JP2012072843A - Floating type disc brake - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disc brake configured such that the cost can be easily reduced, uneven wear in the linings 15c, 15d of both inner and outer pads 4a, 5a can be suppressed, generation of abnormal sounds or vibration can be prevented regardless of the advancing direction of a vehicle upon braking, and both pads 4a, 5a can be easily replaced.SOLUTION: An outer pad 5a is supported on an inner side face of a caliper claw 10a in a brake torque transmittable manner. A main pin 17, which is disposed radially inside an outer circumference edge of a rotor 6 and protrudes from the support 1a into only the inner side, is inserted into a guide hole 30 provided in the turn-out side edge of a caliper 3a so as to be displaced in an axial direction and relatively rotated around the center axis. A turn-in side edge of the caliper 3c is engaged with part of a sub pin 18 provided across the rotor 6 so as to be displaced in the axial direction and support part of the brake torque during braking.

Description

  The present invention relates to an improvement of a floating disc brake used for braking an automobile. Specifically, the support can be easily machined to reduce costs, and the inner and outer pad linings can be prevented from being unevenly worn. Regardless of the situation, it is possible to prevent the generation of noise and vibration caused by the collision between the edges of the pressure plates of the pads and the mating surface, and to make it possible to easily replace the pads if necessary. Is intended.

  Conventionally, as a disc brake for braking a vehicle such as an automobile, a caliper is supported by a support so as to be capable of axial displacement via a pair of guide pins, and only one side of the caliper with respect to the rotor is supported. A floating type provided with a cylinder and a piston has been widely known and widely used in practice as described in Patent Documents 1 to 6, for example. 22 to 23 show a structure described in Patent Document 1 as an example of a conventionally known floating disc brake.

  In the case of an example of this conventional structure, a support 1, a pair of guide pins 2, a caliper 3, an inner pad 4, and an outer pad 5 are provided. Of these, the support 1 is substantially U-shaped when viewed from the axial direction, and the circumferential direction (the axial direction, radial direction, and circumferential direction are the axial direction, radial direction, (Refer to the circumferential direction. The same applies to the entire specification and claims), and a rotor 6 (which is an embodiment of the present invention) is provided with a recessed portion 7 opened radially outwardly and rotating together with a wheel. 2 to 6, 6, 9, 10, 12, 13, 20, and 21 shown, the inner side (inner side) refers to the center in the width direction of the vehicle body when assembled to the vehicle body. The same applies to the entire document and claims). The guide pins 2 are coupled and fixed in parallel with each other in a state in which the base end portions thereof are protruded from the support 1 to the inner side by bolts 8 and 8 at both ends in the circumferential direction of the support 1, respectively. ing.

  Further, the caliper 3 is provided with guide tube portions 9a and 9b at both ends in the circumferential direction, and the inner diameter side spaces of both the guide tube portions 9a and 9b serve as first and second guide holes, respectively. The guide pins 2 are inserted into the guide holes 2 so as to be capable of axial displacement, and the caliper 3 is supported to the support 1 so as to be capable of axial displacement. The caliper 3 is radially inward at the outer side (the outer side means the both ends in the width direction of the vehicle body in the assembled state to the vehicle body; the same applies to the entire specification and claims). A caliper claw 10 protruding to the surface is provided. In addition, a cylinder hole is provided in the cylinder portion 11 constituting the inner side portion of the caliper 3 so as to open toward the inner side surface of the caliper claw 10 through the recessed portion 7 of the support 1. The piston is oil-tightly fitted. The piston is displaced in the axial direction by supplying and discharging the pressure oil into the cylinder hole through the oil supply port 12.

  The inner and outer pads 4 and 5 are supported by a pair of anchor blocks 13 and 13 constituting the support 1 so as to be capable of axial displacement. Both the pads 4 and 5 are formed by attaching linings 15a and 15b to the opposing surfaces of the pressure plates 14a and 14b, respectively. Both the pads 4 and 5 are capable of axial displacement at both end portions of the pressure plates 14a and 14b in the circumferential direction with respect to the two anchor blocks 13 and 13, and the both sides of the rotor 6 in the axial direction. The brake torque applied based on the friction with the linings 15a and 15b is engaged so as to be able to be supported. In such a floating type disc brake, the base plate portion 16 of the support 1 is supported and fixed to a vehicle body (a component of a suspension device such as a knuckle), and both the pads 4 and 5 are arranged on both sides in the axial direction of the rotor 6. Assemble to the state.

  When braking is performed by the floating disc brake having the structure shown in FIGS. 22 to 23, pressure oil is sent into the cylinder hole through the oil supply port 12. Then, the piston is pushed out to the outer side, and the lining 15 a of the inner pad 4 is pressed against the inner side surface of the rotor 6. Then, as a reaction of the pressing, the caliper 3 is displaced toward the inner side, the caliper claw 10 provided on the caliper 3 presses the outer pad 5 toward the inner side, and the lining 15b of the outer pad 5 is moved to the rotor 6. Press against the outer side of the. As a result, the rotor 6 is clamped from both sides in the axial direction, and braking is performed. Brake torque acts on the pads 4 and 5 during braking based on friction between the linings 15 a and 15 b and both side surfaces of the rotor 6. The brake torque is supported by the two anchor blocks 13 and 13. At this time, the anchor block 13 on the delivery side (front side in the rotational direction) of the rotor 6 functions as a push anchor that supports the brake torque as a compression force. On the other hand, the anchor block 13 on the turn-in side (rotation direction rear side) of the rotor 6 functions as a pull anchor that supports the brake torque as a pulling force. If the hydraulic pressure in the cylinder hole is eliminated, the linings 15a and 15b of the pads 4 and 5 are separated from both side surfaces of the rotor 6 by the elasticity of a return spring (not shown), and braking is released.

  In the case of the conventional structure as shown in FIGS. 22 to 23 described above, both the anchor blocks 13 and 13 are provided in a state of straddling the outer peripheral edge of the rotor 6 in the axial direction. The outer pads 4 and 5 are supported. In the case of the conventional structure shown in the figure, the support 1 is divided into a base plate portion 16 and the two anchor blocks 13 and 13, and the base plate portion 16 is fixedly coupled to the vehicle body with bolts or the like. Yes. However, a structure in which both the inner and outer pads are supported by an integrated support having a shape straddling the outer peripheral edge of the rotor is also widely known. In any case, in order to perform braking and releasing smoothly, the support 1 (in the illustrated example, the anchor blocks 13 and 13 thereof) and the both pads 4 and 5 It is necessary to keep the sliding resistance of the engaging portion with the pressure plates 14a and 14b low. For this purpose, a portion of the support 1 that engages with the pressure plates 14a and 14b needs to be finished with high precision by machining. For this reason, it is inevitable that the manufacturing cost of the floating disc brake including the support 1 increases.

  Further, when the linings 15a and 15b are worn due to repeated braking, it is necessary to replace both the pads 4 and 5 with new pads. Thus, it is necessary to attach and detach the inner and outer pads 4 and 5. In the case of the conventional structure shown in FIGS. 22 to 23, when the pads 4 and 5 are attached to and detached from the support 1, the caliper 3 is retracted radially outward with respect to the support 1. It is necessary to slide both pads 4 and 5 in the axial direction. In order to perform such work while the support 1 is mounted in the vehicle body, care is required to prevent the pads 4 and 5 from being dropped, and skill and labor are required.

