JP5816043B2 - Friction pad assembly for disc brake - Google Patents

Description

  The present invention relates to a disc brake friction pad in which a plurality of lining assemblies are rotatably supported on a guide plate that receives braking torque, and a braking force is generated by sliding friction when the lining assembly is pressed against a disc rotor. The present invention relates to an assembly, and more particularly, to an improvement for realizing cost savings and productivity improvement by relaxing processing accuracy of components used and reducing component parts.

  A disc brake device includes a disc rotor fixed to an axle, a disc brake friction pad assembly in which a lining member is assembled on a disc rotor side surface of a torque receiving plate arranged to face the disc rotor, and a torque receiver. And a brake caliper that is fixed to the vehicle body frame with a built-in actuator that drives the plate toward and away from the disk rotor. The torque receiving plate is advanced to the disk rotor side and the lining member is pressed against the disk rotor. Braking force is generated by sliding friction.

  In a disk brake device for a railway vehicle, since the disk rotor and the friction pad assembly are large, if the lining member to be pressed against the disk rotor is formed as an integral part, undulation generated in the disk rotor due to frictional heat or the like The non-contact area increases, a stable friction area cannot be maintained, and stable braking characteristics cannot be obtained.

  Therefore, in order to solve such a problem, a plurality of second link plates are laid on a substantially flat surface on the torque receiving plate, and a plurality of first link plates are connected to each other on each second link plate. A plurality of lining assemblies are installed independently on each first link plate so as to be pivotable independently of each other, and each first link is moved by moving the torque receiving plate toward the disk rotor. A friction pad assembly has been proposed in which each lining assembly on a plate is brought into contact with a disk rotor (see, for example, Patent Document 1).

  In the friction pad assembly having such a configuration, each of the lining assemblies divided into small parts follows the undulation of the surface of the disk rotor and makes contact with the surface of the disk rotor in an individual swiveling operation, so that a stable friction area is obtained. Maintaining stable braking characteristics.

  Further, as a friction pad assembly improved from the above friction pad assembly, a slit is provided in an overlap region of the torque receiving plate with the lining assembly so that the overlap region can be partially elastically deformed. There has also been proposed an improvement in the followability of the lining assembly to the undulation of the disk rotor (see, for example, Patent Document 2).

Japanese National Patent Publication No. 10-507250 JP 2005-530963 A

By the way, in the friction pad assembly described in Patent Document 1, the position regulation of the lining assembly on the torque receiving plate is performed in a direction parallel to the surface of the lining assembly and a direction orthogonal to the surface of the lining assembly. In either case, the lining assembly is pivotably connected to the first link plate by a spherical contact portion, and the first universal joint is used.
The position of the second link plate on the first link plate is restricted by the spherical contact portion in both the direction parallel to the surface of the lining assembly and the direction orthogonal to the surface of the lining assembly. Is performed by a second universal joint that is pivotally connected to the second link plate.

  As a result, all braking torques acting on the lining assembly during braking are transmitted in sequence from the lining assembly to the first link plate and from the first link plate to the second link plate via the spherical joint of the universal joint. Finally, the torque is transmitted to the torque receiving plate to which the second link plate is coupled, and each universal joint is made robust and the spherical contact portion of each universal joint is processed with high accuracy. Otherwise, an excessive load concentrates 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 in that the processing cost of the components increases, leading to an increase in the cost of the friction pad assembly and a decrease in productivity.

  In addition, it is necessary to devise the lining assembly holding structure so that the lining assembly does not fall off inadvertently during transportation of the friction pad assembly or maintenance of the disc brake device. If it seems to increase, there is a problem that an increase in the number of parts leads to an increase in cost, and an increase in the number of assembly steps accompanying an increase in the number of parts causes a decrease in productivity.

  In addition, if the lining assembly rotates inadvertently due to contact with the disk rotor, this causes loss of transmission of braking torque or brake noise, which restricts the rotation of the lining assembly. However, when the number of parts increases, the increase in parts leads to an increase in cost, and at the same time, the increase in the number of assembly steps accompanying the increase in parts causes a decrease in productivity. It was.

  In addition, since the disc brake friction pad assembly has a configuration in which a plurality of lining assemblies are laid out in a plane, unless the dimensional tolerance in the thickness direction of the lining assembly is absorbed, the dimensional tolerance can be reduced. For this reason, the contactability of each lining assembly with respect to the disk rotor may vary, and it may be difficult to maintain stable braking characteristics.

  Further, in the friction pad assembly described in Patent Document 2, the back side of the back plate portion of the lining assembly is exposed to the outside because of a slit that allows the overlap region of the torque receiving plate to be partially elastically deformed. As a result, dust or the like easily enters the back surface of the back plate portion from the slit, and there is a possibility that the turning performance or the like of the lining assembly may be hindered by the entry of dust or the like.

