Apparatus and method for analyzing vibration noise of a panel member of an automobile

Abstract

The present invention obtains a vehicle body model (200) (13), sets a plurality of division regions (15) on the vehicle body model (200), sets a vibration noise reduction object plate member model (17), selects a vibration mode and a peak frequency of an equivalent radiation power of the vibration noise reduction object plate member model by vibration analysis of the vehicle body model (200) (19), changes the weight of one or more division regions to obtain the peak frequency of the equivalent radiation power of the vibration noise reduction object plate member model (21), calculates the contribution degree of the weight of each division region to the obtained peak frequency of the equivalent radiation power (S23), and determines a site for lightening the vehicle body based on the contribution degree of the weight of each division region (25) to reduce the vibration noise from the plate member of the automobile.

Description

Technical Field

[0001] This invention relates to an apparatus and method for analyzing the reduction of vibration and noise in panel parts of automobiles, and particularly to an apparatus and method for analyzing the reduction of vibration and noise in panel parts caused by vibrations from vibration sources and noise sources of the automobile, and to identifying parts of the automobile body that can achieve weight reduction. Background Technology

[0002] Automotive panel components such as the floor panel, dash lower panel, and roof panel are manufactured by pressing steel sheets, aluminum alloy sheets, or sheets plated with Zn alloy, into shape. The vibration of these panel components contributes to road noise and booming noise, worsening interior vehicle noise. Therefore, reducing interior noise is a key challenge in improving a vehicle's quietness and commercial value.

[0003] Figure 2 The causes of vibration noise in the plate member 103 of the automobile 100, which is provided with body frame parts 101 and plate member 103 constituting the body frame, are: (a) vibration input from the engine 105a of the automobile 100 or from the road surface or the like via the tire 105b when driving; (b) transmission on the body frame parts 101, causing (c) vibration of the plate member 103.

[0004] Conventionally, applying reinforcing ribs to the (c) panel component 103 has been an effective technique for reducing vibration noise. Furthermore, Non-Patent Document 1 discloses a technique for determining the optimal position of the reinforcing ribs applied to the panel component, which is the target for vibration noise reduction, as topography optimization. However, in automobiles where aesthetics are important, directly applying reinforcing ribs to outer panel components such as the roof panel is difficult, and there are also problems due to interference with adjacent inner panel components. Therefore, countermeasures are required for the (b) frame component 101, which is located in the vibration propagation path of the automobile.

[0005] Therefore, several solutions have been proposed to reduce the vibration of the panel members by implementing countermeasures against the frame components of the vibration transmission path of the automobile. For example, Patent Document 1 discloses a technology that suppresses the vibration of the roof panel even when resonance occurs on the body frame due to engine vibration, etc. In the technology disclosed in Patent Document 1, in a vehicle roof structure in which a roof panel is joined to a plurality of roof bows provided at predetermined intervals along the longitudinal direction of the vehicle body, the width of the central portion of one roof bow and at least one roof bow adjacent to that roof bow in the width direction of the vehicle body is made wider than the width of the other roof bows.

[0006] Existing technical documents

[0007] Patent documents

[0008] Patent Document 1: Japanese Patent Application Publication No. 2007-186086

[0009] Non-patent literature

[0010] Non-patent document 1: "Altair OptiStruct, a software for constructing optimal designs", [online], [searched on July 18, 2019], Internet<URL:https: / / www.terrabyte.co.jp / Hyper / OptiStruct-3.htm> Summary of the Invention

[0011] The problem that the invention aims to solve

[0012] However, the technology disclosed in Patent Document 1 has the problem of significantly increasing weight due to forming a wide central section of the roof arch. Furthermore, if the shape of the frame components is significantly altered, interference with other components may occur, making implementation difficult. Therefore, a technology is desired that can efficiently reduce vibration and noise of the panel components while achieving vehicle body weight reduction without significantly altering the component shapes.

[0013] The present invention was made in view of the above-mentioned problems, and its object is to provide an analysis apparatus and method for reducing vibration noise of plate components caused by vibration from vibration sources in automobiles and for identifying parts of the automobile body that can achieve lightweighting.

[0014] Methods for solving problems

[0015] The present invention discloses a vibration noise reduction analysis device for a panel component of an automobile, which reduces vibration noise of the panel component caused by vibration from a vibration source in the automobile and identifies parts where lightweighting of the automobile body is possible. The device comprises: a body model acquisition unit that acquires an automobile body model, the body model having a body frame part model and a panel part model formed by modeling the frame components and panel components constituting the automobile body using a mesh model, and an excitation position for inputting vibration from the vibration source; and a division region setting unit that sets multiple division regions on the body model based on the body frame part model and the panel part model. The system includes: a vibration noise reduction target plate component model setting unit, which, according to instructions from the operator, sets the plate component model of the plate component model that is the target for vibration noise reduction as the vibration noise reduction target plate component model in the vehicle body model; a vibration mode and equivalent radiated power peak frequency selection unit, which performs vibration analysis using the vehicle body model to determine the vibration behavior of the vibration noise reduction target plate component model and the frequency characteristics of the equivalent radiated power as an indicator of vibration noise, and selects the vibration mode that contributes significantly to vibration noise and the peak frequency of the equivalent radiated power corresponding to that vibration mode; and a region weight change peak frequency acquisition unit, which changes the weight of one or more regions in the vehicle body model, performs vibration analysis according to the combination of the weights of the regions in the vehicle body model, and obtains the peak frequency of the equivalent radiated power of the vibration noise reduction target plate component model under the vibration mode selected by the vibration mode and equivalent radiated power peak frequency selection unit.The weight contribution calculation unit for each segmented region performs multivariate analysis, using the peak frequency of the equivalent radiated power of the vibration and noise reduction target panel component model as the objective variable and the weight of the segmented region as the explanatory variable, to calculate the degree of contribution of the weight of the segmented region to the peak frequency of the equivalent radiated power of the vibration and noise reduction target panel component model; and the vibration and noise reduction lightweighting part determination unit, based on the calculated contribution degrees of each segmented region, determines the parts of the vehicle body to be lightweighted to reduce vibration and noise from the panel component designated as the vibration and noise reduction target.

