CN100394062C - brake disc friction block - Google Patents

Abstract

A brake disc friction pad that maintains elasticity with an elastic member close to the brake lining even when the brake lining heats up. The brake disc friction block includes: an elastic member (40), which is arranged between the base plate (12) and the brake lining (14), and the brake lining (14) can be obliquely displaced by pressing against the brake disc At the same time, the brake lining (14) can be moved towards the direction close to the base plate (12); the heat conduction member (44) is suppressed, and it is arranged between the elastic member (40) and the brake lining (14). The main body portion (34) of the rivet (30) has an abutment portion (34a) abutting against the base plate (12) and is arranged between the abutment portion (34a) and the head portion (32) and has a diameter smaller than the abutment portion ( 34a) in the middle portion (34b). The gap width (S1) between the contact portion (34a) of the rivet (30) and the cylindrical portion (26) is formed to be smaller than that between the head portion (32) of the rivet (30) and the brake lining (14). Gap width (S2).

Description

brake disc friction block

technical field

The invention relates to a brake disc friction block used in a disc brake of a high-speed railway vehicle.

Background technique

Conventionally, as a brake disc friction pad used in a disc brake of a railway vehicle, as disclosed in the following Patent Document 1, there is generally known a brake pad that is pressed onto a brake disc and a brake pad that supports the brake pad. structure of the substrate. As described in this document 1, as shown in FIG. The elastic member 84 is sandwiched between the brake lining 81 and the base plate 82 . When the brake lining 81 is pressed against the brake disc 85 during the braking operation, the brake lining 81 is displaced relative to the base plate 82 .

Patent Document 1: Specification of German Patent No. DE4301006C2

Since the temperature of the brake lining 81 reaches about 800° C. during braking operation in a high-speed railway vehicle, if the elastic member 84 in contact with the brake lining 81 is made of iron or steel, the temperature rises to a temperature close to the quenching temperature. Therefore, in the above-mentioned conventional device, there is a problem that the elastic member 84 is annealed and deformed due to the temperature rise of the brake lining 81, and the elastic member 84 cannot exert elasticity.

Contents of the invention

The present invention was developed in view of the above problems, and an object of the present invention is to maintain elasticity of an elastic member adjacent to the brake lining even when the temperature of the brake lining rises.

In order to achieve the above object, the brake disc friction block of the present invention is based on the premise that the brake disc friction block is assembled with the brake lining on the base plate, and has: an elastic member arranged on the base plate and the brake lining. Between, by pressing against the brake disc, the brake lining can be tilted and displaced, and at the same time, the brake lining can be moved in a direction close to the base plate; the heat conduction member is suppressed, and it is arranged on the elastic member and between the brake linings.

With this configuration, even if the brake lining heats up due to friction with the brake disc during braking operation, it is possible to suppress transmission of the heat to the elastic member. As a result, since it is possible to make it difficult for the elastic member to rise in temperature, it is possible to easily suppress the temperature rise of the elastic member to a temperature at which it loses its elasticity. Moreover, since the brake lining can be obliquely displaced or moved along the brake disc through the elastic member, the local surface pressure rise of the brake lining can be reduced, and the service life of the brake lining can be improved.

Here, the heat conduction suppressing member may be provided with a contact portion pressed against the brake pad by an elastic member, and an extension portion separated from the brake pad and extending from the contact portion.

In this structure, even if the heat is directly transferred from the brake lining to the extension portion, the heat transfer is weak, and the heat transfer is mainly performed by the contact portion. This suppresses the contact portion of the heat conduction member from dissipating heat directly received from the brake lining to the extension portion, thereby suppressing a temperature rise in the contact portion of the heat conduction member. As a result, the temperature rise of the elastic member in contact with the contact portion can be suppressed more effectively.

In addition, a plurality of the brake linings and elastic members may be respectively provided, and the heat conduction suppressing member may be provided across the respective brake linings.

This configuration can reduce the man-hours for mounting the heat transfer member.

In addition, a through hole having a stepped portion is provided in the brake lining, and a holding member having a head capable of engaging with the stepped portion is provided. In this case, the brake lining may be The structure is configured such that the stepped portion of the through hole abuts against the head of the holding member while being pressed in a direction away from the substrate by the elastic force of the elastic member, thereby retaining the object at the position of the retaining member. state.

In this structure, since the brake lining is pressed by the elastic member, on the other hand, the step portion of the through hole formed on the brake lining is engaged with the head of the holding member to prevent the brake lining from coming off. Displacement of the brake lining is allowed by the elastic member, and the brake lining is not detached from the base plate by the elastic force of the elastic member, so that the base plate and the brake lining can be reliably bonded.