  Accordingly, an object of the present invention is to solve the above-mentioned problems, and by reducing the machining accuracy of the parts used and reducing the parts, it is possible to realize cost savings and productivity improvements, and the lining assembly Allowing dimensional tolerances in the thickness direction to prevent variations in the contactability of each lining assembly to the disk rotor, and thus stable without being affected by the dimensional tolerance in the thickness direction of the lining assembly It is an object of the present invention to provide a friction pad assembly that can maintain the braking characteristics. It is another object of the present invention to provide a disc brake friction pad assembly in which dust or the like hardly enters the back surface of the back plate portion of the lining assembly and can suppress the occurrence of a failure caused by the entry of dust or the like. It is another object of the present invention to provide a disc brake friction pad assembly that can restrict the rotation of the lining assembly due to contact with the disc rotor and prevent the occurrence of braking torque transmission loss, brake noise, and the like.

The above object is achieved by the following configuration.
(1) A disc brake friction pad assembly according to the present invention is for a disc brake in which a plurality of lining assemblies are pivotally supported on a guide plate that receives braking torque, and the lining assembly is pressed against a disc rotor. A friction pad assembly,
The lining assembly has a back plate portion fixed to the back surface of the friction material,
In the back plate portion, a plate fitting portion whose outer peripheral surface is turnably fitted to a guide hole portion provided in the guide plate, a retaining flange portion having an outer diameter larger than the guide hole portion, A curved convex portion is formed integrally with the back plate portion so as to be raised at the center of the retaining flange portion toward the torque receiving plate side fixed to the guide plate with a gap between the back plate portion,
The lining assembly is inserted and mounted in the guide hole portion from the back surface side of the guide plate, and is mounted between the back surface of the back plate portion facing the torque receiving plate and the torque receiving plate. Supported by the member biased toward the guide plate,
When a pressing load acting on the friction material pressed by the disk rotor exceeds a set load, the lining assembly is bent by the spring member and the curved convex portion comes into contact with the torque receiving plate. Inclination of the lining assembly is allowed by the convex portion, and braking torque acting by contact between the disk rotor and the friction material is transmitted from the plate fitting portion to the guide plate for braking.

(2) In the configuration described in (1) above, the guide plate is formed of a flat plate material having a predetermined plate thickness.

(3) In the configuration described in (1) or (2) above, the plate fitting portion is formed in a convex curved shape on the guide hole side.

(4) In the configuration described in any one of (1) to (3) above, the back plate portion is configured to have a spring accommodating groove that accommodates one end side of the spring member.

(5) In the configuration described in any one of (1) to (4) above, the torque receiving plate is configured to seal the back side of the back plate portion.

(6) In the configuration according to any one of (1) to (5), an outer peripheral surface of the back plate portion is relatively rotated with respect to the guide hole portion between the back plate portion and the guide plate. It is set as the structure by which the rotation prevention mechanism which prevents doing is provided.

(7) In the configuration according to (6), the rotation prevention mechanism includes a fitting protrusion protruding from one of an outer peripheral surface of the back plate portion and an inner peripheral surface of the guide hole portion, It is set as the structure which has a fitting recessed part which is recessedly provided in either one of the outer peripheral surface of a backplate part, and the inner peripheral surface of the said guide hole part, and fits into the said fitting protrusion.

(8) In the configuration according to (6), the rotation prevention mechanism includes an engagement convex portion protruding from an outer peripheral surface of the retaining flange portion, and the engagement between a pair of adjacent lining assemblies. It is set as the structure which prevents mutual rotation by engaging convex parts.

(9) In the configuration according to any one of (1) to (8) above, the spring member is configured by combining a plurality of springs having different spring constants.

According to the friction pad assembly of the present invention, the braking torque acting on the lining assembly during braking is transmitted to the guide plate and further directly to the torque receiving plate on which the guide plate is fixed.
Further, the pressing force that presses the lining assembly against the disk rotor is applied to the back of the lining assembly in which the curved convex portions are integrally formed from the torque receiving plate via the curved convex portions that are in contact with the torque receiving plate. Acts on the plate.
That is, the member that receives the braking torque from the lining assembly and the member that applies the pressing force to the lining assembly are set separately, and the curved convex portion that applies the pressing force to the lining assembly and the torque receiving plate A braking torque that is a large load does not act on the contact portion.
Therefore, each contact portion that transmits the pressing force does not need to be a solid engagement such as a ball joint that receives the braking torque, and it is possible to realize cost saving and productivity improvement by relaxing processing accuracy.

