JP2014095417A - Friction pad assembly for disc brake - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a friction pad assembly for a disc brake improved in a degree of freedom in revolution of lining assemblies, and suppressing uneven wear.SOLUTION: A plurality of lining assemblies 27 disposed on a guide plate 25 are respectively provided with: a plate fitting portion 47 revolvably fitted to a guide hole portion 43 formed on the guide plate 25 at its outer peripheral face; and a retaining flange portion 49 having an outer diameter larger than the guide hole portion 43, on a back plate portion 33 fixed to a back surface of a friction material 45. Disc springs 51 supporting the lining assemblies 27 in a state of biasing them to a guide plate side, are held between a first link plate 21 or a second link plate 23, and the back plate portion 33, and are engaged with back plate contact curved face portions 57.

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. It relates to an assembly.

  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, the disk rotor and the friction pad assembly for the disk brake are large, so if the lining member to be pressed against the disk rotor is formed as an integral part, the undulation generated in the disk rotor due to frictional heat, etc. For this reason, the non-contact area increases, a stable friction area cannot be maintained, and stable braking characteristics cannot be obtained.
Further, if the lining member rotates carelessly due to contact with the disk rotor, this causes loss of transmission of braking torque or brake noise. Therefore, a means for regulating the rotation of the lining member is required, and an increase in the number of parts causes an increase in cost. At the same time, an increase in the number of assembly steps accompanying the increase in the number of parts causes a decrease in productivity.

  Therefore, in order to solve such a problem, the lining assembly that is supported by the guide plate so as to be pivotable (swingable) and pressed against the disk rotor is attached to the back plate portion fixed to the back surface of the friction material. A plate fitting portion whose outer peripheral surface is pivotably fitted into a guide hole portion of the guide plate and a retaining flange portion having an outer diameter larger than that of the guide hole portion, and acts when the disc rotor and the friction material are in contact with each other. A braking torque is transmitted from the plate fitting portion to the guide plate, and a plurality of lining assemblies are provided between the torque receiving plate and the back plate portion fixed to the guide plate with a gap between the back plate portion and the back plate portion. There is provided a friction pad assembly for a disc brake having a configuration in which a plurality of link plates are provided so as to apply a pressing force from a torque receiving plate to these lining assemblies. Are plan (e.g., see Patent Document 1).

In the friction pad assembly for a disc brake having such a configuration, the link plate is in contact with the link support portion of the torque receiving plate and is supported so as to be pivotable. A plurality of back plate abutting curved surface portions that pivotably support the lining assembly by abutting against the link contact portion at the center of the back plate portion, and formed at positions away from the center of the back plate portion of each lining assembly. A rotation restricting portion that loosely fits into the formed engagement hole and restricts the turning behavior of each lining assembly.
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 plate contact curved surface portion and the back plate contact that apply the pressing force to the lining assembly are set. A braking torque that is a large load does not act on each contact portion between the contact surface portion and the torque receiving plate. 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.

  Further, since the rotation restricting portion for restricting the turning behavior of each lining assembly is performed by fitting the engagement hole formed in the back plate portion with the rotation restricting portion protruding from the link plate, It is possible to avoid the occurrence of inconveniences such as an increase in cost due to the increase and a decrease in productivity due to an increase in the number of assembly processes.

JP 2008-133948 A

By the way, in the friction pad assembly for disc brakes described in Patent Document 1 and the like, the guide plate is configured such that the leaf spring fitted to the plate fitting portion is sandwiched between the guide plate and the retaining flange portion. Is inserted into and mounted on the guide hole from the back surface side, and a braking torque acting upon contact between the disk rotor and the friction material is transmitted from the plate fitting portion to the guide plate. Since the leaf spring absorbs the dimensional tolerance in the thickness direction of the lining assembly, variation in the contact property of each lining assembly with respect to the disk rotor is prevented.
However, the leaf spring is set to have an outer diameter larger than that of the guide hole portion, is fitted on the outer periphery of the plate fitting portion, and is sandwiched between the guide plate and the retaining flange portion. For this reason, the lining assembly in which the plate spring is fitted to the plate fitting portion has a low degree of freedom in turning, and there is a possibility that uneven wear may occur on the lining surface due to a high temperature state during braking or the like.

