing member is attached to an end portion in the axial direction of the support pin in the support frame main body.

  In the fourth and fifth inventions, by providing the fixing member, it is easy to assemble the gap adjusting mechanism to the brake device, it can be easily retrofitted to the existing brake device, and assembling compatibility can be ensured. Furthermore, maintenance and replacement of each component of the gap adjusting mechanism can be easily performed.

  The sixth invention is characterized in that the support frame main body has an annular fixing groove on the outer periphery, and the fixing member has a locking portion locked to the fixing groove.

  In 6th invention, a fixing member has a latching | locking part latched by the fixing groove normally used in order to attach a boot. Thereby, a clearance adjustment apparatus can be attached using the fixed groove | channel of the existing brake device.

  According to a seventh aspect of the present invention, the clearance adjustment mechanism has a clamp portion that can clamp the support pin, and a clamp portion that exerts a reaction force against the movement of the brake body during braking and resists the movement of the brake body. And a biasing member for biasing.

  In the seventh invention, the reaction force of the urging member accompanying the movement of the brake body during braking is applied to the support pin via the clamp portion. As a result, when the braking of the brake device is released, the brake body moves in a direction in which the second brake lining and the brake disc are separated by a reaction force. Thus, contact between the second brake lining and the brake disc when the brake device is released is prevented.

  According to an eighth aspect of the invention, the support pin is clamped by the clamp portion when the movement amount of the brake body in the pressing direction in which the second brake lining approaches the brake disc is equal to or less than a predetermined reference movement amount, When moving beyond the reference movement amount in the pressing direction, the clamp by the clamp portion is released.

  In the eighth invention, the amount of movement of the brake body required for braking increases due to wear of the second brake lining, and when the brake body moves in the pressing direction beyond the reference movement amount, the brake body and the support pin are Move relative. For this reason, even if the brake body moves beyond the reference movement amount, the clamp portion does not move in the pressing direction, and the reaction force of the urging member does not increase. Therefore, even if the amount of movement of the brake main body exceeds the reference movement amount during braking, an increase in reaction force against the movement of the brake main body is suppressed. Therefore, the stability of the braking force of the brake device is ensured.

  According to a ninth aspect of the present invention, the clamp portion accommodates the wedge member having a wedge surface that forms a wedge space between the outer peripheral surface of the support pin and a wedge space whose interval gradually decreases along the axial direction of the support pin. And a pressing member that presses the wedge member or the rolling element such that the rolling element is pressed against the wedge surface from the axial direction.

  In a tenth aspect of the present invention, the clamp portion further includes a cylindrical inner member that is provided between the wedge member and the support pin and has a through hole that opens to the inner and outer peripheral surfaces. The inner member is in contact with the outer peripheral surface, and the inner member has a receiving portion that supports the pressing member with the wedge member, and a support portion that supports the urging member with the ring body.

  In the ninth and tenth inventions, the pressing member biases the wedge member so that the rolling element is pressed against the wedge surface. As a result, the rolling element is pushed toward a narrow portion in the wedge space. Therefore, relative movement between the clamp part and the support pin is restricted by the wedge effect, and the clamp part clamps the support pin.

  According to the present invention, the gap between the brake lining and the brake disc can be adjusted even when the brake body is inclined with respect to the support frame.

FIG. 1 is a plan view of a brake device according to an embodiment of the present invention. FIG. 2 is a front view of the brake device. FIG. 3 is a cross-sectional view taken along the line AA in FIG. 1 and shows the periphery of the first support pin. FIG. 4 is a diagram illustrating a state in which the brake body is inclined in one direction with respect to the support frame. FIG. 5 is a diagram illustrating a state in which the brake body is inclined in the other direction with respect to the support frame. FIG. 6A is a conceptual diagram illustrating the movement of the gap adjustment mechanism when the brake body is tilted with respect to the support frame. FIG. 6B is a conceptual diagram illustrating the movement of a modified example of the gap adjusting mechanism when the brake body is inclined with respect to the support frame. FIG. 7 is an enlarged cross-sectional view showing the vicinity of the gap adjusting mechanism and shows a non-braking state. FIG. 8 is an enlarged cross-sectional view showing the vicinity of the gap adjusting mechanism, and shows a case where the brake main body moves below the reference movement amount and enters a braking state. FIG. 9 is an enlarged cross-sectional view showing the vicinity of the gap adjustment mechanism, and shows a state where the brake body has moved by a reference movement amount. FIG. 10 is an enlarged cross-sectional view showing the vicinity of the gap adjustment mechanism, and shows a case where the brake body moves beyond the reference movement amount and enters a braking state. FIG. 11 is a cross-sectional view of a brake device according to a modified example of the present invention and is a view showing the periphery of a first support pin. FIG. 12 is a cross-sectional view of a brake device according to another modified example of the present invention and is a view showing the periphery of the first support pin.

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

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

  The brake device 100 is a floating pneumatic brake for railway vehicles that uses compressed air as a working fluid. Instead of compressed air, other working fluid such as hydraulic oil may be used.

  The brake device 100 applies a frictional force to the brake disc 2 that rotates together with the wheel 1. Specifically, the brake device 100 applies friction force to the brake disc 2 by the first and second brake linings 3 and 4 that can apply friction force by sliding contact with the brake disc from both sides of the brake disc 2, The rotation of the wheel 1 is braked.

  The brake disc 2 is formed on both the front and back surfaces of the wheel 1 and rotates integrally with the wheel 1. Instead of forming the brake disc 2 integrally with the wheel 1, a separate brake disc 2 that rotates together with the wheel 1 may be provided.

  The brake device 100 is attached to a truck body (not shown) having a brake body 10 having first and second caliper arms 12 and 14 that support the first and second brake linings 3 and 4 via a guide plate 5, respectively. First and second support pins 21 and 22 (refer to FIG. 2) supported by the support frame 20 so as to be movable in the axial direction and supporting the brake body 10, and a guide plate 5 supported by the first brake lining 3. A pair of anchor pins 33 that are supported on the brake main body 10 so as to be able to advance and retreat, and a pressing portion 35 as a pressing mechanism that presses the first and second brake linings 3 and 4 against the brake disc 2 by the pressure of compressed air.

  The brake body 10 is supported by the carriage via the support frame 20 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. 1, the brake body 10 includes a first caliper arm 12 and a second caliper arm 14 that extend across the brake disc 2, and a yoke that connects the first caliper arm 12 and the second caliper arm 14. Part 13 and first and second bracket parts 15 and 16 for supporting brake body 10 on the carriage.

  The basic structure of the peripheral structure of the first support pin 21 and the peripheral structure of the second support pin 22 is the same. Therefore, hereinafter, the peripheral structure of the first support pin 21 will be specifically described, and the description of the second support pin 22 will be omitted.

