Automobile brake with brake vibration suppression device and parameter optimization method

Abstract

The present invention relates to a vehicle brake with a brake vibration suppression device and a parameter optimization method. The brake vibration suppression device is arranged between the friction block and the piston. The method comprises the following steps: S1: design of a reference vehicle brake brake vibration suppression device; S2: test of a reference vehicle brake brake vibration suppression device; S3: simulation analysis of a reference vehicle brake brake vibration suppression device; S4: correction of a simulation analysis model of a vehicle brake brake vibration suppression device; S5: determination of the hydraulic pressure when the vehicle brake vibration occurs; S6: optimization design of the structural parameters of a conical pressure plate; S7: optimization design of the structural parameters of a cylindrical helical compression spring; S8: optimized design of a brake vibration suppression device for a vehicle brake. The present invention optimizes the size data of the device components to achieve a better vibration suppression effect.

Description

Technical Field

[0001] The invention belongs to the technical field of automobile brakes, and relates to an automobile brake with a brake vibration suppression device and a parameter optimization method. Background Art

[0002] Among the performance evaluation indicators of automobiles, NVH (noise, vibration, harshness) characteristics are important reference factors for measuring automobile comfort, and automobile brake vibration is a very important evaluation indicator for evaluating automobile NVH characteristics. At the same time, the occurrence of automobile brake vibration will also reduce the competitiveness of automobile products. Therefore, the study of automobile brake vibration is of great significance. However, the existing automobile brake vibration suppression scheme cannot achieve good results and needs to be solved. Summary of the invention

[0003] In view of this, an object of the present invention is to provide a vehicle brake with a brake vibration suppression device and a parameter optimization method that can solve the above-mentioned problems.

[0004] In order to achieve the above object, the present invention provides the following technical solutions:

[0005] An automobile brake with a brake vibration suppression device comprises a brake caliper body, a brake block is arranged in the brake caliper body, a friction block for braking the brake block is arranged on the side of the brake block, a piston is arranged on the outer side of the friction block, the piston provides power to the friction block, pushes the friction block to brake, and the friction block and the corresponding piston are connected through the brake vibration suppression device;

[0006] The brake vibration suppression device comprises a bottom plate, a side of the bottom plate close to the friction block is fixed on the outer wall of the friction block, a circular tube guide column is perpendicular to the bottom plate, the circular tube guide column is coaxial with the piston, one end of the circular tube guide column is fixed on the bottom plate, the other end of the circular tube guide column extends into the inner side of the piston, a spring is placed in the circular tube guide column, one end of the spring is fixed to the bottom plate in the circular tube guide column, the height of the spring is higher than the height of the circular tube guide column, a conical pressure plate is sleeved on the outer wall of the circular tube guide column close to the bottom plate, the opening of the conical pressure plate faces downward, the lower end of the conical pressure plate contacts the bottom plate, and the push surface of the piston contacts the conical pressure plate;

[0007] When the brake is in use, the piston presses on the upper surface of the conical pressure plate, and the conical pressure plate deforms. When the conical pressure plate deforms to a certain value, the inner cylindrical end face of the piston will contact the end face of the spring. At this time, the conical pressure plate and the spring will act and support the piston at the same time.

[0008] A method for optimizing parameters of a vehicle brake having a brake vibration suppression device comprises the following steps:

[0009] S1: Design of the brake vibration suppression device for the benchmark automobile brake. According to the internal dimensions of the brake caliper, the designable dimensions between the upper surface of the friction block and the inner cylindrical end surface of the piston, and the diameter of the inner cylinder of the piston, the base plate, the round tube guide column, the conical pressure plate, and the spring are designed;

[0010] S2: Benchmark vehicle brake vibration suppression device test;

[0011] S3: Simulation analysis of brake vibration suppression device for benchmark automobile brakes;

[0012] S4: Modify the simulation analysis model of the automobile brake vibration suppression device;

[0013] S5: Determine the hydraulic pressure when the vehicle brake vibration occurs;

[0014] S6: Optimization design of conical pressure plate structure parameters;

[0015] S7: Structural parameter optimization design of cylindrical helical compression spring;

[0016] S8: Optimized design of brake vibration suppression device for automobile brakes.