[0016] The present invention discloses a method for reducing vibration noise in a vehicle's panel components. To reduce vibration noise in panel components caused by vibrations from a vibration source within the vehicle and to determine the parts of the vehicle body that can achieve weight reduction, a computer performs the following steps: a vehicle body model acquisition step, acquiring a vehicle body model that includes a skeleton component model and a panel component model, each modeled using a mesh to represent a skeleton component and a panel component constituting the vehicle body, and setting an excitation unit that inputs vibrations from the vibration source; a region division step, setting multiple regions on the vehicle body model based on the skeleton component model and the panel component model; a vibration noise reduction target panel component model setting step, setting the panel component model of the panel component model designated as the target for vibration noise reduction as the vibration noise reduction target panel component model in the vehicle body model; and a vibration mode / equivalent radiated power peak frequency selection step, performing vibration analysis using the vehicle body model to determine the vibration behavior of the vibration noise reduction target panel component model and the frequency characteristics of the equivalent radiated power as an indicator of vibration noise. The process involves: selecting a vibration mode that significantly contributes to vibration noise and the peak frequency of the equivalent radiated power corresponding to that vibration mode; obtaining the peak frequency of the vibration noise reduction target panel component model by changing the weight of one or more divisions in the vehicle body model, performing vibration analysis based on the combination of the weights of the divisions in the vehicle body model, and obtaining the peak frequency of the equivalent radiated power of the vibration noise reduction target panel component model under the vibration mode selected in the vibration mode and equivalent radiated power peak frequency selection step; calculating the contribution of the weight of the divisions to the peak frequency of the equivalent radiated power of the vibration noise reduction target panel component model by performing multivariate analysis with the peak frequency of the equivalent radiated power of the vibration noise reduction target panel component model as the objective variable and the weight of the divisions as the explanatory variable; and determining the lightweight parts for vibration noise reduction by determining the parts in the vehicle body to be lightweighted to reduce vibration noise from the panel component set as the vibration noise reduction target based on the calculated contribution of each division.

[0017] Alternatively, in the step of calculating the weight contribution of the divided regions, a relationship between the peak frequency of the equivalent radiated power of the vibration noise reduction target plate component model and the weight of each divided region is derived. The weight of at least one or more of the divided regions is changed and assigned in the derived relationship to predict the peak frequency of the equivalent radiated power of the vibration noise reduction target plate component model, and the parts in the vehicle body to be lightweighted are determined to reduce the vibration noise of the plate components caused by vibration from the vibration source in the vehicle.

[0018] Alternatively, in the step of calculating the weight contribution of the divided regions, a relationship is derived between the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model and the weight of each divided region. A divided region for which the plate thickness is to be calculated is selected, and the derived relationship is assigned the weights of the other divided regions excluding this divided region and the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model. The weight of the selected divided region is calculated, and the plate thickness of the skeleton component model and / or plate component model constituting the divided region is calculated based on the calculated weight of the divided region.

[0019] Alternatively, when calculating the weight of the selected partitioned region using the relationship, a correction value is assigned to the relationship and the weight of the partitioned region is calculated. The correction value corrects the impact of the change in the weight of the partitioned region on the peak frequency of the equivalent radiated power.

[0020] The effects of the invention

[0021] According to the present invention, by calculating the contribution of the weight of the divided area set in the vehicle body model to the peak frequency of the equivalent radiated power of the plate component model corresponding to the plate component that is set as the object of vibration and noise reduction, and by performing weight reduction on the vehicle body based on the calculated contribution, it is possible to determine the parts that contribute to the reduction of vibration and noise from the plate component, and to achieve both the reduction of vibration and noise from the plate component and the weight reduction of the vehicle body. Attached Figure Description

[0022] Figure 1 This is a block diagram of a vibration noise reduction analysis device for a car panel component according to Embodiment 1 of the present invention.

[0023] Figure 2 This is a diagram illustrating the vibration noise of a plate component caused by vibration transmitted from the vibration source of a car, which is the subject of this invention.

[0024] Figure 3 This is a diagram showing an example of a vehicle body model that is set as the object of analysis in Embodiments 1 to 3 of the present invention.

[0025] Figure 4 This is a perspective view obtained from above of the vehicle body model, which is set as the analysis object in Embodiments 1 to 3 of the present invention and has a skeleton component model and a plate component model.

[0026] Figure 5 This is a perspective view obtained from below of a vehicle body model that is set as the analysis object in Embodiments 1 to 3 of the present invention and has a skeleton component model and a plate component model.

[0027] Figure 6This is a perspective view obtained from above, showing the vehicle body model with divided areas as described in Embodiments 1 to 3 of the present invention.

[0028] Figure 7 This is a perspective view obtained from below, showing a vehicle body model with divided areas in an embodiment of the present invention.

[0029] Figure 8 This is a diagram showing an example of the displacement of the vehicle body model generated by vibration in Embodiments 1 to 3 of the present invention.

[0030] Figure 9 This is a diagram illustrating an example of the frequency characteristics of the equivalent radiated power of the middle floor model of the vehicle body model in Embodiments 1 to 3 of the present invention.

[0031] Figure 10 This is a flowchart illustrating the processing flow of the vibration noise reduction analysis method for a car panel component according to Embodiment 1 of the present invention. Detailed Implementation

[0032] Before describing the vibration noise reduction analysis device and analysis method for a car's plate component according to an embodiment of the present invention, the car that is the analysis object in the present invention will be described.

[0033] <Car set as object>

[0034] like Figure 2 As shown, the automobile 100, which is the subject of analysis in this invention, has a frame component 101 and a plate component 103, and a vibration source 105 that imparts vibration (periodic load) to the body of the automobile 100.

[0035] The frame component 101 is a component that constitutes the body frame of the automobile, such as the roof rail, A-pillar, B-pillar, C-pillar, and side sill. The plate component 103 is an outer panel or inner panel that is a sheet structure component, such as the roof panel and floor panel (e.g., middle floor, rear floor). The vibration source 105 includes, for example, the engine 105a and tires 105b. When the automobile is in motion, vibrations from the road surface are input via tires 105b to excitation points such as the front suspension mounting part 106 and the rear suspension mounting part 107.

[0036] The following description of Embodiments 1 to 3 of the present invention pertains to examples in which the middle floor 103a of the automobile 100 is designed as a plate component for reducing vibration and noise. However, the present invention may also designate other plate components (roof or rear floor) as targets for reducing vibration and noise.

[0037] [Implementation Method 1]

[0038] <Vibration and noise reduction analysis device for automotive panel components>

[0039] The structure of the vibration noise reduction analysis device for a car body panel component according to Embodiment 1 of the present invention (hereinafter referred to simply as "vibration noise reduction analysis device") will be described below.

[0040] The vibration noise reduction analysis device 1 of this embodiment reduces the vibration noise emitted by the car 100 ( Figure 2 The vibration noise from the plate component 103 caused by the vibration of the vibration source 105 in the vehicle body 100 is identified by the device that determines the parts that can achieve weight reduction of the vehicle body 100. Figure 1 For example, the vibration noise reduction analysis device 1 is composed of a PC (personal computer) and has a display device 3, an input device 5, a memory storage device 7, a working data memory 9, and an arithmetic processing unit 11.

[0041] Furthermore, the display device 3, input device 5, storage device 7, and working data storage device 9 are connected to the arithmetic processing unit 11, and each performs its respective function according to instructions from the arithmetic processing unit 11. Hereinafter, taking the case where the floor 103a is the target for vibration and noise reduction as an example, the structure of the vibration and noise reduction analysis device 1 will be described. The floor 103a is one of the panel components 103 of the automobile 100.

[0042] Display Devices

[0043] Display device 3 is used in displaying analysis results, etc., and is composed of liquid crystal monitors, etc.