  As shown in FIG. 3, the first support pin 21 is inserted into the insertion hole 20 a of the support frame 20. Both end portions of the first support pin 21 are connected to the first and second bracket portions 15 and 16 of the brake body 10, respectively. The first support pin 21 is provided in parallel with the rotation axis of the wheel 1 and is supported by the support frame 20 so as to be movable in the axial direction. Accordingly, the brake body 10 is supported by the support frame 20 so that the first support pins 21 can move in the axial direction.

  As shown in FIG. 1, the exposed portion of the first support pin 21 is covered with a rubber boot 25 and protected from dust and the like. In this manner, the brake body 10 is floating supported by the first support pins 21 so as to be slidable with respect to the support frame 20. Except for FIG. 1, illustration of the boot 25 is omitted.

  The first and second brake linings 3 and 4 have back plate portions 3a and 4a fixed to the guide plate 5, and friction members 3b and 4b that come into contact with the brake disc 2 during braking. The friction members 3b and 4b are composed of a plurality of segments, and are fixed to the surfaces of the back plate portions 3a and 4a. The first and second brake linings 3 and 4 brake the rotation of the wheel 1 by the frictional force generated by the contact between the friction members 3 b and 4 b and the brake disk 2.

  The first and second brake linings 3 and 4 are opposed to the brake disc 2 with a predetermined interval (state shown in FIG. 1) when not braking. During braking, the first and second brake linings 3 and 4 are each moved toward the brake disc 2 under the pressing force of the pressing portion 35 and are pressed against the brake disc 2 in parallel.

  The guide plate 5 has a dovetail groove 5 a formed along the longitudinal direction and engaged with the back plate portion 3 a of the first brake lining 3. Both ends of the guide plate 5 in the longitudinal direction are supported by the brake body 10 by a pair of anchor pins 33. One anchor pin 33 rotatably supports one end (upper end in FIG. 2) of the guide plate 5 on the brake body 10, and the other anchor pin 33 supports the other end (lower end in FIG. 2) of the guide plate 5 on the brake body. 10 is locked.

  The first caliper arm 12 of the brake main body 10 includes a pair of adjusters 30 disposed at both ends in the longitudinal direction (vertical direction in FIG. 2) and a pressing portion 35 disposed between the pair of adjusters 30. Provided.

  The adjuster 30 adjusts the relative position of the first brake lining 3 with respect to the brake disc 2 to a constant level when not braking. The adjusters 30 are fastened to the upper and lower ends of the brake body 10 by anchor bolts 32, respectively.

  As shown in FIG. 1, the adjuster 30 is provided with a lining receiver 31 fixed to the brake body 10 by an anchor bolt 32, and is provided so as to be able to advance and retreat with respect to the lining receiver 31. The anchor pin 33, the return spring (not shown) for urging the first brake lining 3 away from the brake disc 2, and the gap between the first brake lining 3 and the brake disc 2 are adjusted to be constant during non-braking. A first gap adjusting mechanism (not shown).

  When the first brake lining 3 is close to the brake disc 2, the anchor pin 33 is pulled out from the lining receiver 31 by the guide plate 5 that is displaced together with the first brake lining 3 and is displaced in the axial direction. The anchor pin 33 resists the brake disc 2 from moving the first brake lining 3 in the circumferential direction by frictional force during braking when the first brake lining 3 is in sliding contact with the brake disc 2. 3 is held. A return spring and a first gap adjusting mechanism are accommodated on the inner periphery of the anchor pin 33.

  The return spring is a coil spring that is compressed and interposed on the inner periphery of the anchor pin 33. When the brake device 100 changes from the braking state to the non-braking state, the anchor pin 33 pushes back the first brake lining 3 via the guide plate 5 by the biasing force of the return spring, and the first brake lining 3 is removed from the brake disc 2 by a predetermined amount. Are separated by a distance of. Thereby, the distance of the 1st brake lining 3 and the brake disc 2 at the time of non-braking can be adjusted, and the heat dissipation of the brake disc 2 can be made favorable. The braking state is a state in which the first and second brake linings 3 and 4 are pressed against the brake disc 2 by a pressing portion 35 described later. The non-braking state is a state in which the pressing force pressed against the brake disk 2 by the pressing portion 35 does not act on the first and second brake linings 3 and 4.

  The first clearance adjustment mechanism adjusts the return amount of the first brake lining 3 to be constant by the urging force of the return spring during non-braking. That is, the first gap adjusting mechanism always keeps the distance between the first brake lining 3 and the brake disc 2 during non-braking.

  While the amount of wear of the first brake lining 3 is small and the stroke amount of the anchor pin 33 at the time of braking is small, the anchor pin 33 returns to the original position before braking at the time of non-braking.

  On the other hand, when wear of the first brake lining 3 proceeds and the amount of movement of the anchor pin 33 during braking increases, the first clearance lining 3 during non-braking when the first clearance adjustment mechanism is not braked. Is moved forward by the worn thickness. Thereby, the space | interval of the 1st brake lining 3 and the brake disc 2 at the time of non-braking can be always kept constant.

  The pressing portion 35 presses the first brake lining 3 against the brake disc 2 by the pressure of the compressed air and moves the brake body 10 in the axial direction of the first support pin 21 by the reaction force to brake the second brake lining 4. Press against the disc 2.

  The pressing part 35 can have any configuration as long as it presses the first and second brake linings 3, 4 against the brake disk 2. For this reason, although detailed description of the press part 35 is abbreviate | omitted, for example, the press part 35 deform | transforms a diaphragm by adjusting the air pressure in the pressure chamber provided inside, and makes a piston retract from a cylinder by the deformation | transformation of a diaphragm. . Thus, the pressing portion 35 presses the first brake lining 3 toward the brake disk 2 via the guide plate 5 in the right direction in FIG. 1, and the reaction force causes the brake body 10 to move in the left direction in FIG. 1. Then, the second brake lining 4 is pulled toward the brake disc 2. In this way, the brake disc 2 is sandwiched between the first and second brake linings 3 and 4, and a frictional force as a braking force is exhibited.

  In the following, as shown in FIG. 1, the movement direction of the brake body 10 during braking of the brake device 100, in other words, the movement of the brake body 10 such that the second brake lining 4 approaches and presses the brake disk 2. The direction is referred to as a “pressing direction”. On the contrary, the moving direction of the brake body 10 in which the second brake lining 4 and the brake disc 2 are separated from each other is referred to as a “release direction”.

  As shown in FIG. 3, the brake device 100 includes a spherical bearing 26 provided in the insertion hole 20 a of the support frame 20 and slidably supporting the first support pin 21, and the insertion hole 20 a of the support frame 20. A pair of rubber bushes 27 and 28 provided on both sides in the axial direction of the spherical bearing 26 to slidably support the first support pin 21 and the brake body 10 moved in the axial direction of the first support pin 21 during braking. And a second gap adjusting mechanism 40 as a gap adjusting mechanism that returns a set distance in the opposite direction when the brake is released.

