Automobile valve cover NVH performance analysis method, device and equipment

Abstract

This application relates to the field of NVH analysis technology, and particularly to a method, apparatus, and equipment for NVH performance analysis of automotive valve cover. The method includes: performing structural vibration response analysis using a finite element model based on the valve cover to obtain the spatial coordinates and vibration response data of each node on the valve cover structural surface; generating an acoustic mesh based on the spatial coordinates and vibration response data of each node and interpolating the structural vibration response data; iteratively adjusting the local density of the acoustic mesh until the mapping error meets the preset accuracy requirements, directly solving the high-frequency interpolation distortion problem caused by the non-coincidence of the spatial positions of the structural mesh and acoustic mesh nodes; performing radiated noise simulation calculations based on the acoustic mesh whose mapping error meets the mapping accuracy requirements, and outputting simulation results, ensuring the accuracy and reliability of the input boundary conditions for the radiated noise simulation calculations, ultimately improving the accuracy of the high-frequency radiated noise simulation results of the valve cover.

Description

Technical Field

[0001] This application belongs to the field of NVH analysis technology, and in particular relates to a method, device and equipment for analyzing the NVH performance of automotive valve cover. Background Technology

[0002] As one of the main sources of radiated noise in an engine, the simulation analysis of the NVH performance of the valve cover has become an important part of automotive product development. In existing technologies, the simulation of radiated noise from the valve cover typically employs a combination of the finite element method (FEM) and the boundary element method (BEM): first, structural vibration response analysis is performed based on the finite element model to obtain vibration velocity data for each node on the valve cover surface; then, the vibration velocity of the structural surface is mapped to an acoustic BEM mesh, which serves as the boundary condition for radiated noise simulation calculations.

[0003] In the aforementioned technical approach, there is an inherent contradiction in the dimensions of the structural finite element mesh and the acoustic boundary element mesh. To ensure the accuracy of structural vibration response analysis, especially to accurately capture structural modes in the mid-to-high frequency range, the finite element mesh typically uses a relatively fine size, commonly second-order tetrahedral elements with element sizes between 2 and 4 millimeters. However, the size of the acoustic boundary element mesh is limited by the calculation frequency and the wavelength of the sound wave. According to acoustic simulation theory, to ensure calculation accuracy, at least 6 elements are required per wavelength. Taking the analysis frequency of 2000 Hz as an example, the wavelength of the sound wave is approximately 170 millimeters, while the maximum allowable size of the acoustic mesh is approximately 28 millimeters. Therefore, the size difference between the structural mesh and the acoustic mesh can reach 5 to 10 times. When mapping the vibration velocity data of the structural mesh nodes to the acoustic mesh nodes, an interpolation algorithm must be used. In the simulation of radiated noise from the valve cover, the significant size difference between the structural finite element mesh and the acoustic boundary element mesh (structural mesh 2-4 millimeters, acoustic mesh up to 28 millimeters) leads to non-overlapping spatial positions of the nodes in the two types of meshes. To complete the data transfer, an interpolation algorithm must be used to map the vibration velocity data of the structural mesh nodes to the acoustic mesh nodes.

[0004] However, when the analysis frequency enters the high-frequency range (above 1500 Hz), the spatial distribution of the vibration velocity field on the surface of the valve cover structure becomes complex, with drastic gradient changes in local areas. Given the inherent premise of non-overlapping mesh nodes, existing low-order interpolation algorithms struggle to accurately capture these high-frequency characteristics. This directly leads to the vibration velocity data of the mapped acoustic mesh nodes deviating from the true physical field, resulting in inaccurate radiated noise simulation results and an inability to accurately predict the actual noise performance of the valve cover. Summary of the Invention

[0005] This application provides a method, apparatus, and equipment for analyzing the NVH performance of automotive valve cover, which can solve the problem of high-frequency interpolation distortion caused by spatial misalignment due to mesh mismatch, and the problem of low accuracy of radiated noise simulation results in the prior art.

[0006] In a first aspect, embodiments of this application provide a method for analyzing the NVH performance of an automotive valve cover, including: Structural vibration response analysis was performed based on the finite element model of the valve cover to obtain the spatial coordinates and vibration response data of each node on the surface of the valve cover structure. Based on the spatial coordinates and vibration response data of each node, an acoustic mesh is generated and the structural vibration response data is interpolated and mapped. The local density of the acoustic mesh is iteratively adjusted until the mapping error meets the preset accuracy requirements. The radiated noise is simulated and calculated based on an acoustic mesh whose mapping error meets the mapping accuracy requirements, and the simulation results are output.

[0007] The technical solutions described in this application embodiment have at least the following technical effects: The NVH performance analysis method for automotive valve cover provided in this application analyzes the structural vibration response based on a finite element model of the valve cover, obtaining the spatial coordinates and vibration response data of each node on the structural surface of the valve cover. This provides an accurate basis for the spatial location and vibration information of the nodes for subsequent acoustic mesh generation and data mapping, avoiding mapping deviations caused by incomplete data sources. Based on the spatial coordinates and vibration response data of each node, an acoustic mesh is generated and interpolated onto the structural vibration response data. By iteratively adjusting the local density of the acoustic mesh until the mapping error meets the preset accuracy requirements, the high-frequency interpolation distortion problem caused by the non-coincidence of the spatial locations of the structural mesh and the acoustic mesh nodes is directly solved, significantly improving the accuracy of mapping vibration data to the acoustic mesh. Based on the acoustic mesh whose mapping error meets the mapping accuracy requirements, radiated noise simulation calculation is performed, and the simulation results are output. This ensures that the input boundary conditions for the radiated noise simulation calculation are accurate and reliable, ultimately improving the accuracy of the high-frequency radiated noise simulation results of the valve cover.

[0008] Secondly, embodiments of this application provide an automotive valve cover NVH performance analysis device, applied to electronic devices, the automotive valve cover NVH performance analysis device comprising: The acquisition unit is used to perform structural vibration response analysis based on the finite element model of the valve cover, and to acquire the spatial coordinates and vibration response data of each node on the surface of the valve cover structure. The mapping unit is used to generate an acoustic mesh based on the spatial coordinates and vibration response data of each node and to interpolate and map the structural vibration response data. The local density of the acoustic mesh is adjusted iteratively until the mapping error meets the preset accuracy requirements. The output unit is used to perform radiated noise simulation calculations based on an acoustic mesh that meets the mapping accuracy requirements according to the mapping error, and outputs the simulation results.

