Disc brake

Abstract

The invention provides a disc brake, and relates to the technical field of brakes. The disc brake comprises a brake disc and calipers symmetrically clamped to the two sides of the brake disc, a plurality of oil cavities are formed in the calipers, driving mechanisms are arranged in the oil cavities, each driving mechanism comprises a piston, an end cap is coaxially arranged at one end of each piston, a fixing disc is coaxially and fixedly connected to the interior of each oil cavity, and the fixing discs are fixedly connected to the brake disc. A positioning disc is coaxially arranged in the piston in a sliding mode, the positioning disc is fixedly connected with the fixing disc, a variable-diameter disc is arranged between the end cap and the fixing disc, the stroke of synchronous displacement of the variable-diameter disc and the piston is the first stroke, the stroke of independent displacement of the piston is the second stroke, and after a brake pad is abraded, the variable-diameter disc is driven by the piston to rotate. The piston moves according to the second stroke, the braking effect continues to be formed, in the process, due to the fact that the stress area becomes small from large, the hydraulic oil can make the piston move continuously to form the braking effect under the condition that the pressure is not changed, and the phenomena of brake weakness and fatigue after a brake pad is abraded are avoided.

Description

Technical Field

[0001] The present application relates to the technical field of brakes, and in particular to a disc brake. Background Art

[0002] During actual use, the long-term use between the disc brake pads and the brake disc will inevitably cause wear of the brake pads, which will gradually increase the distance between the pads and the brake disc, and then increase the displacement stroke of the piston inside the caliper, causing the vehicle to exhibit "weak brakes" and "weak brakes" while driving, and increase the braking distance. This will make the vehicle unable to brake normally and bring great safety hazards. Summary of the Invention

[0003] This application aims to solve at least one of the technical problems existing in the prior art. To this end, the present application provides a disc brake, comprising a brake disc and calipers symmetrically clamped on both sides thereof, wherein the caliper is provided with a plurality of oil chambers, the caliper is connected to an oil delivery pipe, the oil delivery pipe and the plurality of oil chambers being connected in sequence, a pad and a brake pad are sequentially provided on the side of the caliper facing the brake disc, a driving mechanism is provided in the oil chamber, the driving mechanism comprises a piston sealingly sliding on the side of the oil chamber facing the pad, an end cap is coaxially provided at the other end of the piston, the end cap and the piston displace synchronously, a fixed disc is coaxially fixed in the oil chamber, a positioning disc is coaxially slidably provided in the piston, the positioning disc and the fixed disc are fixedly connected, a reducing disc is coaxially provided between the end cap and the fixed disc, the outer wall of the reducing disc is slidably engaged with the inner wall of the oil chamber, the stroke of the reducing disc and the piston displacing synchronously is stroke one, and the stroke of the piston displacing alone is stroke two, the stroke two corresponding to the axial wear of the brake pad, and the radial cross-sectional area of ​​the reducing disc is larger than the radial cross-sectional area of ​​the piston.

[0004] Preferably, a brim is coaxially provided on one end of the piston facing the liner, the outer diameter of the brim is larger than the outer diameter of the piston, the brim limits the retraction stroke of the piston into the oil chamber, and the brim is fixedly connected to the liner.

[0005] Preferably, a cavity is coaxially provided inside the piston, and a plurality of positioning rods are evenly fixed in the cavity along the axial and circumferential directions, and the other ends of the plurality of positioning rods extend into the end cap.

[0006] Preferably, one end of the fixed plate is coaxially fixed with a fixed rod, the fixed rod is coaxially fixed to the inner end surface of the oil chamber, the oil delivery pipe is located between the fixed plate and the inner end surface of the oil chamber, a plurality of first through holes are evenly arranged circumferentially on the fixed plate, and the other end of the fixed plate is coaxially fixed with a connecting rod.

[0007] Preferably, the positioning disk is coaxially arranged in the cavity, one end of the positioning disk is coaxially fixed with a shaft core, and the shaft core sealingly slides through the end cap and the reducing disk and is fixed to the connecting rod.

[0008] Preferably, a plurality of second through holes are evenly arranged circumferentially on the positioning plate, and the positioning rod slides through the second through holes.

[0009] Preferably, a first spring is provided between the positioning plate and the end cap, and the first spring is sleeved on the shaft cylinder and located inside the plurality of positioning rods.