1 is a front view of a disc brake friction pad assembly according to a first embodiment of the present invention. It is A arrow directional view of FIG. FIG. 3 is a view taken in the direction of arrow B in FIG. 2. It is CC sectional drawing of FIG. It is a front view of the friction pad assembly for disc brakes concerning a 2nd embodiment of the present invention. FIG. 6 is a rear view of the disc brake friction pad assembly shown in FIG. 5. FIG. 6 is a perspective view from one front side of two unit friction pad assemblies constituting the friction pad assembly shown in FIG. 5. It is a perspective view from the back side of the unit friction pad assembly shown in FIG. It is DD sectional drawing of FIG. It is E arrow line view of FIG. It is a rear view of the state which removed the torque receiving plate of the friction pad assembly for disc brakes concerning 3rd Embodiment of this invention. FIG. 12 is a rear view of the disc brake friction pad assembly shown in FIG. 11 with a torque receiving plate attached thereto. FIG. 12 is a perspective view from the front side of the guide plate and lining assembly of the disc brake friction pad assembly shown in FIG. 11. It is FF sectional drawing of FIG. It is a rear view of the state which removed the torque receiving plate of the friction pad assembly for disc brakes concerning 4th Embodiment of this invention. It is GG sectional drawing of FIG. It is a rear view of the state which removed the torque receiving plate of the friction pad assembly for disc brakes concerning 5th Embodiment of this invention. It is a disassembled perspective view from the back side of the friction pad assembly for disk brakes shown in FIG. It is a principal part rear view for demonstrating the effect | action of the lining assembly shown in FIG. 17, (a) shows the state in which the rotational force is not acting on a lining assembly, (b) is a rotation to a lining assembly. Indicates the state in which a force is applied. It is a rear view of the state which removed the torque receiving plate of the friction pad assembly for disc brakes concerning 6th Embodiment of this invention. FIG. 21 is a main part rear view for explaining the operation of the lining assembly shown in FIG. 20, in which (a) shows a state in which no rotational force is applied to the lining assembly, and (b) shows a rotation of the lining assembly. Indicates the state in which a force is applied. It is principal part sectional drawing for demonstrating the friction pad assembly for disc brakes concerning 7th Embodiment of this invention, (a) shows before torque receiving plate attachment, (b) shows after torque receiving plate attachment. Show.

Embodiments of a disc brake friction pad assembly according to the present invention will be described below in detail with reference to the drawings.
1 to 4 show a friction pad assembly according to a first embodiment of the present invention. FIG. 1 is a front view of the friction pad assembly for a disc brake according to the present invention, and FIG. FIG. 3 is an arrow view, FIG. 3 is an arrow B view of FIG. 2, and FIG.

  The disc brake friction pad assembly (hereinafter simply referred to as “friction pad assembly”) 100 according to the first embodiment is used for a disc brake device for a railway vehicle, and is opposed to a disc rotor on an axle. The brake caliper (not shown) that is disposed and fixed to the vehicle body frame is driven forward and backward toward the disc rotor by an actuator built in the brake caliper.

  The friction pad assembly 100 includes a torque receiving plate 3 that is driven toward and away from the disk rotor by an actuator (not shown), a guide plate 11 that is connected and fixed to the disk rotor side of the torque receiving plate 3, and a pivot on the guide plate 11. And a plurality of (in this embodiment, 12) lining assemblies 13 which are fitted and supported.

  The torque receiving plate 3 is attached to the guide plate 11 in a state in which the lining assembly 13 is inserted and attached to the guide plate 11 and a spring member 24 described later is attached to the back side of the lining assembly 13. As shown in FIG. 4, the torque receiving plate 3 is fixed to the guide plate 11 by a rivet 28 with a gap S <b> 1 formed between the torque receiving plate 3 and the back plate portion 22 of the lining assembly 13. The torque receiving plate 3 is formed in a thin dish shape that seals the back side of the back plate portion 22 in order to open a gap S <b> 1 with the back plate portion 22.

  As shown in FIGS. 3 and 4, an anchor plate 31 is fixedly mounted on the back surface of the torque receiving plate 3 with a rivet 32. The anchor plate 31 is connected to an actuator built in a brake caliper (not shown), so that the friction pad assembly 100 can be driven back and forth to the disk rotor.

  As shown in FIG. 1, the guide plate 11 has a plurality of guide holes 11a (12 holes) formed at predetermined intervals, and the lining assembly 13 is attached to each guide hole 11a. The guide plate 11 is formed of a flat plate material having a predetermined plate thickness capable of receiving a braking torque acting on the lining assembly 13 mounted in each guide hole portion 11a during braking.

  The lining assembly 13 includes a friction material 21 molded in a substantially disk shape and a back plate portion 22 fixed to the back surface of the friction material 21. The back plate portion 22 includes a plate fitting portion 22a that is pivotably fitted to a circular guide hole portion 11a that has an outer peripheral surface penetrating the guide plate 11, and a retaining member having an outer diameter larger than that of the guide hole portion 11a. The flange portion 22b and the curved convex portion 22c are integrally formed.

The friction material 21 is set to have an outer diameter smaller than an inner diameter of the guide hole portion 11a so that the guide hole portion 11a can be inserted.
Further, in the case of this embodiment, the plate fitting portion 22a is formed in a curved surface convex toward the guide hole portion 11a so that the turning operation of the lining assembly 13 by sliding contact with the guide hole portion 11a is smooth. Has been.
Further, the curved convex portion 22c is formed so as to protrude from the center of the retaining flange portion 22b in a curved shape convex toward the torque receiving plate 3 side.

