Research Article  Open Access
Bingrong Miao, Feng Zhou, Chuanying Jiang, Yaoxiang Luo, Hui Chen, "A Load Identification Application Technology Based on Regularization Method and Finite Element Modified Model", Shock and Vibration, vol. 2020, Article ID 8875697, 12 pages, 2020. https://doi.org/10.1155/2020/8875697
A Load Identification Application Technology Based on Regularization Method and Finite Element Modified Model
Abstract
An improved load identification technology of a beam based on different regularization methods and model modifying methods is presented in an attempt to minimize the estimation error at several periodic loads. A hybrid model is developed to simulate such illposed problem interactions under different noise levels. The finite element model is modified with the different optimization algorithms to obtain the equivalent constraint condition. Experimental verification is also carried out to obtain correct modes and frequencies by considered vibration response and different boundary conditions. The measured results demonstrate the good agreement with the identification results. The results are shown that the improved method not only has more adaptive range and higher identification accuracy but also has effective identification ability for loads under different noise levels.
1. Introduction
In recent decade years, extensive application of regularization method to engineering structures’ health monitoring and inverse problems has been reported, as it has been recognized that using such an approach yields to improved quasistatic and dynamic load identification illposed problem characteristics [1]. The general concept for the solution of an illposed problem is to transform it into a wellposed problem by using additional information about the solution [2]. The methods, which transform the problem to the form of a wellposed problem, are regularization processes [3]. For these reasons, the regularization method had found its ways into aeronautical, civil, and mechanical engineering applications and started to become a standard method of solving inverse problem equation [4].
The literature on structural load identification is quite extensive and the research activities in this field have focused on a wide variety of applications. The identification problem was treated as an inverse problem to control certain objective functions. In other words, the structural load identification is reconstructed to achieve the optimization goal bounded by various constraints, among which is as consistent as possible with real loads under limited response data. Many scholars have proposed different identification methods for periodic and impact dynamic loads [2]. Thite and Thompson [4] discussed the relationship between Tikhonov regularization and the selection of regularization parameters by conventional crossvalidation methods and studied the iterative inversion technique of this method considering the influence of regularization matrix inversion. Liu and Han [5] proposed an inverse method which combines the interval analysis with regularization to stably identify the bounds of dynamic load acting on the uncertain structures. Liu et al. [6] found that most timedomainbased load identification methods based on state space have the disadvantages of large discrete error and long sampling time. The implicit Newmarkβ algorithm is transformed into a display algorithm to solve the load identification equation and uses Tikhonov regularization to solve the illconditioned problem. Sun et al. [7] combined a new improved regularization operator with Lcurve method to overcome the illcondition of load reconstruction and obtained the stable and approximate solutions of inverse problems. Jia et al. [8] proposed a weighted regularization approach based on the proper orthogonal decomposition (POD), in which the regularization parameter was selected by the GCV method. Gao Wei et al. [9] proposed a new method for selecting regularized parameters. The method is based on the entropy function method of quadratic programming theory. Numerical examples and experiments verify the effectiveness of the proposed method by identifying the sinusoidal loads acting on the cantilever beam. Prawin and Rao [10] use dynamic principal component analysis (DPCA) to propose an online identification load algorithm from the acceleration time history response measurement of moving windows. MAO et al. [11] proposed a timedomain force identiﬁcation approach for the linear system, which is based on Markov parameter fine integration in the state space, and discussed the influence of the position of the measuring point and noise on the load identification result. In addition, Liu et al. [5] use Green pulse function or shape function to discretely represent the dynamic response relationship of the system, thus establishing a positive problem of load identification and combining different regularization methods to deal with the illposedness in the inverse problem of load identification to improve identification accuracy [12–15]. Miao et al. [16] also used the Green kernel function to establish the load identification equation and compared several regularization methods to solve the identification problem of sine and triangle loads.
