A METHOD FOR AUTOMATICALLY DETECTING FREE VIBRATION RESPONSE OF HIGH-SPEED RAILWAY BRIDGE FOR MODAL IDENTIFICATION

Abstract

A method for automatically detecting the free vibration response segment of the high-speed railway bridges after trains passing. First, pre-select the test response sequence to be decomposed based on the maximum of the time instants corresponding to the absolute maximums of the response vectors at various measuring point. Then, Extract the single-frequency modal response from the test response by the iterative variational mode decomposition and fit the envelope amplitude of the modal response by Hilbert transform. Finally, the vibration features at each time instants are marked as decay vibration or non-decay vibration. The longest structural response segment that meets the decay vibration features is determined as the detected free vibration response segment for modal identification. This invention can effectively detect the free vibration data segment without human participation, which is of great significance for the real-time accurate modal analysis of high-speed railway bridges.

Claims

1. A method for automatically detecting free vibration response of high-speed railway bridge for modal identification, wherein steps are as follows: Step 1: Pre-Selection of the Test Response to be Decomposed the acceleration responses at different measuring points are given as y(t)=[y.sub.1(t),y.sub.2(t), . . . ,y.sub.s(t)].sup.T,t=t,2t, . . . ,Nt, where t is the sampling time interval; N is the number of samples; s is the number of measuring points and the superscript T indicates transposition; calculate the time instant corresponding to the absolute maximum value of the response vector at each measuring point i, i=1,2, . . . ,s, as $t_i=\arg .Math.\underset{.Math..Math.ttN.Math..Math..Math..Math.t}{\max }.Math..Math.y_i\left(t\right).Math.;$ then the measuring point corresponding to the maximum of the time instants t.sub.i, i=1,2, . . . ,s, is obtained as $h=\arg .Math..Math.\underset{1is}{\max }.Math..Math.t_i.Math.,$ where presents the absolute value; then the response sequence y.sub.h(t.sub.h), t=t.sub.h,t.sub.h+t, . . . ,Nt is taken as the test response to be decomposed; Step 2: Extraction of Modal Response decompose the pre-selected test response by variational mode decomposition with the component number of 2 to obtain the modal response, as follows: $\begin{array}{cc}\underset{\left\{y_{h,q}\right\},\left\{{}_q\right\}}{\min }.Math.\left\{\underset{q=1}{\overset{2}{.Math.}}.Math.{.Math.{}_t.Math.\left[\left(\left(t\right)+\frac{j}{.Math..Math.t}\right)*y_{h,q}\left(t\right)\right].Math.e^{-i.Math..Math.{}_q.Math.t}.Math.}_2^2\right\}.Math..Math.s.t..Math.\underset{q=1}{\overset{2}{.Math.}}.Math.y_{h,q}\left(t\right)=y_h\left(t\right)& \left(1\right)\end{array}$ where means the Dirichlet function; j is the imaginary unit; .sub.t represents the gradient function with respect to t; e is the Euler number; is the circumference ratio; .sub.2 denotes the 2-norm of a vector; * represents the convolution; .sub.q is the central angular frequency of the component y.sub.h,q; y.sub.h,q(t) is the q (q=1,2) component decomposed from the test response y.sub.h(t); decompose the test responses y.sub.h(t) into two components y.sub.h,1.sup.[1](t) and y.sub.h,2.sup.[1](t); then calculate the difference of the central angular frequencies as .sup.[1]=|.sub.1.sup.[1].sub.2.sup.[1]|; if the angular frequency difference is greater than 0.01 times of the fundamental frequency of the structure, i.e., .sup.[1]>2f.sub.min/100, calculate the component energy as $e_q^{\left[1\right]}=\underset{t}{.Math.}.Math.{\left(y_{h,q}^{\left[1\right]}\left(t\right)\right)}^2,$ (q=1,2) and the component y.sub.h,{tilde over (q)}.sup.[1](t), $\tilde{q}=\arg .Math..Math.\underset{q=1,2}{\max }.Math..Math.e_q^{\left[1\right]}.Math.$ with higher energy are updated as the test signal to be decomposed; then the variational mode decomposition is used again to decompose the component y.sub.h,{tilde over (q)}.sup.[1](t); the above process will be repeated r times until the angular frequency difference of two components after the r-th decomposition satisfies .sup.[r]2f.sub.min/100, which means that the two components are with the identical frequency; the component y.sub.h,{tilde over (q)}.sup.[1](t) which has larger energy is deemed as the modal response with the angular frequency {tilde over (q)}.sup.[r], labelled as x(t).sub.{tilde over (q)}.sup.[r](t); Step 3: Estimation of Free Vibration Response extend the modal response x(t) as x.sub.e(t), and the Hilbert transform is performed on the continuation modal response x.sub.e(t) to obtain its envelope amplitude a.sub.e(t) as: $\begin{array}{cc}{a}_e\left(t\right)=\sqrt{{\left(x_e\left(t\right)\right)}^2+{\left(\frac{1}{.Math..Math.t}*x_e\left(t\right)\right)}^2}& \left(2\right)\end{array}$ the envelope a(t) corresponding to the modal response x(t) is intercepted from the envelope a.sub.e(t) of the continuation modal response x.sub.e(t), and the instantaneous amplitude difference is calculated as a(t)=a(t+1)a(t); according to the characteristic that the envelope amplitude of the free vibration modal response is decreasing, the vibration feature corresponding to the time instants of a(t)0 is marked as decay vibration and expressed in 1; otherwise, if a(t)>0, the vibration feature is marked as non-decay vibration and expressed in 0; thus, the vibration feature from the selected time instants t=[t.sub.h,t.sub.h+t, . . . ,Nt] will be labelled as a set of 0 or 1; choose the time instants [t.sub.h+wt,t.sub.h+(w+1)t, . . . ,t.sub.h+t] corresponding to the longest vibration feature sequence which are continuously marked as 1; and extract the structural vibration responses y(t) t=t.sub.h+wt, . . . ,t.sub.h+t as the free vibration response segment {tilde over (y)}(k), k=1,2, . . . w+1; Step 4: Identification of Modal Parameters eigensystem realization algorithm with data correlation is used to identify modal parameters; first, construct the Hankel matrix H(k) by the obtained free vibration responses {tilde over (y)}(k) as: $\begin{array}{cc}H\left(k\right)=\left[\begin{array}{cccc}\tilde{y}\left(k+1\right)& \tilde{y}\left(k+2\right)& \mathrm{.Math.}& \tilde{y}\left(k+g\right)\\ \tilde{y}\left(k+2\right)& \tilde{y}\left(k+3\right)& \mathrm{.Math.}& \tilde{y}\left(k+g+1\right)\\ \mathrm{.Math.}& \mathrm{.Math.}& & \mathrm{.Math.}\\ \tilde{y}\left(k+l\right)& \tilde{y}\left(k+l+1\right)& \mathrm{.Math.}& \tilde{y}\left(k+g+l-1\right)\end{array}\right]& \left(3\right)\end{array}$ then build the correlation function matrix S=H(l)H(0).sup.T by the Hankel matrix; implement eigensystem realization algorithm for the correlation function matrix to solve the modal parameters, including the structural frequency, the damping ratio and the mode shape vector.

