iris chapter05
TRANSCRIPT
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The IRIS Damage Assessment Methodology 5-x
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188 10 12 14 16
Natural frequency f [Hz]
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o d e l o r d e r n
Authors:
Michael Döhler
Falk Hille
Laurent MevelWerner Rücker
5Estimation of Modal Parameters and
their Uncertainty Bounds fromSubspace-Based System Identification
Motivation
Operational Modal Analysis of existing structures is performed using output only vi-
bration measurements. To evaluate the quality of the resulting modal parameters (natural
frequencies, damping ratios, mode shapes) from system identification it is essential to
know their statistical uncertainty content.
Main Results
An innovative and efficient algorithm to estimate the modal parameters and their un-
certainties from subspace-based system identification has been developed. Applications
to output only measurements have been demonstrated on the S101 Bridge case.
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5 Estimation of Modal Parameters and their Uncertainty Bounds from Subspace-Based SystemIdentification
5-1 Introduction
Subspace-based system identification methods have proven to be efficient for theidentification of linear-time-invariant systems (LTI), fitting a linear model to input/output
or output only measurements taken from a system. An overview of subspace methods
can be found in [Benveniste and Fuchs, 1985; Benveniste and Mevel, 2007; Döhler and
Mevel, 2012; Van Overschee and De Moor, 1996].
During the last decade, subspace methods found a special interest in mechanical, civil
and aeronautical engineering for modal analysis, namely the identification of vibration
modes of structures from the eigenvalues (natural frequencies and damping ratios) and
observed eigenvectors (mode shapes) of an LTI system. For Operational Modal Analysis,
the identification of a structure under operation conditions, it is often impractical to ex-
cite the structure artificially, so that vibration measurements are taken under unmeasuredambient excitation. Therefore, identifying an LTI system from output-only measurements
is a basic service in vibration analysis, see e. g. [Basseville et al., 2001; Peeters and de
Roeck,1999].
For any system identification method, the estimated modal parameters are afflicted
with statistical uncertainty for many reasons, e. g. finite number of data samples, unde-
fined measurement noises, non-stationary excitations, model order reduction etc. Then
the system identification algorithms do not yield the exact system matrices and identi-
fication results are subject to variance errors. For many system identification methods,
the estimated parameters are asymptotically normal distributed, e. g. for estimates from
prediction error methods [Ljung, 1999], maximum likelihood methods [Pintelon et al.,2007], or the here considered subspace methods [Benveniste et al., 2000; Chiuso and
Picci, 2004]. A detailed formulation of the covariance computation for the modal parame-
ters from covariance-driven stochastic subspace identification is given in [Reynders et al.,
2008], where covariance estimates are based on the propagation of first-order perturba-
tions from the data to the modal parameters. These methods are very attractive for modal
analysis, as covariance estimates are obtained in one shot: From the same data set that
is used to estimate the modal parameters, all the covariance information is obtained by
cutting the available data into blocks, which is then propagated to the modal parameters,
without the need of computing the modal parameters on the blocks.
The variance information on the modal parameters is essential for many applications.
From statistical theory it is known that uncertainty bounds of estimated natural frequen-
cies are much smaller than those of damping ratios [Gersch, 1974]. To evaluate the quality
especially of the estimated damping ratios from system identification, it is essential to
know their uncertainty bounds. Also, a comparison of modal parameters estimated from
different data sets is not meaningful unless one knows the uncertainty bounds of the
parameters to evaluate if a significant change happened or not.
In this chapter, the identification of the modal parameters from output-only measure-
ments and the computation of their uncertainty bounds is described. They are demon-
strated on the system identification of S101 Bridge.
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Stochastic Subspace Identification 5-2
5-2 Stochastic Subspace Identification
Stochastic Subspace Identification methods are state-of-the-art methods for modalparameter estimation. They provide unbiased and consistent estimates, even under non-
stationary excitation [Benveniste and Fuchs, 1985; Benveniste and Mevel, 2007]. In this
section, an overview of the identification algorithm is given.