  The lining assembly 13 is inserted and attached to the guide hole portion 11 a from the back surface side of the guide plate 11 so that the friction material 21 protrudes to the front surface side of the guide plate 11. The lining assembly 13 inserted and mounted in the guide hole portion 11 a is guided by a spring member 24 mounted in a compressed state between the back surface of the back plate portion 22 facing the torque receiving plate 3 and the torque receiving plate 3. 11 is supported in a state of being urged to the side.

In the present embodiment, the spring member 24 is an annular disc spring. The spring member 24 has an inner diameter set larger than the outer diameter of the curved convex portion 22c.
A spring accommodating groove 22d for accommodating one end side (outer diameter side) of the spring member 24 is formed on the back surface of the back plate portion 22 which is an outer peripheral area of the curved convex portion 22c.
The other end side (inner diameter side) of the spring member 24 protrudes from the spring accommodating groove 22d and comes into contact with the torque receiving plate 3 to be in a compressed state.

  In the compressed state where the spring member 24 is sandwiched between the torque receiving plate 3 fixed to the guide plate 11 and the back plate portion 22, the retaining flange portion 22b is in contact with the peripheral portion of the guide hole portion 11a. The lining assembly 13 is biased toward the guide plate 11 so as to be maintained.

In the case of the friction pad assembly 100 of the present embodiment, when the torque receiving plate 3 is moved to the disk rotor side by the actuator built in the brake caliper and the friction material 21 is pressed against the disk rotor, the pressure acting on the friction material 21 When the load exceeds the set load, the spring member 24 is bent and the curved convex portion 22c comes into contact with the torque receiving plate 3, and the curved convex portion 22c allows the lining assembly 13 to tilt.
The portion of the torque receiving plate 3 where the curved convex portion 22c comes into contact is finished with a smooth surface so that the contact can freely move along with the turning operation of the lining assembly 13.

  In the case of the friction pad assembly 100 according to the present embodiment, the braking torque that is applied by the contact between the disk rotor and the friction material 21 is transmitted from the plate fitting portion 22a of the lining assembly 13 to the guide plate 11, thereby guiding the guide. It acts on the torque receiving plate 3 fixed to the plate 11 and is braked.

In the friction pad assembly 100 described above, the position regulation of the lining assembly 13 on the torque receiving plate 3 is limited to the plate of the lining assembly 13 in the direction parallel to the disk rotor surface of the lining assembly 13. This is performed by fitting the fitting portion 22a with the guide hole portion 11a of the guide plate 11, and is mounted between the back surface of the back plate portion 22 and the torque receiving plate 3 in the direction orthogonal to the disk rotor surface. The biasing force of the spring member 24 is used.
Accordingly, the braking torque acting on the lining assembly 13 during braking is transmitted to the guide plate 11 and directly to the torque receiving plate 3 to which the guide plate 11 is fixed.
The pressing force that presses the lining assembly 13 against the disk rotor during braking acts on the lining assembly 13 from the torque receiving plate 3 via the spring member 24.

That is, a member (guide plate 11) that receives braking torque from the lining assembly 13 and a member (torque receiving plate 3) that applies a pressing force to the lining assembly 13 are set separately. The braking torque that is a large load does not act on the contact portion between the spring member 24 and the torque receiving plate 3 that apply the pressing force.
Therefore, the contact portion between the spring member 24 that transmits the pressing force and the torque receiving plate 3 does not have to be a solid engagement such as a ball joint that receives the braking torque, and the cost can be reduced by reducing the machining accuracy and the productivity. Improvement can be realized.

Further, in the friction pad assembly 100 described above, the outer diameter of the retaining flange portion 22b formed on the back plate portion 22 of the lining assembly 13 is set to be larger than the guide hole portion 11a of the guide plate 11, so The lining assembly 13 is prevented from falling off the guide plate 11 due to the catch of the flange portion 22b.
That is, in order to prevent the lining assembly 13 from falling off from the guide plate 11, an independent dedicated part is not added. Therefore, there is an inconvenience such as an increase in cost due to an increase in parts and a decrease in productivity due to an increase in the number of assembly steps. Can be avoided.

Furthermore, the friction pad assembly 100 described above has a configuration in which a plurality of lining assemblies 13 are laid out in a flat shape, but are arranged so as to be sandwiched between the back surface of the lining assembly 13 and the torque receiving plate 3. Since the formed spring member 24 absorbs the dimensional tolerance in the thickness direction of the lining assembly 13, it is possible to prevent variation in the contact property of each lining assembly 13 with respect to the disk rotor.
Therefore, stable braking characteristics can be maintained without being affected by the dimensional tolerance in the thickness direction of the lining assembly 13.

  Further, in the friction pad assembly 100 described above, the guide plate 11 and the torque receiving plate 3 are fastened with the rivets 28 at the outer peripheral portion and the central portion, thereby forming an integral housing structure, so that loosening due to vibration or the like is prevented. A robust housing structure that does not occur can be obtained at low cost.