In addition, a concave curved seat is formed on the base plate to surround the portion where the holding member is fixed, and a convex front end surface facing the curved seat surface is provided on the brake lining. The cylindrical portion, the brake lining may be formed to have a gap between the cylindrical portion and the curved seat and be held by the holding member.

In this structure, when the brake lining is pressed against the brake disc during braking operation and an external force greater than or equal to a predetermined value acts on the elastic member, the cylindrical portion of the brake lining comes into contact with the curved seat of the base plate. . At this time, since the front end surface of the brake lining can move along the curved surface seat, when the cylindrical portion of the brake lining abuts against the curved surface seat of the base plate, the brake lining can be tilted and displaced according to the force received. . In addition, since the external force acting on the brake lining during the braking operation is shared not only by the elastic member, but also by the curved seat of the substrate, the burden on the elastic member can be reduced.

In addition, the holding member has a main body portion having a diameter smaller than that of the head portion, and the main body portion has an abutment portion abutting against the substrate, and is disposed between the abutment portion and the head portion. And when the diameter is smaller than the middle portion of the abutting portion, the width of the gap between the abutting portion of the holding member and the cylindrical portion may be smaller than that between the head of the holding member and the stopper. The width of the gap between the linings.

In this configuration, when the brake lining is displaced obliquely, the contact portion of the holding member comes into contact with the cylindrical portion of the brake lining. During this contact, shear stress and bending stress act on the contact portion, but by providing the contact portion close to the substrate, the influence of the bending stress can be reduced.

In addition, a rotation stop device may be provided which prevents rotation of the brake lining when pressed against the brake disc.

In this structure, it is possible to avoid abrasion of the brake lining and the heat-conducting member as the brake lining rotates.

As described above, according to the present invention, since the heat conduction suppressing member is disposed between the elastic member and the brake lining, even if the temperature of the brake lining rises, the elastic member disposed close to the vibrating lining can maintain elasticity.

Description of drawings

Fig. 1 is the front view of the brake disc friction block of the embodiment of the present invention;

Fig. 2 is the sectional view of II-II line of Fig. 1;

Fig. 3 is a perspective view showing an elastic member;

Fig. 4 is a diagram corresponding to Fig. 2 showing a brake disc shoe in another embodiment;

Fig. 5 is a cross-sectional view showing a conventional brake disc pad.

Explanation of reference signs

12 Substrates

14 brake lining

18 curved seat

22 through holes

22a step part

26 cylindrical part

26a front face

30 rivets (an example of holding parts)

32 heads

34 main body

34a contact part

34b middle part

40 elastic parts

44 Suppression of heat-conducting components

44a contact part

44b extension

48 anti-rotation device

Detailed ways

The best mode for carrying out the present invention will be described in detail below with reference to the drawings.

FIG. 1 shows a brake disc pad 10 according to an embodiment of the present invention. The brake disc friction pad 10 is used in a disc brake of a high-speed railway vehicle, and a plurality of disc brake pads 10 are arranged along the rotation direction of the disc brake (not shown). As shown in FIG. 1 , the brake disc friction block 10 has a base plate 12 and a brake lining 14 installed on the base plate 12 .

The substrate 12 is configured as a flat plate having an elongated shape extending in a predetermined direction when viewed in plan, and both ends in the longitudinal direction form approximately triangular shapes. The base plate 12 is provided in such a manner that its longitudinal direction is along the rotational direction of the brake disc.

As shown in FIG. 2 , a plurality of through holes 16 penetrating in the thickness direction are provided on the substrate 12 . The through hole 16 is provided at the position where the brake lining 14 is provided, and the through hole 16 is formed in the number of the installed brake lining 14 . Each through hole 16 is formed in a shape in which the diameter of the lower end portion in FIG. 2 is enlarged.

Curved surface seats 18 each having a concave curved surface are formed around the respective through holes 16 on the front surface (the upper surface in FIG. 2 ) of the base plate 12 on which the brake lining is disposed. The curved seat 18 is formed by a circular recess in plan view, and the curved surface on the top thereof becomes the seat surface 18a. The through holes 16 are respectively formed in the center of the curved seat 18 .

As shown in FIG. 1 , the brake linings 14 are arranged in two rows in the width direction except at both ends of the base plate 12 in the longitudinal direction, and one is arranged at each end of the base plate 12 . The respective brake linings 14 are arranged in a state of being separated from each other. In addition, although two rows are shown in the illustration, it is also possible to arrange three rows in the width direction by reducing the diameter of the brake lining 14 .