However, fewer studies have considered the application of load identification to different regularization, and the modified model used different optimization method interaction problems [17–23]. Hence, it is the main objective of the current paper to solve load identification problem model using the modified finite element model. Through considering the boundary constraint and different optimization methods, the main vibration frequency of the measured mode is corrected.
2. Theoretical Background and Mathematical Modelling
2.1. Dynamics Equations Based on Duhamel Integrated Method
The structural dynamic equation of motion for a proportional damping system with multidegrees of freedom is described aswhere M, C, and K are the total mass matrix, damping matrix, and stiffness matrix, respectively, F(t) is the load vector, and y(t), , and are the displacement, velocity, and acceleration response vectors.
According to the characteristics of the Dirac function, the external excitation of the system can be expressed as an integral form in which a plurality of pulse functions are superimposed. The equation can be described as
It is assumed that the response of the system under the unit pulse load is represented by the Green function G(t) from the load action point to the response measurement point [3]. According to the principle of Dirac function superposition, the dynamic response caused by the external load of the system is described as
Considering the zero initial condition system, the convolution integral of equation (3) is transformed, where Δ(t) is represented as a discrete sampling time interval and m is the number of sampling points. The equation can be discretized into a set of linear equations whose matrix form is described aswhere y_{i}, G_{i}, and f_{i} are the response of t = iΔt, the Green function, and the unknown external load. Furthermore, equation (4) can be simply described as
Similarly, the identification problem of multiple load effects can be expressed as a matrix which is described aswhere m is the number of applied loads, n is the number of response points, Y_{i} is the response, F_{i} is the column vector of the load, and G_{ij} is the Green Kernel Function between the load F_{j} and the response point Y_{i}.
Since the actually measured response signal always contains noise, there is a small singular value in the Green kernel function matrix [17]. Equations (5) and (6) will become typical illconditioned equations. If not appropriately to directly invert the matrix G, it is generally necessary to use an appropriate regularization technique to obtain an approximate solution to approximate the true result.
2.2. Regularization Technique
Regularization technology improves the illconditioning of load identification problem by modifying the singular value of system matrix and transforms the illconditioned problem into a steadystate problem [24–28]. Therefore, it provides an effective method for accurate load identification. The Tikhonov and TSVD regularization methods are used to be compared.
2.2.1. Tikhonov Regularization Technique
Tikhonov is derived from the variation method and is implemented by introducing stable functions [19]. For any , the quadratic function defined on the Hilbert space X is described aswhere is a regularization parameter and is represents y value containing an error. The Tikhonov regularization method is to find the minimum point of the function Ф_{α}(x) as an approximate solution to the equation.
It is known from the nature of the quadratic function that if the equation is satisfied, it can be obtained by equations (8) and (9):
2.2.2. TSVD Regularization Technique
Assuming that the generalized inverse of a linear equation exists, the solution can be described aswhere σ_{i} is the singular value of the compact operator A. The singular values are arranged in order from largest to smallest. u_{i} and are the standard orthogonal bases of the subspace and . If the right end y of the linear equation has a perturbation error δ_{y}, such as y^{δ} = y + δ_{y}, the approximate solution of the linear equation is described as
And the error between and is described as
It can be seen from the above equation that if the value of σ_{i} is smaller, the influence of the disturbance error δ_{y} on the resulting error δ_{x} becomes larger. The truncated singular value decomposition regularization method is to cut off the right end of the equation for calculating the generalized solution. The solution only retains the first k large singular values and filters the smaller singular values behind. Thus, the method can avoid the disturbance error being overamplified. The TSVD solution of the load identification equation (5) is described aswhere is the solution of the equation and k is called the truncation step of the TSVD method and has the effect of correcting regularization parameters. is a singular system for the matrix G.
How to choose the optimal regularization parameter k will directly affect the error and identification accuracy between the identification load and the real load. The GCV criterion is selected as the parameter selection method for TSVD regularization.