[0017] Furthermore, in step S1, the bottom plate thickness t 1 , the original height value of the spring h 1 , the designable dimension h between the upper surface of the friction block and the inner cylindrical end surface of the piston 设 , must satisfy t 1 +h 1 <h 设 ;

[0018] Inner diameter of round tube guide column d 3 , round tube guide column wall thickness t 2 , the inner cylinder diameter of the piston is d 活内 , then the outer diameter of the circular tube guide column is d 3 +t 2 , then it is necessary to satisfy d 3 +t 2 <d 活内 ;

[0019] The inner diameter value d2 of the upper end of the conical pressing plate and the outer diameter value d3+t2 of the circular tube guide column must satisfy d2<d3+t2;

[0020] The original height value h1 of the spring, the compression deformation value Δh1 of the spring during the brake vibration suppression process, and the height value h2 of the round tube guide column must satisfy h1-Δh1>h2.

[0021] Furthermore, in step S2, an electronic universal testing machine is used to perform a compression test on the brake vibration suppression device. During the compression test, the spring needs to be removed and a load is applied to the piston for testing to obtain a displacement-load curve result during the conical pressure plate compression test. The displacement-load curve relationship during the compression test is further differentiated and data processed to obtain a corresponding displacement-stiffness curve result during the conical pressure plate compression test.

[0022] Furthermore, in step S3, a finite element model is established, and a finite element simulation analysis is performed on the brake vibration suppression device. The spring is removed from the finite element model and the load applied to the piston is simulated, analyzed and calculated. In the finite element model, it is necessary to define the contact relationship between the bottom surface of the piston and the upper surface of the conical pressure plate, the contact relationship between the conical pressure plate and the outer diameter surface of the circular tube guide column, and the contact relationship between the conical pressure plate and the upper surface of the plane bottom plate, and consider the influence of the corresponding friction coefficient. The simulation calculation obtains the corresponding displacement-load curve result of the conical pressure plate, and further performs a derivative data processing on the displacement-load relationship to obtain the corresponding displacement-stiffness curve result of the conical pressure plate.

[0023] Furthermore, in step S4, the displacement-load curve results and the displacement-stiffness curve results in the conical pressure plate compression test in step S2 are used to correct the finite element simulation analysis model in step S3, so that the displacement-load curve results and the displacement-stiffness curve results obtained by the conical pressure plate simulation calculation in step S3 are basically consistent with the results in step S2, thereby obtaining a corrected finite element simulation analysis model of the automobile brake vibration suppression device.

[0024] Further, in step S5, the hydraulic pressure value P of the hydraulic oil in the brake caliper body pushing the piston to move when the brake vibration of the automobile brake occurs is measured. 0 , the cross-sectional area of ​​the brake piston is S, then the force F generated by the piston acting on the brake vibration suppression device is obtained by the following formula:

[0025] F=P 0 ×S.

[0026] Further, in step S6, the hydraulic pressure value P of the hydraulic oil in the brake caliper body pushing the piston to move when the braking vibration of the automobile brake occurs, which is measured in step S5 0 In the modified finite element simulation analysis model input in step S4, an expandable grid sequence method is used to obtain the large outer diameter d of the conical pressure plate structure. 1 、Small mouth inner diameter d 2 , the inner cone height h 3 , thickness t 3 As parameter variables, the experimental design of conical pressure plate structure parameter variables is carried out.

[0027] Further, in step S7, the piston force F is input into the established finite element simulation analysis model of the spring, and an expandable grid sequence method is used to calculate the spring outer diameter d of the spring structure. 4 , Spring free height h 1 , Spring material diameter d 5 , spring deformation Δh 1 , the total number of spring coils and the effective number of spring coils are taken as parameter variables to carry out the spring structure parameter variable experiment design.

[0028] Furthermore, in step S8, based on the optimized conical pressure plate structural parameters obtained in step S6 and the optimized spring structural parameters obtained in step S7, an optimized vehicle brake vibration suppression device is designed.

[0029] The beneficial effects of the present invention are:

[0030] The invention creates an additional braking vibration suppression device for automobile brakes, has a good suppression effect on the braking vibration of automobile brakes, and has the advantages of simple and compact structure, low cost, and easy promotion and application on automobile brakes.