As shown in FIGS. 1 and 2 , each brake lining 14 is formed in a disc shape. Although not shown, each brake lining 14 may be formed in a polygonal shape such as a triangle, a pentagon, or a hexagon.

The front surface (the end surface on the side away from the base plate 12 ) of the brake lining 14 serves as a pressing surface 20 that is pressed against the brake disc. Each of these brake linings 14 is formed with a through-hole 22 penetrating through the center portion up and down (in the plate thickness direction). The through hole 22 is opposite to the through hole 16 of the substrate 12 .

Each through-hole 22 has a small-diameter stepped hole formed on the substrate 12 side, and a small-diameter portion 22 b and a large-diameter portion 22 c are formed with the stepped portion 22 a interposed therebetween. The small-diameter portion 22b is formed on the substrate 12 side of the stepped portion 22a, and the large-diameter portion 22c is formed on the pressing surface 20 side.

Each brake lining 14 has a main body portion 24 formed to have a substantially constant thickness and capable of contacting the brake disc, and a cylindrical portion 26 extending from the main body portion 24 toward the base plate 12 . The through hole 22 is formed in the main body part 24 , and the cylindrical part 26 is formed on the lower end surface of the main body part 24 surrounding the through hole 22 and faces the curved surface seat 18 .

A front end surface (lower end surface) 26 a of the cylindrical portion 26 is formed as a convex curved surface corresponding to the bottom surface 18 a of the curved surface seat 18 of the substrate 12 . In other words, the front end surface 26 a of the cylindrical portion 26 is formed as an arcuate surface in which the axis of the cylindrical portion 26 becomes the center of rotation. In addition, the brake lining 14 forms a gap between the front end surface 26 a of the cylindrical portion 26 and the bottom surface 18 a of the curved seat 18 . Thereby, when the front-end surface 26a of the cylindrical part 26 abuts on the bottom surface 18a of the curved surface seat 18, it can displace along the curved surface seat 18 in the state of this abutment.

The base plate 12 and the brake lining 14 are joined together by a rivet 30 as an example of a holding member. The rivet 30 has a head portion 32 used for preventing detachment and a main body portion 34 with a smaller diameter than the head portion 32 . The rivet 30 is inserted across the through hole 16 of the base plate 12 and the through hole 22 of the brake lining 14 .

The head portion 32 has a smaller diameter than the large diameter portion 22c of the through hole 22 of the brake lining 14, and has an outer diameter larger than that of the small diameter portion 22b. The lower end surface of the head portion 32 is in contact with the upper surface (contact surface) of the step portion 22 a of the through hole 22 of the brake lining 14 from above. As a result, the brake lining 14 is prevented from coming off by the rivet 30 .

The main body part 34 has the contact part 34a which contacts the board|substrate 12, and the intermediate part 34b arrange|positioned between the head part 32 and the contact part 34a.

The intermediate portion 34b has an outer diameter smaller than both the head portion 32 and the abutting portion 34a. In other words, the contact portion 34a is configured to have a larger diameter than the intermediate portion 34b.

The contact portion 34 a has an outer diameter smaller than that of the head portion 32 , and the lower end portion of the contact portion 34 a contacts the curved seat 18 of the substrate 12 .

The main body portion 34 is provided with a connecting portion 36 extending downward from the lower end portion of the abutting portion 34 a and disposed in the through hole 16 of the substrate 12 . The diameter of the lower portion of the connecting portion 36 is enlarged, and the rivet 30 is fixed to the substrate 12 by sandwiching the substrate 12 between the lower portion of the connecting portion 36 and the abutting portion 34 a.

The distance from the lower end surface of the head portion 32 to the lower end surface of the contact portion 34 a is slightly longer than the distance from the upper surface of the stepped portion 22 a to the front end of the cylindrical portion 26 . Accordingly, a slight gap is formed between the front end surface 26 a of the cylindrical portion 26 and the bottom surface 18 a of the curved surface seat 18 in a state where the brake lining 14 is coupled to the base plate 12 .

A gap width S1 between the contact portion 34 a and the cylindrical portion 26 is formed smaller than a gap width S2 between the head portion 32 and the inner peripheral surface of the large-diameter portion 22 c of the through hole 22 . This is because, when the brake lining 14 is tilted, the inner peripheral surface of the cylindrical portion 26 abuts on the outer periphery of the contact portion 34 a before the inner peripheral surface of the through hole 22 abuts on the outer peripheral surface of the head portion 32 . face.