Description

DESCRIPTION OF DRAWINGS

[0020] FIG. 1 presents the numerical example model.

[0021] FIG. 2 shows the extraction process of modal responses by iterative mode decomposition.

[0022] FIG. 3 presents the detected free vibration data segment.

DETAILED DESCRIPTION

[0023] The present invention is further described below in combination with the technical solution.

[0024] The numerical example of a simply supported beam model is employed, as shown in FIG. 1. The length of each element is 10 m. Based on the idea of static condensation, only the vertical displacement of the structure is considered and the torsional displacement is ignored. The element stiffness after static condensation is k.sub.1=k.sub.2=k.sub.3=k.sub.4=k.sub.5=k.sub.6=100 N/m. The mass is m.sub.1=m.sub.2=m.sub.3=m.sub.4=m.sub.5=1.5 kg. Rayleigh damping is adopted with the mass matrix coefficient =0.0446 and the stiffness matrix coefficient =0.0013. The constant loads F.sub.1(t)=F.sub.2(t)=210.sup.3 with the spatial interval of 0.05 m move from the left to the right of the beam at a speed of 1 m/s. The 175 s acceleration responses at each node position are collected at a sampling frequency of 20 Hz.

[0025] The procedures are described as follows:

[0026] The acceleration responses collected at each measuring point is given as y(t)=[y.sub.1(t),y.sub.2(t), . . . ,y.sub.s(t)].sup.T, where the sampling time interval is t=1/f.sub.s=0.05; the number of samples is N=3501; the number of measuring points is s=5.

[0027] Calculate the time instant corresponding to the absolute maximum of the response vector at each measuring point i (i=1,2, . . . ,s) as

[00008]$t_i=\arg .Math..Math.\underset{.Math..Math.ttN.Math..Math..Math..Math.t}{\max }.Math..Math.y_i\left(t\right).Math..$

Then the measuring point corresponding to the maximum of the time instants t.sub.i, i=1,2, . . . ,5, is obtained by

[00009]$h=\arg .Math..Math.\underset{1is}{\max }.Math..Math.t_i.Math.$

as h=1 with t.sub.h=t.sub.1=1022 t=51.1. Then the response sequence y.sub.1(t),t=t.sub.1, . . . ,Nt is taken as the test response to be decomposed.