[0031] The present invention optimizes the size data of the device components to achieve a better vibration suppression effect.

[0032] Other advantages, objectives and features of the present invention will be described in the following description to some extent, and to some extent, will be obvious to those skilled in the art based on the following examination and study, or can be taught from the practice of the present invention. The objectives and other advantages of the present invention can be realized and obtained through the following description. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] In order to make the purpose, technical solutions and advantages of the present invention more clear, the present invention will be described in detail below in conjunction with the accompanying drawings, wherein:

[0034] Figure 1 This is a schematic diagram of the automobile brake structure;

[0035] Figure 2 It is a schematic diagram of the local structure of the brake vibration suppression device;

[0036] Figure 3 It is a schematic diagram of the structural parameters of the brake vibration suppression device;

[0037] Figure 4 Flowchart of the design method for the brake vibration suppression device of the automobile brake.

[0038] Reference numerals:

[0039] 1. Brake caliper body; 2. Friction block; 3. Piston; 4. Brake vibration suppression device; 5. Base plate; 6. Round tube guide column; 7. Conical pressure plate; 8. Spring. DETAILED DESCRIPTION

[0040] The following describes the embodiments of the present invention by specific examples, and those skilled in the art can easily understand other advantages and effects of the present invention from the contents disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and the details in this specification can also be modified or changed in various ways based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that the illustrations provided in the following embodiments only illustrate the basic concept of the present invention in a schematic manner, and the following embodiments and features in the embodiments can be combined with each other without conflict.

[0041] Among them, the drawings are only used for illustrative explanations, and they only represent schematic diagrams rather than actual pictures, and should not be understood as limitations on the present invention. In order to better illustrate the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of actual products. For those skilled in the art, it is understandable that some well-known structures and their descriptions in the drawings may be omitted.

[0042] The same or similar numbers in the drawings of the embodiments of the present invention correspond to the same or similar parts; in the description of the present invention, it should be understood that if the terms "upper", "lower", "left", "right", "front", "rear", etc. indicate the orientation or position relationship, they are based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation. Therefore, the terms describing the position relationship in the drawings are only used for illustrative purposes and cannot be understood as limiting the present invention. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

[0043] See also Figure 1 to Figure 4 , which is an automobile brake with a brake vibration suppression device, including a brake caliper body 1, a brake block is arranged in the brake caliper body 1, a friction block 2 for braking the brake block is arranged on the side of the brake block, a piston 3 is arranged on the outside of the friction block 2, and the piston 3 provides power to the friction block 2 to push the friction block 2 to brake. The friction block 2 and the corresponding piston 3 are connected through a brake vibration suppression device 4.

[0044] The brake vibration suppression device 4 includes a flat bottom plate 5, the side of the bottom plate 5 close to the friction block 2 is fixed on the outer wall of the friction block 2, the circular tube guide column 6 is perpendicular to the bottom plate 5, the circular tube guide column 6 is coaxial with the piston 3, one end of the circular tube guide column 6 is fixed on the bottom plate 5, and the other end of the circular tube guide column 6 extends into the inner side of the piston 3. A spring 8 is placed in the circular tube guide column 6, and the spring 8 is a cylindrical helical compression spring 8. One end of the spring 8 is fixed on the bottom plate 5 in the circular tube guide column 6, and the height of the spring 8 is higher than the height of the circular tube guide column 6. A conical pressure plate 7 is sleeved on the outer wall of the circular tube guide column 6 near the bottom plate 5, the opening of the conical pressure plate 7 faces downward, and the lower end of the conical pressure plate 7 contacts the bottom plate 5. The push surface of the piston 3 contacts the conical pressure plate 7.

[0045] When the brake is in use, the hydraulic oil in the brake caliper body 1 pushes the piston 3 to move, so that the pushing surface of the piston 3 is pressed on the upper surface of the conical pressure plate 7, so that the conical pressure plate 7 slides along the outer wall of the circular tube guide column 6 and the bottom plate 5 at the same time and deforms. When the conical pressure plate 7 is deformed to a certain value under the action of a certain brake fluid pressure value that causes braking vibration, the inner cylindrical end face of the piston 3 will contact the end face of the spring 8. At this time, the conical pressure plate 7 and the spring 8 will act and support the piston 3 at the same time, so that the force of the piston 3 is transmitted to the friction block 2 through the brake vibration suppression device 4 for braking.

