JP6599730B2 - Disc brakes and disc brakes for railway vehicles - Google Patents

Description

  The present invention relates to a disk brake and a railway vehicle disk brake.

A floating caliper type disc brake in which a brake pad drag phenomenon is prevented has been conventionally known (see Patent Document 1).
In this floating caliper type disc brake, one pad (brake pad) is fixed to the arm of one end of the caliper (floating caliper) with both ends opened in two, and the other pad is provided on the arm on the opposite side The piston is driven toward the rotor by a piston (drive piston). Two guide pins are fixed to the arm at the other end of the caliper, and these guide pins are slidably supported in the axial direction on a cylindrical portion of a support coupled to a carriage frame or the like.

  That is, as shown in FIG. 13 (a), a pair of upper and lower guide pins 503 (only the upper side is shown) is spanned between a pair of arms 501 that are formed of a bifurcated caliper. (Not shown). A pair of holding rings 509 are attached to an inner surface of a cylindrical portion 507 of a support (not shown) surrounding the upper guide pin 503 by being sandwiched by a step portion 511 and a snap ring (not shown). A retraction rubber ring (friction rubber ring) 513 having an H-shaped cross section is fitted inside the holding ring 509.

In the above configuration, at the time of non-braking, the distal end portion of the protrusion 515 on the inner periphery of the retraction rubber ring 513 having an H-shaped cross section directly contacts the outer peripheral surface of the guide pin 503 as shown in FIG. It touches.
When braking, the guide pin 503 moves together with the caliper in the direction of arrow A in FIG. 13B by the reaction force with which the pad is pressed against the rotor. At the same time, the protrusion 515 of the retraction rubber ring 513 bends (bends) in the direction of arrow A due to friction between the outer peripheral surface of the guide pin 503 and the tip of the protrusion 515.

  When the braking is released, the retraction rubber ring 513 tries to return to its original posture due to its elasticity, and the guide pin 503 is caused to become frictional between the tip of the inner peripheral protrusion 515 and the outer peripheral surface of the guide pin 503 as shown in FIG. It is moved in the direction of arrow B in (c). As a result, the caliper coupled to the guide pin 503 slightly moves in the direction of arrow B, and the pad fixed to the caliper is slightly separated from the rotor. Thereby, the start of the vehicle can be lightened. When the vehicle starts to travel, the gap between the pad and the rotor becomes sufficiently large due to vibration and the like.

  According to such a floating caliper type disc brake, the pad fixed to the caliper is immediately pulled away from the rotor by the retraction rubber ring 513 when the brake is released to prevent dragging and to prevent an increase in starting torque. The wear of the lining can be prevented.

Japanese Utility Model Publication No. 6-32773

  However, the above-described conventional floating caliper type disc brake manages the caliper retraction effect (return force) and the return amount only by the retraction rubber ring 513, and therefore the manufacturing variations and dimensions of the retraction rubber ring 513 are limited. There is a problem that it is difficult to stably perform a desired caliper returning operation due to tolerances and the like. That is, there is a limit in obtaining the return force only by the retraction rubber ring 513. In addition, a fine adjustment of the return amount is required for calipers with different specifications, so there is a structure that allows fine adjustment of the return amount without any additional work on the existing caliper (casting). It is desired.

  The present invention has been made in view of the above situation, and its purpose is to easily set a caliper return force and to stably exhibit a desired caliper return operation, thereby reliably preventing pad dragging. DISCLOSURE OF THE INVENTION An object of the present invention is to provide a disc brake and a disc brake for railway vehicles.

The above object of the present invention is achieved by the following configuration.
(1) A base portion slidably supported via a guide pin with respect to a cylindrical support portion of the support, and a pair of pressing arms extended from the base portion to a position sandwiching the disk rotor from both sides in the axial direction. A floating caliper having a pair, a pair of brake pads provided at the front ends of the pair of pressing arms so as to face the side surface of the disk rotor, and one of the brake pads is driven toward the side surface of the disk rotor. For this purpose, the drive piston provided on one of the pair of pressing arms and the guide pin are arranged at least at the end opposite to the drive piston side at both ends of the guide pin and slidably supported with respect to the guide pin. And a caliper return mechanism for elastically urging the base portion opposite to the drive piston side.

  According to the disc brake having the structure of (1) above, the caliper return is provided at the end opposite to the drive piston side of the guide pin that slidably supports the base portion of the floating caliper with respect to the cylindrical support portion of the support. A mechanism is provided. The caliper returning mechanism generates a caliper returning force between the guide pin and the floating caliper. Therefore, the caliper returning mechanism causes the pair of pads to be separated from the disk rotor by the same clearance as before braking by the caliper returning force when the brake is released. The guide pin provided with the caliper return mechanism only needs to be replaced with the guide pin in the current floating caliper, and in order to realize pad drag countermeasures for the disc brake without any additional work on the existing floating caliper. Improvements are possible.

(2) The caliper return mechanism is attached to a spring accommodating portion provided at an end portion of the guide pin, and an open end flange is latched to an opening edge of the spring accommodating portion. A member, a spring receiving member that covers the opening of the spring accommodating portion and is fixed to the base, and the spring receiving member in a state having a predetermined interval with respect to the opening end flange, and a bottom portion of the spring accommodating member And a compression spring member interposed therebetween, wherein the disc brake has the configuration (1).

  According to the disc brake having the configuration of (2) above, the spring accommodating portion formed by opening at the end portion of the guide pin has a spring accommodating member in which the opening end flange is engaged with the opening edge of the spring accommodating portion. Inserted. A compression spring member is further accommodated in the spring accommodating member. The spring receiving member is fixed to the base of the floating caliper so as to cover the opening of the spring accommodating portion in a state where the spring receiving member is in contact with the other end of the compression spring member whose one end is in contact with the bottom of the spring accommodating member. Therefore, when the drive piston is driven and the floating caliper is moved toward the drive piston with respect to the guide pin, the compression spring member is compressed. In the caliper returning mechanism, a caliper returning force is obtained by the elastic restoring force of the compressed compression spring member.

(3) The disc brake according to (2), wherein the spring receiving member includes a sliding bearing for slidably supporting the base portion with respect to the guide pin.

  According to the disc brake having the configuration (3), the spring receiving member fixed to the base portion of the floating caliper is slidably supported on the outer periphery of the guide pin via the slide bearing. Thereby, the sliding resistance of the base part of the floating caliper is reduced by the sliding bearing, and the movement with respect to the guide pin can be performed with less force.

(4) The spring receiving member includes a cylindrical guide pin support portion fixed to the base portion so that the base portion is slidably supported with respect to the guide pin via the sliding bearing, and the compression portion. A spring support portion fixed to the guide pin support portion so as to be in contact with one end of the spring member so as to cover the outer opening end of the guide pin support portion. Disc brake.

  According to the disc brake having the configuration (4), the spring receiving member fixed to the base portion of the floating caliper is in contact with the guide pin support portion provided with the slide bearing and fixed to the base portion, and one end of the compression spring member. And a spring support portion fixed to the guide pin support portion. Therefore, the compression spring member can be attached and detached by removing the spring support portion while the guide pin support portion of the spring receiving member fixed to the base portion of the floating caliper is slidably supported on the outer periphery of the guide pin. Thereby, the return force and return amount of the floating caliper can be adjusted very easily by exchanging with a spring support or compression spring member having different specifications.

