Published: 02 December 2021

A method of reverse seeking material parameters by using finite element optimization algorithm

Dayong Jiang1
Peiran Li2
Bin Qiu3
Jingchang Chen4
1, 2, 3, 4State Key Laboratory of Vehicle NVH and Safety Technology, Chongqing, China
1, 2, 3, 4China Automotive Engineering Research Institute Co., Ltd, Chongqing, China
Corresponding Author:
Dayong Jiang
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Abstract

This paper mainly studies a reverse engineering of material parameters through finite element optimization algorithm based on free modal test results, focusing on free modal test and establishment of finite element optimization model. The elastic modulus and density of the material can be solved by the finite element optimization algorithm to ensure the accuracy of the simulation results. When the accurate material parameters are obtained, the accuracy of abnormal sound simulation can be improved. It plays a guiding role in the development of vehicle BSR performance, so as to improve the ride comfort of the vehicle.

1. Introduction

In NVH simulation analysis, the elastic modulus and density of materials are very important to the accuracy of simulation results [1]. For the same material, the material parameters provided by different suppliers are not the same, which leads to great differences between the simulation results and the test results, which has no guiding significance for the development and design.

In order to obtain the elastic modulus and density of the material, first, actual modal frequency and shape can be obtained through the free modal test [2-5], and then the finite element optimization model is constructed, taking values of free modal test as the reference values, and the elastic modulus and density of the material can be solved. Finally, the elastic modulus and density obtained from the solution are used as the input for the modal simulation analysis, comparing with simulation results and the test results.

2. Free mode test

The sample used in this paper is the tailgate trim panel of an SUV, which is made of PP / PE and weighs 1.8 kg. The equipments for modal test are LMS Test. Lab, 15 unidirectional piezoelectric sensors, each weighing 4 g, a rubber hammer. Two points elastic suspension is used for the test sample, as shown in Fig. 1.

Fig. 1Free mode test

Free mode test

The free mode test results are shown in Table 1.

Table 1Mode test results

Modal orders
Frequency / Hz
1
8.8
2
31.6
3
40.4
4
42.8
5
52.3
6
54.5
7
63.0
8
70.2
9
71.0
10
76.8
11
78.6
12
86.4

The first torsional mode and the first bending mode are shown in Figs. 2 and 3.

Fig. 2The first torsional mode

The first torsional mode

Fig. 3The first bending mode

The first bending mode

3. Establish the finite element optimization model

3.1. Mesh the tailgate trim panel

Import the tailgate trim panel into HyperMesh, switch to the Optistruct template, extract the middle plane and mesh the tailgate trim panel. The mesh adopts CQUAD4 & CTRIA3 element, and the average size of the mesh is 5 mm. The finite element model of the tailgate trim panel is shown in Fig. 4. The sensor used in the modal test is simulated by CONM2 element, and the position of the mass element is consistent with that in the modal test.

Fig. 4The trim panel of tailgate

The trim panel of tailgate

4. Establish the finite element optimization model

The finite element optimization model is established in HyperMesh-Optistruct.

4.1. Setting optimization variables

For the content of this paper, the elastic modulus and density of the material should be set as the optimization variables. And associate the variable with the corresponding attribute. The variable setting and attribute association in HyperMesh-Optistruct are shown in Fig. 5.

Fig. 5The optimization variables

The optimization variables

4.2. Setting the responses

This example needs to establish four responses, which are the first order modal frequency of the flexible body, the second order modal frequency of the flexible body, the total mass of the model and the functional response. The functional response is the square sum of the difference between the simulation results and the test results [6-8]. The test modal frequency of the first order flexible body is 8.8 Hz, and that of the second order flexible body is 31.6 Hz. The specific settings are shown in Fig. 6.

Fig. 6The optimization variables

The optimization variables

4.3. Setting the constraints

Since the actual mass of the sample is known, the total mass of the model is set as a constraint variable, and the total mass of the tailgate trim panel and sensor is 1860 g. In order to ensure the convergence of the optimization model, the total mass of the model is allowed to fluctuate in a small range, and the fluctuation range is 40 g. The constraint settings are shown in Fig. 7.

Fig. 7The optimization variables

The optimization variables

4.4. Setting the objectives

In order to improve the consistency between the optimization results and the test results, it is necessary to minimize the error between the simulation and the test. The optimization objective of this paper is to minimize the sum of squares of the differences between the simulation results and the test results, as shown in Fig. 8.

Fig. 8The objective

The objective

4.5. Solving the finite element optimization model

After the optimization model is established, it is submitted to Optistruct solver for solution, and the solution result is shown in Fig. 9.

Fig. 9The optimization results

The optimization results

4.6. Comparative simulation and experiment

From the above optimization results, it can be seen that the elastic modulus of the tailgate trim panel of the SUV is 2756 MPa and the density is 1.0e-9t/mm3. Assign the value to the finite element model, carry out free modal analysis again, and compare the analysis results with the test results. The comparison results are shown in Table 2 and Fig. 10. The error rate defined here is the absolute error rate, that is, the simulation result minus the test result and then divided by the test result.

Table 2Mode benchmarking results

Modal orders
Simulation results
Test results
Error rate
1
9.2
8.8
4.55 %
2
31.6
31.6
0.00 %
3
40.7
40.4
0.74 %
4
42.5
42.8
–0.70 %
5
52.6
52.3
0.57 %
6
54.0
54.5
–0.92 %
7
62.7
63.0
–0.48 %
8
70.3
70.2
0.14 %
9
71.2
71.0
0.28 %
10
76.1
76.8
–0.91 %
11
78.1
78.6
–0.64 %
12
86.5
86.4
0.12 %

Fig. 10The modal benchmarking results

The modal benchmarking results

5. Conclusions

In this paper, the modal frequencies of tailgate trim panel is obtained by modal test, and the elastic modulus and density of the material are solved by the finite element optimization model, and the obtained elastic modulus and density are substituted into the finite element model for free modal analysis. Finally, the simulation values are compared with the test values, and the error of the first flexible body modal frequency is 4.55 % within 80 Hz. The error rate of the remainder is less than 1 %, which verifies the effectiveness of the method, and then can ensure the prediction accuracy of CAE simulation for NVH.

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Cited by

Advances in Mechanical Design
Gang He | Yang Zhou | Zhaoyuan Cao | Hu Yang
(2024)

About this article

Received
14 October 2021
Accepted
18 November 2021
Published
02 December 2021
SUBJECTS
Modal analysis and applications
Keywords
finite element
modal test
NVH
modulus of elasticity
density
optistruct
Acknowledgements

This research was financially supported by the consumer car driving and riding evaluation (011520) and the research on sound quality control method under transient operations of vehicle performance integration (NVHSKL-ZS-202101).