[0044] Input Device

[0045] The input device 5 is used for displaying and indicating the vehicle body model file 30, and for the operator's condition input, etc., and consists of a keyboard, mouse, etc.

[0046] Storage Devices

[0047] Storage device 7 is used for storing various files such as vehicle body model file 30, and is composed of hard disk, etc.

[0048] Model car body 200 (reference) Figure 3 The vehicle model 200 includes multiple skeleton component models formed by modeling multiple skeleton components that constitute the vehicle body skeleton for automobile using meshes (two-dimensional elements and / or three-dimensional elements), and plate component models formed by modeling plate components using meshes (two-dimensional elements). It also includes an excitation unit for vibration input from vibration sources originating from the vehicle. Furthermore, the vehicle model file 30 stores various information about the vehicle model 200, including information related to the elements and nodes of the skeleton component models and plate component models, and information related to material properties.

[0049] Data Storage for Job Operations

[0050] The operational data storage 9 is used for the temporary storage and processing of data used in the arithmetic processing unit 11, and is composed of RAM (Random Access Memory) and the like.

[0051] Computational Processing Department

[0052] like Figure 1 As shown, the computational processing unit 11 includes a vehicle body model acquisition unit 13, a region setting unit 15, a vibration and noise reduction target plate component model setting unit 17, a vibration mode and equivalent radiated power peak frequency selection unit 19, a region weight change peak frequency acquisition unit 21, a region weight contribution calculation unit 23, and a vibration and noise reduction lightweight part determination unit 25, and is composed of a CPU (central processing unit) such as a PC. These units function by executing prescribed programs through the CPU. The functions of the above-mentioned units in the computational processing unit 11 will be explained below.

[0053] (Car Model Acquisition Department)

[0054] The vehicle body model acquisition unit 13 acquires a vehicle body model 200, which includes a frame component 101 and a plate component 103 of the vehicle 100 connected by a mesh (planar features and / or three-dimensional features). Figure 2 Each component is modeled as a skeleton component and a plate component, and each is equipped with an excitation unit.

[0055] exist Figures 3-5The image shows an example of a car body model 200 that includes a skeleton component model and a plate component model.

[0056] As an example of a skeleton component model, it includes an upper beam model 201, an A-column model 203, a B-column model 205, a C-column model 207, a middle floor member model 209, a rear floor side member model 211, and a rear floor cross member model 213, which are modeled using planar and / or three-dimensional elements.

[0057] As an example of a plate component model, in addition to the middle floor model 221, which is set as the object of vibration and noise reduction in this embodiment, there are also a roof model 223 and a rear floor model 225, which are modeled using planar elements. As an example of a vibration excitation unit, there is a vibration excitation unit 231, which is provided with a rear suspension mounting unit 107 for vibration input from the tires of the automobile.

[0058] The vehicle body model 200 can be obtained by reading element information and material property information from the vehicle body model file 30 stored in the storage device 7. It should be noted that the vibration excitation unit 231 in the vehicle body model 200 can save the information preset in the vehicle body model 200 in the vehicle body model file 30, or it can be set in the vehicle body model 200 according to the operator's instructions after the vehicle body model 200 is read from the vehicle body model file 30.

[0059] (Regional Designation Department)

[0060] The region setting unit 15 sets multiple regions in the body model 200 based on the skeleton component model and the plate component model.

[0061] exist Figure 6 and Figure 7 The diagram shows that 12 division areas D1 to D2 are set on the vehicle body model 200. 12Examples: D1. The roof is a region defined using roof model 223. D2. The upper side beam is a region defined using upper side beam model 201. D3. The rear quarter side is a region defined using wheel house model 247 and quarterinner model 245. D4. The rear quarter upper is a region defined using upper back panel model 241. D5. The trunk room opening is a region defined using lower back panel model 243. D6. The B-pillar is a region defined using B-pillar model 205.

[0062] D7. The rear floor is a region defined using rear floor model 225. D8. The middle floor is a region defined using middle floor model 221. D9. The A-pillar is a region defined using A-pillar model 203. 10 The middle floor beam is a region defined using the middle floor beam model 209. (D) 11 The rear floor longitudinal beams are defined using the rear floor longitudinal beam model 211, which divides the area. 12 The rear floor beam is a defined area created using the rear floor beam model 213.

[0063] D1. Roof, D7. Rear Floor, and D8. Middle Floor are all areas defined using only plate component models. D2. Upper Beam, D6. B-pillar, D9. A-pillar, D... 10 .middle floor beam, D 11 Rear floor longitudinal beam, D 12 The rear floor crossbeams are all areas defined using only the skeleton component model. D3. Rear side panel, D4. Rear upper panel, and D5. Luggage compartment opening are all areas that include both panel component models and skeleton component models.

[0064] The division regions set in the vehicle body model 200 using the division region setting unit 15 can be set as described above to take into account the processes of manufacturing the vehicle body, such as ASSY units (assembly units), skeleton component model units, and plate component model units. Alternatively, CAE (computer aided engineering) analysis methods such as sensitivity analysis can be used to set the division regions in the vehicle body model 200.

[0065] (Vibration and noise reduction target plate component model setting department)

[0066] The vibration and noise reduction target plate component model setting unit 17, according to instructions from the operator, sets the plate component model of the plate component model that is designated as the target for vibration and noise reduction as the vibration and noise reduction target plate component model on the vehicle body model 200. In this embodiment, the middle floor 103a of the automobile 100 ( Figure 2 ) is set as the target for vibration and noise reduction, and the middle floor model 221 in the plate component model of the body model 200 is selected. Figure 5 The model is set as a vibration and noise reduction target plate component model.

[0067] (Selected frequency of peak equivalent radiated power in vibration mode)

[0068] The vibration mode and equivalent radiated power peak frequency selection unit 19 performs vibration analysis using the vehicle body model 200 to determine the vibration behavior of the vibration noise reduction target plate component model and the frequency characteristics of the equivalent radiated power, which serves as an indicator of vibration noise. Then, the vibration mode and equivalent radiated power peak frequency selection unit 19 selects the vibration mode that contributes significantly to vibration noise and the peak frequency of the equivalent radiated power corresponding to that vibration mode.

[0069] For example, vibration analysis can be applied, such as frequency response analysis, vibration mode analysis, or vibration energy analysis.

[0070] In the vibration behavior of the vibration noise reduction target plate component model obtained by vibration analysis, there are vibration modes at the natural frequency. The vibration mode selected by the vibration mode-equivalent radiated power peak frequency selection unit 19 can be set as the vibration mode that contributes more to the vibration noise.

[0071] Furthermore, equivalent radiated power is an index representing the acoustic characteristics radiated from a vibrating plate surface, and is proportional to the product of the area of ​​the radiating plate surface and the square of the vibration speed of that plate surface. Therefore, the vibration mode-equivalent radiated power peak frequency selection unit 19 calculates the equivalent radiated power of the vibration noise reduction target plate component model using the following formula (1).