(5) The disc brake according to (4) above, wherein an O-ring is interposed between the guide pin support portion and the spring support portion.

  According to the disc brake having the configuration (5), the mating portion between the guide pin support portion and the spring support portion is sealed in a watertight manner by the O-ring, and water and dust enter the spring accommodating portion and the spring accommodating member. Can be prevented.

(6) The spring support portion in the caliper return mechanism disposed at both ends of the guide pin includes a bolt shaft penetrating through a bottom portion of the spring housing member and the hollow guide pin in a central axis direction, and the bolt shaft The disc brake according to (5), wherein the disc brake is fixed to the base portion by a nut screwed to the tip of the disc brake.

(7) The disk according to (6), wherein an O-ring is interposed between the spring support portion and the bolt shaft, and between the spring support portion and the nut. brake.

(8) A detent mechanism is provided between the guide pin support portion and the spring support portion, and between the spring support portion and the bolt shaft. The disc brake according to (7) above.

(9) The caliper return mechanism disposed at the end portion of the guide pin on the drive piston side has a stopper portion for restricting movement of the spring accommodating member in the axial direction with respect to the base portion at a predetermined interval. The disc brake according to any one of (2) to (8) above, wherein the disc brake is provided in a member.

According to the disc brake having the above configuration (9), since the caliper returning mechanism is arranged at both ends of the guide pin, for example, the base of the floating caliper is placed on the side opposite to the driving piston side required when the wheel is swung. It becomes possible to make the force to return.
During braking, when the drive piston is driven and the floating caliper is moved to the drive piston side with respect to the guide pin, the compression spring in the caliper return mechanism provided at the end of the guide pin opposite to the drive piston side The member is compressed to generate a caliper return force. At this time, the movement of the spring accommodating member in the caliper return mechanism disposed at the end of the guide pin on the driving piston side is regulated at a predetermined interval by the stopper portion of the spring receiving member, so that the floating caliper moves to the driving piston side. As a result of this movement, a gap (interference avoidance gap) is formed between the opening end flange of the spring accommodating member and the piston side end of the guide pin in the caliper return mechanism on the drive piston side. Therefore, the elastic force of the compression spring member in the caliper return mechanism on the drive piston side does not interfere with the caliper return force of the compression spring member in the caliper return mechanism opposite to the drive piston side, and the reaction force (load) against the caliper return force It will not act.

(10) A disc brake for a railway vehicle comprising the disc brake according to any one of (1) to (9) above.

  According to the railway vehicle disc brake having the above configuration (10), when the brake is pressed by the brake pads against the disc rotors attached to both side surfaces of the railway vehicle wheel, braking is performed. In addition, the pad clearance between the brake pad and the disc rotor can be maintained constant. As a result, it is possible to prevent uneven wear and drag of the brake pad and to suppress an increase in the starting torque of the vehicle.

  According to the disc brake and the railcar disc brake according to the present invention, the caliper return force can be easily set, and the desired caliper return operation can be stably exhibited, and the pad drag can be reliably prevented. .

  The present invention has been briefly described above. Further, the details of the present invention will be further clarified by reading through a mode for carrying out the invention described below (hereinafter referred to as “embodiment”) with reference to the accompanying drawings. .

1 is a perspective view of a disc brake according to a first embodiment of the present invention. FIG. 2 is an exploded perspective view of the disc brake shown in FIG. 1. FIG. 2 is a side view of the disc brake shown in FIG. 1. It is AA sectional drawing in FIG. It is BB sectional drawing in FIG. FIG. 2 is an operation explanatory diagram of the disc brake shown in FIG. 1, (a) is an operation explanatory diagram at the initial time, (b) is an operation explanatory diagram at the time of brake braking, and (c) is an operation explanatory diagram at the time of brake release slowly is there. (A) is sectional drawing of the disc brake shown in FIG. 1, (b) is sectional drawing of the disc brake which concerns on a comparative example. It is sectional drawing of the disc brake which concerns on 2nd Embodiment of this invention. It is a principal part enlarged view of FIG. It is a disassembled perspective view of the disc brake which concerns on 3rd Embodiment of this invention. It is sectional drawing of the disc brake shown in FIG. It is a principal part enlarged view of FIG. (A) is a schematic diagram showing the posture of the retraction rubber ring with respect to the guide pin during non-braking in the conventional configuration, (b) is a schematic diagram showing deformation of the protrusion of the retraction rubber ring during braking in (a), (C) is a schematic diagram which shows the effect | action at the time of repositioning of a retraction rubber ring.

Embodiments according to the present invention will be described below with reference to the drawings.
As shown in FIGS. 1 to 5, the floating caliper type disc brake 11 according to the first embodiment of the present invention will be described by taking as an example a case of being used in a railcar disc brake. In addition, the disc brake 11 can be suitably used in various industrial drive device brake devices that generate a braking force on a rotating member such as an elevator.

  The floating caliper type disc brake 11 according to the first embodiment is attached to both side surfaces of a wheel 35 (see FIG. 6) from a base portion 25 slidably supported by a support 23 coupled to a cart frame (not shown). A floating caliper 13 having a piston-side pressing arm 39 and an anti-piston-side pressing arm 41 which are a pair of pressing arms extended to a position sandwiching the disk rotors 37, 37 from both sides in the axial direction; A pair of brake pads 17 and 17 provided on the piston-side pressing arm 39 and the anti-piston-side pressing arm 41 so as to face the outer side surface, and a drive piston 15 provided on the piston-side pressing arm 39 (FIG. 6A ) And a caliper return mechanism 19 disposed at both ends of the upper guide pin (guide pin) 31. It has as a constituent.

  An upper guide pin 31 that is a guide pin with respect to an upper cylindrical support portion 27 and a lower cylindrical support portion 29 that are a pair of upper and lower cylindrical support portions of the support 23 are provided above and below the base portion 25 in the floating caliper 13. Lower guide pins 33 are spanned. The base 25 of the floating caliper 13 is slidably supported on the upper cylindrical support 27 and the lower cylindrical support 29 via the upper guide pin 31 and the lower guide pin 33. Both ends of the upper guide pin 31 are prevented from being detached from the base portion 25 by the caliper return mechanism 19. The lower guide pin 33 is fixed to the base portion 25 by a flange 34 and a nut 36. The base portion 25 of the floating caliper 13 includes a piston-side pressing arm 39 that is a pair of pressing arms and an anti-piston up to a position that sandwiches the disk rotor 37 attached to both sides of the wheel 35 (see FIG. 6) from both sides in the axial direction. The side pressing arm 41 is extended. Note that the piston-side pressing arm 39 and the anti-piston-side pressing arm 41 in the first embodiment are each composed of a bifurcated arm portion.

