WO2022014712A1 - Guide plate assembly and disc brake friction pad assembly - Google Patents

Guide plate assembly and disc brake friction pad assembly Download PDF

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Publication number
WO2022014712A1
WO2022014712A1 PCT/JP2021/026883 JP2021026883W WO2022014712A1 WO 2022014712 A1 WO2022014712 A1 WO 2022014712A1 JP 2021026883 W JP2021026883 W JP 2021026883W WO 2022014712 A1 WO2022014712 A1 WO 2022014712A1
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WO
WIPO (PCT)
Prior art keywords
plate
guide plate
assembly
lining
friction pad
Prior art date
Application number
PCT/JP2021/026883
Other languages
French (fr)
Japanese (ja)
Inventor
祐一 岡田
優子 荒井
Original Assignee
曙ブレーキ工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 曙ブレーキ工業株式会社 filed Critical 曙ブレーキ工業株式会社
Publication of WO2022014712A1 publication Critical patent/WO2022014712A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
    • B61H5/00—Applications or arrangements of brakes with substantially radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes

Definitions

  • the present invention relates to a guide plate assembly and a friction pad assembly for disc brakes.
  • a disc brake device for a railroad vehicle As a disc brake device for a railroad vehicle, a disc rotor fixed to an axle, a disc brake friction pad assembly arranged facing the disc rotor, and a disc brake friction pad assembly are directed toward the disc rotor.
  • Those equipped with a brake caliper that has a built-in actuator that drives forward and backward and is fixed to the vehicle body frame are used.
  • Such a friction pad assembly for disc brakes includes a lining holder attached to a brake caliper and a lining carrier plate (guide plate) attached to the lining holder and to which a lining element (lining assembly) is attached to the surface on the disc rotor side.
  • a brake lining guide plate assembly
  • the lining element arranged on the lining carrier plate has a friction lining (friction material), and the friction lining is attached to the carrier element (back plate portion).
  • the carrier elements are individually attached to the lining carrier plate with pins or the like.
  • the lining carrier plate to which the lining element is assembled serves as a transmission member for the pressing force and the braking torque at the time of braking. Therefore, it is necessary to give the lining carrier plate sufficient strength, which is a factor that increases the mass of the lining carrier plate.
  • the brake lining is configured such that the carrier element (back plate portion) to which the friction lining is attached by sintering or the like is held by a pin or the like on the lining carrier plate. Therefore, in the brake lining in which the lining element is assembled to the lining carrier plate, the thickness of the entire brake lining is thick.
  • the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a lightweight and compact guide plate assembly and a friction pad assembly for a disc brake.
  • the above object according to the present invention is achieved by the following configuration.
  • (1) It has a guide plate that receives braking torque, a friction material that comes into contact with the disc rotor during braking, and a back plate portion that is fixed to the back surface of the friction material, and can swing freely in the guide hole portion of the guide plate.
  • a guide plate assembly provided on the back surface side and provided with a convex portion for swingably supporting the lining assembly pressed against the disc rotor by the lining holder.
  • the lining assembly swingably supported by the guide hole portion of the guide plate is via the convex portion provided on the back surface side of the back plate portion. It is pressed against the disc rotor by the lining holder. That is, the pressing force during braking by the lining holder is directly transmitted to the disc rotor by the lining assembly. Therefore, the pressing force at the time of braking is not transmitted to the guide plate, and only the braking torque is transmitted. Therefore, it is not necessary for the guide plate to have a large strength capable of supporting the pressing force at the time of braking, and the weight of the guide plate can be reduced.
  • the lining assembly is held by the guide plate so as to be movable in the rotor axial direction and not to fall off by the fall-off prevention mechanism. Therefore, in the guide plate assembly of this configuration, a plurality of lining assemblies can be assembled on the guide plate. Therefore, the handling of the guide plate assembly becomes easy and the maintainability is improved.
  • the guide is formed by forming and fitting the plate fitting portion of the back plate portion and the guide hole portion in a non-circular shape.
  • a guide plate assembly that prevents the lining assembly from rotating in the holes.
  • the detent for preventing the rotation of the lining assembly is provided by the plate fitting portion and the guide hole portion of the back plate portion formed in a non-circular shape. Achieved by mating. Therefore, it is possible to prevent the lining assembly from rotating without increasing the number of parts. That is, when the lining assembly rotates, it becomes impossible to apply a sufficient braking force to the disc rotor, so it is desirable to make the lining assembly non-rotatable with respect to the guide plate.
  • the detent for preventing the rotation of the lining assembly is a flat surface formed on the outer peripheral surface of the plate fitting portion and the inner peripheral surface of the guide hole portion. It is achieved by engaging with each other. Therefore, it is possible to easily form a detent for the lining assembly without increasing the number of parts.
  • the spring member when the spring member is arranged between the surface of the guide plate and the back plate portion, it is attached to the convex portion of the back plate portion and the lining holder or the lining holder. A gap is created between the torque receiving plate and the torque receiving plate. As a result, the spring member is elastically deformed to absorb the dimensional tolerance in the thickness direction of the lining assembly, and rattling of the lining assembly is prevented. Therefore, in the guide plate assembly of this configuration, it is possible to prevent variations in the contactability of each lining assembly with respect to the disc rotor, and it is possible to suppress the generation of abnormal noise. Therefore, each lining assembly can maintain stable braking characteristics without being affected by dimensional tolerances in the thickness direction.
  • the convex portion of the back plate portion is pressed against the lining holder or the torque receiving plate by the urging force of the spring member, and the brake is applied.
  • the responsiveness of is improved.
  • a retaining flange portion having an outer diameter larger than that of the guide hole portion is integrally formed on the front surface side of the back plate portion, and the lock plate is attached to the back surface of the back plate portion. Be done. Therefore, the lining assembly inserted through the guide hole can be held so as to be movable in the rotor axial direction and not to come off. Therefore, the fall-out prevention mechanism can be easily configured.
  • the convex portion provided on the back surface side of the back plate portion is composed of a joint member for fixing the lock plate to the back surface of the back plate portion. Therefore, by press-fitting the joint member into the back surface side of the back plate portion to fix the lock plate, the lining assembly inserted through the guide hole portion is held so as not to fall off, and is convex to the back surface side of the back plate portion.
  • the unit can be easily configured.
  • the lock plate can be easily fixed to the back surface of the back plate portion by an inexpensive rivet.
  • the lock plate can be easily fixed to the back surface of the back plate portion by the blind rivet.
  • the guide plate assembly in which the lock plate is fixed by the blind rivet does not need to provide the rivet recess for fixing the rivet in the friction material, and the contact area of the friction material with the disc rotor does not decrease.
  • the convex portion made of a joint member for fixing the lock plate to the back surface of the back plate portion by eyelets at the tip penetrating the back plate portion.
  • the lock plate is easily fixed to the back surface of the back plate portion by the joint member having eyelets at the tip. Therefore, the guide plate assembly of the present configuration can hold the lining assembly inserted through the guide hole portion so as not to fall off, and can easily form a convex portion on the back surface side of the back plate portion.
  • the vibration propagating between the lining assembly and the lining holder is damped by the damping layer.
  • the damping layer contributes to the reduction of noise due to the contact between the lining holder and the convex portion of the back plate portion.
  • the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
  • the damping layer in the guide plate assembly, the handling by hand is improved.
  • a friction pad assembly for a disc brake characterized in that the lining holder is provided with a lining holder that swingably supports the convex portion on the surface thereof.
  • the guide plate assembly in which a plurality of lining assemblies are assembled on the guide plate is detachably held by the lining holder. Therefore, in the disc brake friction pad assembly of the present configuration, it becomes easy to replace the plurality of lining assemblies assembled in the guide plate assembly, and the maintainability is improved.
  • the guide plate assembly in which a plurality of lining assemblies are assembled on the guide plate is detachably held by the torque receiving plate having the anchor plate. .. Therefore, in the disc brake friction pad assembly of the present configuration, the anchor plate of the torque receiving plate can be inserted into the dovetail groove-shaped fixing groove of the lining holder. As a result, in the disc brake friction pad assembly of the present configuration, a plurality of types of guide plate assemblies having different guide plate shapes can be detachably attached to the lining holder.
  • the guide plate assembly fixed to the lining holder via the anchor pin can be replaced simply by removing the anchor pin. Therefore, the disc brake friction pad assembly of this configuration can reduce the weight of replacement parts and improve maintainability.
  • the anchor plate is fixed to the fixing portion of the lining holder by the anchor plate fixing member with respect to the torque receiving plate fixed via the anchor pin.
  • the guide plate assembly can be replaced by simply removing the anchor pin. Therefore, the disc brake friction pad assembly of this configuration can reduce the weight of replacement parts and improve maintainability.
  • the disc brake friction pad assembly having the configuration of (15) above, the anchor pin engaging portion that receives the braking torque facing the braking direction is formed in a semicircular shape. Therefore, the disc brake friction pad assembly of the present configuration can suppress the size of the guide plate from becoming larger than that in the case where the anchor pin engaging portion is formed in a circular shape.
  • the anchor pin engaging portion is formed in a circular shape, so that the anchor pin engaging portion receives braking torque facing each braking direction. Can receive.
  • the circular anchor pin engaging portion is located on the upper side in the vertical direction when attached to the brake caliper, the anchor pin arranged on the upper side in the vertical direction must also be attached / detached when attaching / detaching the guide plate assembly. The workability is not good.
  • the circular anchor pin engaging portion is located on the lower side in the vertical direction, and the semicircular anchor pin engaging portion is located on the upper side in the vertical direction. It is only necessary to attach / detach the anchor pin arranged on the lower side in the direction, which facilitates the attachment / detachment work.
  • the vibration propagating between the lining assembly and the lining holder is damped by the damping layer. Will be done.
  • the damping layer contributes to the reduction of noise due to the contact between the lining holder and the convex portion of the back plate portion. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
  • the vibration propagating between the lining assembly and the torque receiving plate is a damping layer. Is attenuated by.
  • the damping layer contributes to the reduction of noise due to the contact between the torque receiving plate and the convex portion of the back plate portion. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
  • a damping layer facing the convex portion is provided on the surface side of the lining holder, and the damping layer is a circle.
  • a damping layer facing the convex portion is provided on the surface side of the torque receiving plate, and the damping layer is provided with the damping layer.
  • the damping layer is formed on the lining holder or the torque receiving plate by penetrating the anchor pin engagement hole of the damping layer through the anchor pin. It is fixed.
  • the damping layer is fixed to the lining holder or the torque receiving plate by the fastening member.
  • the damping layer is fixed to the lining holder or the torque receiving plate by an adhesive.
  • the guide plate assembly and the friction pad assembly for disc brakes it is possible to realize a lightweight and compact guide plate assembly and a friction pad assembly for disc brakes.
  • FIG. 1 is a perspective view of the guide plate assembly according to the first embodiment of the present invention as viewed from the front side.
  • FIG. 2 is a perspective view of the guide plate assembly shown in FIG. 1 as viewed from the back side.
  • FIG. 3A is a cross-sectional view of the lining assembly shown in FIG. 1
  • FIG. 3B is an exploded perspective view of the lining assembly shown in FIG.
  • FIG. 4 is an exploded perspective view of a main part for explaining a lining assembly attached to the guide plate shown in FIG. 5 (a) and 5 (b) are a cross-sectional view of a main part and an exploded perspective view of the main part for explaining a modified example of the lining assembly shown in FIG.
  • FIG. 6 (a) to 6 (c) are a front view, a cross-sectional view taken along the line AA, and an exploded perspective view for explaining another modification of the lining assembly shown in FIG. 1, and FIG. 6 (d) is shown in FIG. Is a perspective view illustrating the joint member shown in FIG. 6 (c).
  • 7 (a) and 7 (b) are a front view and a sectional view taken along the line BB for explaining another modification of the lining assembly shown in FIG. 1, and FIG. 7 (c) is shown in FIG. It is sectional drawing for demonstrating another modification of the lining assembly shown.
  • 8 (a) and 8 (b) are a front view and a sectional view taken along the line CC for explaining another modification of the lining assembly shown in FIG.
  • FIG. 9 (a) and 9 (b) are a perspective view of the torque receiving plate according to the second embodiment of the present invention as viewed from the front side and a perspective view as viewed from the back side.
  • FIG. 10 is a perspective view of the torque receiving plate according to the second embodiment and the guide plate assembly according to the first embodiment.
  • FIG. 11A is a perspective view of a friction pad assembly for a disc brake in which the guide plate assembly according to the first embodiment is assembled to the torque receiving plate according to the second embodiment as viewed from the front side.
  • 11 (b) is a cross-sectional view taken along the line DD of FIG. 11 (a).
  • FIG. 12 is a schematic perspective view illustrating a state in which the disc brake friction pad assembly shown in FIG. 11 is assembled to the lining holder.
  • FIG. 13 is a cross-sectional view taken along the line EE in FIG.
  • FIG. 14 is a perspective view showing a guide plate assembly according to a modification of the first embodiment shown in FIG. 1.
  • 15 (a) and 15 (b) are a perspective view of the lining holder according to the third embodiment of the present invention as viewed from the front side and a perspective view as viewed from the back side.
  • FIG. 16 is a perspective view of a friction pad assembly for a disc brake in which the guide plate assembly according to the first embodiment is assembled to the lining holder according to the third embodiment as viewed from the front side.
  • FIG. 17 is a perspective view of the guide plate assembly according to the fourth embodiment of the present invention as viewed from the back side.
  • FIG. 18 is an exploded perspective view of the guide plate assembly shown in FIG.
  • FIG. 19A is a perspective view of the torque receiving plate according to the fifth embodiment of the present invention as viewed from the front side
  • FIG. 19B is a torque receiving plate according to a modified example of the fifth embodiment. It is a perspective view seen from the front side.
  • FIG. 20A is a perspective view of the lining holder according to the sixth embodiment of the present invention as viewed from the front side
  • FIG. 20B is a perspective view of the lining holder according to the modified example of the sixth embodiment from the front side. It is a perspective view as seen.
  • the disc brake friction pad assembly (hereinafter, simply referred to as “friction pad assembly”) provided with the guide plate assembly according to the present embodiment is used for a disc brake device for a railroad vehicle.
  • the disc brake friction pad assembly is arranged facing the disc rotor on the axle, and is driven forward and backward toward the disc rotor by an actuator built in the brake caliper fixed to the vehicle body frame.
  • the friction pad assembly for disc brakes of the present invention is not limited to the disc brake device for railway vehicles.
  • FIG. 1 and 2 are perspective views of the guide plate assembly 1 according to the first embodiment of the present invention as viewed from the front side and the back side.
  • 3A is a cross-sectional view of the lining assembly 10 shown in FIG. 1
  • FIG. 3B is an exploded perspective view of the lining assembly 10 shown in FIG.
  • FIG. 4 is an exploded perspective view of a main part for explaining the lining assembly 10 attached to the guide plate 3 shown in FIG.
  • the guide plate assembly 1 has at least swingably supported by a guide plate 3 that receives braking torque and a guide hole portion 5 of the guide plate 3. It includes one (20 in this embodiment) lining assembly 10.
  • the guide plate 3 has a plurality of (20 holes) of guide holes 5 formed at predetermined spacing intervals, and the lining assembly 10 is mounted on each guide hole 5.
  • the guide plate 3 is formed of a flat plate material having a predetermined plate thickness capable of receiving the braking torque acting on the lining assembly 10 mounted on each guide hole portion 5 at the time of braking.
  • An anchor pin engaging portion 7 formed in a semicircular shape is formed at the upper end portion in the longitudinal direction of the guide plate 3 located on the upper side in the vertical direction when attached to a brake caliper (not shown). Further, an anchor pin engaging portion 9 formed in a circular shape is formed at the lower end portion in the longitudinal direction of the guide plate 3 located on the lower side in the vertical direction when attached to the brake caliper.
  • the lining assembly 10 is swingably supported by a guide plate 3 that receives braking torque, and is pressed against the disc rotor by the lining holder 140 (301) described later.
  • the lining assembly 10 has a friction material 11 molded in a substantially disk shape, a back plate portion 12 fixed to the back surface of the friction material 11, and a back plate portion 12 on the back surface side.
  • a convex portion 20 for swingably supporting the lining assembly 10 provided and pressed against the disc rotor by the lining holder 140 (301) and a lining assembly 10 inserted through the guide hole portion 5 are provided in the rotor axial direction. It is equipped with a fall-out prevention mechanism for holding the X so that it can be moved and does not fall off.
  • the friction material 11 is pressed against the disc rotor during braking.
  • the plate fitting portion 15 is fitted to the guide hole portion 5, so that the braking torque acting when the friction material 11 is pressed against the disc rotor is applied from the plate fitting portion 15 to the guide plate 3 Communicate to.
  • the back plate portion 12 has a plate fitting portion 15 that swingably fits into a substantially circular guide hole portion 5 whose outer peripheral surface is formed through the guide plate 3, and is located on the surface side of the back plate portion 12.
  • a retaining flange portion 13 having an outer diameter larger than that of the guide hole portion 5 is integrally formed.
  • a flat surface 16 is formed on the outer peripheral surface of the plate fitting portion 15, and a flat surface 6 is formed on the inner peripheral surface of the guide hole portion 5 as shown in FIG. Is formed. Therefore, the flat surface 16 of the plate fitting portion 15 inserted into the guide hole portion 5 engages with the flat surface 6 of the guide hole portion 5.
  • the lining assembly in the guide hole portion 5 is formed by fitting the plate fitting portion 15 and the guide hole portion 5 of the back plate portion 12 formed in a non-circular shape by the flat surface 16 and the flat surface 6.
  • a detent is achieved to prevent the rotation of 10. It is desirable that the plate fitting portion 15 is formed in a convex curved surface shape on the guide hole portion 5 side so that the lining assembly 10 can be smoothly swung by sliding contact with the guide hole portion 5. ..
  • a circular plate-shaped lock plate 17 having an outer shape larger than the opening shape of the guide hole portion 5 is fixed to the back surface of the back plate portion 12.
  • the lock plate 17 has a flanged pin shape that penetrates the through hole 17a through the fixing hole 14 provided on the back surface of the back plate portion 12 after the plate fitting portion 15 is inserted into the guide hole portion 5 of the guide plate 3.
  • the joint member 22 is fixed to the back surface of the back plate portion 12.
  • the head of the joint member 22 protruding toward the back surface of the back plate portion 12 is a convex portion 20 for swingably supporting the lining assembly 10.
  • the lining assembly 10 inserted into the guide hole portion 5 from the front surface 3a side of the guide plate 3 has a retaining flange portion 13 of the back plate portion 12.
  • the guide plate 3 is held so as to be movable in the rotor axial direction X and not to fall off. That is, the fall-out prevention mechanism is composed of the retaining flange portion 13 and the lock plate 17.
  • annular spring member 25 is fitted to the plate fitting portion 15.
  • the spring member 25 is made of an annular leaf spring.
  • the outer diameter of the spring member 25 is set to be larger than that of the guide hole portion 5.
  • each lining assembly 10 has a plate fitting portion 15 inserted and mounted in the guide hole portion 5 from the surface 3a side of the guide plate 3. Therefore, the spring member 25 fitted to the plate fitting portion 15 is sandwiched between the guide plate 3 and the retaining flange portion 13.
  • the guide plate assembly 1 has a form in which a plurality of lining assemblies 10 are laid out in a plane.
  • the spring member 25 sandwiched between the retaining flange portion 13 of the lining assembly 10 and the guide plate 3 elastically deforms to absorb the dimensional tolerance in the thickness direction of the lining assembly 10. .. Therefore, in the guide plate assembly 1, it is possible to prevent variations in the contact property of each lining assembly 10 with respect to the disc rotor. Therefore, each lining assembly 10 can maintain stable braking characteristics without being affected by dimensional tolerances in the thickness direction.
  • a convex portion 20 is provided on the back surface side of the back plate portion 12. Therefore, the lining assembly 10 swingably supported by the guide hole portion 5 of the guide plate 3 is disced by the lining holder 140 (301) via the convex portion 20 provided on the back surface side of the back plate portion 12. Pressed against the rotor.
  • the lining assembly 10 swingably supported by the guide hole portion 5 of the guide plate 3 is provided on the back surface side of the back plate portion 12. It is pressed against the disc rotor by the lining holder 140 (301) via the convex portion 20. Then, the pressing force at the time of braking by the lining holder 140 (301) is directly transmitted to the disc rotor by the lining assembly 10. Therefore, the pressing force at the time of braking is not transmitted to the guide plate 3, and only the braking torque is transmitted. Therefore, it is not necessary for the guide plate 3 to have a large strength capable of supporting the pressing force at the time of braking, and the weight of the guide plate 3 can be reduced.
  • the lining assembly 10 according to the first embodiment is guided by a fall-out prevention mechanism including a retaining flange portion 13 of the back plate portion 12 and a lock plate 17 so as to be movable in the rotor axial direction X and not to come off. It is held on the plate 3. Therefore, in the guide plate assembly 1 of the first embodiment, a plurality of lining assemblies 10 can be assembled to the guide plate 3. Therefore, the guide plate assembly 1 can be easily handled and maintainability is improved.
  • the plate fitting portion 15 and the guide hole portion 5 of the back plate portion 12 are each formed in a non-circular shape and fitted into the guide hole portion.
  • the rotation of the lining assembly 10 within 5 is prevented. More specifically, on the outer peripheral surface of the plate fitting portion 15 and the inner peripheral surface of the guide hole portion 5, a flat surface 16 and a flat surface for preventing rotation of the lining assembly 10 in the guide hole portion 5 are prevented from rotating. 6 are formed respectively. Therefore, according to the guide plate assembly 1 according to the first embodiment, the detent for preventing the rotation of the lining assembly 10 is provided on the outer peripheral surface of the plate fitting portion 15 and the inner peripheral surface of the guide hole portion 5.
  • the detent of the lining assembly 10 can be easily formed without increasing the number of parts. That is, when the lining assembly 10 rotates, it becomes impossible to apply a sufficient braking force to the disc rotor, so it is desirable to make the lining assembly 10 non-rotatable with respect to the guide plate 3.
  • the lining assembly 10 is placed between the surface 3a of the guide plate 3 and the retaining flange portion 13 of the back plate portion 12 with respect to the guide plate 3.
  • a spring member 25 for urging is arranged on the disc rotor side (left side in FIG. 3A), which is one of the two along the rotor axial direction X. Therefore, according to the guide plate assembly 1 according to the first embodiment, the spring member 25 is arranged between the surface 3a of the guide plate 3 and the back plate portion 12.
  • each lining assembly 10 can maintain stable braking characteristics without being affected by dimensional tolerances in the thickness direction.
  • the convex portion 20 provided on the back surface side of the back plate portion 12 is provided with a joint member 22 for fixing the lock plate 17 to the back surface of the back plate portion 12. It is composed. That is, in the joint member 22, the head protruding toward the back surface side of the back plate portion 12 becomes a convex portion 20 for swingably supporting the lining assembly 10. Therefore, by press-fitting the joint member 22 into the fixing hole 14 provided on the back surface of the back plate portion 12 to fix the lock plate 17, the lining assembly 10 inserted through the guide hole portion 5 is held so as not to fall off. At the same time, the convex portion 20 can be easily formed on the back surface side of the back plate portion 12.
  • 5 (a) and 5 (b) are a cross-sectional view of a main part and an exploded perspective view of the main part for explaining a modified example of the lining assembly 10 shown in FIG.
  • the lining assembly 10 according to the modified example is between the back surface 3b of the guide plate 3 and the lock plate 17 fixed to the back surface of the back plate portion 12.
  • a spring member 25 for urging the lining assembly 10 with respect to the guide plate 3 on the opposite side (right side in (a) of FIG. 5) to the disc rotor which is the other side along the rotor axial direction X. can.
  • the spring member 25 is arranged between the back surface 3b of the guide plate 3 and the back plate portion 12. Therefore, in the guide plate assembly 1 having this configuration, the convex portion 20 of the back plate portion 12 is pressed against the lining holder 301 or the torque receiving plate 101, which will be described later, by the urging force of the spring member 25, and the responsiveness at the time of braking is achieved. Is improved.
  • FIG. 6A to 6C are a front view, a sectional view taken along the line AA, and an exploded perspective view for explaining another modification of the lining assembly 10 shown in FIG. 1, and FIG. 6D is an exploded perspective view. It is a perspective view explaining the joint member 32 shown in (c).