[0046] At this time, the stiffness provided by the conical pressure plate 7 is K 1 , and K 1 <0, the stiffness provided by spring 8 is K 2 , and K 2 >0, and must satisfy K 1 The absolute value is approximately equal to K 2 , that is, satisfying |K 1 ∣≈K 2 , and |K 1 ∣<K 2 , thereby achieving the effect of suppressing the braking vibration of the automobile brake.

[0047] The inner diameter of the upper end of the conical pressing plate 7 is slightly smaller than the outer diameter of the circular tube guide column 6. The upper end surface and the lower end surface of the conical pressing plate 7 are both chamfered.

[0048] The outer diameter of the spring 8 is smaller than the inner diameter of the circular tube guide column 6 .

[0049] Each component of the brake vibration suppression device 4 is made of steel.

[0050] like Figure 3 and Figure 4 A design method for a vehicle brake vibration suppression device 4 comprises the following steps:

[0051] S1: Based on the internal dimensions of the brake caliper body 1, the designable dimensions between the upper surface of the friction block 2 and the inner cylindrical end surface of the piston 3, and the inner cylindrical diameter of the piston 3, the reference automobile brake vibration suppression device 4 is designed, including a base plate 5, a round tube guide column 6, a conical pressure plate 7, and a spring 8. The following design requirements must be met between the various components:

[0052] Thickness of bottom plate 5 t 1 , the original height value h of spring 8 1 , the designable dimension h between the upper surface of the friction block 2 and the inner cylindrical end surface of the piston 3 设 , the three satisfy t 1 +h 1 <h 设 .

[0053] Inner diameter of round tube guide column 6 d 3 , round tube guide column 6 wall thickness t 2 , the inner cylinder diameter of piston 3 is d 活内 , then the outer diameter of the round tube guide column 6 is d 3 +t 2 , then it is necessary to satisfy d 3 +t 2 <d 活内 .

[0054] The inner diameter of the upper end of the conical pressure plate 7 is d 2 The outer diameter of the round tube guide column 6 is d 3 +t 2 , both must satisfy d 2 <d 3 +t 2 .

[0055] The outer diameter of spring 8 is d 4 The inner diameter of the round tube guide column 6 is d 3 , both must satisfy d 4 <d 3 .

[0056] The original height value h of spring 8 1 , the compression deformation value Δh of spring 8 during brake vibration suppression 1 、Height value of round tube guide column 6 h 2 , the three must satisfy h 1 -Δh 1 >h 2 .

[0057] S2: Based on step S1, a compression test is performed on the conical pressure plate 7 using an electronic universal testing machine. During the compression test, the spring 8 needs to be removed and a load is applied to the piston 3 to obtain the displacement-load curve result during the compression test of the conical pressure plate 7. The displacement-load curve relationship during the compression test is further differentiated and data processed to obtain the corresponding displacement-stiffness curve result during the compression test of the conical pressure plate 7.

[0058] S3: Based on step S1, a finite element model is established and a finite element simulation analysis is performed. In the finite element model, the spring 8 is also removed and a load is applied to the piston 3 for simulation analysis and calculation. In the finite element model, it is necessary to define the contact relationship between the bottom surface of the piston 3 and the upper surface of the conical pressure plate 7, the contact relationship between the conical pressure plate 7 and the outer diameter surface of the circular tube guide column 6, and the contact relationship between the conical pressure plate 7 and the upper surface of the plane bottom plate 5, and consider the influence of the corresponding friction coefficient. The simulation calculation obtains the corresponding displacement-load curve result of the conical pressure plate 7, and further performs a derivative data processing on the displacement-load relationship to obtain the corresponding displacement-stiffness curve result of the conical pressure plate 7.

[0059] S4: Use the displacement-load curve results and displacement-stiffness curve results in the compression test of the conical pressure plate 7 in step S2 to correct the finite element simulation analysis model in step S3, so that the displacement-load curve results and displacement-stiffness curve results obtained by the simulation calculation of the conical pressure plate 7 in step S3 are basically consistent with the results in step S2, thereby obtaining a revised finite element simulation analysis model of the automobile brake vibration suppression device 4, and the revised finite element simulation analysis model has a smaller error.