[0072] [Mathematical Expression 1]

[0073] ERP=η*(1 / 2)C*RHO*∑(A j *v i 2 )···(1)

[0074] In equation (1), η is the radiation loss coefficient, C is the acoustic wave velocity, RHO is the material density of the vibration noise reduction object plate component model, and A i The area of ​​mesh i in the object plate component model is reduced by vibration noise, v i It is the vibration velocity of grid i. Then, the vibration velocity v i Assign values ​​to each grid i obtained through vibration analysis.

[0075] exist Figure 8 The figure shows the displacement of the vibration generated on the vehicle body model 200. Figure 9 An example of the frequency characteristics of the equivalent radiated power of the floor model 221 is shown. In this embodiment, as... Figure 8 As shown, the primary vibration mode of the central part of the middle floor model 221, which involves relatively large ground vibration (large displacement), was selected. Then, according to... Figure 9 The peak frequency of the equivalent radiated power corresponding to the selected vibration mode was selected (=39.6Hz).

[0076] (Divided region weight change peak frequency acquisition unit)

[0077] The division area weight change peak frequency acquisition unit 21 changes the weight of one or more division areas in the vehicle body model 200 and performs vibration analysis based on the combination of the weights of the division areas. Then, the division area weight change peak frequency acquisition unit 21 acquires the peak frequency of the equivalent radiated power of the vibration noise reduction target plate component model under the vibration mode selected by the vibration mode-based equivalent radiated power peak frequency selection unit 19. Table 1 shows an example of a combination (level) formed by changing the weight of one or more division areas in the vehicle body model 200.

[0078] [Table 1]

[0079] (Table 1)

[0080]

[0081] Level 1 is for dividing regions D1 to D2. 12The levels are combinations where the weight of any one of the divisions remains unchanged. Levels 2 through 11 are combinations where the weight of any one of the divisions changes. Levels 12 through 22 are combinations where the weight of multiple divisions changes simultaneously. Furthermore, the values ​​recorded in the division column of Table 1 are weight ratios based on the weight of each division in the original vehicle body model 200. For example, level 2 sets the weight of division D1. Roof to 0.75 times the weight of D1. Roof in the original vehicle body model 200.

[0082] The level of the weight combination of the divided areas should be greater than the total number of divided areas set on the vehicle body model 200. The total combination can be set for the divided areas set on the vehicle body model, or the experimental design method can be used to set it efficiently.

[0083] (Calculation of weight contribution of divided regions)

[0084] The division region weight contribution calculation unit 23 performs a multivariate analysis, using the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model as the objective variable and the weight of the division region as the explanatory variable. Then, the division region weight contribution calculation unit 23 calculates the contribution of the weight of the division region to the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model.

[0085] In multivariate analysis, the regression model (relationship) uses the peak frequency (Y) as the objective variable and the partitioned region D as the explanatory variable. i weight (M) i The expression can be represented as follows, for example, the following equation (2) can be listed. It should be noted that, as shown in equation (3), M in equation (2) i Based on the division of region D before the weight change i weight ρ a Region D is defined based on the baseline. i The weight ratio. Additionally, M i Alternatively, it can be set to the region D before the weight change. i density ρ a Region D is defined based on the baseline. i density ρ b The ratio.

[0086] [Mathematical Expression 2]

[0087]

[0088] Then, the partial regression coefficient A in the relationship (Equation (2)) obtained by multivariate analysis in the division of regional weight contribution is calculated. i The value is used as the partitioning region D i The contribution to the peak frequency is calculated.

[0089] It should be noted that in multivariate analysis, the regression model uses the objective variable (Y) and explanatory variables (M) to represent the objective variable (Y). i The linear combination can be used to express the form of the linear combination, for example, the following equation (4) or equation (5) can be used.

[0090] [Mathematical Expression 3]

[0091]

[0092] In addition, the partial regression coefficient A in the regression model (Equation (2), Equation (4), Equation (5), etc.) is calculated using the weight contribution calculation part 23 of the divided region. i When calculating the coefficient of determination (COP) or the adjusted R-squared, the COP can be calculated. The COP or adjusted R-squared is an indicator of the goodness (degree of fit) of the target variable when the explanatory variables are substituted into the regression model. In this embodiment, if the adjusted R-squared is greater than 0.90, then the weight M of the partitioned region is used. i The regression model fits well enough in estimating the peak frequency Y.

[0093] (Identification of lightweight components to reduce vibration and noise)

[0094] The vibration and noise reduction lightweighting part determination unit 25 determines the parts of the automobile body to be lightweighted based on the contribution of each divided region calculated by the division region weight contribution calculation unit 23, so as to reduce the vibration and noise of the plate components that are set as the targets for vibration and noise reduction. That is, the vibration and noise reduction lightweighting part determination unit 25 uses the partial regression coefficient A of the relation (e.g., equation (2)) obtained by multivariate analysis. i Larger value partitioning region D i The corresponding parts in the car are identified as the parts to be weighted down in order to reduce the vibration and noise of the plate components that are the targets for vibration and noise reduction.

[0095] For the parts that are determined in this way to be lightweight, for example, the thickness of the frame components and / or plate components included in that part can be reduced. Then, by lightweighting in this way, the peak frequency of the vibration noise from the plate component, to which the vibration noise is to be reduced, becomes higher, which can prevent resonance with the vibration from the vibration source. In addition, it can move away from the frequency band that is easily perceived by humans, thereby reducing the vibration noise from the plate component.

[0096] <Analysis Methods for Reducing Vibration and Noise in Automotive Panel Components>

[0097] The following describes the structure of the vibration noise reduction analysis method for a car panel component according to Embodiment 1 of the present invention (hereinafter referred to simply as the "vibration noise reduction analysis method").

[0098] The vibration noise reduction analysis method of the embodiments of the present invention reduces, for example, Figure 2 The vibration noise of the plate components in a car equipped with a frame component and plate components, caused by vibration from a vibration source, is shown, and the parts of the car body that can be lightweighted are identified. For example... Figure 10 As shown, the vibration and noise reduction analysis method includes steps S1 (obtaining the vehicle body model), S3 (setting the region division), S5 (setting the vibration and noise reduction target plate component model), S7 (selecting the peak frequency of vibration mode and equivalent radiated power), S9 (obtaining the peak frequency of weight change in the divided region), S11 (calculating the weight contribution of the divided region), and S13 (determining the lightweight parts for vibration and noise reduction). The following is based on... Figure 10 The above steps are explained. It should be noted that in the following description, all the above steps utilize the vibration noise reduction and analysis device 1 of Embodiment 1 of the present invention, which is constructed using a computer. Figure 1 )implement.

[0099] Steps to Obtain a Car Body Model

[0100] like Figures 3-5 As an example, step S1 of obtaining the vehicle body model is the step of obtaining the vehicle body model 200, which is equipped with a mesh (planar features and / or three-dimensional features) to represent the vehicle 100 ( Figure 2 The skeleton component 101 and the plate component 103 () Figure 2 The vehicle body model is modeled from the skeleton component model and the plate component model of the vibration noise reduction analysis device 1, and is equipped with an excitation unit for vibration input from the vibration source. In this embodiment, the vehicle body model acquisition step S1 is performed by the vehicle body model acquisition unit 13 of the vibration noise reduction analysis device 1.