  On the other hand, Patent Documents 2 and 3 describe structures in which the outer pad is supported on the inner side surface of the caliper pawl so as to be able to support brake torque. Further, Patent Documents 4 and 5 describe a structure in which the caliper pawl is omitted and the pressure plate of the outer pad is coupled and fixed to the outer side end portion of the caliper with a bolt. In the case of the structure described in each of these Patent Documents 2 to 5, the outer pad can be attached to and detached from the support together with the caliper, so there is room for easy pad replacement work. However, in the case of a structure in which the outer pad is supported only on the outer side end portion of the caliper and not supported with respect to the support as in the structures described in the above Patent Documents 2 to 5, brake torque applied to the outer pad during braking is applied. Therefore, the caliper posture change tends to be large. Specifically, the outer side end portion of the caliper is strongly pulled toward the rotation side of the rotor, and the caliper tends to rotate around the virtual central axis existing in the radial direction of the rotor. As a result, the distance between the pair of pressure plates constituting the inner and outer pads and the side surface in the axial direction of the rotor tends to be different between the inflow side and the outflow side of the rotor. Wear becomes uneven in the circumferential direction, and uneven wear easily proceeds. Specifically, the outer pad lining is significantly worn on the outlet side, and the inner pad lining is on the inlet side.

JP 2009-133356 A JP-A-8-240232 JP-A-10-26156 JP 2010-121721 A JP 2010-127326 A Japanese Patent No. 3945546

  In view of the circumstances as described above, the present invention has been invented to realize a structure in which support processing can be easily performed, cost can be easily reduced, and uneven lining of both inner and outer pads can be suppressed. Is. In addition, if necessary, it is possible to prevent the generation of noise and vibration caused by the collision between the edges of the pressure plates of the two pads and the mating surface regardless of the traveling direction of the vehicle during braking. Thus, it is possible to realize a structure in which both the pads can be easily exchanged.

The floating disc brake of the present invention includes a support, a pair of guide pins, a caliper, an inner pad, and an outer pad, as in the above-described conventionally known floating disc brake.
Of these, the support is provided with a recessed portion having a radially outward opening at an intermediate portion in the circumferential direction, and is fixed to the vehicle body on the inner side of the rotor that rotates together with the wheel.
The guide pins are fixed to both ends of the support in the circumferential direction in a state where the guide pins are arranged in the axial direction.
The caliper is supported by the both guide pins so as to be capable of axial displacement with respect to the support.
The inner pad is supported by a part of the support so as to be capable of axial displacement.
The outer pad is provided in a state of facing the inner pad via the rotor.
The caliper is provided with a caliper claw projecting radially inward at the outer side end portion, and provided in an inner side portion in a state of opening toward the inner side surface of the caliper claw through the recessed portion of the support. A piston is fitted into the cylinder hole formed so as to be capable of axial displacement.

In particular, in the floating type disc brake of the present invention, the outer pad is supported on the inner side surface of the caliper pawl in a state in which relative displacement with respect to the caliper pawl is prevented in each direction, and is applied to the outer pad during braking. The applied brake torque can be transmitted to the caliper pawl.
The main pin, which is one of the guide pins provided on one end side in the circumferential direction, is provided so as to protrude only from the support toward the inner side, and one end in the circumferential direction of the caliper. It is inserted into a guide hole provided in the section so as to be capable of axial displacement and relative rotation about its own central axis.
Similarly, the sub-pin, which is the other guide pin provided on the other end side in the circumferential direction, straddles this rotor on the outer side in the radial direction from the main pin and on the outer side in the radial direction from the outer peripheral edge of the rotor. It is provided in the state.
The other end of the caliper in the circumferential direction of the sub-pin can be displaced in the axial direction directly or via the pressure plate constituting the outer pad, and the brake torque applied to the outer pad during braking can be reduced. A part is engaged with the sub pin so as to be supported.

Preferably, when the floating disc brake of the present invention as described above is implemented, the central axis of the main pin is set radially inward from the outer peripheral edge of the rotor as in the invention described in claim 2. To do. Further, one end edge in the circumferential direction of the inner pressure plate constituting the inner pad, a radially inner side portion of an inner edge of the circumferential end of the recessed portion provided in the support, a circumferential direction of the inner pressure plate, etc. The end portions are engaged with the sub-pins so that the brake torque can be supported.
Further, when the floating type disc brake of the present invention is implemented, preferably, as in the invention described in claim 3, in the forward traveling state of the vehicle, the circumferential one end side is set as the rotation side of the rotor, and the circumferential Similarly, the other end side in the direction is set as the turn-in side.
Or when implementing the floating type disc brake of this invention, Preferably, the 2nd guide hole is provided in the circumferential direction other end part like the invention described in Claim 4. Further, the sub-pin is projected not only on the outer side of the support but also on the inner side. A portion of the sub pin that protrudes toward the inner side is fitted into the second guide hole so as to allow relative displacement in the axial direction.

  Further, when the floating disc brake of the present invention as described above is implemented, for example, as in the invention described in claim 5, an outer diameter side sleeve is provided in a guide hole provided at one circumferential end of the caliper. Secure with internal fit. Further, the main pin is inserted into the cylindrical inner sleeve on the outer side end surface against the inner side surface of the support in the circumferential direction, and the inner diameter side sleeve is inserted from the inner side to end one end in the circumferential direction of the support. And a rod screwed into a screw hole provided in the portion. Furthermore, the outer diameter is provided by a pair of boots, each of which is made of an elastic material, with both ends locked between outer peripheral surfaces of both ends of the outer diameter side sleeve and outer peripheral surfaces of both ends of the inner diameter side sleeve. The sliding portion between the inner peripheral surface of the side sleeve and the outer peripheral surface of the inner diameter side sleeve is blocked from the external space.

Further, when the floating disc brake of the present invention as described above is implemented, for example, as in the invention described in claim 6, the outer side end of the sub pin is connected to the outer side pressure plate constituting the outer pad. It passes through an outer side guide hole provided at the other circumferential end. The sub pin and the caliper are not directly engaged.
Alternatively, as in the invention described in claim 7, the tip end portion of the sub-pin is inserted into an outer side guide hole provided at the other circumferential end portion of the outer pressure plate constituting the outer pad. Then, the portion closer to the inner side of the sub-pin and the second guide hole provided at the other circumferential end of the caliper are engaged with each other so as to be capable of relative displacement in the axial direction.
Alternatively, as in the invention described in claim 8, with respect to the width dimension in the circumferential direction, the caliper is made larger than the support, and an inner side portion provided with the cylinder hole and the caliper claw portion of the caliper A bridge part is made to exist in the position which pinches | interposes both the said guide pins from the circumferential direction both between. And the front-end | tip part of the said sub pin is inserted in the outer side guide hole provided in the circumferential direction other end part by the outer side end part of the said caliper, the inner side part of the said sub pin, and the circumferential direction other end side of the said caliper The second guide hole provided in the shaft is engaged so as to be capable of relative displacement in the axial direction.

  Further, when carrying out the invention described in claims 7 to 8 as described above, for example, as in the invention described in claim 9, the sub-pin is disposed on the outer side end surface on the other end side in the circumferential direction of the support. A cylindrical sleeve that abuts against the inner side surface, and a rod that is inserted through the sleeve from the inner side and screwed into a screw hole provided at the other circumferential end of the support. Then, the sliding portion between the sub pin and the second guide hole is blocked from the external space by a boot made of an elastic material locked to the outer peripheral surfaces of both ends of the sleeve.