[0010] Preferably, a plurality of sleeve rods are evenly fixed to one end of the variable diameter disk in the circumferential direction, the plurality of sleeve rods seal and slide through the end cap, and the sleeve rod seal is slidably sleeved on the positioning rod.

[0011] Preferably, the outer diameter of the sleeve rod is larger than the diameter of the second through hole.

[0012] Preferably, a plurality of third through holes are evenly arranged circumferentially on the variable diameter disk.

[0013] The beneficial effects of the present invention are as follows: the pressure exerted by the hydraulic oil on the variable diameter disc and the end face of the piston drives the variable diameter disc and the piston to axially displace a stroke of one, driving the lining and the brake pad to abut against the brake disc to form a braking effect; when the brake pad is worn, the variable diameter disc is displaced to the limit of stroke one, and the piston is subjected to the action of the hydraulic oil pressure to displace a stroke of two alone, and continues to drive the lining and the brake pad to abut against the brake disc to form a braking effect; in this process, the hydraulic oil passes through the variable diameter disc and applies pressure directly to the end face of the piston with a smaller cross-sectional area; because the force area changes from large to small, the hydraulic oil can cause the piston to continue to displace without changing the pressure, so as to continue to form a braking effect, thereby avoiding the phenomenon of weak and sluggish brakes after the brake pads are worn.

[0014] Additional aspects and advantages of the present application will be given in part in the description below, and in part will become obvious from the description below, or will be learned through practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] In order to more clearly illustrate the technical solutions of the implementation methods of the present application, the following is a brief introduction to the drawings required for use in the implementation methods. It should be understood that the following drawings only show certain embodiments of the present application and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other relevant drawings can be obtained based on these drawings without paying any creative work.

[0016] Figure 1 is a schematic diagram of the overall structure of a disc brake according to an embodiment of the present application; Figure 2 is a schematic structural diagram of a partial caliper in a disc brake according to an embodiment of the present application; Figure 3 is a schematic diagram of the internal structure of a caliper according to an embodiment of the present application; Figure 4 This is a partial structural cross-section of the caliper according to the embodiment of the present application. Figure 1 ; Figure 5 is an exploded view of a partial structure of a driving mechanism according to an embodiment of the present application; Figure 6 is a cross-sectional schematic diagram of the initial state of the driving mechanism in the caliper according to an embodiment of the present application; Figure 7 is a cross-sectional schematic diagram of a driving mechanism according to an embodiment of the present application in a second stroke state within a caliper; Figure 8 According to the embodiment of this application Figure 6 A magnified view of middle A; Figure 9 According to the embodiment of this application Figure 7 Enlarged view of middle B; Figure 10 is a cross-sectional schematic diagram of an initial state of a driving mechanism in a caliper according to another embodiment of the present application; Figure 11 is a cross-sectional schematic diagram of a driving mechanism in a caliper in a second stroke state according to another embodiment of the present application; Figure 12 According to the embodiment of this application Figure 10 Enlarged view of middle C; Figure 13 According to the embodiment of this application Figure 11 Enlarged view of middle D; Figure 14 According to the embodiment of this application Figure 12 Enlarged view of middle E; Figure 15 According to the embodiment of this application Figure 13 Magnified view of F in the middle.

[0017] Icons: 1. Brake disc; 2. Caliper; 21. Oil chamber; 211. Oil pipe; 22. Pad; 23. Brake pad; 24. Annular chamber; 3. Driving mechanism; 31. Piston; 311. Cap brim; 312. Cavity; 313. Positioning rod; 32. End cap; 33. Fixing disc; 331. Fixing rod; 332. First through hole; 333. Connecting rod; 34. Positioning disc; 341. Axis core cylinder; 342. Second through hole; 343. First spring; 35. Variable diameter disk; 351. Sleeve rod; 352. Third through hole; 4. Variable diameter mechanism; 41. Bevel ring; 42. First variable diameter assembly; 421. Annular plate; 422. Radial rod; 43. Second variable diameter assembly; 431. Outer sliding ring; 432. Inner sliding ring; 433. Outer radial hinge ring; 434. Inner radial hinge ring; 435. Middle radial slip ring; 5. Auxiliary assembly; 51. Guide rod; 52. Slider; 53. Second spring. DETAILED DESCRIPTION

[0018] The technical solutions in the embodiments of the present application will be described below in conjunction with the drawings in the embodiments of the present application.

