Braking noise analysis method and device, storage medium and computer equipment

Abstract

The embodiment of the invention provides a braking noise analysis method and device, a storage medium and computer equipment. The method comprises the steps that finite element models of all parts are assembled, and a brake assembly is generated; joining stiffness is added to the contact surfaces of all the parts in the brake assembly, and joining part parameters are obtained; carrying out actual characteristic value analysis on the brake assembly based on the joint part parameter, and outputting a characteristic value and a characteristic vector; and performing frequency response analysis according to the characteristic value and the characteristic vector, and outputting a braking noise analysis result. In the technical scheme provided by the embodiment of the invention, the actual characteristic value analysis is performed on the brake assembly based on the joint part parameter, and the characteristic value and the characteristic vector are output; frequency response analysis is carried out according to the feature values and the feature vectors, and the brake noise analysis result is output, so that the analysis cost of the brake noise is reduced, various noise sources can be accurately identified, and the analysis accuracy and efficiency of the brake noise are improved.

Description

Technical Field

[0001] The present invention relates to the field of vehicle technology, and in particular to a brake noise analysis method, device, storage medium and computer equipment. Background Art

[0002] Braking noise (sharp noise) is a squeaking noise of about 2KHz to 16KHz that is easily perceived by the user when lightly pressing the brake. It is a low-level sound that damages the quality of the vehicle. Braking noise during braking is generated based on the following two principles: 1. Vibration (energy) source: caused by the μ-v characteristics of the friction surface and the instability of the geometric structure of the brake caliper. 2. Resonance system: The internal damping of the brake parts such as the caliper, brake pad, rotor, etc. and the damping of the contact surface that constitute the system do not work due to the influence of their respective eigenvalues, eigenvectors, and the joint stiffness on the contact surface.

[0003] In the related art, experiments are conducted on actual vehicles to test the braking noise under different working conditions in order to analyze the braking noise. However, the analysis cost is high and it is difficult to accurately identify all noise sources. The accuracy and efficiency of the braking noise analysis are low. Summary of the invention

[0004] In view of this, an embodiment of the present invention provides a brake noise analysis method, apparatus, storage medium and computer equipment to reduce the analysis cost of brake noise, accurately identify multiple noise sources, and improve the accuracy and efficiency of brake noise analysis.

[0005] In one aspect, an embodiment of the present invention provides a brake noise analysis method, comprising:

[0006] Assemble the finite element models of each component to generate a brake assembly;

[0007] Adding joint stiffness to the contact surface of each part in the brake assembly to obtain joint part parameters;

[0008] Performing actual eigenvalue analysis on the brake assembly based on the joint part parameters, and outputting eigenvalues ​​and eigenvectors;

[0009] A frequency response analysis is performed according to the eigenvalue and the eigenvector, and a brake noise analysis result is output.

[0010] Optionally, the joint part parameters include a spring coefficient and a damping coefficient, and the joint stiffness is added to the contact surface of each part in the brake assembly to obtain the joint part parameters, including:

[0011] Establishing an equivalent model of the joint part of the brake assembly;

[0012] Obtaining a resonance frequency and a damping ratio obtained through a vibration test of the brake assembly;

[0013] The spring coefficient and the damping coefficient of the equivalent model of the joint part are obtained based on the finite element model according to the resonance frequency and the damping ratio.

[0014] Optionally, the eigenvalue includes a natural vibration number, the eigenvector includes a natural frequency, and the actual eigenvalue analysis of the brake assembly based on the joint part parameters is performed to output the eigenvalue and the eigenvector, including:

[0015] Adding the joint part parameters and the joint stiffness to the brake assembly to generate an assembly model;

[0016] Model calculation is performed on the assembly model to generate natural vibration numbers and natural frequencies.

[0017] Optionally, performing frequency response analysis according to the eigenvalue and the eigenvector includes:

[0018] Specifying a vibration point and a response point and performing a modal analysis according to a transfer function obtained from a vibration test to obtain an experimental result, wherein the experimental result includes an experimental frequency;

[0019] The experimental frequency is compared with the natural frequency to perform frequency response analysis on the eigenvalues ​​and eigenvectors.

[0020] Optionally, the brake noise analysis result includes: reducing the peak level of the transfer function; curbing the movement of the cylinder teeth in the brake assembly; or keeping the brake pad rigid and curbing its bending and torsion.

[0021] Optionally, before assembling the finite element models of the various parts to generate the brake assembly, the process includes:

[0022] Create finite element models of multiple parts;

[0023] Enter the material coefficients corresponding to each part in the finite element model;

[0024] Calculate the part eigenvalues ​​of each part based on the canonical mode algorithm;

[0025] Brake noise analysis is performed based on the part characteristic values ​​of each part, and treatment countermeasures are generated.