  • the same components as those of the lining assembly 10 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • the lining assembly 10A backs the lock plate 17 with eyelets 33 at the tip penetrating the stepped fixing hole 14A of the back plate portion 12. It has a convex portion 20 made of a joint member 32 fixed to the back surface of the plate portion 12. As shown in FIG. 6D, the joint member 32 has an opening 11a formed in the friction material 11 after the shaft portion is inserted into the through hole 17a of the lock plate 17 and the stepped fixing hole 14 of the back plate portion 12. A jig is inserted from the side, and the eyelet 33 at the tip is bent outward to be locked to the step portion. Therefore, in the joint member 32, the lock plate 17 is fixed to the back surface of the back plate portion 12, and the head projecting to the back surface side of the back plate portion 12 is convex for swingably supporting the lining assembly 10A. It becomes part 20.
  • the lock plate 17 is easily fixed to the back surface of the back plate portion 12 by the joint member 32 having the eyelet 33 at the tip. Therefore, the lining assembly 10A having the present configuration can hold the lining assembly 10A inserted through the guide hole portion 5 so as not to fall off, and can easily form the convex portion 20 on the back surface side of the back plate portion 12. can.
  • FIG. 7 (a) and 7 (b) are a front view and a sectional view taken along the line BB for explaining another modification of the lining assembly 10 shown in FIG. 1, and FIG. 7 (c) is shown in FIG. It is sectional drawing for demonstrating another modification of a lining assembly 10.
  • the same components as those of the lining assembly 10 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • the convex portion 20 provided on the back surface side of the back plate portion 12 is composed of the joint member 43. ..
  • the joint member 43 has a disk-shaped base portion 43a placed in the recess 12a of the back plate portion 12 and a pin-shaped shaft portion 43b penetrating through the through hole 17a of the lock plate 17 having a diameter smaller than that of the base portion 43a. ..
  • the joint member 43 is formed by placing the base portion 43a in the recess 12a of the back plate portion 12 and then fixing the lock plate 17 through which the shaft portion 43b is inserted into the through hole 17a to the back surface of the back plate portion 12. It is fixed to the back surface side of the portion 12. That is, in the joint member 43, the shaft portion 43b protruding toward the back surface side of the back plate portion 12 becomes a convex portion 20 for swingably supporting the lining assembly 10B.
  • the lock plate 17 having this configuration is fixed to the back surface of the back plate portion 12 by a rivet 45 penetrating the fixing hole 17b of the lock plate 17 and the fixing hole 14 of the back plate portion 12. Therefore, the lock plate 17 can be easily fixed to the back surface of the back plate portion 12 by an inexpensive rivet 45.
  • the friction material 11 needs to be provided with a rivet recess 18 for fixing the rivet 45.
  • the convex portion 20 provided on the back surface side of the back plate portion 12 has a joint member 43 similar to the lining assembly 10B. It is composed of.
  • the lock plate 17 of the lining assembly 10C is fixed to the back surface of the back plate portion 12 by a blind rivet 53 penetrating the fixing hole 17b of the lock plate 17 and the fixing hole 14 of the back plate portion 12.
  • the lining assembly 10C to which the lock plate 17 is fixed by the blind rivet 53 does not need to provide the rivet recess 18 for fixing the rivet 45 in the friction material 11 as in the lining assembly 10B, and is a disc rotor.
  • the contact area of the friction material 11 with respect to the rivet 11 does not decrease.
  • the lining assembly 10D is a friction material 11 molded into a substantially disk shape having an outer diameter through which the guide hole portion 5 can be inserted.
  • the back plate portion 12A fixed to the back surface of the friction material 11 and the lining assembly 10D provided on the back surface side of the back plate portion 12A and pressed against the disc rotor by the lining holder 140 (301) can be swung.
  • a convex portion 20 for supporting the lining and a fall-off prevention mechanism for holding the lining assembly 10D inserted through the guide hole portion 5 so as to be movable in the rotor axial direction X and not to fall off.
  • the convex portion 20 is composed of a head of a joint member 22 that is press-fitted into a fixing hole 14 provided on the back surface of the back plate portion 12A and projects toward the back surface side. Since the joint member 22 is formed separately from the back plate portion 12A, the optimum material having excellent wear resistance and the like is selected as the convex portion 20 for swingably supporting the lining assembly 10D. be able to.
  • the back plate portion 12A is located on the back surface side of the back plate portion 12A and the plate fitting portion 15 which swingably fits into the substantially circular guide hole portion 5 whose outer peripheral surface is formed through the guide plate 3.
  • a retaining flange portion 13 having an outer diameter larger than that of the guide hole portion 5 is integrally formed.
  • An annular groove 19 on which the snap ring 51 is mounted is formed on the outer peripheral surface of the plate fitting portion 15.
  • the annular groove 19 of the plate fitting portion 15 in the back plate portion 12A has an outer shape larger than the opening shape of the guide hole portion 5, and a snap ring 51 having an inner shape smaller than the outer diameter of the plate fitting portion 15. Is installed.
  • a snap ring 51 is attached to the annular groove 19 of the plate fitting portion 15 in the back plate portion 12A. Therefore, the lining assembly 10D inserted into the guide hole portion 5 from the back surface 3b side of the guide plate 3 is in the rotor axial direction with respect to the guide plate 3 by the retaining flange portion 13 of the back plate portion 12A and the snap ring 51. It is movable to X and is held so that it will not fall out. That is, the fall-off prevention mechanism is composed of the retaining flange portion 13 and the snap ring 51.
  • the spring member 25 fitted to the plate fitting portion 15 is sandwiched between the guide plate 3 and the snap ring 51 and elastically deformed to absorb the dimensional tolerance in the thickness direction of the lining assembly 10D.
  • FIG. 9 (a) and 9 (b) are a perspective view of the torque receiving plate 101 according to the second embodiment of the present invention as viewed from the front side and a perspective view as viewed from the back side.
  • FIG. 10 is a perspective view of the torque receiving plate 101 according to the second embodiment and the guide plate assembly 1 according to the first embodiment.
  • FIG. 11A is a perspective view of the disc brake friction pad assembly 100 in which the guide plate assembly 1 according to the first embodiment is assembled to the torque receiving plate 101 according to the second embodiment.
  • 11 (b) is a cross-sectional view taken along the line DD of FIG. 11 (a).
  • the torque receiving plate 101 As shown in FIGS. 9A and 9B, the torque receiving plate 101 according to the second embodiment is fitted to the peripheral edge portion of the guide plate 3 to detachably hold the guide plate assembly 1. A plurality of grooves 105 are provided. Then, the torque receiving plate 101 swingably supports the convex portion 20 of the lining assembly 10 on the surface 101a.
  • the back surface 101b of the torque receiving plate 101 is provided with an anchor plate 120 that is inserted from the groove end into a lining holder 140 (see FIG. 13) provided with a dovetail groove-shaped fixing groove 141.
  • a pair of anchor pin fitting portions 110 formed in circular holes are formed at both ends of the torque receiving plate 101 in the longitudinal direction.
  • the peripheral edge portion of the guide plate 3 is fitted into the groove 105 from one end side in the longitudinal direction of the torque receiving plate 101.
  • FIG. 11 (a) As shown in (b), the back surface 3b of the guide plate 3 is overlapped so as to face the surface 101a of the torque receiving plate 101, whereby the disc brake friction pad assembly 100 is configured.
  • the guide plate 3 held in the groove portion 105 of the torque receiving plate 101 has an inside that allows the lining assembly 10 to swing between the surface 101a and the surface 101a of the torque receiving plate 101.
  • the space S is defined.
  • the anchor pins 130 fitted into the pair of anchor pin fitting portions 110 of the torque receiving plate 101 penetrate the anchor pin engaging portion 9 of the guide plate 3 and the anchor pin engaging portion. By engaging with 7, it is fixed to the torque receiving plate 101.
  • FIG. 12 is a schematic perspective view illustrating a state in which the disc brake friction pad assembly 100 shown in FIG. 11 is assembled to the lining holder 140.
  • FIG. 13 is a cross-sectional view taken along the line EE in FIG.
  • the disc brake friction pad assembly 100 is attached to the caliper lining holder 140 as shown in FIGS. 12 and 13.
  • An anchor plate 120 is fixed to the back surface 101b of the torque receiving plate 101 by rivets 133.
  • the anchor plate 120 has a groove end in a dovetail groove-shaped fixing groove 141 formed in the brake pad mounting portion 143 (disc rotor side mounting surface of the lining holder 140) in the lining holder 140. It is attached by being inserted from.
  • the back surface 101b of the torque receiving plate 101 is in close contact with the brake pad mounting portion 143 of the lining holder 140.
  • the lining assembly 10 swingably supported by the guide hole portion 5 of the guide plate 3 is pressed against the disc rotor by the lining holder 140 via the convex portion 20 provided on the back surface side of the back plate portion 12. .. Then, the pressing force during braking by the lining holder 140 is directly transmitted to the disc rotor by the lining assembly 10. Therefore, the pressing force at the time of braking is not transmitted to the guide plate 3, and only the braking torque is transmitted.
  • the guide plate assembly 1 in which a plurality of lining assemblies 10 are assembled on the guide plate 3 is detachably held by the torque receiving plate 101 having the anchor plate 120. Therefore, in the disc brake friction pad assembly 100 having the present configuration, the anchor plate 120 of the torque receiving plate 101 can be inserted into the dovetail groove-shaped fixing groove 141 of the lining holder 140. As a result, in the disc brake friction pad assembly 100 having the present configuration, a plurality of types of guide plate assemblies 1 having different shapes of the guide plates 3 can be detachably attached to the lining holder 140.
  • the plate fitting portion 15 of the back plate portion 12 is inserted and mounted in the guide hole portion 5 of the guide plate 3, and the braking torque acting when the disc rotor and the friction material 11 come into contact with each other is generated. It is transmitted from the plate fitting portion 15 to the guide plate 3, and further transmitted from the anchor pin engaging portions 7 and 9 of the guide plate 3 to the anchor pin fitting portion 110 of the torque receiving plate 101 by the anchor pin 130, and further transmitted to the anchor pin fitting portion 110 of the torque receiving plate 101. It is transmitted from the anchor plate 120 of 101 to the brake pad mounting portion 143 which is the fixing portion of the lining holder 140 by the anchor plate fixing member 145.
  • the guide plate assembly 1 fixed via the anchor pin 130 to the torque receiving plate 101 in which the anchor plate 120 is fixed to the brake pad mounting portion 143 of the lining holder 140 by the anchor plate fixing member 145 is an anchor. It can be replaced simply by removing the pin 130. Therefore, the disc brake friction pad assembly 100 can reduce the weight of replacement parts and improve maintainability.
  • the anchor pin engaging portion 7 of the guide plate 3 facing the braking direction and receiving the braking torque is formed in a semicircular shape. Therefore, the disc brake friction pad assembly 100 can prevent the guide plate 3 from becoming larger than the anchor pin engaging portion 9 formed in a circular shape.
  • the anchor pin engaging portion located on the lower side in the vertical direction when attached to the brake caliper. 9 is formed in a circular shape and receives a braking torque. Therefore, according to the disc brake friction pad assembly 100, the anchor pin engaging portion 9 is formed in a circular shape, so that the anchor pin engaging portion 9 receives braking torque facing each braking direction. Can be done.
  • the anchor pin 130 arranged on the upper side in the vertical direction is also attached / detached when attaching / detaching the guide plate assembly 1. It has to be, and workability is not good.
  • the circular anchor pin engaging portion 9 is located on the lower side in the vertical direction, and the semicircular anchor pin engaging portion 7 is located on the upper side in the vertical direction. It is only necessary to attach / detach the anchor pin 130 arranged on the lower side in the vertical direction, which facilitates the attachment / detachment work. It is also possible to omit the anchor pin engaging portion 7 on the upper side in the vertical direction and receive the braking torque only on the anchor pin engaging portion 9 on the lower side in the vertical direction.
  • FIG. 14 is a perspective view showing the guide plate assembly 1A according to the modified example of the first embodiment shown in FIG.
  • the same components as those of the guide plate assembly 1 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • a pair of anchor pin engaging portions 7 and 7 formed at both ends in the longitudinal direction of the guide plate 3A are formed in a semicircular shape, respectively. Therefore, the guide plate assembly 1A can be made smaller and lighter than the guide plate assembly 1.
  • FIG. 15 (a) and 15 (b) are a perspective view of the lining holder 301 according to the third embodiment of the present invention as viewed from the front side and a perspective view as viewed from the back side.
  • FIG. 16 is a perspective view of a disc brake friction pad assembly 200 in which the guide plate assembly 1 according to the first embodiment is assembled to the lining holder 301 according to the third embodiment as viewed from the front side.
  • the lining holder 301 As shown in FIGS. 15A and 15B, the lining holder 301 according to the third embodiment is fitted to the peripheral edge portion of the guide plate 3 to detachably hold the guide plate assembly 1. Groove 305 is provided. Then, the lining holder 301 swingably supports the convex portion 20 of the lining assembly 10 on the surface 301a. A brake pad mounting portion 320 to be mounted on the caliper is provided on the back surface 301b of the lining holder 301. A pair of anchor pin fitting portions 310 formed in circular holes are formed at both ends of the lining holder 301 in the longitudinal direction.
  • the peripheral edge portion of the guide plate 3 is fitted into the groove portion 305 from one end side in the longitudinal direction of the lining holder 301. Then, as shown in FIG. 16, the back surface 3b of the guide plate 3 is overlapped so as to face the surface 301a of the lining holder 301, whereby the disc brake friction pad assembly 200 is configured.
  • the guide plate 3 held in the groove portion 305 of the lining holder 301 defines an internal space S that allows the lining assembly 10 to swing with the surface 301a of the lining holder 301.
  • the anchor pins 130 fitted into the pair of anchor pin fitting portions 310 of the lining holder 301 penetrate the anchor pin engaging portion 9 of the guide plate 3 and the anchor pin engaging portion 7 Engage in. Therefore, the guide plate assembly 1 is fixed to the lining holder 301.
  • the lining assembly 10 swingably supported by the guide hole portion 5 of the guide plate 3 is pressed against the disc rotor by the lining holder 301 via the convex portion 20 provided on the back surface side of the back plate portion 12. .. Then, the pressing force during braking by the lining holder 301 is directly transmitted to the disc rotor by the lining assembly 10. Therefore, the pressing force at the time of braking is not transmitted to the guide plate 3, and only the braking torque is transmitted.
  • the guide plate assembly 1 in which a plurality of lining assemblies 10 are assembled on the guide plate 3 is detachably held by the lining holder 301. Therefore, in the disc brake friction pad assembly 200 having the present configuration, the guide plate assembly 1 can be easily replaced and the maintainability is improved.
  • the plate fitting portion 15 of the back plate portion 12 is inserted and mounted in the guide hole portion 5 of the guide plate 3, and the braking torque acting when the disc rotor and the friction material 11 come into contact with each other is generated. It is transmitted from the plate fitting portion 15 to the guide plate 3, and further transmitted from the anchor pin engaging portions 7 and 9 of the guide plate 3 to the anchor pin fitting portion 310 of the lining holder 301 by the anchor pin 130.
  • the guide plate assembly 1 fixed to the lining holder 301 via the anchor pin 130 can be replaced only by removing the anchor pin 130. Therefore, the disc brake friction pad assembly 200 can reduce the weight of replacement parts and improve maintainability.
  • FIG. 17 is a perspective view of the guide plate assembly 1B according to the fourth embodiment of the present invention as viewed from the back side.
  • FIG. 18 is an exploded perspective view of the guide plate assembly 1B shown in FIG.
  • the same components as those of the guide plate assembly 1A are designated by the same reference numerals, and detailed description thereof will be omitted.
  • the guide plate assembly 1B is provided with a damping layer 70 covering the convex portion 20 of the lining assembly 10 on the back surface 3b side of the guide plate 3A.
  • the damping layer 70 is formed with a uniform thickness.
  • the damping layer 70 is formed along the back surface 3b of the guide plate 3A in a shape substantially similar to that of the guide plate 3A.
  • the damping layer 70 is provided with a fixing hole 71 for fixing by the fastening member 80 via a spacer 75 provided on the back surface 3b of the guide plate 3A.
  • the surface of the damping layer 70 is a flat surface parallel to the back surface 3b of the guide plate 3A.
  • the damping layer 70 is fixed to the back surface 3b of the guide plate 3A by the fastening member 80.
  • the damping layer 70 for example, a laminated shim in which a metal support plate and an elastic material are laminated and laminated can be used, and the damping layer 70 has a laminated structure having an appropriate elastic modulus in the in-plane and in the perpendicular direction. Will be.
  • the laminated structure for example, rubber as an elastic material, a stainless steel plate as a metal support plate, an adhesive material as an elastic material, a cold-rolled steel plate as a metal support plate, and rubber as an elastic material are laminated in this order. It can be a structure.
  • the damping layer 70 is not limited to the laminated structure of the present embodiment, and noise can be reduced by damping the vibration propagating between the lining assembly 10 and the lining holder 140 (301).
  • Various laminated structures or single-layer structures can be adopted as long as they are.
  • the vibration propagating between the lining assembly 10 and the lining holder 140 (301) is a damping layer. It is attenuated by 70.
  • the damping layer 70 contributes to the reduction of noise due to the contact between the lining holder 140 (301) and the convex portion 20 of the back plate portion 12. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
  • FIG. 19A is a perspective view of the torque receiving plate 101A according to the fifth embodiment of the present invention as viewed from the front side
  • FIG. 19B is a torque receiving plate according to a modified example of the fifth embodiment. It is a perspective view which saw 101B from the front side.
  • the same components as those of the torque receiving plate 101 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • the torque receiving plate 101A is provided with a damping layer 70 facing the convex portion 20 of the lining assembly 10 on the surface 101a side.
  • the damping layer 70 is formed with a uniform thickness.
  • the damping layer 70 is formed along the surface 101a of the torque receiving plate 101A in a shape substantially similar to that of the torque receiving plate 101A.
  • the surface of the damping layer 70 is a flat surface parallel to the surface 101a of the torque receiving plate 101A.
  • the damping layer 70 is formed with an anchor pin engaging hole 73 penetrating through the anchor pin 130 penetrating the anchor pin fitting portion 110 of the torque receiving plate 101A formed in a circular shape. Therefore, the damping layer 70 is fixed to the surface 101a of the torque receiving plate 101A by the anchor pin 130.
  • the damping layer 70 is fixed to the surface 101a of the torque receiving plate 101B by the fastening member 80.
  • the damping layer 70 may be fixed to the torque receiving plate 101B with an adhesive.
  • the vibration propagating between the lining assembly 10 and the torque receiving plate 101A (101B) is generated. , It is attenuated by the damping layer 70.
  • the damping layer 70 contributes to the reduction of noise due to the contact between the torque receiving plate 101A (101B) and the convex portion 20 of the back plate portion 12. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
  • FIG. 20A is a perspective view of the lining holder 301A according to the sixth embodiment of the present invention as viewed from the front side
  • FIG. 20B is a front side view of the lining holder 301B according to the modification of the sixth embodiment. It is a perspective view seen from.
  • the same components as those of the lining holder 301 are designated by the same reference numerals, and detailed description thereof will be omitted.
  • the lining holder 301A is provided with a damping layer 70 facing the convex portion 20 of the lining assembly 10 on the surface 301a side.
  • the damping layer 70 is formed with a uniform thickness.
  • the damping layer 70 is formed along the surface 301a of the lining holder 301A in a shape substantially similar to that of the lining holder 301A.
  • the surface of the damping layer 70 is a flat surface parallel to the surface 301a of the lining holder 301A.
  • the damping layer 70 is formed with an anchor pin engaging hole 73 penetrating through the anchor pin 130 penetrating the anchor pin fitting portion 310 of the lining holder 301A formed in a circular shape. Therefore, the damping layer 70 is fixed to the surface 301a of the lining holder 301A by the anchor pin 130.
  • the damping layer 70 is fixed to the surface 301a of the lining holder 301B by the fastening member 80.
  • the damping layer 70 may be fixed to the lining holder 301B with an adhesive.
  • the present invention is not limited to the above-described embodiment, and can be appropriately modified, improved, or the like.
  • the material, shape, dimensions, number, arrangement location, etc. of each component in the above-described embodiment are arbitrary as long as the present invention can be achieved, and are not limited.
  • a guide plate assembly (1,1A, 1B) comprising a convex portion (20) for swingably supporting the lining assembly (10) pressed against.
  • the plate fitting portion (15) of the back plate portion (12) and the guide hole portion (5) are formed in a non-circular shape and fitted to each other, whereby the said in the guide hole portion (5).
  • a detent On the outer peripheral surface of the plate fitting portion (15) and the inner peripheral surface of the guide hole portion (5), a detent that prevents the lining assembly (10) from rotating in the guide hole portion (5).
  • the lining assembly (10) is placed between the front surface (3a) or the back surface (3b) of the guide plate (3) and the back plate portion (12) with respect to the guide plate (3).
  • a spring member (25) for urging any one along the axial direction (X) is arranged.
  • the fall-out prevention mechanism has a guide plate assembly (17) having an outer shape larger than the opening shape of the guide hole portion (5) and having a lock plate (17) attached to the back surface of the back plate portion (12). 1,1A, 1B). [6] The guide plate assembly according to the above [5]. A guide plate having the convex portion (20) made of a joint member (22) that fixes the lock plate (17) to the back surface of the back plate portion (12) by being press-fitted into the back plate portion (12). Assembly (1,1A, 1B). [7] The guide plate assembly according to the above [5]. A guide plate assembly (1,1A, 1B) in which the lock plate (17) is fixed to the back surface of the back plate portion (12) by a rivet (45).
  • the guide plate assembly (1,1A, 1B) according to any one of the above [1] to [10] is fitted to the peripheral portion of the guide plate (3) to form the guide plate assembly.
  • the lining holder (301, 301A, 301B) provided with a groove portion (305) for detachably holding the solid (1,1A, 1B) and swingably supporting the convex portion (20) on the surface (301a). And, a friction pad assembly for disc brakes (200).
  • the guide plate assembly (1,1A, 1B) according to any one of the above [1] to [10] is fitted to the peripheral portion of the guide plate (3) to form the guide plate assembly.
  • a torque receiving plate (101, 101A, 101B) provided with a groove portion (105) for detachably holding a solid (1,1A, 1B) and swingably supporting the convex portion (20) on the surface (101a).
  • An anchor plate is inserted from the groove end into the lining holder (140) provided on the back surface (101b) of the torque receiving plates (101, 101A, 101B) and provided with a dovetail groove-shaped fixing groove (141). (120), and a friction pad assembly for disc brakes (100). [13] The disc brake friction pad assembly according to the above [11].
  • the plate fitting portion (15) of the back plate portion (12) is inserted and mounted in the guide hole portion (5), and the braking torque acting at the time of contact between the disc rotor and the friction material (11) is the braking torque.
  • the lining holder (301, 301A) is transmitted from the plate fitting portion (15) to the guide plate (3), and further from the anchor pin engaging portion (7, 9) of the guide plate (3) by the anchor pin (130). ),
  • the friction pad assembly for disc brakes (200) transmitted to the anchor pin fitting portion (310).
  • the plate fitting portion (15) of the back plate portion (12) is inserted and mounted in the guide hole portion (5), and the braking torque acting at the time of contact between the disc rotor and the friction material (11) is the braking torque.
  • the torque is transmitted from the plate fitting portion (15) to the guide plate (3), and further from the anchor pin engaging portion (7, 9) of the guide plate (3) to the torque receiving plate (101,) by the anchor pin (130). It is transmitted to the anchor pin fitting portion (110) of 101A, 101B), and further, the lining holder (140) is transmitted from the anchor plate (120) of the torque receiving plate (101, 101A, 101B) to the anchor plate fixing member (145).
  • a disc brake friction pad assembly (200) provided with a damping layer (70) facing the convex portion (20) on the surface (301a) side of the lining holders (301A, 301B). [18] The disc brake friction pad assembly according to the above [12].
  • a disc brake friction pad assembly (100) provided with a damping layer (70) facing the convex portion (20) on the surface (101a) side of the torque receiving plates (101A, 101B). [19] The disc brake friction pad assembly according to the above [13].
  • a damping layer (70) facing the convex portion (20) is provided on the surface (301a) side of the lining holder (301A), and the damping layer (70) is formed in a circular shape.
  • the damping layer (70) is a friction pad assembly (200) for disc brakes, which is fixed to the lining holder (301B) by a fastening member (80). [22] The disc brake friction pad assembly according to the above [18].
  • the damping layer (70) is a friction pad assembly (100) for disc brakes, which is fixed to the torque receiving plate (101B) by a fastening member (80). [23] The disc brake friction pad assembly according to the above [17].
  • the damping layer (70) is a friction pad assembly (200) for disc brakes, which is fixed to the lining holder (301A) by an adhesive. [24] The disc brake friction pad assembly according to the above [18].
  • the damping layer (70) is a friction pad assembly (100) for disc brakes, which is fixed to the torque receiving plate (101A) by an adhesive.
  • the guide plate assembly and the friction pad assembly for disc brakes of the present invention it is possible to realize a lightweight and compact guide plate assembly and a friction pad assembly for disc brakes.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

The present invention provides a guide plate assembly comprising a guide plate (3), a lining assembly (10) which includes a friction material (11) that contacts a disc rotor when braking and a backplate (12) affixed to the back surface of the friction material (11) and which is swingably supported on a guide hole (5) of the guide plate (3), a fall-off prevention mechanism for holding the lining assembly (10) inserted into the guide hole (5) so as to allow the lining assembly (10) to move in a rotor axis direction (X) without falling off, and a projection (20), provided on the back side of the backplate (12), for swingably supporting the lining assembly (10) pressed against the disc rotor by a lining holder.