  The present invention has been made in view of the above situation, and an object of the present invention is to provide a disc brake friction pad assembly in which the degree of freedom of turning of the lining assembly is increased and uneven wear is suppressed.

The above object of the present invention is achieved by the following configuration.
(1) Provided on the outer peripheral surface of a plurality of lining assemblies that are pivotally supported by a guide plate that receives braking torque and pressed against the disc rotor, and a back plate portion fixed to the back surface of the friction material of the lining assembly. A plate fitting portion that is pivotably fitted in a guide hole portion provided in the guide plate, a retaining flange portion that is provided in the lining assembly and has a larger outer diameter than the guide hole portion, and the back plate A torque receiving plate fixed to the guide plate with a gap between the torque receiving plate and the torque receiving plate and the back plate, and the torque receiving plate disposed across a plurality of lining assemblies. A link plate for applying a pressing force from the receiving plate to the lining assembly; and a link support for the torque receiving plate provided on the link plate. A single plate abutting curved surface portion that abuts on the holding portion and rotatably supports the link plate, and is provided on the link plate, and is provided on the link abutting portion at the center of the back plate portion of the lining assembly. A plurality of back plate abutting curved surface portions that abut and support the lining assembly so as to be pivotable, and are provided on the link plate, and are formed at positions away from the center of the back plate portion of each of the lining assemblies. A rotation restricting portion that loosely fits in the engaging hole and restricts the turning behavior of each lining assembly, and is sandwiched between the link plate and the back plate portion, and the lining assembly is attached to the guide plate side. A disc brake friction pad assembly comprising: a spring member that supports the biased state.

According to the disc brake friction pad assembly configured as described in (1) above, the single plate contact curved surface provided on the link plate contacts the link support portion of the torque receiving plate so that the link plate receives the torque receiving plate. It is pivotally supported with respect to the plate. Further, the back plate abutting curved surface portion provided on the link plate abuts on the link abutting portion of the back plate portion of each lining assembly, and the lining assembly is supported so as to be rotatable with respect to the link plate.
Therefore, the lining assembly during non-braking is supported in a state of being biased toward the guide plate by a spring member that is mounted in a compressed state between the back plate portion facing the link plate and the front surface of the link plate. The In the compressed state sandwiched between the link plate and the back plate, the spring member holds the lining assembly in the guide plate so that the retaining flange is kept in contact with the peripheral edge of the guide hole. Energize to the side.
At the start of braking, the pressing force that presses the lining assembly against the disk rotor acts on the lining assembly from the torque receiving plate via the link plate and the spring member. When the reaction force from the disk rotor increases, the spring member and the plate flexible portion of the link plate are elastically deformed, and the pressing force that presses the lining assembly is applied to the lining assembly from the torque receiving plate only through the link plate. Works. At this time, the retaining flange portion is separated from the peripheral edge portion of the guide hole portion, and the lining assembly is pivotally supported with respect to the link plate by the back plate abutting curved surface portion, so that the position adjustment is possible. Accordingly, the lining assembly having a high degree of freedom of rotation follows the undulation of the surface of the disk rotor and contacts the surface of the disk rotor in each individual rotation operation, so that a stable friction area is maintained and stable braking characteristics are maintained. Can be maintained.
The link plate for adjusting the position of the lining assembly is arranged to compress the spring member so as to contact the lining assembly. That is, the set load of the spring member is received by the guide plate and the link plate. When braking is released, the lining assembly whose position has been adjusted at the time of braking becomes a position where the retaining flange portion is in contact with the peripheral edge portion of the guide hole due to the set load of the spring member (that is, the reset position). Therefore, even when uneven wear occurs on the lining surface due to a high temperature state during braking, when the braking is released, the lining assembly moves from the position where the uneven wear occurs to the flange portion to the periphery of the guide hole. It is returned to the reset position where it abuts the part. Thereby, at the time of the next braking, the lining assembly starts to contact the disk rotor surface from the convex portion of the lining surface, so that the growth of uneven wear is suppressed.