[0019] To make the purpose, technical solutions, and advantages of the embodiments of this application more clear, the technical solutions in the embodiments of this application will be clearly and completely described below in conjunction with the drawings in the embodiments of this application. Obviously, the described embodiments are part of the embodiments of this application, not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0020] Example 1, as Figure 1-Figure 7 As shown, a disc brake according to an embodiment of the present application includes a brake disc 1 and calipers 2 symmetrically clamped on both sides thereof, the two calipers 2 are fixedly connected, wherein a plurality of oil chambers 21 are provided in the caliper 2, an oil pipe 211 is connected to the caliper 2, the oil pipe 211 and the plurality of oil chambers 21 are connected in sequence, and a pad 22 and a brake pad 23 are sequentially provided on the side of the caliper 2 facing the brake disc 1.

[0021] In the specific embodiments of this application, Figure 3-Figure 5 As shown, a driving mechanism 3 is provided in the oil chamber 21, and the driving mechanism 3 includes a piston 31 that slides sealingly in the oil chamber 21 and faces one side of the liner 22. An end cap 32 is coaxially provided at the other end of the piston 31, and the end cap 32 and the piston 31 move synchronously. It should be noted that the end cap 32 and the piston 31 can be threadedly connected to facilitate installation or disassembly between the end cap 32 and the piston 31.

[0022] Among them, a fixed plate 33 is coaxially fixed in the oil chamber 21, a positioning plate 34 is coaxially slidably arranged in the piston 31, the positioning plate 34 and the fixed plate 33 are fixedly connected, and a reducing plate 35 is coaxially arranged between the end cap 32 and the fixed plate 33, and the outer wall of the reducing plate 35 and the inner wall of the oil chamber 21 are slidably matched.

[0023] It should be noted that, in the specific embodiment of the present application, the stroke of synchronous displacement of the reducing disc 35 and the piston 31 is stroke one, and the stroke of independent displacement of the piston 31 is stroke two, and stroke two corresponds to the axial wear of the brake pad 23.

[0024] It should be further explained that the radial cross-sectional area of ​​the variable diameter disk 35 is larger than the radial cross-sectional area of ​​the piston 31. Figure 3 and Figure 4 As shown, the inner diameter of the oil chamber 21 is larger than the outer diameter, that is, the oil chamber 21 is designed to be variable in diameter to adapt to the sliding of the variable diameter plate 35 and the piston 31.

[0025] The caliper 2 involves a design of a variable diameter of the oil chamber 21, which can be achieved in a variety of ways. For example, the caliper 2 is composed of two sealed and detachably connected parts, or a cylindrical detachable part with a small diameter on the outside of the oil chamber 21 can be axially embedded in the caliper 2. Only the variable diameter and sealing design of the oil chamber 21 are required, which will not be repeated here.

[0026] Among them Figure 3-Figure 5 As shown, a brim 311 is coaxially provided at one end of the piston 31 facing the pad 22, and the outer diameter of the brim 311 is larger than the outer diameter of the piston 31. It should be noted that a corresponding recess is provided on the outer side (opening) of the oil chamber 21, so that the brim 311 limits the retraction stroke of the piston 31 into the oil chamber 21, wherein the brim 311 and the pad 22 are fixedly connected (detachable), so that when the piston 31 retracts into the oil chamber 21, it can drive the pad 22 and the brake pad 23 to move toward the side wall of the caliper 2 at the same time, that is, away from the brake disc 1.

[0027] Furthermore, a cavity 312 is coaxially provided inside the piston 31 , and a plurality of positioning rods 313 are evenly fixed in the cavity 312 along the axial and circumferential directions. The other ends of the plurality of positioning rods 313 extend into the end cap 32 .

[0028] In a specific embodiment of the present application, a fixing rod 331 is coaxially fixed to one end of the fixed plate 33, and the fixing rod 331 is coaxially fixed to the inner end surface of the oil chamber 21 (a detachable method such as a threaded connection can be adopted). The oil delivery pipe 211 is located between the fixed plate 33 and the inner end surface of the oil chamber 21. A plurality of first through holes 332 are evenly arranged circumferentially on the fixed plate 33 to facilitate the hydraulic oil to pass through the fixed plate 33. The other end of the fixed plate 33 is coaxially fixed to a connecting rod 333.

