CN220185671U - Elastic floating train brake pad - Google Patents
Elastic floating train brake pad Download PDFInfo
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- CN220185671U CN220185671U CN202321636667.1U CN202321636667U CN220185671U CN 220185671 U CN220185671 U CN 220185671U CN 202321636667 U CN202321636667 U CN 202321636667U CN 220185671 U CN220185671 U CN 220185671U
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- spherical
- brake pad
- hole
- triangular support
- train brake
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- 238000007667 floating Methods 0.000 title claims abstract description 22
- 241000357293 Leptobrama muelleri Species 0.000 claims abstract description 21
- 230000013011 mating Effects 0.000 claims 1
- 238000000034 method Methods 0.000 description 17
- 238000004519 manufacturing process Methods 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000005489 elastic deformation Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000004663 powder metallurgy Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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Abstract
An elastic floating train brake pad comprises a steel back, N triangular supports, 3N friction blocks, 3N belleville springs and 3N spring buckles; the steel back is provided with N spherical counter bores, N rotation stopping holes and 3N mounting holes; the bottom of each spherical counter bore is provided with a positioning hole, and the upper part of each mounting hole is provided with a containing counter bore; each friction block is provided with a back plate, and a spherical boss is arranged on the back plate; the spherical boss is provided with a shaft pin, and the end part of the shaft pin is provided with an annular clamping groove; the disc spring is arranged between the triangular support and the steel back, the shaft pin penetrates through the triangular support, the disc spring and the mounting hole, and the shaft pin is clamped in the annular clamping groove by the spring buckle to be mounted in the accommodating counter bore. The friction block is matched with the triangular support through the spherical structure, and the triangular support is also matched with the steel back through the spherical structure; the friction blocks on the triangular support can float in a self-adaptive manner, so that the phenomenon of eccentric wear can be reduced; a disc spring is arranged between the triangular support and the steel back and can absorb impact vibration generated by braking.
Description
Technical Field
The utility model relates to a brake pad manufacturing technology, in particular to an elastic floating train brake pad, and belongs to the technical field of brake pad manufacturing and production.
Background
At present, disc brake systems are adopted in the motor train unit trains in China, huge kinetic energy of train running is converted into heat energy through friction between brake pads and brake discs, the running speed of the trains is slowed down, and the motor train unit trains are ensured to finish parking braking within a safe distance. The brake pad is the most critical executive component in a train braking system of a motor train unit, not only is the stable, wear-resistant and high-temperature-resistant friction coefficient required, but also the effective friction area of the brake pad and a brake disc is ensured, the phenomena of unstable braking, abnormal abrasion, edge breakage, block falling and the like caused by eccentric wear are reduced, and the braking efficiency and the service life of the brake pad are improved.
Powder metallurgy brake pads for motor train units in the prior art generally comprise a steel back plate, a dovetail block and a plurality of brake pad friction bodies; the steel backboard and the dovetail block are of an integrated forming structure, any brake pad friction body is fixed on the steel backboard through a large gasket and a rivet, and the large gasket is positioned between the brake pad friction body and the steel backboard.
In the prior art, the friction blocks are distributed in a scattered manner, and in each friction block group, the distances from each friction block in the group to the stress point are different; the phenomenon of uneven stress, inconsistent wear degree or abnormal wear of friction blocks in the group exists; even if a spherical contact surface is arranged below each friction block, the single friction block can realize floating deflection; however, since the positions of the friction blocks of each group are different, the abrasion amounts between the friction blocks of each group are not uniform.
Therefore, developing a brake pad that can continuously and effectively form a floating structure without increasing manufacturing cost is a technical problem to be solved by those skilled in the art.
Disclosure of Invention
The utility model provides a novel elastic floating train brake pad, which forms a floating structure by spherical surface matching between a triangular support and a friction block and between the triangular support and a steel back, and can effectively reduce the technical problem of eccentric wear of the friction block in the prior art.