  Further, in the friction pad assembly 100 described above, when the pressing load acting on the friction material 21 exceeds the set load, the curved convex portion 22c that makes the lining assembly 13 abut on the torque receiving plate 3 in a tiltable manner is provided on the back side. Since it is integrally formed on the plate portion 22 and no independent dedicated parts are added, it is possible to avoid inconveniences such as an increase in cost due to an increase in parts and a decrease in productivity due to an increase in the number of assembly steps.

  In the friction pad assembly 100 described above, the guide plate 11 that receives the braking torque acting on the lining assembly 13 mounted in each guide hole portion 11a is formed of a flat plate material having a predetermined plate thickness. Therefore, the guide plate 11 can receive the braking torque applied from the lining assembly 13 during braking on the inner peripheral surface extending in the plate thickness direction of each guide hole portion 11a. Therefore, the guide plate 11 having a predetermined plate thickness and sufficient rigidity is bent and deformed into the guide hole by the braking torque applied from the lining assembly like the guide hole of the guide plate formed by bending from a thin plate material. Therefore, a smooth turning operation in the guide hole portion 11a of the lining assembly 13 can be ensured.

  Further, in the friction pad assembly 100 described above, a plate fitting portion 22a inscribed in the guide hole portion 11a of the guide plate 11 is formed in a convex curved shape on the guide hole portion 11a side in order to transmit braking torque. . Therefore, when the lining assembly 13 is pivoted, the plate fitting portion 22a can slide on the inner peripheral surface of the guide hole portion 11a with a low frictional force, and the sliding between the plate fitting portion 22a and the guide hole portion 11a can be performed. The turning operation of the lining assembly 13 by contact can be made smooth.

  Further, in the friction pad assembly 100 described above, the back plate portion 22 is formed with a spring accommodating groove 22 d that accommodates one end side (outer diameter side) of the spring member 24. Therefore, since the spring member 24 is disposed between the back plate portion 22 and the torque receiving plate 3, it is possible to prevent an increase in the arrangement interval between the back plate portion 22 and the torque receiving plate 3. The assembly 100 can be made compact by suppressing the dimension in the direction orthogonal to the sliding surface of the disk rotor.

  Further, in the friction pad assembly 100 described above, the torque receiving plate 3 is not provided with a slit for communicating the inside and the outside, and the torque receiving plate is configured to seal the back side of the back plate portion. In addition, it is difficult for dust and the like to enter the back surface of the back plate portion in the lining assembly, and it is possible to suppress the occurrence of a failure due to the entry of dust and the like.

Next, a disc brake friction pad assembly according to a second embodiment of the present invention will be described with reference to FIGS.
5 is a front view of a disc brake friction pad assembly according to a second embodiment of the present invention, FIG. 6 is a rear view of the disc brake friction pad assembly shown in FIG. 5, and FIG. 7 is shown in FIG. FIG. 8 is a perspective view from the front side of one of the two unit friction pad assemblies constituting the friction pad assembly, FIG. 8 is a perspective view from the back side of the unit friction pad assembly shown in FIG. 7, and FIG. 5 is a sectional view taken along the line DD of FIG. 5, and FIG. 10 is a view taken in the direction of arrow E in FIG.

The disc brake friction pad assembly 100A of the second embodiment is an improvement of the friction pad assembly 100 of the first embodiment, and is arranged adjacent to the circumferential direction of the disc rotor as shown in FIGS. The two unit friction pad assemblies 110 and 120 are formed.
The unit friction pad assemblies 110 and 120 have the same configuration. Each unit friction pad assembly 110, 120 is disposed to face the disk rotor, and is driven forward and backward toward the disk rotor by an actuator built in a brake caliper (not shown).

  The basic configuration of each unit friction pad assembly 110, 120 conforms to the configuration of the previous friction pad assembly 100, and the same configuration as the friction pad assembly 100, or the corresponding configuration, the friction pad assembly. The same reference numerals as those of the body 100 are given and the description thereof is omitted.

  Each of the friction pad assemblies 110 and 120 is configured such that five lining assemblies 13 are pivotably arranged on the guide plate 11. As shown in FIG. 9, each unit friction pad assembly 110, 120 uses a compression coil spring as a spring member 24 mounted in a compressed state between the back surface of the lining assembly 13 and the torque receiving plate 3. And the structure similar to the friction pad assembly 100 may be sufficient except that the anchor plate 31 fixed to the back surface of the torque receiving plate 3 by the rivet 32 is a press-formed product of a metal plate.

  The friction pad assembly 100A described above is divided into a plurality of unit friction pad assemblies 110 and 120, and each unit friction pad assembly can individually follow the undulation of the disk rotor. Compared with the friction pad assembly 100, the followability of the disk rotor to waviness is further improved.