[0029] It should be noted that the positioning plate 34 is coaxially arranged in the cavity 312, and one end of the positioning plate 34 is coaxially fixed with a shaft cylinder 341. The shaft cylinder 341 seals and slides through the end cap 32 and the reducing plate 35 and is fixed to the connecting rod 333. It should be noted here that the shaft cylinder 341 and the connecting rod 333 also adopt a detachable connection method (specifically, it can be a threaded connection method). At the same time, the connecting rod 333 can also limit the displacement position of the reducing plate 35 toward the inside of the oil chamber 21.

[0030] Among them, a plurality of second through holes 342 are evenly arranged circumferentially on the positioning plate 34, and the positioning rod 313 slides through the second through hole 342, so that when the piston 31 undergoes axial displacement, the positioning rod 313 can normally follow the piston 31 and move synchronously without causing motion interference with the positioning plate 34.

[0031] It should be noted that a first spring 343 is provided between the positioning plate 34 and the end cap 32 . The first spring 343 is sleeved on the shaft cylinder 341 and located inside the plurality of positioning rods 313 .

[0032] It can be understood that in the specific embodiment of the present application, the positions of the fixed plate 33 and the positioning plate 34 in the oil chamber 21 are fixed, that is, the two will not be displaced, and when the piston 31 is displaced axially from the inside of the oil chamber 21 to the outside, the end cap 32 will squeeze the first spring 343. It can be understood that when the driver releases the brake pedal, under the action of the elastic force of the first spring 343, the end cap 32 will be forced to move the piston 31 from the outside of the oil chamber 21 to the inside, so that the piston 31 and the brake pad 23 are reset.

[0033] Furthermore, a plurality of sleeve rods 351 are evenly fixed to one end of the variable diameter disk 35 in the circumferential direction. The plurality of sleeve rods 351 seal and slide through the end cap 32 , and the sleeve rods 351 seal and slide on the positioning rod 313 . It should be noted that the outer diameter of the sleeve rod 351 is larger than the diameter of the second through hole 342 .

[0034] Preferably, a plurality of third through holes 352 are evenly arranged circumferentially on the reducing disk 35 to facilitate the hydraulic oil to pass through the reducing disk 35 .

[0035] It is understandable that, in the actual use process, when the brake pad 23 is not worn, the driver steps on the brake pedal, and the hydraulic oil flows into the oil chamber 21 through the oil pipe 211. After passing through the multiple first through holes 332 on the fixed plate 33, the hydraulic oil applies pressure to the variable diameter plate 35 and the piston 31 that are now attached together. At this time, the force-bearing area of ​​the two is the cross-sectional area of ​​the variable diameter plate 35. Under the pressure provided by the hydraulic oil, the variable diameter plate 35, the end cap 32, and the piston 31 are synchronously displaced to the outside of the oil chamber 21 (the displacement at this time is 0. The stroke is stroke 1, that is, the distance that the variable diameter disc 35 can be displaced in the oil chamber 21), and drives the lining block 22 and the brake pad 23 to abut against the brake disc 1 to achieve vehicle braking. During this process, the first spring 343 is squeezed, and its elastic force can be used to ensure that the piston 31 is reset when the driver releases the brake pedal, that is, to ensure that the brake pad 23 is separated from the abutment against the brake disc 1; when the brake pad 23 gradually wears during use and the thickness of the brake pad 23 decreases, when the brake pedal is stepped on, the hydraulic oil moves to the variable diameter disc 23 in the oil chamber 21. The disc 35 and the piston 31 apply pressure. When the reducing disc 35 and the piston 31 have moved to the limit of the first stroke, the brake pad 23 is not thick enough and the brake pad 23 does not press the brake disc 1 against the brake disc 1 to achieve a braking effect. Therefore, under the action of the hydraulic oil pressure (the driver continues to depress the brake pedal), the hydraulic oil passes through the third through-hole 352 on the reducing disc 35 and applies pressure on the end face of the piston 31, which can continue to move, forcing the piston 31 to move to the second stroke, so that a braking effect can be achieved between the brake pad 23 and the brake disc 1. During this process, because the reducing disc 35 does not move further, the hydraulic oil pressure is supplied to the piston 31 with a relatively small cross-sectional area. It can be understood that the force-bearing area is reduced from a large area, which means that the piston 31 does not need to apply a greater force during the displacement process of the second stroke. This design ensures that the driver does not need to apply too much force during actual operation to ensure effective braking of the vehicle (the brake pad 23 is within the effective thickness), avoiding the phenomenon of weak and ineffective vehicle braking due to wear of the brake pad 23 during long-term use.