The utility model discloses an elastic floating train brake pad, which comprises a steel back, N triangular supports, 3N friction blocks, 3N belleville springs and 3N spring buckles, wherein the steel back is provided with a plurality of triangular supports; the steel back is provided with N spherical counter bores, N rotation stopping holes and 3N mounting holes; a positioning hole is formed in the bottom of each spherical counter bore, and an accommodating counter bore is formed in the upper part of each mounting hole; each friction block is provided with a back plate, and a spherical boss is arranged on the back plate; the spherical boss is provided with a shaft pin, and the end part of the shaft pin is provided with an annular clamping groove; the disc spring is arranged between the triangular support and the steel back, the shaft pin penetrates through the triangular support, the disc spring and the mounting hole, and the disc spring is clamped in the annular clamping groove by the spring buckle to be arranged in the accommodating counter bore.
Further, each triangular support is provided with 3 spherical grooves, 1 stop pin and 1 spherical convex part, the bottom of each spherical convex part is provided with a positioning pin, and the bottom of each spherical groove is provided with a through hole; the upper part of the through hole is provided with a sinking platform hole, and the disc spring is arranged in the sinking platform hole; and the distances from the centers of the 3 through holes to the center of the locating pin are equal.
Further, the spherical boss of the backboard is embedded in the spherical groove of the triangular support, and the backboard can slide relative to the matching surface.
Further, the spherical counter bore is equal to the spherical radius of the spherical convex part, and the centers of the two spherical surfaces are positioned on the axis of the positioning pin.
Further, the diameter of the locating pin is smaller than the diameter of the locating hole; the diameter of the shaft pin is smaller than the diameters of the mounting hole and the through hole.
Further, the rotation stop pin is assembled in the rotation stop hole in a clearance fit.
Further, the space between the three friction blocks on each triangular support is 1-3mm.
Further, the gap between the friction blocks on the adjacent triangular supports is 3-6mm.
Further, the N is equal to 5 or 6, preferably N is equal to 6.
In the braking process of the train, the friction blocks are contacted with the triangular support through the spherical structure, and the triangular support is also contacted with the steel back through the spherical structure, so that the friction blocks on the triangular support can generate a floating displacement effect when braking is carried out, and the stress is more uniform; in addition, the elastic deformation of the butterfly spring is realized well when the brake pad and the brake disc are pressed, so that the eccentric wear of the friction block is reduced to the greatest extent.
Drawings
FIG. 1 is an overall schematic view of an elastic floating train brake pad according to an embodiment of the present utility model;
FIG. 2 is a schematic view in partial cross-section of FIG. 1;
FIG. 3 is a schematic view of FIG. 2 in an operating state;
FIG. 4 is a schematic view of the friction block of FIG. 1;
FIG. 5 is a schematic view of the steel back structure of FIG. 1;
FIG. 6 is a schematic view of the triangular bracket of FIG. 2;
fig. 7 is a schematic back view of fig. 6.
Detailed Description
The present utility model will be described in further detail with reference to the accompanying drawings and examples.
Example 1
As shown in fig. 1, and with reference to fig. 2-7; the elastic floating train brake pad of the embodiment comprises a steel back 1, 6 triangular supports 3, 18 friction blocks 2, 18 belleville springs 5 and 18 spring buckles 4; the steel back 1 is provided with 6 spherical counter bores 10, 6 rotation stopping holes 13 and 18 mounting holes 12; a positioning hole 11 is formed in the bottom of each spherical counter bore 10, and a containing counter bore 14 is formed in the upper part of each mounting hole 12; each friction block 2 is provided with a back plate 20, and a spherical boss 21 is arranged on the back plate 20; the spherical boss 21 is provided with a shaft pin 22, and the end part of the shaft pin 22 is provided with an annular clamping groove 23; the disc spring 5 is installed between the triangular support 3 and the steel back 1, the shaft pin 22 passes through the triangular support 3, the disc spring 5 and the mounting hole 12, and is clamped in the annular clamping groove 23 by the spring clamp 4 to be installed in the accommodating counter bore 14.