  According to the floating disc brake of the present invention configured as described above, it is possible to realize a structure in which the support can be easily processed to reduce the cost and the uneven wear of the inner and outer pad linings can be reduced. In addition, if necessary, it is possible to prevent the generation of noise or vibration caused by the collision between the edge of the pressure plate of the inner pad of the two pads and the mating surface, regardless of the traveling direction of the vehicle during braking. Further, if necessary, it is possible to realize a structure capable of easily exchanging both the pads.

  First, the support processing can be facilitated by supporting the outer pad on the inner side surface of the caliper claw. That is, by adopting this structure, the shape of the support can be simplified. In addition, the manufacturing cost of the floating disc brake including the support can be reduced. In particular, as in the invention described in claim 2, if both ends of the inner pad in the circumferential direction are supported by the part of the support and the sub pin so that the brake torque applied to the inner pad can be supported, the inner pad can be supported. The manufacturing cost can be further reduced by facilitating the processing of the portion for supporting.

  Next, the uneven wear of the linings of the two pads can be reduced by disposing the main pin radially inward of the sub-pin and by supporting a part of the brake torque applied to the outer pad by the sub-pin. First, by disposing the main pin radially inward of the sub pin, the distance between the main pin and a portion where the support is coupled to the vehicle body can be shortened. The main pin and the rigidity of the caliper supported by the main pin when the brake torque is applied to the main pin during braking can be increased. Can be reduced. Further, since the sub pin supports a part of the brake torque applied to the outer pad, the brake torque applied from the outer pad to the caliper claw at the time of braking is reduced correspondingly, and the caliper posture changes based on the brake torque. Less. As a result, the bias of the pressing force of both the pads due to the pushing out of the piston built in the caliper can be suppressed to a small extent, and the uneven wear of the linings of both the pads can be suppressed. In particular, as in the invention described in claim 2, if the central axis of the main pin is installed radially inward from the outer peripheral edge of the rotor, the distance can be sufficiently shortened and the support rigidity can be sufficiently increased. Thus, the effect of suppressing the uneven wear of both the pads can be further increased.

  According to the second aspect of the present invention, it is possible to prevent the inner pad and a part of the support or the sub pin from colliding with each other at the time of braking, regardless of the traveling direction of the vehicle. The generation of sound and vibration can be prevented. In other words, a tangential force is applied to the inner pad with respect to the center of the friction surface based on the friction between the lining and the inner side surface of the rotor during braking. Then, depending on the relationship between the direction of application of this force and the position of the anchor portion for supporting this force, the inner pad passes through the center of the friction surface and is around a virtual central axis parallel to the central axis of the rotor. The moment is added. If there is a gap in the front part of the moment application direction at the moment of the start of braking, abnormal noise and vibration are generated due to the collision as the gap disappears. If the traveling direction of the vehicle is constant, the collision can be prevented by eliminating the gap with an anti-rattle spring. However, in the case of an automobile, for example, even if the gap is eliminated in the forward state, there is a possibility that the gap cannot be eliminated in the reverse state. On the other hand, if the configuration of the invention described in claim 2 is adopted, a moment in the same direction is applied to the inner pad during braking from the forward state and during braking from the reverse state. For this reason, as long as this inner pad is elastically pressed in the same direction as this moment by an anti-rattle spring such as a pad clip, there is no gap on the front side of the moment acting direction during braking. Generation of abnormal noise and vibration due to the collision can be prevented.

  The outer pad may be assembled to the inner surface of the caliper claw in a state where relative displacement with respect to the caliper claw is prevented. In the engaging portion between the tip portion of the sub pin and the pressure plate constituting the outer pad, there is a gap necessary for relative displacement of the sub pin and the pressure plate in the axial direction. However, when the sub-pin is installed radially outside the outer peripheral edge of the rotor, the direction of the moment acting on the outer pad during braking is the same regardless of the rotational direction of the rotor. Therefore, with respect to the outer pad, if an anti-rattle spring that presses the outer pad in an appropriate direction is provided, there is no gap on the front side of the moment application direction during braking, and noise and vibration are generated due to the collision. Can be prevented.

Next, the pad replacement operation can be facilitated by arranging the central axis of the main pin on the radially inner side of the outer peripheral edge of the rotor. That is, in a state where the sub pin is removed from the support, the caliper can be rotated around the main pin. Even when the inner pad and the outer pad are supported by the caliper, a part of both the pads and the part of the support may interfere during the rotation around the main pin. Absent. For this reason, the attachment / detachment of these pads to / from the caliper can be performed with the caliper rotated radially outward about the main pin, thereby facilitating the pad replacement operation.
Furthermore, the replacement of the two pads can be performed with the main pin removed from the guide hole of the caliper and the caliper separated from the support. If the caliper and the support are separated, the caliper can be taken out of the vehicle body within a range not damaging the brake hose, and the replacement operation can be performed more easily. Moreover, in the manufacturing process of floating disc brakes at the factory, if the two pads are assembled to the caliper before the caliper is assembled to the support, then the caliper is assembled to the support. Can be simplified.

The perspective view which shows the 1st example of embodiment of this invention in the state seen from the outer side and radial direction outer side. The orthographic view shown in the state similarly seen from the outer side. The orthographic view shown in the state similarly seen from radial direction outward. FIG. 3 is an orthographic projection view as seen from the left side of FIG. 2. The orthographic view shown in the state similarly seen from the inner side. Similarly, aa sectional view of FIG. The perspective view which shows the state which removed the caliper which assembled | attached both inner and outer pads from the support in the state seen from the outer side and radial direction inner side. The perspective view which shows the support which removed the caliper in the state seen from the outer side and radial direction outer side. The schematic diagram for demonstrating the moment added to an inner pad at the time of advance (A), and the schematic diagram for demonstrating the moment added to an outer pad (B). The same figure as FIG. 9 for demonstrating the moment added to both pads at the time of reverse. The perspective view which shows the 2nd example of embodiment of this invention in the state seen from the outer side and radial direction outer side. The orthographic view shown in the state similarly seen from radial direction outward. Similarly, sectional drawing similar to FIG. The perspective view which shows the 3rd example of embodiment of this invention in the state seen from the outer side and radial direction outer side. The orthographic view shown in the state similarly seen from the outer side. The orthographic view shown in the state similarly seen from radial direction outward. FIG. 16 is an orthographic view showing the state viewed from the left side of FIG. 15. Similarly, an orthographic view seen from the right. The orthographic view shown in the state similarly seen from the inner side. The orthographic projection shown in the state similarly seen from radial inside. Bb sectional drawing of FIG. The perspective view shown in the state seen from the inner side and radial direction outer side in the state which assembled the example of the conventional structure. Similarly disassembled perspective view.

[First example of embodiment]
FIGS. 1-10 has shown the 1st example of embodiment of this invention corresponding to Claims 1-3,6. The floating type disc brake of this example includes a support 1a, a main pin 17 and a sub pin 18, each of which is a guide pin, a caliper 3a, an inner pad 4a, and an outer pad 5a.