[0036] In the related art, the disc brake has a change in the force-bearing area between stroke one and stroke two. Although this ensures that the driver does not need to apply too much force to brake the vehicle, the sudden change in the force-bearing area will still cause a change in the force during the braking process. Under the influence of habit, it is difficult for the driver to suddenly adapt to the sudden change in braking force. For example, originally, a 30° change in the pedal was required to achieve a smooth brake stop. Now, due to the sudden change in the force-bearing area, the vehicle suddenly stops when the brake pedal is pressed 30° during driving. The sudden change in the angle of the brake pedal (the force applied) corresponding to smooth braking and the braking phenomenon will cause obvious discomfort to the driver, and it is easy to cause sudden stops due to driving habits, affecting driving safety (for example, the driver originally only wanted to brake smoothly, but actually applied the habitual force, and the vehicle suddenly stopped, which may cause the following vehicle to fail to brake in time and cause a rear-end collision).

[0037] Example 2: According to some embodiments of this application, Figure 6-Figure 9 As shown, the outer diameters of the piston 31 and the end cap 32 are consistent, the inner diameter of the oil chamber 21 is set to be variable, and an annular cavity 24 is formed between the circumference of the piston 31 and the end cap 32 and the inner wall of the oil chamber 21. A diameter reducing mechanism 4 is provided in the annular cavity 24. The diameter reducing mechanism 4 includes a bevel ring 41 coaxially fixed to the annular cavity 24, and a first diameter reducing component 42 coaxially arranged on the outer wall of the end cap 32. The first diameter reducing component 42 is deformed when it abuts the bevel ring 41, and its shape is restored when it abuts the diameter reducing disk 35.

[0038] Among them, Figure 8 As shown, one end of the bevel ring 41 is inclined toward the inner end of the oil chamber 21 , and the other end is not inclined. The inner side of the bevel ring 41 is farther away from the inner end of the oil chamber 21 than the outer side.

[0039] Specifically, the first diameter-reducing assembly 42 includes a plurality of annular plates 421 that slide coaxially and seal each other, and radial rods 422 disposed within the plurality of annular plates 421 .

[0040] Furthermore, the axial lengths and radial thicknesses of the multiple annular sheets 421 are consistent, wherein the inner annular sheet 421 is fixedly connected to the outer wall of the end cap 32 , and the outer annular sheet 421 is slidably fitted to the inner wall of the oil chamber 21 .

[0041] The radial rod 422 has an axial telescopic function. Both ends of the radial rod 422 are rotatably connected to the two annular plates 421 on the inner and outer sides respectively. The radial rod 422 is coupled to the other multiple annular plates 421.

[0042] It should be noted that this design allows the multiple annular pieces 421 located in the middle to exhibit uniform axial sliding displacement, which causes the end surfaces of the multiple annular pieces 421 to exhibit linear shape changes.

[0043] It should be noted that, in the initial state (i.e., when the brake pedal is not depressed), the variable diameter disc 35 abuts against the side walls of the plurality of annular plates 421. At this time, the radial cross-sections of the plurality of annular plates 421 are rectangular. When the first stroke ends, the variable diameter disc 35 moves outward to the limit and stops moving, and the piston 31 and the end cap 32 start to move in the second stroke. Figure 8 and Figure 9 As shown, when multiple annular pieces 421 abut against the bevel ring 41, affected by the bevel portion, the multiple annular pieces 421 that originally had a rectangular cross-section will gradually transform into a parallelogram. At this time, the force-bearing area of ​​the piston 31 and the end cap 32 will show a gradually shrinking change, and its force-bearing area will show a linear change from the variable diameter disk 35 to the final cross-sectional area of ​​the piston 31. In this way, the force fed back to the driver during the process of stepping on the brake pedal will show a linear change, and will not cause the driver to be uncomfortable and cause the vehicle to stop due to sudden changes. On the contrary, in the above process, when the driver releases the brake pedal, under the action of the elastic force of the first spring 343, the piston 31 and the end cap 32 will move in the opposite direction and gradually return to their original position. During this process, the multiple annular pieces 421 that are parallelograms will abut against the variable diameter disk 35 in turn, and gradually return from a parallelogram to a rectangle.