Elastic members 40 are respectively provided between the base plate 12 and the respective brake linings 14 . As shown in FIG. 3 , each elastic member 40 is formed of a metal coil spring, and is a disk-shaped member whose bottom surface forms an opening 40 a. The elastic member 40 is disposed between the base plate 12 and the brake lining 14 in a state where the cylindrical portion 26 is inserted through the opening 40 a.

The elastic member 40 applies elastic force to the base plate 12 and the brake lining 14 in a direction to separate them. The elastic member 40 has a modulus of elasticity such that the brake lining 14 elastically deforms when the brake lining 14 is pressed against the brake disc for a braking action. Accordingly, when the brake lining 14 presses the brake disc, the brake lining 14 is elastically deformed by the pressing force transmitted to the elastic member 40 via the brake lining 14 , whereby the brake lining 14 is displaced vertically or obliquely.

A heat conduction suppression member 44 is disposed between the brake lining 14 and the elastic member 40 . The heat conduction suppressing member 44 is formed of a plate material having the same shape and size as the base plate 12 in plan view, and the heat conduction suppressing member 44 is provided across each brake lining 14 . In addition, since the board|substrate 12 is arrange|positioned on the back surface of the heat conduction suppression member 44, the board|substrate 12 is not shown directly in FIG.

The heat-restraining member 44 has contact portions 44a provided correspondingly to the respective brake linings 14 and extension portions 44b provided between these contact portions 44a. Each contact portion 44 a is an annular portion having a diameter slightly larger than the inner diameter of the cylindrical portion 26 and an outer diameter substantially the same as that of the upper end portion of the elastic member 40 . The suppressing heat conduction member 44 is arranged on the lower surface of the brake lining 14 in a state where the cylindrical portion 26 is inserted through the opening of the contact portion 44 a. And the contact portion 44 a is brought into contact with the brake lining 14 .

The extension part 44b is a site|part which connects each contact part 44a mutually, and extends stepwise from each contact part 44a. Accordingly, the extension portion 44b is separated from the lower surface of the brake lining 14, and extends in a direction substantially parallel to the lower surface of the brake lining 14 in this state.

The heat-conducting member 44 is made of a material having a lower thermal conductivity than the brake lining 14 . The heat conduction suppressing member 44 is made of, for example, a stainless steel plate material whose thermal conductivity is lower than that of cast iron constituting the portion (lower end portion) of the brake lining 14 on the side of the base plate 12 .

A lock device 48 for the brake lining 14 is provided in the brake disc pad 10 of the present embodiment. The anti-rotation device 48 is composed of a pin 49 arranged between the base plate 12 and the brake lining 14 , an engaging groove (recess) 50 provided on the brake lining 14 , and an engaging hole 51 provided on the base plate 12 . . That is, the engaging groove 50 is arranged opposite to the engaging hole 51 , the upper end of the pin 49 is inserted into the engaging groove 50 , and the lower end of the pin 49 is inserted into the engaging hole 51 . Thereby, the pin 49 engages with the inner peripheral surface of the engaging groove 50 and the inner peripheral surface of the engaging hole 51 , and the rotation of the brake lining 14 is prevented.

The insertion hole 44c through which the said pin 49 is inserted is provided in the heat conduction suppression member 44. As shown in FIG. Since the suppressing heat conduction member 44 is disposed between the base plate 12 and the brake pad 14 , the insertion hole 44 c allows the pin 49 to be joined to both the base plate 12 and the brake pad 14 to insert the pin 49 .

Next, the operation of the brake disc friction pad 10 constructed as above will be described.

In this brake disc friction block 10 , when the brake lining 14 is not pressed against the brake disc during non-braking operation, the brake lining 14 is held between the cylindrical portion 26 and the cylindrical portion 26 by the elastic force of the elastic member 40 . A gap is formed between the curved seats 18 of the substrate 12 . At this time, the step portion 22 a of the through hole 22 of the brake lining 14 is engaged with the head portion 32 of the rivet 30 , so that the brake lining 14 does not come off from the base plate 12 .

When the brake lining 14 is pressed onto the brake disc (during braking action), it maintains the same state as the state during the non-braking action until the pressing force becomes equal to the elastic force of the elastic member 40, but if When the pressing force becomes greater than the elastic force of the elastic member 40 , the elastic member 40 elastically deforms. The elastic deformation of the elastic member 40 moves the brake lining 14 toward the base plate 12 .