  Of these, the support 1a is a plate having irregularities by casting (including die-casting) an iron-based alloy or an aluminum-based alloy, or by pressing a steel plate having sufficient strength and rigidity. In the middle portion in the circumferential direction (left and right direction in FIGS. 1 to 3 and 5 to 8), a recessed portion 7 a having an outer opening in the radial direction is provided. In addition, mounting holes 19 and 19 are formed in the support 1a at portions near the inner diameter at both ends in the circumferential direction. The support 1a is inserted through the mounting holes 19 and 19 (when the mounting holes 19 and 19 are simple circular holes) or screwed into the mounting holes 19 and 19 (both the mounting holes 19 and 19). When 19 is a screw hole) A part of a suspension device such as a knuckle is coupled and fixed to the vehicle body by a bolt. In any case, the support 1a is fixed to the vehicle body on the inner side of the rotor 6 that rotates together with the wheels. In the case of this example, the rotor 6 moves from the right to the left of each figure as shown by the arrow α in FIGS. 2, 3, 6 and 9 (the opposite of FIGS. Rotate clockwise. Therefore, the turn-in side in the forward state is the right side of FIGS. 1 to 3 and 5 to 9, and the turn-out side is the left side of these drawings. Moreover, in the following description, the inflow side and the outflow side are in the state at the time of advance unless otherwise indicated. In the case of this example, the entrance edge is equivalent to the other circumferential edge described in the claims, and the delivery edge is also equivalent to the circumferential one edge.

The main pin 17 and the sub pin 18 are arranged in parallel to each other, and their base end portions are coupled and fixed to both ends in the circumferential direction of the support 1a.
The main pin 17 is coupled and fixed to one end of the support 1a in the circumferential direction so as to protrude from the inner side surface of the support 1a to the inner side. For this purpose, the main pin 17 is further tightened by screwing a small-diameter male screw portion 20 provided at the base end portion into a screw hole 21 formed at one end portion in the circumferential direction of the support 1a. In this state, at least the central axis of the main pin 17 (in the illustrated example, the main pin 17 as a whole) is present radially inward from the outer peripheral edge of the rotor 6.

  On the other hand, the sub pin 18 is coupled and fixed to the other circumferential end of the support 1a so as to protrude from the outer side surface of the support 1a to the outer side. For this purpose, the sub-pin 18 has a male screw portion 23 provided near the proximal end portion of the intermediate portion with another screw hole 22 formed in the other circumferential end portion of the support 1a inserted from the inner side to the outer side. The screw hole 22 is screwed and further tightened. In this state, the entire portion of the sub-pin 18 that protrudes from the outer side surface of the support 1 a to the outer side exists radially outward from the outer peripheral edge of the rotor 6. The sub pin 18 has the largest outer diameter of the flange portion 25 adjacent to the locking portion 24 for locking a tool such as a spanner provided at the base end portion (inner side end portion). And the outer diameter of the base half part 26 adjacent to the outer side of this collar part 25 is comparatively large, and the outer diameter of the front half part 27 which exists in the outer side further than this base half part 26 is comparatively small.

  In the case of this example, by adopting a structure in which the main pin 17 as described above and the sub pin 18 as described above are assembled to the support 1a as described above, the processing of the support 1a can be facilitated. That is, by adopting these structures, the shape of the support 1a can be simplified, and the processing for supporting the inner pad 4a described later can be facilitated. And the manufacturing cost of the floating type disc brake including the support 1a can be reduced.

  The caliper 3a is capable of axial displacement with respect to the support 1a by the main pin 17 as described above and the sub pin 18 as described above, and the main pin 17 by brake torque applied during braking. Is supported so that it does not rotate around the center. That is, a guide arm portion 28 is provided in the circumferential direction from a side surface on one side in the circumferential direction of the caliper 3a (in this example, a side surface on the outlet side), and a guide cylinder is provided at the tip of the guide arm portion 28. A portion 29 is provided. Further, a guide hole 30 is provided in the guide tube portion 29 in the axial direction so as to open to the outer side. The guide hole 30 has at least its central axis (in the illustrated example, the entire guide hole 30) disposed radially inward of the outer peripheral edge of the rotor 6. The main pin 17 is inserted into such a guide hole 30 so as to be capable of axial displacement. The outer diameter of a portion of the main pin 17 inserted into the guide hole 30 does not change in the axial direction, and the outer diameter is only slightly smaller than the inner diameter of the guide hole 30. Therefore, the main pin 17 is fitted in the guide hole 30 without rattling so that the displacement and rotation are possible. A boot 31 made of an elastic material is installed between the outer end surface of the guide tube portion 29 and the inner side surface of the output side end portion of the support 1a, and the inner peripheral surface of the guide hole 30 and the Foreign matter such as muddy water is prevented from entering the sliding portion with the outer peripheral surface of the main pin 17.

  On the other hand, the sub-pin 18 does not rattle the locking holes 32a and 32b formed at the other circumferential ends of the pressure plates 14c and 14d constituting the pads 4a and 5a, but the axial displacement is not caused. Insert as loosely as possible. For this purpose, the other circumferential ends of the pressure plates 14c and 14d are sufficiently projected radially outward from the outer peripheral edge of the rotor 6, and the locking holes 32a, 32b is formed. The inner diameters (diameters of the inscribed circles) of both the locking holes 32a and 32b are larger at the locking holes 32a formed in the pressure plate 14c of the inner pad 4a in accordance with the outer diameter of the sub pin 18, and the pressure of the outer pad 5a is increased. The size is reduced by a locking hole 32b formed in the plate 14d.

  Of the both ends in the circumferential direction of the caliper 3a, the outlet side end is directly connected to the support 1a by the main pin 17, and the inlet side end is also connected to the support 1a by the sub pin 18 through the outer pad 5a. Axial displacement is supported. The outer pad 5a supports the caliper 3a so that the brake torque can be supported and is not rotated by the brake torque. For this purpose, the pressure plate 14d constituting the outer pad 5a is engaged at two locations on the inner side surface of the caliper claw 10a provided at the outer side end of the caliper 3a (a convex portion 39 and a locking hole 40 described later). And a restraining spring (a pad spring 41 described later).

  That is, the caliper 3a is provided with a caliper claw 10a at an outer side end portion and a cylinder portion 11a at an inner side half portion. The caliper pawls 10a and the cylinder portion 11a are connected to each other at the radially outer ends by a bridge portion 34 that is present radially outward from the outer peripheral edge of the rotor 6 (provided at a position straddling the rotor 6). Are integrally connected. In other words, the caliper claw 10a is provided in a state of projecting radially inward from the outer side end of the bridge portion 34. Further, a cylinder hole 35 is provided in the cylinder portion 11a so as to open toward the inner side surface of the caliper claw 10a through the recessed portion 7a of the support 1a. A piston 36 is fitted in the cylinder hole 35 through a seal ring 37 in an oil-tight manner. Pressure oil can be supplied and discharged into the cylinder hole 35 via the oil supply port 12a. The piston 36 can be displaced in the axial direction within the cylinder hole 35 based on the supply and discharge of the pressure oil.

  Further, the inner pad 4a is supported in such a manner that it can be displaced in the axial direction and can support brake torque in both directions in a state of being spanned between a part of the support 1a and the base end portion of the sub pin 18. is doing. That is, the edge of the outlet side of the pressure plate 14c constituting the inner pad 4a abuts against the inner surface of the outlet side end of the recessed portion 7a formed in the support 1a, and the inlet side of the pressure plate 14c. As described above, the end portion is supported by the engagement between the base end portion of the sub-pin 18 and the locking hole 32a. Further, in this state, the pad clip 38 locked to the back surface of the pressure plate 14c is elastically fitted in the opening of the piston 36 to be locked to the tip of the piston 36.