(2) The disc brake friction pad assembly according to (1) above, wherein the spring member is a disc spring, and the disc spring has an inner diameter abutting against the link plate and an outer diameter portion of the disc spring. A friction pad assembly for a disc brake, which abuts against a back plate portion.

  According to the disc brake friction pad assembly having the configuration (2), the inner diameter portion of the disc spring contacts the link plate and the outer diameter portion contacts the back plate portion of the lining assembly. When the lining surface follows the deformation of the disk rotor surface due to, for example, an inclination of the lining assembly, the restraining force against the inclination of the lining assembly by the disc spring having a high spring constant increases. Thereby, induction of vibration is suppressed and occurrence of brake squeal is reduced.

  According to the friction pad assembly for a disc brake according to the present invention, the degree of freedom of turning of the lining assembly can be increased and uneven wear can be suppressed.

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

It is a front view of the friction pad assembly for disk brakes concerning one embodiment of the present invention. FIG. 2 is a rear view of the disc brake friction pad assembly shown in FIG. 1. It is the perspective view which looked at the 1st friction pad assembly shown in Drawing 1 from the back side. It is a front view of the 1st friction pad assembly shown in FIG. FIG. 4 is a rear view of the first friction pad assembly shown in FIG. 3 with a torque receiving plate removed. It is an AA arrow line view of FIG. It is a BB arrow line view of FIG. 7A is an enlarged view of a main part of FIG. 7 during non-braking, FIG. 7B is an enlarged view of a main part of FIG. 7 during braking, and FIG.

Embodiments according to the present invention will be described below with reference to the drawings.
A disc brake friction pad assembly 11 according to an embodiment of the present invention is used in a rail brake disc brake device, and is shown in FIGS. 1 and 2 in a circumferential direction of a disc rotor (not shown) on an axle. As shown, the first friction pad assembly 13 and the second friction pad assembly 15 are arranged adjacent to each other.
The first friction pad assembly 13 and the second friction pad assembly 15 have the same configuration, and are arranged in opposition to the disk rotor on the axle and are built in the brake caliper fixed to the vehicle body frame. As a result, the disk rotor is moved forward and backward toward the disk rotor surface.

  As shown in FIGS. 4 to 7, the first friction pad assembly 13 and the second friction pad assembly 15 are a torque receiving plate that is driven forward and backward toward the disk rotor by an actuator built in a brake caliper (not shown). 17, the first link plate 21 and the second link plate 23, which are two types of link plates laid on a substantially flat surface on the surface of the torque receiving plate 17 on the disk rotor side, and the disk of the torque receiving plate 17 On the rotor side, it is composed of a guide plate 25 connected and fixed to the torque receiving plate 17 and five lining assemblies 27 fitted and supported on the guide plate 25 so as to be able to turn.

  As shown in FIG. 3, an anchor plate 29 is fixedly mounted on the back surface of the torque receiving plate 17 by a rivet 32. The anchor plate 29 is connected to an actuator built in the brake caliper, so that the first friction pad assembly 13 and the second friction pad assembly 15 can be driven back and forth to the disk rotor.

  Since the torque receiving plate 17 is provided with a gap 35 between the torque receiving plate 17 and the back plate portion 33 of the lining assembly 27 shown in FIG. It is molded into a thin dish for sealing. The torque receiving plate 17 is fixed to the outer peripheral portion of the guide plate 25 by the rivets 31 with a gap 35 between the torque receiving plate 17 and the back plate portion 33 of the lining assembly 27.