[0044] In another embodiment of the present application, Figure 10-15 As shown, the original first reducing assembly 42 can also be designed as a second reducing assembly 43. Specifically, the second reducing assembly 43 includes an outer sliding ring 431 sliding on the inner wall of the oil chamber 21, and an inner sliding ring 432 fixed to the outer wall of the end cap 32. The two ends of the outer sliding ring 431 are respectively sealed and rotatably connected with an outer radial hinge ring 433, and the two ends of the inner sliding ring 432 are respectively sealed and rotatably connected with an inner radial hinge ring 434. A middle radial sliding ring 435 is sealed and slidably connected between the outer radial hinge ring 433 and the inner radial hinge ring 434 located at the same end.

[0045] Therefore, in actual use, when the second reducing assembly 43 gradually abuts against the bevel ring 41, the outer slip ring 431 stops moving first, and the inner slip ring 432 continues to move following the end cap 32 until it abuts against the bevel ring 41 and stops moving. Figure 14 and Figure 15 As shown, the outer radial hinge rings 433 and the inner radial hinge rings 434 on both sides will change in angle, wherein the slidingly connected middle radial sliding ring 435 serves to connect the two (to prevent the two side lengths from changing during the rectangle and parallelogram changes, causing the side to be disconnected) and form a sealing effect, and will prevent the outer radial hinge ring 433 and the inner radial hinge ring 434 at the same end from separating. Conversely, when the piston 31 is reset, it will cause the first diameter-changing component 42 of the cylinder to undergo the same deformation.

[0046] It should be noted that if Figure 14 As shown, in the initial state, the outer radial hinge ring 433 and the inner radial hinge ring 434 are misaligned, and the middle radial sliding ring 435 slides sealingly between the two.

[0047] In the related art, when the first reducing assembly 42 or the second reducing assembly 43 reaches its limit during actual operation, the displacement stroke of the piston 31 is restricted (the piston 31 can no longer move axially outward). Although this design results in a linear change in vehicle braking, the stroke of the piston 31 is limited. This can easily lead to brake failure in the vehicle if the brake pad 23 is severely worn and the driver is unaware of it, thus affecting vehicle driving safety.

[0048] Example 3: According to some embodiments of this application, Figure 8 and Figure 9 As shown, a plurality of auxiliary components 5 are evenly embedded circumferentially on the side wall of the end cap 32 , and the plurality of auxiliary components 5 enable the inner annular sheet 421 and the end cap 32 to have an axial elastic displacement function.

[0049] Among them, a groove is provided on the side wall of the end cap 32, and the auxiliary component 5 is embedded in the groove. The auxiliary component 5 includes a guide rod 51 fixed in the groove along the axial direction, and a slider 52 is slidably connected to the guide rod 51. A second spring 53 is sleeved on the guide rod 51, and one end of the second spring 53 abuts against the slider 52, and the other end abuts against the inner end surface of the groove. The second spring 53 is located at the end of the slider 52 facing the inner side of the oil chamber 21.

[0050] Specifically, the slider 52 is fixedly connected to the inner annular piece 421 .

[0051] It should be noted that, in the specific embodiment of the present application, after the first reducing assembly 42 or the second reducing assembly 43 is abutted against the bevel ring 41, the piston 31 continues to undergo outward axial displacement positioning stroke three, and the corresponding brake pad 23 wear value exceeds the safety range.

[0052] Therefore, during actual use, when the second displacement of the stroke ends, if the wear of the brake pad 23 has exceeded the safe range, the driver will step on the brake pedal without knowing it. At this time, the piston 31 will be forced to continue to move axially outward, so that the brake pad 23 is pressed against the brake disc 1 to achieve braking. During this process, the force-bearing area of ​​the piston 31 no longer changes. In this way, the driver's braking force will change. From the first stroke, the second stroke to the third stroke of the piston 31, the force of stepping on the brake pedal will obviously show different tactile sensations, which will help the driver to have obvious tactile feedback, so that the driver can know that the brake pad 23 has been worn beyond the safe range after safely parking, and replace it in time to reduce driving risks.

[0053] It should be noted, however, that during the third stroke of the piston 31, the first reducing assembly 42 or the second reducing assembly 43 will no longer deform, and the end cap 32 will continue to move outward with the piston 31. At this time, the position of the slider 52 remains unchanged, and it will undergo an axial displacement inward relative to the groove, that is, the slider 52 will squeeze the second spring 53. In this way, after the brake pedal is released, when the piston 31 resets, it can drive the first reducing assembly 42 or the second reducing assembly 43 to form a normal reset (cross-sectional shape change).