Description

ガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体Guide plate assembly and friction pad assembly for disc brakes
　本発明は、ガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体に関する。 The present invention relates to a guide plate assembly and a friction pad assembly for disc brakes.
　鉄道車両用のディスクブレーキ装置としては、車軸に固定されるディスクロータと、このディスクロータに対峙して配置されるディスクブレーキ用摩擦パッド組立て体と、ディスクブレーキ用摩擦パッド組立て体をディスクロータに向かって進退駆動するアクチュエータを内蔵して車体フレームに固定されるブレーキキャリパとを備えるものが使用されている。 As a disc brake device for a railroad vehicle, a disc rotor fixed to an axle, a disc brake friction pad assembly arranged facing the disc rotor, and a disc brake friction pad assembly are directed toward the disc rotor. Those equipped with a brake caliper that has a built-in actuator that drives forward and backward and is fixed to the vehicle body frame are used.
　このようなディスクブレーキ用摩擦パッド組立て体には、ブレーキキャリパに取付けられるライニングホルダと、ライニングホルダに取付けられてディスクロータ側の面にライニング要素（ライニング組立体）を組み付けたライニングキャリアプレート（ガイドプレート）とを有するブレーキライニング（ガイドプレート組立体）を備えたものがある（特許文献１参照）。 Such a friction pad assembly for disc brakes includes a lining holder attached to a brake caliper and a lining carrier plate (guide plate) attached to the lining holder and to which a lining element (lining assembly) is attached to the surface on the disc rotor side. ) With a brake lining (guide plate assembly) (see Patent Document 1).
　上記ブレーキライニングにおいて、ライニングキャリアプレートに配置されるライニング要素は、摩擦ライニング（摩擦材）を有し、摩擦ライニングがキャリア要素（裏板部）に取り付けられている。これらライニング要素は、キャリア要素が個々にピン等でライニングキャリアプレートに取付けられている。 In the above brake lining, the lining element arranged on the lining carrier plate has a friction lining (friction material), and the friction lining is attached to the carrier element (back plate portion). In these lining elements, the carrier elements are individually attached to the lining carrier plate with pins or the like.
日本国特許第６５０１８９０号公報Japanese Patent No. 6501890
　しかしながら、上記ブレーキライニングは、ライニング要素が組み付けられたライニングキャリアプレートが制動時の押し付け力と制動トルクそれぞれの伝達部材とされる。そこで、ライニングキャリアプレートには十分な強度を持たせる必要があり、ライニングキャリアプレートの質量が大きくなる要因となっていた。
　また、上記ブレーキライニングは、摩擦ライニングが焼結等により取り付けられたキャリア要素（裏板部）をピン等でライニングキャリアプレートに保持する構成である。そのため、ライニングキャリアプレートにライニング要素が組み付けられたブレーキライニングは、ブレーキライニング全体の厚みが厚くなっていた。 However, in the brake lining, the lining carrier plate to which the lining element is assembled serves as a transmission member for the pressing force and the braking torque at the time of braking. Therefore, it is necessary to give the lining carrier plate sufficient strength, which is a factor that increases the mass of the lining carrier plate.
Further, the brake lining is configured such that the carrier element (back plate portion) to which the friction lining is attached by sintering or the like is held by a pin or the like on the lining carrier plate. Therefore, in the brake lining in which the lining element is assembled to the lining carrier plate, the thickness of the entire brake lining is thick.
　本発明は上記状況に鑑みてなされたもので、その目的は、軽量で小型のガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体を提供することにある。 The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a lightweight and compact guide plate assembly and a friction pad assembly for a disc brake.
　本発明に係る上記目的は、下記構成により達成される。
（１）　制動トルクを受けるガイドプレートと、制動時にディスクロータと接触する摩擦材と、前記摩擦材の裏面に固着された裏板部とを有し、前記ガイドプレートのガイド孔部に揺動自在に支持される少なくとも１つのライニング組立体と、前記ガイド孔部に挿通された前記ライニング組立体をロータ軸方向に移動可能かつ抜け落ちないように保持するための抜け落ち防止機構と、前記裏板部の裏面側に設けられ、ライニングホルダにより前記ディスクロータへ押圧された前記ライニング組立体を揺動可能に支持するための凸部と、を備えたガイドプレート組立体。 The above object according to the present invention is achieved by the following configuration.
(1) It has a guide plate that receives braking torque, a friction material that comes into contact with the disc rotor during braking, and a back plate portion that is fixed to the back surface of the friction material, and can swing freely in the guide hole portion of the guide plate. At least one lining assembly supported by the guide hole, a fall-out prevention mechanism for holding the lining assembly inserted in the guide hole portion so as to be movable in the rotor axial direction and not to fall off, and a back plate portion. A guide plate assembly provided on the back surface side and provided with a convex portion for swingably supporting the lining assembly pressed against the disc rotor by the lining holder.
　上記（１）の構成のガイドプレート組立体によれば、ガイドプレートのガイド孔部に揺動自在に支持されたライニング組立体は、裏板部の裏面側に設けられた凸部を介して、ライニングホルダによりディスクロータへ押圧される。即ち、ライニングホルダによる制動時の押し付け力は、ライニング組立体により直接、ディスクロータに伝達される。そこで、ガイドプレートには、制動時の押し付け力が伝達されず、制動トルクのみが伝達される。従って、ガイドプレートには、制動時の押し付け力を支持できる大きな強度を持たせる必要がなく、ガイドプレートを軽量化することができる。
　また、ライニング組立体は、抜け落ち防止機構により、ロータ軸方向に移動可能かつ抜け落ちないようにガイドプレートに保持される。そこで、本構成のガイドプレート組立体は、複数のライニング組立体をガイドプレートにアッセンブリすることができる。従って、ガイドプレート組立体のハンドリングが容易となりメンテナンス性が向上する。 According to the guide plate assembly having the configuration of (1) above, the lining assembly swingably supported by the guide hole portion of the guide plate is via the convex portion provided on the back surface side of the back plate portion. It is pressed against the disc rotor by the lining holder. That is, the pressing force during braking by the lining holder is directly transmitted to the disc rotor by the lining assembly. Therefore, the pressing force at the time of braking is not transmitted to the guide plate, and only the braking torque is transmitted. Therefore, it is not necessary for the guide plate to have a large strength capable of supporting the pressing force at the time of braking, and the weight of the guide plate can be reduced.
Further, the lining assembly is held by the guide plate so as to be movable in the rotor axial direction and not to fall off by the fall-off prevention mechanism. Therefore, in the guide plate assembly of this configuration, a plurality of lining assemblies can be assembled on the guide plate. Therefore, the handling of the guide plate assembly becomes easy and the maintainability is improved.
（２）　上記（１）に記載のガイドプレート組立体であって、前記裏板部のプレート嵌合部と前記ガイド孔部とがそれぞれ非円形状に形成されて嵌合することによって、前記ガイド孔部内での前記ライニング組立体の回転が阻止される、ガイドプレート組立体。 (2) In the guide plate assembly according to (1) above, the guide is formed by forming and fitting the plate fitting portion of the back plate portion and the guide hole portion in a non-circular shape. A guide plate assembly that prevents the lining assembly from rotating in the holes.
　上記（２）の構成のガイドプレート組立体によれば、ライニング組立体の回転を阻止するための回り止めが、非円形状に形成された裏板部のプレート嵌合部とガイド孔部とが嵌合することで達成される。そこで、部品点数を増加させることなくライニング組立体の回り止めが可能となる。即ち、ライニング組立体が回転すると、ディスクロータに十分な制動力を作用させることができなくなるため、ガイドプレートに対してライニング組立体を回転不能にすることが望ましい。 According to the guide plate assembly having the configuration of (2) above, the detent for preventing the rotation of the lining assembly is provided by the plate fitting portion and the guide hole portion of the back plate portion formed in a non-circular shape. Achieved by mating. Therefore, it is possible to prevent the lining assembly from rotating without increasing the number of parts. That is, when the lining assembly rotates, it becomes impossible to apply a sufficient braking force to the disc rotor, so it is desirable to make the lining assembly non-rotatable with respect to the guide plate.
（３）　上記（２）に記載のガイドプレート組立体であって、前記プレート嵌合部の外周面及び前記ガイド孔部の内周面には、前記ガイド孔部内での前記ライニング組立体の回転を阻止する回り止め用の平坦面が形成される、ガイドプレート組立体。 (3) In the guide plate assembly according to (2) above, the rotation of the lining assembly in the guide hole portion is formed on the outer peripheral surface of the plate fitting portion and the inner peripheral surface of the guide hole portion. A guide plate assembly that forms a flat surface for detent to prevent.
　上記（３）の構成のガイドプレート組立体によれば、ライニング組立体の回転を阻止するための回り止めが、プレート嵌合部の外周面及びガイド孔部の内周面に形成された平坦面同士が係合することで達成される。そこで、部品点数を増加させることなくライニング組立体の回り止めを容易に形成することができる。 According to the guide plate assembly having the configuration of (3) above, the detent for preventing the rotation of the lining assembly is a flat surface formed on the outer peripheral surface of the plate fitting portion and the inner peripheral surface of the guide hole portion. It is achieved by engaging with each other. Therefore, it is possible to easily form a detent for the lining assembly without increasing the number of parts.
（４）　上記（１）～（３）のいずれか１つに記載のガイドプレート組立体であって、前記ガイドプレートの表面又は裏面と、前記裏板部との間には、前記ライニング組立体を前記ガイドプレートに対して前記ロータ軸方向に沿う何れか一方に付勢するばね部材が配置される、ガイドプレート組立体。 (4) The guide plate assembly according to any one of (1) to (3) above, and the lining assembly between the front surface or the back surface of the guide plate and the back plate portion. A guide plate assembly in which a spring member for urging the guide plate to any one along the rotor axial direction is arranged.
　上記（４）の構成のガイドプレート組立体によれば、ばね部材がガイドプレートの表面と裏板部との間に配置される場合、裏板部の凸部と、ライニングホルダ或いはライニングホルダに取付けられたトルク受けプレートとの間に隙間が生じる。これにより、ばね部材が弾性変形してライニング組立体の厚さ方向の寸法公差を吸収すると共に、ライニング組立体のガタツキが防止される。このため、本構成のガイドプレート組立体では、ディスクロータに対する各ライニング組立体の接触性にばらつきの生じることが防止されると共に、異音の発生が抑制される。従って、各ライニング組立体は、厚さ方向の寸法公差の影響を受けずに、安定した制動特性を維持することができる。
　また、ばね部材がガイドプレートの裏面と裏板部との間に配置される場合、ばね部材の付勢力により裏板部の凸部がライニングホルダ或いはトルク受けプレートに押し付けられた状態となり、ブレーキ時の応答性が向上する。 According to the guide plate assembly having the configuration of (4) above, when the spring member is arranged between the surface of the guide plate and the back plate portion, it is attached to the convex portion of the back plate portion and the lining holder or the lining holder. A gap is created between the torque receiving plate and the torque receiving plate. As a result, the spring member is elastically deformed to absorb the dimensional tolerance in the thickness direction of the lining assembly, and rattling of the lining assembly is prevented. Therefore, in the guide plate assembly of this configuration, it is possible to prevent variations in the contactability of each lining assembly with respect to the disc rotor, and it is possible to suppress the generation of abnormal noise. Therefore, each lining assembly can maintain stable braking characteristics without being affected by dimensional tolerances in the thickness direction.
When the spring member is placed between the back surface of the guide plate and the back plate portion, the convex portion of the back plate portion is pressed against the lining holder or the torque receiving plate by the urging force of the spring member, and the brake is applied. The responsiveness of is improved.
（５）　上記（１）～（４）のいずれか１つに記載のガイドプレート組立体であって、前記抜け落ち防止機構は、前記ガイド孔部の開口形状よりも大きい外形状を有して前記裏板部の裏面に取り付けられるロックプレートを有する、ガイドプレート組立体。 (5) The guide plate assembly according to any one of (1) to (4) above, wherein the fall-out prevention mechanism has an outer shape larger than the opening shape of the guide hole portion. A guide plate assembly with a lock plate attached to the back of the back plate.
　上記（５）の構成のガイドプレート組立体によれば、ガイド孔部よりも大きな外径の抜け止めフランジ部が裏板部の表面側に一体形成され、ロックプレートが裏板部の裏面に取り付けられる。そこで、ガイド孔部に挿通されたライニング組立体をロータ軸方向に移動可能かつ抜け落ちないように保持することができる。従って、抜け落ち防止機構を容易に構成することができる。 According to the guide plate assembly having the configuration of (5) above, a retaining flange portion having an outer diameter larger than that of the guide hole portion is integrally formed on the front surface side of the back plate portion, and the lock plate is attached to the back surface of the back plate portion. Be done. Therefore, the lining assembly inserted through the guide hole can be held so as to be movable in the rotor axial direction and not to come off. Therefore, the fall-out prevention mechanism can be easily configured.
（６）　上記（５）に記載のガイドプレート組立体であって、前記裏板部に圧入されることで前記ロックプレートを前記裏板部の裏面に固定するジョイント部材からなる前記凸部を有する、ガイドプレート組立体。 (6) The guide plate assembly according to (5) above, which has the convex portion formed of a joint member that fixes the lock plate to the back surface of the back plate portion by being press-fitted into the back plate portion. , Guide plate assembly.
　上記（６）の構成のガイドプレート組立体によれば、裏板部の裏面側に設けられる凸部が、ロックプレートを裏板部の裏面に固定するジョイント部材により構成される。そこで、ジョイント部材を裏板部の裏面側に圧入してロックプレートを固定することで、ガイド孔部に挿通されたライニング組立体を抜け落ちないように保持すると共に、裏板部の裏面側に凸部を容易に構成することができる。 According to the guide plate assembly having the configuration of (6) above, the convex portion provided on the back surface side of the back plate portion is composed of a joint member for fixing the lock plate to the back surface of the back plate portion. Therefore, by press-fitting the joint member into the back surface side of the back plate portion to fix the lock plate, the lining assembly inserted through the guide hole portion is held so as not to fall off, and is convex to the back surface side of the back plate portion. The unit can be easily configured.
（７）　上記（５）に記載のガイドプレート組立体であって、前記ロックプレートが、リベットにより前記裏板部の裏面に固定される、ガイドプレート組立体。 (7) The guide plate assembly according to (5) above, wherein the lock plate is fixed to the back surface of the back plate portion by rivets.
　上記（７）の構成のガイドプレート組立体によれば、安価なリベットによりロックプレートを裏板部の裏面に容易に固定することができる。 According to the guide plate assembly having the configuration of (7) above, the lock plate can be easily fixed to the back surface of the back plate portion by an inexpensive rivet.
（８）　上記（５）に記載のガイドプレート組立体であって、前記ロックプレートが、ブラインドリベットにより前記裏板部の裏面に固定される、ガイドプレート組立体。 (8) The guide plate assembly according to (5) above, wherein the lock plate is fixed to the back surface of the back plate portion by a blind rivet.
　上記（８）の構成のガイドプレート組立体によれば、ブラインドリベットによりロックプレートを裏板部の裏面に容易に固定することができる。ブラインドリベットによりロックプレートが固定されたガイドプレート組立体は、リベットを固定するためのリベット用凹部を摩擦材に設ける必要がなく、ディスクロータに対する摩擦材の接触面積が低下することはない。 According to the guide plate assembly having the configuration of (8) above, the lock plate can be easily fixed to the back surface of the back plate portion by the blind rivet. The guide plate assembly in which the lock plate is fixed by the blind rivet does not need to provide the rivet recess for fixing the rivet in the friction material, and the contact area of the friction material with the disc rotor does not decrease.
（９）　上記（５）に記載のガイドプレート組立体であって、前記裏板部を貫通した先端のハトメにより前記ロックプレートを前記裏板部の裏面に固定するジョイント部材からなる前記凸部を有する、ガイドプレート組立体。 (9) In the guide plate assembly according to (5) above, the convex portion made of a joint member for fixing the lock plate to the back surface of the back plate portion by eyelets at the tip penetrating the back plate portion. Have a guide plate assembly.
　上記（９）の構成のガイドプレート組立体によれば、先端にハトメを有するジョイント部材によりロックプレートが裏板部の裏面に容易に固定される。そこで、本構成のガイドプレート組立体は、ガイド孔部に挿通されたライニング組立体を抜け落ちないように保持すると共に、裏板部の裏面側に凸部を容易に構成することができる。 According to the guide plate assembly having the configuration of (9) above, the lock plate is easily fixed to the back surface of the back plate portion by the joint member having eyelets at the tip. Therefore, the guide plate assembly of the present configuration can hold the lining assembly inserted through the guide hole portion so as not to fall off, and can easily form a convex portion on the back surface side of the back plate portion.
（１０）　上記（１）～（９）の何れか１つに記載のガイドプレート組立体であって、前記ガイドプレートの裏面側には、減衰層が設けられる、ガイドプレート組立体。 (10) The guide plate assembly according to any one of (1) to (9) above, wherein a damping layer is provided on the back surface side of the guide plate.
　上記（１０）の構成のガイドプレート組立体によれば、ライニングホルダに取付けられた際、ライニング組立体とライニングホルダとの間を伝搬する振動が、減衰層により減衰される。減衰層は、ライニングホルダと裏板部の凸部との接触によるノイズの低減に寄与する。これにより、制動過程時に生じる振動が減衰され、スキール騒音（所謂ブレーキ鳴き）が抑制される。また、ガイドプレート組立体に減衰層を設けることにより、手扱いがよくなる。 According to the guide plate assembly having the configuration of (10) above, when attached to the lining holder, the vibration propagating between the lining assembly and the lining holder is damped by the damping layer. The damping layer contributes to the reduction of noise due to the contact between the lining holder and the convex portion of the back plate portion. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed. Further, by providing the damping layer in the guide plate assembly, the handling by hand is improved.
（１１）　上記（１）～（１０）の何れか１つに記載のガイドプレート組立体と、前記ガイドプレートの周縁部分に嵌合して前記ガイドプレート組立体を着脱自在に保持する溝部が設けられ、表面で前記凸部を揺動可能に支持する前記ライニングホルダと、を備えたことを特徴とするディスクブレーキ用摩擦パッド組立て体。 (11) The guide plate assembly according to any one of (1) to (10) above, and a groove portion that fits into the peripheral portion of the guide plate and holds the guide plate assembly detachably are provided. A friction pad assembly for a disc brake, characterized in that the lining holder is provided with a lining holder that swingably supports the convex portion on the surface thereof.
　上記（１１）の構成のディスクブレーキ用摩擦パッド組立て体によれば、複数のライニング組立体がガイドプレートにアッセンブリされたガイドプレート組立体は、ライニングホルダに着脱自在に保持される。そこで、本構成のディスクブレーキ用摩擦パッド組立て体は、ガイドプレート組立体にアッセンブリされた複数のライニング組立体の交換が容易となりメンテナンス性が向上する。 According to the disc brake friction pad assembly having the configuration of (11) above, the guide plate assembly in which a plurality of lining assemblies are assembled on the guide plate is detachably held by the lining holder. Therefore, in the disc brake friction pad assembly of the present configuration, it becomes easy to replace the plurality of lining assemblies assembled in the guide plate assembly, and the maintainability is improved.
（１２）　上記（１）～（１０）の何れか１つに記載のガイドプレート組立体と、前記ガイドプレートの周縁部分に嵌合して前記ガイドプレート組立体を着脱自在に保持する溝部が設けられ、表面で前記凸部を揺動可能に支持するトルク受けプレートと、前記トルク受けプレートの裏面に設けられ、蟻溝状の固定溝が設けられた前記ライニングホルダへ、溝端から挿入されるアンカープレートと、を備えたことを特徴とするディスクブレーキ用摩擦パッド組立て体。 (12) The guide plate assembly according to any one of (1) to (10) above, and a groove portion that fits into the peripheral portion of the guide plate and holds the guide plate assembly detachably are provided. Anchor inserted from the groove end into the torque receiving plate that swingably supports the convex portion on the front surface and the lining holder provided on the back surface of the torque receiving plate and provided with a dovetail groove-shaped fixing groove. A friction pad assembly for disc brakes featuring a plate and.
　上記（１２）の構成のディスクブレーキ用摩擦パッド組立て体によれば、複数のライニング組立体がガイドプレートにアッセンブリされたガイドプレート組立体は、アンカープレートを有するトルク受けプレートに着脱自在に保持される。そこで、本構成のディスクブレーキ用摩擦パッド組立て体は、ライニングホルダの蟻溝状の固定溝にトルク受けプレートのアンカープレートを挿入することができる。これにより、本構成のディスクブレーキ用摩擦パッド組立て体は、ガイドプレートの形状が異なる複数種のガイドプレート組立体をライニングホルダに着脱自在に取付けることができる。 According to the disc brake friction pad assembly having the configuration of (12) above, the guide plate assembly in which a plurality of lining assemblies are assembled on the guide plate is detachably held by the torque receiving plate having the anchor plate. .. Therefore, in the disc brake friction pad assembly of the present configuration, the anchor plate of the torque receiving plate can be inserted into the dovetail groove-shaped fixing groove of the lining holder. As a result, in the disc brake friction pad assembly of the present configuration, a plurality of types of guide plate assemblies having different guide plate shapes can be detachably attached to the lining holder.
（１３）　上記（１１）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記裏板部のプレート嵌合部が前記ガイド孔部に挿入装着され、前記ディスクロータと前記摩擦材との接触時に作用する前記制動トルクが、前記プレート嵌合部から前記ガイドプレートに伝達され、更に前記ガイドプレートのアンカーピン係合部からアンカーピンにより前記ライニングホルダのアンカーピン嵌合部に伝達される、ディスクブレーキ用摩擦パッド組立て体。 (13) In the disc brake friction pad assembly according to (11) above, the plate fitting portion of the back plate portion is inserted and mounted in the guide hole portion, and the disc rotor and the friction material come into contact with each other. The braking torque that sometimes acts is transmitted from the plate fitting portion to the guide plate, and further transmitted from the anchor pin engaging portion of the guide plate to the anchor pin fitting portion of the lining holder by the anchor pin. Brake friction pad assembly.
　上記（１３）の構成のディスクブレーキ用摩擦パッド組立て体によれば、アンカーピンを介してライニングホルダに固定されたガイドプレート組立体は、アンカーピンを取り外すだけで交換可能となる。そのため、本構成のディスクブレーキ用摩擦パッド組立て体は、交換部品の軽量化が可能となりメンテナンス性が向上する。 According to the disc brake friction pad assembly having the configuration of (13) above, the guide plate assembly fixed to the lining holder via the anchor pin can be replaced simply by removing the anchor pin. Therefore, the disc brake friction pad assembly of this configuration can reduce the weight of replacement parts and improve maintainability.
（１４）　上記（１２）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記裏板部のプレート嵌合部が前記ガイド孔部に挿入装着され、前記ディスクロータと前記摩擦材との接触時に作用する前記制動トルクが、前記プレート嵌合部から前記ガイドプレートに伝達され、更に前記ガイドプレートのアンカーピン係合部からアンカーピンにより前記トルク受けプレートのアンカーピン嵌合部に伝達され、更に前記トルク受けプレートの前記アンカープレートからアンカープレート固定部材により前記ライニングホルダの固定部に伝達される、ディスクブレーキ用摩擦パッド組立て体。 (14) In the disc brake friction pad assembly according to (12) above, the plate fitting portion of the back plate portion is inserted and mounted in the guide hole portion, and the disc rotor and the friction material come into contact with each other. The braking torque that sometimes acts is transmitted from the plate fitting portion to the guide plate, and further transmitted from the anchor pin engaging portion of the guide plate to the anchor pin fitting portion of the torque receiving plate by the anchor pin. A friction pad assembly for a disc brake, which is transmitted from the anchor plate of the torque receiving plate to the fixing portion of the lining holder by the anchor plate fixing member.