  The brake pads 17 are respectively provided at the tip portions of the piston-side pressing arm 39 and the anti-piston-side pressing arm 41 so as to face the outer surface of the disk rotor 37 attached to both side surfaces of the wheel 35. In the first embodiment, a structure in which the lining surface of the brake pad 17 presses the disc rotor 37 to perform a brake operation will be described as an example. Of course, the disc brake 11 may be configured to brake by directly pressing both side surfaces of the wheel 35.

  In the first embodiment, the drive piston 15 is provided on a piston-side pressing arm 39 that is one of a pair of pressing arms in order to drive one of the brake pads 17 toward the side surface of the disk rotor 37.

  The caliper return mechanism 19 is disposed at both ends of the upper guide pin 31 in the first embodiment. The caliper return mechanism 19 elastically urges the base 25 slidably supported with respect to the upper guide pin 31 to the side opposite to the drive piston side (hereinafter referred to as the drive piston side). In addition, the caliper return mechanism 19 according to the present invention may be provided at least at the end portion (right end portion in FIG. 5) on both sides of the upper guide pin 31 opposite to the drive piston side. The caliper return mechanism 19 will be described in detail later. In the first embodiment, an example in which the caliper return mechanism 19 is provided only on the upper guide pin 31 will be described. However, the caliper return mechanism 19 may be provided on both the upper guide pin 31 and the lower guide pin 33. Good.

  A pair of friction rubber rings 21 are fitted inside the upper cylindrical support portion 27 of the support 23. As shown in FIG. 5, washer members 43 are disposed on both axial sides of the friction rubber ring 21. The washer member 43 restricts movement in the direction along the upper guide pin 31 of the friction rubber ring 21.

  A centering bearing 49 is fixed by a step 45 and a snap ring 47 at the center of the inner peripheral surface of the upper cylindrical support 27 surrounding the upper guide pin 31. The aligning bearing 49 supports the upper guide pin 31 in a swingable manner. In the aligning bearing 49, the upper guide pin 31 and the upper cylindrical support portion 27 of the support 23 are not connected to each other because the wheel 35 elastically supported by the carriage frame is displaced (swing) relative to the carriage frame. Even if they are parallel, the sliding surfaces of the brake pad 17 and the disk rotor 37 can be brought into close contact with each other during braking.

  A rubber bush 52 and a sleeve 51 are interposed between the lower guide pin 33 and the lower cylindrical support portion 29 as shown in FIG. The lower guide pin 33 is supported slidably in the axial direction with respect to the lower cylindrical support portion 29 via the rubber bush 52 and the sleeve 51 instead of the aligning bearing 49.

  The pair of friction rubber rings 21 are arranged on both sides in the axial direction of the aligning bearing 49 on the inner peripheral surface of the upper cylindrical support portion 27. The pair of friction rubber rings 21 are fitted to the upper cylindrical support portion 27 and elastically support the upper guide pin 31 in a slidable manner.

  The washer members 43 are arranged on both sides in the axial direction of the friction rubber ring 21 and restrict the axial movement of the friction rubber ring 21. In the first embodiment, as shown in FIG. 5, the friction rubber ring 21 is restricted from moving in one axial direction by a step portion 53 formed on the inner peripheral surface of the upper cylindrical support portion 27. 55 restricts movement in the other axial direction. Accordingly, the pair of friction rubber rings 21 are fixed to the inner peripheral surface of the upper cylindrical support portion 27 in a state where movement in the axial direction is restricted.

The friction rubber ring 21 is selected to have a shape and material having a high elastic range (deformation amount) and a return force (retraction effect). In the first embodiment, the cross-sectional shape of the friction rubber ring 21 including the axis includes a U-shaped cross section having an annular groove 57 that can hold grease on the inner peripheral surface. As shown in FIG. 5, the friction rubber ring 21 is in sliding contact with the outer peripheral surface of the upper guide pin 31 at the tip end of the pair of convex portions on the inner peripheral surface side having the annular groove 57. Solid lubricant such as molybdenum disulfide is provided between the tip of the convex portion of the friction rubber ring 21 and the outer peripheral surface of the upper guide pin 31 in order to set the sliding resistance value between the two to an appropriate value of 5 to 50 kgf. High performance grease mixed with can be retained.
Note that the cross-sectional shape of the friction rubber ring 21 according to the present invention is not limited to the U-shape of the first embodiment, and may be an H-shaped cross section as long as the elastic restoring action can be adjusted. Various shapes can be adopted.

The friction rubber ring 21 is formed in a U-shaped cross section, and has an elastic restoring action when the tip of the convex portion is in sliding contact with the outer peripheral surface of the upper guide pin 31. Thus, for example, when the upper guide pin 31 moves to the drive piston side with respect to the upper cylindrical support portion 27 during brake braking, when the brake is slowly released, the drive piston side is opposite (hereinafter referred to as the anti-drive piston side). It is possible to create a force for returning the upper guide pin 31 to the above.
In addition, the optimum combination of the type and the presence / absence of application of grease is selected from the above-mentioned tones.

The caliper return mechanism 19 according to the first embodiment includes a spring accommodating member 59 that is mounted on a spring accommodating portion 69 provided at both ends of the upper guide pin 31 and a base 25 that is slidable with respect to the upper guide pin 31. A sliding bearing 61 for supporting the spring receiving portion 69, a spring receiving member 63 covering the opening of the spring accommodating portion 69, a compression spring member 65 interposed between the spring receiving member 63 and the bottom portion 83 of the spring accommodating member 59, Have
The spring accommodating member 59 is formed in a bottomed cylindrical shape and has an open end flange 67 on the open end side. The spring accommodating member 59 is attached to a spring accommodating portion 69 that is recessed in the piston side end portion 87 (end portion) and the anti-piston side end portion (end portion) 91 of the upper guide pin 31. In the spring accommodating member 59 attached to the spring accommodating portion 69, the opening end flange 67 is locked to the opening edge of the spring accommodating portion 69, and further insertion into the spring accommodating portion 69 is restricted. In the first embodiment, an example in which a compression coil spring is used as the compression spring member 65 will be described. However, the compression spring member 65 may be an elastic member such as rubber.

  The slide bearing 61 is formed in a cylindrical shape, is fitted into the guide pin support portion 71 of the spring receiving member 63, and is disposed between the upper guide pin 31 and the spring receiving member 63. The slide bearing 61 reduces the sliding resistance of the base portion 25 with respect to the upper guide pin 31.

The spring receiving member 63 is fixed to the base portion 25 so as to cover the opening of the spring accommodating portion 69. As described above, the spring receiving member 63 is slidable with respect to the upper guide pin 31 via the sliding bearing 61. In the first embodiment, the spring receiving member 63 includes a guide pin support portion 71 and a spring support portion 73.
The guide pin support portion 71 is formed in a cylindrical shape, and is fixed to the base portion 25 so as to slidably support the upper guide pin 31 via the slide bearing 61. This fixing is performed by the flange portion 75 of the guide pin support portion 71 that contacts the base portion 25 shown in FIG. 5 and the retaining ring 77 that engages the guide pin support portion 71 on the opposite side of the flange portion 75 across the base portion 25. Is called. Further, between the guide pin support portion 71 and the base portion 25, there is provided a detent mechanism for restricting relative rotation of each other by engaging the notch portion 76 of the collar portion 75 with the locking rib 78 of the base portion 25. It has been.
The spring support portion 73 is fixed to the guide pin support portion 71 with a plurality of bolts 79 so as to cover the outer opening end of the guide pin support portion 71 in a state of being in contact with one end of the compression spring member 65. An O-ring 81 is mounted between the flange portion 75 of the guide pin support portion 71 and the spring support portion 73. The O-ring 81 seals the joint between the guide pin support portion 71 and the spring support portion 73 in a watertight manner, and prevents water and dust from entering the spring accommodating portion 69 and the spring accommodating member 59.