Next, a disc brake friction pad assembly according to a third embodiment of the present invention will be described with reference to FIGS.
FIG. 11 is a rear view of the disc brake friction pad assembly according to the third embodiment of the present invention with the torque receiving plate removed, and FIG. 12 shows the torque receiving plate of the disc brake friction pad assembly shown in FIG. FIG. 13 is a perspective view from the front side of the guide plate and the lining assembly of the disc brake friction pad assembly shown in FIG. 11, and FIG. 14 is a sectional view taken along line FF of FIG. is there.

  The friction pad assembly for disc brake (hereinafter simply referred to as “friction pad assembly”) 200 of the third embodiment is an improvement of the friction pad assembly 100 of the first embodiment, and is as shown in FIG. Further, between the back plate portion 222 in each lining assembly 213 and the guide plate 211 formed of a flat plate material having a predetermined plate thickness, the outer peripheral surface of the back plate portion 222 is relative to the guide hole portion 211a. An anti-rotation mechanism 210 that prevents the rotation is provided.

  The basic configuration of the friction pad assembly 200 conforms to the configuration of the friction pad assembly 100 of the first embodiment, and the same configuration as the friction pad assembly 100 or a corresponding configuration is the friction pad assembly. The same reference numerals as those of the body 100 are given and the description thereof is omitted.

  The anti-rotation mechanism 210 according to the third embodiment includes a semicircular fitting protrusion protruding from the plate fitting portion 22a that is the outer peripheral surface of the back plate portion 222, as shown in FIGS. 22e and a semicircular fitting recess 211b provided in the inner peripheral surface of the guide hole 211a.

  The fitting protrusion 22e and the fitting recess 211b are fitted with an appropriate clearance that does not hinder the turning operation of the lining assembly 213, so that the outer peripheral surface of the back plate 222 is fitted into the guide hole 211a. An anti-rotation mechanism 210 that prevents relative rotation is configured. That is, the rotation of the lining assembly 213 in the guide hole 211a is restricted by the rotation prevention mechanism 210.

  In the friction pad assembly 200 described above, in addition to the same function and effect as the friction pad assembly 100 described above, the rotation of the lining assembly 213 due to contact with the disk rotor during braking is regulated to transmit braking torque. Loss and brake noise can be prevented.

  Further, the rotation prevention mechanism 210 is configured by a simple-shaped fitting protrusion 22e and a fitting recess 211b integrally formed with the back plate portion 222 and the guide plate 211, respectively, and does not add independent dedicated parts. Thus, it is possible to avoid the occurrence of inconveniences such as an increase in cost due to an increase in parts and a decrease in productivity due to an increase in the number of assembly steps.

Next, a disc brake friction pad assembly according to a fourth embodiment of the present invention will be described with reference to FIGS. 15 and 16.
15 is a rear view of the disc brake friction pad assembly according to the fourth embodiment of the present invention with the torque receiving plate removed, and FIG. 16 is a sectional view taken along the line GG of FIG.

  The disc brake friction pad assembly (hereinafter simply referred to as “friction pad assembly”) 300 according to the fourth embodiment is an improvement of the friction pad assembly 200 according to the third embodiment. As shown in FIG. 3, the outer peripheral surface of the back plate portion 322 is formed between the back plate portion 322 in each lining assembly 313 and the guide plate 311 formed of a flat plate material having a predetermined plate thickness. An anti-rotation mechanism 310 is provided to prevent relative rotation.

  The basic configuration of the friction pad assembly 300 conforms to the configuration of the friction pad assembly 200 of the third embodiment, and the same configuration as the friction pad assembly 200 or a corresponding configuration is the friction pad assembly. The same reference numerals as those of the body 200 are given and the description is omitted.

  As shown in FIGS. 15 and 16, the rotation preventing mechanism 310 according to the fourth embodiment includes a semicircular fitting protrusion 311c protruding from the inner peripheral surface of the guide hole portion 311a, and a back plate portion. And a semicircular fitting recess 22f recessed in the plate fitting portion 22a, which is the outer peripheral surface of 322.

The fitting protrusion 311c and the fitting recess 22f are fitted with an appropriate clearance that does not hinder the turning operation of the lining assembly 313, so that the outer peripheral surface of the back plate portion 322 fits into the guide hole portion 311a. An anti-rotation mechanism 310 that prevents relative rotation is configured. That is, the rotation of the lining assembly 313 in the guide hole 311a is restricted by the rotation prevention mechanism 310.
Also with the friction pad assembly 300 described above, the same effects as those of the friction pad assembly 200 described above can be obtained.

Next, a disc brake friction pad assembly according to a fifth embodiment of the present invention will be described with reference to FIGS.
17 is a rear view of the disc brake friction pad assembly according to the fifth embodiment of the present invention with the torque receiving plate removed. FIG. 18 is a rear view of the disc brake friction pad assembly shown in FIG. FIG. 19 is an exploded perspective view from the side, FIG. 19 is a main part rear view for explaining the operation of the lining assembly shown in FIG. 17, and (a) is a state in which no rotational force is applied to the lining assembly. (B) shows a state in which a rotational force is applied to the lining assembly.