[0009] Thirdly, embodiments of this application provide an electronic device, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the method as described in any of the first aspects above.

[0010] Fourthly, embodiments of this application provide a computer-readable storage medium storing computer instructions that, when executed on a computer, cause the computer to perform the method described in any of the first aspects above.

[0011] Fifthly, embodiments of this application provide a computer program product that, when run on an electronic device, causes the electronic device to perform the method described in any one of the first aspects above.

[0012] It is understood that the beneficial effects of the second to fifth aspects mentioned above can be found in the relevant descriptions in the above aspects, and will not be repeated here. Attached Figure Description

[0013] To more clearly illustrate the technical solutions in the embodiments of this application, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0014] Figure 1 This is a flowchart illustrating an embodiment of the NVH performance analysis method for automotive valve cover provided in this application. Figure 2 This is a schematic diagram of the finite element model of the NVH performance analysis method for automotive valve cover provided in an embodiment of this application; Figure 3 This is a grid diagram of an embodiment of the NVH performance analysis method for automotive valve cover provided in this application; Figure 4 This is a schematic diagram of the structure of an automotive valve cover NVH performance analysis device provided in one embodiment of this application; Figure 5 This is a schematic diagram of the structure of an electronic device provided in an embodiment of this application. Detailed Implementation

[0015] In the following description, specific details such as particular system architectures and techniques are set forth for illustrative purposes and not for limitation, in order to provide a thorough understanding of the embodiments of this application. However, those skilled in the art will understand that this application may also be implemented in other embodiments without these specific details. In other instances, detailed descriptions of well-known systems, apparatuses, circuits, and methods have been omitted so as not to obscure the description of this application with unnecessary detail.

[0016] It should be understood that, when used in this application specification and the appended claims, the term "comprising" indicates the presence of the described features, integrals, steps, operations, elements and / or components, but does not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or a collection thereof.

[0017] It should also be understood that the term “and / or” as used in this application specification and the appended claims means any combination of one or more of the associated listed items and all possible combinations, and includes such combinations.

[0018] As used in this application specification and the appended claims, the term "if" may be interpreted, depending on the context, as "when," "once," "in response to determination," or "in response to detection." Similarly, the phrase "if determination" or "if the described condition or event is detected" may be interpreted, depending on the context, as "once determination," "in response to determination," "once the described condition or event is detected," or "in response to the detection of the described condition or event."

[0019] Furthermore, in the description of this application and the appended claims, the terms "first," "second," "third," etc., are used only to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0020] References to "one embodiment" or "some embodiments" as described in this specification mean that one or more embodiments of this application include a specific feature, structure, or characteristic described in connection with that embodiment. Therefore, the phrases "in one embodiment," "in some embodiments," "in other embodiments," "in still other embodiments," etc., appearing in different parts of this specification do not necessarily refer to the same embodiment, but rather mean "one or more, but not all, embodiments," unless otherwise specifically emphasized. The terms "comprising," "including," "having," and variations thereof mean "including but not limited to," unless otherwise specifically emphasized.

[0021] As one of the main sources of radiated noise in an engine, the simulation analysis of the NVH performance of the valve cover has become an important part of automotive product development. In existing technologies, the simulation of radiated noise from the valve cover typically employs a combination of the finite element method (FEM) and the boundary element method (BEM): first, structural vibration response analysis is performed based on the finite element model to obtain vibration velocity data for each node on the valve cover surface; then, the vibration velocity of the structural surface is mapped to an acoustic BEM mesh, which serves as the boundary condition for radiated noise simulation calculations.

[0022] In the aforementioned technical approach, there is an inherent contradiction in the dimensions of the structural finite element mesh and the acoustic boundary element mesh. To ensure the accuracy of structural vibration response analysis, especially to accurately capture structural modes in the mid-to-high frequency range, the finite element mesh typically uses a relatively fine size, commonly second-order tetrahedral elements with element sizes between 2 and 4 millimeters. However, the size of the acoustic boundary element mesh is limited by the calculation frequency and the wavelength of the sound wave. According to acoustic simulation theory, to ensure calculation accuracy, at least 6 elements are required per wavelength. Taking the analysis frequency of 2000 Hz as an example, the wavelength of the sound wave is approximately 170 millimeters, while the maximum allowable size of the acoustic mesh is approximately 28 millimeters. Therefore, the size difference between the structural mesh and the acoustic mesh can reach 5 to 10 times. When mapping the vibration velocity data of the structural mesh nodes to the acoustic mesh nodes, an interpolation algorithm must be used. In the simulation of radiated noise from the valve cover, the significant size difference between the structural finite element mesh and the acoustic boundary element mesh (structural mesh 2-4 millimeters, acoustic mesh up to 28 millimeters) leads to non-overlapping spatial positions of the nodes in the two types of meshes. To complete the data transfer, an interpolation algorithm must be used to map the vibration velocity data of the structural mesh nodes to the acoustic mesh nodes.

[0023] However, when the analysis frequency enters the high-frequency range (above 1500 Hz), the spatial distribution of the vibration velocity field on the surface of the valve cover structure becomes complex, with drastic gradient changes in local areas. Given the inherent premise of non-overlapping mesh nodes, existing low-order interpolation algorithms struggle to accurately capture these high-frequency characteristics. This directly leads to the vibration velocity data of the mapped acoustic mesh nodes deviating from the true physical field, resulting in inaccurate radiated noise simulation results and an inability to accurately predict the actual noise performance of the valve cover.

[0024] To address the aforementioned issues, this application provides a method for analyzing the NVH performance of automotive valve cover. This method involves analyzing the structural vibration response using a finite element model of the valve cover, obtaining the spatial coordinates and vibration response data of each node on the valve cover's structural surface. This provides an accurate foundation of node spatial location and vibration information for subsequent acoustic mesh generation and data mapping, avoiding mapping deviations caused by incomplete data sources. Based on the spatial coordinates and vibration response data of each node, an acoustic mesh is generated, and the structural vibration response data is interpolated and mapped. By iteratively adjusting the local density of the acoustic mesh until the mapping error meets the preset accuracy requirements, the high-frequency interpolation distortion caused by the non-coincidence of the spatial locations of the structural mesh and the acoustic mesh nodes is directly resolved, significantly improving the accuracy of mapping vibration data to the acoustic mesh. Based on the acoustic mesh whose mapping error meets the accuracy requirements, radiated noise simulation calculations are performed, and the simulation results are output. This ensures the accuracy and reliability of the input boundary conditions for the radiated noise simulation calculations, ultimately improving the accuracy of the high-frequency radiated noise simulation results for the valve cover.