  As shown in FIGS. 4 and 5, the compression spring member 65 is accommodated inside the spring accommodation member 59. One end of the compression spring member 65 accommodated in the spring accommodating member 59 abuts on the bottom 83 of the spring accommodating member 59 and the other end abuts on the spring support 73 of the spring receiving member 63. The compression spring member 65 is interposed between the spring receiving member 63 and the bottom 83 of the spring housing member 59 in a state having a predetermined distance S1 with respect to the opening end flange 67.

  The caliper return mechanism 19 has a stopper portion 85 (see FIG. 5). The stopper portion 85 is formed in a step shape on the inner periphery of the guide pin support portion 71. The stopper portion 85 abuts against the opening end flange 67 of the spring housing member 59 to restrict the movement of the spring housing member 59 in the axial direction relative to the base portion 25 via the guide pin support portion 71 at a predetermined interval S1. In other words, the movement of the spring housing member 59 in the caliper return mechanism 19 is restricted to the predetermined interval S1 by the stopper portion 85 of the guide pin support portion 71 in the spring receiving member 63. Therefore, during braking, movement of the floating caliper 13 toward the drive piston causes a gap between the open end flange 67 of the spring accommodating member 59 and the piston side end 87 of the upper guide pin 31 in the caliper return mechanism 19 on the drive piston side. Is configured such that a gap (interference avoidance gap) S2 shown in FIG. 5 is formed.

Here, in the disc brake 11 having the above-described configuration, the force relationship necessary for the caliper returning force is as follows. That is, F1: sliding resistance of the upper guide pin 31 and the support 23 (aligning bearing 49, friction rubber ring 21), F2: spring force of the compression spring member 65, F3: lower guide pin 33 and support 23 (sleeve 51) F4: When the sliding resistance of the sliding bearing 61 at both ends of the upper guide pin 31 is
F1>F2> (F3 + F4)
It is set so as to have a power relationship of

Next, the operation of the disc brake 11 having the above configuration will be described.
In the floating caliper type disc brake 11 according to the first embodiment, when the drive piston 15 provided at the tip of the piston side pressing arm 39 is driven, one brake pad (left side in FIG. 6) is provided. 17 is pressed against the disk rotor 37. As a result, one brake pad 17 receives a reaction force from the disk rotor 37.
The reaction force received by one brake pad 17 moves the piston-side pressing arm 39 in a direction away from the disk rotor 37 (leftward in FIG. 5).

5, the floating caliper 13 causes the base 25 on the side opposite to the piston side pressing arm 41 to move the spring receiving member 63 on the side opposite to the driving piston (right side in FIG. 5) closer to the disk rotor 37. The base 25 on the piston-side pressing arm 39 side moves the spring receiving member 63 on the drive piston side (left side in FIG. 5) away from the disk rotor 37 (FIG. 5). 5 to the left).
By the movement of the floating caliper 13, the compression spring member 65 accommodated in the spring accommodating member 59 of the spring receiving member 63 on the counter driving piston side is compressed and deformed. As a result, the caliper return force is accumulated in the caliper return mechanism 19 disposed on the counter drive piston side. When the compression spring member 65 is compressed, the spring receiving member 63 moves on the outer periphery of the upper guide pin 31 with sliding resistance reduced in the direction along the axis by the slide bearing 61. Due to the movement of the spring receiving member 63, the spring support portion 73 on the counter drive piston side comes into contact with the open end flange 67 locked to the counter piston side end portion 91 of the upper guide pin 31 as shown in FIG. .

  By the movement of the floating caliper 13, the piston-side pressing arm 39 moves the spring receiving member 63 on the driving piston side in a direction away from the disk rotor 37. Then, the spring housing member 59 on the drive piston side is moved in the direction of being pulled out from the spring housing portion 69 of the upper guide pin 31 by the opening end flange 67 being pressed by the stopper portion 85 of the spring receiving member 63. Thereby, a gap (interference avoidance gap) S2 is formed between the open end flange 67 and the piston side end portion 87 (see FIG. 5) of the upper guide pin 31. Further, the opening end flange 67 remains in contact with the stopper portion 85 due to the urging force of the compression spring member 65, and is disposed in a state of being separated from the spring support portion 73. Therefore, the compression spring member 65 on the drive piston side is disposed. Does not affect the compression deformation of the compression spring member 65 on the counter-drive piston side. The above is the state at the time of brake braking.

  On the other hand, after the brake is slowly opened, the drive piston 15 moves backward. Then, the reaction force in the direction separating from the disk rotor 37 does not act on the piston-side pressing arm 39. Therefore, the compression spring member 65 that has been compressed and deformed on the side opposite to the piston side pressing arm 41 is elastically restored. The resiliently restored compression spring member 65 presses the spring support portion 73 in a direction away from the opening end flange 67. Due to this elastic restoring force, the spring receiving member 63 on the counter-drive piston side moves in a direction away from the disk rotor 37 by the sliding bearing 61 (right direction in FIG. 5). The movement of the spring receiving member 63 on the counter driving piston side moves the counter piston side pressing arm 41 in a direction away from the disk rotor 37. As a result, the floating caliper 13 returns to the state before braking (at the time of initial), and the pair of brake pads 17 are separated from the disc rotor 37 with the same clearance as before braking.

  Note that, at the time of this slow braking, the piston-side pressing arm 39 moves the spring receiving member 63 on the drive piston side in a direction to approach the disk rotor 37. The interference avoidance gap S2 is formed between the opening end flange 67 and the piston side end portion 87 of the upper guide pin 31. For this reason, the elastic force of the compression spring member 65 on the drive piston side does not act as a reaction force (load) against the caliper return force.

  Here, as shown in FIG. 6A, the clearance d between each brake pad 17 and the disc rotor 37 is set to 3 mm before braking (during initial). At the time of brake braking shown in FIG. 6B, the drive piston 15 protrudes 6 mm (piston stroke s = 6 mm), so that the base 25 moves by 3 mm opposite to the protruding direction of the drive piston 15 by the reaction force. At this time, since the upper guide pin 31 does not move and the caliper return mechanism 19 moves, the compression spring member 65 on the counter-drive piston side is compressed and deformed. The restoring force due to the deformation of the compression spring member 65 creates a force (retraction effect) for returning the floating caliper 13. Therefore, after the brake is slowly opened as shown in FIG. 6C, the drive caliper 15 is pulled back by 6 mm, and at the same time, the floating caliper 13 is moved to the opposite piston side by 3 mm, so that the pad clearance is 3 mm. When lining wear occurs, the amount of deviation between the support 23 and the upper guide pin 31 appears after the brake is slowly opened.