[0026] Optionally, the treatment measures include: changing the thickness of the brake pad back plate, changing the shape of the brake pad opening; changing the spoke thickness distribution of the rotor sliding part, changing the number and shape of ribs; or changing the stiffness of the cylinder body.

[0027] On the other hand, an embodiment of the present invention provides a braking noise analysis device, comprising:

[0028] The assembly module is used to assemble the finite element models of various parts to generate a brake assembly;

[0029] An acquisition module, used to add a joint stiffness to the contact surface of each part in the brake assembly to obtain joint part parameters;

[0030] A first analysis module, configured to perform actual eigenvalue analysis on the brake assembly based on the joint part parameters, and output eigenvalues ​​and eigenvectors;

[0031] The second analysis module is used to perform frequency response analysis according to the eigenvalues ​​and eigenvectors and output a brake noise analysis result.

[0032] On the other hand, an embodiment of the present invention provides a storage medium, wherein the storage medium includes a stored program, wherein when the program is executed, the device where the storage medium is located is controlled to execute the above-mentioned brake noise analysis method.

[0033] On the other hand, an embodiment of the present invention provides a computer device, including a memory and a processor, wherein the memory is used to store information including program instructions, and the processor is used to control the execution of the program instructions, wherein the program instructions implement the steps of the above-mentioned braking noise analysis method when loaded and executed by the processor.

[0034] In the technical solution provided by the embodiment of the present invention, the finite element models of various parts are assembled to generate a brake assembly; the joint stiffness is added to the contact surface of each part in the brake assembly to obtain the joint part parameters; the actual eigenvalue analysis of the brake assembly is performed based on the joint part parameters, and the eigenvalue and eigenvector are output; the frequency response analysis is performed based on the eigenvalue and eigenvector, and the brake noise analysis result is output. In the technical solution provided by the embodiment of the present invention, the actual eigenvalue analysis of the brake assembly is performed based on the joint part parameters, and the eigenvalue and eigenvector are output; the frequency response analysis is performed based on the eigenvalue and eigenvector, and the brake noise analysis result is output, which reduces the analysis cost of the brake noise, can accurately identify a variety of noise sources, and improves the accuracy and efficiency of the brake noise analysis. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0036] Figure 1 A flowchart of a brake noise analysis method provided by an embodiment of the present invention;

[0037] Figure 2 A flowchart of another brake noise analysis method provided by an embodiment of the present invention;

[0038] Figure 3 A schematic diagram of the noise result of the characteristic value of a part provided by an embodiment of the present invention;

[0039] Figure 4 A schematic diagram of a model of a brake assembly provided by an embodiment of the present invention;

[0040] Figure 5 A schematic diagram of an equivalent model of a joint portion provided by an embodiment of the present invention;

[0041] Figure 6 A schematic diagram of a vibration test provided by an embodiment of the present invention;

[0042] Figure 7 A schematic diagram of a finite element model provided in one embodiment of the present invention;

[0043] Figure 8 A schematic diagram of a spring coefficient and a damping coefficient provided in one embodiment of the present invention;

[0044] Fig.9A A schematic diagram of the relationship between contact surface pressure and spring coefficient provided by an embodiment of the present invention;

[0045] Fig. 9B A schematic diagram of the relationship between contact surface pressure and damping coefficient provided by an embodiment of the present invention;

[0046] Fig.10 A schematic diagram of a vibration test result provided by an embodiment of the present invention;

[0047] Fig.11 A schematic diagram of a brake noise analysis device provided by an embodiment of the present invention;

[0048] Fig.12 A schematic diagram of a computer device provided by an embodiment of the present invention. DETAILED DESCRIPTION

[0049] In order to better understand the technical solution of the present invention, the embodiments of the present invention are described in detail below with reference to the accompanying drawings.

[0050] It should be clear that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0051] The terms used in the embodiments of the present invention are only for the purpose of describing specific embodiments, and are not intended to limit the present invention. The singular forms "a", "said" and "the" used in the embodiments of the present invention and the appended claims are also intended to include plural forms, unless the context clearly indicates other meanings.

[0052] It should be understood that the term "and / or" used in this article is only a description of the association relationship of associated objects, indicating that there can be three relationships. For example, A and / or B can represent: A exists alone, A and B exist at the same time, and B exists alone. In addition, the character " / " in this article generally indicates that the associated objects before and after are in an "or" relationship.