5-2-1 Models and Parameters
The behaviour of a mechanical system is assumed to be described by a stationary
linear dynamical system
( ) ( ) ( ) ( )Mz t Cz t Kz t v t + + = E.5-1
where t denotes continuous time, M, C , K d d ×∈ are the mass, damping and stiffness ma-
trices, high-dimensional vector d z ∈ collects the displacements of the degrees of free-
dom of the structure and the external force v is unmeasured and considered as noise. The
eigenstructure of [E.5-1] with the modes i µ and mode shapes (observed eigenvectors)r
i ψ ∈ is a solution of
2det( ) 0i i M C K µ µ + + = ,2( ) 0i i i M C K µ µ φ + + = , i i Lψ φ = ,
where matrix r d L ×
∈ maps the r sensor locations to the d degrees of freedom of the struc-ture. Observing model [E.5-1] at the r sensor locations (e. g. by acceleration, velocity or
displacement measurements) and sampling it at some rate 1/τ yields the discrete model
in state-space form
1k k k
k k k
x Fx v
y Hx w + = +
= + E.5-2
where n nF ×∈ is the state transition matrix, r nH ×∈ is the observation matrix, nk x ∈ are
the states of the system and r k y ∈ the output measurements at the discrete times t k τ = ,
where n is the system order. The vectors v k and w
k are the unmeasured input and output
disturbances. The eigenstructure of system is given by
det( ) 0i F I λ − = , ( ) 0i i F I λ φ − = , i i H ϕ φ = . E.5-3
The eigenstructure of the continuous system [E.5-1] is related to the eigenstructure of
the discrete system [E.5-2] by
i
i eτµ λ = , i i ψ ϕ = . E.5-4
From the eigenvalues , the natural frequencies f i and damping ratios i ρ of the sys-
tem are directly recovered from
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5 Estimation of Modal Parameters and their Uncertainty Bounds from Subspace-Based SystemIdentification
2 2
2
i i
i
a bf
πτ
+= ,
2 2
i i
i i
b
a b ρ
−=
+ where
Im( )arctan
Re( )i
i
i
a λ
λ = , lni i b λ = . E.5-5
5-2-2 Covariance-Driven Stochastic Subspace Identification
To obtain the eigenstructure of system [E.5-3] and the modal parameters from vibra-
tion measurements 1,...,( )k k N p q y = + + the stochastic subspace identification algorithm is used
[Benveniste and Fuchs, 1985; Peeters and de Roeck, 1999] . In the first step, the block
Hankel matrix H is filled with the output correlations ( )i k i k R y y
1 2
2 3 1
1 2
( )
q
q
i
p p p q
R R R
R R R
Hank R
R R R
+
+ + +
= =
H
, E.5-6
that can be estimated from
ˆ T r r i k i k R y y ×= ∈∑ . E.5-7
In the case of measurements at many coordinates, a subset of0
r r ≤ sensors can be
chosen as reference sensors in the output vector r k y ∈ , corresponding to the reference
output vectors 0(ref) r k y ∈ . Then, the output correlations
0(ref)
1
1ˆN
r r T
i k i k
k
R y y N
×+
=
= ∈∑
are estimated instead of E.5-7 to increase computation time and to improve the quality
of the results [Peeters and de Roeck, 1999]. The parameters p and q in the block Hankel
matrix E.5-6 are chosen such that { }0min , pr qr n≥ , with in general 1 p q+ = .Matrix H possesses the factorization property H = O C into observability matrix O and
stochastic controllability matrix C, where O is obtained from H by a singular value decom-
position (SVD) and truncation at the desired model order
1
1 0
0
( ) T U U V D
= D
H ,def
1/2 ( 1)
1 1
p r n
p
H
HF U
HF
+ ×
= D = ∈
O
. E.5-8
From the observability matrix O the matrices H in the first block row and F from a least
squares solution of
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Stochastic Subspace Identification 5-2
F =O O with
1 p
H
HF
HF −
=
O
,
HF
HF
HF
E.5-9
are obtained. The eigenstructure ( i λ , i ϕ ) of the system E.5-3 and the modal parameters are
finally obtained from E.5-3 to E.5-5.
5-2-3 Stabilization Diagram
In Operational Modal Analysis, the eigenstructure of mechanical, civil and aeronauti-
cal structures is identified from output-only data under ambient excitation. The model
order n of the discrete-time system E.5-2 is generally unknown (and is in fact infinity forthe mechanical system in most practical cases).
On the other side, the input and output noise processes ( )k k v and ( )k k w in model E.5-2
are hardly stationary Gaussian white noise sequences in practice. It was shown that the
identified system parameters converge to the true values when the number of data sam-
ples goes to infinity also under non-stationary excitation [Benveniste and Fuchs, 1985;
Benveniste and Mevel, 2007]. Moreover, coloured noise can be considered. Then, the
estimated eigenstructure corresponds to a combined system of a higher model order,
where the modes corresponding to the noise dynamics are also contained.