  On the other hand, the outer pad 5 a is provided in a state of facing the inner pad 4 a through the rotor 6. Further, the outer pad 5a is supported on the inner side surface of the caliper claw 10a in a state where the brake torque applied to the outer pad 5a during braking is engaged with the caliper claw 10a so as to be able to be transmitted. For this reason, in the case of this example, a pair of convex portions 39, 39 project from the back surface of the pressure plate 14d constituting the outer pad 5a, and both the convex portions 39, 39 are formed on the caliper claw 10a, respectively. The engagement holes 40, 40 are fitted with no backlash. Further, the pad spring 41 attached to the back surface of the pressure plate 14d constituting the outer pad 5a prevents rattling and separation of the outer pad 5a with respect to the caliper claw 10a.

  When braking is performed by the floating disc brake of the present invention configured as described above, pressure oil is fed into the cylinder hole 35 through the oil supply port 12a. Then, the piston 36 is pushed out to the outer side, and the lining 15 c of the inner pad 4 a is pressed against the inner side surface of the rotor 6. Then, as a reaction of this pressing, the caliper 3a causes the fitting portion between the main pin 17 and the guide hole 30 and the engaging portion between the tip portion of the sub pin 18 and the locking hole 32b in the axial direction. It is displaced to the inner side while sliding. The caliper claw 10 a provided on the caliper 3 a presses the outer pad 5 a toward the inner side, and presses the lining 15 d of the outer pad 5 a against the outer side surface of the rotor 6. As a result, the rotor 6 is clamped from both sides in the axial direction, and braking is performed. If the hydraulic pressure in the cylinder hole 35 is eliminated, the linings 15c and 15d of the pads 4a and 5a are separated from both side surfaces of the rotor 6 by the elastic force of a return spring (not shown) and the braking is released.

  During braking performed as described above, brake torque acts on the pads 4a and 5a based on friction between the linings 15c and 15d and both side surfaces of the rotor 6. During forward movement, the brake torque is supported on the inner surface of the outlet side end portion of the recessed portion 7a formed in the support 1a (by the inner surface functioning as a push anchor) with respect to the inner pad 4a. Further, when the braking torque is large and the amount of elastic deformation of the support 1a is increased during sudden braking or the like, the engaging portion between the base end portion of the sub pin 18 and the locking hole 32a (the sub pin 18 is pulled and the anchor is A part of the brake torque may be supported.

  On the other hand, a part of the brake torque applied to the outer pad 5a is transmitted to the caliper 3a, and is transmitted from the caliper 3a to the support 1a via the main pin 17, and the support 1a is coupled and fixed. The body is supported. The remaining portion of the brake torque applied to the outer pad 5a is supported by the sub pin 18. That is, the brake torque applied to the outer pad 5a during braking is transmitted to the caliper pawl 10a based on the engagement between the both convex portions 39, 39 and the locking holes 40, 40. As a result, the caliper pawl 10a tends to be displaced together with the outer pad 5a to the outlet side, and the outer peripheral surface of the tip of the sub pin 18 and the outlet side portion of the inner peripheral surface of the locking hole 32b are in contact with each other. Touch. As a result, the sub pin 18 functions as a pulling anchor and supports a part of the brake torque applied to the outer pad 5a. In this way, when the brake torque applied to the outer pad 5a is supported, a moment is applied to the caliper 3a to rotate clockwise in FIGS. Then, due to this moment, the caliper 3a tends to be improper.

  In the case of this example, the main pin 17 exists radially inward from the outer peripheral edge of the rotor 6, and the distance between the main pin 17 and the portion connecting the support 1a to the vehicle body is short. The rigidity of the support 1a with respect to the brake torque applied to the support 1a from the caliper 3a, that is, the support rigidity of the caliper 3a supported by the support 1a via the main pin 17 is sufficiently high. Accordingly, when the braking force applied to the outer pad 5a (and the inner pad 4a) is small as in the case of light braking such as when the vehicle is gradually decelerated, the posture of the caliper 3a is deteriorated when the moment is small. , Small enough to be ignored. The contact pressure between the linings 15c and 15d of the pads 4a and 5a and both axial side surfaces of the rotor 6 is less likely to cause a large difference between the turn-in side and the turn-out side. As a result, both sides of the linings 15c and 15d can be less likely to cause uneven wear.

  Even when the brake torque applied to the pads 4a and 5a is large, such as during sudden braking, in addition to the high support rigidity of the caliper 3a, the brake torque applied to the pads 4a and 5a (particularly the outer pad 5a) Since a part is supported by the sub pin 18 fixed to the support 1a, the posture of the caliper 3a is prevented from deteriorating, and uneven wear of the linings 15c and 15d can be suppressed.

  During braking in the reverse state, the brake 1 applied to the inner pad 4 a is supported by the support 1 a via the base end portion of the sub pin 18. The brake torque applied to the outer pad 5a is supported by the caliper 3a as in the forward state. The caliper 3a tends to swing counterclockwise in FIGS. The braking torque applied to the pads 4a and 5a during braking in the reverse state is smaller than the braking torque applied in the forward state and the frequency of braking is low, so the linings 15c and 15d of the pads 4a and 5a Uneven wear is not a problem. Rather, if the linings 15c and 15d are unevenly worn at the time of braking in the reverse state, there is a possibility that the uneven wear caused by the braking in the forward state (cannot be solved by the structure of the present invention) can be offset. There is.

  Out of the two pads 4a and 5a, the outer pad 5a supports the caliper claw 10a of the caliper 3a without rattling in a state where the outer pad 5a is not relatively displaced by the above-described structure. Therefore, the outer pad 5a does not rattle against the caliper pawl 10a during braking in any of the forward and backward states. However, also with respect to the outer pad 5a, the tip end portion of the sub-pin 18 and the locking hole 32b are engaged with each other so as to be capable of relative displacement in the axial direction. For this reason, there is a possibility that vibrations and abnormal noises associated with rattling may occur at the engaging portion. The inner pad 4a supports the support 1a and the sub pin 18 so as to be capable of axial displacement. Therefore, there is a possibility that the inner pad 4a rattles with respect to the support 1a when not braked, and unpleasant noises and vibrations are generated. In order to prevent the engaging portions between the pressure plates 14c and 14d of the pads 4a and 5a and the mating member from rattling during non-braking, an anti-rattle spring is provided between the pressure plates 14c and 14d and the mating member. Should be provided. However, if the direction of the moment applied to the pressure plates 14c and 14d is different between the forward and reverse directions, the pressure plates 14c and 14d will be in the above-described state during braking either during forward or reverse movement. While the anti-rattle spring is elastically deformed, it may collide with the mating member vigorously, and the vibration or noise may occur.

  On the other hand, in the case of the structure of this example, the moment in the same direction is applied to both the inner and outer pads 4a and 5a during braking in either the forward state or the backward state. This point will be described with reference to FIGS. Of these FIGS. 9 to 10, FIG. 9 shows the behavior during braking in the forward movement state, and the rotor 6 rotates counterclockwise as shown by an arrow α. FIG. 10 shows the behavior at the time of braking in the reverse state, and the rotor 6 rotates in the clockwise direction as shown by an arrow β. In each figure, the upper pad (a) shows the inner pad 4a, and the lower pad (b) shows the outer pad 5a.