[0053] An embodiment of the present invention provides a brake noise analysis method. Figure 1 A flowchart of a brake noise analysis method provided by an embodiment of the present invention is shown in FIG. Figure 1 As shown, the method includes:

[0054] Step 102: Assemble the finite element models of the various parts to generate a brake assembly.

[0055] In the embodiment of the present invention, each step is performed by a computer device. For example, the computer device includes a computer or a tablet computer.

[0056] In the embodiment of the present invention, the finite element method (FEM) models of multiple parts are assembled to generate a brake assembly. For example, the parts constituting the brake assembly include: a back plate, a brake pad, a cylinder body, a cylinder jaw, a rotor, and a torque member.

[0057] Step 104: Add joint stiffness to the contact surface of each part in the brake assembly to obtain joint part parameters.

[0058] In the embodiment of the present invention, the vibration characteristics of the structure formed by connecting various parts are determined according to the vibration characteristics of each part and the way in which the parts are connected (also called the characteristics of the joint part).

[0059] In the embodiment of the present invention, the parameters of the joint part include a spring coefficient and a damping coefficient.

[0060] Step 106: Perform actual eigenvalue analysis on the brake assembly based on the joint part parameters, and output eigenvalues ​​and eigenvectors.

[0061] In the embodiment of the present invention, for the nodes with added contact stiffness and damping coefficient, the nodes with added contact stiffness should be set so that they are evenly distributed on the entire contact surface. The contact node positions between the two parts should be accurate and consistent, and if there is a difference on one side, it should be controlled within 1mm.

[0062] In the embodiment of the present invention, the eigenvalue includes the natural vibration number, and the eigenvector includes the natural frequency.

[0063] Step 108: Perform frequency response analysis based on the eigenvalues ​​and eigenvectors and output the brake noise analysis results.

[0064] In an embodiment of the present invention, vibration points and response points can be specified and modal analysis can be performed based on the transfer function obtained from the vibration test to obtain experimental results, which include experimental frequencies; the experimental frequencies and natural frequencies are compared to perform frequency response analysis on eigenvalues ​​and eigenvectors.

[0065] In the technical solution provided by the embodiment of the present invention, the finite element models of various parts are assembled to generate a brake assembly; the joint stiffness is added to the contact surface of each part in the brake assembly to obtain the joint part parameters; the actual eigenvalue analysis of the brake assembly is performed based on the joint part parameters, and the eigenvalue and eigenvector are output; the frequency response analysis is performed based on the eigenvalue and eigenvector, and the brake noise analysis result is output. In the technical solution provided by the embodiment of the present invention, the actual eigenvalue analysis of the brake assembly is performed based on the joint part parameters, and the eigenvalue and eigenvector are output; the frequency response analysis is performed based on the eigenvalue and eigenvector, and the brake noise analysis result is output, which reduces the analysis cost of the brake noise, can accurately identify a variety of noise sources, and improves the accuracy and efficiency of the brake noise analysis.

[0066] An embodiment of the present invention provides another brake noise analysis method. Figure 2 A flowchart of another brake noise analysis method provided by an embodiment of the present invention is shown in FIG. Figure 2 As shown, the method includes:

[0067] Step 202: Establish finite element models of multiple parts.

[0068] In the embodiment of the present invention, each step is performed by a computer device. For example, the computer device includes a computer or a tablet computer.

[0069] In the embodiment of the present invention, a FEM model of multiple parts is established, wherein the multiple parts may include: a rotor, a caliper, a brake pad, a cylinder and / or a torque member.

[0070] Step 204: Input the material coefficient corresponding to each part in the finite element model.

[0071] In the embodiment of the present invention, the material coefficients corresponding to each part include: elastic modulus, Poisson's ratio and / or density. For example, the elastic modulus corresponding to the rotor is 117.6 GPa, the Poisson's ratio is 0.27, and the density is 7240 kg / m 3 .

[0072] Step 206: Calculate the part feature value of each part based on the canonical mode algorithm.

[0073] In the embodiment of the present invention, the part characteristic value of each part can be calculated by Nastran SOL.103. (If there is a test result, it can be compared with the test value to make the error of the part characteristic value within ±5%. If the error is large, the elastic modulus can be changed and then calculated).

[0074] Step 208: Perform brake noise analysis based on the component characteristic value of each component and generate a treatment strategy.

[0075] In the embodiment of the present invention, the brake noise is generated by the ductile vibration of the cylinder, rotor, brake pad, torque member, etc. Therefore, when the component characteristic values ​​of each component are close, it is easy to generate a sharp abnormal sound.