Thus, the selection of the model order in E.5-8 is a major practical issue. In order to
retrieve a desired number of modes, an even larger model order must be assumed whileperforming identification. A number of spurious modes appears in the identified model
due to this over-specification, as well as due to coloured noise that appears in practice.
Techniques from statistics to estimate the best model order may lead to a model with the
best prediction capacity, but one is rather interested in a model containing only the physi-
cal modes of the investigated structure, while rejecting the spurious modes.
Based on the observation that physical modes remain quite constant when estimated
at different over-specified model orders, while spurious modes vary, they can be distin-
guished using so-called stabilization diagrams. The system is identified truncating in E.5-8
at multiple model orders [Döhler and Mevel, 2012], and frequencies from this multi-order
system identification are plotted against the model order. From the modes common to
many models and using further stabilization criteria, such as threshold on damping val-
ues, low variation between modes and mode shapes of successive orders etc., the final
estimated model is obtained. Like this, stabilization diagrams provide a GUI where the
user is assisted in selecting the identified modes of an investigated structure.
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5 Estimation of Modal Parameters and their Uncertainty Bounds from Subspace-Based SystemIdentification
5-3 Covariance Estimates of Modal
Parameters The statistical uncertainty of the estimated modal parameters is necessary to assess
the quality of the estimates from the data. The uncertainty bounds of damping ratios are
particularly interesting, as the estimates of damping ratios are in general afflicted with a
high uncertainty according to statistical theory, and are thus difficult to obtain.
When estimated from a finite number of data samples, not the “true” parameters of the
system are obtained, but estimates that are naturally subject to variance errors depending
on the data and the estimation method, as the input of the system E.5-2 is unmeasured
noise. A variance analysis of the system matrices obtained from Stochastic Subspace Iden-
tification is made e. g. in [Chiusi and Picci, 2004] and expressions for their computationin the context of structural vibration analysis are given in [Döhler et al., 2013; Döhler
and Mevel, 2013; Reynders et al., 2008]. These computations are based on the propaga-
tion of first-order perturbations from the data to the identified parameters by a sensitivity
analysis. Like this, the uncertainties of the modal parameters at a chosen system order can
be computed from the uncertainty of the block Hankel matrix H, whose covariance ΣH
can be estimated by cutting the sensor data into blocks on which instances of the Hankel
matrix are computed. In the following, the underlying theory and the computation are
explained in detail.
5-3-1 Uncertainty Propagation
First, the principle of the uncertainty propagation is stated. Let θ be some parameter
vector and ˆN θ its estimate based on N data samples, whose expected valueˆ
N N θ θ = E tends
to*
θ as N goes to infinity. Define the estimated covariance ( )ˆ ˆ ˆcov( ) ( )( )T N N N N N θ θ θ θ θ = − −E and let ˆN θ fulfill the Central Limit Theorem
*ˆ( ) (0, )d N N θ θ − → Σ . E.5-10
for N → ∞ , where Σ is the asymptotic covariance and designates the normal distribu-
tion. As the number of data samples N is usually large, the distribution of N̂ θ is approxi-
mated to be normal with 1ˆcov( )N N θ ≈ Σ. Property E.5-10 is fulfilled directly for estimates
e. g. from subspace methods, maximum likelihood or prediction error methods.
Now, let ( )f θ be a vector-valued function of the parameter. Suppose that its first de-
rivative, the sensitivity matrix*
( )f f θ = exists in *θ and that it is full row rank. Using the
Taylor approximation
2* * *ˆ ˆ ˆ( ) ( ) ( ) ( )N f N N f f Oθ θ θ θ θ θ = + − + − ,
it follows
*
ˆ( ( ) ( )) (0, )d T
N f f N f f θ θ − → Σ ,
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Covariance Estimates of Modal Parameters 5-3
which is known as the delta method , and the covariance of ˆ( )N f θ can be approximated by
ˆ ˆcov( ( )) cov( ) T N f N f f θ θ ≈ . E.5-11
Note that*
( )f f θ = in the derivation above. A consistent estimate of the sensitivity is
then obtained from ˆ( )f N θ . Thus, starting from the covarianceˆcov( )N θ of an estimate
ˆN θ ,
that can for example be obtained from a sample covariance, the covariance of a function
of this estimate is obtained in E.5-11.