[0060] S5: Determine the hydraulic pressure value P of the hydraulic oil in the brake caliper 1 pushing the piston 3 to move when the vehicle brake vibration occurs 0 , the cross-sectional area of ​​the brake piston 3 is S, then the force F generated by the piston 3 acting on the brake vibration suppression device 4 is obtained by the following formula:

[0061] F=P 0 ×S

[0062] S6: The hydraulic pressure value P of the hydraulic oil in the brake caliper body 1 pushing the piston 3 to move when the brake vibration of the automobile brake occurs, which is measured in step S5 0 In the finite element simulation analysis model modified in step S4, an expandable grid sequence is used to obtain the large outer diameter d of the conical pressure plate 7 structure. 1 、Small mouth inner diameter d 2 , the inner cone height h 3 , thickness t 3 As parameter variables, the experimental design of the conical pressure plate 7 structural parameter variables is carried out.

[0063] Preferably, based on the variable test design results of the conical pressing plate 7 structural parameters, an approximate model of the finite element simulation analysis model in step S4 is created using the moving least squares method. Further, based on the created approximate model, the conical pressing plate 7 structural parameters are used as design variables, and the stiffness K of the conical pressing plate 7 is used as the design variable. 1 Existence K 1 <0 and the corresponding deformation range are taken as the design objectives, and the created approximate model is optimized and calculated by the global response surface method.

[0064] Preferably, the results of the approximate model optimization calculation are brought into the corrected finite element simulation analysis model in step S4 for calculation verification, and the parameter optimization calculation results and the corresponding displacement-load curve results that meet the verification requirements are obtained. The displacement-load relationship is further differentiated and data processed to obtain the corresponding displacement-stiffness curve results of the conical pressure plate 7.

[0065] Preferably, based on the displacement-load curve result of the conical pressure plate 7, the deformation Δh corresponding to the conical pressure plate 7 when the force F is applied is determined. 3 , and then determine the deformation Δh based on the corresponding displacement-stiffness curve results of the conical pressure plate 7 3 The stiffness K corresponding to the conical pressure plate 7 is 1 .

[0066] S7: Input the piston 3 force F into the established finite element simulation analysis model of the spring 8, and use an expandable grid sequence method to calculate the outer diameter d of the spring 8 of the spring 8 structure. 4 、Spring 8 free height h 1 、Spring 8 material diameter d 5 , spring 8 deformation Δh 1 , the total number of coils of spring 8, and the effective number of coils of spring 8 are taken as parameter variables, and the experimental design of structural parameter variables of spring 8 is carried out.

[0067] Preferably, based on the variable test design results of the structural parameters of the spring 8, an approximate model of the finite element simulation analysis model of the spring 8 is created using the moving least squares method.

[0068] Preferably, based on the created approximate model, the structural parameters of the spring 8 are used as design variables, and the stiffness K of the spring 8 is used as 2 is the design target, where K 2 Need to meet K 1 The absolute value is approximately equal to K 2 , that is, satisfying |K 1 ∣≈K 2 , and |K 1 ∣<K 2 The created approximate model is optimized and calculated by global response surface method.

[0069] Preferably, the results of the approximate model optimization calculation are brought into the finite element simulation analysis model of the spring 8 for calculation verification, and the parameter optimization calculation results that meet the verification requirements are obtained, thereby completing the optimization design of the structural parameters of the spring 8.

[0070] S8: Based on the optimized conical pressure plate 7 structural parameters obtained in step S6 and the optimized spring 8 structural parameters obtained in step S7, an optimized design of the automobile brake vibration suppression device 4 is performed. When the brake is used, the hydraulic oil in the brake caliper body 1 pushes the piston 3 to move, so that the piston 3 pushes the surface on the upper surface of the conical pressure plate 7, so that the conical pressure plate 7 slides along the outer diameter surface of the circular tube guide column 6 and the surface of the bottom plate 5 and deforms. The conical pressure plate 7 is deformed at a brake fluid pressure value P at which the brake vibration occurs. 0 Deformed to Δh 3 When the piston 3 is in contact with the upper end of the spring 8, the conical pressure plate 7 and the spring 8 will act and support the piston 3 at the same time, so that the force of the piston 3 is transmitted to the friction block 2 through the brake vibration suppression device 4 for braking. At this time, the stiffness provided by the conical pressure plate 7 is K 1 , and K 1 <0, the stiffness provided by the cylindrical helical compression spring 8 is K 2 , and K 2 >0, and must satisfy K 1 The absolute value is approximately equal to K 2 , that is, satisfying |K 1 ∣≈K 2 , and |K 1 ∣<K 2 , thereby achieving the effect of suppressing the braking vibration of the automobile brake.

