JP4611263B2 - Friction pad assembly for vehicle disc brake device - Google Patents

Description

  The present invention can maintain a stable frictional area by maintaining a stable friction area regardless of the deformation of the disk rotor, and can reduce cost and increase productivity by reducing the number of components and reducing the machining accuracy of the parts used. The present invention relates to a friction pad assembly of a vehicle disc brake device improved so as to realize improvement.

  A disc brake device includes a disc rotor fixed to an axle, a torque receiving plate disposed opposite to the disc rotor, and an actuator that drives the torque receiving plate to advance and retract toward the disc rotor. When the brake caliper is fixed and the lining member is assembled to the disk rotor side surface of the torque receiving plate, the torque receiving plate is advanced to the disk rotor side and the lining member is pressed against the disk rotor. A braking force is generated by the sliding friction.

  In the disk brake device for railway vehicles, the disk rotor and brake lining are large, so if the lining member to be pressed against the disk rotor is formed as an integral part, it is non-contact due to undulations generated in the disk rotor due to frictional heat, etc. Therefore, the stable friction area cannot be maintained, and stable braking characteristics cannot be obtained.

  Therefore, in order to solve such problems, a large number of second link plates are laid on a substantially flat surface on the torque receiving plate, and a large number of first link plates are attached to each other on each second link plate. A plurality of lining members are installed independently on each first link plate so as to be able to turn independently of each other, and each first link plate is moved by moving the torque receiving plate toward the disk rotor. A brake lining having a configuration in which each of the above lining members is brought into contact with a disk rotor has been proposed (for example, see Patent Document 1).

  In the brake lining having such a configuration, each of the lining members divided into small parts follows the undulations on the surface of the disk rotor and makes contact with the surface of the disk rotor by individual turning operations, so that a stable friction area is maintained. , Stable braking characteristics can be maintained.

Japanese National Patent Publication No. 10-507250

  By the way, in the brake lining described in Patent Document 1, the position regulation of the lining member on the torque receiving plate is spherical contact in both the direction parallel to the surface of the lining member and the direction orthogonal to the surface of the lining member. The lining member is pivoted by the first universal joint that is pivotally connected to the first link plate.

  In addition, the position of the second link plate on the first link plate is also swiveled by the spherical contact portion in both the direction parallel to the surface of the lining member and the direction orthogonal to the surface of the lining member. The second universal joint is freely connected to the second link plate.

  As a result, all braking torques acting on the lining member during braking are transmitted in order from the lining member to the first link plate and from the first link plate to the second link plate via the spherical contact portion of the universal joint, And finally it will be transmitted to the torque receiving plate to which the second link plate is connected, each universal joint must be robust and the spherical contact part of each universal joint must be processed with high precision , Excessive loads may concentrate on some universal joints, which may cause damage.

  However, since there are many places where universal joints are used, all universal joints must be made to have a robust structure, and the spherical contact portion and the mating contact portion with which the spherical contact portion contacts must be processed with high precision. As a result, there is a problem that the processing cost of parts increases, resulting in an increase in brake lining costs and a decrease in productivity.

  Further, the brake lining described in Patent Document 1 is for railway vehicles, and braking torque acting on the lining member during braking is applied in order from the lining member to the first link plate, and from the first link plate to the second link plate. Because of the transmission structure, there are many components and the device becomes large, so that it could not be used for a disc brake of a small vehicle such as a passenger car.

  Accordingly, an object of the present invention is to solve the above-mentioned problems, and can maintain a stable braking area by maintaining a stable friction area regardless of the deformation of the disk rotor, and can reduce the number of components and reduce the number of components used. Friction pad assembly for a vehicle disc brake device that can reduce costs and improve productivity by reducing machining accuracy, can be downsized, and is also suitable as a brake device for small vehicles such as passenger cars Is to provide.