  The spherical bearing 26 includes an outer ring 26a and an inner ring 26b having bearing surfaces that are slidably fitted to each other. The outer ring 26a and the inner ring 26b are engaged with each other so as to be relatively rotatable.

  The outer ring 26 a is provided by being fitted to the inner peripheral surface of the insertion hole 20 a of the support frame 20. The first support pin 21 is slidably inserted into the inner ring 26b. Accordingly, the spherical bearing 26 supports the brake body 10 so as to be swingable with respect to the support frame 20 and slides in the axial direction of the first support pin 21 (the rotation axis direction of the wheel 1) with respect to the support frame 20. Support floating as possible.

  The support frame 20 has an engagement groove 29b that is formed on the inner peripheral surface and engages with a ring body 49 (to be described later) of the second gap adjustment mechanism 40 to restrict the movement of the second gap adjustment mechanism 40 in the axial direction. The support frame 20 includes a support frame main body 24 attached to a vehicle body or a carriage, and a fixing ring 29 as a fixing member attached to the support frame main body 24 and having an engagement groove 29b formed on the inner periphery thereof.

  The support frame main body 24 has an annular fixing groove 20b on the outer periphery of the end portion. The fixing groove 20b is a groove used for fixing the boot 25 (see FIG. 1) when the second gap adjusting mechanism 40 is not provided.

  The fixing ring 29 is attached to the axial ends of the first and second support pins 21 and 22 in the support frame main body 24. The fixing ring 29 includes a locking portion 29 a that is locked to the fixing groove 20 b of the support frame body 24, an engagement groove 29 b, a boot groove 29 c for attaching the boot 25, and the fixing ring 29 to the support frame body 24. And an outer peripheral groove 29d to which a retaining ring (not shown) to be fixed is attached.

  By providing the fixing ring 29, the second gap adjusting mechanism 40 can be easily assembled to the brake device 100, and can easily be retrofitted to the existing brake device 100, and assembling compatibility can be ensured. Furthermore, maintenance and replacement of each component of the second gap adjustment mechanism 40 can be easily performed.

  The fixing ring 29 has a locking portion 29a that is locked to a fixing groove 20b that is normally used for mounting the boot 25, and a boot groove 29c for mounting the boot 25. Thus, the second gap adjusting mechanism 40 can be attached using the fixed groove 20b of the existing brake device 100, and the boot 25 can be attached as usual.

  The second gap adjusting mechanism 40 separates the second brake lining 4 adjacent to the brake disc 2 during braking by a set distance when releasing the brake. The second gap adjustment mechanism 40 exhibits a reaction force so as to resist the movement of the clamp body 40a provided on the inner periphery of the fixing ring 29 and capable of clamping the first support pin 21 and the brake body 10 during braking. A release spring 50 as an urging member for urging the clamp portion 40a and a ring body 49 provided on the outer periphery of the first support pin 21 and in contact with the support frame 20 are provided.

  The ring body 49 supports the release spring 50 in the axial direction with the clamp portion 40a. The ring body 49 comes into contact with the end portion of the support frame 20. The ring body 49 is pressed against the end of the support frame 20 in a state where the second gap adjusting mechanism 40 is operating. The internal configuration of the second gap adjustment mechanism 40 will be described in detail later with reference to FIG.

  The second gap adjusting mechanism 40 is provided on the support frame 20, and the movement of the first support pin 21 in the axial direction is restricted and the movement in the radial direction is allowed.

  Specifically, the inner diameter of the bottom of the engagement groove 29 b of the fixing ring 29 is formed larger than the outer diameter of the ring body 49 of the second gap adjustment mechanism 40. Therefore, even if the brake body 10 is inclined with respect to the support frame 20, the ring body 49 can move in the engagement groove 29b and maintain the engaged state.

  More specifically, the distance between the inner diameter of the bottom of the engagement groove 29b and the outer diameter of the ring body 49 of the second gap adjusting mechanism 40 is when the maximum inclination angle θmax [deg] with respect to the support frame 20 of the brake main body 10. The ring body 49 is formed to have a size larger than the displacement amount. Therefore, even when the brake body 10 is inclined by the maximum inclination angle θmax with respect to the support frame 20, the ring body 49 can move in the engagement groove 29b and maintain the engagement state.

  The brake main body 10 is inclined in the left-right direction (the rotation axis direction of the wheel 1) with respect to the support frame 20 so as to follow the tilting of the traveling wheel 1. The maximum inclination angle θmax of the brake body 10 with respect to the support frame 20 is, for example, ± 3 [deg].

  On the other hand, the second gap adjusting mechanism 40 is floatingly supported so as to be movable in the radial direction with respect to the support frame 20. Therefore, as shown in FIGS. 4 and 5, the ring body 49 of the second gap adjustment mechanism 40 is not affected even when the brake main body 10 is inclined by the angle θ [deg] in one direction or the other direction with respect to the support frame 20. At least a portion is engaged with the engaging groove 29 b of the fixing ring 29. Accordingly, even in this state, the movement of the second gap adjusting mechanism 40 in the axial direction is restricted, so that the second brake lining 4 that is close to the brake disk 2 during braking can be separated by a set distance when braking is released. Therefore, in the floating brake device 100, it is possible to prevent contact between the second brake lining 4 supported by the second caliper arm 14 where the pressing portion 35 is not provided and the brake disc 2.

  In the second gap adjusting mechanism 40, as shown in FIG. 6A, the ring body 49 is formed in a circular shape. Thus, even when the brake body 10 is inclined in the left-right direction with respect to the support frame 20, at least a part of the ring body 49 is engaged with the engagement groove 29 b of the fixing ring 29 (a state indicated by a two-dot chain line). ). Instead, as shown in FIG. 6B, the ring body 49 may be formed in an elliptical shape. In this case, the ring body 49 is arranged so as to move in the direction of an elliptical short side when the brake body 10 is tilted left and right with respect to the support frame 20. Therefore, even when the brake body 10 is inclined in the left-right direction with respect to the support frame 20, the vicinity of the end of the elliptical long side of the ring body 49 is engaged with the engagement groove 29 b of the fixing ring 29 (two State indicated by a dotted line). As described above, the ring body 49 may have a shape in which at least a part of the ring body 49 is engaged with the engagement groove 29b when the brake body 10 is tilted left and right with respect to the support frame 20.

  Next, each member of the second gap adjustment mechanism 40 will be described with reference to FIG.

  The release spring 50 is a coil spring that biases the clamp portion 40a that clamps the first support pin 21 in the release direction.