[0101] Steps for setting up regional divisions

[0102] The region setting step S3 is a step of setting multiple regions in the vehicle body model 200 based on the skeleton component model and the plate component model. In this embodiment, the region setting step S3 is performed by the region setting unit 15 of the vibration noise reduction analysis device 1.

[0103] The division region of the body model 200 set in step S3 can be set as an ASSY unit, a skeleton component model, or a plate component model unit that takes into account the manufacturing process of the body. Alternatively, CAE analysis methods such as sensitivity analysis can be used to set the division region in the body model 200.

[0104] Steps for Setting Up a Vibration and Noise Reduction Object Plate Component Model

[0105] The vibration and noise reduction target plate component model setting step S5 is a step of setting the plate component model of the plate component model in the vehicle body model 200, which is set as the target of vibration and noise reduction, as the vibration and noise reduction target plate component model. In this embodiment, the vibration and noise reduction target plate component model setting step S5 is performed by the vibration and noise reduction target plate component model setting unit 17 of the vibration and noise reduction analysis device 1.

[0106] Steps for Selecting the Peak Frequency of Vibration Mode and Equivalent Radiated Power

[0107] The vibration mode / equivalent radiated power peak frequency selection step S7 involves performing vibration analysis using the vehicle body model 200 to determine the vibration behavior of the vibration noise reduction target panel component model and the frequency characteristics of the equivalent radiated power, which serves as an indicator of vibration noise. The step then selects the vibration mode that contributes significantly to vibration noise and the peak frequency of the equivalent radiated power corresponding to that vibration mode. In this embodiment, the vibration mode / equivalent radiated power peak frequency selection step S7 is performed by the vibration mode / equivalent radiated power peak frequency selection unit 19 of the vibration noise reduction analysis device 1.

[0108] As a vibration analysis, for example, the vibration behavior of the vibration noise reduction target plate component model can be determined by applying frequency response analysis, vibration mode analysis, and vibration energy analysis. In the vibration behavior of the vibration noise reduction target plate component model determined by vibration analysis, vibration modes exist at their natural frequencies. In the vibration mode / equivalent radiated power peak frequency selection step S7, the vibration mode that contributes significantly to the vibration noise is selected. For example, a primary vibration mode that vibrates significantly in the central part of the vibration noise reduction target plate component model can be selected.

[0109] In addition, based on the vibration behavior of the object plate component model obtained by vibration analysis, the equivalent radiated power is calculated according to the above equation (1).

[0110] Steps for Obtaining Peak Frequency of Weight Changes in Divided Regions

[0111] Step S9, which involves obtaining the peak frequency of the weight change in the divided areas, involves changing the weight of one or more divided areas in the vehicle body model 200, performing vibration analysis based on the combination of the weights of the divided areas, and obtaining the peak frequency of the equivalent radiated power of the vibration noise reduction target plate component model under the vibration mode selected in step S7, which is based on the vibration mode and equivalent radiated power peak frequency selection. In this embodiment 1, step S9, which involves obtaining the peak frequency of the weight change in the divided areas, is performed by the peak frequency acquisition unit 21 of the vibration noise reduction analysis device 1.

[0112] Changing the weight of one or more divisions in the vehicle body model 200 means changing the weight of one division or changing the weight of multiple divisions simultaneously.

[0113] Furthermore, the level of the weight combination of the divided regions in the vehicle body model only needs to be greater than the total number of divided regions set on the vehicle body model 200. The divided regions can be set using the total combination method, or the experimental design method can be used to set them efficiently.

[0114] Steps for calculating the weight contribution of different regions

[0115] Step S11, which calculates the weight contribution of the partitioned region, involves performing a multivariate analysis using the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model as the objective variable and the weight of the partitioned region as the explanatory variable. The result is a calculation of the contribution of the weight of the partitioned region to the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model. In this embodiment 1, step S11 is performed by the partitioned region weight contribution calculation unit 23 of the vibration and noise reduction analysis device 1.

[0116] The relationship (regression model) derived through multivariate analysis is used as the peak frequency (Y) as the objective variable and the region division D as the explanatory variable. i weight (M) i The expression can be represented by ), for example, it can be listed as equation (2), equation (4) or equation (5) above.

[0117] Then, the partial regression coefficient A in equation (2), (4), or (5) obtained through multivariate analysis is calculated by dividing the weight contribution of the regions into sections 23. i As each of the divided regions D i Contribution to peak frequency.

[0118] In addition, in step S11 of calculating the weight contribution of the divided regions, the partial regression coefficient A in the regression model (equations (2), (4), (5), etc.) is calculated. iIf the coefficient of determination is above 0.90 after the degrees of freedom are adjusted, the regression model fits well enough in estimating the peak frequency of the equivalent radiated power based on the weight of the divided region.

[0119] Steps for determining lightweight components to reduce vibration and noise

[0120] The vibration noise reduction and lightweighting part determination step S13 is a step of determining the parts of the vehicle body to be lightweighted based on the contribution of each divided region calculated in step S11 using the weight contribution of the divided regions, in order to reduce the vibration noise from the plate component designated as the target of vibration noise reduction. In this embodiment 1, the vibration noise reduction and lightweighting part determination step S13 is performed by the vibration noise reduction and lightweighting part determination unit 25 of the vibration noise reduction analysis device 1.

[0121] Specifically, the vibration and noise reduction lightweight part determination unit 25 calculates the partial regression coefficient A of the relationship (equation (2), etc.) obtained by multivariate analysis in step S11 by dividing the weight contribution of the region. i Larger value partitioning region D i The corresponding parts of the car were identified as those in the body that needed to be lightweighted to reduce vibration and noise.

[0122] Then, as a measure to reduce weight in the identified area, for example, the thickness of the frame component and / or plate component constituting that area can be reduced to decrease weight. By implementing this measure, the peak frequency of vibration noise from the plate component, to which vibration noise is to be reduced, can be increased, resonance with vibrations from the vibration source can be prevented, and vibration noise can be reduced by moving it away from the range that is easily perceived by humans.

[0123] [Implementation Method 2]

[0124] The vibration noise reduction analysis method for automotive panel components according to Embodiment 2 of the present invention derives a relationship between the peak frequency of the equivalent radiated power of the panel component model to be reduced and the weight of each segmented region in step S11 of the vibration noise reduction analysis method for automotive panel components according to Embodiment 1 of the present invention. In this derived relationship, the weight of at least one or more of the segmented regions is changed and assigned relative to the derived relationship, and the peak frequency of the equivalent radiated power of the panel component model to be reduced is predicted. The parts in the automotive body to be lightweighted are determined to reduce the vibration noise of the panel components caused by vibration from vibration sources in the automotive.