The above object is achieved by the following configuration.
(1) a guide plate that is disposed opposite to the disk rotor and has a plurality of guide holes formed therethrough;
A back plate is affixed to the back surface of the lining main body to be brought into contact with the disk rotor, and the outer peripheral surface of the torque transmission boss projectingly provided on the back plate is pivotably fitted into the guide hole from the surface side of the guide plate. A plurality of matching lining members;
A spherical spring is fitted by a wire spring that is fitted on the spherical contact boss projecting from the center of the tip of the torque transmitting boss from the back side of the guide plate and engaged with the outer periphery of the spherical contact boss. A leaf spring that is fixed to the contact boss, and that prevents the lining member from slipping into the guide hole by abutting the outer periphery with the peripheral edge of the guide hole;
A link plate disposed on the back side of the guide plate and rotatably supporting end surfaces of the spherical contact bosses of the plurality of lining members by a spherical contact structure;
A torque receiving plate that is fixed to the guide plate and pivotally supports the link plate by a spherical contact structure, and is driven forward and backward toward the disk rotor;
With
The braking torque that acts on the lining body when the lining body is pressed by the disk rotor is transmitted to the torque receiving plate through a guide plate that is fitted with the torque transmission boss portion of the back plate. A friction pad assembly for a vehicle disc brake device.

(2) In addition to the configuration of (1) above, the link plate contacts the tip surface of the spherical contact boss at the bottom of the concave portion that accommodates the spherical contact boss. It has a spherical contact surface that supports the contact boss part in a pivotable manner,
A friction pad assembly for a vehicle disc brake device, wherein a difference between an outer diameter of the spherical contact boss portion and an inner diameter of the recess is set to be smaller than a wire diameter of the wire spring.

  (3) In addition to the configuration of (1) or (2) above, the torque transmitting boss portion is fitted with a guide ring having a convex arc surface formed on the outer peripheral surface thereof, and contacts the inner peripheral surface of the guide hole. A friction pad assembly for a disc brake device for a vehicle.

  (4) In addition to the configurations of (1) to (3), the spherical contact structure includes a spherical convex surface and a spherical concave surface that comes into spherical contact with a curvature larger than the curvature of the spherical convex surface. A friction pad assembly for a vehicle disc brake device.

  In the friction pad assembly according to the above (1), the lining member pressed against the disk rotor is composed of a plurality of lining members divided into small parts, and each lining member can turn freely by a spherical contact structure. Therefore, each lining member flexibly follows the deformation of the disk rotor surface against the deformation of the disk rotor surface, and maintains good contact with the disk rotor surface. Therefore, a stable friction area can be maintained and a stable braking characteristic can be maintained regardless of the deformation of the disk rotor.

In addition, the position regulation of the lining member on the torque receiving plate is formed on the torque transmission boss projecting on the back plate of the lining member and the guide plate in the direction parallel to the disk rotor surface. This is performed by fitting with a guide hole, and in a direction perpendicular to the disk rotor surface, a spherical contact structure is used.
Accordingly, the braking torque acting on the lining member during braking is transmitted from the lining member to the torque receiving plate fixed to the guide plate via the guide plate. Also, the pressing force of the piston that presses the torque receiving plate toward the disk rotor and presses the lining member against the disk rotor is transmitted from the torque receiving plate to the link plate and from the link plate to each lining member via the spherical contact structure. Is done.
That is, the member that receives the braking torque from the lining member and the member that receives the pressing force from the lining member are set separately, and the braking torque that becomes a large load only by the pressing force does not act on the spherical contact structure.
For this reason, the spherical abutment surface and abutment holding surface constituting the aspherical abutment structure can achieve robust positioning to receive the braking torque even if machining accuracy is eased and machining is facilitated. Costs can be reduced and productivity can be improved by relaxing processing accuracy of structural parts.