[0025] The NVH performance analysis method for automotive valve cover provided in this application embodiment can be applied to electronic devices. In this case, the electronic device is the executing subject of the NVH performance analysis method for automotive valve cover provided in this application embodiment. This application embodiment does not impose any restrictions on the specific type of electronic device.

[0026] It is understandable that electronic devices can be various smart devices. For example, electronic devices can be mobile phones, tablets, wearable devices, in-vehicle devices, augmented reality (AR) / virtual reality (VR) devices, laptops, ultra-mobile personal computers (UMPCs), netbooks, personal digital assistants (PDAs), desktop computers, smart screens, smart TVs, and other terminal devices.

[0027] To better understand the NVH performance analysis method for automotive valve cover provided in this application, the specific implementation process of the NVH performance analysis method for automotive valve cover provided in this application will be described below by way of example.

[0028] Figure 1 This paper illustrates a schematic flowchart of an NVH performance analysis method for automotive valve cover provided in an embodiment of this application. The NVH performance analysis method for automotive valve cover includes: S100, based on the finite element model of the valve cover, performs structural vibration response analysis to obtain the spatial coordinates and vibration response data of each node on the surface of the valve cover structure.

[0029] The finite element model (FEM) is a mathematical model that discretizes the geometric model of the valve cover into a finite number of elements and nodes, used to numerically solve the vibration response of the structure under stress. Structural vibration response analysis refers to calculating the vibration characteristics of the valve cover under engine operating load excitation using the finite element method, including the displacement, velocity, acceleration, and other response quantities of each node. It can obtain the spatial coordinates (i.e., the X, Y, and Z coordinates of each node in three-dimensional space) and vibration response data (such as vibration velocity amplitude and acceleration amplitude) of all nodes on the valve cover structural surface. This data serves as the input basis for subsequent acoustic mesh generation and radiated noise simulation, discretizing the continuous valve cover structure into computable node data, thus providing a data source for the mapping from structural vibration to sound radiation.

[0030] In one possible implementation, S100, structural vibration response analysis is performed based on the finite element model of the valve cover, obtaining the spatial coordinates and vibration response data of each node on the surface of the valve cover structure, including: S110, Obtain the finite element model of the valve cover; wherein, the finite element model includes the valve cover body structure and surrounding connecting parts.

[0031] As you can understand, a finite element model is a numerical analysis model established using the finite element method, including definitions of nodes, elements, material properties, boundary conditions, etc. Please refer to [link / reference]. Figure 2 The valve cover body structure refers to the geometric main body of the valve cover, including features such as the cover plate, reinforcing ribs, and bolt holes. Peripheral connecting components refer to other parts connected to the valve cover, such as the cylinder head, bolts, gaskets, and connecting brackets. These peripheral components affect the constraint stiffness and vibration transmission path of the valve cover and must be considered in the finite element model. The finite element model can be obtained by generating it from a CAD model using meshing software or by reading it from an existing simulation database. This establishes a structural analysis model that reflects the actual working state of the valve cover, providing an accurate geometric and physical basis for subsequent vibration response calculations.

[0032] S120 applies boundary conditions and load excitation to the finite element model and calculates the vibration response of the finite element model within a preset frequency range; the load excitation includes dynamic loads under engine operating conditions.

[0033] Boundary conditions refer to the displacement degrees of freedom constrained by the valve cover model, simulating the actual constraint state of the valve cover connected to the cylinder head by bolts, such as applying fixed or elastic constraints at the bolt hole locations. Load excitation refers to the dynamic force applied to the model, originating from the impacts and vibrations generated by internal moving parts (such as the camshaft and valve mechanism) during engine operation. Dynamic loads are usually given as force varying with frequency, such as the harmonic excitation forces of various orders within the engine's commonly used speed range (e.g., 600 rpm to 6000 rpm). The preset frequency range typically covers the audible range of 20 Hz to 20000 Hz or the main frequency band of engine radiated noise. The finite element method obtains the vibration response of the model at each frequency point by solving the dynamic equations, such as the vibration displacement, velocity, or acceleration amplitude of each node. Simulation calculations obtain the vibration response of the valve cover under real working loads, avoiding the high cost and long cycle of physical prototype testing, and providing reliable vibration boundary conditions for subsequent acoustic analysis.

[0034] S130, based on the vibration response, extracts the spatial coordinates and vibration velocity amplitude of each node on the surface of the valve cover structure, and determines the vibration velocity amplitude of each node as the vibration response data corresponding to each node.

[0035] It can be understood that the structural surface refers to the set of all nodes and elements exposed to the external air in the finite element model of the valve cover. Spatial coordinates are directly read from the node information of the model. Vibration velocity amplitude refers to the magnitude of the vibration velocity at each node, usually a scalar value (taken as the magnitude or normal component of the velocity vector). Since acoustic radiation is directly related to the normal vibration velocity of the structural surface, the normal velocity amplitude is often used as the acoustic boundary condition. This step filters out surface nodes from the vibration response results of the entire model, extracts the spatial coordinates and corresponding vibration velocity amplitude of each surface node, forming a data set of structural vibration response. This simplifies the finite element calculation results to the structural surface boundary conditions required for acoustic simulation, removes irrelevant data such as internal nodes, and improves the computational efficiency of subsequent acoustic mapping.

[0036] S200 generates an acoustic mesh based on the spatial coordinates and vibration response data of each node and performs interpolation mapping on the structural vibration response data. The local density of the acoustic mesh is adjusted iteratively until the mapping error meets the preset accuracy requirements.