[0028] The test response y.sub.1(t) is decomposed by the variational mode decomposition in Eq. (1) where the number of components is fixed as 2. After the first decomposition, two components y.sub.1,1.sup.[1](t) and y.sub.1,2.sup.[1](t) with the central angular frequencies .sub.1.sup.[1] and .sub.2.sup.[1] are obtained, as shown in FIG. 2. The fundamental frequency is determined as f.sub.min=0.6727 Hz in accordance with the power spectrum of the vibration responses. Since .sup.[1]>2f.sub.min/100, the energy of each component is calculated as

[00010]$e_1^{\left[1\right]}=\underset{t}{.Math.}.Math.{\left(y_{1,1}^{\left[1\right]}\left(t\right)\right)}^2.Math..Math.\mathrm{and}.Math..Math.e_2^{\left[1\right]}=\underset{t}{.Math.}.Math.{\left(y_{1,2}^{\left[1\right]}\left(t\right)\right)}^2.$

Since e.sub.1.sup.[1]>e.sub.2.sup.[1], the component y.sub.1,1.sup.[1](t) is considered as the new test signal to be decomposed by the variational mode decomposition. Repeat the above process until the angular frequency difference .sup.[4]=|.sub.1.sup.[4].sub.2.sup.[4]|<2f.sub.min/100. Since e.sub.1.sup.[4]>e.sub.2.sup.[4], the component y.sub.1,1.sup.[4](t) is selected as the modal response, which will be labelled as x(t)y.sub.1,1.sup.[4](t).

[0029] Extend the modal response x(t) to obtain the continuation signal x.sub.e(t) to avoid the edge effect in the subsequent transform. Then the Hilbert transform is used to obtain the envelope amplitude of the continuation signal x.sub.e(t) as a.sub.e(t), as Eq. (2).

[0030] The envelope a(t) corresponding to the modal response x(t) is intercepted from the envelope a.sub.e(t) of the continuation modal response x.sub.e(t), and the instantaneous amplitude difference is calculated as a(t)=a(t+1)a(t). According to the characteristic that the envelope amplitude of the free vibration modal response is decreasing, the vibration feature corresponding to the time instants of a(t)0 is marked as decay vibration and expressed in 1. Otherwise, if a(t)>0, the vibration feature is marked as non-decay vibration and expressed in 0. Thus, the vibration feature from the selected time instants t=[t.sub.h,t.sub.h+t, . . . ,Nt] will be labelled as a set of 0 or 1. Choose the time instants [t.sub.h+wt,t.sub.h+(w+1)t, . . . ,t.sub.h+t] corresponding to the longest vibration feature sequence which are continuously marked as 1. And extract the structural vibration responses y(t), t=t.sub.h+wt, . . . ,t.sub.h+t as the free vibration response segment {tilde over (y)}(k), k=1,2, . . . w+1, as shown in FIG. 3.

[0031] The eigensystem realization algorithm with data correlation is performed on the detected free vibration response segment. First, the obtained free vibration responses are utilized to construct the Hankel matrix H(k) as Eq. (3). Set k=l=30, g=N.sub.b2 l+1, and build the correlation function matrix as S=H(l)H(0).sup.T. Implement eigensystem realization algorithm for the correlation function matrix to solve the first 5 modal parameters of the structure, which are consistent with the numerical solution. The identified frequencies are f.sub.1=0.6727 Hz, f.sub.2=1.2995 Hz, f.sub.3=1.8378 Hz, f.sub.4=2.2508 Hz, f.sub.5=2.5104 Hz and the identified damping ratios are d.sub.1=0.8000%, d.sub.2=0.8000%, d.sub.3=0.9384%, d.sub.4=1.0706%, d.sub.5=1.1596%. As a comparison, the vibration responses corresponding to the time instants t=t.sub.h, . . . ,Nt are implemented into the eigensystem realization algorithm to solve the first 5 modal parameters, which are a little dissimilarity with the numerical solution. The estimated frequencies are f.sub.1=0.6712 Hz, f2=1.2963 Hz, f.sub.3=1.8413 Hz, f.sub.4=2.2513 Hz, f.sub.5=2.5132 Hz. The estimated damping ratios are d.sub.1=0.7621%, d.sub.2=2.1911%, d.sub.3=0.6523%, d.sub.4=0.8205%, d.sub.5=1.3894%.