Furthermore, as a mechanism for fastening the back plate of the lining member and the leaf spring, for example, a structure using a support shaft that penetrates these components and a retaining ring that fits into a groove formed in the support shaft is used. However, in such a mechanism that uses a support shaft and a retaining ring that are separate from the back plate, an increase in the number of parts and an increase in the assembly process cause an increase in cost.
However, in the case of the friction pad assembly configured as described above, after the leaf spring is fitted to the spherical contact boss formed integrally with the back plate, the wire spring is engaged with the spherical contact boss. Thus, the leaf spring is fastened to the back plate, and the cost can be reduced by reducing the number of parts and the assembly process because the support shaft separate from the back plate is not used.

In the friction pad assembly described in (2) above, the gap between the outer diameter of the spherical contact boss and the inner diameter of the recess of the link plate that houses the spherical contact boss is a leaf spring. Is set smaller than the wire diameter of the wire spring engaged with the spherical contact boss, and the inner peripheral surface of the recess moves to the tip side of the spherical contact boss. To regulate.
Accordingly, it is possible to reliably prevent the wire spring engaged with the spherical abutting boss portion from coming off to the tip side of the spherical abutting boss portion, and to improve the reliability of the fixing function of the leaf spring by the wire spring. it can.

Furthermore, in the friction pad assembly described in (3) above, the torque transmitting boss portion pivots on the inner peripheral surface of the guide hole via a guide ring fitted on the outer periphery with the outer peripheral surface being a convex arc surface. Fits freely.
Accordingly, the convex arc surface of the guide ring allows the torque transmission boss to be inclined along with the turning of the lining member when the lining member turns due to the deformation of the disk rotor surface, thereby smoothing the turning operation of the lining member. be able to.

In the friction pad assembly described in (4) above, the spherical contact structure includes a spherical convex surface and a spherical concave surface that comes into spherical contact with a curvature larger than the curvature of the spherical convex surface, for example, a spherical convex surface. The tip surface of the spherical contact boss and the spherical contact surface of the link plate formed as a spherical concave surface are in contact with each other with a difference in curvature.
Therefore, the contact of the lining member with a difference in curvature allows the lining member to maintain the turning independence at the contact portion with the link plate via the spherical contact boss portion of the back plate.

Preferred embodiments of a friction pad assembly for a vehicle disc brake device according to the present invention will be described below in detail with reference to the drawings.
1 to 10 show an embodiment of a friction pad assembly according to the present invention. FIG. 1 is a front view of a friction pad assembly of a vehicle disc brake device according to the present invention, and FIG. FIG. 3 is a perspective view of one of the two friction pad assembly units constituting the friction pad assembly shown in FIG. 1 as viewed from the upper front side, and FIG. 4 is a perspective view of FIG. FIG. 5 is a cross-sectional view of the friction pad assembly unit shown in FIG. 5, viewed from below on the back side, FIG. 5 is a cross-sectional view taken along the line BB in FIG. FIG. 7 is an enlarged view of a portion C in FIG. 5, FIG. 8 is an enlarged view of a portion D in FIG. 5, and FIG. 9 is a lining assembly shown in FIG. Limp that abuts against the backside of each lining member to maintain the pivotability of each lining member Perspective view of a state in which the assembled over preparative, FIG. 10 is a perspective view of the assembled state of the cover assembly of the guide plate shown in FIG.

  A friction pad assembly 1 of a vehicle disc brake device according to an embodiment is used for a disc brake device for a railway vehicle, and as shown in FIG. The two friction pad assembly units 1A and 1B divided into two.