Next, the operation of the disc brake 11 having the above-described structure when the wheel is swung will be described.
In the railway vehicle, the wheel 35 swings with respect to the floating caliper 13 fixed to the carriage frame during braking during curve traveling.
In the disc brake 11 having the above-described configuration, even when the wheel is swung, the clearance of both brake pads 17 is maintained at the same value even after the wheel is swung as long as the amount of wheel swing is twice the pad clearance.

The floating caliper type disc brake 11 of the first embodiment can secure both pad clearances of 3 mm up to a wheel swing amount of ± 6 mm.
Table 1 below shows the predicted value of each pad clearance when the wheel swings 6 mm or more to the piston side. Table 1 shows pad clearances when the wheel 35 returns to the position before the movement after the wheel 35 is moved to the drive piston side by the swinging of the wheel 35.
In the operation of the floating caliper 13 at the time of swinging, when the wheel 35 moves to the non-piston side, the clearances (piston side clearance and anti-piston side clearance) in Table 1 are reversed.
When the wheel swing amount exceeds 9 mm, the pressing force of the brake pad 17 against the disc rotor 37 is generated by the compression deformation of the compression spring member 65 on the drive piston side.

  That is, when the wheel 35 swings 6 mm in the direction of the drive piston from the initial time when the wheel 35 is initialized, the displacement amount between the support 23 and the base portion 25 becomes 3 mm, and the displacement amount between the wheel 35 and the base portion 25 becomes 3 mm. . In this case, a return force of 3 mm is generated in the caliper return mechanism 19 on the drive piston side. If the disc brake 11 is released from the swinging, it is possible to secure a pad clearance of 3 mm.

In addition, when the wheel 35 swings 10 mm in the direction of the driving piston from the initial time, the disc brake 11 at the initial time has a displacement amount of 7 mm between the support 23 and the base portion 25 and a deviation amount between the wheel 35 and the base portion 25 becomes 3 mm. .
Therefore, when the wheel return amount is 6 mm, the shift amount between the support 23 and the base portion 25 is 4 mm, and the shift amount between the wheel 35 and the base portion 25 is 0 mm. The pad clearance between the disc rotor 37 and the brake pad 17 is 3 mm.
When the wheel return amount is 9 mm, the amount of deviation between the support 23 and the base portion 25 is 4 mm, and the amount of deviation between the wheel 35 and the base portion 25 is 0 mm. The remaining amount of movement of the wheel 35 is 1 mm, and the disc rotor 37 contacts the brake pad 17. By moving the wheel 35 by the remaining movement amount of 1 mm, the compression spring member 65 on the drive piston side is deflected, and a pressing force of the brake pad 17 against the disc rotor 37 is generated.

7A is a cross-sectional view of the disc brake shown in FIG. 1, and FIG. 7B is a cross-sectional view of a disc brake according to a comparative example.
As shown in FIG. 7A, in the floating caliper type disc brake 11 according to the first embodiment, the base portion 25 of the floating caliper 13 is slidably supported with respect to the upper cylindrical support portion 27 of the support 23. The caliper return mechanism 19 is provided at both ends of the upper guide pin 31 to be performed. The caliper return mechanism 19 on the counter-drive piston side generates a caliper return force between the upper guide pin 31 and the floating caliper 13. Accordingly, the caliper return mechanism 19 on the counter-drive piston side separates the pair of brake pads 17 from the disc rotor 37 with the same clearance as before braking by the caliper return force when the brake is released. The upper guide pin 31 provided with the caliper return mechanism 19 only needs to be replaced with the upper guide pin 95 in the current floating caliper 13A shown in FIG. 7B, and any addition to the existing floating caliper 13A is required. An improvement for realizing a countermeasure against pad dragging with respect to the floating caliper type disc brake 93 is possible without any work.

  In the floating caliper type disc brake 11 of the present embodiment, the opening end flange 67 is formed at the opening edge of the spring accommodating portion 69 in the spring accommodating portion 69 formed to be opened at the end portion of the upper guide pin 31. The locked spring accommodating member 59 (see FIG. 5) is inserted. The spring accommodating member 59 further accommodates a compression spring member 65. The spring receiving member 63 is attached to the base 25 of the floating caliper 13 so as to cover the opening of the spring accommodating portion 69 in a state where it abuts against the other end of the compression spring member 65 whose one end abuts against the bottom 83 of the spring accommodating member 59. Fixed. Therefore, when the drive piston 15 is driven and the floating caliper 13 is moved to the drive piston side with respect to the upper guide pin 31, the compression spring member 65 in the caliper return mechanism 19 on the counter drive piston side is compressed. The caliper return mechanism 19 on the counter-drive piston side can obtain a caliper return force by the elastic restoring force of the compressed compression spring member 65.

  In the floating caliper type disc brake 11 of the present embodiment, the spring receiving member 63 fixed to the base 25 of the floating caliper 13 slides on the outer periphery of the upper guide pin 31 via the sliding bearing 61 (see FIG. 5). It is supported freely. Accordingly, the sliding resistance of the base portion 25 of the floating caliper 13 is reduced by the sliding bearing 61, and the base portion 25 can be moved relative to the upper guide pin 31 with less force.

  In the floating caliper type disc brake 11 of the present embodiment, the spring receiving member 63 fixed to the base portion 25 of the floating caliper 13 includes a guide pin support portion 71 provided with the sliding bearing 61 and fixed to the base portion 25, and It comprises a spring support portion 73 that is in contact with one end of the compression spring member 65 and fixed to the guide pin support portion 71 (see FIG. 5). Therefore, the spring support 73 is removed while the guide pin support 71 of the spring receiving member 63 fixed to the base 25 of the floating caliper 13 is slidably supported on the outer periphery of the upper guide pin 31, and the compression spring member is removed. 65 can be attached and detached. Thereby, the return force and return amount of the floating caliper 13 can be adjusted very easily by exchanging with the spring support portion 73 and the compression spring member 65 having different specifications (predetermined interval S1, spring constant, etc.).

Further, in the floating caliper type disc brake 11 of the present embodiment, the caliper return mechanism 19 is disposed at both ends of the upper guide pin 31, so that it floats to the counter-drive piston side required when the wheel 35 swings, for example. It is possible to create a force for returning the base 25 of the caliper 13.
At the time of braking, when the drive piston 15 is driven and the floating caliper 13 is moved to the drive piston side with respect to the upper guide pin 31, the caliper return provided at the end of the upper guide pin 31 on the counter drive piston side is returned. The compression spring member 65 in the mechanism 19 is compressed to generate a caliper returning force. At this time, the movement of the spring accommodating member 59 in the caliper return mechanism 19 arranged at the end of the upper guide pin 31 on the drive piston side is regulated at a predetermined interval S1 by the stopper portion 85 of the spring receiving member 63. Due to the movement of the floating caliper 13 to the drive piston side, a gap (interference) is formed between the open end flange 67 of the spring accommodating member 59 and the piston side end portion 87 of the upper guide pin 31 in the caliper return mechanism 19 on the drive piston side. An avoidance gap (S2) is formed. Therefore, the elastic force of the compression spring member 65 in the caliper return mechanism 19 on the drive piston side does not interfere with the caliper return force of the compression spring member 65 in the caliper return mechanism 19 on the counter drive piston side, and the reaction force against the caliper return force ( It does not act as a load).