[0037] It is understandable that acoustic meshes are discretized meshes used for boundary element or finite element acoustic simulations, and their node and element distributions differ from those of structural finite element meshes. Since structural finite element meshes and acoustic boundary element meshes typically do not coincide spatially, structural vibration response data is originally defined on the nodes of the structural finite element mesh, while acoustic simulations require defining vibration velocity boundary conditions on the nodes of the acoustic mesh. Therefore, data transfer must be achieved through interpolation mapping. Existing technologies commonly employ low-order algorithms such as linear interpolation or nearest-neighbor interpolation, and process the entire domain uniformly. When the analysis frequency enters the high-frequency range (above 1500 Hz), the spatial distribution of the vibration velocity field on the valve cover surface becomes complex, and local gradient changes drastically. Low-order interpolation struggles to accurately capture these characteristics, easily leading to spatial frequency aliasing, peak attenuation, and phase distortion. This causes the mapped acoustic mesh node vibration velocity data to deviate from the true physical field, resulting in inaccurate radiated noise simulation results. To address the high-frequency interpolation distortion caused by non-coincident node spatial locations, this method first utilizes a refined acoustic mesh and high-precision interpolation in regions of drastic vibration variation, based on the spatial variation characteristics of the structural vibration response, to reduce mapping errors caused by node position deviations. In regions of gradual variation, a sparse mesh and conventional interpolation are used to conserve computational resources. Iterative optimization ensures global mapping accuracy, thereby fundamentally overcoming the distortion defects of low-order interpolation in the high-frequency band in existing technologies.

[0038] In one possible implementation, S200 generates an acoustic mesh based on the spatial coordinates and vibration response data of each node and interpolates and maps the structural vibration response data. The local density of the acoustic mesh is iteratively adjusted until the mapping error meets a preset accuracy requirement, including: S210, based on the spatial coordinates and vibration response data of each node, calculate the spatial rate of change corresponding to the vibration response of each node on the surface of the valve cover structure.

[0039] The spatial rate of change can be understood as the gradient magnitude of the vibration response (such as vibration velocity amplitude) as a function of location, reflecting the intensity of vibration fluctuations in space. The method for calculating the spatial rate of change is as follows: for each node on the structural surface, based on the vibration response values ​​and spatial coordinates of that node and its adjacent nodes, the partial derivatives of the vibration response in three spatial directions are obtained using the finite difference method or gradient calculation algorithm. These partial derivatives are then synthesized to obtain the scalar value of the spatial rate of change for that node. A larger spatial rate of change indicates more intense vibration changes with location near that node, requiring more refined acoustic meshes in that region to accurately capture the spatial distribution of vibration. In the high-frequency band, regions with large spatial rates of change are precisely where interpolation distortion is most severe. Quantifying this characteristic provides an objective basis for subsequent differentiated mesh refinement and high-precision interpolation, avoiding blind refinement or missing critical areas.

[0040] Optionally, S210, based on the spatial coordinates and vibration response data of each node, calculate the spatial rate of change corresponding to the vibration response of each node on the valve cover structure surface, including: S211, based on the spatial coordinates and vibration response data of each node, calculate the rate of change of vibration velocity of each node in the three spatial directions.

[0041] It can be understood that the three spatial directions refer to the X-axis, Y-axis, and Z-axis directions in the finite element model. For each node on the structural surface, using the spatial coordinates of that node and its adjacent nodes, and the vibration velocity amplitude, the partial derivatives of the vibration velocity along the X-axis (Δv / Δx), Y-axis (Δv / Δy), and Z-axis (Δv / Δz) are calculated. A specific calculation method using the finite difference method can be employed: selecting node i and its adjacent node j, calculating the coordinate difference and velocity difference, dividing the velocity difference by the coordinate difference to obtain the approximate rate of change in that direction, and then averaging over multiple adjacent nodes. Decomposing the spatial variation of vibration velocity into components in three orthogonal directions facilitates the subsequent synthesis of the total spatial rate of change, while the rates of change in each direction can be used to analyze the wave characteristics of vibration in a specific direction.

[0042] S212, based on the rate of change of vibration velocity of each node in three spatial directions, the spatial rate of change of each node is obtained.

[0043] It can be understood that the spatial rate of change is the magnitude of the vibration velocity gradient, i.e., the square root of the sum of the squares of the rates of change in the three directions. The specific calculation formula is: G_i = sqrt((∂v / ∂x)^2 + (∂v / ∂y)^2 + (∂v / ∂z)^2), where G_i represents the spatial rate of change at node i. The spatial rate of change comprehensively reflects the degree of drastic change in the vibration response at the node with space, unaffected by direction. It combines the components of the three directions into a comprehensive index that is easy to compare and threshold, providing a unified metric for subsequent identification of high-frequency sensitive areas.

[0044] S220 identifies high-frequency sensitive areas where the spatial change rate exceeds a preset threshold based on the spatial change rate.

[0045] It is understandable that high-frequency sensitive regions refer to localized areas on the valve cover surface with large spatial rates of change in vibration response. In these regions, vibration varies drastically with location, indicating the presence of local modalities or high-frequency vibration characteristics that significantly contribute to sound radiation. This also necessitates a high-resolution acoustic mesh to accurately capture the vibration distribution. The preset threshold is an empirical value or a value determined through trial and error, such as a multiple of the arithmetic mean of the spatial rates of change of all nodes, or a fixed numerical threshold. All surface nodes can be traversed, and nodes with spatial rates of change greater than the preset threshold are marked as belonging to high-frequency sensitive regions. The regions connecting these nodes are merged into continuous high-frequency sensitive regions, automatically identifying the areas most sensitive to acoustic mapping accuracy. Mesh refinement resources are then concentrated on these critical areas, avoiding the waste of computational resources caused by uniform refinement.

[0046] Optionally, S220 identifies high-frequency sensitive regions whose spatial change rate exceeds a preset threshold based on the spatial change rate, including: S221, calculate the arithmetic mean of the spatial change rates of all nodes.

[0047] The arithmetic mean, as we understand it, refers to the sum of the spatial variation rates of all nodes on the valve cover structural surface, divided by the total number of nodes, and denoted as μ. This average reflects the overall level of the spatial variation rate of vibration across the entire structural surface. The method for calculating the arithmetic mean is simple and statistically representative, providing a global reference benchmark for relative threshold setting. This allows the threshold to adapt to the vibration characteristics of different structural components, avoiding the inapplicability of fixed thresholds on different valve cover models.

[0048] S222 marks nodes whose spatial change rate is greater than twice the arithmetic mean as candidate nodes.