　上記（１４）の構成のディスクブレーキ用摩擦パッド組立て体によれば、ライニングホルダの固定部にアンカープレート固定部材によりアンカープレートが固定されたトルク受けプレートに対して、アンカーピンを介して固定されたガイドプレート組立体は、アンカーピンを取り外すだけで交換可能となる。そのため、本構成のディスクブレーキ用摩擦パッド組立て体は、交換部品の軽量化が可能となりメンテナンス性が向上する。 According to the disc brake friction pad assembly having the configuration of (14) above, the anchor plate is fixed to the fixing portion of the lining holder by the anchor plate fixing member with respect to the torque receiving plate fixed via the anchor pin. The guide plate assembly can be replaced by simply removing the anchor pin. Therefore, the disc brake friction pad assembly of this configuration can reduce the weight of replacement parts and improve maintainability.
（１５）　上記（１３）又は（１４）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記アンカーピン係合部が、半円形状に形成されて前記制動トルクを受ける、ディスクブレーキ用摩擦パッド組立て体。 (15) The disc brake friction pad assembly according to (13) or (14) above, wherein the anchor pin engaging portion is formed in a semicircular shape and receives the braking torque. Pad assembly.
　上記（１５）の構成のディスクブレーキ用摩擦パッド組立て体によれば、制動方向に対向して制動トルクを受けるアンカーピン係合部が半円形状に形成される。そこで、本構成のディスクブレーキ用摩擦パッド組立て体は、アンカーピン係合部を円形状に形成した場合よりもガイドプレートが大型化するのを抑制できる。 According to the disc brake friction pad assembly having the configuration of (15) above, the anchor pin engaging portion that receives the braking torque facing the braking direction is formed in a semicircular shape. Therefore, the disc brake friction pad assembly of the present configuration can suppress the size of the guide plate from becoming larger than that in the case where the anchor pin engaging portion is formed in a circular shape.
（１６）　上記（１３）又は（１４）に記載のディスクブレーキ用摩擦パッド組立て体であって、複数の前記アンカーピン係合部のうちで、ブレーキキャリパに取り付けられた際に鉛直方向下側に位置する前記アンカーピン係合部が、円形状に形成されて前記制動トルクを受ける、ディスクブレーキ用摩擦パッド組立て体。 (16) The disc brake friction pad assembly according to (13) or (14) above, which is vertically downward when attached to the brake caliper among the plurality of anchor pin engaging portions. A friction pad assembly for a disc brake in which the anchor pin engaging portion located is formed in a circular shape and receives the braking torque.
　上記（１６）の構成のディスクブレーキ用摩擦パッド組立て体によれば、アンカーピン係合部が円形状に形成されることで、アンカーピン係合部はそれぞれの制動方向に対向して制動トルクを受けることができる。
　また、ブレーキキャリパに取り付けられた際に鉛直方向上側に円形状のアンカーピン係合部が位置すると、ガイドプレート組立体を着脱する際に鉛直方向上側に配置されたアンカーピンも着脱しなければならず、作業性がよくない。これに対し、ブレーキキャリパに取り付けられた際に鉛直方向下側に円形状のアンカーピン係合部が位置し、鉛直方向上側に半円形状のアンカーピン係合部が位置する場合には、鉛直方向下側に配置されたアンカーピンを着脱するだけでよく、着脱作業が容易となる。 According to the disc brake friction pad assembly having the configuration of (16) above, the anchor pin engaging portion is formed in a circular shape, so that the anchor pin engaging portion receives braking torque facing each braking direction. Can receive.
In addition, if the circular anchor pin engaging portion is located on the upper side in the vertical direction when attached to the brake caliper, the anchor pin arranged on the upper side in the vertical direction must also be attached / detached when attaching / detaching the guide plate assembly. The workability is not good. On the other hand, when it is attached to the brake caliper, the circular anchor pin engaging portion is located on the lower side in the vertical direction, and the semicircular anchor pin engaging portion is located on the upper side in the vertical direction. It is only necessary to attach / detach the anchor pin arranged on the lower side in the direction, which facilitates the attachment / detachment work.
（１７）　上記（１１）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記ライニングホルダの前記表面側には、前記凸部と対向する減衰層が設けられる、ディスクブレーキ用摩擦パッド組立て体。 (17) The disc brake friction pad assembly according to (11) above, wherein a damping layer facing the convex portion is provided on the surface side of the lining holder. ..
　上記（１７）の構成のディスクブレーキ用摩擦パッド組立て体によれば、ガイドプレート組立体がライニングホルダに取付けられた際、ライニング組立体とライニングホルダとの間を伝搬する振動が、減衰層により減衰される。減衰層は、ライニングホルダと裏板部の凸部との接触によるノイズの低減に寄与する。これにより、制動過程時に生じる振動が減衰され、スキール騒音（所謂ブレーキ鳴き）が抑制される。 According to the disc brake friction pad assembly having the configuration of (17) above, when the guide plate assembly is attached to the lining holder, the vibration propagating between the lining assembly and the lining holder is damped by the damping layer. Will be done. The damping layer contributes to the reduction of noise due to the contact between the lining holder and the convex portion of the back plate portion. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
（１８）　上記（１２）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記トルク受けプレートの前記表面側には、前記凸部と対向する減衰層が設けられる、ディスクブレーキ用摩擦パッド組立て体。 (18) The disc brake friction pad assembly according to (12) above, wherein a damping layer facing the convex portion is provided on the surface side of the torque receiving plate. body.
　上記（１８）の構成のディスクブレーキ用摩擦パッド組立て体によれば、ガイドプレート組立体がトルク受けプレートに取付けられた際、ライニング組立体とトルク受けプレートとの間を伝搬する振動が、減衰層により減衰される。減衰層は、トルク受けプレートと裏板部の凸部との接触によるノイズの低減に寄与する。これにより、制動過程時に生じる振動が減衰され、スキール騒音（所謂ブレーキ鳴き）が抑制される。 According to the disc brake friction pad assembly having the configuration of (18) above, when the guide plate assembly is attached to the torque receiving plate, the vibration propagating between the lining assembly and the torque receiving plate is a damping layer. Is attenuated by. The damping layer contributes to the reduction of noise due to the contact between the torque receiving plate and the convex portion of the back plate portion. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
（１９）　上記（１３）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記ライニングホルダの前記表面側には、前記凸部と対向する減衰層が設けられ、前記減衰層には、円形状に形成された前記アンカーピン係合部を貫通した前記アンカーピンに貫通されるアンカーピン係合穴が形成される、ディスクブレーキ用摩擦パッド組立て体。
（２０）　上記（１４）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記トルク受けプレートの前記表面側には、前記凸部と対向する減衰層が設けられ、前記減衰層には、円形状に形成された前記アンカーピン係合部を貫通した前記アンカーピンに貫通されるアンカーピン係合穴が形成される、ディスクブレーキ用摩擦パッド組立て体。 (19) In the disc brake friction pad assembly according to (13) above, a damping layer facing the convex portion is provided on the surface side of the lining holder, and the damping layer is a circle. A friction pad assembly for a disc brake in which an anchor pin engaging hole is formed through the anchor pin that penetrates the anchor pin engaging portion formed in a shape.
(20) In the disc brake friction pad assembly according to (14) above, a damping layer facing the convex portion is provided on the surface side of the torque receiving plate, and the damping layer is provided with the damping layer. A friction pad assembly for a disc brake in which an anchor pin engaging hole is formed through the anchor pin that penetrates the anchor pin engaging portion formed in a circular shape.
　上記（１９）又は（２０）の構成のディスクブレーキ用摩擦パッド組立て体によれば、減衰層のアンカーピン係合穴がアンカーピンに貫通されることで、減衰層はライニングホルダ又はトルク受けプレートに固定される。 According to the disc brake friction pad assembly having the configuration of (19) or (20) above, the damping layer is formed on the lining holder or the torque receiving plate by penetrating the anchor pin engagement hole of the damping layer through the anchor pin. It is fixed.
（２１）　上記（１７）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記減衰層は、前記ライニングホルダに対して締結部材によって固定される、ディスクブレーキ用摩擦パッド組立て体。
（２２）　上記（１８）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記減衰層は、前記トルク受けプレートに対して締結部材によって固定される、ディスクブレーキ用摩擦パッド組立て体。 (21) The disc brake friction pad assembly according to (17) above, wherein the damping layer is fixed to the lining holder by a fastening member.
(22) The disc brake friction pad assembly according to (18) above, wherein the damping layer is fixed to the torque receiving plate by a fastening member.
　上記（２１）又は（２２）の構成のディスクブレーキ用摩擦パッド組立て体によれば、減衰層はライニングホルダ又はトルク受けプレートに締結部材によって固定される。 According to the disc brake friction pad assembly having the configuration of (21) or (22) above, the damping layer is fixed to the lining holder or the torque receiving plate by the fastening member.
（２３）　上記（１７）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記減衰層は、前記ライニングホルダに対して接着剤によって固定される、ディスクブレーキ用摩擦パッド組立て体。
（２４）　上記（１８）に記載のディスクブレーキ用摩擦パッド組立て体であって、前記減衰層は、前記トルク受けプレートに対して接着剤によって固定される、ディスクブレーキ用摩擦パッド組立て体。 (23) The disc brake friction pad assembly according to (17) above, wherein the damping layer is fixed to the lining holder by an adhesive.
(24) The disc brake friction pad assembly according to (18) above, wherein the damping layer is fixed to the torque receiving plate by an adhesive.
　上記（２３）又は（２４）の構成のディスクブレーキ用摩擦パッド組立て体によれば、減衰層はライニングホルダ又はトルク受けプレートに接着剤によって固定される。 According to the disc brake friction pad assembly having the configuration of (23) or (24) above, the damping layer is fixed to the lining holder or the torque receiving plate by an adhesive.
　本発明に係るガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体によれば、軽量で小型のガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体を実現できる。 According to the guide plate assembly and the friction pad assembly for disc brakes according to the present invention, it is possible to realize a lightweight and compact guide plate assembly and a friction pad assembly for disc brakes.
　以上、本発明について簡潔に説明した。更に、以下に説明される発明を実施するための形態（以下、「実施形態」という。）を添付の図面を参照して通読することにより、本発明の詳細は更に明確化されるであろう。 The present invention has been briefly described above. Further, the details of the present invention will be further clarified by reading through the embodiments described below (hereinafter referred to as "embodiments") with reference to the accompanying drawings. ..
図１は、本発明の第１実施形態に係るガイドプレート組立体を表側から見た斜視図である。FIG. 1 is a perspective view of the guide plate assembly according to the first embodiment of the present invention as viewed from the front side. 図２は、図１に示したガイドプレート組立体を裏側から見た斜視図である。FIG. 2 is a perspective view of the guide plate assembly shown in FIG. 1 as viewed from the back side. 図３の（ａ）は図１に示したライニング組立体の断面図であり、図３の（ｂ）は図１に示したライニング組立体の分解斜視図である。FIG. 3A is a cross-sectional view of the lining assembly shown in FIG. 1, and FIG. 3B is an exploded perspective view of the lining assembly shown in FIG. 図４は、図１に示したガイドプレートに取り付けられるライニング組立体を説明するための要部分解斜視図である。FIG. 4 is an exploded perspective view of a main part for explaining a lining assembly attached to the guide plate shown in FIG. 図５の（ａ）及び（ｂ）は、図１に示したライニング組立体の変形例を説明するための要部断面図及び要部分解斜視図である。5 (a) and 5 (b) are a cross-sectional view of a main part and an exploded perspective view of the main part for explaining a modified example of the lining assembly shown in FIG. 図６の（ａ）～（ｃ）は図１に示したライニング組立体の他の変形例を説明するための正面図、Ａ－Ａ断面図及び分解斜視図であり、図６の（ｄ）は図６の（ｃ）に示したジョイント部材を説明する斜視図である。6 (a) to 6 (c) are a front view, a cross-sectional view taken along the line AA, and an exploded perspective view for explaining another modification of the lining assembly shown in FIG. 1, and FIG. 6 (d) is shown in FIG. Is a perspective view illustrating the joint member shown in FIG. 6 (c). 図７の（ａ）及び（ｂ）は図１に示したライニング組立体の他の変形例を説明するための正面図及びＢ－Ｂ断面図であり、図７の（ｃ）は図１に示したライニング組立体の別の変形例を説明するための断面図である。7 (a) and 7 (b) are a front view and a sectional view taken along the line BB for explaining another modification of the lining assembly shown in FIG. 1, and FIG. 7 (c) is shown in FIG. It is sectional drawing for demonstrating another modification of the lining assembly shown. 図８の（ａ）及び（ｂ）は、図１に示したライニング組立体の他の変形例を説明するための正面図及びＣ－Ｃ断面図である。8 (a) and 8 (b) are a front view and a sectional view taken along the line CC for explaining another modification of the lining assembly shown in FIG. 図９の（ａ）及び（ｂ）は、本発明の第２実施形態に係るトルク受けプレートを表側から見た斜視図及び裏側から見た斜視図である。9 (a) and 9 (b) are a perspective view of the torque receiving plate according to the second embodiment of the present invention as viewed from the front side and a perspective view as viewed from the back side. 図１０は、本第２実施形態に係るトルク受けプレート及び本第１実施形態に係るガイドプレート組立体の斜視図である。FIG. 10 is a perspective view of the torque receiving plate according to the second embodiment and the guide plate assembly according to the first embodiment. 図１１の（ａ）は本第２実施形態に係るトルク受けプレートに本第１実施形態に係るガイドプレート組立体が組み付けられたディスクブレーキ用摩擦パッド組立て体を表側から見た斜視図であり、図１１の（ｂ）は図１１の（ａ）のＤ－Ｄ断面図である。FIG. 11A is a perspective view of a friction pad assembly for a disc brake in which the guide plate assembly according to the first embodiment is assembled to the torque receiving plate according to the second embodiment as viewed from the front side. 11 (b) is a cross-sectional view taken along the line DD of FIG. 11 (a). 図１２は、図１１に示したディスクブレーキ用摩擦パッド組立て体がライニングホルダに組み付けられた状態を説明する概略斜視図である。FIG. 12 is a schematic perspective view illustrating a state in which the disc brake friction pad assembly shown in FIG. 11 is assembled to the lining holder. 図１３は、図１２におけるＥ－Ｅ断面図である。FIG. 13 is a cross-sectional view taken along the line EE in FIG. 図１４は、図１に示した本第１実施形態の変形例に係るガイドプレート組立体を示す斜視図である。FIG. 14 is a perspective view showing a guide plate assembly according to a modification of the first embodiment shown in FIG. 1. 図１５の（ａ）及び（ｂ）は、本発明の第３実施形態に係るライニングホルダを表側から見た斜視図及び裏側から見た斜視図である。15 (a) and 15 (b) are a perspective view of the lining holder according to the third embodiment of the present invention as viewed from the front side and a perspective view as viewed from the back side. 図１６は、本第３実施形態に係るライニングホルダに本第１実施に係るガイドプレート組立体が組み付けられたディスクブレーキ用摩擦パッド組立て体を表側から見た斜視図である。FIG. 16 is a perspective view of a friction pad assembly for a disc brake in which the guide plate assembly according to the first embodiment is assembled to the lining holder according to the third embodiment as viewed from the front side. 図１７は、本発明の第４実施形態に係るガイドプレート組立体を裏側から見た斜視図である。FIG. 17 is a perspective view of the guide plate assembly according to the fourth embodiment of the present invention as viewed from the back side. 図１８は、図１７に示したガイドプレート組立体の分解斜視図である。FIG. 18 is an exploded perspective view of the guide plate assembly shown in FIG. 図１９の（ａ）は本発明の第５実施形態に係るトルク受けプレートを表側から見た斜視図であり、図１９の（ｂ）は本第５実施形態の変形例に係るトルク受けプレートを表側から見た斜視図である。FIG. 19A is a perspective view of the torque receiving plate according to the fifth embodiment of the present invention as viewed from the front side, and FIG. 19B is a torque receiving plate according to a modified example of the fifth embodiment. It is a perspective view seen from the front side. 図２０の（ａ）は本発明の第６実施形態に係るライニングホルダを表側から見た斜視図であり、図２０の（ｂ）は本第６実施形態の変形例に係るライニングホルダを表側から見た斜視図である。FIG. 20A is a perspective view of the lining holder according to the sixth embodiment of the present invention as viewed from the front side, and FIG. 20B is a perspective view of the lining holder according to the modified example of the sixth embodiment from the front side. It is a perspective view as seen.
　以下、本発明に係る実施形態を、図面を参照して説明する。
　本実施形態に係るガイドプレート組立体を備えたディスクブレーキ用摩擦パッド組立て体（以下、単に「摩擦パッド組立て体」と言う）は、鉄道車両用のディスクブレーキ装置に使用されるものである。このディスクブレーキ用摩擦パッド組立て体は、車軸上のディスクロータに対峙して配置され、車体フレームに固定されたブレーキキャリパに内蔵のアクチュエータによりディスクロータに向かって進退駆動される。勿論、本発明のディスクブレーキ用摩擦パッド組立て体は、鉄道車両用のディスクブレーキ装置に限定されるものではない。 Hereinafter, embodiments according to the present invention will be described with reference to the drawings.
The disc brake friction pad assembly (hereinafter, simply referred to as “friction pad assembly”) provided with the guide plate assembly according to the present embodiment is used for a disc brake device for a railroad vehicle. The disc brake friction pad assembly is arranged facing the disc rotor on the axle, and is driven forward and backward toward the disc rotor by an actuator built in the brake caliper fixed to the vehicle body frame. Of course, the friction pad assembly for disc brakes of the present invention is not limited to the disc brake device for railway vehicles.
　図１及び図２は、本発明の第１実施形態に係るガイドプレート組立体１を表側及び裏側から見た斜視図である。図３の（ａ）は図１に示したライニング組立体１０の断面図であり、図３の（ｂ）は図１に示したライニング組立体１０の分解斜視図である。図４は、図１に示したガイドプレート３に取り付けられるライニング組立体１０を説明するための要部分解斜視図である。 1 and 2 are perspective views of the guide plate assembly 1 according to the first embodiment of the present invention as viewed from the front side and the back side. 3A is a cross-sectional view of the lining assembly 10 shown in FIG. 1, and FIG. 3B is an exploded perspective view of the lining assembly 10 shown in FIG. FIG. 4 is an exploded perspective view of a main part for explaining the lining assembly 10 attached to the guide plate 3 shown in FIG.
　本第１実施形態に係るガイドプレート組立体１は、図１～図４に示すように、制動トルクを受けるガイドプレート３と、ガイドプレート３のガイド孔部５に揺動自在に支持された少なくとも１つ（本実施形態では２０個）のライニング組立体１０と、を備えている。
　ガイドプレート３は、ガイド孔部５が所定の離間間隔で複数（２０孔）形成されており、各ガイド孔部５にライニング組立体１０が装着される。ガイドプレート３は、制動時に各ガイド孔部５に装着されたライニング組立体１０に作用する制動トルクを受け止めることができる所定の板厚を有した平板材で形成される。 As shown in FIGS. 1 to 4, the guide plate assembly 1 according to the first embodiment has at least swingably supported by a guide plate 3 that receives braking torque and a guide hole portion 5 of the guide plate 3. It includes one (20 in this embodiment) lining assembly 10.
The guide plate 3 has a plurality of (20 holes) of guide holes 5 formed at predetermined spacing intervals, and the lining assembly 10 is mounted on each guide hole 5. The guide plate 3 is formed of a flat plate material having a predetermined plate thickness capable of receiving the braking torque acting on the lining assembly 10 mounted on each guide hole portion 5 at the time of braking.
　図示しないブレーキキャリパに取り付けられた際に鉛直方向上側に位置するガイドプレート３の長手方向上端部には、半円形状に形成されたアンカーピン係合部７が形成されている。また、ブレーキキャリパに取り付けられた際に鉛直方向下側に位置するガイドプレート３の長手方向下端部には、円形状に形成されたアンカーピン係合部９が形成されている。 An anchor pin engaging portion 7 formed in a semicircular shape is formed at the upper end portion in the longitudinal direction of the guide plate 3 located on the upper side in the vertical direction when attached to a brake caliper (not shown). Further, an anchor pin engaging portion 9 formed in a circular shape is formed at the lower end portion in the longitudinal direction of the guide plate 3 located on the lower side in the vertical direction when attached to the brake caliper.
　ライニング組立体１０は、制動トルクを受けるガイドプレート３に揺動自在に支持されて、後述するライニングホルダ１４０（３０１）によりディスクロータへ押圧される。
　ライニング組立体１０は、図３に示すように、略円板状に成型された摩擦材１１と、この摩擦材１１の裏面に固着された裏板部１２と、裏板部１２の裏面側に設けられ、ライニングホルダ１４０（３０１）によりディスクロータへ押圧されたライニング組立体１０を揺動可能に支持するための凸部２０と、ガイド孔部５に挿通されたライニング組立体１０をロータ軸方向Ｘに移動可能かつ抜け落ちないように保持するための抜け落ち防止機構と、を備えている。 The lining assembly 10 is swingably supported by a guide plate 3 that receives braking torque, and is pressed against the disc rotor by the lining holder 140 (301) described later.
As shown in FIG. 3, the lining assembly 10 has a friction material 11 molded in a substantially disk shape, a back plate portion 12 fixed to the back surface of the friction material 11, and a back plate portion 12 on the back surface side. A convex portion 20 for swingably supporting the lining assembly 10 provided and pressed against the disc rotor by the lining holder 140 (301) and a lining assembly 10 inserted through the guide hole portion 5 are provided in the rotor axial direction. It is equipped with a fall-out prevention mechanism for holding the X so that it can be moved and does not fall off.
　摩擦材１１は、制動時にディスクロータに押圧される。ライニング組立体１０は、プレート嵌合部１５がガイド孔部５に嵌合されていることで、ディスクロータに摩擦材１１が押圧された時に作用する制動トルクをプレート嵌合部１５からガイドプレート３に伝達する。 The friction material 11 is pressed against the disc rotor during braking. In the lining assembly 10, the plate fitting portion 15 is fitted to the guide hole portion 5, so that the braking torque acting when the friction material 11 is pressed against the disc rotor is applied from the plate fitting portion 15 to the guide plate 3 Communicate to.
　裏板部１２には、外周面がガイドプレート３に貫通形成された略円形のガイド孔部５に揺動自在に嵌合するプレート嵌合部１５と、裏板部１２の表面側に位置してガイド孔部５よりも大きな外径の抜け止めフランジ部１３と、が一体形成されている。
　プレート嵌合部１５の外周面には、図３の（ｂ）に示すように、平坦面１６が形成され、ガイド孔部５の内周面には、図４に示すように、平坦面６が形成されている。そこで、ガイド孔部５に挿通されたプレート嵌合部１５の平坦面１６は、ガイド孔部５の平坦面６に係合する。即ち、平坦面１６及び平坦面６によって非円形状に形成された裏板部１２のプレート嵌合部１５とガイド孔部５とが嵌合することで、ガイド孔部５内でのライニング組立体１０の回転を阻止するための回り止めが達成される。
　なお、プレート嵌合部１５は、ガイド孔部５との摺接によるライニング組立体１０の揺動動作が円滑になるように、ガイド孔部５側に凸の曲面状に形成されることが望ましい。 The back plate portion 12 has a plate fitting portion 15 that swingably fits into a substantially circular guide hole portion 5 whose outer peripheral surface is formed through the guide plate 3, and is located on the surface side of the back plate portion 12. A retaining flange portion 13 having an outer diameter larger than that of the guide hole portion 5 is integrally formed.
As shown in FIG. 3B, a flat surface 16 is formed on the outer peripheral surface of the plate fitting portion 15, and a flat surface 6 is formed on the inner peripheral surface of the guide hole portion 5 as shown in FIG. Is formed. Therefore, the flat surface 16 of the plate fitting portion 15 inserted into the guide hole portion 5 engages with the flat surface 6 of the guide hole portion 5. That is, the lining assembly in the guide hole portion 5 is formed by fitting the plate fitting portion 15 and the guide hole portion 5 of the back plate portion 12 formed in a non-circular shape by the flat surface 16 and the flat surface 6. A detent is achieved to prevent the rotation of 10.
It is desirable that the plate fitting portion 15 is formed in a convex curved surface shape on the guide hole portion 5 side so that the lining assembly 10 can be smoothly swung by sliding contact with the guide hole portion 5. ..
　裏板部１２の裏面には、ガイド孔部５の開口形状よりも大きい外形状を有する円形板状のロックプレート１７が固定されている。ロックプレート１７は、ガイドプレート３のガイド孔部５にプレート嵌合部１５が挿通された後、裏板部１２の裏面に設けた固定穴１４に対して貫通孔１７ａを貫通したフランジ付ピン状のジョイント部材２２の軸部を圧入することで、裏板部１２の裏面に固定されている。