For subspace-based system identification, this initial covariance estimate is the covari-
ance of the vectorized Hankel matrix ΣH
cov(vec( ))= H that can be obtained as a sample
covariance by cutting the available data into blocks and computing instances of H on
each block, where vec is the column-stacking vectorization operator. As the system ma-
trices and subsequently the modal parameters are functions of H, it is the objective to
compute the sensitivities of these parameters with respect to vec(H) to finally obtain theircovariance from E.5-11.
In order to obtain the desired sensitivity matrices, first-order perturbations are used.
Let the vector θ be close to the true value*
θ and let the scalar ε be the perturbation
magnitude, writing*
(0)θ θ = (meaning no perturbation) and*
( )θ θ ε = . Then, a first-order
perturbation is defined as
2*
( )Oθ
θ ε θ θ θ ε ε
∂D = = − + =
∂,
and a first-order perturbation of ( )f θ yields
( )
( ) f f f
f θ θ
θ ε ε θ ε ε
∂ ∂D = = = D
∂ ∂ .
Thus, the desired sensitivity matrices can be obtained by applying first-order pertur-
bations. The following definitions are needed in the following sections. Let I a the identity
matrix of size a×a and 0a,b
the zero matrix of size a×b. Define the selection matrices
1 ,[ 0 ] pr pr r S I = , 2 ,[0 ] pr r pr S I = ,
such that 1S =O O , 2S =O O . Also, some properties of the vectorization operator are im-
portant. For ,a b ∈ define the permutation
, ,
, , ,
1 1
a ba b b a
a b k l l k
k l
E E = =
= ⊗∑∑ ,
where ,,a b
k l E is a matrix of size a×b that is equal to 1 at position (k ,l ) and zero elsewhere,
and ⊗ denotes the Kronecker product. Then, for any matrix ,a b X ∈ it holds
,vec( ) vec( )T
a b X X =
For any compatible matrices X , Y and Z the vectorization operator yields the relation
vec( ) ( )vec( )T XYZ Z X Y = ⊗
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5-3-2 Covariance of the Hankel Matrix
The covariance ΣH
cov(vec( ))= H of the vectorized Hankel matrix is the starting point
on the right hand side in E.5-11 before propagating it to the covariance of estimatesthat are a function of this matrix. For its calculation, the available data is separated into
nb blocks of the same length N
b for simplicity, with
b bn N N ⋅ = . Each block may be long
enough to assume statistical independence between the blocks. The correlations
( ) (ref )
1 ( 1)
1ˆb
b
jN j T
i k i k
k j N b
R y y N
+= + −
= ∑ E.5-12
are computed each of the blocks and the corresponding Hankel matrix
( )ˆ( ) j j i Hank R=H E.5-13
is filled. Then, 11
b
b
n
j n j == ∑H H and the covariance of the Hankel matrix in follows from the
covariance of the sample mean as
( )( )1
1vec( ) vec( ) vec( ) vec( )
( 1)
bn T
j j
j b bn n =Σ = − −
− ∑H H H H H .
As this matrix of dimension 0 0( 1) ( 1) p qrr p qrr + × + can get very large and for practicalapplications the number of available data blocks is usually smaller,
0( 1)bn p qrr < + , it is pro-
posed to store instead the matrix [Döhler and Mevel, 2013]
1 2 ... bnT t t t = H where ( )
1vec( ) vec( )
( 1) j j
b b
t n n
= −−
H H . E.5-14
Then, the relationship
T T T Σ =H H H E.5-15
holds and will be used for the computations.
5-3-3 Sensitivities of the System Matrices
The sensitivities of the system matrices A and C are obtained in two steps: First, a per-
turbation DH of the Hankel matrix is propagated to a perturbation DO of the observability
matrix, and second, a perturbation DO is propagated to perturbations D A and DC in the
system matrices.
In order to obtain DO, the sensitivities of the singular values and vectors in E.5-8 are
necessary. They have been derived in [Pintelon et al., 2007].
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Covariance Estimates of Modal Parameters 5-3
Lemma 1 [Pintelon et al., 2007]. Let i σ , ui and v i be the i -th singular value, left and
right singular vector of the matrix 0( 1) p r qr + ×∈H and DH be a first-order perturbation on
H. Then it holds
( ) vec( )T i i i v uσ D = ⊗ DH , vec( )i
i i
i
uB C
v
D = D
D H
where
0
1( 1)
1
i
i
p r
i T
qr
I B
I
σ
σ
+ −=
−
H
H,
0 0
( 1)
( 1) ,
( )1
( ( ))
T T
i p r i i
i T T
i qr i i p r qr i
v I u uC
u I v v σ
+
+
⊗ −=
⊗ − .