2.2.3. Selection of Regularization Parameters
It can be known from (9) and (13) that it is essential to select the optimal regularization parameters when the regularization technique solves the load identification equation. The Tikhonov regularization method uses the Lcurve criterion for regularization parameter selection, while the TSVD regularization method is combined with the GCV criterion for research. The size of the regularization parameter will directly affect the error between the identification load and the real load. Here is a brief description of two regularization parameter selection strategies.
(1) LCurve Criterion. In the optimization problem of Tikhonov regularization, the norm of the regularization and the residual norm are functions of the regularization parameter. Taking these two variables as the horizontal and vertical coordinates, and the resulting curve is as follows. In the general coordinate system, the curve will appear as a distinct L shape. The corner of L curve is the norm between the regularization and the residual value to obtain the optimal equilibrium position. The corresponding parameter of this corner point is the optimal regularization parameter. In order to reasonably determine the position of the corner of the curve, the maximum curvature point of the curve at the scale is generally selected. Assign the parameter , ; then, the curvature equation of the L curve is described aswhere , , and are the first and second derivatives of the regularization parameter, respectively. The optimal regularization parameters determined by the Lcurve criterion should be satisfy the following condition:
(2) GCV Curve Criterion. The generalized crossvalidation (GCV) curve criterion is based on the PRESS criterion in statistical theory. And it is more robust than the PRESS criterion. The basic idea of the GCV method is that reasonable regularization parameters can effectively predict any new unknown load. The equation defining the GCV function is described aswhere and T_{r} represents the trace of the matrix. And the equation satisfies the condition ; then, equation (16) can be simplified to the following equation:
The criteria for selecting the optimal regularization parameters according to the GCV method are described as
In solving this minimization problem, the numerator term of the GCV function in equation (17) is actually the residual norm of the regularization solution. This item is easier to obtain, but when the matrix dimension is large, the function of the denominator matrix trace of the function is very large.
3. The Improved Load Identification Algorithm
The load identification technology for periodic loads proposed in this paper is an inverse problem analysis method based on finite vibration response data, which mainly considers the problem of large fluctuations in the identification results due to differences in model accuracy and boundary conditions [29–35]. In order to avoid the uncertainty of the boundary conditions and structural parameters of the actual structural model from affecting the recognition accuracy, the recognition method proposed in this paper takes into account the model modification, using the results of the calculated and experimental modalities and several optimization algorithms to modify the limited boundary conditions and structural parameters of the meta model. Based on the abovementioned theoretical formula, load identification is carried out through vibration response. At the same time, the recognition accuracy of several regularization methods after model modification is compared in the algorithm. The specific flow chart is shown in Figure 1.
The improved algorithm of load identification is listed as follows: Step 1: establish numerical and experimental models of Euler–Bernoulli beam structure according to actual conditions. Step 2: use experimental modal and computational modal analysis methods to obtain the modal and mode shapes of the beam structure under different boundary conditions. Step 3: determine the type and number of sensors based on the condition number of the system matrix and the criteria for obtaining the vibration response accurately. The selection requirements of sensor location need to improve the noise immunity, signaltonoise ratio, and reliability of the data as much as possible. Step 4: according to the analysis results of the calculated mode and the experimental mode, an optimization method is selected to modify the boundary conditions and structural parameters of the finite element model to ensure that the relative error between the finite element mode and the experimental mode is minimized. Step 5: after confirming that the model correction result satisfies the conditions, apply the type, size, and position of the periodic load on the numerical model and the experimental model. Step 6: carry out onsite verification test according to the measured load to obtain the measured vibration response data. Step 7: use Picard’s condition to determine the wellposedness of the inverse problem. Step 8: perform load identification simulation according to the finite element simulation model, and calculate the vibration response. Step 9: obtain the measured data of the vibration response according to the experimental model. Step 10: according to Green's function and different regularization algorithms, considering different degrees of noise, use vibration response data to calculate the kernel function matrix. Step 11: determine the optimal regularization parameter (GCV curve and Lcurve) according to the regularization parameter selection criterion to reduce the influence of noise and boundary conditions. Step 12: if it is an illposed problem, determine the appropriate regularization technique to solve the load identification matrix equation. Step 13: compare and verify the simulation results and experimental results and evaluate the effectiveness of the recognition algorithm.