[0076] Figure 3 A schematic diagram of the noise result of the part characteristic value provided by an embodiment of the present invention, such as Figure 3 As shown, there are cases where the characteristic values ​​of the components of the whole composition are close to each other and produce abnormal noise, but there are also cases where the characteristic values ​​of two parts are close to each other (at the same time as they become closer to each other) and produce abnormal noise. In addition, even if the sharp abnormal noise frequency is inconsistent with the characteristic values ​​of the components, if the difference is within 1kHz, it can be considered as the cause of the abnormal noise. In the actual assembly (ASSY) state, after the hydraulic pressure and braking force act, the joint stiffness will be generated on each contact surface, and the characteristic value of the parts will also change by about 1kHz.

[0077] In the embodiment of the present invention, the treatment measures include: changing the thickness of the brake pad back plate, changing the shape of the brake pad opening (vertical, horizontal, inclined, etc.); changing the spoke thickness distribution of the rotor sliding part, changing the number and shape of ribs; or changing the stiffness of the cylinder body (modal analysis can be performed to determine the changed part of the body).

[0078] For example, when the part is a rotor, a FEM model of the rotor can be established, and the rotor eigenvalues ​​can be calculated through the finite element model (Nastran), the rotor eigenvalues ​​can be input, the difference between the rotor's out-of-plane eigenvalues ​​and the rotor's in-plane eigenvalues ​​can be determined, and the frequency of the out-of-plane eigenvalues ​​can be changed according to the rotor eigenvalues. Braking noise (sharp abnormal noise) is caused by the friction force during braking, which makes the rotor's in-plane eigenvalues ​​and the rotor's out-of-plane eigenvalues ​​form a close eigenvalue arrangement, resulting in unstable vibration. Therefore, changing the shape of the rotor to increase the difference between the rotor's in-plane eigenvalues ​​and the out-of-plane eigenvalues ​​is also an effective countermeasure. When the frequency difference increases, it is more recommended because changing the out-of-plane eigenvalues ​​only requires a smaller-scale shape change than changing the rotor's in-plane eigenvalues. Regarding the frequency sensitivity of the rotor's numerical out-of-plane eigenvalues, it is necessary to consider the impact on heat capacity, thermal strength, and cooling properties before deciding on the change location and size.

[0079] Step 210: Assemble the finite element models of the various parts to generate a brake assembly.

[0080] In the embodiment of the present invention, the finite element models of the various parts after the above-mentioned treatment measures are executed can be assembled to generate a brake assembly.

[0081] Figure 4 A schematic diagram of a brake assembly according to an embodiment of the present invention is shown in FIG. Figure 4 As shown, the various parts that make up the brake assembly include: a back plate, a brake pad, a cylinder body, a cylinder jaw, a rotor and a torque member.

[0082] Step 212: Add joint stiffness to the contact surface of each part in the brake assembly to obtain joint part parameters.

[0083] In the embodiment of the present invention, the vibration characteristics of the structure formed by connecting various parts are determined according to the vibration characteristics of each part and the way in which the parts are connected (also called the characteristics of the joint part).

[0084] In the embodiment of the present invention, the parameters of the joint part include a spring coefficient and a damping coefficient.

[0085] In the embodiment of the present invention, step 212 includes:

[0086] Step 2122: Establish an equivalent model of the joint part of the brake assembly.

[0087] Figure 5 A schematic diagram of an equivalent model of a joint portion provided by an embodiment of the present invention, such as Figure 5As shown, the joint is modeled as a spring and a shock absorber in the form of an equivalent model, and the joint parameters include the spring coefficient K and the damping coefficient C.

[0088] Step 2124: Obtain the resonance frequency and damping ratio obtained through the vibration test of the brake assembly.

[0089] Figure 6 A schematic diagram of a vibration test provided by an embodiment of the present invention is shown in FIG. Figure 6 As shown, in order to avoid interference as much as possible, the test piece is suspended in the air for testing. The bolt preload is adjusted to produce the required contact surface pressure. In order to obtain the axial force of each bolt, a bolt gauge is used. In order to achieve a balanced contact surface pressure, not only the bolt clamping axial force but also the arrangement of the bolts should be considered. For soft friction materials, it is more appropriate to use a method of inserting between metals to produce contact surface pressure rather than tightening bolts. Vibrate with a rocker and measure the frequency response function. Here, the resonance frequency ωno and the damping ratio ζn0 are obtained. The damping ratio ζn0 can be calculated using the 1-degree-of-freedom curve fitting method.

[0090] Step 2126: Obtain the spring coefficient and damping coefficient of the equivalent model of the joint part based on the finite element model according to the resonance frequency and the damping ratio.