  When the brake main body 10 and the first support pin 21 move in the pressing direction during braking, the release spring 50 generates a reaction force against the movement, and the brake main body 10 and the first support pin 21 pass through the clamp portion 40a. Is biased in the release direction. As a result, the brake body 10 and the first support pin 21 are moved in the release direction by the urging force of the release spring 50 during non-braking, so that a predetermined gap is formed between the second brake lining 4 and the brake disc 2.

  Further, the brake body 10 and the first support pin 21 are urged in the release direction by the release spring 50 even in the non-braking state. This prevents the brake main body 10 and the first support pin 21 from moving in the pressing direction due to vehicle vibration or the like during non-braking.

  The clamp portion 40a includes a retainer 41 as a wedge member having a wedge surface 41a that forms a wedge space with the outer peripheral surface of the first support pin 21, a rolling element 42 accommodated in the wedge space, and a rolling element 42. A clamp spring 43 as a pressing member that presses the retainer 41 so as to be pressed against the wedge surface 41a from the axial direction of the first support pin 21, and an inner and outer periphery provided between the retainer 41 and the first support pin 21 in the radial direction. And a cylindrical inner member 44 having a through hole 45a that opens to the surface.

  The retainer 41 is a cylindrical member provided on the outer periphery of the inner member 44. The retainer 41 has a tapered wedge surface 41 a that is inclined with respect to the axial direction of the first support pin 21. The retainer 41 forms a wedge space with the outer peripheral surface of the first support pin 21 by the wedge surface 41 a, in which the radial distance gradually decreases along the axial direction of the first support pin 21.

  A shim ring 41 b for adjusting the gap and a fixing ring 41 c for fixing the shim ring 41 b to the retainer 41 are provided between the retainer 41 and a flange portion 47 described later of the inner member 44. By changing the thickness of the shim ring 41b, the force with which the retainer 41 presses the rolling element 42 against the first support pin 21 can be adjusted.

  The rolling element 42 is formed in a cylindrical shape and contacts both the outer peripheral surface of the first support pin 21 and the wedge surface 41a through the through hole 45a. The rolling element 42 is not limited to a cylindrical shape, and may be formed in a spherical shape. Moreover, in FIG. 7, although the single rolling element 42 is shown in figure, the number of the rolling elements 42 is not restricted to this, A plurality may be provided. By providing the plurality of rolling elements 42, the clamp portion 40a can stably support the first support pin 21.

  The inner member 44 is formed as a receiving portion that supports the clamp spring 43 between the cylindrical main body 45 in which the through hole 45 a is formed and the retainer 41 that is formed to extend radially outward from the outer peripheral surface of the main body 45. A spring receiving portion 46, a flange portion 47 that extends radially outward from one end of the main body 45 and supports the release spring 50 between the ring body 49, and the spring receiving portion 46. And a C-ring 48 as a restricting portion attached to the outer peripheral surface of the main body 45 on the side opposite to the flange 47 toward the radially outer side.

  The spring receiving portion 46 is provided on the side opposite to the flange portion 47 across the through hole 45a. The clamp spring 43 is interposed between the spring receiving portion 46 and the retainer 41 in a compressed state, and urges the retainer 41 to the right in FIG. 7 so that the rolling element 42 is pressed against the wedge surface 41a. Thereby, the rolling element 42 is pushed toward the narrow part (left part in FIG. 7) in the wedge space. Therefore, the relative movement between the clamp portion 40a and the first support pin 21 is restricted by the wedge effect. The clamp part 40a clamps the first support pin 21 in this way.

  The spring receiving portion 46 has a spring receiving surface 46a with which the clamp spring 43 abuts and a contact surface 46b with which the ring body 49 abuts. The spring receiving portion 46 is pressed against the C ring 48 by the urging force of the clamp spring 43. The position of the spring receiving portion 46 in the axial direction is defined by a C ring 48.

  As shown in FIG. 7, when the brake device 100 is in the non-braking state, the contact surface 46 b of the spring receiving portion 46 and the ring body 49 contact each other. When the spring receiving part 46 and the ring body 49 contact | abut, the further movement of the clamp part 40a to a cancellation | release direction is controlled.

  Next, the operation of the brake device 100 will be described with reference to FIGS.

  8 to 10, the first support pin 21 in the non-braking state is indicated by a broken line. Hereinafter, an axial distance between the flange portion 47 of the clamp portion 40a and the second bracket portion 16 of the brake body 10 is referred to as a “relative distance” between the clamp portion 40a and the brake body 10. Further, as shown in FIG. 7, the relative distance when the second brake lining 4 is not worn is “L0”.

  When the railway vehicle travels, the wheel 1 rotates at a high speed. Here, when the brake device 100 is switched to the braking state by an operation of the driver or the like, the pressing portion 35 (see FIG. 1) is pressed via the guide plate 5 by the compressed air supplied from the air pressure source to the first brake lining 3. Is pressed toward the brake disc 2 provided on the wheel 1.

  At this time, a reaction force that the pressing portion 35 presses the first brake lining 3 acts on the brake body 10. Thus, as shown in FIG. 8, the brake body 10 is attached with the release spring 50 together with the first support pin 21 and the clamp portion 40a by the reaction force of the pressing portion 35 while maintaining the relative distance L0 from the clamp portion 40a. It moves in the pressing direction against the force. Therefore, the second brake lining 4 is drawn toward the brake disc 2, the first and second brake linings 3 and 4 come into contact with both sides of the brake disc 2, and frictional force is generated, and the rotation of the wheel 1 is braked. The As a result, the railway vehicle will eventually stop due to a decrease in speed.

  When the braking of the wheel 1 by the brake device 100 is released by the driver's operation or the like, the first brake lining 3 is separated from the state in contact with the brake disc 2 by the restoring force of the return spring provided in the adjuster 30. To do. Also, the compressed air in the pressure chamber is discharged from a through hole (not shown), and the first brake lining 3 returns to the position before braking.

  As a result, the brake disc 2 and the first brake lining 3 face each other again at a constant interval by the action of the first gap adjustment mechanism.

  On the other hand, when the compressed air in the pressure chamber is discharged, the brake body 10, the first support pin 21, and the clamp portion 40a receive the urging force of the release spring 50 compressed at the time of braking as a restoring force, and the release direction Move towards The brake body 10, the first support pin 21, and the clamp portion 40 a move in the release direction until the contact surface 46 b of the spring receiving portion 46 contacts the ring body 49, and the state before braking (see FIG. 7). Return to the state shown.

  Thereby, the brake disc 2 and the second brake lining 4 are separated from each other and face each other with a certain gap again. Therefore, contact between the second brake lining 4 and the brake disc 2 when the brake device 100 is released is prevented. Thereby, abrasion of the 2nd brake lining 4 is suppressed and the life of the 2nd brake lining 4 can be improved. Further, the wheel 1 can rotate without being affected by the brake device 100.