As shown in FIG. 5, the first link plate 21 and the second link plate 23 are provided across a plurality of lining assemblies 27, and the pressing force from the torque receiving plate 17 acts on these lining assemblies 27. Let
Links on the first link plate 21 and the second link plate 23 side of the torque receiving plate 17 are smooth surfaces for rotatably supporting the first link plate 21 and the second link plate 23, respectively. The support portion 39 is formed so as to correspond to the approximate center of gravity of each of the first link plate 21 and the second link plate 23.
On the other hand, at a substantially center of gravity position of the first link plate 21 and the second link plate 23, a single plate abutting curved surface portion that is pivotably supported by abutting on a link support portion 39 formed on the torque receiving plate 17 is provided. 41 is formed. In the case of this embodiment, the plate abutting curved surface portion 41 is formed in a convex curved surface that abuts on the link support portion 39 so as to be rotatable.
In the case of the present embodiment, the first link plate 21 and the second link plate 23 are supported so that the plate contact curved surface portion 41 at a substantially center of gravity is in contact with the torque receiving plate 17 so as to be rotatable. Except for the abutting curved surface portion 41, a clearance allowing the turning is formed between the torque receiving plate side surfaces of the first link plate 21 and the second link plate 23 and the torque receiving plate 17.

  The guide plate 25 has five guide hole portions 43 formed at predetermined intervals, and the lining assembly 27 is attached to each guide hole portion 43.

  The lining assembly 27 includes a friction material 45 molded in a substantially disk shape and a back plate portion 33 fixed to the back surface of the friction material 45. As shown in FIGS. 6 and 7, the back plate portion 33 has a plate fitting portion 47 that is pivotably fitted into a circular guide hole portion 43 whose outer peripheral surface is formed through the guide plate 25, and a guide hole. A retaining flange portion 49 having an outer diameter larger than that of the portion 43 is provided. The lining assembly 27 transmits a braking torque that is applied when the disk rotor and the friction material 45 are in contact from the plate fitting portion 47 to the guide plate 25.

  Here, between the 1st link plate 21 and the 2nd link plate 23, and the backplate part 33 of each lining assembly 27, the spring member which supports the lining assembly 27 in the state urged | biased by the guide plate side Is sandwiched.

The spring member in the present embodiment includes a disc spring 51 shown in FIG. The disc spring 51 has an inner diameter portion 53 in contact with the first link plate 21 or the second link plate 23 and an outer diameter portion 55 in contact with the back plate portion 33 so that the first link plate 21 or the second link plate 23 is in contact. And the back plate portion 33. The position of the disc spring 51 is regulated by the inner diameter portion 53 engaging with the back plate contact curved surface portion 57 of the first link plate 21 or the second link plate 23. The disc spring 51 desirably has a spring constant of about 0.3 to 0.8 N / mm / mm ² .

The back plate portion 33 of each lining assembly 27 is formed with a concave curved link contact portion 59 at the center, and an anti-rotation engagement hole 61 shown in FIG. 5 at a position away from the center. Has been.
Correspondingly, the first link plate 21 and the second link plate 23 are provided with rotation restricting portions 63 that loosely fit into the engagement holes 61 and restrict the rotational behavior of the respective lining assemblies 27. .

  In the case of the present embodiment, the back plate contact curved surface portion 57 is formed as a convex curved surface with which the link contact portion 59 is rotatably contacted. The rotation restricting portion 63 is formed by bending the protruding pieces extending to the end portions of the first link plate 21 and the second link plate 23 toward the engagement hole.

Next, the assembly procedure of the first friction pad assembly 13 and the second friction pad assembly 15 will be described by taking the first friction pad assembly 13 as an example.
First, as shown in FIG. 5, the friction material 45 projects to the front side of the guide plate 25 (lower side in FIG. 6) in the guide hole portion 43 of the guide plate 25 set with the back side facing upward. The lining assembly 27 is inserted and mounted. The lining assembly 27 inserted and mounted in the guide hole portion 43 is in a state in which the retaining flange portion 49 is in contact with the peripheral edge portion of the guide hole portion 43.

  Next, the disc spring 51 is placed on the back plate portion 33 of each lining assembly 27. Further, the back plate contact curved surface portion 57 is engaged with the inner diameter portion 53 of the disc spring 51 so as to face the center of the back surface of the back plate portion 33. At the same time, the rotation restricting portions 63 of the first link plate 21 and the second link plate 23 engage with the engagement holes 61 for preventing rotation, and the first link plate 21 and the second link plate 23 are placed on the disc spring 51. Placed.