[0091] Figure 7 A schematic diagram of a finite element model provided in one embodiment of the present invention is shown in FIG. Figure 7 As shown, the FEM model is established to make the calculated resonance frequency ωno and damping ratio ζn0 as close to the experimental value as possible, and the spring coefficient K and damping coefficient C are changed to repeat the calculation. The spring-shock absorber can be modeled in three directions (one vertical direction and two shear directions), assuming that the two shear directions are the same. Figure 8 The values ​​of spring coefficient K and damping coefficient C are obtained analytically.

[0092] Figure 8 A schematic diagram of a spring coefficient and a damping coefficient provided by an embodiment of the present invention, such as Figure 8 As shown, we can obtain the K1 (vertical direction) and K2 (shear direction) curves about the first-order eigenvector, and the same relationship curves can be obtained using the second-order eigenvector. The point of intersection is used as the spring coefficient K and the damping coefficient C, and the damping force is also derived in the same way.

[0093] In the embodiment of the present invention, if the contact surface pressure increases, the natural vibration frequency will increase, and conversely, the damping ratio will decrease. The higher the contact surface pressure, the closer the structure is to an integrated structure. Regarding the characteristics of the joint part, compared with the integrated type, its damping force increases and the natural vibration frequency decreases.

[0094] Fig.9AA schematic diagram of the relationship between contact surface pressure and spring coefficient provided by an embodiment of the present invention, Fig. 9B A schematic diagram of the relationship between the contact surface pressure and the damping coefficient provided by an embodiment of the present invention, such as Fig.9A and Fig. 9B As shown, the spring stiffness in the normal direction is greater than that in the tangential direction. In addition, with the increase in contact surface pressure, the spring stiffness in the normal direction increases at a higher rate than that in the tangential direction. Although the normal stiffness of NP (black surface coating) ~ SI0C material and NP (black surface coating) ~ FCD material is lower than that of FCA ~ friction material (NP-01), it can be considered that this is the result of the NP material being coated with black. The contact (combination) stiffness is greatly affected by two factors: (1) the material combination of the two contacting parts; and (2) the contact surface pressure.

[0095] In the embodiment of the present invention, it is possible to use Fig.9A and Fig. 9B The joint stiffness and damping coefficient obtained can be used when establishing the FEM model of the brake assembly. Fig.9A Where x is LOG10 (contact surface pressure), y is LOG10 (spring coefficient), Fig. 9B In the figure, x is LOG10 (contact surface pressure) and y is LOG10 (damping coefficient). The units can be converted as needed, and the relationship between the contact surface pressure and the hydraulic pressure must also be considered.

[0096] Step 214: Perform actual eigenvalue analysis on the brake assembly based on the joint part parameters, and output eigenvalues ​​and eigenvectors.

[0097] In the embodiment of the present invention, for nodes with additional contact stiffness and damping coefficient, the nodes with additional contact stiffness should be set so that they are evenly distributed on the entire contact surface. The contact node positions between two parts should be accurate and consistent. If there is a difference on one side, it should be controlled within 1mm. The additional contact stiffness and damping coefficient on the contact surface between each part is used Fig.9A and Fig. 9B data.

[0098] In the embodiment of the present invention, the eigenvalue includes the natural vibration number, and the eigenvector includes the natural frequency.

[0099] In the embodiment of the present invention, the joint part parameters and the joint stiffness can be added to the brake assembly to generate an assembly model; the assembly model is calculated to generate the natural vibration number and the natural frequency.

[0100] Specifically, the joint parameters and joint stiffness can be added to the brake assembly model and input into the IDEAS SYSTEM DYNAMICS ANALYSIS commercial program for assembly (the digital model of the contact part is very important when assembling the brake assembly model). The COMPONENTDEFINITION TASK function in I-DEAS MODEL SOLUTION can be used to read the geometric data and modal data of each part. The SYSTEM DEFINITION TASK SYSTEM function can be used to match the three-dimensional position of the parts. At this time, not only the contact surface geometry between the two parts should be consistent, but also the nodes should be as consistent as possible. In the CONNECTORDEFINITION TASK function, enter the definition of the connection number and contact stiffness of each contact surface. Define the node number connecting each contact surface in the SYSTEM DEFINITION TASK.

[0101] Specifically, select the number of models to be calculated. Generally, if you set it to about 50, the model around 18kHz will be calculated, and the natural vibration number (EIGENVALUE) and strain energy (STRAIN ENERGY) will be output. It can be seen that the vibration of the caliper has a great influence on the generation of the squeal.

[0102] Step 216: Perform frequency response analysis based on the eigenvalues ​​and eigenvectors and output the brake noise analysis results.

[0103] In an embodiment of the present invention, vibration points and response points can be specified and modal analysis can be performed based on the transfer function obtained from the vibration test to obtain experimental results, which include experimental frequencies; the experimental frequencies and natural frequencies are compared to perform frequency response analysis on eigenvalues ​​and eigenvectors.