  The disc brake friction pad assembly (hereinafter simply referred to as “friction pad assembly”) 400 of the fifth embodiment is an improvement of the friction pad assembly 200 of the third embodiment. As shown in FIG. 4, between the back plate portions 422 of the pair of adjacent lining assemblies 413, the rotation that prevents the outer peripheral surface of the back plate portion 422 from rotating relative to the guide hole portion 11a of the guide plate 11 is prevented. A prevention mechanism 410 is provided.

  The basic configuration of the friction pad assembly 400 conforms to the configuration of the friction pad assembly 200 of the third embodiment, and the same configuration as the friction pad assembly 200 or a corresponding configuration is the friction pad assembly. The same reference numerals as those of the body 200 are given and the description is omitted.

  In the rotation prevention mechanism 410 according to the fifth embodiment, as shown in FIGS. 17 and 18, the substantially rectangular engagement convex portion 22 g protrudes from the outer peripheral surface of the retaining flange portion 22 b of each back plate portion 422. It is the structure which prevents mutual rotation by engaging the engaging convex-shaped parts 22g in a pair of adjacent lining assembly 413 provided mutually.

  As shown in FIG. 19 (a), the engaging convex portions 22g in the adjacent pair of retaining flange portions 22b have an appropriate clearance that does not hinder the turning operation of the lining assembly 413, and have a distal end portion. 22h are arranged close to each other so as to face each other. The front end portion 22h is a contact surface extending a predetermined width parallel to the tangent line on the outer peripheral surface of the retaining flange portion 22b.

  Therefore, as shown in FIG. 19B, when the pair of lining assemblies 413 rotate relative to each other, the adjacent tip portions 22h can engage with each other to prevent mutual rotation. FIG. 19B shows the case where the pair of lining assemblies 413 are rotated in the same direction (counterclockwise direction), but the adjacent tip ends even when the pair of lining assemblies 413 are rotated in different directions. The portions 22h can be engaged with each other to prevent mutual rotation.

  In the friction pad assembly 400 described above, in addition to the operational effects similar to those of the friction pad assemblies 200 and 300 described above, the engagement convex portion having a simple shape in which the anti-rotation mechanism 410 is integrally formed with the back plate portion 422. Since it is composed of only 22 g and the guide plate 11 does not require additional processing, the cost can be reduced.

Next, a disc brake friction pad assembly according to a sixth embodiment of the present invention will be described with reference to FIGS.
FIG. 20 is a rear view of the disc brake friction pad assembly according to the sixth embodiment of the present invention with the torque receiving plate removed, and FIG. 21 is a view for explaining the operation of the lining assembly shown in FIG. FIG. 7A is a rear view of the main part of the lining assembly, in which FIG. 7A shows a state in which no rotational force is applied to the lining assembly, and FIG. 5B shows a state in which the rotational force is applied to the lining assembly.

  The disc brake friction pad assembly (hereinafter simply referred to as “friction pad assembly”) 500 of the sixth embodiment is an improvement of the friction pad assembly 400 of the fifth embodiment. As shown in FIG. 5, between the back plate portions 522 of the pair of adjacent lining assemblies 513, there is an anti-rotation mechanism 510 that prevents the outer peripheral surface of the back plate portion 522 from rotating relative to the guide hole portion 11a. Is provided.

  The basic configuration of the friction pad assembly 500 conforms to the configuration of the friction pad assembly 400 of the fifth embodiment, and the same configuration as the friction pad assembly 400 or a corresponding configuration is the friction pad assembly. The same reference numerals as those of the body 400 are given and the description thereof is omitted.

  As shown in FIGS. 20 and 21, the rotation preventing mechanism 510 according to the sixth embodiment includes an engagement convex portion 22 i formed by a pair of substantially rectangular convex portions 22 j extending in parallel with each back plate portion. 522 is configured to protrude from the outer peripheral surface of the retaining flange portion 22b of 522 and to prevent mutual rotation by engaging the engaging convex portions 22i of the pair of adjacent lining assemblies 413 with each other.

  As shown in FIG. 21 (a), the engaging convex portions 22i of the adjacent pair of retaining flange portions 22b mesh with each other with an appropriate clearance that does not hinder the turning operation of the lining assembly 513. Arranged in this way. The engaging convex portions 22i are a pair of substantially rectangular convex portions 22j extending in parallel from a position slightly offset in the clockwise direction with respect to the center line X of the back plate portion 522 on the outer peripheral surface of the retaining flange portion 22b. And a substantially rectangular concave portion 22k formed between the convex portions 22j.

Therefore, as shown in FIG. 21 (b), when the pair of lining assemblies 513 rotate with each other, the side surfaces of the convex portions 22j and the concave portions 22k of the engaging convex portions 22i meshing with each other are engaged with each other. Can be prevented.
Also with the friction pad assembly 500 described above, the same effects as those of the friction pad assembly 4 described above can be obtained.