  Each of the friction pad assembly units 1A and 1B has substantially the same component structure, and is disposed so as to face the disk rotor on the axle and has a plurality of guide holes 3a (see FIG. 5) formed therethrough. A back plate (pressure plate) 6 is affixed to the back surface of the plate 3 and the lining body 5 to be brought into contact with the disk rotor, and the outer peripheral surface of a cylindrical torque transmission boss 6a projecting from the back plate 6 is a guide plate. A guide plate is attached to a plurality of lining members 8 that are pivotably fitted into a cylindrical guide hole 3a from the surface side of 3 and a spherical abutting boss portion 6b protruding from the center of the tip of the torque transmitting boss portion 6a. 3 is a spherical contact with the inner periphery of the leaf spring 9 that is fitted on the outer periphery of the spherical contact boss 6b by engaging with the outer periphery of the spherical contact boss 6b. Positioning on the boss 6b A plurality of wire springs 12 and a plurality of lining members 8 which are arranged on the back surface side of the guide plate 3 and maintain the pivotability of the lining member 8 by the spherical contact structure on the end surfaces of the spherical contact bosses 6b of the lining members 8. The first link plate 11 (see FIGS. 5 and 9) and the second link plate 13 (see FIG. 5) that maintains the pivotability of the first link plate 11 through the spherical contact structure between the first link plates 11. 9) and a torque receiving plate 17 fixed to the guide plate 3 via a cover 15 (FIGS. 4 and 10) covering the link plates 11 and 13.

As shown in FIG. 6, the guide plate 3 has mounting holes 3 b for fixing the cover 15 by screwing, which are formed at appropriate intervals on the peripheral edge.
In the case of the present embodiment, five guide holes 3a for attaching the lining member 8 are formed. As shown in FIG. 5, the torque transmission boss 6a of the back plate 6 is pivotably fitted into a cylindrical guide hole 3a via a guide ring 14 fitted on the outer periphery thereof.
As shown in FIG. 8, the outer peripheral surface of the guide ring 14 that contacts the inner peripheral surface of the guide hole 3a is a convex circular arc surface 14a. When the lining member 8 turns due to the deformation of the disk rotor surface, the convex arcuate surface 14a allows the torque transmitting boss portion 6a to be tilted along with the turning of the lining member 8, thereby smoothly turning the lining member 8. To do.

The back plate 6 to be affixed to the lining body 5 is formed by pressing a metal plate or the like so that a torque transmitting boss portion 6a or a spherical contact boss portion 6b protruding from a plate portion fixed to the back surface of the lining body 5 is provided. It is integrally formed.
The torque transmission boss 6a and the spherical contact boss 6b are both cylindrical. The spherical contact boss 6b has a smaller diameter than the torque transmission boss 6a, and is provided in a form in which the central axis coincides with the torque transmission boss 6a.

The wire spring 12 is formed by forming a steel wire having an appropriate spring property into a ring shape. As shown in FIG. 7, the wire spring 12 is engaged with a groove portion 61 formed on the outer periphery on the base end side of the spherical contact boss portion 6b. By joining, it is fixed to the spherical contact boss 6b.
When the wire spring 12 is engaged with the groove 61 on the outer periphery of the spherical contact boss 6b, as shown in FIGS. 7 and 11, the outer peripheral surface of the wire spring 12 is fitted to the spherical contact boss 6b. The inner peripheral edge of the spring 9 is pressed, and the inner peripheral edge of the leaf spring 9 is positioned and fixed in a state where it is pressed against the step at the base end of the spherical contact boss 6b (end surface of the torque transmitting boss 6a).

  As shown in FIG. 6, the leaf spring 9 has a disc shape in which a hole fitted around the spherical contact boss portion 6b is formed at the center, and the outer peripheral portion 9a abuts on the peripheral portion of the guide hole 3a. The outer diameter is set. And the slit 9b is formed toward the vicinity of the hole of the center part from the outer peripheral part 9a. The slit 9b facilitates elastic deformation of the outer peripheral portion 9a in the plate thickness direction, and obtains a spring characteristic when the outer peripheral portion 9a contacts the peripheral edge of the guide hole 3a.

  As shown in FIG. 5, the leaf spring 9 is inserted into the spherical contact boss 6 b in a state of being inserted through the guide hole 3 a of the guide plate 3 and protruding to the back side of the guide plate 3. And assembled into the spherical contact boss 6b. The leaf spring 9 is fixed to the spherical contact boss 6b by engaging the wire spring 12 with the groove 61 of the spherical contact boss 6b. When the fixing of the leaf spring 9 to the spherical contact boss portion 6b is completed, at the same time, the outer peripheral portion 9a of the leaf spring 9 presses the peripheral portion of the guide hole 3a so that the lining member 8 does not fall out of the guide hole 3a. The retaining is completed.