  The torque receiving plate 17 is fixed to the outer peripheral portion of the guide plate 25 by the rivet 31 in a state where the disc spring 51 and the first link plate 21 and the second link plate 23 are mounted on the back side of the lining assembly 27. Further, the vicinity of the central portion of the torque receiving plate 17 and the guide plate 25 is sandwiched and fixed by a rivet 34 that penetrates the guide plate 25 and the torque receiving plate 17. As shown in FIG. 6, a part of the outer periphery of the torque receiving plate 17 and the guide plate 25 is sandwiched and fixed by a rivet 36 that penetrates the anchor plate 29 together with the guide plate 25 and the torque receiving plate 17. Note that a spacer member 38 is interposed between the guide plate 25 and the torque receiving plate 17 sandwiched and fixed by the rivets 34 and 36 to maintain a distance between the two members.

Next, the operation of the disc brake friction pad assembly 11 having the above-described configuration will be described.
In the disc brake friction pad assembly 11 according to the present embodiment, the position of each lining assembly 27 on the torque receiving plate 17 is regulated in the direction parallel to the disc rotor surface of the lining assembly 27. This is performed by fitting the plate fitting portion 47 of the assembly 27 with the guide hole portion 43 of the guide plate 25, and in the direction perpendicular to the disk rotor surface, the link contact portion 59 of the lining assembly 27 and the This is performed by contacting the back link contact curved surface portion 57 of the first link plate 21 and the second link plate 23.
Therefore, the braking torque acting on the lining assembly 27 during braking is transmitted to the guide plate 25 and directly to the torque receiving plate 17 to which the guide plate 25 is fixed.
The pressing force that presses the lining assembly 27 against the disk rotor is from the torque receiving plate 17 to the link support portion 39 of the torque receiving plate 17 and the plate contact curved surface portion 41 of the first link plate 21 and the second link plate 23. Is transmitted to the first link plate 21 and the second link plate 23 through the contact portion, and the back plate contact curved surface portion 57 of the first link plate 21 and the second link plate 23 and the link contact of the lining assembly 27. It acts on the lining assembly 27 through a contact portion with the portion 59.

That is, a member (guide plate 25) that receives braking torque from the lining assembly 27 and a member (first link plate 21, second link plate 23, and torque receiving plate 17) that apply a pressing force to the lining assembly 27 are provided. It is set separately. Therefore, the contact portion between the lining assembly 27 that applies a pressing force to the lining assembly 27 and the first link plate 21 and the second link plate 23, the first link plate 21, the second link plate 23, and the torque receiving plate 17. The braking torque that is a large load does not act on the contact portion.
Therefore, it is not necessary for each contact portion that transmits the pressing force 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. .

Further, in the disc brake friction pad assembly 11 described above, when the reaction force of the pressing force when the friction material 45 is pressed against the disc rotor is in the normal range, the lining assembly 27 starts to It is transmitted via the back plate contact curved surface portion 57 and the plate contact curved surface portion 41 of the first link plate 21 and the second link plate 23 and is received by the torque receiving plate 17. However, when an excessive reaction force is input from the disk rotor, a gap that allows the first link plate 21 and the second link plate 23 that are manufactured by press working to pivot with the torque receiving plate 17 is provided. It is deformed so as to be buried, and strongly contacts the torque receiving plate 17.
Therefore, the first link plate 21 and the second link plate 23 bring the excessive reaction force into the torque receiving plate 17 by bringing the vicinity of the back plate contact curved surface portion 57 and the plate contact curved surface portion 41 into contact with the torque receiving plate 17. At the same time as it is transmitted to the plate 17, damage is prevented.

Further, in the disc brake friction pad assembly 11 described above, the outer diameter of the retaining flange portion 49 formed on the back plate portion 33 of the lining assembly 27 is set larger than that of the guide hole portion 43 of the guide plate 25. Thus, the lining assembly 27 is prevented from falling off from the guide plate 25 due to the catch of the retaining flange portion 49, and high safety can be obtained.
In addition, in order to prevent the lining assembly 27 from falling off from the guide plate 25, an independent dedicated part is not added. Therefore, there is an inconvenience of 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.