  In the railway vehicle disc brake according to the first embodiment, by providing the configuration of the disc brake 11 described above, the brake pads 17 are pressed against the disc rotors 37 attached to both side surfaces of the railcar wheel 35 for braking. In doing so, the pad clearance between the brake pad 17 and the disc rotor 37 can be maintained constant. As a result, it is possible to prevent uneven wear and drag of the brake pad 17 and to suppress an increase in the starting torque of the vehicle.

Next, a floating caliper type disc brake according to a second embodiment of the present invention will be described.
Note that in the floating caliper type disc brake according to the second embodiment, the same members as those in the floating caliper type disc brake according to the first embodiment are denoted by the same reference numerals, and redundant description is omitted.
As shown in FIGS. 8 and 9, in the floating caliper type disc brake 97 according to the second embodiment, the caliper return mechanisms 103 are arranged at both ends of the upper guide pin 99. The upper guide pin 99 is formed as a hollow pipe.

  The caliper return mechanism 103 according to the second embodiment includes a spring housing member 107 mounted on a spring housing portion 69 provided at both ends of the hollow upper guide pin 99 and a base portion 25 that slides against the upper guide pin 99. A sliding bearing 61 for movably supporting, a spring receiving member 105 covering the opening of the upper guide pin 99 serving as the spring accommodating portion 69, and interposed between the spring receiving member 105 and the bottom portion 108 of the spring accommodating member 107. A compression spring member 65.

  The slide bearing 61 is formed in a cylindrical shape, is fitted into the guide pin support portion 109 of the spring receiving member 105, and is disposed between the upper guide pin 99 and the spring receiving member 105. Therefore, spring receiving members 105 are slidably inserted on the outer peripheral sides of both ends of the upper guide pin 99. The spring receiving member 105 has a cylindrical guide pin support portion 109 and a cap nut-like spring support portion 111. The inner periphery of the guide pin support portion 109 is extrapolated to the outer periphery of the slide bearing 61. A retaining projection 113 is formed at the end of the guide pin support 109 on the side of the alignment bearing 49. The retaining protrusion 113 restricts the guide pin support portion 109 from coming out from the base portion 25 outward.

  A male screw portion 115 is formed on the outer periphery of the guide pin support portion 109 penetrating the base portion 25. A female screw portion 117 of the spring support portion 111 is screwed into the male screw portion 115. That is, the spring support part 111 clamps the base part 25 with the retaining protrusion 113 by screwing into the male thread part 115 of the guide pin support part 109 penetrating the base part 25 outward. Thereby, the spring receiving member 105 is fixed integrally with the base portion 25. The spring receiving member 105 fixed integrally with the base portion 25 is slidable on the upper guide pin 99 via the sliding bearing 61. That is, the base 25 is slidably supported with respect to the upper guide pin 99 via the spring receiving member 105.

  A spring accommodating member 107 formed in a bottomed cylindrical shape is inserted into an inner hollow portion of the upper guide pin 99 serving as the spring accommodating portion 69. The spring housing member 107 is provided with an open end flange 67 on the open end side. The spring accommodating member 107 attached to the spring accommodating portion 69 has the opening end flange 67 locked to the opening edge of the upper guide pin 99, and further insertion into the spring accommodating portion 69 is restricted. In addition, the outer peripheral end of the open end flange 67 can be brought into contact with the end surface 110 of the guide pin support portion 109 on the spring support portion 111 side.

In the caliper return mechanism 103 according to the second embodiment, an O-ring mounting portion 119 having a reduced outer diameter is formed at the end of the guide pin support portion 109 on the spring support portion 111 side. An O-ring 81 is attached to the O-ring attachment portion 119.
Further, the end surface 110 of the guide pin support portion 109 closer to the central axis than the O-ring mounting portion 119 has the same function as the stopper portion 85 of the first embodiment.

Next, the operation of the disc brake 97 having the above configuration will be described.
In the floating caliper type disc brake 97 according to the second embodiment, when the drive piston 15 (refer to the partially broken portion in FIG. 6A) provided at the tip of the piston-side pressing arm 39 is driven. One brake pad 17 is pressed against the disk rotor 37 and receives a reaction force from the disk rotor 37.
The reaction force received by one brake pad 17 moves the piston-side pressing arm 39 in a direction away from the disc rotor 37 (rightward in FIG. 9).

By this movement, the floating caliper 13 causes the base 25 on the side opposite to the piston side pressing arm 41 to move the spring receiving member 105 on the side opposite to the driving piston (left side in FIG. 9) closer to the disk rotor 37 (in FIG. The base portion 25 on the piston side pressing arm 39 side is moved in the direction (right direction in FIG. 9) so that the spring receiving member 105 on the drive piston side (right side in FIG. 9) is separated from the disk rotor 37. Move.
By the movement of the floating caliper 13, the compression spring member 65 accommodated in the spring accommodating member 107 of the spring receiving member 105 on the counter driving piston side is compressed and deformed. As a result, the caliper return force is accumulated in the caliper return mechanism 103 disposed on the counter drive piston side. When the compression spring member 65 is compressed, the spring bearing member 105 moves on the outer periphery of the upper guide pin 99 with the sliding resistance reduced in the direction along the axis by the slide bearing 61. Due to the movement of the spring receiving member 105, the spring support portion 111 on the counter drive piston side comes into contact with the open end flange 67 that is locked to the counter piston side end portion 91 of the upper guide pin 99.

  By the movement of the floating caliper 13, the piston-side pressing arm 39 moves the spring receiving member 105 on the driving piston side in a direction away from the disk rotor 37. Then, the spring accommodating member 107 on the drive piston side is moved in a direction in which the opening end flange 67 is pressed against the end face 110 of the spring receiving member 105 and is pulled out from the spring accommodating portion 69 of the upper guide pin 99. Thereby, a gap (interference avoidance gap) is formed between the open end flange 67 and the piston side end portion 87 of the upper guide pin 99. Further, the opening end flange 67 remains in contact with the end face 110 by the urging force of the compression spring member 65 and is arranged in a state of being separated from the spring support portion 111, so that the compression spring member 65 on the drive piston side is arranged. The spring force does not affect the compressive deformation of the compression spring member 65 on the counter drive piston side. The above is the state at the time of brake braking.

  On the other hand, after the brake is slowly opened, the drive piston 15 moves backward. Then, the reaction force in the direction separating from the disk rotor 37 does not act on the piston-side pressing arm 39. Therefore, the compression spring member 65 that has been compressed and deformed on the side opposite to the piston side pressing arm 41 is elastically restored. The resiliently restored compression spring member 65 presses the spring support 111 in a direction away from the opening end flange 67 (left direction in FIG. 9). Due to this elastic restoring force, the spring receiving member 105 on the counter driving piston side moves in a direction away from the disk rotor 37 by the sliding bearing 61. The movement of the spring receiving member 105 on the anti-piston side moves the anti-piston side pressing arm 41 in a direction away from the disk rotor 37. As a result, the floating caliper 13 returns to the state before braking (at the time of initial), and the pair of brake pads 17 are separated from the disc rotor 37 with the same clearance as before braking.