Using this result, the sensitivity of the observability matrix is derived.
Lemma 2 [Reynders et al., 2008]. Let Bi and C
i be given in Lemma 1 for i = 1, …, n. Then,
,vec( ) vec( )D = D
O HO H E.5-16
where 0( 1) ( 1), p rn p rqr + × +∈
O H with
0
1 1 1 1
1/2 1/2, 1 1 3 1 ( 1) ( 1)
( )1
( ) ( 0 )2( )
T
N p r p r qr
T
n n n n
v u B C
I U S I v u B C
+
− + + ×
+
⊗
= ⊗ Σ + Σ ⊗ ⊗
O H , 3 ( 1) ,n nk n k k S E − +∑
Proof. From the definition of O follows
1/2 1/2 1/2 1/211 1 1 1 1 1 1 1 12U U U U −D = DΣ + D DΣ = Σ DΣ + D ΣO ,
1/2 1/211 1 1 1 ( 1) 12
vec( ) ( )vec( ) ( )vec( )n p r I U I U −
+D = ⊗ Σ DΣ + Σ ⊗ DO .
The sensitivities of Σ1 and U
1 are obtained from Lemma 1 by stacking as
1 1 1( )
= vec( )
( )
T
T
n n n
v u
v u
σ
σ
D ⊗
D D ⊗
H ,
1 1
1
1
vec = vec( )
n n
B C U
V B C
+
+
D
D D
H
and the assertion follows.
The results of [Reynders et al., 2008] on the sensitivity of the system matrices are col-
lected in the following lemma.
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5 Estimation of Modal Parameters and their Uncertainty Bounds from Subspace-Based SystemIdentification
Lemma 3 [Reynders et al., 2008]. Let the system matrix A be obtained from O in E.5-9
and C from the first block row of O. Then, a perturbation on O is propagated to A and C by
,vec( ) vec( ) A AD = DO O , ,vec( ) vec( )C C D = D
O O E.5-17
where2 ( 1)
,
n p rn
A
× +∈O
, ( 1),rn p rn
C
× +∈O
, with
1, 2 1 2 2 ( 1) ,( ) ( ) (( ) ( ) )T T T T T
A n p r nI S A S S A S+ + −
+= ⊗ − ⊗ + − ⊗O O O O O O O ,
, ,0C n r r pr I I = ⊗ O
Proof. Using the product rule for a perturbation on 1( )T T A + −= =O O O O O O and Kro-
necker algebra leads to the assertion.
5-3-4 Sensitivities of the Modal Parameters
The natural frequencies and the damping ratios are functions of the eigenvalues of
system matrix A and the mode shapes depend on both A and C . In [Reynders et al., 2008],
the sensitivity derivations for the eigenvalues and eigenvectors of a matrix and subse-
quently for the modal parameters are stated, based on derivations in [Golub and van
Loan, 1996; Pintelon et al., 2007]. They are summarized in the following.
Lemma 4. Let i λ , i φ and i χ be the i -th eigenvalue, left eigenvector and right eigenvec-
tor of A with
i i i Aφ λ φ = ,* *
i i i A χ λ χ = ,
where * denotes the complex conjugate transpose. Then,
, vec( )i i A Aλ λ D = D , , vec( )i i A Aφ φ D = D ,
where21
,i
n
Aλ
×∈ ,2
,i
n n
Aφ
×∈ , with
*, *1
( )i
T
A i i
i i
λ φ χ χ φ
= ⊗ ,*
, *( )
i
T i i A i n i n
i i
I A I φ φ χ
λ φ χ φ
+
= − ⊗ −
.