[0049] It's understandable that twice the arithmetic mean is used as the screening threshold, i.e., nodes with a spatial variation rate greater than 2μ are selected. Twice is an empirical multiple and can be adjusted according to actual needs (e.g., 1.5 times or 3 times). The vibration variation rate in the regions where these nodes are located is significantly higher than the average level, and they are most likely to have a significant impact on the accuracy of acoustic mapping. After being marked as candidate nodes, these nodes are initially categorized into the candidate set of high-frequency sensitive regions. Using a relative threshold to adaptively screen nodes with drastic vibration changes avoids the subjectivity and lack of universality of manually setting fixed thresholds, while also improving the automation of the screening process.

[0050] S223, determine the high-frequency sensitive area based on candidate nodes and preset thresholds.

[0051] It is understandable that candidate nodes are scattered nodes, requiring further processing to form continuous regions. Preset thresholds here can include area thresholds, connectivity requirements, etc. Spatially adjacent candidate nodes are merged into connected regions, and the geometric features (such as area and maximum size) of each connected region are calculated. Small regions that do not meet the preset threshold requirements are eliminated (for example, isolated regions with too small an area may be numerical noise). The remaining connected regions are finally identified as high-frequency sensitive regions. By extracting continuous regions with engineering significance from discrete candidate nodes and eliminating isolated numerical noise points, the identification results of high-frequency sensitive regions are made more reliable and practical.

[0052] For example, S223, determining high-frequency sensitive regions based on candidate nodes and preset thresholds includes: S2231, perform connected component analysis on the candidate nodes, group interconnected candidate nodes into the same connected component, and calculate the area of ​​each connected component.

[0053] Connected component analysis can be understood as grouping spatially adjacent (sharing edges or corners) candidate nodes into the same connected set. Adjacency is determined based on whether the distance between nodes is less than a certain multiple of the mesh feature size (e.g., 1.5 times the average cell side length). Each connected component corresponds to a candidate high-frequency sensitive region. Area calculation can be performed using the polygon area formula: connect the nodes on the boundary of the connected component sequentially to form a polygon and calculate the area of ​​that polygon, or by statistically analyzing the total area of ​​the cells within the connected component. Connected component analysis clusters discrete nodes into continuous physical regions, facilitating subsequent region selection and mesh refinement operations.

[0054] S2232, remove connected components with an area smaller than a preset area threshold, and retain the connected components as high-frequency sensitive regions.

[0055] It's understandable that the preset area threshold is a minimum area value set based on engineering experience, such as 50 square millimeters or 100 square millimeters. Connected regions with excessively small areas may be caused by local singularities or numerical noise in the finite element mesh, rather than genuine areas of intense vibration. Removing these regions avoids over-refining the mesh in unnecessary locations. Retaining connected regions that meet the area threshold serves as the final high-frequency sensitive region. Area filtering removes false regions, improving the accuracy and engineering practicality of high-frequency sensitive region identification, while reducing the computational cost of subsequent mesh refinement.

[0056] The S230 uses a densified acoustic mesh in high-frequency sensitive areas and a standard acoustic mesh in non-high-frequency sensitive areas.

[0057] It's understandable that the generation method for acoustic meshes varies depending on the region. Please refer to [link / reference]. Figure 3In high-frequency sensitive regions, a smaller mesh size (i.e., a denser mesh), such as half or one-third the standard size, is used to ensure sufficient spatial resolution to capture high-frequency spatial variations in vibration. In non-high-frequency sensitive regions, a standard mesh size is used, determined according to general acoustic simulation requirements (e.g., at least 6 elements per wavelength), which meets the mapping accuracy for conventional vibration responses. A transition process is required at the boundary between the two meshes to ensure node continuity and element quality, thereby achieving a variable density distribution of the acoustic mesh. Densification in critical regions ensures accuracy, while sparseness in non-critical regions saves computational resources, achieving an optimal balance between accuracy and efficiency. The direct purpose of differentiated densification is to reduce the spatial positional deviation between acoustic mesh nodes and structural mesh nodes in high-frequency sensitive regions. The denser the nodes, the smaller the spatial distance during interpolation mapping, and the smaller the interpolation error caused by positional misalignment. Simultaneously, a sparse mesh is maintained in non-sensitive regions to control the overall computational scale, thus minimizing the acoustic mesh size while meeting high-frequency mapping accuracy requirements.

[0058] S240: Map the vibration response data to acoustic mesh nodes, calculate the local mapping error of the high-frequency sensitive area, and adjust the mesh density of the high-frequency sensitive area according to the local mapping error until the local mapping error of the high-frequency sensitive area meets the preset accuracy requirements; wherein the high-frequency sensitive area adopts the first interpolation accuracy, and the non-high-frequency sensitive area adopts the second interpolation accuracy, and the first interpolation accuracy is higher than the second interpolation accuracy.

[0059] Mapping can be understood as the process of interpolating the vibration velocity amplitudes from the structural finite element mesh nodes to the acoustic mesh nodes. Since the two types of mesh nodes are located at different positions, interpolation methods are required. In high-frequency sensitive regions, due to drastic vibration changes, high-precision interpolation methods (such as radial basis function interpolation, which can accurately reproduce high-frequency changes) are needed, i.e., the first interpolation accuracy. In non-high-frequency sensitive regions, where vibration changes are gradual, lower-precision interpolation methods (such as second-order shape function interpolation) can be used, i.e., the second interpolation accuracy. After mapping, the error between the interpolation results on the acoustic mesh nodes in the high-frequency sensitive region and the original vibration data of the structural mesh is calculated (e.g., through cross-validation or using additional validation points). If the error exceeds the preset accuracy requirement, the acoustic mesh in that region is further refined (e.g., the mesh size is reduced), and mapping and error calculation are repeated, forming an iterative cycle until the error meets the requirements. Iterative optimization ensures the mapping accuracy in the high-frequency sensitive region, while maintaining computational efficiency in non-sensitive regions through a regionally differentiated interpolation strategy, ultimately obtaining an acoustic mesh that meets the overall accuracy requirements.

[0060] Optionally, S240 maps the vibration response data to acoustic mesh nodes, calculates the local mapping error in the high-frequency sensitive region, and adjusts the mesh density in the high-frequency sensitive region according to the local mapping error until the local mapping error in the high-frequency sensitive region meets the preset accuracy requirements, including: S241 maps vibration response data to acoustic grid nodes based on encrypted acoustic grids and standard acoustic grids; radial basis function interpolation is used in high-frequency sensitive regions, and second-order shape function interpolation is used in non-high-frequency sensitive regions.