According to the floating caliper type disc brake 97 according to the second embodiment, since a hollow pipe is used for the upper guide pin 99, the weight can be reduced.
Further, since the spring support portion 111 of the spring receiving member 105 has a cap nut shape, the caliper return mechanism 103 can be provided with high dust resistance and waterproofness. Further, the spring support 111 is removed while the guide pin support 109 of the spring receiving member 105 fixed to the base 25 of the floating caliper 13 is slidably supported on the outer periphery of the upper guide pin 99, and the compression spring member is removed. 65 can be attached and detached. Thereby, the return force and return amount of the floating caliper 13 can be adjusted very easily by exchanging with the spring support 111 or the compression spring member 65 having different specifications (predetermined interval S1, spring constant, etc.).

Next, a floating caliper type disc brake according to a third embodiment of the present invention will be described.
In addition, in the floating caliper type disc brake according to the third embodiment, the same members as those in the floating caliper type disc brake according to the first embodiment are denoted by the same reference numerals, and redundant description is omitted.
As shown in FIGS. 10 to 12, in the caliper type disc brake 121 according to the third embodiment, caliper return mechanisms 123 and 124 are arranged at both ends of the upper guide pin 151, respectively. The upper guide pin 151 is formed as a hollow pipe.

  The caliper returning mechanism 123 is configured to slide the base portion 25 against the spring accommodating member 127 attached to the spring accommodating portion 69 provided in the piston side end opening (end portion) 187 of the hollow upper guide pin 151 and the upper guide pin 151. A sliding bearing 61 for supporting the movement, a spring receiving member 135 covering the opening of the upper guide pin 151 serving as the spring accommodating portion 69, and an intermediate between the spring receiving member 135 and the bottom portion 128 of the spring accommodating member 127. A compression spring member 65.

  On the other hand, the caliper returning mechanism 124 has a spring housing member 127 that is mounted on a spring housing portion 69 provided at the end opening (end portion) 191 on the side opposite to the piston of the hollow upper guide pin 151 and a base portion with respect to the upper guide pin 151. Between the spring bearing member 136 that covers the opening of the upper guide pin 151 that serves as the spring accommodating portion 69, and the bottom portion 128 of the spring accommodating member 127. A compression spring member 65 interposed therebetween.

  The slide bearing 61 is formed in a cylindrical shape, is fitted into the guide pin support portion 131 of the spring receiving members 135 and 136, and is disposed between the upper guide pin 151 and the spring receiving members 135 and 136. Therefore, spring receiving members 135 and 136 are slidably inserted on the outer peripheral sides of both ends of the upper guide pin 151.

The spring receiving member 135 has a cylindrical guide pin support portion 131 and an annular spring support portion 133. Further, the spring receiving member 136 includes a cylindrical guide pin support portion 131 and an annular spring support portion 134.
The guide pin support portion 131 is formed in a cylindrical shape, and is fixed to the base portion 25 so as to slidably support the upper guide pin 151 via the slide bearing 61. This fixing is performed by a flange portion 175 of the guide pin support portion 131 that contacts the base portion 25 and a retaining ring 77 that engages with the guide pin support portion 131 on the opposite side of the flange portion 175 across the base portion 25. Further, between the guide pin support portion 131 and the base portion 25, there is provided a detent mechanism that restricts the relative rotation of the flange portion 175 by engaging the notch portion 176 with the locking rib 78 of the base portion 25. It has been.
Further, in the caliper return mechanisms 123 and 124, a stopper portion 85 is formed in a step shape on the inner periphery of the guide pin support portion 131.

  The spring support portion 133 and the spring support portion 134 are respectively in contact with the opening 129 in the bottom portion 128 of the spring accommodating member 127 so as to cover the outer opening end of the guide pin support portion 131 in a state of being in contact with one end of the compression spring member 65. It is fixed to the guide pin support part 131 by a bolt shaft 141 penetrating through the hollow upper guide pin 151 in the central axis direction and a nut 145 screwed to the tip of the bolt shaft 141. Thereby, the spring receiving members 135 and 136 are fixed integrally with the base portion 25. The spring receiving members 135 and 136 fixed integrally with the base portion 25 are slidable on the upper guide pin 151 via the sliding bearing 61. That is, the base 25 is slidably supported with respect to the upper guide pin 151 via the spring receiving members 135 and 136.

  In the caliper return mechanism 123, an O-ring 155 is mounted between the washer 147 tightened by the nut 145 and the spring support portion 133. In the caliper return mechanism 124, the bolt head 143 of the bolt shaft 141 and the spring support portion 134 are connected. An O-ring 153 is mounted between them. The O-rings 153 and 155 seal the through holes of the spring support portions 133 and 134 through which the bolt shaft 141 passes, respectively, to prevent water and dust from entering the spring accommodating portion 69 and the spring accommodating member 127.

  Further, between the guide pin support part 131 and the spring support part 134, the notch part 138 of the spring support part 134 engages with the locking projection 177 of the flange part 175 to restrict relative rotation of each other. A stop mechanism is provided. Further, between the spring support part 134 and the bolt shaft 141, a bolt head 143 having a two-sided width is fitted into the fitting recess 139 of the spring support part 134 to restrict mutual relative rotation. Is provided. Therefore, when the nut 145 is screwed onto the tip of the bolt shaft 141, the bolt shaft 141 does not idle, and the assembly workability is improved.

Next, the operation of the disc brake 121 having the above configuration will be described.
In the floating caliper type disc brake 121 according to the third embodiment, when the drive piston 15 provided at the tip of the piston side pressing arm 39 is driven, one brake pad 17 is pressed by the disc rotor 37. The disk rotor 37 receives a reaction force.
The reaction force received by one brake pad 17 moves the piston-side pressing arm 39 in a direction away from the disc rotor 37 (rightward in FIG. 12).

With this movement, the floating caliper 13 causes the base 25 on the side opposite to the piston side pressing arm 41 to move the spring receiving member 136 on the side opposite to the driving piston (left side in FIG. 12) closer to the disk rotor 37 (in FIG. The base 25 on the piston side pressing arm 39 side is moved in the direction (right direction in FIG. 12) so that the spring receiving member 135 on the drive piston side (right side in FIG. 12) is separated from the disk rotor 37. Move.
By the movement of the floating caliper 13, the compression spring member 65 accommodated in the spring accommodating member 127 of the spring receiving member 136 on the counter-drive piston side is compressed and deformed. As a result, the caliper return force is accumulated in the caliper return mechanism 124 arranged on the counter drive piston side. When the compression spring member 65 is compressed, the spring receiving member 136 moves with the sliding resistance reduced in the direction along the axis along the outer periphery of the upper guide pin 99 by the sliding bearing 61. Due to the movement of the spring receiving member 136, the spring support portion 111 on the anti-drive piston side comes into contact with the open end flange 67 that is locked to the anti-piston side end portion 191 of the upper guide pin 99.