[0104] Specifically, specifying the vibration point and the response point may include: specifying the vibration point, vibration mode, load condition, responsiveness, response direction, frequency range, and acceleration.

[0105] Fig.10 A schematic diagram of a vibration test result provided by an embodiment of the present invention is shown in FIG. Fig.10As shown, modal analysis (GLOBAL CURVE FITTING method) is performed using the transfer function obtained from the vibration test. Cylinder body = 50 points, rotor = 36 points, brake pad = 6 points. Brake fluid pressure = 1.7Mpa. Vibration point = outer brake pad. Response point = rotor sliding surface. Internal impedance peak = 6.0kHz. At the frequency of the screech (6.0kHz), the rotor, brake pad, and cylinder body all have ductile vibrations, which are very similar to the actual screech vibration mode.

[0106] In the embodiment of the present invention, the brake noise analysis results include: reducing the peak level of the transfer function; changing the vibration mode (for example, curbing the movement of the cylinder teeth in the brake assembly; or keeping the brake pad rigid to curb its bending and torsion).

[0107] In the technical solution provided by the embodiment of the present invention, the finite element models of various parts are assembled to generate a brake assembly; the joint stiffness is added to the contact surface of each part in the brake assembly to obtain the joint part parameters; the actual eigenvalue analysis of the brake assembly is performed based on the joint part parameters, and the eigenvalue and eigenvector are output; the frequency response analysis is performed based on the eigenvalue and eigenvector, and the brake noise analysis result is output. In the technical solution provided by the embodiment of the present invention, the actual eigenvalue analysis of the brake assembly is performed based on the joint part parameters, and the eigenvalue and eigenvector are output; the frequency response analysis is performed based on the eigenvalue and eigenvector, and the brake noise analysis result is output, which reduces the analysis cost of the brake noise, can accurately identify a variety of noise sources, and improves the accuracy and efficiency of the brake noise analysis.

[0108] In the technical solution provided by the embodiment of the present invention, the braking noise of the currently mass-produced brake pads is relatively large, and the newly developed brake pads based on the above-mentioned braking noise analysis method have better subjective noise performance.

[0109] An embodiment of the present invention provides a braking noise analysis device, Fig.11 A schematic diagram of a brake noise analysis device provided by an embodiment of the present invention is shown in FIG. Fig.11 As shown, the device includes: an assembly module 11, an acquisition module 12, a first analysis module 13 and a second analysis module 14.

[0110] The assembly module 11 is used to assemble the finite element models of various parts to generate a brake assembly.

[0111] The acquisition module 12 is used to add the joint stiffness to the contact surface of each part in the brake assembly and obtain the joint part parameters.

[0112] The first analysis module 13 is used to perform actual characteristic value analysis on the brake assembly based on the joint part parameters to output characteristic values ​​and characteristic vectors.

[0113] The second analysis module 14 is used to perform frequency response analysis according to the eigenvalues ​​and eigenvectors and output a brake noise analysis result.

[0114] In the embodiment of the present invention, the joint part parameters include a spring coefficient and a damping coefficient, and the acquisition module 12 is specifically used for:

[0115] Establishing an equivalent model of the joint part of the brake assembly;

[0116] Obtaining a resonance frequency and a damping ratio obtained through a vibration test of the brake assembly;

[0117] The spring coefficient and the damping coefficient of the equivalent model of the joint part are obtained based on the finite element model according to the resonance frequency and the damping ratio.

[0118] In an embodiment of the present invention, the eigenvalue includes a natural vibration number, the eigenvector includes a natural frequency, and the first analysis module is specifically used to add the joint part parameters and the joint stiffness to the brake assembly to generate an assembly model; perform model calculation on the assembly model to generate a natural vibration number and a natural frequency.

[0119] In the embodiment of the present invention, the second analysis module 14 is specifically used to specify the vibration point and the response point and perform modal analysis according to the transfer function obtained from the vibration test to obtain experimental results, wherein the experimental results include experimental frequency; the experimental frequency is compared with the natural frequency to perform frequency response analysis on the eigenvalue and eigenvector.

[0120] In an embodiment of the present invention, the brake noise analysis result includes: reducing the peak level of the transfer function; curbing the movement of the cylinder teeth in the brake assembly; or keeping the brake pad rigid to curb its bending and torsion.

[0121] In the embodiment of the present invention, the device further includes: an establishment module 15 , an input module 16 , a calculation module 17 and a third analysis module 18 .

[0122] The building module 15 is used to build finite element models of multiple parts.