[0054] It should be noted that the specific models and specifications of the brake disc 1, caliper 2, pad 22, brake pad 23, oil pipe 211, first spring 343 and second spring 53 need to be selected and determined based on the actual specifications of the device. The specific selection calculation method adopts the existing technology in this field, so it will not be described in detail.

[0055] The above are only specific embodiments of the present application, but the scope of protection of this application is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in this application should be included in the scope of protection of this application. Therefore, the scope of protection of this application should be based on the scope of protection of the claims.

Claims

1. A disc brake, comprising a brake disc (1) and calipers (2) symmetrically clamped on both sides thereof, wherein a plurality of oil chambers (21) are provided in the caliper (2), an oil delivery pipe (211) is connected to the caliper (2), the oil delivery pipe (211) and the plurality of oil chambers (21) are connected in sequence, and a pad (22) and a brake shoe (23) are sequentially provided on the side of the caliper (2) facing the brake disc (1), characterized in that: A driving mechanism (3) is provided in the oil chamber (21), and the driving mechanism (3) includes a piston (31) that slides in a sealed manner on the oil chamber (21) toward the side of the liner (22), and an end cap (32) is coaxially provided on the other end of the piston (31), and the end cap (32) and the piston (31) move synchronously, a fixed plate (33) is coaxially fixed in the oil chamber (21), and a positioning plate (34) is coaxially slidably provided in the piston (31), and the positioning plate (34) and the fixed plate (33) are coaxially fixed in the oil chamber (21). 3) Fixed connection, a reducing disk (35) is coaxially arranged between the end cap (32) and the fixed disk (33), the outer wall of the reducing disk (35) and the inner wall of the oil chamber (21) are slidably matched, the stroke of synchronous displacement of the reducing disk (35) and the piston (31) is stroke one, the stroke of independent displacement of the piston (31) is stroke two, the stroke two corresponds to the axial wear of the brake pad (23), and the radial cross-sectional area of ​​the reducing disk (35) is larger than the radial cross-sectional area of ​​the piston (31).

2. A disc brake according to claim 1, characterized in that: A brim (311) is coaxially provided on one end of the piston (31) facing the liner (22). The outer diameter of the brim (311) is larger than the outer diameter of the piston (31). The brim (311) limits the stroke of the piston (31) retracting into the oil chamber (21). The brim (311) and the liner (22) are fixedly connected.

3. A disc brake according to claim 1, characterized in that: A cavity (312) is coaxially provided inside the piston (31), and a plurality of positioning rods (313) are evenly fixed in the cavity (312) along the axial and circumferential directions. The other ends of the plurality of positioning rods (313) extend into the end cap (32).

4. A disc brake according to claim 3, characterized in that: One end of the fixed disk (33) is coaxially fixedly connected to a fixed rod (331), the fixed rod (331) is coaxially fixedly connected to the inner end surface of the oil chamber (21), the oil delivery pipe (211) is located between the fixed disk (33) and the inner end surface of the oil chamber (21), a plurality of first through holes (332) are evenly arranged circumferentially on the fixed disk (33), and the other end of the fixed disk (33) is coaxially fixedly connected to a connecting rod (333).

5. A disc brake according to claim 4, characterized in that: The positioning disk (34) is coaxially arranged in the cavity (312), and one end of the positioning disk (34) is coaxially fixed with a shaft core cylinder (341). The shaft core cylinder (341) slides through the end cap (32) and the reducing disk (35) in a sealing manner and is fixed to the connecting rod (333).

6. A disc brake according to claim 3, characterized in that: A plurality of second through holes (342) are evenly arranged circumferentially on the positioning plate (34), and the positioning rod (313) slides through the second through holes (342).

7. A disc brake according to claim 5, characterized in that: A first spring (343) is provided between the positioning plate (34) and the end cap (32). The first spring (343) is sleeved on the shaft core cylinder (341) and is located inside the plurality of positioning rods (313).

8. A disc brake according to claim 6, characterized in that: One end of the variable diameter disc (35) is evenly fixed with a plurality of sleeve rods (351) in a circumferential direction. The plurality of sleeve rods (351) are sealingly slidably passed through the end cap (32). The sleeve rods (351) are sealingly slidably sleeved on the positioning rod (313).

9. A disc brake according to claim 8, characterized in that: The outer diameter of the sleeve rod (351) is greater than the diameter of the second through hole (342).

10. A disc brake according to claim 1, characterized in that: A plurality of third through holes (352) are evenly arranged circumferentially on the diameter-changing disk (35).

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