When the surface height of the brake lining is not uniform at the time of the new product, only the protruding brake lining 14 is pressed against the brake disc, but the cylindrical portion 26 corresponding to the protruding brake lining 14 Contacting the curved surface seat 18 prevents the elastic member 40 of the brake pad 14 from being plastically deformed due to large deformation, and prevents subsequent reduction in elastic force. Due to the abutment, the front end surface 26a of the cylindrical portion 26 is displaced along the bottom surface 18a of the curved surface seat 18, whereby the brake lining 14 is obliquely displaced. At this time, since the gap width S1 between the contact portion 34a and the cylindrical portion 26 is formed smaller than the gap width S2 between the head portion 21 and the inner peripheral surface of the large-diameter portion 22c of the through hole 22 of the brake lining 14, Therefore, the inner peripheral surface of the cylindrical part 26 is in contact with the outer peripheral surface of the contact part 34a, and this state is maintained. Also, even when the brake lining 14 is tilted, the brake lining 14 does not displace further upward (in the direction away from the base plate 12 ) because the step portion 22 a engages with the head portion 32 of the rivet 30 . During the braking operation, the heat-conducting member 44 is interposed between the brake lining 14 and the elastic member 40, so even if the brake lining 14 heats up due to friction with the brake disc, it can restrain its heat from flowing to the elastic member. 40 passes.

As described above, according to the present invention, even if the temperature of the brake lining 14 increases due to friction with the brake pads during the braking operation, transmission of the heat to the elastic member 40 can be suppressed. As a result, it is possible to make the elastic member 40 less likely to rise in temperature, thereby making it easier to suppress the elastic member 40 from being annealed to a temperature at which it loses its elasticity, and preventing the elastic member 40 from losing its elasticity. Moreover, since the brake lining 14 can be obliquely displaced and moved along the brake disc through the elastic member 40 , the local surface pressure rise can be reduced, and the service life of the brake lining 14 can be improved.

In particular, in this embodiment, in order to make it difficult to conduct heat directly from the brake lining 14 to the extension portion 44b, the contact portion 44a of the heat transfer member 44 is prevented from dissipating the heat directly received from the brake lining 14 to the extension portion 44b. The temperature rise of the contact portion 44 a of the heat conduction member 44 is suppressed. As a result, a rise in temperature of the elastic member 40 in contact with the contact portion 44a can be effectively suppressed.

In addition, in this embodiment, only one suppressing heat conduction member 44 is provided as a whole, and the man-hours for mounting the suppressing heat conduction member 44 can be reduced. Furthermore, in this embodiment, since the adjacent brake linings 14 are arranged at intervals from each other, and the extension portion 44b that suppresses the heat conduction member 44 is also arranged between the brake linings 14, the extension portion 44b can Insulating and dissipating the heat from the brake lining 14 can more effectively suppress the temperature rise of the elastic member 40 .

In this embodiment, since the brake lining 14 is pressed by the elastic member 40, on the other hand, the stepped portion 22a of the through hole 22 formed on the brake lining 14 is engaged with the head 32 of the rivet 30 to prevent the The disengagement of the brake lining 14, so the displacement of the brake lining 14 can be allowed by the elastic member, and the brake lining 14 is not detached from the base plate 12 by the elastic force of the elastic member 40 at the same time, so that the base plate 12 and the brake pad are connected. The lining 14 is securely engaged.

In the present embodiment, since the cylindrical portion 26 of the brake lining 14 is in contact with the curved surface seat 18 of the base plate 12 when an overload is applied only to a predetermined brake lining 14 during braking operation, The elastic member 40 is not deformed up to the plastic deformation region, and enables the brake lining 14 to be obliquely displaced according to the direction of the applied force.

In addition, in the present embodiment, by arranging the abutting portion 34a of the rivet 30 close to the substrate 12 on which a large shearing stress and bending force act, the bending stress generated on the rivet 30 can be reduced, and thus the stability of the rivet 30 can be achieved. Small diameter.

In addition, in the present embodiment, since the rotation stop device for the brake lining 14 is provided, it is possible to avoid wear of the brake lining 14 and the suppressing heat transfer member 44 as the brake lining 14 rotates.

In the present embodiment, the brake lining 14 has a main body portion 24 and a cylindrical portion 26 , but instead of this structure, the brake lining 14 may be formed in a plate shape having a substantially constant thickness as shown in FIG. 4 . In this structure, the curved seat 18 is not provided on the base plate 12, and the elastic member 40 is arranged between the base plate 12 and the brake lining 14 in a state where the rivet 30 is directly inserted through the opening 40a.