[0123] The input module 16 is used to input the material coefficient corresponding to each part in the finite element model.

[0124] The calculation module 17 is used to calculate the part characteristic value of each part based on the canonical mode algorithm.

[0125] The third analysis module 18 is used to analyze the brake noise according to the component characteristic value of each component and generate a treatment strategy.

[0126] In the embodiment of the present invention, the treatment measures include: changing the thickness of the brake pad back plate, changing the shape of the brake pad opening; changing the spoke thickness distribution of the rotor sliding part, changing the number and shape of ribs; or changing the stiffness of the cylinder body.

[0127] In the technical solution provided by the embodiment of the present invention, the finite element models of various parts are assembled to generate a brake assembly; the joint stiffness is added to the contact surface of each part in the brake assembly to obtain the joint part parameters; the actual eigenvalue analysis of the brake assembly is performed based on the joint part parameters, and the eigenvalue and eigenvector are output; the frequency response analysis is performed based on the eigenvalue and eigenvector, and the brake noise analysis result is output. In the technical solution provided by the embodiment of the present invention, the actual eigenvalue analysis of the brake assembly is performed based on the joint part parameters, and the eigenvalue and eigenvector are output; the frequency response analysis is performed based on the eigenvalue and eigenvector, and the brake noise analysis result is output, which reduces the analysis cost of the brake noise, can accurately identify a variety of noise sources, and improves the accuracy and efficiency of the brake noise analysis.

[0128] The brake noise analysis device provided in the embodiment of the present invention can be used to achieve the above Figure 1 or Figure 2 The braking noise analysis method of the present invention can be specifically described in the embodiment of the braking noise analysis method described above, and will not be described again here.

[0129] An embodiment of the present invention provides a storage medium, which includes a stored program, wherein when the program is running, the device where the storage medium is located is controlled to execute the steps of the embodiment of the above-mentioned braking noise analysis method. For a specific description, please refer to the embodiment of the above-mentioned braking noise analysis method.

[0130] An embodiment of the present invention provides a computer device, including a memory and a processor, wherein the memory is used to store information including program instructions, and the processor is used to control the execution of the program instructions. When the program instructions are loaded and executed by the processor, the steps of the embodiment of the above-mentioned brake noise analysis method are implemented. For a specific description, please refer to the embodiment of the above-mentioned brake noise analysis method.

[0131] Fig.12 A schematic diagram of a computer device provided by an embodiment of the present invention. Fig.12 As shown, the computer device 20 of this embodiment includes: a processor 21, a memory 22, and a computer program 23 stored in the memory 22 and executable on the processor 21. When the computer program 23 is executed by the processor 21, the method for analyzing braking noise in the embodiment is implemented. To avoid repetition, it is not described one by one here. Alternatively, when the computer program is executed by the processor 21, the functions of each model / unit in the device for analyzing braking noise in the embodiment are implemented. To avoid repetition, it is not described one by one here.

[0132] The computer device 20 includes, but is not limited to, a processor 21 and a memory 22. Those skilled in the art will appreciate that Fig.12 It is only an example of the computer device 20 and does not constitute a limitation of the computer device 20. It may include more or fewer components than shown in the figure, or a combination of certain components, or different components. For example, the computer device may also include input and output devices, network access devices, buses, etc.

[0133] The processor 21 may be a central processing unit (CPU), or other general-purpose processors, digital signal processors (DSP), application-specific integrated circuits (ASIC), field-programmable gate arrays (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. A general-purpose processor may be a microprocessor or any conventional processor, etc.

[0134] The memory 22 may be an internal storage unit of the computer device 20, such as a hard disk or memory of the computer device 20. The memory 22 may also be an external storage device of the computer device 20, such as a plug-in hard disk, a smart media card (SMC), a secure digital (SD) card, a flash card, etc. equipped on the computer device 20. Further, the memory 22 may also include both an internal storage unit of the computer device 20 and an external storage device. The memory 22 is used to store computer programs and other programs and data required by the computer device. The memory 22 may also be used to temporarily store data that has been output or is to be output.

[0135] Those skilled in the art can clearly understand that, for the convenience and brevity of description, the specific working processes of the systems, devices and units described above can refer to the corresponding processes in the aforementioned method embodiments and will not be repeated here.

[0136] In the several embodiments provided by the present invention, it should be understood that the disclosed systems, devices and methods can be implemented in other ways. For example, the device embodiments described above are only schematic. For example, the division of the units is only a logical function division. There may be other division methods in actual implementation. For example, multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the mutual coupling or direct coupling or communication connection shown or discussed can be an indirect coupling or communication connection through some interfaces, devices or units, which can be electrical, mechanical or other forms.