  In the manufacturing process of the friction pad assembly 1, first, as shown in FIG. 6, the lining members 8 are assembled in all the guide holes 3a of the guide plate 3, and then the wire springs 12 are attached to the spherical contact bosses 6b. Thus, the lining assembly 10 in which the leaf spring 9 is fixed to each lining member 8 is completed. Then, the first link plate 11, the second link plate 13, the cover 15, and the torque receiving plate 17 are sequentially assembled to the lining assembly 10.

As shown in FIGS. 5 and 7, the first link plate 11 is provided with two recesses 11 a for accommodating the spherical contact bosses 6 b corresponding to the arrangement pitch of the guide holes 3 a on the guide plate 3. ing. The concave portion 11a is a substantially cylindrical cavity, and a spherical contact surface 11b of a spherical concave surface that is in spherical contact with the spherical convex contact surface 63 which is the tip surface of the spherical contact boss portion 6b is formed at the bottom. ing. The spherical concave surface of the spherical contact surface 11b is formed with a larger curvature than the spherical convex surface of the spherical contact boss portion 6b. The spherical abutting surface 11b cooperates with the spherical abutting surface 11b and the abutting surface 63 at the tip of the spherical abutting boss portion 6b having a difference in curvature to maintain the pivotability of the lining member 8. The spherical contact structure is configured.
That is, when the first link plate 11 is mounted, the two lining members 8 having the spherical contact surface 63 in contact with the spherical contact surface 11b of the recess 11a of the first link plate 11 pivot independently of each other. It is supported freely.

  In the case of this embodiment, as shown in FIG. 7, the difference between the outer diameter d1 of the spherical contact boss 6b and the inner diameter d2 of the recess 11a is set smaller than the wire diameter of the wire spring 12. Yes.

As shown in FIG. 9, the second link plate 13 is placed on the two first link plates 11, and the two first links are formed by a spherical contact structure (not shown) configured in the same manner as described above. The link plate 11 and the lining member 8 that is not supported by the first link plate 11 are pivotally contacted to ensure the pivotability of these members independently of each other.
Although the spherical contact structure in which the second link plate 13 maintains the pivotability of the first link plate 11 or the lining member 8 is not shown, the first link plate 11 on the second link plate 13 side is not shown. Since the position near the center of gravity of the surface is pivotably pressed, the first link plate 11 can have a contact structure similar to the structure in which the lining member 8 is pivotally pressed.
As shown in FIG. 9, a spherical contact surface 13a that forms a spherical contact structure with the torque receiving plate 17 is located at the center of gravity of the surface of the second link plate 13 on the torque receiving plate 17 side. Is formed.

As shown in FIG. 10, the cover 15 covers the top of each of the link plates 11 and 13 after the first link plate 11 and the second link plate 13 are assembled to the back surface of the lining assembly 10. 3 and 4, the peripheral edge portion of the lining assembly 10 is guided by a screw 16a inserted from the front surface side of the guide plate 3 and a nut 16b screwed into the screw 16a. The plate 3 is fastened and fixed to the mounting hole 3 b of the plate 3.
As shown in FIG. 10, the cover 15 has a window portion 15 a that exposes the second link plate 13.

As shown in FIG. 4, the torque receiving plate 17 is fixed to the outer surface of the cover 15 by rivets 18. Therefore, the torque receiving plate 17 is fixed to the guide plate 3 via the cover 15.
Although not shown, the surface of the torque receiving plate 17 on the cover 15 side contacts the spherical contact surface 13a exposed to the window portion 15a opened in the cover 15, and the second link plate 13 turns. A contact holding surface having a larger curvature than the contact surface 13a is formed to maintain flexibility.

  The torque receiving plate 17 fixed to the cover 15 is driven forward and backward toward the disc rotor by an actuator built in a brake caliper (not shown) fixed to the vehicle body frame. Due to the movement of the torque receiving plate 17 toward the disk rotor, the lining body 5 is pressed against the disk rotor and exerts a braking force.