First, the behavior of the inner pad 4a in the forward state will be described with reference to FIG. In this case, the rotor 6 rotates counterclockwise as shown by an arrow α. The said inner pad 4a at the time of braking, the braking torque F ₁ at the center portion of the friction surface between the inner side and the lining 15c of the rotor 6 and at the central portion, the center of rotation of the rotor 6 and the center arc Can be considered to be added in the tangential direction. The brake torque F ₁ is mainly caused by a contact portion (push anchor portion) between a portion closer to the inner diameter of the outlet side edge of the pressure plate 14c and the inner surface of the outlet side end portion of the recessed portion 7a of the support 1a. Support (see arrow a). The position (power point) at which the brake torque F ₁ acts is located radially outside the position (fulcrum) where the brake torque F ₁ is supported. For this reason, the inner pad 4a tends to swing counterclockwise in FIG. As a result, the radially inner end edge of the outlet side end portion of the pressure plate 14c is pressed against the bottom of the recessed portion 7a as shown by the arrow b in FIG. Further, at the turn-in side end, the inner peripheral surface of the locking hole 32a and the outer peripheral surface of the base end portion of the sub-pin 18 are the respective inner ends in the radial direction, as indicated by arrows C in FIG. Pressed against.

Next, the behavior of the outer pad 5a in the forward state will be described with reference to FIG. In this case, it can be considered that the brake torque F ₂ is applied to the outer pad 5a at the central portion of the friction surface between the outer side surface of the rotor 6 and the lining 15d in the tangential direction with respect to the central portion. The brake torque F ₂ is supported mainly by the engaging portion (push anchor portion) between the main pin 17 and the guide tube portion 29 (see arrow D). The position (power point) at which the brake torque F ₂ acts also exists radially outside the position (fulcrum) where the brake torque F ₂ is supported. For this reason, the outer pad 5a tends to swing counterclockwise in FIG. As a result, the inner peripheral surface of the guide tube portion 29 is pressed radially inward against the outer peripheral surface of the main pin 17 as indicated by an arrow E in FIG. Further, at the turn-in side end, the inner peripheral surface of the locking hole 32b and the outer peripheral surface of the tip end portion of the sub pin 18 are the respective inner ends in the radial direction, as indicated by arrows in FIG. 9B. Pressed.

Next, the behavior of the inner pad 4a in the retracted state will be described with reference to FIG. In this case, it can be considered that the brake torque F ₃ is applied to the inner pad 4a at the central portion of the friction surface between the inner side surface of the rotor 6 and the lining 15c in the tangential direction with respect to the central portion. Further, the brake torque F ₃ is mainly present at the radially outer portion of the outer edge of the rotor 6 at the end of the pressure plate 14c at the turn-in side end (actually, the end at the return side in the retracted state). It is supported by the engaging portion between the locking hole 32a and the base end portion of the sub pin 18 (see arrow G). The position (power point) at which the brake torque F ₃ acts exists radially inward from the position (fulcrum) at which the brake torque F ₃ is supported. For this reason, the inner pad 4a tends to swing counterclockwise in FIG. As a result, as in the case of braking in the forward state described above, the radially inner end edge of the outlet side end portion of the pressure plate 14c is as shown by the arrow B in FIG. It is pressed against the bottom of the recessed portion 7a. Further, at the turn-in side end, the inner peripheral surface of the locking hole 32a and the outer peripheral surface of the base end portion of the sub-pin 18 are the respective inner ends in the radial direction, as indicated by arrows C in FIG. Pressed against.

Finally, the behavior of the outer pad 5a in the retracted state will be described with reference to FIG. In this case, it can be considered that the brake torque F ₄ is applied to the outer pad 5a in the tangential direction with respect to the central portion of the friction surface between the outer side surface of the rotor 6 and the lining 15d. The brake torque F ₄ is supported mainly by an engaging portion (push anchor portion) between the tip end portion of the sub-pin 18 and the locking hole 32b (see arrow H). The position (power point) at which the brake torque F ₄ acts also exists radially inward from the position (fulcrum) where the brake torque F ₄ is supported. Therefore, the outer pad 5a tends to swing counterclockwise as shown in FIG. As a result, as in the case of braking in the above-described forward state, the inner peripheral surface of the guide tube portion 29 is the outer peripheral surface of the main pin 17, as shown by the arrow H in FIG. It is pressed radially inward. Further, at the turn-in side end portion (actually, the turn-out side end portion in the retracted state), the inner peripheral surface of the locking hole 32b and the outer peripheral surface of the tip end portion of the sub pin 18 are the respective inner end portions in the radial direction. Then, it is pressed as shown by the arrow in FIG.

  As apparent from the above description, in the case of the structure of this example, both the inner and outer pads 4a and 5a are connected to both side surfaces of the rotor 6 during braking in the forward state and during braking in the reverse state. The direction of the moment applied along with the friction between the linings 15c and 15d is the same. Accordingly, in order to prevent the engaging portions between the pressure plates 14c and 14d of the pads 4a and 5a and the mating member from rattling during non-braking, an anti-rattle provided between the pressure plates 14c and 14d and the mating member is prevented. If the direction in which the spring urges both the pads 4a and 5a coincides with the direction of the moment, it is possible to prevent unpleasant noise and vibration from occurring at the moment of braking. That is, the gap between the pressure plates 14c and 14d and the mating member is pressed by the anti-rattle spring while pressing the pads 4a and 5a in the direction of applying a counterclockwise moment in FIGS. If this is eliminated, the gap is not eliminated while the anti-rattle spring is elastically deformed by the brake torque during braking, and unpleasant noise or vibration can be prevented from occurring at the moment of braking. Various types of anti-rattle springs for disc brakes have been known in the art, and those skilled in the art can easily implement them as long as they know the direction in which elasticity is applied.

  Further, in the structure of this example, the work of exchanging the inner and outer pads 4a and 5a is performed by loosening the threaded portion between the male screw portion provided at the base portion of the sub pin 18 and the screw hole 22 of the support 1a. Thereafter, the sub-pin 18 is pulled out from the screw hole 22 to the inner side, and the caliper 3a is rotated radially outward about the main pin 17. At this time, the old inner and outer pads 4a and 5a, whose linings 15c and 15d are worn, are rotated while being supported by the caliper 3a. The main pin 17 serving as the center of rotation exists radially inward from the outer peripheral edge of the rotor 6, and in a state where the sub-pin 18 is removed, the inner end and outer pads 4a and 5a are provided on the outlet side ends. There is no portion that prevents the portion near the outer diameter from being displaced radially outward. Accordingly, the caliper 3a can be largely rotated radially outward about the main pin 17 while the inner and outer pads 4a and 5a are supported by the caliper 3a.

  Therefore, in a state where the caliper 3a is retracted sufficiently radially outward from the outer peripheral edges of the rotor 6 and the support 1a, the old inner and outer pads 4a and 5a are sequentially placed one by one. The pad clip 38 and the pad spring 41 are removed from the caliper 3a while being elastically deformed. Thereafter, new inner and outer pads 4a and 5a (in which the linings 15c and 15d are not worn) one by one in order, the pad clip 38 and the pad spring 41 attached thereto are elastically deformed, and the caliper 3a is Assemble. Such assembling of the pads 4a and 5a to the caliper 3a is performed by removing the wheel from the suspension device, and the caliper 3a is sufficiently radially outward from the outer peripheral edges of the rotor 6 and the support 1a. It can be performed in a relatively large space while being evacuated. Therefore, the pad replacement work can be facilitated.

  The caliper 3a assembled with the new inner and outer pads 4a and 5a is radially inward with respect to the main pin 17, and the radial direction of the end portions of the pressure-in side of the pressure plates 14c and 14d of the pads 4a and 5a. The two through holes 32a and 32b formed in the outer portion are rotated until the screw holes 22 provided at the end of the support 1a are aligned. Then, the sub pin 18 inserted through the screw hole 22 from the inner side is inserted into the through holes 32 a and 32 b from the inner side, and the male screw portion 23 provided at the base end portion of the sub pin 18 is screwed into the screw hole 22. And tighten further. With this operation, the replacement operation of the pads 4a and 5a is completed. During the replacement work, the sub-pin 18 can be easily and reliably attached to and detached from the support 1a, and after the replacement work is completed, the posture of the caliper 3a during braking can be stabilized.