Each triangular support 3 is provided with 3 spherical grooves 33, 1 stop pin 32 and 1 spherical convex part 30, the bottom of each spherical convex part 30 is provided with a positioning pin 31, and the bottom of each spherical groove 33 is provided with a through hole 34; a counter sink hole 35 is formed in the upper portion of the through hole 34, and the belleville spring 5 is installed in the counter sink hole 35; the distances from the centers of the 3 through holes 34 to the center of the positioning pin 31 are equal.
The spherical boss 21 of the back plate 20 is embedded in the spherical groove 33 of the triangular bracket 3, and the back plate 20 can slide relative to the matching surface.
The spherical counter bore 10 is equal to the spherical radius of the spherical convex part 30, and the centers of the two spherical surfaces are positioned on the axis of the positioning pin 31.
The diameter of the positioning pin 31 is smaller than the diameter of the positioning hole 11; the diameter of the axle pin 22 is smaller than the diameters of the mounting hole 12 and the through hole 34.
The rotation stop pin 32 is fitted in the rotation stop hole 13 with a clearance fit.
The spacing between the three friction blocks 2 on each triangular support 3 is 2mm.
The gap between the friction blocks 2 on the adjacent triangular supports 3 is 4.5mm.
In the braking process of the train, the friction block 2 contacts the triangular support 3 through the spherical structure, and the triangular support 3 contacts the steel back 1 through the spherical structure, so that the friction block 2 on the triangular support 3 can generate a floating displacement effect when braking is performed, and the stress is more uniform; in addition, in the embodiment, the belleville spring 5 capable of elastically deforming is arranged between the triangular support 3 and the steel back 1, and when the brake pad and the brake disc are pressed, elastic deformation can be well realized, so that eccentric wear of the friction block is reduced to the greatest extent. In the using process of the brake pad, the eccentric wear amount of the friction block is 1.0-1.6mm; in the prior art of the brake discs of the same type, the eccentric wear amount of the friction block is 5-7.5mm.
Example 2
The difference between this embodiment and embodiment 1 is only that a 3mm gap is provided between the friction blocks 2 on adjacent triangular brackets 3. A 3mm gap is arranged between the friction blocks 2 on each triangular support 3.
In the using process of the brake pad, the eccentric wear amount of the friction block is 1.0-1.5mm; in the prior art of the brake discs of the same type, the eccentric wear amount of the friction block is 5-7.5mm.
The procedure is as in example 1.
Example 3
The difference between this embodiment and embodiment 1 is only that a 1mm gap is provided between the friction blocks 2 on the adjacent triangular brackets 3. A gap of 6mm is arranged between the friction blocks 2 on each triangular support 3.
In the using process of the brake pad, the eccentric wear amount of the friction block is 1.0-1.6mm; in the prior art of the brake discs of the same type, the eccentric wear amount of the friction block is 5-7.5mm.
The procedure is as in example 1.
Example 4
The difference between this embodiment and embodiment 1 is that N is equal to 5, and a 3mm gap is provided between the friction blocks 2 on the adjacent triangular brackets 3. A 5mm gap is arranged between the friction blocks 2 on each triangular support 3.
In the using process of the brake pad, the eccentric wear amount of the friction block is 1.0-1.5mm; in the prior art of the brake discs of the same type, the eccentric wear amount of the friction block is 5-7.5mm.
The procedure is as in example 1.
Example 5
This embodiment differs from embodiment 1 only in that N is equal to 5, and a 1.5mm gap is provided between the friction blocks 2 on adjacent triangular brackets 3. A gap of 4mm is arranged between the friction blocks 2 on each triangular support 3.
In the using process of the brake pad, the eccentric wear amount of the friction block is 1.0-1.4mm; in the prior art of the brake discs of the same type, the eccentric wear amount of the friction block is 5-7.5mm.
The procedure is as in example 1.