  In the friction pad assembly 1 described above, the lining member 8 pressed against the disk rotor is composed of a plurality of lining members 8 divided into small parts, and each lining member 8 is provided on a guide plate. Since it is supported in the hole so as to be rotatable, each lining member 8 follows the deformation of the disk rotor surface and maintains good contact with the disk rotor surface. Therefore, a stable friction area can be maintained and a stable braking characteristic can be maintained regardless of the deformation of the disk rotor.

Moreover, the position regulation of the lining member 8 on the torque receiving plate is such that the torque transmission boss 6a projecting from the back plate 6 of the lining member 8 and the guide plate in the direction parallel to the disk rotor surface. In the direction perpendicular to the disk rotor surface, between the lining member 8 and the first link plate 11, the first link plate 11 is achieved. This is achieved by each spherical contact structure having a difference in curvature between the second link plate 13 and the second link plate 13 and between the second link plate 13 and the torque receiving plate 17.
Therefore, the braking torque acting on the lining member 8 during braking is directly transmitted from the lining member 8 to the torque receiving plate 17 fixed to the guide plate 3 via the guide ring 14 and the guide plate 3. Further, the pressing force of the piston that presses the torque receiving plate 17 toward the disk rotor and presses the lining body 5 against the disk rotor is applied from the torque receiving plate 17 to the second link plate 13 via the spherical contact structures described above. The second link plate 13 is transmitted to the first link plate 11, and the first link plate 11 is transmitted to each lining member 8.

That is, the member that receives the braking torque from the lining member 8 and the member that receives the pressing force from the lining member 8 are set separately, and the braking torque that is a large load does not act on the spherical contact structure.
Therefore, the spherical contact surface and the contact holding surface constituting the spherical contact structure can realize a robust positioning that firmly receives the braking torque even if the processing accuracy is reduced and the processing is facilitated. Cost reduction and productivity improvement can be realized by relaxing processing accuracy of spherical contact structure parts.

Furthermore, as a mechanism for fastening the back plate 6 and the leaf spring 9 of the lining member 8, for example, a support shaft that penetrates these components and a retaining ring that fits into a groove formed in the support shaft are used. Although it can be configured, in such a mechanism that uses a support shaft and a retaining ring that are separate from the back plate, an increase in the number of parts and an increase in the assembly process cause an increase in cost.
However, in the case of the friction pad assembly 1 of the present embodiment, after the leaf spring 9 is fitted to the spherical contact boss 6b formed integrally with the back plate 6, the spherical contact boss 6b By engaging the wire spring 12, the leaf spring 9 is fastened to the back plate 6, and the number of parts and the assembly process are reduced as much as the support shaft separate from the back plate 6 is not used. Reduction can be achieved.

  Further, by integrally forming the torque transmission boss 6a and the spherical contact boss 6b on the back plate 6 of the lining member 8, it is possible to reduce the number of parts and achieve compactness, such as a passenger car. Therefore, it is possible to achieve downsizing that is useful as a brake device for a small vehicle.

  Further, the torque transmission boss 6a formed integrally with the back plate 6 is set to have a larger diameter than the spherical contact boss 6b formed integrally with the tip, but the torque transmission boss 6a having a larger diameter is formed. By fitting the outer periphery of the guide plate 3 to the guide member, it becomes easy to ensure the strength necessary for transmitting the braking torque from the lining member 8 to the guide plate 3, and the durability can be improved.

In the friction pad assembly 1 of the present embodiment, the outer diameter d1 of the spherical contact boss 6b and the inner diameter d2 of the recess 11a of the first link plate 11 that accommodates the spherical contact boss 6b. The gap between them is set smaller than the wire diameter of the wire spring 12 engaged with the spherical contact boss 6b for fixing the leaf spring 9, and the inner peripheral surface of the recess 11a is used for spherical contact. The movement of the wire spring 12 toward the distal end side of the boss 6b is restricted.
Accordingly, it is possible to reliably prevent the wire spring 12 engaged with the spherical contact boss 6b from coming off to the tip side of the spherical contact boss 6b, and the reliability of the function of fixing the leaf spring 9 by the wire spring 12 Can be improved.