　ジョイント部材２２は、裏板部１２の裏面側に突出する頭部が、ライニング組立体１０を揺動可能に支持するための凸部２０となる。 A circular plate-shaped lock plate 17 having an outer shape larger than the opening shape of the guide hole portion 5 is fixed to the back surface of the back plate portion 12. The lock plate 17 has a flanged pin shape that penetrates the through hole 17a through the fixing hole 14 provided on the back surface of the back plate portion 12 after the plate fitting portion 15 is inserted into the guide hole portion 5 of the guide plate 3. By press-fitting the shaft portion of the joint member 22 of the above, the joint member 22 is fixed to the back surface of the back plate portion 12.
The head of the joint member 22 protruding toward the back surface of the back plate portion 12 is a convex portion 20 for swingably supporting the lining assembly 10.
　裏板部１２の裏面にロックプレート１７が固定されることで、ガイドプレート３の表面３ａ側からガイド孔部５に挿通されたライニング組立体１０は、裏板部１２の抜け止めフランジ部１３とロックプレート１７とによって、ガイドプレート３に対してロータ軸方向Ｘに移動可能かつ抜け落ちないように保持される。即ち、抜け落ち防止機構が、これら抜け止めフランジ部１３及びロックプレート１７によって構成されている。 By fixing the lock plate 17 to the back surface of the back plate portion 12, the lining assembly 10 inserted into the guide hole portion 5 from the front surface 3a side of the guide plate 3 has a retaining flange portion 13 of the back plate portion 12. By the lock plate 17, the guide plate 3 is held so as to be movable in the rotor axial direction X and not to fall off. That is, the fall-out prevention mechanism is composed of the retaining flange portion 13 and the lock plate 17.
　プレート嵌合部１５には、環状のばね部材２５が嵌着される。ばね部材２５は、円環状の板ばねよりなる。ばね部材２５の外径は、ガイド孔部５よりも大きく設定されている。各ライニング組立体１０は、図４に示すように、プレート嵌合部１５がガイドプレート３の表面３ａ側からガイド孔部５に挿入装着される。そこで、プレート嵌合部１５に嵌着されたばね部材２５は、ガイドプレート３と抜け止めフランジ部１３との間に挟まれる。 An annular spring member 25 is fitted to the plate fitting portion 15. The spring member 25 is made of an annular leaf spring. The outer diameter of the spring member 25 is set to be larger than that of the guide hole portion 5. As shown in FIG. 4, each lining assembly 10 has a plate fitting portion 15 inserted and mounted in the guide hole portion 5 from the surface 3a side of the guide plate 3. Therefore, the spring member 25 fitted to the plate fitting portion 15 is sandwiched between the guide plate 3 and the retaining flange portion 13.
　本第１実施形態に係るガイドプレート組立体１は、複数個のライニング組立体１０を平面状に敷き並べた形態となる。ガイドプレート組立体１は、ライニング組立体１０の抜け止めフランジ部１３とガイドプレート３との間に挟まれたばね部材２５が、弾性変形してライニング組立体１０の厚さ方向の寸法公差を吸収する。このため、ガイドプレート組立体１では、ディスクロータに対する各ライニング組立体１０の接触性にばらつきの生じることが防止される。従って、各ライニング組立体１０は、厚さ方向の寸法公差の影響を受けずに、安定した制動特性を維持することができる。 The guide plate assembly 1 according to the first embodiment has a form in which a plurality of lining assemblies 10 are laid out in a plane. In the guide plate assembly 1, the spring member 25 sandwiched between the retaining flange portion 13 of the lining assembly 10 and the guide plate 3 elastically deforms to absorb the dimensional tolerance in the thickness direction of the lining assembly 10. .. Therefore, in the guide plate assembly 1, it is possible to prevent variations in the contact property of each lining assembly 10 with respect to the disc rotor. Therefore, each lining assembly 10 can maintain stable braking characteristics without being affected by dimensional tolerances in the thickness direction.
　また、裏板部１２の裏面側には、凸部２０が設けられている。そこで、ガイドプレート３のガイド孔部５に揺動自在に支持されたライニング組立体１０は、裏板部１２の裏面側に設けられた凸部２０を介して、ライニングホルダ１４０（３０１）によりディスクロータへ押圧される。 Further, a convex portion 20 is provided on the back surface side of the back plate portion 12. Therefore, the lining assembly 10 swingably supported by the guide hole portion 5 of the guide plate 3 is disced by the lining holder 140 (301) via the convex portion 20 provided on the back surface side of the back plate portion 12. Pressed against the rotor.
　従って、本第１実施形態に係るガイドプレート組立体１によれば、ガイドプレート３のガイド孔部５に揺動自在に支持されたライニング組立体１０は、裏板部１２の裏面側に設けられた凸部２０を介して、ライニングホルダ１４０（３０１）によりディスクロータへ押圧される。そして、ライニングホルダ１４０（３０１）による制動時の押し付け力は、ライニング組立体１０により直接、ディスクロータに伝達される。
　そこで、ガイドプレート３には、制動時の押し付け力が伝達されず、制動トルクのみが伝達される。従って、ガイドプレート３には、制動時の押し付け力を支持できる大きな強度を持たせる必要がなく、ガイドプレート３を軽量化することができる。 Therefore, according to the guide plate assembly 1 according to the first embodiment, the lining assembly 10 swingably supported by the guide hole portion 5 of the guide plate 3 is provided on the back surface side of the back plate portion 12. It is pressed against the disc rotor by the lining holder 140 (301) via the convex portion 20. Then, the pressing force at the time of braking by the lining holder 140 (301) is directly transmitted to the disc rotor by the lining assembly 10.
Therefore, the pressing force at the time of braking is not transmitted to the guide plate 3, and only the braking torque is transmitted. Therefore, it is not necessary for the guide plate 3 to have a large strength capable of supporting the pressing force at the time of braking, and the weight of the guide plate 3 can be reduced.
　更に、本第１実施形態に係るライニング組立体１０は、裏板部１２の抜け止めフランジ部１３とロックプレート１７とからなる抜け落ち防止機構により、ロータ軸方向Ｘに移動可能かつ抜け落ちないようにガイドプレート３に保持される。
　そこで、本第１実施形態のガイドプレート組立体１は、複数のライニング組立体１０をガイドプレート３にアッセンブリすることができる。従って、ガイドプレート組立体１のハンドリングが容易となりメンテナンス性が向上する。 Further, the lining assembly 10 according to the first embodiment is guided by a fall-out prevention mechanism including a retaining flange portion 13 of the back plate portion 12 and a lock plate 17 so as to be movable in the rotor axial direction X and not to come off. It is held on the plate 3.
Therefore, in the guide plate assembly 1 of the first embodiment, a plurality of lining assemblies 10 can be assembled to the guide plate 3. Therefore, the guide plate assembly 1 can be easily handled and maintainability is improved.
　また、本第１実施形態に係るガイドプレート組立体１では、裏板部１２のプレート嵌合部１５とガイド孔部５とがそれぞれ非円形状に形成されて嵌合することによって、ガイド孔部５内でのライニング組立体１０の回転が阻止される。さらに詳しくは、プレート嵌合部１５の外周面及びガイド孔部５の内周面には、ガイド孔部５内でのライニング組立体１０の回転を阻止する回り止め用の平坦面１６及び平坦面６がそれぞれ形成されている。
　そこで、本第１実施形態に係るガイドプレート組立体１によれば、ライニング組立体１０の回転を阻止するための回り止めが、プレート嵌合部１５の外周面及びガイド孔部５の内周面に形成された平坦面１６，６同士が係合することで達成される。そこで、部品点数を増加させることなくライニング組立体１０の回り止めを容易に形成することができる。即ち、ライニング組立体１０が回転すると、ディスクロータに十分な制動力を作用させることができなくなるため、ガイドプレート３に対してライニング組立体１０を回転不能にすることが望ましい。 Further, in the guide plate assembly 1 according to the first embodiment, the plate fitting portion 15 and the guide hole portion 5 of the back plate portion 12 are each formed in a non-circular shape and fitted into the guide hole portion. The rotation of the lining assembly 10 within 5 is prevented. More specifically, on the outer peripheral surface of the plate fitting portion 15 and the inner peripheral surface of the guide hole portion 5, a flat surface 16 and a flat surface for preventing rotation of the lining assembly 10 in the guide hole portion 5 are prevented from rotating. 6 are formed respectively.
Therefore, according to the guide plate assembly 1 according to the first embodiment, the detent for preventing the rotation of the lining assembly 10 is provided on the outer peripheral surface of the plate fitting portion 15 and the inner peripheral surface of the guide hole portion 5. It is achieved by engaging the flat surfaces 16 and 6 formed on the surface with each other. Therefore, the detent of the lining assembly 10 can be easily formed without increasing the number of parts. That is, when the lining assembly 10 rotates, it becomes impossible to apply a sufficient braking force to the disc rotor, so it is desirable to make the lining assembly 10 non-rotatable with respect to the guide plate 3.
　また、本第１実施形態に係るガイドプレート組立体１では、ガイドプレート３の表面３ａと、裏板部１２の抜け止めフランジ部１３との間には、ライニング組立体１０をガイドプレート３に対してロータ軸方向Ｘに沿う何れか一方であるディスクロータ側（図３の（ａ）における左側）に付勢するばね部材２５が配置されている。
　そこで、本第１実施形態に係るガイドプレート組立体１によれば、ばね部材２５がガイドプレート３の表面３ａと裏板部１２との間に配置される。そこで、後述するライニングホルダ３０１或いはトルク受けプレート１０１と裏板部１２の凸部２０との間に隙間が生じることにより、ばね部材２５が弾性変形してライニング組立体１０の厚さ方向（ロータ軸方向Ｘ）の寸法公差を吸収する。このため、本第１実施形態のガイドプレート組立体１では、ディスクロータに対する各ライニング組立体１０の接触性にばらつきの生じることが防止されると共に、異音の発生が抑制される。従って、各ライニング組立体１０は、厚さ方向の寸法公差の影響を受けずに、安定した制動特性を維持することができる。 Further, in the guide plate assembly 1 according to the first embodiment, the lining assembly 10 is placed between the surface 3a of the guide plate 3 and the retaining flange portion 13 of the back plate portion 12 with respect to the guide plate 3. A spring member 25 for urging is arranged on the disc rotor side (left side in FIG. 3A), which is one of the two along the rotor axial direction X.
Therefore, according to the guide plate assembly 1 according to the first embodiment, the spring member 25 is arranged between the surface 3a of the guide plate 3 and the back plate portion 12. Therefore, a gap is generated between the lining holder 301 or the torque receiving plate 101 and the convex portion 20 of the back plate portion 12, which will be described later, and the spring member 25 is elastically deformed in the thickness direction of the lining assembly 10 (rotor shaft). Absorbs dimensional tolerances in direction X). Therefore, in the guide plate assembly 1 of the first embodiment, it is possible to prevent variations in the contact property of each lining assembly 10 with respect to the disc rotor, and it is possible to suppress the generation of abnormal noise. Therefore, each lining assembly 10 can maintain stable braking characteristics without being affected by dimensional tolerances in the thickness direction.
　また、本第１実施形態に係るガイドプレート組立体１によれば、裏板部１２の裏面側に設けられる凸部２０が、ロックプレート１７を裏板部１２の裏面に固定するジョイント部材２２により構成される。即ち、ジョイント部材２２は、裏板部１２の裏面側に突出する頭部が、ライニング組立体１０を揺動可能に支持するための凸部２０となる。そこで、ジョイント部材２２を裏板部１２の裏面に設けた固定穴１４に圧入してロックプレート１７を固定することで、ガイド孔部５に挿通されたライニング組立体１０を抜け落ちないように保持すると共に、裏板部１２の裏面側に凸部２０を容易に構成することができる。 Further, according to the guide plate assembly 1 according to the first embodiment, the convex portion 20 provided on the back surface side of the back plate portion 12 is provided with a joint member 22 for fixing the lock plate 17 to the back surface of the back plate portion 12. It is composed. That is, in the joint member 22, the head protruding toward the back surface side of the back plate portion 12 becomes a convex portion 20 for swingably supporting the lining assembly 10. Therefore, by press-fitting the joint member 22 into the fixing hole 14 provided on the back surface of the back plate portion 12 to fix the lock plate 17, the lining assembly 10 inserted through the guide hole portion 5 is held so as not to fall off. At the same time, the convex portion 20 can be easily formed on the back surface side of the back plate portion 12.
　図５の（ａ）及び（ｂ）は、図１に示したライニング組立体１０の変形例を説明するための要部断面図及び要部分解斜視図である。
　変形例に係るライニング組立体１０は、図５の（ａ）及び（ｂ）に示すように、ガイドプレート３の裏面３ｂと、裏板部１２の裏面に固定されたロックプレート１７との間に、ライニング組立体１０をガイドプレート３に対してロータ軸方向Ｘに沿う何れか他方であるディスクロータと反対側（図５の（ａ）における右側）に付勢するばね部材２５を配置することもできる。
　このような構成のガイドプレート組立体１によれば、ばね部材２５がガイドプレート３の裏面３ｂと裏板部１２との間に配置される。そこで、本構成のガイドプレート組立体１は、ばね部材２５の付勢力により裏板部１２の凸部２０が後述するライニングホルダ３０１或いはトルク受けプレート１０１に押し付けられた状態となり、ブレーキ時の応答性が向上する。 5 (a) and 5 (b) are a cross-sectional view of a main part and an exploded perspective view of the main part for explaining a modified example of the lining assembly 10 shown in FIG.
As shown in FIGS. 5A and 5B, the lining assembly 10 according to the modified example is between the back surface 3b of the guide plate 3 and the lock plate 17 fixed to the back surface of the back plate portion 12. It is also possible to arrange a spring member 25 for urging the lining assembly 10 with respect to the guide plate 3 on the opposite side (right side in (a) of FIG. 5) to the disc rotor which is the other side along the rotor axial direction X. can.
According to the guide plate assembly 1 having such a configuration, the spring member 25 is arranged between the back surface 3b of the guide plate 3 and the back plate portion 12. Therefore, in the guide plate assembly 1 having this configuration, the convex portion 20 of the back plate portion 12 is pressed against the lining holder 301 or the torque receiving plate 101, which will be described later, by the urging force of the spring member 25, and the responsiveness at the time of braking is achieved. Is improved.
　図６の（ａ）～（ｃ）は、図１に示したライニング組立体１０の他の変形例を説明するための正面図、Ａ－Ａ断面図及び分解斜視図であり、（ｄ）は（ｃ）に示したジョイント部材３２を説明する斜視図である。なお、上記ライニング組立体１０と同様の構成部材については、同符号を付して詳細な説明を省略する。 6A to 6C are a front view, a sectional view taken along the line AA, and an exploded perspective view for explaining another modification of the lining assembly 10 shown in FIG. 1, and FIG. 6D is an exploded perspective view. It is a perspective view explaining the joint member 32 shown in (c). The same components as those of the lining assembly 10 are designated by the same reference numerals, and detailed description thereof will be omitted.
　他の変形例に係るライニング組立体１０Ａは、図６の（ａ）～（ｃ）に示すように、裏板部１２の段付き固定穴１４Ａを貫通した先端のハトメ３３によりロックプレート１７を裏板部１２の裏面に固定するジョイント部材３２からなる凸部２０を有する。
　ジョイント部材３２は、図６の（ｄ）に示すように、ロックプレート１７の貫通孔１７ａ及び裏板部１２の段付き固定穴１４に軸部を挿通した後、摩擦材１１に形成した開口１１ａ側から治具を挿入し、先端のハトメ３３を外側に折り曲げて段部に係止させる。そこで、ジョイント部材３２は、ロックプレート１７を裏板部１２の裏面に固定すると共に、裏板部１２の裏面側に突出する頭部が、ライニング組立体１０Ａを揺動可能に支持するための凸部２０となる。 As shown in FIGS. 6A to 6C, the lining assembly 10A according to another modification backs the lock plate 17 with eyelets 33 at the tip penetrating the stepped fixing hole 14A of the back plate portion 12. It has a convex portion 20 made of a joint member 32 fixed to the back surface of the plate portion 12.
As shown in FIG. 6D, the joint member 32 has an opening 11a formed in the friction material 11 after the shaft portion is inserted into the through hole 17a of the lock plate 17 and the stepped fixing hole 14 of the back plate portion 12. A jig is inserted from the side, and the eyelet 33 at the tip is bent outward to be locked to the step portion. Therefore, in the joint member 32, the lock plate 17 is fixed to the back surface of the back plate portion 12, and the head projecting to the back surface side of the back plate portion 12 is convex for swingably supporting the lining assembly 10A. It becomes part 20.
　従って、本構成のライニング組立体１０Ａによれば、先端にハトメ３３を有するジョイント部材３２によりロックプレート１７が裏板部１２の裏面に容易に固定される。そこで、本構成のライニング組立体１０Ａは、ガイド孔部５に挿通されたライニング組立体１０Ａを抜け落ちないように保持すると共に、裏板部１２の裏面側に凸部２０を容易に構成することができる。 Therefore, according to the lining assembly 10A having the present configuration, the lock plate 17 is easily fixed to the back surface of the back plate portion 12 by the joint member 32 having the eyelet 33 at the tip. Therefore, the lining assembly 10A having the present configuration can hold the lining assembly 10A inserted through the guide hole portion 5 so as not to fall off, and can easily form the convex portion 20 on the back surface side of the back plate portion 12. can.
　図７の（ａ）及び（ｂ）は図１に示したライニング組立体１０の他の変形例を説明するための正面図及びＢ－Ｂ断面図であり、（ｃ）は図１に示したライニング組立体１０の別の変形例を説明するための断面図である。なお、上記ライニング組立体１０と同様の構成部材については、同符号を付して詳細な説明を省略する。 7 (a) and 7 (b) are a front view and a sectional view taken along the line BB for explaining another modification of the lining assembly 10 shown in FIG. 1, and FIG. 7 (c) is shown in FIG. It is sectional drawing for demonstrating another modification of a lining assembly 10. The same components as those of the lining assembly 10 are designated by the same reference numerals, and detailed description thereof will be omitted.
　他の変形例に係るライニング組立体１０Ｂは、図７の（ａ）及び（ｂ）に示すように、裏板部１２の裏面側に設けられる凸部２０が、ジョイント部材４３により構成されている。ジョイント部材４３は、裏板部１２の凹部１２ａに載置される円板状の基部４３ａと、基部４３ａより小径のロックプレート１７の貫通孔１７ａに貫通されるピン状の軸部４３ｂとを有する。ジョイント部材４３は、基部４３ａを裏板部１２の凹部１２ａに載置した後、軸部４３ｂを貫通孔１７ａに挿通させたロックプレート１７を裏板部１２の裏面に固定することで、裏板部１２の裏面側に固定される。即ち、ジョイント部材４３は、裏板部１２の裏面側に突出する軸部４３ｂが、ライニング組立体１０Ｂを揺動可能に支持するための凸部２０となる。 In the lining assembly 10B according to another modification, as shown in FIGS. 7A and 7B, the convex portion 20 provided on the back surface side of the back plate portion 12 is composed of the joint member 43. .. The joint member 43 has a disk-shaped base portion 43a placed in the recess 12a of the back plate portion 12 and a pin-shaped shaft portion 43b penetrating through the through hole 17a of the lock plate 17 having a diameter smaller than that of the base portion 43a. .. The joint member 43 is formed by placing the base portion 43a in the recess 12a of the back plate portion 12 and then fixing the lock plate 17 through which the shaft portion 43b is inserted into the through hole 17a to the back surface of the back plate portion 12. It is fixed to the back surface side of the portion 12. That is, in the joint member 43, the shaft portion 43b protruding toward the back surface side of the back plate portion 12 becomes a convex portion 20 for swingably supporting the lining assembly 10B.
　本構成のロックプレート１７は、ロックプレート１７の固定孔１７ｂと裏板部１２の固定穴１４とを貫通させたリベット４５により裏板部１２の裏面に固定される。
　そこで、安価なリベット４５によりロックプレート１７を裏板部１２の裏面に容易に固定することができる。但し、摩擦材１１には、リベット４５を固定するためのリベット用凹部１８を設ける必要がある。 The lock plate 17 having this configuration is fixed to the back surface of the back plate portion 12 by a rivet 45 penetrating the fixing hole 17b of the lock plate 17 and the fixing hole 14 of the back plate portion 12.
Therefore, the lock plate 17 can be easily fixed to the back surface of the back plate portion 12 by an inexpensive rivet 45. However, the friction material 11 needs to be provided with a rivet recess 18 for fixing the rivet 45.
　別の変形例に係るライニング組立体１０Ｃは、図７の（ｃ）に示すように、裏板部１２の裏面側に設けられる凸部２０が、上記ライニング組立体１０Ｂと同様に、ジョイント部材４３により構成されている。
　ライニング組立体１０Ｃのロックプレート１７は、ロックプレート１７の固定孔１７ｂと裏板部１２の固定穴１４とを貫通させたブラインドリベット５３により裏板部１２の裏面に固定される。 In the lining assembly 10C according to another modification, as shown in FIG. 7C, the convex portion 20 provided on the back surface side of the back plate portion 12 has a joint member 43 similar to the lining assembly 10B. It is composed of.
The lock plate 17 of the lining assembly 10C is fixed to the back surface of the back plate portion 12 by a blind rivet 53 penetrating the fixing hole 17b of the lock plate 17 and the fixing hole 14 of the back plate portion 12.
　そこで、ブラインドリベット５３によりロックプレート１７が固定されたライニング組立体１０Ｃは、上記ライニング組立体１０Ｂのようにリベット４５を固定するためのリベット用凹部１８を摩擦材１１に設ける必要がなく、ディスクロータに対する摩擦材１１の接触面積が低下することはない。 Therefore, the lining assembly 10C to which the lock plate 17 is fixed by the blind rivet 53 does not need to provide the rivet recess 18 for fixing the rivet 45 in the friction material 11 as in the lining assembly 10B, and is a disc rotor. The contact area of the friction material 11 with respect to the rivet 11 does not decrease.
　図８の（ａ）及び（ｂ）は、図１に示したライニング組立体１０の他の変形例を説明するための正面図及びＣ－Ｃ断面図である。なお、上記ライニング組立体１０と同様の構成部材については、同符号を付して詳細な説明を省略する。
　他の変形例に係るライニング組立体１０Ｄは、図８の（ａ）及び（ｂ）に示すように、ガイド孔部５を挿通可能な外径を有する略円板状に成型された摩擦材１１と、この摩擦材１１の裏面に固着された裏板部１２Ａと、裏板部１２Ａの裏面側に設けられ、ライニングホルダ１４０（３０１）によりディスクロータへ押圧されたライニング組立体１０Ｄを揺動可能に支持するための凸部２０と、ガイド孔部５に挿通されたライニング組立体１０Ｄをロータ軸方向Ｘに移動可能かつ抜け落ちないように保持するための抜け落ち防止機構と、を備えている。 8 (a) and 8 (b) are a front view and a sectional view taken along the line CC for explaining another modification of the lining assembly 10 shown in FIG. The same components as those of the lining assembly 10 are designated by the same reference numerals, and detailed description thereof will be omitted.
As shown in FIGS. 8A and 8B, the lining assembly 10D according to another modification is a friction material 11 molded into a substantially disk shape having an outer diameter through which the guide hole portion 5 can be inserted. The back plate portion 12A fixed to the back surface of the friction material 11 and the lining assembly 10D provided on the back surface side of the back plate portion 12A and pressed against the disc rotor by the lining holder 140 (301) can be swung. It is provided with a convex portion 20 for supporting the lining, and a fall-off prevention mechanism for holding the lining assembly 10D inserted through the guide hole portion 5 so as to be movable in the rotor axial direction X and not to fall off.
　凸部２０は、裏板部１２Ａの裏面に設けた固定穴１４に圧入されて裏面側に突出するジョイント部材２２の頭部により構成されている。ジョイント部材２２は、裏板部１２Ａと別体で構成されることにより、ライニング組立体１０Ｄを揺動可能に支持するための凸部２０として、耐摩耗性等に優れた最適な材質を選択することができる。 The convex portion 20 is composed of a head of a joint member 22 that is press-fitted into a fixing hole 14 provided on the back surface of the back plate portion 12A and projects toward the back surface side. Since the joint member 22 is formed separately from the back plate portion 12A, the optimum material having excellent wear resistance and the like is selected as the convex portion 20 for swingably supporting the lining assembly 10D. be able to.
　裏板部１２Ａには、外周面がガイドプレート３に貫通形成された略円形のガイド孔部５に揺動自在に嵌合するプレート嵌合部１５と、裏板部１２Ａの裏面側に位置してガイド孔部５よりも大きな外径の抜け止めフランジ部１３と、が一体形成されている。
　プレート嵌合部１５の外周面には、スナップリング５１が装着される環状溝１９が形成されている。 The back plate portion 12A is located on the back surface side of the back plate portion 12A and the plate fitting portion 15 which swingably fits into the substantially circular guide hole portion 5 whose outer peripheral surface is formed through the guide plate 3. A retaining flange portion 13 having an outer diameter larger than that of the guide hole portion 5 is integrally formed.
An annular groove 19 on which the snap ring 51 is mounted is formed on the outer peripheral surface of the plate fitting portion 15.
　裏板部１２Ａにおけるプレート嵌合部１５の環状溝１９には、ガイド孔部５の開口形状よりも大きい外形状を有すると共に、プレート嵌合部１５の外径より小さい内形状を有するスナップリング５１が装着されている。
　裏板部１２Ａにおけるプレート嵌合部１５の環状溝１９には、スナップリング５１が装着される。そこで、ガイドプレート３の裏面３ｂ側からガイド孔部５に挿通されたライニング組立体１０Ｄは、裏板部１２Ａの抜け止めフランジ部１３とスナップリング５１とによって、ガイドプレート３に対してロータ軸方向Ｘに移動可能かつ抜け落ちないように保持される。即ち、抜け落ち防止機構が、これら抜け止めフランジ部１３及びスナップリング５１によって構成されている。 The annular groove 19 of the plate fitting portion 15 in the back plate portion 12A has an outer shape larger than the opening shape of the guide hole portion 5, and a snap ring 51 having an inner shape smaller than the outer diameter of the plate fitting portion 15. Is installed.