  Further, in the disc brake friction pad assembly 11 described above, in order to increase the transmission efficiency of the braking torque when the lining assembly 27 comes into contact with the disc rotor, the lining assembly in a plane parallel to the disc rotor surface is used. The rotation restriction of the three-dimensional body 27 is performed by fitting the engagement hole 61 formed in the back plate portion 33 of the lining assembly 27 with the rotation restriction portion 63 projecting from the first link plate 21 and the second link plate 23. Has been done. That is, since no independent dedicated part is added to the rotation regulation of the lining assembly 27 in a plane parallel to the disk rotor surface, the number of parts does not increase due to the rotation regulation of the lining assembly 27. 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.

Further, the disc brake friction pad assembly 11 described above has a configuration in which a plurality of lining assemblies 27 are laid out in a plane, but the back plate portion 33 and the guide plate 25 of each lining assembly 27 are arranged. Since the disc springs 51 arranged so as to be sandwiched between them absorb the dimensional tolerance in the thickness direction of the lining assembly 27, it is possible to prevent variation in the contact property of the lining assembly 27 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 27.

  In the disc brake friction pad assembly 11 according to the present embodiment, the guide plate 25 and the torque receiving plate 17 are fastened by rivets 31, 34, and 36 to form an integral housing structure, so that they are loosened by vibration or the like. It is possible to obtain a robust housing structure that does not cause low cost.

In addition to the above basic operation, the disc brake friction pad assembly 11 according to the present embodiment further includes the following operations by including the disc spring 51.
That is, in the disc brake friction pad assembly 11 of the present embodiment, as described above, the single plate contact curved surface portion 41 provided on each of the first link plate 21 and the second link plate 23 is the torque receiving plate. The first link plate 21 and the second link plate 23 are pivotally supported by the torque receiving plate 17 in contact with the 17 link support portions 39. Further, the back plate abutting curved surface portion 57 provided on the first link plate 21 and the second link plate 23 abuts on the link abutting portion 59 of the back plate portion 33 of each lining assembly 27, and the lining assembly. 27 is supported so as to be rotatable with respect to the first link plate 21 or the second link plate 23.

  Therefore, at the time of non-braking shown in FIG. 8A, the lining assembly 27 includes the back plate portion 33 facing the first link plate 21 or the second link plate 23 and the first link plate 21 or the second link plate 23. Is supported in a state of being biased toward the guide plate 25 by a disc spring 51 mounted in a compressed state. The disc spring 51 is in a state where the retaining flange portion 49 is in contact with the peripheral edge portion of the guide hole portion 43 in a compressed state sandwiched between the first link plate 21 or the second link plate 23 and the back plate portion 33. The lining assembly 27 is urged toward the guide plate 25 so as to be maintained.

When the braking shown in FIG. 8B is started, the pressing force that presses the lining assembly 27 against the disk rotor is transmitted from the torque receiving plate 17 via the first link plate 21, the second link plate 23, and the disc spring 51. Acting on the lining assembly 27.
As shown in FIG. 8C, when the reaction force from the disk rotor increases, the disc spring 51 and the plate flexible portions 65 of the first link plate 21 and the second link plate 23 are elastically deformed, and the lining assembly The pressing force that presses the solid 27 acts on the lining assembly 27 from the torque receiving plate 17 only through the first link plate 21 and the second link plate 23. At this time, the retaining flange portion 49 is separated from the peripheral edge portion of the guide hole portion 43, and the lining assembly 27 can be rotated with respect to the first link plate 21 or the second link plate 23 by the back plate contact curved surface portion 57. It is supported and position adjustment becomes possible.

  Accordingly, since the lining assembly 27 having a high degree of freedom of rotation follows the undulation of the surface of the disk rotor and contacts the surface of the disk rotor in each individual swing operation, a stable friction area is maintained and stable braking characteristics are maintained. Can be maintained.