  When the friction member 3b of the first brake lining 3 is worn, the guide plate 5 is advanced toward the brake disc 2 by the amount of wear of the friction member 3b by the first gap adjusting mechanism. For this reason, the gap between the first brake lining 3 and the brake disc 2 is kept constant.

  On the other hand, since the first caliper arm 14 is not provided with the first gap adjusting mechanism, the friction member 4b of the second brake lining 4 is worn (hereinafter, simply referred to as “the second brake lining 4 is worn”). Then, the clearance gap between the 2nd brake lining 4 and the brake disc 2 becomes large. For this reason, the amount of movement of the brake body 10 that moves in the pressing direction in order to bring the second brake lining 4 and the brake disc 2 into contact with each other from the non-braking state to make the braking state increases.

  Here, in the brake device 100, when the brake body 10 moves in the pressing direction by a predetermined reference movement amount S0 from the non-braking state (the state shown in FIG. 7), the first support pin 21 and the clamp portion 40a are moved relative to each other. The clamp part 40a and the release spring 50 are configured so that the moving force is balanced with the force (hereinafter referred to as “clamping force”) that clamps the first support pin 21 by the clamp part 40a.

  More specifically, during braking, the force for moving the first support pin 21 and the clamp portion 40a relative to each other (hereinafter simply referred to as “relatively moving force”) acts on the brake body 10 from the pressing portion 35. And the urging force of the release spring 50 that acts on the clamp portion 40a and changes according to the amount of movement of the clamp portion 40a. That is, the relative moving force is the reaction force of the pressing portion 35 that acts on the brake body 10 and the first support pin 21 in the pressing direction, and the biasing force of the release spring 50 that acts on the clamping portion 40a in the releasing direction. It is due to. Since the reaction force of the pressing portion 35 is determined according to a desired braking force, the force for relative movement is mainly determined by the urging force of the release spring 50.

  The clamping force of the clamp part 40a is a frictional force generated between the rolling element 42 and the first support pin 21 with respect to the force of relative movement. The clamping force is determined by the biasing force of the clamp spring 43, the shape of the wedge surface 41a, the shape of the rolling element 42, the coefficient of friction between the first support pin 21 and the rolling element 42, and the like. By appropriately setting these, a desired clamping force can be obtained. The clamping force of the clamp part 40a is constant regardless of the amount of movement of the brake body 10. 8 to 10, the clamping force and the relative moving force are schematically shown by arrows.

  Hereinafter, the operation of the second gap adjustment mechanism 40 will be specifically described.

  As shown in FIG. 8, when the wear of the second brake lining 4 is small and the movement amount of the brake body 10 is the movement amount S1 smaller than the reference movement amount S0, the relative movement force in the braking state is the clamp portion 40a. The clamping force 40a and the first support pin 21 do not move relative to each other. That is, at the time of braking, the brake body 10, the first support pin 21, and the clamp part 40a are pressed together while maintaining the state in which the first support pin 21 is clamped by the clamp part 40a and maintaining the relative distance L0. Move in the direction.

  As shown in FIG. 9, when the amount of movement of the brake body 10 during braking becomes the reference amount of movement S0, the force of relative movement by the urging force of the release spring 50 and the reaction force of the pressing portion 35 is the clamping force of the clamping portion 40a. Balance with. Hereinafter, the urging force of the release spring 50 when the brake body 10 moves by the reference movement amount S0 is referred to as “reference urging force”.

  When the brake body 10 tries to move in the pressing direction beyond the reference movement amount S0, the release spring 50 is further compressed, so that the relative moving force is generated between the rolling element 42 and the first support pin 21. The friction force (clamping force) generated is exceeded. As a result, the clamp of the clamp part 40a is released, and the first support pin 21 and the brake body 10 move in the pressing direction beyond the reference movement amount S0, while the clamp part 40a does not move further in the pressing direction. Do not move. In this way, relative movement between the clamp portion 40a, the first support pin 21, and the brake body 10 is allowed.

  As described above, in the brake device 100 according to this embodiment, the relative movement force exceeds the frictional force (clamping force) between the rolling element 42 and the first support pin 21, so that the clamp portion 40 a and the first support are supported. A state in which the pin 21 moves relative to the pin 21 is a state in which the clamp of the first support pin 21 by the clamp portion 40a is released.

  As shown in FIG. 10, the first support pin 21 and the brake main body 10 move relative to the clamp portion 40 a up to a movement amount S <b> 2 such that the brake device 100 is in a braking state. At this time, the relative distance between the brake body 10 and the clamp portion 40a is L1 smaller than L0. When the braking of the brake device 100 is released, the reaction force acting on the brake body 10 from the pressing portion 35 disappears. For this reason, the force which moves the brake main body 10 and the 1st support pin 21, and the clamp part 40a relatively is lost, and the force which moves relatively is less than a clamp force. Therefore, it will be in the clamped state which the 1st support pin 21 does not move relatively with the clamp part 40a again. As a result, the brake body 10, the first support pin 21, and the clamp portion 40a move together in the release direction by the reference biasing force of the release spring 50. Therefore, the brake disc 2 and the second brake lining 4 are separated from each other and again face each other with a certain gap.

  Explaining in more detail with reference to FIGS. 8 to 10, the clamp portion 40a does not move in the pressing direction when the clamp is released, and the brake body 10 and the first support pin 21 have the reference movement amount S0. It moves beyond the pressing direction. The clamp part 40a whose clamp is released clamps the first support pin 21 again after the braking of the brake device 100 is released.

  As shown in FIGS. 8 and 9, the clamp portion 40a is positioned at the position where the relative distance between the brake body 10 and the clamp portion 40a is L0 before the release of the clamp where the movement amount of the brake body 10 is the reference movement amount S0 or less. 1 The support pin 21 is clamped. On the other hand, as shown in FIG. 10, when the clamp portion 40a moves relative to the brake body 10 and the first support pin 21 and clamps the first support pin 21 again, the relative distance is L1 which is smaller than L0. The first support pin 21 is clamped in position. That is, the position where the first support pin 21 is clamped is shifted by the relative movement distance T between the clamp portion 40a and the brake body 10 compared to before the clamp is released. For this reason, when the brake main body 10 is returned to the release direction by the release spring 50, the position of the brake main body 10 after the release of the brake is a position shifted by the relative movement distance T in the pressing direction.