A snap ring 51 is attached to the annular groove 19 of the plate fitting portion 15 in the back plate portion 12A. Therefore, the lining assembly 10D inserted into the guide hole portion 5 from the back surface 3b side of the guide plate 3 is in the rotor axial direction with respect to the guide plate 3 by the retaining flange portion 13 of the back plate portion 12A and the snap ring 51. It is movable to X and is held so that it will not fall out. That is, the fall-off prevention mechanism is composed of the retaining flange portion 13 and the snap ring 51.
　プレート嵌合部１５に嵌着されたばね部材２５は、ガイドプレート３とスナップリング５１との間に挟まれ、弾性変形してライニング組立体１０Ｄの厚さ方向の寸法公差を吸収する。 The spring member 25 fitted to the plate fitting portion 15 is sandwiched between the guide plate 3 and the snap ring 51 and elastically deformed to absorb the dimensional tolerance in the thickness direction of the lining assembly 10D.
　図９の（ａ）及び（ｂ）は、本発明の第２実施形態に係るトルク受けプレート１０１を表側から見た斜視図及び裏側から見た斜視図である。図１０は、本第２実施形態に係るトルク受けプレート１０１及び本第１実施形態に係るガイドプレート組立体１の斜視図である。図１１の（ａ）は本第２実施形態に係るトルク受けプレート１０１に本第１実施形態に係るガイドプレート組立体１が組み付けられたディスクブレーキ用摩擦パッド組立て体１００を表側から見た斜視図であり、図１１の（ｂ）は図１１の（ａ）のＤ－Ｄ断面図である。 9 (a) and 9 (b) are a perspective view of the torque receiving plate 101 according to the second embodiment of the present invention as viewed from the front side and a perspective view as viewed from the back side. FIG. 10 is a perspective view of the torque receiving plate 101 according to the second embodiment and the guide plate assembly 1 according to the first embodiment. FIG. 11A is a perspective view of the disc brake friction pad assembly 100 in which the guide plate assembly 1 according to the first embodiment is assembled to the torque receiving plate 101 according to the second embodiment. 11 (b) is a cross-sectional view taken along the line DD of FIG. 11 (a).
　本第２実施形態に係るトルク受けプレート１０１は、図９の（ａ）及び（ｂ）に示すように、ガイドプレート３の周縁部分に嵌合してガイドプレート組立体１を着脱自在に保持する複数の溝部１０５が設けられる。そして、トルク受けプレート１０１は、表面１０１ａでライニング組立体１０の凸部２０を揺動可能に支持する。トルク受けプレート１０１の裏面１０１ｂには、蟻溝状の固定溝１４１が設けられたライニングホルダ１４０（図１３参照）へ、溝端から挿入されるアンカープレート１２０を備えている。
　トルク受けプレート１０１の長手方向両端部には、円形状の穴に形成された一対のアンカーピン嵌合部１１０が形成されている。 As shown in FIGS. 9A and 9B, the torque receiving plate 101 according to the second embodiment is fitted to the peripheral edge portion of the guide plate 3 to detachably hold the guide plate assembly 1. A plurality of grooves 105 are provided. Then, the torque receiving plate 101 swingably supports the convex portion 20 of the lining assembly 10 on the surface 101a. The back surface 101b of the torque receiving plate 101 is provided with an anchor plate 120 that is inserted from the groove end into a lining holder 140 (see FIG. 13) provided with a dovetail groove-shaped fixing groove 141.
A pair of anchor pin fitting portions 110 formed in circular holes are formed at both ends of the torque receiving plate 101 in the longitudinal direction.
　図１０に示すように、ガイドプレート組立体１は、トルク受けプレート１０１の長手方向一端側からガイドプレート３の周縁部分が溝部１０５に嵌合される。図１１の（ａ），
（ｂ）に示すように、ガイドプレート３の裏面３ｂがトルク受けプレート１０１の表面１０１ａに対向するように重ね合わされることで、ディスクブレーキ用摩擦パッド組立て体１００が構成される。 As shown in FIG. 10, in the guide plate assembly 1, the peripheral edge portion of the guide plate 3 is fitted into the groove 105 from one end side in the longitudinal direction of the torque receiving plate 101. FIG. 11 (a),
As shown in (b), the back surface 3b of the guide plate 3 is overlapped so as to face the surface 101a of the torque receiving plate 101, whereby the disc brake friction pad assembly 100 is configured.
　トルク受けプレート１０１の溝部１０５に保持されたガイドプレート３は、図１１の（ｂ）に示すように、トルク受けプレート１０１の表面１０１ａとの間に、ライニング組立体１０を揺動可能とする内部空間Ｓを画成している。
　ガイドプレート組立体１は、トルク受けプレート１０１の一対のアンカーピン嵌合部１１０にそれぞれ嵌挿されたアンカーピン１３０が、ガイドプレート３のアンカーピン係合部９を貫通すると共にアンカーピン係合部７に係合することで、トルク受けプレート１０１に固定される。 As shown in FIG. 11B, the guide plate 3 held in the groove portion 105 of the torque receiving plate 101 has an inside that allows the lining assembly 10 to swing between the surface 101a and the surface 101a of the torque receiving plate 101. The space S is defined.
In the guide plate assembly 1, the anchor pins 130 fitted into the pair of anchor pin fitting portions 110 of the torque receiving plate 101 penetrate the anchor pin engaging portion 9 of the guide plate 3 and the anchor pin engaging portion. By engaging with 7, it is fixed to the torque receiving plate 101.
　図１２は、図１１に示したディスクブレーキ用摩擦パッド組立て体１００がライニングホルダ１４０に組み付けられた状態を説明する概略斜視図である。図１３は、図１２におけるＥ－Ｅ断面図である。
　ディスクブレーキ用摩擦パッド組立て体１００は、図１２及び図１３に示すように、キャリパーのライニングホルダ１４０に取り付けられる。トルク受けプレート１０１の裏面１０１ｂには、アンカープレート１２０がリベット１３３によって固定される。ディスクブレーキ用摩擦パッド組立て体１００は、このアンカープレート１２０が、ライニングホルダ１４０におけるブレーキパッド取付部１４３（ライニングホルダ１４０のディスクロータ側取付面）に形成された蟻溝状の固定溝１４１に、溝端から挿入されることにより取り付けられる。 FIG. 12 is a schematic perspective view illustrating a state in which the disc brake friction pad assembly 100 shown in FIG. 11 is assembled to the lining holder 140. FIG. 13 is a cross-sectional view taken along the line EE in FIG.
The disc brake friction pad assembly 100 is attached to the caliper lining holder 140 as shown in FIGS. 12 and 13. An anchor plate 120 is fixed to the back surface 101b of the torque receiving plate 101 by rivets 133. In the disc brake friction pad assembly 100, the anchor plate 120 has a groove end in a dovetail groove-shaped fixing groove 141 formed in the brake pad mounting portion 143 (disc rotor side mounting surface of the lining holder 140) in the lining holder 140. It is attached by being inserted from.
　ディスクブレーキ用摩擦パッド組立て体１００は、トルク受けプレート１０１の裏面１０１ｂが、このライニングホルダ１４０のブレーキパッド取付部１４３に密着する。
　ガイドプレート３のガイド孔部５に揺動自在に支持されたライニング組立体１０は、裏板部１２の裏面側に設けられた凸部２０を介して、ライニングホルダ１４０によりディスクロータへ押圧される。そして、ライニングホルダ１４０による制動時の押し付け力は、ライニング組立体１０により直接、ディスクロータに伝達される。そこで、ガイドプレート３には、制動時の押し付け力が伝達されず、制動トルクのみが伝達される。 In the disc brake friction pad assembly 100, the back surface 101b of the torque receiving plate 101 is in close contact with the brake pad mounting portion 143 of the lining holder 140.
The lining assembly 10 swingably supported by the guide hole portion 5 of the guide plate 3 is pressed against the disc rotor by the lining holder 140 via the convex portion 20 provided on the back surface side of the back plate portion 12. .. Then, the pressing force during braking by the lining holder 140 is directly transmitted to the disc rotor by the lining assembly 10. Therefore, the pressing force at the time of braking is not transmitted to the guide plate 3, and only the braking torque is transmitted.
　ディスクブレーキ用摩擦パッド組立て体１００によれば、複数のライニング組立体１０がガイドプレート３にアッセンブリされたガイドプレート組立体１は、アンカープレート１２０を有するトルク受けプレート１０１に着脱自在に保持される。そこで、本構成のディスクブレーキ用摩擦パッド組立て体１００は、ライニングホルダ１４０の蟻溝状の固定溝１４１にトルク受けプレート１０１のアンカープレート１２０を挿入することができる。これにより、本構成のディスクブレーキ用摩擦パッド組立て体１００は、ガイドプレート３の形状が異なる複数種のガイドプレート組立体１をライニングホルダ１４０に着脱自在に取付けることができる。 According to the disc brake friction pad assembly 100, the guide plate assembly 1 in which a plurality of lining assemblies 10 are assembled on the guide plate 3 is detachably held by the torque receiving plate 101 having the anchor plate 120. Therefore, in the disc brake friction pad assembly 100 having the present configuration, the anchor plate 120 of the torque receiving plate 101 can be inserted into the dovetail groove-shaped fixing groove 141 of the lining holder 140. As a result, in the disc brake friction pad assembly 100 having the present configuration, a plurality of types of guide plate assemblies 1 having different shapes of the guide plates 3 can be detachably attached to the lining holder 140.
　ディスクブレーキ用摩擦パッド組立て体１００は、裏板部１２のプレート嵌合部１５がガイドプレート３のガイド孔部５に挿入装着され、ディスクロータと摩擦材１１との接触時に作用する制動トルクが、プレート嵌合部１５からガイドプレート３に伝達され、更にガイドプレート３のアンカーピン係合部７，９からアンカーピン１３０によりトルク受けプレート１０１のアンカーピン嵌合部１１０に伝達され、更にトルク受けプレート１０１のアンカープレート１２０からアンカープレート固定部材１４５によりライニングホルダ１４０の固定部であるブレーキパッド取付部１４３に伝達される。 In the disc brake friction pad assembly 100, the plate fitting portion 15 of the back plate portion 12 is inserted and mounted in the guide hole portion 5 of the guide plate 3, and the braking torque acting when the disc rotor and the friction material 11 come into contact with each other is generated. It is transmitted from the plate fitting portion 15 to the guide plate 3, and further transmitted from the anchor pin engaging portions 7 and 9 of the guide plate 3 to the anchor pin fitting portion 110 of the torque receiving plate 101 by the anchor pin 130, and further transmitted to the anchor pin fitting portion 110 of the torque receiving plate 101. It is transmitted from the anchor plate 120 of 101 to the brake pad mounting portion 143 which is the fixing portion of the lining holder 140 by the anchor plate fixing member 145.
　そこで、ライニングホルダ１４０のブレーキパッド取付部１４３にアンカープレート固定部材１４５によりアンカープレート１２０が固定されたトルク受けプレート１０１に対して、アンカーピン１３０を介して固定されたガイドプレート組立体１は、アンカーピン１３０を取り外すだけで交換可能となる。そのため、ディスクブレーキ用摩擦パッド組立て体１００は、交換部品の軽量化が可能となりメンテナンス性が向上する。 Therefore, the guide plate assembly 1 fixed via the anchor pin 130 to the torque receiving plate 101 in which the anchor plate 120 is fixed to the brake pad mounting portion 143 of the lining holder 140 by the anchor plate fixing member 145 is an anchor. It can be replaced simply by removing the pin 130. Therefore, the disc brake friction pad assembly 100 can reduce the weight of replacement parts and improve maintainability.
　また、ディスクブレーキ用摩擦パッド組立て体１００によれば、制動方向に対向して制動トルクを受けるガイドプレート３のアンカーピン係合部７が半円形状に形成される。そこで、ディスクブレーキ用摩擦パッド組立て体１００は、円形状に形成したアンカーピン係合部９よりもガイドプレート３が大型化するのを抑制できる。 Further, according to the disc brake friction pad assembly 100, the anchor pin engaging portion 7 of the guide plate 3 facing the braking direction and receiving the braking torque is formed in a semicircular shape. Therefore, the disc brake friction pad assembly 100 can prevent the guide plate 3 from becoming larger than the anchor pin engaging portion 9 formed in a circular shape.
　また、ディスクブレーキ用摩擦パッド組立て体１００では、ガイドプレート３における複数のアンカーピン係合部７，９のうちで、ブレーキキャリパに取り付けられた際に鉛直方向下側に位置するアンカーピン係合部９が、円形状に形成されて制動トルクを受ける。
　そこで、ディスクブレーキ用摩擦パッド組立て体１００によれば、アンカーピン係合部９が円形状に形成されることで、アンカーピン係合部９はそれぞれの制動方向に対向して制動トルクを受けることができる。 Further, in the disc brake friction pad assembly 100, among the plurality of anchor pin engaging portions 7 and 9 in the guide plate 3, the anchor pin engaging portion located on the lower side in the vertical direction when attached to the brake caliper. 9 is formed in a circular shape and receives a braking torque.
Therefore, according to the disc brake friction pad assembly 100, the anchor pin engaging portion 9 is formed in a circular shape, so that the anchor pin engaging portion 9 receives braking torque facing each braking direction. Can be done.
　また、ブレーキキャリパに取り付けられた際に鉛直方向上側に円形状のアンカーピン係合部９が位置すると、ガイドプレート組立体１を着脱する際に鉛直方向上側に配置されたアンカーピン１３０も着脱しなければならず、作業性がよくない。これに対し、ブレーキキャリパに取り付けられた際に鉛直方向下側に円形状のアンカーピン係合部９が位置し、鉛直方向上側に半円形状のアンカーピン係合部７が位置する場合には、鉛直方向下側に配置されたアンカーピン１３０を着脱するだけでよく、着脱作業が容易となる。なお、鉛直方向上側のアンカーピン係合部７を省略し、鉛直方向下側のアンカーピン係合部９のみで制動トルクを受けることもできる。 Further, when the circular anchor pin engaging portion 9 is located on the upper side in the vertical direction when attached to the brake caliper, the anchor pin 130 arranged on the upper side in the vertical direction is also attached / detached when attaching / detaching the guide plate assembly 1. It has to be, and workability is not good. On the other hand, when it is attached to the brake caliper, the circular anchor pin engaging portion 9 is located on the lower side in the vertical direction, and the semicircular anchor pin engaging portion 7 is located on the upper side in the vertical direction. It is only necessary to attach / detach the anchor pin 130 arranged on the lower side in the vertical direction, which facilitates the attachment / detachment work. It is also possible to omit the anchor pin engaging portion 7 on the upper side in the vertical direction and receive the braking torque only on the anchor pin engaging portion 9 on the lower side in the vertical direction.
　図１４は、図１に示した本第１実施形態の変形例に係るガイドプレート組立体１Ａを示す斜視図である。なお、上記ガイドプレート組立体１と同様の構成部材については、同符号を付して詳細な説明を省略する。
　ガイドプレート組立体１Ａは、図１４に示すように、ガイドプレート３Ａの長手方向両端部に形成された一対のアンカーピン係合部７，７がそれぞれ半円形状に形成される。そこで、ガイドプレート組立体１Ａは、上記ガイドプレート組立体１よりも小型・軽量化することができる。 FIG. 14 is a perspective view showing the guide plate assembly 1A according to the modified example of the first embodiment shown in FIG. The same components as those of the guide plate assembly 1 are designated by the same reference numerals, and detailed description thereof will be omitted.
As shown in FIG. 14, in the guide plate assembly 1A, a pair of anchor pin engaging portions 7 and 7 formed at both ends in the longitudinal direction of the guide plate 3A are formed in a semicircular shape, respectively. Therefore, the guide plate assembly 1A can be made smaller and lighter than the guide plate assembly 1.
　図１５の（ａ）及び（ｂ）は本発明の第３実施形態に係るライニングホルダ３０１を表側から見た斜視図及び裏側から見た斜視図である。図１６は、本第３実施形態に係るライニングホルダ３０１に本第１実施に係るガイドプレート組立体１が組み付けられたディスクブレーキ用摩擦パッド組立て体２００を表側から見た斜視図である。 15 (a) and 15 (b) are a perspective view of the lining holder 301 according to the third embodiment of the present invention as viewed from the front side and a perspective view as viewed from the back side. FIG. 16 is a perspective view of a disc brake friction pad assembly 200 in which the guide plate assembly 1 according to the first embodiment is assembled to the lining holder 301 according to the third embodiment as viewed from the front side.
　本第３実施形態に係るライニングホルダ３０１は、図１５の（ａ）及び（ｂ）に示すように、ガイドプレート３の周縁部分に嵌合してガイドプレート組立体１を着脱自在に保持する複数の溝部３０５が設けられる。そして、ライニングホルダ３０１は、表面３０１ａでライニング組立体１０の凸部２０を揺動可能に支持する。ライニングホルダ３０１の裏面３０１ｂには、キャリパーに取付けられるブレーキパッド取付部３２０が設けられている。
　ライニングホルダ３０１の長手方向両端部には、円形状の穴に形成された一対のアンカーピン嵌合部３１０が形成されている。 As shown in FIGS. 15A and 15B, the lining holder 301 according to the third embodiment is fitted to the peripheral edge portion of the guide plate 3 to detachably hold the guide plate assembly 1. Groove 305 is provided. Then, the lining holder 301 swingably supports the convex portion 20 of the lining assembly 10 on the surface 301a. A brake pad mounting portion 320 to be mounted on the caliper is provided on the back surface 301b of the lining holder 301.
A pair of anchor pin fitting portions 310 formed in circular holes are formed at both ends of the lining holder 301 in the longitudinal direction.
　ガイドプレート組立体１は、ライニングホルダ３０１の長手方向一端側からガイドプレート３の周縁部分が溝部３０５に嵌合される。そして、図１６に示すように、ガイドプレート３の裏面３ｂがライニングホルダ３０１の表面３０１ａに対向するように重ね合わされることで、ディスクブレーキ用摩擦パッド組立て体２００が構成される。 In the guide plate assembly 1, the peripheral edge portion of the guide plate 3 is fitted into the groove portion 305 from one end side in the longitudinal direction of the lining holder 301. Then, as shown in FIG. 16, the back surface 3b of the guide plate 3 is overlapped so as to face the surface 301a of the lining holder 301, whereby the disc brake friction pad assembly 200 is configured.
　ライニングホルダ３０１の溝部３０５に保持されたガイドプレート３は、ライニングホルダ３０１の表面３０１ａとの間に、ライニング組立体１０を揺動可能とする内部空間Ｓを画成している。
　ガイドプレート組立体１は、ライニングホルダ３０１の一対のアンカーピン嵌合部３１０にそれぞれ嵌挿されたアンカーピン１３０が、ガイドプレート３のアンカーピン係合部９を貫通すると共にアンカーピン係合部７に係合する。そこで、ガイドプレート組立体１は、ライニングホルダ３０１に固定される。 The guide plate 3 held in the groove portion 305 of the lining holder 301 defines an internal space S that allows the lining assembly 10 to swing with the surface 301a of the lining holder 301.
In the guide plate assembly 1, the anchor pins 130 fitted into the pair of anchor pin fitting portions 310 of the lining holder 301 penetrate the anchor pin engaging portion 9 of the guide plate 3 and the anchor pin engaging portion 7 Engage in. Therefore, the guide plate assembly 1 is fixed to the lining holder 301.
　ガイドプレート３のガイド孔部５に揺動自在に支持されたライニング組立体１０は、裏板部１２の裏面側に設けられた凸部２０を介して、ライニングホルダ３０１によりディスクロータへ押圧される。そして、ライニングホルダ３０１による制動時の押し付け力は、ライニング組立体１０により直接、ディスクロータに伝達される。そこで、ガイドプレート３には、制動時の押し付け力が伝達されず、制動トルクのみが伝達される。 The lining assembly 10 swingably supported by the guide hole portion 5 of the guide plate 3 is pressed against the disc rotor by the lining holder 301 via the convex portion 20 provided on the back surface side of the back plate portion 12. .. Then, the pressing force during braking by the lining holder 301 is directly transmitted to the disc rotor by the lining assembly 10. Therefore, the pressing force at the time of braking is not transmitted to the guide plate 3, and only the braking torque is transmitted.
　ディスクブレーキ用摩擦パッド組立て体２００によれば、複数のライニング組立体１０がガイドプレート３にアッセンブリされたガイドプレート組立体１は、ライニングホルダ３０１に着脱自在に保持される。そこで、本構成のディスクブレーキ用摩擦パッド組立て体２００は、ガイドプレート組立体１の交換が容易となりメンテナンス性が向上する。 According to the disc brake friction pad assembly 200, the guide plate assembly 1 in which a plurality of lining assemblies 10 are assembled on the guide plate 3 is detachably held by the lining holder 301. Therefore, in the disc brake friction pad assembly 200 having the present configuration, the guide plate assembly 1 can be easily replaced and the maintainability is improved.
　ディスクブレーキ用摩擦パッド組立て体２００は、裏板部１２のプレート嵌合部１５がガイドプレート３のガイド孔部５に挿入装着され、ディスクロータと摩擦材１１との接触時に作用する制動トルクが、プレート嵌合部１５からガイドプレート３に伝達され、更にガイドプレート３のアンカーピン係合部７，９からアンカーピン１３０によりライニングホルダ３０１のアンカーピン嵌合部３１０に伝達される。 In the disc brake friction pad assembly 200, the plate fitting portion 15 of the back plate portion 12 is inserted and mounted in the guide hole portion 5 of the guide plate 3, and the braking torque acting when the disc rotor and the friction material 11 come into contact with each other is generated. It is transmitted from the plate fitting portion 15 to the guide plate 3, and further transmitted from the anchor pin engaging portions 7 and 9 of the guide plate 3 to the anchor pin fitting portion 310 of the lining holder 301 by the anchor pin 130.
　そこで、ディスクブレーキ用摩擦パッド組立て体２００によれば、アンカーピン１３０を介してライニングホルダ３０１に固定されたガイドプレート組立体１は、アンカーピン１３０を取り外すだけで交換可能となる。そのため、ディスクブレーキ用摩擦パッド組立て体２００は、交換部品の軽量化が可能となりメンテナンス性が向上する。 Therefore, according to the disc brake friction pad assembly 200, the guide plate assembly 1 fixed to the lining holder 301 via the anchor pin 130 can be replaced only by removing the anchor pin 130. Therefore, the disc brake friction pad assembly 200 can reduce the weight of replacement parts and improve maintainability.
　図１７は、本発明の第４実施形態に係るガイドプレート組立体１Ｂを裏側から見た斜視図である。図１８は、図１７に示したガイドプレート組立体１Ｂの分解斜視図である。なお、上記ガイドプレート組立体１Ａと同様の構成部材については、同符号を付して詳細な説明を省略する。 FIG. 17 is a perspective view of the guide plate assembly 1B according to the fourth embodiment of the present invention as viewed from the back side. FIG. 18 is an exploded perspective view of the guide plate assembly 1B shown in FIG. The same components as those of the guide plate assembly 1A are designated by the same reference numerals, and detailed description thereof will be omitted.
　本第４実施形態に係るガイドプレート組立体１Ｂは、図１７に示すように、ガイドプレート３Ａの裏面３ｂ側に、ライニング組立体１０の凸部２０を覆う減衰層７０が設けられる。
　減衰層７０は、均一な厚みで形成される。減衰層７０は、図１８に示すように、ガイドプレート３Ａの裏面３ｂに沿うことで、ガイドプレート３Ａと略相似形状で形成されている。減衰層７０には、ガイドプレート３Ａの裏面３ｂに設けたスペーサ７５を介して締結部材８０により固定するための固定穴７１が穿設されている。減衰層７０の表面は、ガイドプレート３Ａの裏面３ｂと平行な平坦面となる。減衰層７０は、締結部材８０によってガイドプレート３Ａの裏面３ｂに固定される。 As shown in FIG. 17, the guide plate assembly 1B according to the fourth embodiment is provided with a damping layer 70 covering the convex portion 20 of the lining assembly 10 on the back surface 3b side of the guide plate 3A.
The damping layer 70 is formed with a uniform thickness. As shown in FIG. 18, the damping layer 70 is formed along the back surface 3b of the guide plate 3A in a shape substantially similar to that of the guide plate 3A. The damping layer 70 is provided with a fixing hole 71 for fixing by the fastening member 80 via a spacer 75 provided on the back surface 3b of the guide plate 3A. The surface of the damping layer 70 is a flat surface parallel to the back surface 3b of the guide plate 3A. The damping layer 70 is fixed to the back surface 3b of the guide plate 3A by the fastening member 80.
　減衰層７０には、例えば金属支持板と弾性材が貼りあわせて積層された状態の積層シムを用いることができ、減衰層７０は、面内および面直方向に適切な弾性率を持つ積層構造となる。積層構造は、例えば弾性材であるゴム、金属支持板であるステンレス鋼板、弾性材である粘着材、金属支持板である冷間圧延鋼板、及び弾性材であるゴムを順に貼り合わせて積層させた構造とすることができる。勿論、減衰層７０は、本実施形態の積層構造に限定されるものではなく、ライニング組立体１０とライニングホルダ１４０（３０１）との間を伝搬する振動を減衰させることにより、ノイズの低減が可能となるものであれば種々の積層構造或いは単層構造を採り得る。 For the damping layer 70, for example, a laminated shim in which a metal support plate and an elastic material are laminated and laminated can be used, and the damping layer 70 has a laminated structure having an appropriate elastic modulus in the in-plane and in the perpendicular direction. Will be. In the laminated structure, for example, rubber as an elastic material, a stainless steel plate as a metal support plate, an adhesive material as an elastic material, a cold-rolled steel plate as a metal support plate, and rubber as an elastic material are laminated in this order. It can be a structure. Of course, the damping layer 70 is not limited to the laminated structure of the present embodiment, and noise can be reduced by damping the vibration propagating between the lining assembly 10 and the lining holder 140 (301). Various laminated structures or single-layer structures can be adopted as long as they are.