[0125] Therefore, by changing the weight of one or more pre-defined regions in the vehicle body model, and performing a vibration analysis to determine the frequency characteristics of the equivalent radiated power of the vibration noise reduction target plate component model, the relationship can be derived. Thus, by reducing the weight of the parts of the car including the frame components or plate components, an index of the peak frequency of the equivalent radiated power can be easily obtained. The peak frequency of the equivalent radiated power becomes an index of the vibration noise from the plate component designated as the vibration noise reduction target.

[0126] It should be noted that the relationship between the peak frequency of the equivalent radiated power of the vibration noise reduction target plate component model and the weight of the divided area set in the vehicle body model can be any one of the formulas (2), (4), and (5) shown in the above embodiment 1, without particular limitation.

[0127] [Implementation Method 3]

[0128] The vibration noise reduction analysis method for automotive panel components according to Embodiment 3 of the present invention derives the relationship between the peak frequency of the equivalent radiated power of the panel component model to be subject to vibration noise reduction and the weight of each division region in the step S11 of the division region weight contribution calculation in Embodiment 1 above. For a division region to which the derived relationship is to be used to calculate the plate thickness, the weight of the other division regions and the peak frequency of the equivalent radiated power of the panel component model to be subject to vibration noise reduction are assigned, and the weight of the division region is calculated. Based on the calculated weight of the division region, the plate thickness of the skeleton component model and / or panel component model constituting the division region is calculated.

[0129] In this way, by using the relationship between the peak frequency of the equivalent radiated power and the weight of the divided area, it is not only easy to select one or more parts for weight reduction as a measure to reduce vibration and noise, but also to estimate the effect of increasing the peak frequency of the equivalent radiated power by reducing the weight of one or more parts of the car body as a measure to reduce vibration and noise. This makes it easy to achieve both the reduction of vibration and noise from sheet metal parts and the weight reduction of the car body in car-body design.

[0130] It should be noted that, similar to Embodiment 2 above, the relationship between the peak frequency of the equivalent radiated power and the weight of the divided area set in the vehicle body model can be any one of the equations (2), (4), and (5) shown in Embodiment 1 above for the vibration and noise reduction target plate component model, and is not particularly limited.

[0131] However, if the peak frequency of the equivalent radiated power assigned to the relation is too high compared to the peak frequency of the equivalent radiated power obtained from the vehicle body model before changing the weight of each division region, the change in rigidity accompanying the weight change of the division region (e.g., excessive thinning of the plate thickness leading to a decrease in component rigidity) will have an excessive impact on the vibration behavior of the vibration noise reduction target plate component model. The peak frequency (Y) of the equivalent radiated power in Equation (2) and the weight (M) of the division region i The correlation (accuracy of the predicted value) can sometimes decrease.

[0132] Therefore, as another approach to the vibration noise reduction analysis method for the plate component of the automobile in Embodiment 3, it is preferable to calculate the weight of a division region by assigning the peak frequency of the equivalent radiated power and the weight of other division regions excluding the already calculated plate thickness to equation (6). Equation (6) assigns a correction value α to equation (2), which is the relationship between the peak frequency of the equivalent radiated power and the weight of the division region. i Thus, the correction value corrects the division region D of the weight change. i The impact of lightweighting on the peak frequency of equivalent radiated power. In this case, the residual sum of squares between the predicted values ​​calculated based on the relationship between the pre-modified plate thicknesses of multiple divided regions and the calculated values ​​obtained through vibration analysis can be used to determine the minimum correction value α. i And set.

[0133] [Mathematical Expression 4]

[0134] Y = A0 + ∑A i ×log2(1 / α i M i (6)

[0135] Preferably, the correction value α is calculated for each division region selected for determining the weight using the methods described above. i In equation (6), the weights of other partitioned regions can be assigned to α without modification. i =1, for other partitioned regions with significantly altered weights, a correction value α can be appropriately assigned. i .

[0136] Thus, according to other solutions of the vibration noise reduction analysis method for automotive panel components according to Embodiment 3, it is possible to take into account the change in rigidity caused by reducing the weight of the part where vibration noise reduction measures are implemented, and to accurately calculate the panel thickness of that part, thereby achieving both the reduction of vibration noise of panel components and the lightweighting of the vehicle body.

[0137] Example

[0138] Numerical experiments were conducted to verify the effectiveness of the vibration noise reduction analysis device and analysis method for the plate components of the automobile of the present invention, and these will be described below.

[0139] In numerical experiments, such as Figures 3-5 As shown, the vehicle body model 200 is set as the parsing object. The vehicle body model 200 is equipped with a mesh (planar features and / or solid features) to separate the skeleton component 101 and the plate component 103 of the vehicle 100. Figure 2 The plate component model and the skeleton component model are respectively modeled, and will be integrated with the rear suspension mounting part 107 of the vehicle 100. Figure 2 The corresponding part is set as the vibration excitation part 231. Then, the middle floor 103a of the car 100 is set as the object of vibration and noise reduction, and the middle floor model 221 in the body model 200 is set as the plate component model of the object of vibration and noise reduction. It should be noted that the physical property values ​​shown in Table 2 are set in both the skeleton component model and the plate component model in the body model 200.

[0140] [Table 2]

[0141] (Table 2)

[0142] steel 210 7.89

[0143] And, as Figure 6 and Figure 7 As shown, the vehicle body model 200 is divided into regions D1 to D2. 12 Regarding the constituent regions D1 to D2 12 The skeleton component model and plate component model are as described in Embodiment 1. Then, as an analysis for reducing vibration and noise from the mid-floor 103a of the automobile 100 and for lightweighting the vehicle body, the following steps are performed: A. Determination of vibration and noise reduction and lightweighting parts; B. Prediction of the peak frequency of the equivalent radiated power of the mid-floor model in the vehicle body model; and C. Calculation of the plate thickness of the vibration and noise reduction and lightweighting parts. Hereinafter, A to C will be explained in sequence.

[0144] [A. Determining the lightweight components for vibration and noise reduction]

[0145] The areas that contribute to reducing vibration noise in the mid-floor model 221 of the vehicle body model 200, and the parts that contribute to the weight reduction of the vehicle body, were identified. First, frequency response analysis was performed using the vehicle body model 200 to determine the frequency characteristics of the vibration behavior and equivalent radiated power of the mid-floor model. Then, based on the results of the vibration analysis, as shown in Embodiment 1 above, a vibration mode with significant vibration in the central part of the mid-floor model was selected, and the peak frequency of the equivalent radiated power corresponding to that vibration mode was obtained.

[0146] Next, change one or more partitioned regions D1 to D2. 12 The weight is used to perform frequency response analysis, and the peak frequency of the equivalent radiated power is obtained according to the combination of weights in the divided regions. Here, the regions are divided into D1 to D2. 12 The level number for the combination of weights is set to 52. Table 1 above shows a portion of the combinations of weights used to divide the regions.