[0071] Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solution of the present invention can be modified or replaced by equivalents without departing from the purpose and scope of the technical solution, which should be included in the scope of the claims of the present invention.

Claims

1. An automobile brake with a brake vibration suppression device, characterized in that: The invention comprises a brake caliper body (1), a brake block is arranged inside the brake caliper body (1), a friction block (2) for braking the brake block is arranged on the side of the brake block, a piston (3) is arranged on the outside of the friction block (2), the piston (3) provides power to the friction block (2), and the friction block (2) and the corresponding piston (3) are connected via a brake vibration suppression device (4); The brake vibration suppression device (4) comprises a base plate (5), wherein the side of the base plate (5) close to the friction block (2) is fixed on the outer wall of the friction block (2), a circular tube guide column (6) is perpendicular to the base plate (5), the circular tube guide column (6) is coaxial with the piston (3), one end of the circular tube guide column (6) is fixed on the base plate (5), and the other end of the circular tube guide column (6) extends into the inner side of the piston (3), a spring (8) is placed in the circular tube guide column (6), one end of the spring (8) is fixed on the base plate (5) in the circular tube guide column (6), the height of the spring (8) is higher than the height of the circular tube guide column (6), a conical pressure plate (7) is sleeved on the outer wall of the circular tube guide column (6) close to the base plate (5), the opening of the conical pressure plate (7) faces downward, the lower end of the conical pressure plate (7) contacts the base plate (5), and the pushing surface of the piston (3) contacts the conical pressure plate (7); When the brake is in use, the piston (3) is pressed on the upper surface of the conical pressure plate (7), and the conical pressure plate (7) is deformed. When the conical pressure plate (7) is deformed to a certain value, the inner cylindrical end surface of the piston (3) will come into contact with the end surface of the spring (8). At this time, the conical pressure plate (7) and the spring (8) will act and support the piston (3) at the same time.

2. A parameter optimization method for a vehicle brake with a brake vibration suppression device according to claim 1, characterized in that: The following steps are involved: S1: Design of a reference automobile brake vibration suppression device (4), based on the internal dimensions of the brake caliper (1), the designable dimensions between the upper surface of the friction block (2) and the inner cylindrical end surface of the piston (3), and the inner cylindrical diameter of the piston (3), the base plate (5), the circular tube guide column (6), the conical pressure plate (7), and the spring (8) are designed; S2: Reference vehicle brake vibration suppression device (4) test; S3: Simulation analysis of the brake vibration suppression device (4) of the benchmark automobile brake; S4: Modify the simulation analysis model of the automobile brake vibration suppression device (4); S5: Determine the hydraulic pressure when the vehicle brake vibration occurs; S6: Optimization design of structural parameters of the conical pressure plate (7); S7: Optimization design of structural parameters of cylindrical helical compression spring (8); S8: Design of optimized brake vibration suppression device (4) for automobile brakes.

3. The parameter optimization method of the automobile brake with a brake vibration suppression device according to claim 2, characterized in that: In step S1, the thickness t1 of the base plate (5), the original height value h1 of the spring (8), the designable dimension h between the upper surface of the friction block (2) and the inner cylindrical end surface of the piston (3) 设 , it is necessary to satisfy t1+h1<h 设 ; The inner diameter d3 of the circular tube guide column (6), the wall thickness t2 of the circular tube guide column (6), and the inner cylindrical diameter d of the piston (3) are 活内 , then the outer diameter of the circular tube guide column (6) is d3+2t2, which needs to satisfy d3+2t2<d 活内 ; The inner diameter value d2 of the upper end of the conical pressing plate (7) and the outer diameter value d3+2t2 of the circular tube guide column (6) must satisfy d2>d3+2t2; The original height value h1 of the spring (8), the compression deformation value Δh1 of the spring (8) during the brake vibration suppression process, and the height value h2 of the round tube guide column (6) must satisfy h1-Δh1>h2.