　本第４実施形態に係るガイドプレート組立体１Ｂによれば、ライニングホルダ１４０（３０１）に取付けられた際、ライニング組立体１０とライニングホルダ１４０（３０１）との間を伝搬する振動が、減衰層７０により減衰される。減衰層７０は、ライニングホルダ１４０（３０１）と裏板部１２の凸部２０との接触によるノイズの低減に寄与する。これにより、制動過程時に生じる振動が減衰され、スキール騒音（所謂ブレーキ鳴き）が抑制される。 According to the guide plate assembly 1B according to the fourth embodiment, when attached to the lining holder 140 (301), the vibration propagating between the lining assembly 10 and the lining holder 140 (301) is a damping layer. It is attenuated by 70. The damping layer 70 contributes to the reduction of noise due to the contact between the lining holder 140 (301) and the convex portion 20 of the back plate portion 12. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
　図１９の（ａ）は本発明の第５実施形態に係るトルク受けプレート１０１Ａを表側から見た斜視図であり、図１９の（ｂ）は本第５実施形態の変形例に係るトルク受けプレート１０１Ｂを表側から見た斜視図である。なお、上記トルク受けプレート１０１と同様の構成部材については、同符号を付して詳細な説明を省略する。 FIG. 19A is a perspective view of the torque receiving plate 101A according to the fifth embodiment of the present invention as viewed from the front side, and FIG. 19B is a torque receiving plate according to a modified example of the fifth embodiment. It is a perspective view which saw 101B from the front side. The same components as those of the torque receiving plate 101 are designated by the same reference numerals, and detailed description thereof will be omitted.
　本第５実施形態に係るトルク受けプレート１０１Ａは、図１９の（ａ）に示すように、表面１０１ａ側に、ライニング組立体１０の凸部２０と対向する減衰層７０が設けられる。
　減衰層７０は、均一な厚みで形成される。減衰層７０は、トルク受けプレート１０１Ａの表面１０１ａに沿うことで、トルク受けプレート１０１Ａと略相似形状で形成されている。減衰層７０の表面は、トルク受けプレート１０１Ａの表面１０１ａと平行な平坦面となる。減衰層７０には、円形状に形成されたトルク受けプレート１０１Ａのアンカーピン嵌合部１１０を貫通したアンカーピン１３０に貫通されるアンカーピン係合穴７３が形成される。そこで、減衰層７０は、アンカーピン１３０によってトルク受けプレート１０１Ａの表面１０１ａに固定される。 As shown in FIG. 19A, the torque receiving plate 101A according to the fifth embodiment is provided with a damping layer 70 facing the convex portion 20 of the lining assembly 10 on the surface 101a side.
The damping layer 70 is formed with a uniform thickness. The damping layer 70 is formed along the surface 101a of the torque receiving plate 101A in a shape substantially similar to that of the torque receiving plate 101A. The surface of the damping layer 70 is a flat surface parallel to the surface 101a of the torque receiving plate 101A. The damping layer 70 is formed with an anchor pin engaging hole 73 penetrating through the anchor pin 130 penetrating the anchor pin fitting portion 110 of the torque receiving plate 101A formed in a circular shape. Therefore, the damping layer 70 is fixed to the surface 101a of the torque receiving plate 101A by the anchor pin 130.
　本第５実施形態の変形例に係るトルク受けプレート１０１Ｂは、図１９の（ｂ）に示すように、減衰層７０が、締結部材８０によってトルク受けプレート１０１Ｂの表面１０１ａに固定される。なお、減衰層７０は、トルク受けプレート１０１Ｂに対して接着剤によって固定されてもよい。 As shown in FIG. 19B, in the torque receiving plate 101B according to the modified example of the fifth embodiment, the damping layer 70 is fixed to the surface 101a of the torque receiving plate 101B by the fastening member 80. The damping layer 70 may be fixed to the torque receiving plate 101B with an adhesive.
　これらトルク受けプレート１０１Ａ，１０１Ｂによれば、ガイドプレート組立体１がトルク受けプレート１０１Ａ（１０１Ｂ）に取付けられた際、ライニング組立体１０とトルク受けプレート１０１Ａ（１０１Ｂ）との間を伝搬する振動が、減衰層７０により減衰される。減衰層７０は、トルク受けプレート１０１Ａ（１０１Ｂ）と裏板部１２の凸部２０との接触によるノイズの低減に寄与する。これにより、制動過程時に生じる振動が減衰され、スキール騒音（所謂ブレーキ鳴き）が抑制される。 According to these torque receiving plates 101A and 101B, when the guide plate assembly 1 is attached to the torque receiving plate 101A (101B), the vibration propagating between the lining assembly 10 and the torque receiving plate 101A (101B) is generated. , It is attenuated by the damping layer 70. The damping layer 70 contributes to the reduction of noise due to the contact between the torque receiving plate 101A (101B) and the convex portion 20 of the back plate portion 12. As a result, the vibration generated during the braking process is damped, and the squeal noise (so-called brake squeal) is suppressed.
　図２０の（ａ）は本発明の第６実施形態に係るライニングホルダ３０１Ａを表側から見た斜視図であり、図２０の（ｂ）は本第６実施形態の変形に係るライニングホルダ３０１Ｂを表側から見た斜視図である。なお、上記ライニングホルダ３０１と同様の構成部材については、同符号を付して詳細な説明を省略する。 FIG. 20A is a perspective view of the lining holder 301A according to the sixth embodiment of the present invention as viewed from the front side, and FIG. 20B is a front side view of the lining holder 301B according to the modification of the sixth embodiment. It is a perspective view seen from. The same components as those of the lining holder 301 are designated by the same reference numerals, and detailed description thereof will be omitted.
　本第６実施形態に係るライニングホルダ３０１Ａは、図２０の（ａ）に示すように、表面３０１ａ側に、ライニング組立体１０の凸部２０と対向する減衰層７０が設けられる。
　減衰層７０は、均一な厚みで形成される。減衰層７０は、ライニングホルダ３０１Ａトの表面３０１ａに沿うことで、ライニングホルダ３０１Ａと略相似形状で形成されている。減衰層７０の表面は、ライニングホルダ３０１Ａの表面３０１ａと平行な平坦面となる。減衰層７０には、円形状に形成されたライニングホルダ３０１Ａのアンカーピン嵌合部３１０を貫通したアンカーピン１３０に貫通されるアンカーピン係合穴７３が形成される。そこで、減衰層７０は、アンカーピン１３０によってライニングホルダ３０１Ａの表面３０１ａに固定される。 As shown in FIG. 20A, the lining holder 301A according to the sixth embodiment is provided with a damping layer 70 facing the convex portion 20 of the lining assembly 10 on the surface 301a side.
The damping layer 70 is formed with a uniform thickness. The damping layer 70 is formed along the surface 301a of the lining holder 301A in a shape substantially similar to that of the lining holder 301A. The surface of the damping layer 70 is a flat surface parallel to the surface 301a of the lining holder 301A. The damping layer 70 is formed with an anchor pin engaging hole 73 penetrating through the anchor pin 130 penetrating the anchor pin fitting portion 310 of the lining holder 301A formed in a circular shape. Therefore, the damping layer 70 is fixed to the surface 301a of the lining holder 301A by the anchor pin 130.
　本第６実施形態の変形例に係るライニングホルダ３０１Ｂは、図２０の（ｂ）に示すように、減衰層７０が、締結部材８０によってライニングホルダ３０１Ｂの表面３０１ａに固定される。なお、減衰層７０は、ライニングホルダ３０１Ｂに対して接着剤によって固定されてもよい。 As shown in FIG. 20B, in the lining holder 301B according to the modified example of the sixth embodiment, the damping layer 70 is fixed to the surface 301a of the lining holder 301B by the fastening member 80. The damping layer 70 may be fixed to the lining holder 301B with an adhesive.
　従って、本実施形態に係るガイドプレート組立体１，１Ａ，１Ｂ及びディスクブレーキ用摩擦パッド組立て体１００，２００によれば、軽量で小型のガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体を実現できる。 Therefore, according to the guide plate assemblies 1, 1A, 1B and the disc brake friction pad assemblies 100, 200 according to the present embodiment, it is possible to realize a lightweight and compact guide plate assembly and a disc brake friction pad assembly. ..
　なお、本発明は、上述した実施形態に限定されるものではなく、適宜、変形、改良、等が可能である。その他、上述した実施形態における各構成要素の材質、形状、寸法、数、配置箇所、等は本発明を達成できるものであれば任意であり、限定されない。 The present invention is not limited to the above-described embodiment, and can be appropriately modified, improved, or the like. In addition, the material, shape, dimensions, number, arrangement location, etc. of each component in the above-described embodiment are arbitrary as long as the present invention can be achieved, and are not limited.
　ここで、上述した本発明に係るガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体の実施の形態の特徴をそれぞれ以下に簡潔に纏めて列記する。
　［１］　制動トルクを受けるガイドプレート（３）と、制動時にディスクロータと接触する摩擦材（１１）と、前記摩擦材（１１）の裏面に固着された裏板部（１２）とを有し、前記ガイドプレート（３）のガイド孔部（５）に揺動自在に支持される少なくとも１つのライニング組立体（１０）と、前記ガイド孔部（５）に挿通された前記ライニング組立体（１０）をロータ軸方向（Ｘ）に移動可能かつ抜け落ちないように保持するための抜け落ち防止機構と、前記裏板部（１２）の裏面側に設けられ、ライニングホルダ（１４０，３０１）により前記ディスクロータへ押圧された前記ライニング組立体（１０）を揺動可能に支持するための凸部（２０）と、を備えたガイドプレート組立体（１，１Ａ，１Ｂ）。
　［２］　上記［１］に記載のガイドプレート組立体であって、
　前記裏板部（１２）のプレート嵌合部（１５）と前記ガイド孔部（５）とがそれぞれ非円形状に形成されて嵌合することによって、前記ガイド孔部（５）内での前記ライニング組立体（１０）の回転が阻止される、ガイドプレート組立体（１，１Ａ，１Ｂ）。
　［３］　上記［２］に記載のガイドプレート組立体であって、
　前記プレート嵌合部（１５）の外周面及び前記ガイド孔部（５）の内周面には、前記ガイド孔部（５）内での前記ライニング組立体（１０）の回転を阻止する回り止め用の平坦面（１６）が形成される、ガイドプレート組立体（１，１Ａ，１Ｂ）。
　［４］　上記［１］～［３］のいずれか１つに記載のガイドプレート組立体であって、
　前記ガイドプレート（３）の表面（３ａ）又は裏面（３ｂ）と、前記裏板部（１２）との間には、前記ライニング組立体（１０）を前記ガイドプレート（３）に対して前記ロータ軸方向（Ｘ）に沿う何れか一方に付勢するばね部材（２５）が配置される、ガイドプレート組立体（１，１Ａ，１Ｂ）。
　［５］　上記［１］～［４］のいずれか１つに記載のガイドプレート組立体であって、
　前記抜け落ち防止機構は、前記ガイド孔部（５）の開口形状よりも大きい外形状を有して前記裏板部（１２）の裏面に取り付けられるロックプレート（１７）を有する、ガイドプレート組立体（１，１Ａ，１Ｂ）。
　［６］　上記［５］に記載のガイドプレート組立体であって、
　前記裏板部（１２）に圧入されることで前記ロックプレート（１７）を前記裏板部（１２）の裏面に固定するジョイント部材（２２）からなる前記凸部（２０）を有する、ガイドプレート組立体（１，１Ａ，１Ｂ）。
　［７］　上記［５］に記載のガイドプレート組立体であって、
　前記ロックプレート（１７）が、リベット（４５）により前記裏板部（１２）の裏面に固定される、ガイドプレート組立体（１，１Ａ，１Ｂ）。
　［８］　上記［５］に記載のガイドプレート組立体であって、
　前記ロックプレート（１７）が、ブラインドリベット（５３）により前記裏板部（１２）の裏面に固定される、ガイドプレート組立体（１，１Ａ，１Ｂ）。
　［９］　上記［５］に記載のガイドプレート組立体であって、
　前記裏板部（１２）を貫通した先端のハトメ（３３）により前記ロックプレート（１７）を前記裏板部（１２）の裏面に固定するジョイント部材（３２）からなる前記凸部（２０）を有する、ガイドプレート組立体（１，１Ａ，１Ｂ）。
　［１０］　上記［１］～［９］の何れか１つに記載のガイドプレート組立体であって、
　前記ガイドプレート（３Ａ）の裏面（３ｂ）側には、減衰層（７０）が設けられる、ガイドプレート組立体（１Ｂ）。
　［１１］　上記［１］～［１０］の何れか１つに記載のガイドプレート組立体（１，１Ａ，１Ｂ）と、前記ガイドプレート（３）の周縁部分に嵌合して前記ガイドプレート組立体（１，１Ａ，１Ｂ）を着脱自在に保持する溝部（３０５）が設けられ、表面（３０１ａ）で前記凸部（２０）を揺動可能に支持する前記ライニングホルダ（３０１，３０１Ａ，３０１Ｂ）と、を備えたディスクブレーキ用摩擦パッド組立て体（２００）。
　［１２］　上記［１］～［１０］の何れか１つに記載のガイドプレート組立体（１，１Ａ，１Ｂ）と、前記ガイドプレート（３）の周縁部分に嵌合して前記ガイドプレート組立体（１，１Ａ，１Ｂ）を着脱自在に保持する溝部（１０５）が設けられ、表面（１０１ａ）で前記凸部（２０）を揺動可能に支持するトルク受けプレート（１０１，１０１Ａ，１０１Ｂ）と、前記トルク受けプレート（１０１，１０１Ａ，１０１Ｂ）の裏面（１０１ｂ）に設けられ、蟻溝状の固定溝（１４１）が設けられた前記ライニングホルダ（１４０）へ、溝端から挿入されるアンカープレート（１２０）と、を備えたディスクブレーキ用摩擦パッド組立て体（１００）。
　［１３］　上記［１１］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記裏板部（１２）のプレート嵌合部（１５）が前記ガイド孔部（５）に挿入装着され、前記ディスクロータと前記摩擦材（１１）との接触時に作用する前記制動トルクが、前記プレート嵌合部（１５）から前記ガイドプレート（３）に伝達され、更に前記ガイドプレート（３）のアンカーピン係合部（７，９）からアンカーピン（１３０）により前記ライニングホルダ（３０１，３０１Ａ）のアンカーピン嵌合部（３１０）に伝達される、ディスクブレーキ用摩擦パッド組立て体（２００）。
　［１４］　上記［１２］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記裏板部（１２）のプレート嵌合部（１５）が前記ガイド孔部（５）に挿入装着され、前記ディスクロータと前記摩擦材（１１）との接触時に作用する前記制動トルクが、前記プレート嵌合部（１５）から前記ガイドプレート（３）に伝達され、更に前記ガイドプレート（３）のアンカーピン係合部（７，９）からアンカーピン（１３０）により前記トルク受けプレート（１０１，１０１Ａ，１０１Ｂ）のアンカーピン嵌合部（１１０）に伝達され、更に前記トルク受けプレート（１０１，１０１Ａ，１０１Ｂ）の前記アンカープレート（１２０）からアンカープレート固定部材（１４５）により前記ライニングホルダ（１４０）の固定部（ブレーキパッド取付部１４３）に伝達される、ディスクブレーキ用摩擦パッド組立て体（１００）。
　［１５］　上記［１３］又は［１４］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記アンカーピン係合部（７）が、半円形状に形成されて前記制動トルクを受ける、ディスクブレーキ用摩擦パッド組立て体（１００，２００）。
　［１６］　上記［１３］又は［１４］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　複数の前記アンカーピン係合部（７，９）のうちで、ブレーキキャリパに取り付けられた際に鉛直方向下側に位置する前記アンカーピン係合部（９）が、円形状に形成されて前記制動トルクを受ける、ディスクブレーキ用摩擦パッド組立て体（１００，２００）。
　［１７］　上記［１１］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記ライニングホルダ（３０１Ａ，３０１Ｂ）の前記表面（３０１ａ）側には、前記凸部（２０）と対向する減衰層（７０）が設けられる、ディスクブレーキ用摩擦パッド組立て体（２００）。
　［１８］　上記［１２］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記トルク受けプレート（１０１Ａ，１０１Ｂ）の前記表面（１０１ａ）側には、前記凸部（２０）と対向する減衰層（７０）が設けられる、ディスクブレーキ用摩擦パッド組立て体（１００）。
　［１９］　上記［１３］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記ライニングホルダ（３０１Ａ）の前記表面（３０１ａ）側には、前記凸部（２０）と対向する減衰層（７０）が設けられ、前記減衰層（７０）には、円形状に形成された前記アンカーピン係合部（３１０）を貫通した前記アンカーピン（１３０）に貫通されるアンカーピン係合穴（７３）が形成される、ディスクブレーキ用摩擦パッド組立て体（２００）。
　［２０］　上記［１４］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記トルク受けプレート（１０１Ａ）の前記表面（１０１ａ）側には、前記凸部（２０）と対向する減衰層（７０）が設けられ、前記減衰層（７０）には、円形状に形成された前記アンカーピン係合部（３１０）を貫通した前記アンカーピン（１３０）に貫通されるアンカーピン係合穴（７３）が形成される、ディスクブレーキ用摩擦パッド組立て体（１００）。
　［２１］　上記［１７］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記減衰層（７０）は、前記ライニングホルダ（３０１Ｂ）に対して締結部材（８０）によって固定される、ディスクブレーキ用摩擦パッド組立て体（２００）。
　［２２］　上記［１８］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記減衰層（７０）は、前記トルク受けプレート（１０１Ｂ）に対して締結部材（８０）によって固定される、ディスクブレーキ用摩擦パッド組立て体（１００）。
　［２３］　上記［１７］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記減衰層（７０）は、前記ライニングホルダ（３０１Ａ）に対して接着剤によって固定される、ディスクブレーキ用摩擦パッド組立て体（２００）。
　［２４］　上記［１８］に記載のディスクブレーキ用摩擦パッド組立て体であって、
　前記減衰層（７０）は、前記トルク受けプレート（１０１Ａ）に対して接着剤によって固定される、ディスクブレーキ用摩擦パッド組立て体（１００）。 Here, the features of the embodiments of the guide plate assembly and the friction pad assembly for disc brakes according to the present invention described above are briefly summarized below.
[1] It has a guide plate (3) that receives braking torque, a friction material (11) that comes into contact with the disc rotor during braking, and a back plate portion (12) that is fixed to the back surface of the friction material (11). , At least one lining assembly (10) swingably supported by the guide hole portion (5) of the guide plate (3), and the lining assembly (10) inserted through the guide hole portion (5). ) Is movable in the rotor axial direction (X) and is provided on the back surface side of the back plate portion (12), and the disc rotor is provided by the lining holders (140, 301). A guide plate assembly (1,1A, 1B) comprising a convex portion (20) for swingably supporting the lining assembly (10) pressed against.
[2] The guide plate assembly according to the above [1].
The plate fitting portion (15) of the back plate portion (12) and the guide hole portion (5) are formed in a non-circular shape and fitted to each other, whereby the said in the guide hole portion (5). Guide plate assembly (1,1A, 1B) from which rotation of the lining assembly (10) is blocked.
[3] The guide plate assembly according to the above [2].
On the outer peripheral surface of the plate fitting portion (15) and the inner peripheral surface of the guide hole portion (5), a detent that prevents the lining assembly (10) from rotating in the guide hole portion (5). Guide plate assembly (1,1A, 1B) on which a flat surface (16) is formed.
[4] The guide plate assembly according to any one of the above [1] to [3].
The lining assembly (10) is placed between the front surface (3a) or the back surface (3b) of the guide plate (3) and the back plate portion (12) with respect to the guide plate (3). A guide plate assembly (1,1A, 1B) in which a spring member (25) for urging any one along the axial direction (X) is arranged.
[5] The guide plate assembly according to any one of the above [1] to [4].
The fall-out prevention mechanism has a guide plate assembly (17) having an outer shape larger than the opening shape of the guide hole portion (5) and having a lock plate (17) attached to the back surface of the back plate portion (12). 1,1A, 1B).
[6] The guide plate assembly according to the above [5].
A guide plate having the convex portion (20) made of a joint member (22) that fixes the lock plate (17) to the back surface of the back plate portion (12) by being press-fitted into the back plate portion (12). Assembly (1,1A, 1B).
[7] The guide plate assembly according to the above [5].
A guide plate assembly (1,1A, 1B) in which the lock plate (17) is fixed to the back surface of the back plate portion (12) by a rivet (45).
[8] The guide plate assembly according to the above [5].
A guide plate assembly (1,1A, 1B) in which the lock plate (17) is fixed to the back surface of the back plate portion (12) by a blind rivet (53).
[9] The guide plate assembly according to the above [5].
The convex portion (20) made of a joint member (32) for fixing the lock plate (17) to the back surface of the back plate portion (12) by an eyelet (33) at the tip penetrating the back plate portion (12). Guide plate assembly (1,1A, 1B) having.
[10] The guide plate assembly according to any one of the above [1] to [9].
A guide plate assembly (1B) provided with a damping layer (70) on the back surface (3b) side of the guide plate (3A).
[11] The guide plate assembly (1,1A, 1B) according to any one of the above [1] to [10] is fitted to the peripheral portion of the guide plate (3) to form the guide plate assembly. The lining holder (301, 301A, 301B) provided with a groove portion (305) for detachably holding the solid (1,1A, 1B) and swingably supporting the convex portion (20) on the surface (301a). And, a friction pad assembly for disc brakes (200).
[12] The guide plate assembly (1,1A, 1B) according to any one of the above [1] to [10] is fitted to the peripheral portion of the guide plate (3) to form the guide plate assembly. A torque receiving plate (101, 101A, 101B) provided with a groove portion (105) for detachably holding a solid (1,1A, 1B) and swingably supporting the convex portion (20) on the surface (101a). An anchor plate is inserted from the groove end into the lining holder (140) provided on the back surface (101b) of the torque receiving plates (101, 101A, 101B) and provided with a dovetail groove-shaped fixing groove (141). (120), and a friction pad assembly for disc brakes (100).
[13] The disc brake friction pad assembly according to the above [11].
The plate fitting portion (15) of the back plate portion (12) is inserted and mounted in the guide hole portion (5), and the braking torque acting at the time of contact between the disc rotor and the friction material (11) is the braking torque. The lining holder (301, 301A) is transmitted from the plate fitting portion (15) to the guide plate (3), and further from the anchor pin engaging portion (7, 9) of the guide plate (3) by the anchor pin (130). ), The friction pad assembly for disc brakes (200) transmitted to the anchor pin fitting portion (310).
[14] The disc brake friction pad assembly according to the above [12].
The plate fitting portion (15) of the back plate portion (12) is inserted and mounted in the guide hole portion (5), and the braking torque acting at the time of contact between the disc rotor and the friction material (11) is the braking torque. The torque is transmitted from the plate fitting portion (15) to the guide plate (3), and further from the anchor pin engaging portion (7, 9) of the guide plate (3) to the torque receiving plate (101,) by the anchor pin (130). It is transmitted to the anchor pin fitting portion (110) of 101A, 101B), and further, the lining holder (140) is transmitted from the anchor plate (120) of the torque receiving plate (101, 101A, 101B) to the anchor plate fixing member (145). ) Is transmitted to the fixed portion (brake pad mounting portion 143) of the disc brake friction pad assembly (100).
[15] The disc brake friction pad assembly according to the above [13] or [14].
A disc brake friction pad assembly (100, 200) in which the anchor pin engaging portion (7) is formed in a semicircular shape and receives the braking torque.
[16] The disc brake friction pad assembly according to the above [13] or [14].
Among the plurality of anchor pin engaging portions (7, 9), the anchor pin engaging portion (9) located on the lower side in the vertical direction when attached to the brake caliper is formed in a circular shape. Friction pad assembly for disc brakes (100,200) that receives braking torque.
[17] The disc brake friction pad assembly according to the above [11].
A disc brake friction pad assembly (200) provided with a damping layer (70) facing the convex portion (20) on the surface (301a) side of the lining holders (301A, 301B).
[18] The disc brake friction pad assembly according to the above [12].
A disc brake friction pad assembly (100) provided with a damping layer (70) facing the convex portion (20) on the surface (101a) side of the torque receiving plates (101A, 101B).
[19] The disc brake friction pad assembly according to the above [13].
A damping layer (70) facing the convex portion (20) is provided on the surface (301a) side of the lining holder (301A), and the damping layer (70) is formed in a circular shape. A disc brake friction pad assembly (200) in which an anchor pin engaging hole (73) is formed through the anchor pin (130) that penetrates the anchor pin engaging portion (310).
[20] The disc brake friction pad assembly according to the above [14].
A damping layer (70) facing the convex portion (20) is provided on the surface (101a) side of the torque receiving plate (101A), and the damping layer (70) is formed in a circular shape. A friction pad assembly (100) for a disc brake, wherein an anchor pin engaging hole (73) is formed through the anchor pin (130) that penetrates the anchor pin engaging portion (310).
[21] The disc brake friction pad assembly according to the above [17].
The damping layer (70) is a friction pad assembly (200) for disc brakes, which is fixed to the lining holder (301B) by a fastening member (80).
[22] The disc brake friction pad assembly according to the above [18].
The damping layer (70) is a friction pad assembly (100) for disc brakes, which is fixed to the torque receiving plate (101B) by a fastening member (80).
[23] The disc brake friction pad assembly according to the above [17].
The damping layer (70) is a friction pad assembly (200) for disc brakes, which is fixed to the lining holder (301A) by an adhesive.
[24] The disc brake friction pad assembly according to the above [18].
The damping layer (70) is a friction pad assembly (100) for disc brakes, which is fixed to the torque receiving plate (101A) by an adhesive.
　なお、本出願は、２０２０年７月１７日出願の日本特許出願（特願２０２０－１２３０１７）に基づくものであり、その内容は本出願の中に参照として援用される。 Note that this application is based on a Japanese patent application filed on July 17, 2020 (Japanese Patent Application No. 2020-12307), the contents of which are incorporated herein by reference.
　本発明のガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体によれば、軽量で小型のガイドプレート組立体及びディスクブレーキ用摩擦パッド組立て体を実現できる。 According to the guide plate assembly and the friction pad assembly for disc brakes of the present invention, it is possible to realize a lightweight and compact guide plate assembly and a friction pad assembly for disc brakes.
１…ガイドプレート組立体
３…ガイドプレート
５…ガイド孔部
１０…ライニング組立体
１１…摩擦材
１２…裏板部
１３…抜け止めフランジ部
１５…プレート嵌合部
１７…ロックプレート
２０…凸部
２２…ジョイント部材
２５…ばね部材
１００…ディスクブレーキ用摩擦パッド組立て体 1 ... Guide plate assembly 3 ... Guide plate 5 ... Guide hole 10 ... Lining assembly 11 ... Friction material 12 ... Back plate 13 ... Retaining flange 15 ... Plate fitting 17 ... Lock plate 20 ... Convex 22 ... Joint member 25 ... Spring member 100 ... Friction pad assembly for disc brakes