  The first link plate 21 and the second link plate 23 that adjust the position of the lining assembly 27 are disposed so as to contact the lining assembly 27 by compressing the disc spring 51. That is, the set load of the disc spring 51 is received by the guide plate 25, the first link plate 21, and the second link plate 23. When the braking is released, the lining assembly 27 whose position is adjusted at the time of braking is a position where the retaining flange portion 49 is again in contact with the peripheral edge portion of the guide hole portion 43 by the set load of the disc spring 51 (that is, the reset position). ) Therefore, even when uneven wear occurs on the lining surface due to a high temperature state or the like during braking, when braking is released, the lining assembly 27 causes the retaining flange portion 49 to guide from the posture where uneven wear occurs. It is returned to the reset position where it comes into contact with the peripheral edge of the hole 43. As a result, at the time of the next braking, the lining assembly 27 starts to contact the disk rotor surface from the convex portion of the lining surface, thereby suppressing the growth of uneven wear.

  Further, in the disc brake friction pad assembly 11 of the present embodiment, the inner diameter portion 53 of the disc spring 51 contacts the first link plate 21 or the second link plate 23, and the outer diameter portion 55 is the back plate of the lining assembly 27. Since the lining surface follows the deformation of the disk rotor surface due to heat or the like during braking, if the lining assembly 27 tends to tilt, the lining assembly 27 by the disc spring 51 having a high spring constant is brought into contact with the portion 33. The restraining force against the inclination of increases. Thereby, induction of vibration is suppressed and occurrence of brake squeal is reduced.

  Therefore, according to the disc brake friction pad assembly 11 according to the present embodiment, the degree of freedom of turning of the lining assembly 27 can be increased and uneven wear can be suppressed.

Note that the disc brake friction pad assembly of the present invention is not limited to the above-described embodiment, and can be appropriately modified and improved.
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 one, or three or more. Further, the number of link plates is not limited to two in the above embodiment, but may be one or three or more.

11 ... Disc brake friction pad assembly 17 ... Torque receiving plate 21 ... First link plate (link plate)
23 ... Second link plate (link plate)
25 ... Guide plate 27 ... Lining assembly 33 ... Back plate part 39 ... Link support part 41 ... Plate contact curved surface part 43 ... Guide hole part 45 ... Friction material 47 ... Plate fitting part 49 ... Retaining flange part 51 ... Dish Spring (spring member)
53 ... Inner diameter part 55 ... Outer diameter part 57 ... Back plate contact curved surface part 59 ... Link contact part 61 ... Engagement hole 63 ... Rotation restricting part

Claims (2)

A plurality of lining assemblies that are pivotally supported by a guide plate that receives braking torque and pressed against a disk rotor;
A plate fitting portion that is provided on the outer peripheral surface of the back plate portion fixed to the back surface of the friction material of the lining assembly, and that is pivotably fitted to a guide hole portion provided in the guide plate;
A retaining flange portion provided on the lining assembly and having an outer diameter larger than that of the guide hole portion,
A torque receiving plate secured to the guide plate with a gap between the back plate portion and
A link plate that is provided between the torque receiving plate and the back plate portion, and is provided across a plurality of lining assemblies to apply a pressing force from the torque receiving plate to the lining assembly;
A single plate abutting curved surface provided on the link plate and abutting on a link support portion of the torque receiving plate to rotatably support the link plate;
A plurality of back plate abutting curved surface portions provided on the link plate and abutting against a link abutting portion at the center of the back plate portion of each of the lining assemblies to rotatably support the lining assembly;
A rotation restricting portion that is provided on the link plate and loosely fits in an engagement hole formed at a position away from the center of the back plate portion of each of the lining assemblies to restrict the turning behavior of each of the lining assemblies; ,
A spring member sandwiched between the link plate and the back plate portion and supporting the lining assembly in a state of being biased toward the guide plate;
A friction pad assembly for a disc brake, comprising: The disc brake friction pad assembly according to claim 1,
The spring member comprises a disc spring;
The disc brake friction pad assembly, wherein the disc spring has an inner diameter portion in contact with the link plate and an outer diameter portion in contact with the back plate portion.

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