4. The parameter optimization method of the automobile brake with a brake vibration suppression device according to claim 2, characterized in that: In step S2, an electronic universal testing machine is used to perform a compression test on the brake vibration suppression device (4). During the compression test, the spring (8) needs to be removed and a load is applied to the piston (3) for testing to obtain a displacement-load curve result of the conical pressure plate (7) during the compression test. The displacement-load curve relationship during the compression test is further subjected to a derivative data processing to obtain a corresponding displacement-stiffness curve result during the compression test of the conical pressure plate (7).

5. The parameter optimization method of the automobile brake with a brake vibration suppression device according to claim 2, characterized in that: In step S3, a finite element model is established, and a finite element simulation analysis is performed on the brake vibration suppression device (4). The spring (8) is removed from the finite element model and a load is applied to the piston (3) for simulation analysis and calculation. In the finite element model, it is necessary to define the contact relationship between the bottom surface of the piston (3) and the upper surface of the conical pressure plate (7), the contact relationship between the conical pressure plate (7) and the outer diameter surface of the circular tube guide column (6), and the contact relationship between the conical pressure plate (7) and the upper surface of the plane bottom plate (5). The influence of the corresponding friction coefficient is considered, and the corresponding displacement-load curve result of the conical pressure plate (7) is obtained by simulation calculation. The displacement-load relationship is further subjected to a derivative data processing to obtain the corresponding displacement-stiffness curve result of the conical pressure plate (7).

6. The parameter optimization method of the automobile brake with a brake vibration suppression device according to claim 2, characterized in that: In step S4, the displacement-load curve results and displacement-stiffness curve results obtained during the compression test of the conical pressure plate (7) in step S2 are used to correct the finite element simulation analysis model in step S3, so that the displacement-load curve results and displacement-stiffness curve results obtained by simulation calculation of the conical pressure plate (7) in step S3 are basically consistent with the results in step S2, thereby obtaining a corrected finite element simulation analysis model of the automobile brake vibration suppression device (4).

7. The parameter optimization method of the automobile brake with a brake vibration suppression device according to claim 2, characterized in that: In step S5, when the braking vibration of the automobile brake occurs, the hydraulic pressure value P0 of the hydraulic oil in the brake caliper (1) pushing the piston (3) to move is measured. The cross-sectional area of ​​the brake piston (3) is S. Then, the force F generated by the piston (3) acting on the braking vibration suppression device (4) is obtained by the following formula: 。 8. The parameter optimization method of a vehicle brake with a brake vibration suppression device according to claim 2, characterized in that: In step S6, the hydraulic pressure value P0 of the hydraulic oil in the brake caliper (1) pushing the piston (3) to move when the braking vibration of the automobile brake occurs, which is measured in step S5, is input into the finite element simulation analysis model corrected in step S4, and an expandable grid sequence method is used to use the large mouth outer diameter d1, the small mouth inner diameter d2, the inner cone height h3, and the thickness t3 of the conical pressure plate (7) structure as parameter variables to perform a parameter variable test design of the conical pressure plate (7) structure.

9. The parameter optimization method of the automobile brake with a brake vibration suppression device according to claim 2, characterized in that: In step S7, the piston (3) force F is input into the established finite element simulation analysis model of the spring (8), and an expandable grid sequence method is used to use the spring (8) outer diameter d4, the spring (8) free height h1, the spring (8) material diameter d5, the spring (8) deformation Δh1, the total number of spring (8) turns, and the effective number of spring (8) turns of the spring (8) structure as parameter variables to perform a spring (8) structural parameter variable test design.

10. The parameter optimization method of the automobile brake with a brake vibration suppression device according to claim 2, characterized in that: In step S8, based on the optimized conical pressure plate (7) structural parameters obtained in step S6 and the optimized spring (8) structural parameters obtained in step S7, an optimized automobile brake vibration suppression device (4) is designed.

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