Claims (24)

  1. 　制動トルクを受けるガイドプレートと、制動時にディスクロータと接触する摩擦材と、前記摩擦材の裏面に固着された裏板部とを有し、前記ガイドプレートのガイド孔部に揺動自在に支持される少なくとも１つのライニング組立体と、前記ガイド孔部に挿通された前記ライニング組立体をロータ軸方向に移動可能かつ抜け落ちないように保持するための抜け落ち防止機構と、前記裏板部の裏面側に設けられ、ライニングホルダにより前記ディスクロータへ押圧された前記ライニング組立体を揺動可能に支持するための凸部と、を備えたことを特徴とするガイドプレート組立体。 It has a guide plate that receives braking torque, a friction material that comes into contact with the disc rotor during braking, and a back plate portion that is fixed to the back surface of the friction material, and is swingably supported by the guide hole portion of the guide plate. On the back surface side of the back plate portion, at least one lining assembly, a fall-off prevention mechanism for holding the lining assembly inserted through the guide hole portion so as to be movable in the rotor axial direction and not to fall off. A guide plate assembly provided, comprising a convex portion for swingably supporting the lining assembly pressed against the disc rotor by a lining holder.
  2. 　請求項１に記載したガイドプレート組立体であって、
    　前記裏板部のプレート嵌合部と前記ガイド孔部とがそれぞれ非円形状に形成されて嵌合することによって、前記ガイド孔部内での前記ライニング組立体の回転が阻止される、ガイドプレート組立体。     The guide plate assembly according to claim 1.
    A guide plate assembly in which the plate fitting portion of the back plate portion and the guide hole portion are formed in a non-circular shape and fitted to each other to prevent the lining assembly from rotating in the guide hole portion. Solid.
  3. 　請求項２に記載のガイドプレート組立体であって、
    　前記プレート嵌合部の外周面及び前記ガイド孔部の内周面には、前記ガイド孔部内での前記ライニング組立体の回転を阻止する回り止め用の平坦面が形成される、ガイドプレート組立体。     The guide plate assembly according to claim 2.
    A guide plate assembly is formed with a flat surface for preventing rotation of the lining assembly in the guide hole on the outer peripheral surface of the plate fitting portion and the inner peripheral surface of the guide hole. ..
  4. 　請求項１～３のいずれか１項に記載のガイドプレート組立体であって、
    　前記ガイドプレートの表面又は裏面と、前記裏板部との間には、前記ライニング組立体を前記ガイドプレートに対して前記ロータ軸方向に沿う何れか一方に付勢するばね部材が配置される、ガイドプレート組立体。     The guide plate assembly according to any one of claims 1 to 3.
    A spring member is arranged between the front surface or the back surface of the guide plate and the back plate portion to urge the lining assembly to either side along the rotor axial direction with respect to the guide plate. Guide plate assembly.
  5. 　請求項１～４のいずれか１項に記載のガイドプレート組立体であって、
    　前記抜け落ち防止機構は、前記ガイド孔部の開口形状よりも大きい外形状を有して前記裏板部の裏面に取り付けられるロックプレートを有する、ガイドプレート組立体。     The guide plate assembly according to any one of claims 1 to 4.
    The fall-out prevention mechanism is a guide plate assembly having a lock plate having an outer shape larger than the opening shape of the guide hole portion and attached to the back surface of the back plate portion.
  6. 　請求項５に記載のガイドプレート組立体であって、
    　前記裏板部に圧入されることで前記ロックプレートを前記裏板部の裏面に固定するジョイント部材からなる前記凸部を有する、ガイドプレート組立体。     The guide plate assembly according to claim 5.
    A guide plate assembly having the convex portion including a joint member for fixing the lock plate to the back surface of the back plate portion by being press-fitted into the back plate portion.
  7. 　請求項５に記載のガイドプレート組立体であって、
    　前記ロックプレートが、リベットにより前記裏板部の裏面に固定される、ガイドプレート組立体。     The guide plate assembly according to claim 5.
    A guide plate assembly in which the lock plate is fixed to the back surface of the back plate portion by rivets.
  8. 　請求項５に記載のガイドプレート組立体であって、
    　前記ロックプレートが、ブラインドリベットにより前記裏板部の裏面に固定される、ガイドプレート組立体。     The guide plate assembly according to claim 5.
    A guide plate assembly in which the lock plate is fixed to the back surface of the back plate portion by a blind rivet.
  9. 　請求項５に記載のガイドプレート組立体であって、
    　前記裏板部を貫通した先端のハトメにより前記ロックプレートを前記裏板部の裏面に固定するジョイント部材からなる前記凸部を有する、ガイドプレート組立体。     The guide plate assembly according to claim 5.
    A guide plate assembly having the convex portion made of a joint member for fixing the lock plate to the back surface of the back plate portion by eyelets at the tip penetrating the back plate portion.
  10. 　請求項１～９の何れか１項に記載のガイドプレート組立体であって、
    　前記ガイドプレートの裏面側には、減衰層が設けられる、ガイドプレート組立体。     The guide plate assembly according to any one of claims 1 to 9.
    A guide plate assembly in which a damping layer is provided on the back surface side of the guide plate.
  11. 　請求項１～１０の何れか１項に記載のガイドプレート組立体と、前記ガイドプレートの周縁部分に嵌合して前記ガイドプレート組立体を着脱自在に保持する溝部が設けられ、表面で前記凸部を揺動可能に支持する前記ライニングホルダと、を備えたディスクブレーキ用摩擦パッド組立て体。 The guide plate assembly according to any one of claims 1 to 10 is provided with a groove portion that is fitted to a peripheral portion of the guide plate and holds the guide plate assembly detachably, and is convex on the surface. A friction pad assembly for disc brakes, comprising the lining holder that swingably supports the portion.
  12. 　請求項１～１０の何れか１項に記載のガイドプレート組立体と、前記ガイドプレートの周縁部分に嵌合して前記ガイドプレート組立体を着脱自在に保持する溝部が設けられ、表面で前記凸部を揺動可能に支持するトルク受けプレートと、前記トルク受けプレートの裏面に設けられ、蟻溝状の固定溝が設けられた前記ライニングホルダへ、溝端から挿入されるアンカープレートと、を備えたディスクブレーキ用摩擦パッド組立て体。 The guide plate assembly according to any one of claims 1 to 10 is provided with a groove portion that is fitted to the peripheral edge portion of the guide plate and holds the guide plate assembly detachably, and is convex on the surface. It is provided with a torque receiving plate that swingably supports the portion, and an anchor plate that is provided on the back surface of the torque receiving plate and is inserted from the groove end into the lining holder provided with a dovetail groove-shaped fixing groove. Friction pad assembly for disc brakes.
  13. 　請求項１１に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記裏板部のプレート嵌合部が前記ガイド孔部に挿入装着され、前記ディスクロータと前記摩擦材との接触時に作用する前記制動トルクが、前記プレート嵌合部から前記ガイドプレートに伝達され、更に前記ガイドプレートのアンカーピン係合部からアンカーピンにより前記ライニングホルダのアンカーピン嵌合部に伝達される、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 11.
    The plate fitting portion of the back plate portion is inserted and mounted in the guide hole portion, and the braking torque acting at the time of contact between the disc rotor and the friction material is transmitted from the plate fitting portion to the guide plate. Further, a friction pad assembly for a disc brake, which is transmitted from the anchor pin engaging portion of the guide plate to the anchor pin fitting portion of the lining holder by the anchor pin.
  14. 　請求項１２に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記裏板部のプレート嵌合部が前記ガイド孔部に挿入装着され、前記ディスクロータと前記摩擦材との接触時に作用する前記制動トルクが、前記プレート嵌合部から前記ガイドプレートに伝達され、更に前記ガイドプレートのアンカーピン係合部からアンカーピンにより前記トルク受けプレートのアンカーピン嵌合部に伝達され、更に前記トルク受けプレートの前記アンカープレートからアンカープレート固定部材により前記ライニングホルダの固定部に伝達される、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 12.
    The plate fitting portion of the back plate portion is inserted and mounted in the guide hole portion, and the braking torque acting at the time of contact between the disc rotor and the friction material is transmitted from the plate fitting portion to the guide plate. Further, it is transmitted from the anchor pin engaging portion of the guide plate to the anchor pin fitting portion of the torque receiving plate by the anchor pin, and further from the anchor plate of the torque receiving plate to the fixing portion of the lining holder by the anchor plate fixing member. Friction pad assembly for disc brakes that is transmitted.
  15. 　請求項１３又は１４に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記アンカーピン係合部が、半円形状に形成されて前記制動トルクを受ける、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 13 or 14.
    A friction pad assembly for a disc brake in which the anchor pin engaging portion is formed in a semicircular shape and receives the braking torque.
  16. 　請求項１３又は１４に記載のディスクブレーキ用摩擦パッド組立て体であて、
    　複数の前記アンカーピン係合部のうちで、ブレーキキャリパに取り付けられた際に鉛直方向下側に位置する前記アンカーピン係合部が、円形状に形成されて前記制動トルクを受ける、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 13 or 14.
    Among the plurality of anchor pin engaging portions, the anchor pin engaging portion located on the lower side in the vertical direction when attached to the brake caliper is formed in a circular shape to receive the braking torque for a disc brake. Friction pad assembly.
  17. 　請求項１１に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記ライニングホルダの前記表面側には、前記凸部と対向する減衰層が設けられる、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 11.
    A friction pad assembly for a disc brake provided with a damping layer facing the convex portion on the surface side of the lining holder.
  18. 　請求項１２に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記トルク受けプレートの前記表面側には、前記凸部と対向する減衰層が設けられる、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 12.
    A friction pad assembly for a disc brake provided with a damping layer facing the convex portion on the surface side of the torque receiving plate.
  19. 　請求項１３に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記ライニングホルダの前記表面側には、前記凸部と対向する減衰層が設けられ、前記減衰層には、円形状に形成された前記アンカーピン係合部を貫通した前記アンカーピンに貫通されるアンカーピン係合穴が形成される、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 13.
    A damping layer facing the convex portion is provided on the surface side of the lining holder, and the damping layer is penetrated by the anchor pin penetrating the anchor pin engaging portion formed in a circular shape. Friction pad assembly for disc brakes with anchor pin engagement holes formed.
  20. 　請求項１４に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記トルク受けプレートの前記表面側には、前記凸部と対向する減衰層が設けられ、前記減衰層には、円形状に形成された前記アンカーピン係合部を貫通した前記アンカーピンに貫通されるアンカーピン係合穴が形成される、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 14.
    A damping layer facing the convex portion is provided on the surface side of the torque receiving plate, and the damping layer is penetrated by the anchor pin penetrating the anchor pin engaging portion formed in a circular shape. Friction pad assembly for disc brakes to which anchor pin engagement holes are formed.
  21. 　請求項１７に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記減衰層は、前記ライニングホルダに対して締結部材によって固定される、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 17.
    The damping layer is a friction pad assembly for disc brakes, which is fixed to the lining holder by a fastening member.
  22. 　請求項１８に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記減衰層は、前記トルク受けプレートに対して締結部材によって固定される、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 18.
    The damping layer is a friction pad assembly for disc brakes, which is fixed to the torque receiving plate by a fastening member.
  23. 　請求項１７に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記減衰層は、前記ライニングホルダに対して接着剤によって固定される、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 17.
    The damping layer is a friction pad assembly for disc brakes, which is fixed to the lining holder by an adhesive.
  24. 　請求項１８に記載のディスクブレーキ用摩擦パッド組立て体であって、
    　前記減衰層は、前記トルク受けプレートに対して接着剤によって固定される、ディスクブレーキ用摩擦パッド組立て体。     The disc brake friction pad assembly according to claim 18.
    The damping layer is a friction pad assembly for disc brakes, which is fixed to the torque receiving plate by an adhesive.
PCT/JP2021/026883 2020-07-17 2021-07-16 Guide plate assembly and disc brake friction pad assembly WO2022014712A1 (en)

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Cited By (1)

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DE102022106026A1 (en) 2022-03-15 2023-09-21 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Brake pad for a disc brake of a rail vehicle and disc brake

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JP2007162780A (en) * 2005-12-12 2007-06-28 Akebono Brake Ind Co Ltd Brake lining
JP2008106850A (en) * 2006-10-25 2008-05-08 Akebono Brake Ind Co Ltd Friction pad assembly for disc brake, and disc brake device for vehicle
JP2018185036A (en) * 2017-04-24 2018-11-22 曙ブレーキ工業株式会社 Friction pad assembly for disc brake

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JP2007162780A (en) * 2005-12-12 2007-06-28 Akebono Brake Ind Co Ltd Brake lining
JP2008106850A (en) * 2006-10-25 2008-05-08 Akebono Brake Ind Co Ltd Friction pad assembly for disc brake, and disc brake device for vehicle
JP2018185036A (en) * 2017-04-24 2018-11-22 曙ブレーキ工業株式会社 Friction pad assembly for disc brake

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022106026A1 (en) 2022-03-15 2023-09-21 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Brake pad for a disc brake of a rail vehicle and disc brake

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