[0061] Radial basis function interpolation is an accurate interpolation method. By selecting radial basis functions (such as quadratic functions or Gaussian functions) and shape parameters, it can interpolate all known data points without error, making it particularly suitable for interpolating high-frequency changing data. Second-order shape function interpolation is a commonly used interpolation method in finite element analysis. It uses the shape functions of the element nodes to interpolate the values ​​at arbitrary points inside, offering high accuracy but lower than radial basis function interpolation, while requiring less computation. Radial basis function interpolation is used in high-frequency sensitive regions to ensure accuracy, while second-order shape function interpolation is used in non-high-frequency sensitive regions to improve efficiency. This optimizes the allocation of computational resources while maintaining accuracy, achieving regionally differentiated selection of interpolation methods.

[0062] S242, calculate the local mapping error in the high-frequency sensitive region.

[0063] Local mapping error can be understood as the difference between the interpolation result at the acoustic mesh node and the theoretical vibration velocity value at the corresponding location on the structural mesh within a high-frequency sensitive region. Methods for calculating this error include: selecting some structural nodes within the high-frequency sensitive region that did not participate in the interpolation construction as verification points; substituting the coordinates of the verification points into the interpolation function to obtain predicted values; comparing these predicted values ​​with the original vibration values ​​of the verification points; and calculating the absolute or relative error. Alternatively, a cross-validation method can be used, where some structural nodes are removed each time, and the values ​​of the removed nodes are predicted using interpolation with the remaining nodes, and the error distribution is statistically analyzed. Finally, error statistics for this region (such as maximum error and root mean square error) are obtained, quantifying the accuracy of the interpolation mapping and providing an objective basis for determining whether further mesh refinement is needed.

[0064] S243, based on the difference between the local mapping error of the high-frequency sensitive area and the preset accuracy requirement, adjust the mesh density of the high-frequency sensitive area, and recalculate the mapping and error until the local mapping error of the high-frequency sensitive area meets the preset accuracy requirement.

[0065] It is understandable that the preset accuracy requirement can be a maximum permissible error value (e.g., vibration velocity amplitude error not exceeding 5%) or a root mean square error threshold. If the local mapping error exceeds the preset accuracy requirement, it indicates that the current mesh density is insufficient to accurately capture vibration changes, and the mesh needs to be refined. Refinement is achieved by reducing the target size of the acoustic mesh, for example, by multiplying the current mesh size by a coefficient less than 1 (e.g., 0.7). Then, based on the new mesh size, the acoustic mesh for the high-frequency sensitive region is regenerated, and the mapping in step S241 and the error calculation in step S242 are re-executed. This process is repeated until the local mapping error meets the preset accuracy requirement, ensuring that the mapping accuracy of the high-frequency sensitive region meets the requirements, while avoiding the waste of computational resources caused by excessive refinement at once.

[0066] For example, in step S243, based on the difference between the local mapping error of the high-frequency sensitive region and the preset accuracy requirement, the mesh density of the high-frequency sensitive region is adjusted, and the mapping and error calculation are re-performed until the local mapping error of the high-frequency sensitive region meets the preset accuracy requirement, including: S2431, if the local mapping error in the high-frequency sensitive area exceeds the first preset threshold, the encryption coefficient is calculated based on the ratio of the difference between the local mapping error and the first preset threshold.

[0067] It is understandable that the first preset threshold is a key upper limit in the preset accuracy requirements, such as 80% or 90% of the maximum permissible error. If the local mapping error exceeds this threshold, it indicates that refinement is required. The refinement coefficient can be calculated as: refinement coefficient = (local mapping error / first preset threshold) raised to a power (such as a square root), or simply linearly scaled: refinement coefficient = first preset threshold / local mapping error (less than 1). The refinement coefficient is used to determine the proportion of mesh size reduction. The technical effect of this step is that it quantifies and maps the degree of error exceeding the limit to the refinement magnitude, making the mesh adjustment adapt to the error magnitude and avoiding empirical blind adjustments.

[0068] S2432, reduce the encryption size of the high-frequency sensitive area according to the encryption coefficient, and regenerate the acoustic mesh.

[0069] It can be understood that the encryption size refers to the target side length of the acoustic mesh. Multiplying the current encryption size by an encryption coefficient yields a new, smaller encryption size. For example, if the current encryption size is 5mm and the encryption coefficient is 0.8, the new size is 4mm. Then, based on the new encryption size, the acoustic mesh is regenerated in the high-frequency sensitive region (e.g., using Delaunay triangulation or wavefront advancement), generating denser mesh cells. During mesh regeneration, the mesh density is adaptively adjusted according to the error magnitude, achieving on-demand encryption and avoiding uniform or over-encryption.

[0070] S2433, based on the regenerated acoustic mesh, repeat the mapping and error calculation until the local mapping error in the high-frequency sensitive area does not exceed the first preset threshold.

[0071] Understandably, the newly generated acoustic mesh is used to perform mapping and error calculation again, and then it is determined whether the local mapping error is ≤ a first preset threshold. If it still exceeds the threshold, the iterative process is repeated until the condition is met. During the iteration process, the density coefficient may become smaller and the mesh may become denser. A maximum number of iterations or a minimum mesh size limit can be set to prevent infinite iteration. Through iterative approximation, the optimal mesh density that meets the accuracy requirements is finally obtained, achieving a balance between accuracy and efficiency.

[0072] S300 performs radiated noise simulation calculations based on an acoustic mesh whose mapping error meets the mapping accuracy requirements, and outputs the simulation results.