  The main pin 17 fixed to the support 1a side in the state where the caliper 3a is withdrawn from the outer peripheral edge of the rotor 6 and the support 1a sufficiently outward in the radial direction by pulling out the sub pin 18 is provided. The caliper 3a and the support 1a can be separated as shown in FIGS. 7 to 8 by removing the guide hole 30 from the caliper 3a. In this state, the caliper 3a can be taken out of the vehicle body within a range that does not damage the flexible brake hose disposed between the caliper 3a and the vehicle body. In this manner, in a state where the caliper 3a is taken out from the vehicle body 3a, the operation of attaching and detaching the pads 4a and 5a to the caliper 3a can be performed in a wider space, and both the pads 4a 5a can be replaced more easily.

  Furthermore, before assembling the caliper 3a to the support 1a in the manufacturing process of the floating disc brake at the factory, both the pads 4a and 5a are assembled to the caliper 3a, and then the caliper 3a is attached to the support 1a. If assembled, the assembly work in the factory can be facilitated. That is, the work of assembling the pads 4a and 5a to the caliper 3a at the factory can be easily performed without requiring any special jig or skill. At the time of the assembly process in such a factory, since one end of the brake hose is not yet connected to the caliper 3a, the assembly work of the pads 4a and 5a to the caliper 3a can be performed more easily. . Since a pair of pads is assembled in advance on the support side, a jig for preventing the pads from being dropped and considerations for preventing the drops, which are necessary for assembling the calipers to the support, are unnecessary.

[Second Example of Embodiment]
FIGS. 11 to 13 show a first example of an embodiment of the present invention corresponding to claims 1 to 4 and 7. In the case of this example, the arm part 42 is provided in the state which protrudes in the circumferential direction at the turn-in side edge part which is a circumferential other end part among the circumferential direction both ends of the caliper 3b. A second guide hole 43 is provided at the tip of the arm portion 42. Further, the sub-pin 18a is composed of a cylindrical sleeve 44 and a circular rod 45. Then, the sleeve 45 is abutted against the opening of the screw hole 22 formed at the end of the turn-in side on the inner side surface of the support 1a, and the rod 45 is inserted into the sleeve 44 and the screw hole 22 in this state. Further, the male screw portion 23a formed at the intermediate portion of the rod 45 is screwed into the screw hole 22 and further tightened, and the rod 45 and the sleeve 44 are connected to the turning-in side of the support 1a. It is fixed to the end. In this state, the leading half portion (outer side half portion) of the rod 45 is similar to the sub-pin 18 (see, for example, FIG. 6) in the first example of the above-described embodiment, and the inward side end of the support 1a. It protrudes from the outer side surface of the part to the outer side. Thus, the structure and operation of the portion protruding to the outer side are the same as those of the sub-pin 18 in the first example of the embodiment described above.

In particular, in the case of the structure of this example, the sleeve 44 can be displaced in the second guide hole 43 through an elastic material such as an elastomer such as rubber and a cylindrical bush 46 in the axial direction. I support it. Further, the distal ends of a pair of boots 47 a and 47 b in which the base ends are integrally coupled to both ends of the bush 46 are engaged with locking step portions formed at both ends of the sleeve 44. In the case of the present example, this configuration improves the support rigidity of the caliper 3b, suppresses the displacement of the caliper 3b during braking, and prevents uneven wear of the linings 15c and 15d of the inner and outer pads 4a and 5a. , So that it can be kept less.
Since the configuration and operation of the other parts are the same as those of the first example of the embodiment described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.

[Third example of embodiment]
FIGS. 14-21 has shown the 3rd example of embodiment of this invention corresponding to Claims 1-3, 5, 8, and 9. FIG. In the case of this example, the caliper 3c is made larger than the support 1b with respect to the width dimension in the circumferential direction. The caliper 3c is made by die casting of a light alloy such as an aluminum alloy. Further, in the caliper 3c, between the inner side portion 48 provided with the cylinder hole 35 and the caliper claw 10b portion, the main pin 17a and the sub pin 18b, which are guide pins, are sandwiched from both sides in the circumferential direction. Portions 49 and 49 are provided. The sub-pin 18b is substantially the same as the sub-pin 18a of the second example of the embodiment described above (see, for example, FIG. 13), and is provided with a cylindrical sleeve 44a and a circular screw-shaped male screw portion 23b in the middle portion. Rod 45a. In the case of this example, in order to assemble such a sub pin 18b, a holding cylinder portion 50 having a center hole as a screw hole is provided at the radially outer end portion of the end portion of the support 1b. Then, the male thread portion 23b of the rod 45a is screwed into the holding cylinder portion 50 and further tightened, and the sub pin 18b formed of the rod 45a and the sleeve 44a is connected in the radial direction of the end of the support 1b. It is fixed to the outer end.

  In the case of this example, an outer side guide hole 51 is formed concentrically with the sub-pin 18b at a portion near the turn-in side end of the outer side end of the caliper 3c. And the front-end | tip part (outer side edge part) of the said rod 45a which comprises this subpin 18b is fitted in the said outer side guide hole 51 via the slide bearing 52. As shown in FIG. As with the second example of the above-described embodiment, the inner portion of the sub-pin 18b can be displaced in the axial direction by fitting the sleeve 44a into the second guide hole 43a via the bush 46. I support it.

  Further, in the case of this example, the structure of the main pin 17a for supporting the end portion of the caliper 3c on the support 1b so as to be capable of axial displacement is also described in the above embodiment. This is different from the first and second examples. That is, in the case of this example, the guide hole 30a provided at the outlet side end portion of the inner side portion 48 of the caliper 3c is made of a metal having wear resistance such as an iron-based alloy such as stainless steel. The outer diameter side sleeve 53 is internally fitted and fixed. On the other hand, the main pin 17a, like the sub pin 18b, is composed of a cylindrical inner sleeve 54 and a bolt-shaped rod 55 having a male threaded portion 20a formed at the tip (outer end). Yes. Then, the rod 55 is inserted into the inner sleeve 54 from the inner side, and the male screw portion 20a formed at the tip is screwed into a screw hole 21a provided at the outlet side end of the support 1b. Further, the main pin 17a is fixed to the end portion of the support 1b so as to protrude toward the inner side by further tightening. Further, a fixed-side locking groove formed on the outer peripheral surface of both ends in the axial direction of the outer diameter side sleeve 53 and a locking step portion on the moving side formed on the outer peripheral surface of both ends of the inner diameter side sleeve 54 in the axial direction. The both ends of the boots 56a and 56b made of an elastic material are locked. The sliding portion between the outer peripheral surface of the inner diameter side sleeve 54 and the inner peripheral surface of the outer diameter side sleeve 53 is blocked from the external space.

In the case of this example, based on the difference in the shape of the caliper 3c, the shapes of the inner pad 4b and the outer pad 5b are different from those in the first and second examples of the above-described embodiment. Further, the shape of the pad spring 41a for locking the pressure plate 14d constituting the outer pad 5b to the inner side surface of the caliper claw 10b is also different from the case of the first and second examples of the above-described embodiment. It is
In the case of this example, the radially outward portion of the pressure-in side end of the pressure plate 14c constituting the inner pad 4b is abutted against the output side end of the outer peripheral surface of the holding cylinder portion. Thus, it is possible to support the brake torque applied to the inner pad 4b during braking in the reverse state.