[0147] Then, the peak frequency (Y) of the equivalent radiated power obtained from the vibration analysis is used as the objective variable to divide the region D. i weight (M) i Using Y as an explanatory variable, multivariate analysis was performed to determine the peak frequency Y of the equivalent radiated power and the weight M of the partitioned region. i The relationship is shown in equation (7). Here, multiple regression analysis is performed as a multivariate analysis, using equation (2) in the regression model. The relationship obtained through multivariate analysis is shown in equation (7). Additionally, the partial regression coefficients A in equation (7) are also shown in Table 3. i The standard partial regression coefficients are obtained through multivariate analysis.

[0148] [Mathematical Expression 5]

[0149]

[0150] [Table 3]

[0151] (Table 3)

[0152]

[0153] According to equation (7) and Table 3, the partial regression coefficient A i The larger values ​​of the partitioning region D8 (middle floor, A8 = 1.81) and the partitioning region D 10 (middle floor beam, A) 10 The weight of 3.57 contributes significantly to the peak frequency of the equivalent radiated power of the middle floor model 221.

[0154] In contrast, it can be seen that regions with smaller partial regression coefficients, such as D1 (roof, A1 = -0.07) and D... 11 (Rear floor longitudinal beam, A) 11 The weight of 0.001 contributes little to the peak frequency of the equivalent radiated power of the middle floor model 221.

[0155] Based on the above results, it is possible to determine the floor and the division area D8 in the partitioned area. 10 The corresponding parts of the vehicle body in the floor beam were identified as areas to be lightweighted as a measure to reduce vibration and noise.

[0156] [B. Prediction of the peak frequency of equivalent radiated power]

[0157] Next, the peak frequency of the equivalent radiated power is predicted. The relationship between the peak frequency of the equivalent radiated power and the weight of the divided region is expressed using the above equation (7). Then, the vehicle body model 200 (refer to...) is modified. Figure 4 and Figure 5 The region D in the diagram contributes significantly to the peak frequency of the equivalent radiated power of the floor model 221. 10 The floor beam and the D-zone, which contributes less to the division, are also included. 11 The weight of each of the rear floor longitudinal beams is used to calculate the peak frequency (predicted value) of the equivalent radiated power. On the other hand, as a comparison, the modified division area D is used... 10 . Floor beams or dividing area D 11 The frequency response of the vehicle body model 200, formed by the weight of the rear floor longitudinal beams, was analyzed to determine the frequency response of the equivalent radiated power of the middle floor model 221. The peak frequency (calculated value) of the vibration mode (the primary vibration mode) that causes significant deformation in the central part of the middle floor model 221 was also determined. Table 4 shows the division of region D. 10 . Floor beams and division of area D 11 The weight of the rear floor longitudinal beam and the result obtained by predicting the peak frequency using equation (7) are shown in Table 4. Additionally, Table 4 also shows the result obtained by calculating the peak frequency of the equivalent radiated power of the middle floor model 221 using the original vehicle body model 200.

[0158] [Table 4]

[0159] (Table 4)

[0160]

[0161] In Table 4, No. 1 represents the frequency response analysis using the original vehicle body model 200, and No. 2 represents the analysis using the divided region D.11 When the weight of the rear floor longitudinal beam is set to 0.5 times, No.3 divides area D. 10 The weight of the floor beam is set to 0.5 times.

[0162] As shown in Table 4, the predicted value of the peak frequency of the equivalent radiated power obtained by using equation (7) is approximately equal to the calculated value of the peak frequency of the equivalent radiated power obtained by vibration analysis of the vehicle body model 200.

[0163] In the region D where the contribution of change is relatively low 11 When the weight of the rear floor longitudinal beam is 0.5 times (No.2), the predicted and calculated values ​​of the peak frequency of the equivalent radiated power are approximately the same as the peak frequency of the equivalent radiated power obtained by vibration analysis of the vehicle body model 200 before the weight of the floor longitudinal beam was changed.

[0164] On the other hand, in the partitioned region D with a higher contribution to the change... 10 Under the weight of the floor beam, the predicted and calculated peak frequencies of the equivalent radiated power are 3.5 Hz and 3.2 Hz higher than the peak frequencies of the original vehicle body model, respectively.

[0165] This also shows that even if the contribution of the peak frequency of the equivalent radiated power in the mid-floor model is relatively low, D 11 The weight of the rear floor longitudinal beam and the peak frequency of vibration noise remain roughly unchanged. In contrast, by using D, which contributes significantly more... 10 Setting the weight of the floor beam to 0.5 times can increase the peak frequency by more than 3Hz, achieving both vehicle body weight reduction and vibration and noise reduction.

[0166] [Calculation of plate thickness for vibration and noise reduction in lightweight components]

[0167] Next, the effect of plate thickness on the peak frequency of the vibration noise reduction and lightweighting section was investigated. Here, the above equation (7) was used as the relationship between the peak frequency of the equivalent radiated power and the weight of the divided region to predict the effect of changing the divided region D. 10 The floor model 221 with the same slab thickness as the floor beam model (refer to...) Figure 4 and Figure 5 The peak frequency of the equivalent radiated power. Furthermore, for a correction value α that takes into account rigidity changes... i The situation also predicted the peak frequency, and the rigidity change was determined by the division of region D. 10 The lightweighting of the floor beam model resulted in this. Table 5 shows the predicted and calculated peak frequencies.

[0168] [Table 5]

[0169] (Table 5)

[0170]

[0171] In Table 5, No.1 is set as D in the original car body model 200. 10 Regarding the weight of the floor beams, No. 4 and No. 5 respectively constitute the dividing area D. 10 The thickness of the floor beam components was reduced from 1.2mm to 0.9mm and 0.8mm, resulting in weight reduction.

[0172] According to Table 5, the division of region D was changed. 10 The thickness of the floor beam increases the peak frequency, resulting in both the predicted and calculated values ​​being higher than the original vehicle body. The thinner the beam, the lower the weight, and the higher the peak frequency becomes. Furthermore, regarding the predicted value, a correction value α is applied to the stiffness change caused by the weight reduction, as shown in equation (6) above. i This allows the result to approximate the calculated value, resulting in a good outcome.

[0173] The above results show that the peak frequency was obtained by changing the plate thickness of the segmented regions that contribute significantly to vibration and noise reduction in the model of the target plate component. However, even when the plate thickness of the segmented regions is determined with a given peak frequency, the plate thickness can still be determined in a manner that satisfies the specified peak frequency, thus achieving both vibration and noise reduction and weight reduction. Furthermore, by applying a correction value related to the change in rigidity caused by the weight change of the segmented regions, the plate thickness of the segmented regions can be calculated with higher accuracy.

[0174] Industrial availability

[0175] According to the present invention, an apparatus and method for reducing vibration noise of plate components of an automobile, which reduces vibration noise of plate components caused by vibration from vibration sources in an automobile and identifies parts of the automobile body that can achieve lightweighting of the automobile body, are provided.