  Here, as shown in FIG. 10, even when the brake body 10 has moved beyond the reference movement amount S0, the clamp portion 40a does not move in the pressing direction, so the return amount of the release spring 50 in the release direction. Is constant at the reference movement amount S0. Therefore, when the brake body 10 moves beyond the reference movement amount S0 to brake the wheel 1 and the braking is released, the brake disc 2 and the second brake lining 4 again return to the return amount (reference movement amount S0). ) Face each other with a certain gap. Thus, the release spring 50 and the clamp part 40a can exhibit a gap adjusting function for adjusting the gap between the second brake lining 4 and the brake disc 2. Thereby, even if wear of the second brake lining 4 progresses, a gap between the second brake lining 4 and the brake disk 2 can be appropriately secured.

  When the amount of movement of the brake body 10 during braking increases, the amount of compression of the release spring 50 increases accordingly, and the urging force of the release spring 50 that urges the clamp portion 40a also increases. Since the urging force of the release spring 50 becomes a resistance to the movement of the brake body 10 during braking, if it becomes excessive, the pressing force of the second brake lining 4 against the brake disc 2 decreases, and the braking force becomes unstable. There is a fear.

  On the other hand, in the brake device 100, when the amount of wear of the second brake lining 4 increases and the amount of movement of the brake body 10 during braking exceeds the reference amount of movement S0, clamping by the clamp portion 40a is released. For this reason, the urging force of the release spring 50 does not exceed the reference urging force. In other words, even if the amount of wear of the second brake lining 4 increases, the reaction force from the release spring 50 is suppressed below the reference urging force, and an increase in resistance to the movement of the brake body 10 can be suppressed. Thus, even if the brake body 10 moves in the pressing direction beyond the reference movement amount S0, the urging force of the release spring 50 is suppressed below the reference urging force, so that the stability of the braking force is ensured.

  As described above, in the brake device 100, even if the movement amount of the brake body 10 in the pressing direction exceeds the reference movement amount S0, the urging force of the release spring 50 does not exceed the reference urging force. When the release spring 50 biases the clamp portion 40a, the second brake lining 4 and the brake disk 2 are separated from each other during non-braking, and when the reference movement amount S0 is exceeded, the clamp is released and the reaction force of the release spring 50 is released. Can be suppressed. That is, resistance to movement of the brake body 10 during braking is suppressed, and the second brake lining 4 and the brake disk 2 can be separated by the urging force of the release spring 50 during non-braking.

  The reference movement amount S0 is determined so that the stability of the braking force and the life of the second brake lining 4 become desired. Specifically, the clamping force and the release determined based on the configuration of the clamp portion 40a according to the allowable reaction force of the release spring 50 and the amount of movement of the brake body 10 (the amount of wear of the second brake lining 4). It is predetermined by adjusting the relationship with the relative moving force determined by the spring 50.

  Hereinafter, the clamping force and the force for relative movement will be described in detail with specific examples.

  The set load of the clamp part 40a is set to 1000 N, for example. Further, the urging force of the clamp spring 43 is set to about 200 N or less, for example. Thereby, the clamping force of the clamp part 40a, that is, the frictional force between the rolling element 42 and the first support pin 21 is about 800N.

  The urging force (set load) of the release spring 50 in the non-braking state is set to about 500 N, for example. The urging force of the release spring 50 is set so as not to exceed 800 N when the brake body 10 is moved by a movement amount equal to or less than the reference movement amount S0 and the second brake lining 4 is in contact with the brake disc 2. For example, the urging force of the release spring 50 becomes an urging force of about 700 N when the second brake lining 4 comes into contact with the brake disc 2 and enters the braking state in a state where the second brake lining 4 is not worn.

  When the brake body 10 moves in the pressing direction by the reference movement amount S0, the release spring 50 is compressed by that amount, and a reference biasing force of 800 N that balances the clamping force is exhibited.

  When the brake body 10 moves beyond the reference movement amount S0, the release spring 50 is further compressed, and exerts an urging force of slightly larger than 800N and about 1000N. For this reason, with a clamping force of 800 N, the relative movement between the clamp portion 40a and the first support pin 21 cannot be restricted, and both of them move relative to each other to release the clamp.

  When the clamp by the clamp part 40a is released, the clamp part 40a does not move further in the pressing direction, and the reaction force of the release spring 50 does not increase. That is, the biasing force of the release spring 50 does not greatly exceed 800N. Therefore, even if the amount of movement of the brake body 10 increases beyond the reference movement amount S0 during braking, the reaction force against the movement of the brake body 10 is suppressed to about 800N. Therefore, contact between the second brake lining 4 and the brake disc 2 during non-braking is prevented while ensuring the stability of the braking force of the brake device 100.

  In addition, the above specific example showed only an example about the force moved relative to a clamping force, and the structure of the brake device 100 is not restricted to the said specific example. In the brake device 100, the force that moves relative to the clamping force may be configured as in the above-described specific example, or may be other configurations.

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

  The second gap adjusting mechanism 40 is restricted from moving in the axial direction of the first support pin 21 and is capable of moving in the radial direction. Therefore, even when the brake body 10 is inclined with respect to the support frame 20, the movement of the second gap adjustment mechanism 40 in the axial direction is restricted. Therefore, even when the brake body 10 is tilted with respect to the support frame 20, the brake body 10 that has moved in the axial direction of the first support pin 21 during braking is returned by a set distance in the opposite direction when braking is released. Accordingly, it is possible to provide the brake device 100 that can adjust the gap between the second brake lining 4 and the brake disk 2 even when the brake body 10 is inclined with respect to the support frame 20.

  In the brake device 100, the reaction force of the release spring 50 accompanying the movement of the brake body 10 during braking is applied to the first support pin 21 via the clamp portion 40a. Thus, when the braking of the brake device 100 is released, the brake body 10 moves in a direction in which the second brake lining 4 and the brake disc 2 are separated by a reaction force. Therefore, the contact between the second brake lining 4 and the brake disc 2 when the brake device 100 is not braked is prevented. Therefore, wear of the second brake lining 4 during non-braking is suppressed, and the life of the second brake lining 4 can be improved.

  Further, when the amount of movement of the brake body 10 necessary for braking increases due to wear of the second brake lining 4 and the brake body 10 moves in the pressing direction beyond the reference movement amount S0, the first support pin 21 and the clamp portion 40a. Is greater than the frictional force between the first support pin 21 and the rolling element 42 of the clamp portion 40a. Since the clamp portion 40a moves relative to the first support pin 21 without moving in the pressing direction, the reaction force of the release spring 50 does not increase even if the brake body 10 moves beyond the reference movement amount S0. Thereby, even if the movement amount of the brake main body 10 exceeds the reference movement amount S0 during braking, an increase in the reaction force with respect to the movement of the brake main body 10 is suppressed. Therefore, while ensuring the stability of the braking force of the brake device 100, the gap between the second brake lining 4 and the brake disc 2 during non-braking is appropriately secured to prevent contact between the two brakes. The life of the lining 4 can be improved.