Lemma 5. Let i λ and i φ be the i -th eigenvalue and left eigenvector of A and
ln( ) / ( ) /i i i i b a i λ λ τ τ = = + the eigenvalue of the corresponding continuous-time state
transition matrix as in E.5-5. Let furthermore the natural frequency f i and the damping
ratio i ρ be given in E.5-5. Then,
, vec( )i i f Af AD = D , , vec( )i i A A ρ ρ D = D , , , vec( )vec( )i i A C AC
ϕ ϕ D D = D
, E.5-18
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Covariance Estimates of Modal Parameters 5-3
where ,i f A ,21
,i
n
A ρ
×∈ ,2( )
, ,i
r n rn
A C ϕ
× +∈ , with
, , ,
, , ,
Re( )
Im( )i i i i
i i i i
f A f A
A A
λ λ
ρ ρ λ λ
=
, , , ,i i T
A C A i r C I ϕ φ φ
= ⊗ , and
, 2 2
2 2 2,
1/ (2 ) 0 Re( ) Im( ) Re( ) Im( )1
Im( ) Re( )| | | | 0 100/ | | Im( ) Re( )Im( )
i i
i i
f i i i i
i i i i i i i i
λ
ρ λ
π λ λ λ λ
λ λ τ λ λ λ λ λ λ
×
= ∈ − −
.
5-3-5 Summary of the Computation
From Equations E.5-16, E.5-17 and E.5-18 it follows that perturbations on a frequency
f i , damping ratio i ρ and mode shape i ϕ can be written as
,
, ,,
vec( )i
i
Ai
A
Ai
f λ
ρ ρ
D = D
D O O H
H
,,
, , ,,
vec( )i
A
i A C
C
ϕ ϕ
D = D
O
O H
O
H
.
From this expression and E.5-11, the covariance of a frequency and damping ratio of
a mode i yields
, ,
, , , ,, ,
cov i i i i
T
f A f Ai T T A A
A Ai
f
ρ ρ ρ
= Σ
O O H H O H O
, E.5-19
and the covariance of the real and imaginary parts of a mode shape yields
, , , ,, ,
, ,, , , ,, ,
Re( ) Re( )Re( )cov
Im( ) Im( )Im( )i i
i i
T T
A C A C A Ai T
A C A C C C i
ϕ ϕ
ϕ ϕ
ϕ
ϕ
= Σ
O O
O H H O H
O O
. E.5-20
From these covariances, the standard deviations of the respective modal parameters
are obtained from the square roots of the diagonal entries. The following procedure sum-
marizes an efficient computation of the covariance estimates for the modal parameters at
some model order n, which is equivalent to computing the products E.5-19 to E.5-20. It
takes into account the relation T T T Σ =H H H
in E.5-15 for a covariance estimate of the vector-
ized Hankel matrix, reducing the size of the involved matrices significantly:
1) Compute matrix T H from n
b blocks of the available data in equations E.5-12, E.5-13,
E.5-14
2) Compute products , , A AT T = O O H H for frequency and damping covariance, and
, ,C C T T = O O H H for mode shape covariance
3) For each mode i compute the covariance of the frequency and damping estimate
from
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5 Estimation of Modal Parameters and their Uncertainty Bounds from Subspace-Based SystemIdentification
Bridge S101 [VCE, 2009] F.5-1
covi i i i
i T
f f
i
f T T ρ ρ
ρ
=
where
,
,
i
i i
i
f A
f A
A
T T ρ ρ
=
,
and the covariance of the mode shape estimate from
Re( )
covIm( ) i i
i T
i i
T T ϕ ϕ ϕ
ϕ
=
where
, ,
, ,
Re( )
Im( )
i A C A
i
i A C C
T T
T
ϕ
ϕ
ϕ
=
.
For a detailed discussion of this computation and its numerical optimization the inter-
ested reader is referred to E.5-14.
5-4 Modal Analysis of S101 Bridge
5-4-1 S101 Bridge
Within the IRIS project an extensive measurement campaign of the prestressed con-
crete road bridge S101 [Döhler et al., 2011a; 2011b; VCE, 2009] was taken, which was
planned and organized by the Austrian company VCE and accomplished by VCE and the
University of Tokyo [VCE, 2009].
For vibration measurements a BRIMOS® measurement system was used, consisting in15 sensor locations on the bridge deck, where 14 sensors were placed on one side of the
deck and one sensor on the other side of the deck. In each location the bridge deck’s ver-
tical, longitudinal and transversal directions were measured. Altogether, 45 acceleration
sensors were applied. All values were recorded permanently with a sampling frequency
of 500 Hz. During the three days measurement campaign 714 data files with 165 000 data
points were produced. In this study only the first dataset is used.