1 is a front view of an embodiment of a friction pad assembly of a vehicle disc brake device according to the present invention. It is A arrow directional view of FIG. FIG. 2 is a perspective view of one unit of two friction pad assembly units constituting the friction pad assembly shown in FIG. 1 as viewed from the upper front side. It is the perspective view seen from the back side lower side of the friction pad assembly unit shown in FIG. It is BB sectional drawing of FIG. It is the perspective view which looked at the lining assembly which attached the lining member to each guide hole of the guide plate shown in FIG. 5 from the back side lower side. It is an enlarged view of the C section of FIG. It is an enlarged view of the D section of FIG. FIG. 7 is a perspective view of a state in which a limp plate for maintaining the pivotability of each lining member is attached to the back surface of the lining assembly shown in FIG. 6. FIG. 10 is a perspective view of a state in which a cover is assembled to the guide plate of the assembly illustrated in FIG. 9.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Friction pad assembly 1A, 1B Friction pad assembly unit 3 Guide plate 3a Guide hole 5 Lining body 6 Back plate (pressure plate)
6a Torque transmitting boss portion 6b Spherical contact boss portion 8 Lining member 9 Leaf spring 9a Outer peripheral portion 9b Slit 11 First link plate 11a Recessed portion 11b Spherical contact surface 12 Wire spring 13 Second link plate 13a Spherical contact Surface 15 Cover 17 Torque receiving plate 61 Groove 62 Bottom surface 63 Spherical contact surface

Claims (4)

A guide plate that is disposed opposite to the disk rotor and has a plurality of guide holes formed therethrough,
A back plate is affixed to the back surface of the lining main body to be brought into contact with the disk rotor, and the outer peripheral surface of the torque transmission boss projectingly provided on the back plate is pivotably fitted into the guide hole from the surface side of the guide plate. A plurality of matching lining members;
A spherical spring is fitted by a wire spring that is fitted on the spherical contact boss projecting from the center of the tip of the torque transmitting boss from the back side of the guide plate and engaged with the outer periphery of the spherical contact boss. A leaf spring that is fixed to the contact boss, and that prevents the lining member from slipping into the guide hole by abutting the outer periphery with the peripheral edge of the guide hole;
A link plate disposed on the back side of the guide plate and rotatably supporting end surfaces of the spherical contact bosses of the plurality of lining members by a spherical contact structure;
A torque receiving plate that is fixed to the guide plate and pivotally supports the link plate by a spherical contact structure, and is driven forward and backward toward the disk rotor;
With
The braking torque that acts on the lining body when the lining body is pressed by the disk rotor is transmitted to the torque receiving plate through a guide plate that is fitted with the torque transmission boss portion of the back plate. A friction pad assembly for a vehicle disc brake device. The link plate has a spherical abutting contact with a tip end surface of the spherical abutting boss portion and rotatably supporting the spherical abutting boss portion at a bottom portion of a recess accommodating the spherical abutting boss portion. With a surface,
2. The vehicle disc brake device according to claim 1, wherein a difference between an outer diameter of the spherical contact boss portion and an inner diameter of the concave portion is set smaller than a wire diameter of the wire spring. Friction pad assembly.   3. The vehicle disk according to claim 1, wherein the torque transmitting boss portion is fitted with a guide ring having a convex arc surface formed on an outer peripheral surface thereof, and contacts the inner peripheral surface of the guide hole. Brake device friction pad assembly. 4. The vehicle disc brake according to claim 1, wherein the spherical contact structure includes a spherical convex surface and a spherical concave surface that comes into spherical contact with a curvature larger than the curvature of the spherical convex surface. 5. The friction pad assembly of the device.

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