  Further, in the brake device 100, the relative movement force and the clamping force are set so that the first support pin 21 and the clamp portion 40a move relative to each other when the movement amount of the brake body 10 exceeds the reference movement amount S0. Yes. For this reason, the clamp can be released without providing a release mechanism for releasing the clamp, the space around the clamp portion 40a can be saved, and the brake device 100 can be downsized.

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

  The brake device 100 that applies frictional force to the brake disc 2 that rotates together with the wheel 1 includes first and second brake linings 3 and 4 that can apply frictional force by slidingly contacting the brake disc 2 from both sides of the brake disc 2. The brake body 10 having the first and second caliper arms 12 and 14 to be supported, and the first and second support pins that are supported by the support frame 20 attached to the carriage so as to be movable in the axial direction and that support the brake body 10. 21 and 22, the first brake lining 3 provided on the first caliper arm 12 is pressed against the brake disc 2, and the brake body 10 is moved in the axial direction of the first and second support pins 21 and 22, thereby A pressing portion 35 that presses the lining 4 against the brake disc 2, and shafts of the first and second support pins 21 and 22 during braking And a second gap adjustment mechanism 40 that returns the brake body 10 that has moved in the opposite direction by a set distance in the opposite direction when the brake is released. The second gap adjustment mechanism 40 is provided in the support frame 20 and is provided with first and second supports. The movement of the pins 21 and 22 in the axial direction is restricted and the movement in the radial direction is allowed.

  In this configuration, the second gap adjusting mechanism 40 is restricted from moving in the axial direction of the first and second support pins 21 and 22 and is capable of moving in the radial direction. Therefore, even when the brake body 10 is inclined with respect to the support frame 20, the movement of the second gap adjustment mechanism 40 in the axial direction is restricted. Therefore, even when the brake body 10 is inclined with respect to the support frame 20, the brake body 10 that has moved in the axial direction of the first and second support pins 21 and 22 during braking returns to the opposite direction by a set distance when the brake is released. It is. Accordingly, it is possible to provide the brake device 100 that can adjust the gap between the second brake lining 4 and the brake disk 2 even when the brake body 10 is inclined with respect to the support frame 20.

  The second gap adjustment mechanism 40 includes a ring body 49 provided on the outer periphery of the first and second support pins 21 and 22 and abutting against the support frame 20, and the support frame 20 includes the first and second support members. An engagement groove 29b is formed on the inner peripheral surface of the insertion hole 20a through which the pins 21 and 22 are inserted, and the ring body 49 is engaged to restrict the movement of the second gap adjustment mechanism 40 in the axial direction. The inner diameter of the bottom of the groove 29 b is formed larger than the outer diameter of the ring body 49.

  In this configuration, the inner diameter of the bottom of the engagement groove 29 b is formed larger than the outer diameter of the ring body 49, so that the ring body 49 is engaged even when the brake body 10 is inclined with respect to the support frame 20. The engaged state can be maintained by moving in the groove 29b.

  Further, the interval between the inner diameter of the bottom of the engagement groove 29b and the outer diameter of the ring body 49 is formed to be larger than the displacement amount of the ring body 49 when the maximum inclination angle θmax with respect to the support frame 20 of the brake body 10 is formed. The

  In this configuration, even when the brake body 10 is inclined by the maximum inclination angle θmax with respect to the support frame 20, the ring body 49 can move in the engagement groove 29 b and maintain the engagement state.

  The support frame 20 includes a support frame main body 24 attached to the vehicle body or the carriage, and a fixing ring 29 attached to the support frame main body 24 and having an engagement groove 29b formed on the inner periphery.

  The fixing ring 29 is attached to the axial ends of the first and second support pins 21 and 22 in the support frame body 24.

  In these configurations, by providing the fixing ring 29, the second gap adjusting mechanism 40 can be easily assembled to the brake device 100, and can be easily retrofitted to the existing brake device 100 to ensure assembly compatibility. it can. Furthermore, maintenance and replacement of each component of the second gap adjustment mechanism 40 can be easily performed.

  The support frame main body 24 has an annular fixing groove 20b on the outer periphery, and the fixing ring 29 has a locking portion 29a locked to the fixing groove 20b.

  In this configuration, the fixing ring 29 has a locking portion 29 a that is locked to a fixing groove 20 b that is normally used for attaching the boot 25. Thereby, the 2nd clearance gap adjustment mechanism 40 can be attached using the fixed groove | channel 20b of the existing brake device 100. FIG.

  Further, the second gap adjusting mechanism 40 exhibits a reaction force against the movement of the clamp body 40a capable of clamping the first and second support pins 21 and 22 and the brake body 10 during braking. And a release spring 50 that urges the clamp portion 40a so as to resist the movement.

  In this configuration, the reaction force of the release spring 50 accompanying the movement of the brake body 10 during braking is applied to the first and second support pins 21 and 22 via the clamp portions 40a and 140. Thus, when the braking of the brake device 100 is released, the brake body 10 moves in a direction in which the second brake lining 4 and the brake disc 2 are separated by a reaction force. Therefore, contact between the second brake lining 4 and the brake disc 2 when the brake device 100 is released is prevented. Therefore, the lifetime of the second brake lining 4 of the brake device 100 can be improved.

  Further, the brake device 100 has the first and second clamps 40a in a state where the movement amount of the brake body 10 in the pressing direction in which the second brake lining 4 approaches the brake disc 2 is equal to or less than a predetermined reference movement amount S0. When the second support pins 21 and 22 are clamped and the brake body 10 moves in the pressing direction beyond the reference movement amount S0, the clamps of the first and second support pins 21 and 22 are released.

  In this configuration, when the amount of movement of the brake body 10 necessary for braking increases due to wear of the second brake lining 4 and the brake body 10 moves in the pressing direction beyond the reference movement amount S0, the brake body 10 and the first and The second support pins 21 and 22 move relative to the clamp portion 40a. For this reason, even if the brake body 10 moves beyond the reference movement amount S0, the clamp portion 40a does not move in the pressing direction, and the reaction force of the release spring 50 does not increase. Therefore, even when the amount of movement of the brake body 10 increases beyond the reference movement amount S0 during braking, an increase in the reaction force with respect to the movement of the brake body 10 is suppressed. Therefore, it is possible to improve the life of the second brake lining 4 by preventing the contact between the second brake lining 4 and the brake disc 2 during non-braking while ensuring the stability of the braking force of the brake devices 100 and 200. Can do.

  In addition, the brake device 100 has a wedge space in which the interval gradually decreases along the axial direction of the first and second support pins 21 and 22, and the outer peripheral surface of the first and second support pins 21 and 22. A retainer 41 having a wedge surface 41a formed therebetween, a rolling element 42 accommodated in the wedge space, and a clamp spring 43 that presses the retainer 41 so that the rolling element 42 is pressed against the wedge surface 41a from the axial direction; Have.