[0176] Explanation of reference numerals in the attached figures

[0177] 1. Vibration and noise reduction analysis device

[0178] 3 Display devices

[0179] 5 Input Devices

[0180] 7. Storage devices

[0181] 9. Data storage for operation

[0182] 11. Computation and Processing Department

[0183] 13. Vehicle Model Acquisition Department

[0184] 15. Division of Areas Setting Department

[0185] 17 Vibration and Noise Reduction Object Plate Component Model Setting Department

[0186] 19 Vibration Modes - Selection of Peak Frequency of Equivalent Radiated Power

[0187] 21. Obtaining the peak frequency of weight changes in the divided regions.

[0188] 23. Calculation of weight contribution of divided regions

[0189] 25. Vibration and noise reduction, lightweight component identification

[0190] 30 Body Model Files

[0191] 100 cars

[0192] 101 Skeleton Components

[0193] 103 Plate Components

[0194] 103a floor

[0195] 105 vibration source

[0196] 105a engine

[0197] 105b tires

[0198] 106 Front Suspension Mounting Section

[0199] 107 Rear Suspension Mounting Section

[0200] 200 car body model

[0201] 201 Upper Beam Model

[0202] 203 A-pillar model

[0203] 205 B-pillar model

[0204] 207 C-pillar model

[0205] 209 Floor Beam Model

[0206] 211 Rear Floor Longitudinal Beam Model

[0207] 213 Rear Floor Beam Model

[0208] 221 Floor Model

[0209] 223 Rooftop Model

[0210] 225 Rear Floor Model

[0211] 231 Excitation Section

[0212] 241 Rear bumper cover model

[0213] 243 Rear lower cover model

[0214] 245 Inner side panel model

[0215] 247 Wheel Cover Model

Claims

1. A vibration noise reduction analysis device for sheet metal components of an automobile, which reduces vibration noise of sheet metal components caused by vibrations from vibration sources in the automobile, and identifies parts that can achieve weight reduction of the automobile body, wherein, The vibration noise reduction and analysis device for the plate components of the automobile includes: The vehicle body model acquisition unit acquires a vehicle body model, which includes a skeleton component model and a plate component model formed by modeling the skeleton component and plate component that constitute the vehicle body using a mesh, and is equipped with an excitation unit that inputs vibration from the vibration source. The region setting unit sets multiple regions on the vehicle body model based on the skeleton component model and the plate component model; The vibration and noise reduction target plate component model setting unit sets the plate component model of the plate component model that is set as the vibration and noise reduction target plate component model in the vehicle body model according to the instructions from the operator. The vibration mode and equivalent radiated power peak frequency selection unit uses the vehicle body model to perform vibration analysis, calculates the vibration behavior of the vibration noise reduction target plate component model and the frequency characteristics of the equivalent radiated power as an indicator of vibration noise, and selects the vibration mode that contributes significantly to vibration noise and the peak frequency of the equivalent radiated power corresponding to that vibration mode. The division area weight change peak frequency acquisition unit changes the weight of one or more division areas in the vehicle body model, performs vibration analysis according to the combination of the weights of the division areas in the vehicle body model, and obtains the peak frequency of the equivalent radiation power of the vibration noise reduction target plate component model in the vibration mode selected by the vibration mode and equivalent radiation power peak frequency selection unit. The division region weight contribution calculation unit uses a regression model to perform multivariate analysis, taking the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model as the objective variable and the weight of the division region as the explanatory variable, and calculates the partial regression coefficient value in the regression model obtained through multivariate analysis as the contribution of the weight of the division region to the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model. as well as The vibration and noise reduction lightweighting part determination unit determines the parts of the vehicle body to be lightweighted based on the calculated contribution of each divided region in order to reduce the vibration and noise from the plate components that are designated as vibration and noise reduction targets.

2. Analysis methods for reducing vibration noise in automotive sheet metal components, among which, To reduce vibration noise in plate components caused by vibrations from vibration sources within the vehicle and to identify areas where lightweighting of the vehicle body can be achieved, a computer performs the following steps, the method comprising: The body model acquisition step involves acquiring a body model, which includes a skeleton component model and a plate component model formed by modeling the skeleton components and plate components that constitute the body of the automobile using a mesh, and is equipped with an excitation unit that inputs vibrations from the vibration source. The step of defining the division area involves defining multiple division areas on the vehicle body model based on the skeleton component model and the plate component model. The vibration and noise reduction target plate component model setting step involves setting the plate component model of the plate component model that is set as the vibration and noise reduction target plate component model in the vehicle body model. The vibration mode and equivalent radiated power peak frequency selection step involves using the vehicle body model to perform vibration analysis, determining the vibration behavior of the vibration noise reduction target plate component model and the frequency characteristics of the equivalent radiated power as an indicator of vibration noise, and selecting the vibration mode that contributes significantly to vibration noise and the peak frequency of the equivalent radiated power corresponding to that vibration mode. The step of obtaining the peak frequency of the weight change of the divided area involves changing the weight of one or more divided areas in the vehicle body model, performing vibration analysis according to the combination of the weights of the divided areas in the vehicle body model, and obtaining the peak frequency of the equivalent radiation power of the vibration noise reduction target plate component model in the vibration mode selected in the vibration mode selected in the vibration mode and equivalent radiation power peak frequency selection step. The step of calculating the weight contribution of the divided region involves using a regression model with the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model as the objective variable and the weight of the divided region as the explanatory variable in a multivariate analysis. The partial regression coefficients obtained through multivariate analysis are then used as the contribution of the weight of the divided region to the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model. The vibration and noise reduction and lightweighting part determination step involves determining the parts of the vehicle body to be lightweighted based on the calculated contribution of each divided region in order to reduce vibration and noise from the plate components designated as vibration and noise reduction targets.

3. The method for reducing vibration noise of automotive panel components according to claim 2, wherein, In the step of calculating the weight contribution of the divided regions, a relationship is derived between the peak frequency of the equivalent radiated power of the vibration noise reduction target plate component model and the weight of each divided region. The weight of at least one or more of the divided regions is changed and assigned in the derived relationship to predict the peak frequency of the equivalent radiated power of the vibration noise reduction target plate component model, and the parts in the vehicle body to be lightweighted are determined to reduce the vibration noise of the plate components caused by vibration from the vibration source in the vehicle.

4. The method for reducing vibration noise of automotive panel components according to claim 2, wherein, In the step of calculating the weight contribution of the divided regions, a relationship is derived between the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model and the weight of each divided region. A divided region for which the plate thickness is to be calculated is selected. The derived relationship is assigned the weights of the other divided regions excluding this divided region and the peak frequency of the equivalent radiated power of the vibration and noise reduction target plate component model. The weight of the selected divided region is calculated. Based on the calculated weight of the divided region, the plate thickness of the skeleton component model and / or plate component model constituting the divided region is calculated.

5. The method for reducing vibration noise of automotive panel components according to claim 4, wherein, When calculating the weight of the selected partitioned region using the relationship, a correction value is assigned to the relationship and the weight of the partitioned region is calculated. The correction value corrects the impact of the weight change of the partitioned region on the peak frequency of the equivalent radiated power.

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