4. Numerical Example
4.1. Simulation Model for Load Identification
As a typical force structure, the cantilever beam structure can be used to identify the dynamic load, which is of great significance for both theoretical research and engineering practice. Therefore, the cantilever beam structure is selected as a numerical simulation model for periodic dynamic load identification, as shown in Figure 2. The cantilever beam has a structural size of 0.8 m × 0.06 m × 0.004 m, and the elastic modulus of the steel material is 2.1 × 10^{11} Pa, the density is 7.8 × 10^{3} kg/m^{3}, and Poisson's ratio is 0.3. It is assumed here that the structural damping of the cantilever beam is proportional damping.
The vibration data is obtained to simulate the measured response through adding white Gaussian noise to the simulation model. The response with noise is described aswhere y^{c} is the response calculated by the simulation, which can be displacement, velocity, and acceleration, std(y^{c}) is the standard deviation of the calculated response, l^{δ} is a percentage representing the noise level, And randn represents a white noise random number of the same length as y^{c}, where the mean is 0 and the variance is 1.
In order to evaluate the degree of conformity between the identification load and the real load, a relative error function is introduced, which is described aswhere i = 1, 2, …, n, and n is the number of sampling points.
In addition, in order to describe the effectiveness of the identification method, two indicators of total relative error (RE) and correlation coefficient (CC) are required. The equation is described by equations (21) and (22):where E(f) and E(f^{α, δ}) are the average of the actual load and the identified load, respectively.
A unit pulse load is applied to the above excitation point (corresponding to the node 16 of the simulation model), and the Green pulse kernel function response of the excitation point to the response point (node 15) is obtained by finite element calculation, and a corresponding kernel function matrix G is established [36, 37]. At 5% white noise level, the TSVD regularization identification results are compared with the traditional Tikhonov regularization method. The identification comparison results of sinusoidal loads at 5% noise level is shown in Figure 3.
The relative errors of these two regularization methods in identifying sinusoidal loads in the whole time period are obtained. The relative errors results are described in Figure 4.
It can be seen that both the TSVD regularization and the Tikhonov regularization can identify the added sinusoidal load. Obviously, the load identified by the Tikhonov method is fluctuated greatly, while the TSVD method is closer to the true load value. The error of TSVD regularization identification is lower than the Tikhonov regularization at most time points, and the relative error value can be guaranteed to be around 10% or less. The relative error of Tikhonov regularization is basically above 15%, and the overall relative error of identification is 21.36%. It shows that TSVD regularization identification can more accurately and stably identify the applied sinusoidal load compared to Tikhonov. In addition, the reason for the higher individual peak point identification error is due to the smoothing effect of the TSVD method on the identified load during the regularization process.
In order to further analyze the identification effect of TSVD regularization, Table 1 shows the overall relative error and correlation coefficient values identified by the TSVD method and the Tikhonov method under different noise levels, and the TSVD regularization is selected at 10%, 20%, and 30% noise levels.

It can be seen from Table 1 that, as the noise level increases, the overall relative error of the TSVD and Tikhonov regularization methods increases, and the correlation coefficient decreases. However, the relative error identified by the Tikhonov method increases by more than 10%, and the correlation coefficient has dropped to 0.77 when the noise level is 40%. The error identified by the TSVD method is only increased by about 3% each time, and the correlation coefficient can be guaranteed to be above 0.96. This shows that the TSVD regularization has a better suppression of noise, and the applied load can be more accurately recognized even at a higher noise level (20%). The results are shown in Figure 5.
A periodic mixed sinusoidal load, a triangular load, and a square wave load are applied to the free end of the beam (node 16), respectively, and 5% of the white noise is added to the acceleration response on node 15, using the response and TSVD. Regularization is performed for load identification, and the results obtained are shown in Figures 6–8. For the triangular and mixed sinusoidal loads, the respective identification results at five time points are shown in Table 2.