When the present invention is applied to the structure having the wide caliper 3c as described above, a large stress based on a large brake torque is applied during braking, and the main pin 17a is attached to the delivery side portion of the caliper 3c. There is no need to form holes for engaging the ends. This is advantageous in terms of ensuring the rigidity of the caliper 3c.
In the case of this example, both ends of the boots 56a and 56b are also locked with respect to the structure of the portion where the guide hole 30a and the main pin 17a are engaged with each other so as to be capable of relative displacement in the axial direction. For example, it is possible to easily process the locking groove and the locking step portion.
Since the configuration and operation of the other parts are the same as those in the first and second examples of the above-described embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted.

  The present invention can also be implemented as a disc brake dedicated to parking. In this case, there is no need to supply / discharge pressure oil into / from the cylinder hole of the caliper, and it is not necessary to provide a structure (oil supply port or the like) for supplying / discharging pressure oil.

1, 1a, 1b Support 2 Guide pin 3, 3a, 3b, 3c Caliper 4, 4a, 4b Inner pad 5, 5a, 5b Outer pad 6 Rotor 7, 7a Recessed portion 8 Bolt 9a, 9b Guide tube portion 10, 10a, 10b Caliper claw 11, 11a Cylinder part 12, 12a Oil supply port 13 Anchor block 14a, 14b, 14c, 14d Pressure plate 15a, 15b, 15c, 15d Lining 16 Substrate part 17, 17a Main pin 18, 18a, 18b Sub pin 19 Mounting hole 20 , 20a Male screw part 21, 21a Screw hole 22 Screw hole 23, 23a, 23b Male screw part 24 Locking part 25 Gutter part 26 Base half part 27 Front half part 28 Guide arm part 29 Guide cylinder part 30 Guide hole 31 Boots 32a, 32b Locking hole 34 Bridge part 35 Cylinder Double hole 36 Piston 37 Seal ring 38 Pad clip 39 Protruding part 40 Locking hole 41, 41a Pad spring 42 Arm part 43, 43a Second guide hole 44, 44a Sleeve 45, 45a Rod 46 Bushing 47a, 47b Boot 48 Inner side Portion 49 Bridge portion 50 Holding cylinder portion 51 Outer side guide hole 52 Slide bearing 53 Outer diameter side sleeve 54 Inner diameter side sleeve 55 Rod 56a, 56b Boot

Claims (9)

  A support that is fixed to the vehicle body on the inner side of the rotor that rotates together with the wheel, and a support that is arranged in the axial direction, is provided with a recessed portion that opens radially outward in the middle of the circumferential direction. A pair of guide pins fixed at both ends in the direction, a caliper supported by the guide pins so as to be capable of axial displacement with respect to the support, and a portion of the support supported by the portion capable of axial displacement. An inner pad and an outer pad provided in a state of being opposed to the inner pad via the rotor, and the caliper is provided with a caliper claw protruding radially inward at an outer side end portion, and on the inner side. The piston is fitted in the cylinder hole provided in a state where it opens toward the inner side surface of the caliper claw through the recessed portion of the support so as to be capable of axial displacement. In the floating type disc brake, the outer pad is supported on the inner side surface of the caliper pawl in a state in which relative displacement with respect to the caliper pawl is prevented in each direction, and applied to the outer pad during braking. Torque can be transmitted to the caliper pawl, and the main pin, which is one of the guide pins provided on one end in the circumferential direction, protrudes only from the support toward the inner side. The guide hole provided at one end in the circumferential direction of the caliper is inserted so as to be capable of axial displacement and relative rotation about its own central axis, and is also provided at the other end in the circumferential direction. The sub-pin that is the other guide pin is radially outward from the main pin and radially outward from the outer peripheral edge of the rotor. This part is provided so as to straddle the rotor, and the other end in the circumferential direction of the caliper can be displaced partly on the part of the sub-pin and can be displaced in the axial direction directly or via the pressure plate constituting the outer pad. A floating disc brake characterized in that a part of the brake torque applied to the outer pad during braking is engaged with the sub pin so as to be supported.   The central axis of the main pin is disposed radially inward from the outer peripheral edge of the rotor, and the circumferential one end edge of the inner pad is the diameter of the inner circumferential edge of the recessed portion provided in the support. The floating disc brake according to claim 1, wherein the inner side portion and the other circumferential end of the inner pressure plate constituting the inner pad are engaged with the sub pin so as to be able to support brake torque. .   The floating type according to any one of claims 1 to 2, wherein one end side in the circumferential direction is a return side of the rotor and the other end side in the circumferential direction is a return-in side in the forward movement state of the vehicle. Disc brake.   A second guide hole is provided at the other circumferential end of the caliper, and the sub pin protrudes also to the inner side of the support, and a portion of the sub pin that protrudes to the inner side is the second guide. The floating disk brake according to any one of claims 1 to 3, wherein the hole is fitted in the hole so as to be capable of relative displacement in the axial direction.   An outer diameter side sleeve is fitted and fixed in a guide hole provided at one end in the circumferential direction of the caliper, and the main pin is a cylinder in which the outer side end surface is abutted against the inner side surface at one end in the circumferential direction of the support An inner diameter side sleeve and a rod inserted through the inner diameter side sleeve from the inner side and screwed into a screw hole provided at one end in the circumferential direction of the support. The inner peripheral surface of the outer diameter side sleeve and the inner diameter side sleeve by a pair of boots, each of which is made of an elastic material, each of which is locked between the outer peripheral surface of the inner diameter side sleeve and the outer surface of the inner diameter side sleeve The floating type disc brake according to any one of claims 1 to 4, wherein a sliding portion with respect to the outer peripheral surface is cut off from an external space.   An outer side end portion of the sub pin is inserted into an outer side guide hole provided at the other circumferential end portion of the outer side pressure plate constituting the outer pad, and the sub pin and the caliper are directly engaged with each other. The floating type disc brake according to any one of claims 1 to 5, wherein the floating type disc brake is not provided.   The tip of the sub pin is inserted into an outer side guide hole provided at the other circumferential end of the outer pressure plate that constitutes the outer pad, and the inner portion of the sub pin and the other circumferential end of the caliper The floating type disc brake according to any one of claims 1 to 5, wherein a second guide hole provided on the side is engaged so as to be capable of relative displacement in the axial direction.   The caliper is larger than the support with respect to the width dimension in the circumferential direction, and the position where the guide pins are sandwiched from both sides in the circumferential direction between the inner side portion of the caliper provided with the cylinder hole and the caliper claw portion. A bridge portion is present, and the tip end portion of the sub pin is inserted into an outer side guide hole provided at the other end portion in the circumferential direction at the outer side end portion of the caliper, and a portion closer to the inner side of the sub pin The floating described in any one of Claims 1-5 with which the 2nd guide hole provided in the circumferential direction other end side of the said caliper is engaged so that relative displacement of an axial direction is possible. Type disc brake.   The sub-pin includes a cylindrical sleeve having an outer side end surface abutted against an inner side surface on the other end side in the circumferential direction of the support, and a screw provided on the other end in the circumferential direction of the support by inserting the sleeve from the inner side. It consists of a rod screwed into a hole, and the sliding part between the sub-pin and the second guide hole is cut off from the external space by a boot made of an elastic material locked to the outer peripheral surface of both ends of the sleeve. The floating type disc brake according to any one of claims 7 to 8.

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