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Modal Analysis of S101 Bridge 5-4
6420
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80
90100
188 10 12 14 166420
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20
30
40
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90100
188 10 12 14 16
Natural frequency f [Hz]
M o d e l o r d e r n
Natural frequency f [Hz]
M o d e l o r d e r n
00
10
20
30
40
50
60
70
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100
2.50.5 1 1.5 24.034.024.014.00
10
20
30
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50
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100
4.104.04 4.05 4.06 4.07 4.08 4.09
Damping ratio ρ [%]
M o d e l o r d e r n
Natural frequency f [Hz]
M o d e l o r d e r n
Stabilization diagrams containing the natural frequencies of the first five
modes with their confidence intervals (horizontal bars)
Zoom on first mode: estimated natural frequencies (left) and corresponding
damping ratios (right) at different model orders
F.5-2
F.5-3
5-4-2 Confidence Intervals of Modal Parameters
Restricting the system identification to the first five modes in the frequency range
[0–18 Hz], the data was downsampled from sampling rate 500 Hz by factor 5. System
identification and the covariance computation was done with the covariance-driven
subspace identification detailed in chapter 5-2 with parameters p + 1 = q = 35 at model or-
ders n = 1,…,100. All r = 45 sensors were used and r 0 = 3 reference sensors were chosen. The covariance computation on all identified modes at the different model orders was
accomplished with the strategy explained in chapter 5-3. For the covariance estimate on
the Hankel matrix, the data was cut into nb = 100 blocks. In F.5-2 (left), the stabilization
diagram of the natural frequencies vs. the model order are presented, where a confidence
interval (± one standard deviation) of each frequency is plotted as a horizontal bar. In
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5 Estimation of Modal Parameters and their Uncertainty Bounds from Subspace-Based SystemIdentification
mode f [Hz] [%]
1 4.036 0.12 0.78 15
2 6.281 0.08 0.56 20
3 9.677 0.18 1.3 14
4 13.27 0.13 1.5 13
5 15.72 0.37 1.3 17
Mode 1 Mode 2
Mode 5
Mode 3 Mode 4
Overview of the estimated first five modes with natural frequencies f , their
variation coefficient / 100f f f σ σ = ⋅ , the damping ratios ρ and their variation
coefficient / 100 ρ ρ σ σ ρ = ⋅
T.5-1
First five mode shapes in vertical direction on one side of the deck (line) and the
sensor on the other side of the deck (red point) with their 2 ϕ σ ± uncertainty bounds
F.5-4
F.5-2 (left) it can be seen that the (true) structural modes seem to have much lower un-
certainty bounds than spurious modes. With this observation, a threshold of 1 % was put
on the variation coefficient of the frequencies (standard deviation divided by frequency),which leads to a much clearer diagram in F.5-2 (right). Such a cleaned diagram would also
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References 5
be easier to evaluate for an automated modal parameter extraction. In F.5-3, the frequen-
cy and damping ratio of first mode identified at the different model orders is magnified for
a better visibility of the confidence bounds. Using the information from these confidence
bounds, values for the frequency and the damping ratio of a mode can be chosen that areoptimal for different model orders, as the true model order is unknown.
From the stabilization diagrams, the modal parameters are chosen. In T.5-1, the sys-
tem identification results with their variation coefficients are summarized. As expected,
the variation coefficients of the frequency estimates are very low (lower than 0.5 %), while
the estimates of the damping ratios show much higher variation coefficients (up to 20 %
in this case). In F.5-4, the real parts of the obtained mode shapes in the vertical direction at
the 14 sensors of one side of the bridge deck are displayed with their uncertainty bounds
(±2 standard deviations). From the 15th sensor on the other side of the bridge deck, whose
contribution is marked as the red point in F.5-4, information about the kind of the mode
is obtained: modes 1, 3 and 5 are vertical bending modes and modes 2 and 4 are torsionalmodes.
5-5 Conclusion
In this chapter, a method was presented to identify modal parameters – frequencies,
damping ratios and mode shapes – and their uncertainty bounds from output-only vibra-
tion measurements. The knowledge of the uncertainty bounds is essential to evaluate any
identified parameter and as it is known that especially estimated damping values showlarge uncertainties in system identification.
In operational modal analysis, where the system order is unknown and the input can-
not be measured, output-only subspace-based identification methods are very conveni-
ent. It was shown how the uncertainty bounds on the identified modal parameters can
improve system identification in this case by giving additional information to choose
modes in a stabilization diagram from identification results at different model orders. An
efficient implementation of the method was suggested and successfully applied to the
identification of modal parameters from output-only vibration data of S101 Bridge.
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