Example 6
This embodiment differs from embodiment 1 only in that N is equal to 5, and a 2.5mm gap is provided between the friction blocks 2 on adjacent triangular brackets 3. A gap of 3.5mm is arranged between the friction blocks 2 on each triangular support 3.
In the using process of the brake pad, the eccentric wear amount of the friction block is 1.0-1.5mm; in the prior art of the brake discs of the same type, the eccentric wear amount of the friction block is 5-7.5mm.
The procedure is as in example 1.
The foregoing embodiment numbers of the present utility model are merely for the purpose of description, and do not represent the advantages or disadvantages of the embodiments. From the description of the above embodiments, it will be apparent to those skilled in the art that the above example methods may be implemented by means of a superposition of some variants plus the necessary general techniques; of course, the method can also be realized by simplifying some important technical features. Based on such understanding, the technical solution of the present utility model essentially or partly contributes to the prior art is: overall structure, and with the methods described in the various embodiments of the utility model.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present utility model, and not for limiting the same; although the utility model has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the utility model.
Claims (9)
1. The elastic floating train brake pad is characterized by comprising a steel back, N triangular supports, 3N friction blocks, 3N belleville springs and 3N spring buckles; the steel back is provided with N spherical counter bores, N rotation stopping holes and 3N mounting holes; a positioning hole is formed in the bottom of each spherical counter bore, and an accommodating counter bore is formed in the upper part of each mounting hole; each friction block is provided with a back plate, and a spherical boss is arranged on the back plate; the spherical boss is provided with a shaft pin, and the end part of the shaft pin is provided with an annular clamping groove; the disc spring is arranged between the triangular support and the steel back, the shaft pin penetrates through the triangular support, the disc spring and the mounting hole, and the disc spring is clamped in the annular clamping groove by the spring buckle to be arranged in the accommodating counter bore.
2. The elastic floating train brake pad according to claim 1, wherein each triangular bracket is provided with 3 spherical grooves, 1 stop pin and 1 spherical convex part, the bottom of the spherical convex part is provided with a positioning pin, and the bottom of the spherical groove is provided with a through hole; the upper part of the through hole is provided with a sinking platform hole, and the disc spring is arranged in the sinking platform hole; and the distances from the centers of the 3 through holes to the center of the locating pin are equal.
3. The resilient floating train brake pad of claim 2, wherein said spherical boss of said back plate is fitted into said spherical recess of said triangular bracket, said back plate being slidable relative to the mating surface.
4. The resilient floating train brake pad of claim 3, wherein said spherical counterbore is of equal spherical radius to said spherical boss, and the centers of the two spheres are located on said locating pin axis.
5. Spring floating train brake pad according to one of the claims 2-4, characterized in that the diameter of the locating pin is smaller than the diameter of the locating hole; the diameter of the shaft pin is smaller than the diameters of the mounting hole and the through hole.
6. An elastic floating train brake pad according to any one of claims 2 to 4, wherein said detent pin is fitted in said detent hole in a clearance fit.
7. An elastic floating train brake pad according to any one of claims 1 to 4, wherein the three friction pads on each of said triangular supports are spaced apart by a distance of 1 to 3mm.
8. An elastic floating train brake pad according to any one of claims 1 to 4, wherein the gap between adjacent friction blocks on said triangular support is 3-6mm.
9. Spring floating train brake pad according to one of the claims 1-4, characterized in that N is equal to 5 or 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321636667.1U CN220185671U (en) | 2023-06-26 | 2023-06-26 | Elastic floating train brake pad |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321636667.1U CN220185671U (en) | 2023-06-26 | 2023-06-26 | Elastic floating train brake pad |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN220185671U true CN220185671U (en) | 2023-12-15 |
Family
ID=89105187
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202321636667.1U Active CN220185671U (en) | 2023-06-26 | 2023-06-26 | Elastic floating train brake pad |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN220185671U (en) |
-
2023
- 2023-06-26 CN CN202321636667.1U patent/CN220185671U/en active Active
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