  In addition, the brake device 100 further includes a cylindrical inner member 44 having a through hole 45a in which the clamp portion 40a is provided between the retainer 41 and the first and second support pins 21 and 22 and opens on the inner and outer peripheral surfaces. The rolling element 42 contacts the outer peripheral surfaces of the first and second support pins 21 and 22 through the through hole 45a, and the inner member 44 supports the clamp spring 43 with the retainer 41. And a flange portion 47 that supports the release spring 50 between the ring body 49 and the ring body 49.

  In these configurations, the clamp spring 43 biases the retainer 41 so that the rolling element 42 is pressed against the wedge surface 41a. Thereby, the rolling element 42 is pushed toward the narrow part in the wedge space. Therefore, the relative movement between the clamp part 40a and the first and second support pins 21 and 22 is restricted by the wedge effect, and the clamp part 40a clamps the first and second support pins 21 and 22.

  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, in the above embodiment, the second gap adjustment mechanism 40 is provided on the first and second support pins 21 and 22, respectively. Instead of this, the second gap adjusting mechanism 40 may be provided only on one of the first and second support pins 21 and 22.

  Moreover, in the said embodiment, the fixing ring 29 formed integrally so that it may have the latching | locking part 29a latched by the fixing groove 20b of the support frame 20, and the boot groove 29c for attaching the boot 25 is provided. ing. Instead, as in the modification shown in FIG. 11, a U-shaped ring 29e having a U-shaped cross-sectional shape and having a boot groove 29c, and also having a U-shaped cross-sectional shape and an inner circumference The fixing ring 29 may be formed by combining with the fixing cover 29f in which the engaging groove 29b is formed. The fixed cover 29f is formed in a C shape and is fastened by a bolt 29g to form a ring shape. In this case, since it is a combination of two members having a U-shaped cross-sectional shape, the fixing ring 29 can be easily formed.

  In the above embodiment, the fixing ring 29 is attached to the support frame main body 24 to form the engagement groove 29b. Instead of this, the engaging groove 29b may be formed in the support frame main body 24 without providing the fixing ring 29 as in another modification shown in FIG. In this case, space saving around the support frame 20 can be achieved, and the brake device 100 can be downsized.

DESCRIPTION OF SYMBOLS 100 ... Brake device, 1 ... Wheel, 2 ... Brake disc, 3 ... 1st brake lining, 4 ... 2nd brake lining, 10 ... Brake body, 12 ... 1st DESCRIPTION OF SYMBOLS 1 caliper arm, 14 ... 2nd caliper arm, 20 ... support frame, 20b ... fixing groove, 21 ... 1st support pin (support pin), 22 ... 2nd support pin (support) Pin), 24 ... support frame body, 29 ... fixing ring (fixing member), 29a ... locking portion, 35 ... pressing portion (pressing mechanism), 40 ... second gap adjusting mechanism (Gap adjustment mechanism), 40a ... clamp part, 41 ... retainer (wedge member), 41a ... wedge surface, 42 ... rolling element, 43 ... clamp spring (pressing member), 44 ..Inner member, 45a ... through hole, 47 Flange portion (supporting portion), 48 ... C-ring (restricting portion), 49 ... ring body, 50 ... release spring (biasing member)

Claims (10)

A brake device that holds and brakes a brake disc that rotates together with wheels,
A brake body having first and second caliper arms that respectively support first and second brake linings that slidably contact the brake disc from both sides of the brake disc to apply a frictional force;
A support pin that is supported by the support frame attached to the vehicle body or the carriage so as to be movable in the axial direction and supports the brake body;
A pressing mechanism that is provided on the first caliper arm and presses the first brake lining against the brake disc and moves the brake body in the axial direction of the support pin to press the second brake lining against the brake disc; ,
A gap adjusting mechanism for returning the brake body moved in the axial direction of the support pin during braking by a set distance in the opposite direction when releasing the brake, and
The gap adjustment mechanism is provided on the support frame, and the movement of the support pin in the axial direction is restricted and the movement in the radial direction is allowed.
Brake device characterized by that. The brake device according to claim 1,
The gap adjustment mechanism has a ring body that is provided on the outer periphery of the support pin and contacts the support frame;
The support frame has an engagement groove that is formed on an inner peripheral surface of an insertion hole through which the support pin is inserted and that engages with the ring body and restricts movement of the gap adjustment mechanism in the axial direction.
The inner diameter of the bottom of the engagement groove is formed larger than the outer diameter of the ring body,
Brake device characterized by that. The brake device according to claim 2,
The interval between the inner diameter of the bottom of the engagement groove and the outer diameter of the ring body is formed to be larger than the displacement amount of the ring body when the brake body has a maximum inclination angle with respect to the support frame.
Brake device characterized by that. The brake device according to claim 2 or 3,
The support frame is
A support frame body attached to the vehicle body or the carriage,
A fixing member attached to the support frame main body and having the engagement groove formed on the inner periphery thereof,
Brake device characterized by that. The brake device according to claim 4,
The fixing member is attached to an axial end portion of the support pin in the support frame main body.
Brake device characterized by that. The brake device according to claim 4 or 5,
The support frame body has an annular fixing groove on the outer periphery,
The fixing member has a locking portion locked in the fixing groove.
Brake device characterized by that. The brake device according to any one of claims 2 to 6,
The gap adjusting mechanism is
A clamp part capable of clamping the support pin;
An urging member that exerts a reaction force against the movement of the brake main body during braking and urges the clamp portion to resist the movement of the brake main body.
Brake device characterized by that. The brake device according to claim 7,
The support pin is clamped by the clamp portion when the movement amount of the brake body in the pressing direction in which the second brake lining approaches the brake disc is equal to or less than a predetermined reference movement amount, and the brake body is When moving in the pressing direction beyond the reference movement amount, the clamp by the clamp part is released,
Brake device characterized by that. The brake device according to claim 7 or 8,
The clamp part is
A wedge member having a wedge surface that forms a wedge space with the outer peripheral surface of the support pin, the wedge space of which the interval gradually decreases along the axial direction of the support pin;
Rolling elements housed in the wedge space;
A pressing member that presses the wedge member or the rolling element so that the rolling element is pressed against the wedge surface from an axial direction.
Brake device characterized by that. The brake device according to claim 9, wherein
The clamp part further includes a cylindrical inner member having a through hole provided between the wedge member and the support pin and opening in an inner and outer peripheral surface,
The rolling element contacts the outer peripheral surface of the support pin through the through hole,
The inner member is
A receiving part for supporting the pressing member between the wedge member;
A support portion for supporting the biasing member between the ring body,
Brake device characterized by that.

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