[0137] The units described as separate components may or may not be physically separated, and the components shown as units may or may not be physical units, that is, they may be located in one place or distributed on multiple network units. Some or all of the units may be selected according to actual needs to achieve the purpose of the solution of this embodiment.

[0138] In addition, each functional unit in each embodiment of the present invention may be integrated into one processing unit, or each unit may exist physically separately, or two or more units may be integrated into one unit. The above-mentioned integrated unit may be implemented in the form of hardware or in the form of hardware plus software functional units.

[0139] The above-mentioned integrated unit implemented in the form of a software functional unit can be stored in a computer-readable storage medium. The above-mentioned software functional unit is stored in a storage medium, including a number of instructions for a computer device (which can be a personal computer, a server, or a network device, etc.) or a processor (Processor) to perform some steps of the method described in each embodiment of the present invention. The aforementioned storage medium includes: U disk, mobile hard disk, read-only memory (Read-Only Memory, ROM), random access memory (Random Access Memory, RAM), disk or optical disk and other media that can store program codes.

[0140] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A brake noise analysis method, characterized in that: include: Assemble the finite element models of each component to generate a brake assembly; Adding joint stiffness to the contact surface of each part in the brake assembly to obtain joint part parameters; Performing actual eigenvalue analysis on the brake assembly based on the joint part parameters, and outputting eigenvalues ​​and eigenvectors; A frequency response analysis is performed according to the eigenvalue and the eigenvector, and a brake noise analysis result is output.

2. The method according to claim 1, characterized in that The joint part parameters include spring coefficients and damping coefficients. The joint stiffness is added to the contact surfaces of the various parts in the brake assembly. The joint part parameters are obtained, including: Establishing an equivalent model of the joint part of the brake assembly; Obtaining a resonance frequency and a damping ratio obtained through a vibration test of the brake assembly; The spring coefficient and the damping coefficient of the equivalent model of the joint part are obtained based on the finite element model according to the resonance frequency and the damping ratio.

3. The method according to claim 1, characterized in that The characteristic value includes a natural vibration number, the characteristic vector includes a natural frequency, and the actual characteristic value analysis of the brake assembly based on the joint part parameters is performed to output the characteristic value and the characteristic vector, including: Adding the joint part parameters and the joint stiffness to the brake assembly to generate an assembly model; Model calculation is performed on the assembly model to generate natural vibration numbers and natural frequencies.

4. The method according to claim 1, characterized in that: The performing frequency response analysis according to the eigenvalue and the eigenvector comprises: Specifying a vibration point and a response point and performing a modal analysis according to a transfer function obtained from a vibration test to obtain an experimental result, wherein the experimental result includes an experimental frequency; The experimental frequency is compared with the natural frequency to perform frequency response analysis on the eigenvalues ​​and eigenvectors.

5. The method according to claim 4, characterized in that The brake noise analysis results include: reducing the peak level of the transfer function; curbing the movement of the cylinder teeth in the brake assembly; or keeping the brake pad rigid and curbing its bending and torsion.

6. The method according to claim 1, characterized in that Before assembling the finite element models of the various parts to generate the brake assembly, the process includes: Create finite element models of multiple parts; Enter the material coefficients corresponding to each part in the finite element model; Calculate the part eigenvalues ​​of each part based on the canonical mode algorithm; Brake noise analysis is performed based on the part characteristic values ​​of each part, and treatment countermeasures are generated.

7. The method according to claim 6, characterized in that The treatment measures include: changing the thickness of the brake pad back plate, changing the shape of the brake pad opening; changing the spoke thickness distribution of the rotor sliding part, changing the number and shape of ribs; or changing the rigidity of the cylinder body.

8. A braking noise analysis device, characterized in that: include: The assembly module is used to assemble the finite element models of various parts to generate a brake assembly; An acquisition module, used to add a joint stiffness to the contact surface of each part in the brake assembly to obtain joint part parameters; A first analysis module, configured to perform actual eigenvalue analysis on the brake assembly based on the joint part parameters, and output eigenvalues ​​and eigenvectors; The second analysis module is used to perform frequency response analysis according to the eigenvalues ​​and eigenvectors and output a brake noise analysis result.

9. A storage medium, characterized in that: The storage medium includes a stored program, wherein when the program is executed, the device where the storage medium is located is controlled to execute the brake noise analysis method according to any one of claims 1 to 7.

10. A computer device comprising a memory and a processor, wherein the memory is used to store information including program instructions, and the processor is used to control the execution of the program instructions, characterized in that: When the program instructions are loaded and executed by the processor, the steps of the brake noise analysis method according to any one of claims 1 to 7 are implemented.

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