Tables 2 and 3 show that the Tikhonov identification load error is basically higher than TSVD at these five time points, whether it is sinusoidal load or triangular load, and the error of some points is even more than 20%, and the relative error of TSVD is 10%. At the same time, the correlation coefficient of the TSVD regularization identification load is above 0.99, while the Tikhonov is below 0.99. Therefore, from the above chart, the feasibility of the TSVD regularization method to identify the periodic load and the superiority with respect to Tikhonov are explained in the acceleration response as the load identification input.

The results in the figures and tables show that the TSVD regularization method is more efficient than the Tikhonov regularization method. Furthermore, the fluctuation and relative error of the identified loads are smaller. In addition, due to the transient abrupt change of the square wave load, the TSVD method recognizes that when identifying the type of load, the identification error is large at some points in time, and the overall identification error is higher than the other two types of loads.
4.2. Experiment Validation
4.2.1. Establishment of Experimental Model
From the previous analysis results, it can be seen that the uncorrected finite element model still has a certain error in the load identification. As the modal order increases, the error will be greater. It is necessary to establish a modified finite element model to improve the recognition effect. Therefore, this article established a detailed experiment validation plan. The experimental object is a cantilever steel beam with the same material and size as the simulation model. This article mainly analyzes the structural modal test data in the DH5923 software. The sampling frequency is 2 kHz. And the equivalent constraint boundary conditions can be simplified by linear springs and torsion springs. The linear spring stiffness is set to 1 × 10^{5} N/m, and the torsion spring stiffness is set to 1 × 10^{6} N/m. The experimental scene is as shown in Figure 9.
The modal analysis of the finite element model is carried out, and the comparison of finite element modal and experimental modal frequencies of the beam structure is listed in Table 4.

From the table, it is found that the relative errors of the first and second order modal frequencies obtained by experimental measurements and finite element analysis are small, while the relative errors of other orders are greater than 5%. This shows that the modal frequencies calculated by the finite element method are quite different from the measured frequencies, and the finite element model needs to be revised. Therefore, the first and second order modal frequency is chosen as the modification target of finite element model updating.
4.2.2. Model Correction and Sensitivity Analysis
Before performing specific model corrections, it is necessary to determine the correction parameters from the numerous elements. Choosing correction parameters is the key to successful model correction. The interpretability, correctness, and reliability of the correction model greatly depend on the composition of the correction parameters. In addition to the empirical screening method, parameters with higher sensitivity to vibration measurement parameters can also be selected as correction parameters through sensitivity analysis. Sensitivity analysis method is selected to model correction because it can measure the rate of change of structural response caused by the change of parameters or design variables. Through sensitivity analysis, the uncertainty of output variables can be ranked according to the degree of influence of design variables. In order to achieve the correction of the finite element model, the elastic modulus, the linear spring stiffness, and the torsional spring stiffness of the cantilever beam structure are used to design variables.
In order to ensure the accuracy of the dynamic load identification, it is necessary to carefully modify the finite element model in the load identification process. This paper uses several optimization algorithms to modify the finite element model and compares the relative errors of the natural frequency changes after different optimization algorithms modify the model [38].
For the optimization parameters, the equivalent elastic modulus of the beam structure and the stiffness value of the equivalent linear spring are set, and the corresponding upper and lower limits are 1 × 10^{11} ≤ E ≤ 3.0 × 10^{11} MPa and 1 × 10^{4} ≤ K_{1} ≤ 1 × 10^{7} N/m. The objective function in the optimization process is defined as follows:where represents the calculated natural frequency and is the experimentally measured natural frequency.