The rivet 30 has a head portion 32 for retaining and a cylindrical body portion 34 integrally provided with the head portion 32 . The main body portion 34 has an outer diameter smaller in diameter than the head portion 32 .

The contact portion 44a of the heat-conducting member 44 is formed in an annular shape having an inner diameter slightly larger than the main body portion 34 of the rivet 30 and an outer diameter substantially the same as the upper end portion of the elastic member 40 . The rivet 30 is directly inserted into the contact portion 44a.

The elastic member 40 is set to have a modulus of elasticity that prevents the heat conduction member 44 from coming into contact with the substrate 12 during a braking operation in which the brake lining 14 is pressed against the brake disc.

When the pressing force becomes larger than the elastic force of the elastic member 40 during the braking operation, the elastic member 40 elastically deforms. The elastic deformation of the elastic member 40 moves the brake lining 14 toward the base plate 12 or tilts the brake lining 14 . That is, depending on the installation state of the brake disc friction pad 10 and the wear state of the brake lining 14, etc., the brake lining 14 is inclined when the entire surface of the brake lining 14 is stressed unevenly, and the brake lining 14 is inclined. The brake pad 14 moves in parallel to the base plate 12 side maintaining its posture while the entire surface of the sheet 14 is uniformly stressed. At this time, the pressing force of the brake lining 14 is borne by the elastic force of the elastic member 40 .

In this modified example, since the temperature of the elastic member 40 can be made difficult to rise, it is easy to suppress the temperature rise of the elastic member 40 to a temperature at which the elastic member 40 loses its elasticity. In addition, since the brake lining 14 is obliquely displaced and moved along the brake disc through the elastic member 40, the local surface pressure rise can be reduced, and the life of the brake lining 14 can be improved.

In the above-described embodiment and modified example, the heat conduction suppressing member 44 is formed as an integral structure straddling each brake lining 14 , but instead of this structure, an independent heat conduction suppressing member may be provided on each brake lining 14 .

In addition, in the above-described embodiment, the extension portion 44 b of the heat conduction member 44 is prevented from separating from the brake lining 14 , but the present invention is not limited thereto, and the extension portion 44 b may be in contact with the brake lining 14 . However, it is preferable that the extension portion 44b be separated from the brake lining 14 in terms of effectively suppressing the temperature rise of the extension portion 44b.

Claims (6)

1. friction block of brake disk, it forms with the state assembling brake lining of leaving from this substrate on substrate, it is characterized in that, comprising:

Elastic member, it is configured between described substrate and the described brake lining, by making described brake lining tilt displacement to pushing of brake disc, described brake lining is moved to the direction near described substrate;

Suppress conducting-heat elements, it is configured between described elastic member and the described brake lining,

On described inhibition conducting-heat elements, be provided with the contacting part pushed to described brake lining by described elastic member and leave and from the extended extension part of described contacting part from described brake lining.

2. friction block of brake disk as claimed in claim 1 is characterized in that described brake lining and elastic member are provided with a plurality of respectively, and described inhibition conducting-heat elements is crossed over described each brake lining and is provided with.

3. friction block of brake disk as claimed in claim 1, it is characterized in that, through hole with stepped part is set on described brake lining, and the holding member of the head with the shape that can engage with described stepped part is set, described brake lining is pushed to the direction of leaving described substrate by the elastic force that utilizes described elastic member, the stepped part of described through hole and the head butt of described holding member remain on thus by under the state of anti-avulsion simultaneously.

4. friction block of brake disk as claimed in claim 3, it is characterized in that, on described substrate, form the curved shoe of concavity, the position that is fixed with described holding member is surrounded, be provided with the cylindrical portion of the front-end face that has convex of relative configuration with described bent seat surface on described brake lining, described brake lining has the gap and is kept by described holding member between described cylindrical portion and described curved shoe.

5. friction block of brake disk as claimed in claim 4, it is characterized in that, described holding member has the diameter main part littler than described head, described main part have and the abutting part of described substrate butt and be configured in this abutting part and described head between and diameter less than the intermediate portion of described abutting part, the gap width between the abutting part of described holding member and the described cylindrical portion forms less than the head of described holding member and the gap width between the described brake lining.

6. as each described friction block of brake disk in the claim 1～5, it is characterized in that, whirl-stop device is set, it prevents the rotation in described brake lining when described brake disc is pushed.

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