Next, a disc brake friction pad assembly according to a seventh embodiment of the present invention will be described with reference to FIG.
FIG. 22 is a cross-sectional view of a main part for explaining a disc brake friction pad assembly according to a seventh embodiment of the present invention, wherein (a) shows a state before the torque receiving plate is attached, and (b) shows a torque receiving plate. Shown after installation.

  The disc brake friction pad assembly (hereinafter simply referred to as “friction pad assembly”) 600 of the seventh embodiment is mounted in a compressed state between the back surface of the lining assembly 13 and the torque receiving plate 3. The configuration is the same as that of the friction pad assembly 100 of each of the above embodiments, except that a plurality of (two in this embodiment) disc springs (springs) 24a and 24b having different spring constants are used for the spring member 24. .

As shown in FIG. 22 (a), the disc springs 24a and 24b are housed in the spring housing groove 22d at one end side (outer diameter side) and attached to the other end side (inner diameter side) before the torque receiving plate 3 is attached. ) Protrudes from the spring accommodating groove 22d.
After the torque receiving plate 3 is attached, as shown in FIG. 22B, the disc springs 24a and 24b are brought into a compressed state with the other end abutting against the torque receiving plate 3.

  In the case of the friction pad assembly 600 of the present embodiment, the spring member 24 is configured by combining disc springs 24a and 24b having different spring constants, so that the spring member 24 is configured by a single disc spring. Thus, the load when the lining assembly 13 is urged toward the guide plate 11 can be stabilized.

Note that the disc brake friction pad assembly of the present invention is not limited to the above-described embodiments, and appropriate modifications and improvements can be made.
For example, when one disc brake friction pad assembly is composed of a plurality of unit friction pad assemblies, the number of unit friction pad assemblies to be configured may be three or more.

DESCRIPTION OF SYMBOLS 3 Torque receiving plate 11 Guide plate 11a Guide hole 13 Lining assembly 21 Friction material 22 Back plate part 22a Plate fitting part 22b Retaining flange part 22c Curved convex part 22d Spring accommodating groove 24 Spring member 28 Rivet 31 Anchor plate 32 Rivet 100 Friction pad assembly 110, 120 Unit Friction pad assembly

Claims (9)

A disc brake friction pad assembly in which a plurality of lining assemblies are pivotally supported by a guide plate that receives a braking torque, and the lining assembly is pressed against a disc rotor,
The lining assembly has a back plate portion fixed to the back surface of the friction material,
In the back plate portion, a plate fitting portion whose outer peripheral surface is turnably fitted to a guide hole portion provided in the guide plate, a retaining flange portion having an outer diameter larger than the guide hole portion, A curved convex portion is formed integrally with the back plate portion so as to be raised at the center of the retaining flange portion toward the torque receiving plate side fixed to the guide plate with a gap between the back plate portion,
The lining assembly is inserted and mounted in the guide hole portion from the back surface side of the guide plate, and is mounted between the back surface of the back plate portion facing the torque receiving plate and the torque receiving plate. Supported by the member biased toward the guide plate,
When a pressing load acting on the friction material pressed by the disk rotor exceeds a set load, the lining assembly is bent by the spring member and the curved convex portion comes into contact with the torque receiving plate. The disc is characterized in that the lining assembly is allowed to tilt by a convex portion, and a braking torque acting by contact between the disc rotor and the friction material is transmitted from the plate fitting portion to the guide plate for braking. Brake friction pad assembly.   The disc brake friction pad assembly according to claim 1, wherein the plate fitting portion is formed of a flat plate material having a predetermined plate thickness.   3. The disc brake friction pad assembly according to claim 1, wherein the plate fitting portion is formed in a curved surface shape convex toward the guide hole portion side. 4.   4. The disc brake friction pad assembly according to claim 1, wherein the back plate portion is formed with a spring accommodating groove that accommodates one end of the spring member. 5.   The friction pad assembly for a disk brake according to any one of claims 1 to 4, wherein the torque receiving plate seals a back side of the back plate portion.   The anti-rotation mechanism for preventing the outer peripheral surface of the back plate portion from rotating relative to the guide hole portion is provided between the back plate portion and the guide plate. 6. A friction pad assembly for a disc brake according to any one of 1 to 5.   The anti-rotation mechanism includes a fitting protrusion protruding from one of an outer peripheral surface of the back plate portion and an inner peripheral surface of the guide hole portion, an inner surface of the outer surface of the back plate portion and the guide hole portion. The disc brake friction pad assembly according to claim 6, further comprising: a fitting recess that is recessed in any one of the peripheral surfaces and fits into the fitting protrusion.   The anti-rotation mechanism is configured such that an engaging convex portion protrudes from the outer peripheral surface of the retaining flange portion, and the engaging convex portions in a pair of adjacent lining assemblies are engaged with each other. 7. The friction pad assembly for a disc brake according to claim 6, which prevents rotation.   The disc brake friction pad assembly according to any one of claims 1 to 8, wherein the spring member is a combination of a plurality of springs having different spring constants.

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