[0073] As can be understood, radiated noise simulation calculation refers to solving the sound field radiated outward by the valve cover using the acoustic boundary element method or finite element method, with the interpolated vibration velocity on the acoustic mesh as the boundary condition. The calculated results include: the spatial distribution of sound pressure level, radiated sound power, directivity map, and sound pressure frequency response curve at a specified field point. The simulation results can be used to evaluate the NVH performance of the valve cover, identify the main noise contribution areas, and guide structural optimization design. In existing technologies, due to the non-coincidence of the spatial positions of the structural mesh and acoustic mesh nodes and the lack of high-precision mapping and error control, direct radiated noise simulation often leads to distortion in high-frequency results, failing to accurately reflect the true noise characteristics of the valve cover. This method fundamentally solves the high-frequency interpolation distortion problem caused by non-coincidence of node positions by identifying high-frequency sensitive areas, differentially refining the mesh, performing high-precision interpolation in zones, and iterative error control. Therefore, the acoustic mesh and the vibration velocity boundary conditions obtained at this time have high mapping accuracy, and the radiated noise simulation calculation results based on this are realistic and reliable. The output simulation results not only provide an accurate basis for the NVH performance evaluation of the valve cover, but also provide reliable guidance for the subsequent low-noise structural design.

[0074] Corresponding to the automotive valve cover NVH performance analysis method in the above embodiments, this application also provides an automotive valve cover NVH performance analysis device, the various units of which can implement the various steps of the automotive valve cover NVH performance analysis method. Figure 4 The diagram shows a structural block diagram of the automotive valve cover NVH performance analysis device provided in an embodiment of this application. For ease of explanation, only the parts related to the embodiment of this application are shown.

[0075] Reference Figure 4 The automotive valve cover NVH performance analysis device includes: The acquisition unit is used to perform structural vibration response analysis based on the finite element model of the valve cover, and to acquire the spatial coordinates and vibration response data of each node on the surface of the valve cover structure. The mapping unit is used to generate an acoustic mesh based on the spatial coordinates and vibration response data of each node and to interpolate and map the structural vibration response data. The local density of the acoustic mesh is adjusted iteratively until the mapping error meets the preset accuracy requirements. The output unit is used to perform radiated noise simulation calculations based on an acoustic mesh that meets the mapping accuracy requirements according to the mapping error, and outputs the simulation results.

[0076] It should be noted that the information interaction and execution process between the above-mentioned devices / units are based on the same concept as the method embodiments of this application. For details on their specific functions and technical effects, please refer to the method embodiments section, and they will not be repeated here.

[0077] Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the above-described division of functional units and modules is merely an example. In practical applications, the above functions can be assigned to different functional units and modules as needed, that is, the internal structure of the device can be divided into different functional units or modules to complete all or part of the functions described above. The functional units and modules in the embodiments can be integrated into one processing unit, or each unit module can exist physically separately, or two or more unit modules can be integrated into one unit. The integrated unit can be implemented in hardware or as a software functional unit. Furthermore, the specific names of the functional units and modules are only for easy differentiation and are not intended to limit the scope of protection of this application. The specific working process of the units and modules in the above device can be referred to the corresponding process in the foregoing method embodiments, and will not be repeated here.

[0078] This application also provides an electronic device. Figure 5 This is a schematic diagram of the structure of an electronic device provided in an embodiment of this application. Figure 5 As shown, the electronic device 6 of this embodiment includes: at least one processor 60 ( Figure 5 Only one is shown in the image), at least one memory 61 ( Figure 5 (Only one is shown in the image) and a computer program 62 stored in the at least one memory 61 and executable on the at least one processor 60, wherein when the processor 60 executes the computer program 62, it causes the electronic device 6 to perform the steps in any of the above embodiments of the automotive valve cover NVH performance analysis method, or causes the electronic device 6 to perform the functions of each unit in the above system embodiments.

[0079] For example, the computer program 62 may be divided into one or more units, which are stored in the memory 61 and executed by the processor 60 to complete this application. The one or more units may be a series of computer program instruction segments capable of performing a specific function, which describe the execution process of the computer program 62 in the electronic device 6.

[0080] Electronic device 6 can be a computing device or terminal device such as a mobile phone, tablet computer, desktop computer, laptop, handheld computer, and cloud server. This electronic device may include, but is not limited to, a processor 60 and a memory 61. Those skilled in the art will understand that... Figure 5 This is merely an example of electronic device 6 and does not constitute a limitation on electronic device 6. It may include more or fewer components than shown, or combine certain components, or different components, such as input / output devices, network access devices, buses, etc.

[0081] The processor 60 can be a Central Processing Unit (CPU), or it can be other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), field-programmable gate arrays (FPGAs), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. The general-purpose processor can be a microprocessor or any conventional processor.

[0082] In some embodiments, the memory 61 may be an internal storage unit of the electronic device 6, such as a hard disk or memory of the electronic device 6. In other embodiments, the memory 61 may be an external storage device of the electronic device 6, such as a plug-in hard disk, smart media card (SMC), secure digital (SD) card, flash card, etc., equipped on the electronic device 6. Furthermore, the memory 61 may include both internal and external storage units of the electronic device 6. The memory 61 is used to store the operating system, applications, bootloader, data, and other programs, such as the program code of the computer program. The memory 61 can also be used to temporarily store data that has been output or will be output.

[0083] This application also provides a computer-readable storage medium storing a computer program that, when executed by a processor, implements the steps in any of the above method embodiments.

[0084] This application provides a computer program product that, when run on an electronic device, causes the electronic device to perform the steps in any of the above method embodiments.

[0085] If the integrated unit is implemented as a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, all or part of the processes in the methods of the above embodiments of this application can be implemented by a computer program instructing related hardware. The computer program can be stored in a computer-readable storage medium, and when executed by a processor, it can implement the steps of the various method embodiments described above. The computer program includes computer program code, which can be in the form of source code, object code, executable files, or certain intermediate forms. The computer-readable medium can include at least: any entity or device capable of carrying computer program code to an electronic device, a recording medium, a computer memory, a read-only memory (ROM), a random access memory (RAM), an electrical carrier signal, a telecommunication signal, and a software distribution medium. Examples include USB flash drives, portable hard drives, magnetic disks, or optical disks.

[0086] In the above embodiments, the descriptions of each embodiment have different focuses. For parts that are not described in detail or recorded in a certain embodiment, please refer to the relevant descriptions of other embodiments.

[0087] Those skilled in the art will recognize that the units and algorithm steps of the various examples described in conjunction with the embodiments disclosed herein can be implemented in electronic hardware, or a combination of computer software and electronic hardware. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of this application.

[0088] In the embodiments provided in this application, it should be understood that the disclosed automotive valve cover NVH performance analysis method can be implemented in other ways. For example, the embodiments of the automotive valve cover NVH performance analysis method described above are merely illustrative. For instance, the division of units is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. Furthermore, the coupling or direct coupling or communication connection shown or discussed may be an indirect coupling or communication connection through some interfaces, devices, or units, and may be electrical, mechanical, or other forms.