The target of optimization is the first and second order finite element modal frequencies, and the tolerance of the objective function is set to 10^{−3}. Set the optimal constraints to ensure that the relative error is less than 5% for other finite element modal frequencies. In the optimization, the LSGRG (Large Scale Generalized Reduced Gradient), the DS (Downhill Simplex), and the MIGA (Multiisland genetic algorithm) are compared for analysis [39]. The results of comparing the natural frequencies of the 1st to 5th modes of the finite element model with the experimental modes are shown in Figure 10.
From Figure 10, it can be found that the three optimization algorithms LSGRG, DS, and MIGA all have a certain effect on the modified finite element model, especially the correction effect of the MIGA method is the best, and the error rate of the natural frequency is relatively minimal. It shows that the models modified by these three optimization methods can basically meet the requirements of load identification. Of course, in the load identification process, an accurate finite element model is only the basic condition, and the vibration response is also an important indicator to evaluate whether the improved model and the experimental model are suitable. Therefore, the influence of boundary conditions needs to be paid enough attention when carrying out load identification.
4.2.3. Results Analysis and Discussion
In this paper, the multiisland genetic optimization algorithm is mainly used to modify the finite element model in the example, and the accuracy of the TSVD (GCV) regularization method is verified. In order to compare the results of the modified finite element model load identification, an experimental verification analysis is performed. In the test process, the sampling frequency is 2000 Hz and the sampling time is 2 s. In order to improve the calculation efficiency, load identification is performed on 200 data points among them. Then, the unit pulse loads are applied to the modified model, and the kernel function response is calculated to construct a Green function matrix G for load identification. The loads are identified by the TSVD (GCV) and the Tikhonov (Lcurve) regularization method, respectively. The comparison result is shown in Figure 11.
As can be seen in Figure 11, the experimental results have shown that TSVD has better identification than Tikhonov regularization. According to the comparison of simulation and test results, both methods can effectively identify the dynamic load, and the TSVD regularization method has better recognition effect than the Tikhonov method. There is only a slight deviation in the load identification at the peak, which is mainly due to the excessive regularization of the model equation.
In addition, results comparison of the finite element model correction based on the Tikhonov method is shown in Figure 12.
In Figure 12, in order to verify the before and after recognition results of the improved method, the Tikhonov regularization method with better identification effect is selected for comparison. The study found that using the load identification method of the modified finite element model, the identification result is closer to the measured load, which is better than the identification effect without the modified model. Through the comparison before and after the recognition results, it is necessary to consider the boundary constraints and the influence of noise. By optimizing the boundary conditions and structural parameters of the simulation model, the recognition effect and accuracy can be further improved.
5. Conclusion
In order to improve the accuracy of periodic dynamic load identification in practical engineering, the paper proposes a structural load identification method based on two regularization methods and a finite element correction model through simulation and experimental verification methods. This method compares the results of TSVD and Tikhonov regularization methods and verifies the effectiveness of the method through experiments. The specific conclusions are as follows:(1)When performing periodic load recognition, although both recognition methods have certain recognition effects, the TSVD method has a better recognition effect on periodic loads and can effectively deal with the illconditioned problem of kinematics equations in the load recognition process.(2)During the test verification process, the improved method can make use of the optimization algorithm to determine the appropriate design variables to ensure that the modified model has a better recognition effect.(3)When carrying out load identification, the influence of boundary conditions needs to be fully considered. And it is necessary to use optimization algorithms to select design variables to ensure better equivalence of model boundary conditions. At the same time, when performing the finite element model parameter correction based on the actual structural modal measurement results, it is recommended to select the modal with better measured results for correction.
Data Availability
The data used to support the findings of this study are included within the article. The data are published on figshare website. The files’ link can be found in https://figshare.com/s/79df76d5d71a5606eff8.
Conflicts of Interest
The authors declare that they have no conflicts of interest.
Acknowledgments
The authors wish to thank the teachers and students who participated in the research team on Load Identification and Damage Identification for their contributions. The work was financed by the National Natural Science Foundation of China (51775456) and SelfDeveloped Research Project of the State Key Laboratory of Traction Power (2019TPL T03).
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Copyright © 2020 Bingrong Miao et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.