  By the movement of the floating caliper 13, the piston-side pressing arm 39 moves the spring receiving member 135 on the driving piston side in a direction away from the disk rotor 37. Then, the spring accommodating member 127 on the drive piston side is moved in a direction in which the opening end flange 67 is pressed against the stopper portion 85 of the spring receiving member 135 and pulled out from the spring accommodating portion 69 of the upper guide pin 151. Thereby, a gap (interference avoidance gap) is formed between the open end flange 67 and the piston side end portion 187 of the upper guide pin 151. Further, the opening end flange 67 remains in contact with the stopper portion 85 due to the urging force of the compression spring member 65, and is disposed in a state of being separated from the spring support portion 133. Therefore, the compression spring member 65 on the drive piston side is arranged. Does not affect the compression deformation of the compression spring member 65 on the counter-drive piston side. The above is the state at the time of brake braking.

  On the other hand, after the brake is slowly opened, the drive piston 15 moves backward. Then, the reaction force in the direction separating from the disk rotor 37 does not act on the piston-side pressing arm 39. Therefore, the compression spring member 65 that has been compressed and deformed on the side opposite to the piston side pressing arm 41 is elastically restored. The resiliently restored compression spring member 65 presses the spring support portion 134 in a direction away from the opening end flange 67 (left direction in FIG. 9). Due to this elastic restoring force, the spring receiving member 136 on the counter driving piston side moves in a direction away from the disk rotor 37 by the sliding bearing 61. The movement of the spring receiving member 136 on the anti-piston side causes the anti-piston side pressing arm 41 to move away from the disk rotor 37. As a result, the floating caliper 13 returns to the state before braking (at the time of initial), and the pair of brake pads 17 are separated from the disc rotor 37 with the same clearance as before braking.

According to the floating caliper type disc brake 121 according to the third embodiment, since a hollow pipe is used for the upper guide pin 151, the weight can be reduced.
The spring support portion 133 and the spring support portion 134 are screwed into the bolt shaft 141 penetrating the opening 129 and the hollow upper guide pin 151 in the bottom portion 128 of the spring housing member 127 in the central axis direction, and the tip of the bolt shaft 141. The nuts 145 are fixed to the guide pin support portions 131, respectively. Therefore, the spring receiving members 135 and 136 according to the third embodiment are compared with the spring receiving member 63 of the first embodiment in which the spring support portion 73 is fixed to the guide pin support portion 71 by a plurality of bolts 79. The part dotted line can be reduced.

  Further, the spring support portions 133 and 134 are removed while the guide pin support portions 131 of the spring receiving members 135 and 136 fixed to the base portion 25 of the floating caliper 13 are slidably supported on the outer periphery of the upper guide pin 151. Thus, the compression spring member 65 can be attached and detached. As a result, the return force and return amount of the floating caliper 13 can be adjusted very easily by replacing the spring support parts 133 and 134 and the compression spring member 65 with different specifications (predetermined interval S1, spring constant, etc.). Become.

  Therefore, according to the floating caliper type disc brakes 11, 97, 121 and the railcar disc brake according to the first to third embodiments, the caliper return force can be easily set, and a desired caliper return operation can be performed. Can be stably exhibited, and the brake pad 17 can be reliably prevented from being dragged.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

DESCRIPTION OF SYMBOLS 11 ... Disc brake 13 ... Floating caliper 15 ... Drive piston 17 ... Brake pad 19 ... Caliper return mechanism 23 ... Support 25 ... Base 27 ... Upper cylindrical support part (cylindrical support part)
29 ... Lower cylindrical support part (cylindrical support part)
31 ... Upper guide pin (guide pin)
37: Disc rotor 39 ... Piston side pressing arm (pressing arm)
41 ... Anti-piston side pressing arm (pressing arm)
59 ... Spring housing member 61 ... Sliding bearing 63 ... Spring receiving member 65 ... Compression spring member 67 ... Open end flange 69 ... Spring housing portion 71 ... Guide pin support portion 73 ... Spring support portion 81 ... O-ring 83 ... Bottom portion 85 ... Stopper Part 87: Piston side end (end)
91 ... The end on the side opposite to the piston (end)
97 ... Disc brake 103 ... Caliper return mechanism 105 ... Spring receiving member 107 ... Spring housing member 109 ... Guide pin support 111 ... Spring support

Claims (10)

A floating caliper having a base slidably supported via a guide pin with respect to a cylindrical support portion of the support, and a pair of pressing arms extending from the base to a position sandwiching the disk rotor from both axial sides When,
A pair of brake pads respectively provided at the tip portions of the pair of pressing arms so as to face the side surfaces of the disk rotor;
A drive piston provided on one of the pair of pressing arms to drive one of the brake pads toward the side of the disk rotor;
The base portion, which is disposed at least on the opposite side of the drive piston side at both ends of the guide pin and is slidably supported with respect to the guide pin, is elastically biased to the side opposite to the drive piston side. And a caliper return mechanism for the disc brake. The caliper return mechanism is
A bottomed cylindrical spring accommodating member that is mounted on a spring accommodating portion provided at an end portion of the guide pin and whose opening end flange is locked to an opening edge of the spring accommodating portion;
A spring receiving member that covers the opening of the spring accommodating portion and is fixed to the base portion;
The compression spring member interposed between the spring receiving member in a state having a predetermined interval with respect to the opening end flange and the bottom portion of the spring accommodating member. Disc brake. The spring receiving member is
The disc brake according to claim 2, further comprising a slide bearing for slidably supporting the base portion with respect to the guide pin. The spring receiving member is
A cylindrical guide pin support portion fixed to the base portion so that the base portion is slidably supported with respect to the guide pin via the sliding bearing;
The spring support part fixed to the said guide pin support part so that it may contact | abut one end of the said compression spring member, and the outer opening end of the said guide pin support part may be provided. Disc brake.   The disk brake according to claim 4, wherein an O-ring is interposed between the guide pin support portion and the spring support portion. The spring support portion in the caliper return mechanism disposed at both ends of the guide pin is:
The bolt is fixed to the base by a bolt shaft that penetrates the bottom of the spring housing member and the hollow guide pin in a central axis direction, and a nut that is screwed to the tip of the bolt shaft. 5. The disc brake according to 5.   The disc brake according to claim 6, wherein an O-ring is interposed between the spring support portion and the bolt shaft, and between the spring support portion and the nut.   An anti-rotation mechanism is provided between the guide pin support portion and the spring support portion and between the spring support portion and the bolt shaft to restrict relative rotation of each other. Item 8. The disc brake according to item 7. The caliper return mechanism disposed at the end of the guide pin on the drive piston side is:
The disc brake according to any one of claims 2 to 8, wherein the spring receiving member has a stopper portion for restricting movement of the spring accommodating member in the axial direction with respect to the base portion to a predetermined interval.   A disc brake for railway vehicles, comprising the disc brake according to any one of claims 1 to 9.

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