[0089] The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the units can be selected to achieve the purpose of this embodiment according to actual needs.

[0090] The above-described embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this application, and should all be included within the protection scope of this application.

Claims

1. A method for analyzing the NVH performance of automotive valve cover, characterized in that, include: Structural vibration response analysis was performed based on the finite element model of the valve cover to obtain the spatial coordinates and vibration response data of each node on the surface of the valve cover structure. Based on the spatial coordinates and vibration response data of each node, an acoustic mesh is generated and the structural vibration response data is interpolated and mapped. The local density of the acoustic mesh is iteratively adjusted until the mapping error meets the preset accuracy requirements. The radiated noise is simulated and calculated based on an acoustic mesh whose mapping error meets the mapping accuracy requirements, and the simulation results are output.

2. The method as described in claim 1, characterized in that, The structural vibration response analysis based on the finite element model of the valve cover is performed to obtain the spatial coordinates and vibration response data of each node on the surface of the valve cover structure, including: Obtain a finite element model of the valve cover; wherein the finite element model includes the valve cover body structure and surrounding connecting components; Boundary conditions and load excitations are applied to the finite element model, and the vibration response of the finite element model within a preset frequency range is calculated; the load excitations include dynamic loads under engine operating conditions. Based on the vibration response, the spatial coordinates and vibration velocity amplitude of each node on the surface of the valve cover structure are extracted, and the vibration velocity amplitude of each node is determined as the vibration response data corresponding to each node.

3. The method as described in claim 1, characterized in that, The process of generating an acoustic mesh based on the spatial coordinates and vibration response data of each node, interpolating and mapping the structural vibration response data, and iteratively adjusting the local density of the acoustic mesh until the mapping error meets the preset accuracy requirements includes: Based on the spatial coordinates and vibration response data of each node, calculate the spatial rate of change of the vibration response of each node on the surface of the valve cover structure. Based on the spatial change rate, high-frequency sensitive regions whose spatial change rate exceeds a preset threshold are identified; A dense acoustic mesh is used in the high-frequency sensitive area, while a standard acoustic mesh is used in the non-high-frequency sensitive area; Vibration response data is mapped to acoustic mesh nodes, the local mapping error of the high-frequency sensitive region is calculated, and the mesh density of the high-frequency sensitive region is adjusted according to the local mapping error until the local mapping error of the high-frequency sensitive region meets the preset accuracy requirements; wherein the high-frequency sensitive region adopts a first interpolation accuracy, and the non-high-frequency sensitive region adopts a second interpolation accuracy, and the first interpolation accuracy is higher than the second interpolation accuracy.

4. The method as described in claim 3, characterized in that, The step of calculating the spatial rate of change corresponding to the vibration response of each node on the valve cover structure surface based on the spatial coordinates and vibration response data of each node includes: Based on the spatial coordinates and vibration response data of each node, calculate the rate of change of vibration velocity of each node in the three spatial directions; The spatial variation rate of each node is obtained based on the rate of change of vibration velocity in the three spatial directions.

5. The method as described in claim 3, characterized in that, The step of identifying high-frequency sensitive regions whose spatial change rate exceeds a preset threshold based on the spatial change rate includes: Calculate the arithmetic mean of the spatial change rates of all nodes; Nodes with a spatial change rate greater than twice the arithmetic mean are marked as candidate nodes; High-frequency sensitive regions are determined based on the candidate nodes and preset thresholds.

6. The method as described in claim 5, characterized in that, The step of determining the high-frequency sensitive region based on the candidate nodes and the preset threshold includes: Perform connectivity analysis on the candidate nodes, group interconnected candidate nodes into the same connectivity region, and calculate the area of ​​each connectivity region; Connected components with an area smaller than a preset area threshold are removed, and the remaining connected components are designated as high-frequency sensitive regions.

7. The method as described in claim 3, characterized in that, The process of mapping vibration response data to acoustic mesh nodes, calculating the local mapping error of the high-frequency sensitive region, and adjusting the mesh density of the high-frequency sensitive region based on the local mapping error until the local mapping error of the high-frequency sensitive region meets the preset accuracy requirements includes: Based on the encrypted acoustic grid and the standard acoustic grid, vibration response data is mapped to acoustic grid nodes; wherein, the high-frequency sensitive region uses radial basis function interpolation, and the non-high-frequency sensitive region uses second-order shape function interpolation; Calculate the local mapping error of the high-frequency sensitive region; Based on the difference between the local mapping error of the high-frequency sensitive area and the preset accuracy requirement, the grid density of the high-frequency sensitive area is adjusted, and the mapping and error calculation are re-performed until the local mapping error of the high-frequency sensitive area meets the preset accuracy requirement.

8. The method as described in claim 7, characterized in that, The step of adjusting the grid density of the high-frequency sensitive region based on the difference between the local mapping error of the high-frequency sensitive region and the preset accuracy requirement, and recalculating the mapping and error until the local mapping error of the high-frequency sensitive region meets the preset accuracy requirement, includes: If the local mapping error of the high-frequency sensitive area exceeds the first preset threshold, the encryption coefficient is calculated based on the ratio of the difference between the local mapping error and the first preset threshold. The encryption size of the high-frequency sensitive region is reduced according to the encryption coefficient, and the acoustic mesh is regenerated. The mapping and error calculation are repeated based on the regenerated acoustic mesh until the local mapping error of the high-frequency sensitive region does not exceed the first preset threshold.

9. A device for analyzing the NVH performance of automotive valve cover, characterized in that, include: The acquisition unit is used to perform structural vibration response analysis based on the finite element model of the valve cover, and to acquire the spatial coordinates and vibration response data of each node on the surface of the valve cover structure. The mapping unit is used to generate an acoustic mesh based on the spatial coordinates and vibration response data of each node and to interpolate and map the structural vibration response data. The local density of the acoustic mesh is adjusted iteratively until the mapping error meets the preset accuracy requirements. The output unit is used to perform radiated noise simulation calculations based on an acoustic mesh that meets the mapping accuracy requirements according to the mapping error, and outputs the simulation results.

10. An electronic device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, When the processor executes the computer program, it implements the steps of the method as described in any one of claims 1 to 8.

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