modalsd

R2026b

Generate stabilization diagram for modal analysis

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Syntax

modalsd(frf,f,Fs)
modalsd(frf,f,Fs,Name=Value)
fn = modalsd(___)

Description

modalsd(frf,f,Fs) generates a stabilization diagram in the current figure. modalsd estimates the natural frequencies and damping ratios from 1 to 50 modes and generates the diagram using the least-squares complex exponential (LSCE) algorithm. Fs is the sample rate. The frequency, f, is a vector with a number of elements equal to the number of rows of the frequency-response function, frf. You can use this diagram to differentiate between computational and physical modes.

modalsd(frf,f,Fs,Name=Value) specifies options using name-value arguments.

example

fn = modalsd(___) returns a cell array of natural frequencies, fn, identified as being stable between consecutive model orders. The ith element contains a length-i vector of natural frequencies of stable poles. Poles that are not stable are returned as NaNs. This syntax accepts any combination of inputs from previous syntaxes.

Examples

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Open Live Script

Compute the frequency-response functions for a two-input/two-output system excited by random noise.

Load the data file. Compute the frequency-response functions using a 5000-sample Hann window and 50% overlap between adjoining data segments. Specify that the output measurements are displacements.

load modaldata
wl = 5000;

[frf,f] = modalfrf(Xrand,Yrand,fs,hann(wl),wl/2,Sensor="dis");

Generate a stabilization diagram to identify up to 20 physical modes.

modalsd(frf,f,fs,MaxModes=20)

Figure contains an axes object. The axes object with title Stabilization Diagram, xlabel Frequency (kHz), ylabel Model Order contains 4 objects of type line. One or more of the lines displays its values using only markers These objects represent Stable in frequency, Stable in frequency and damping, Not stable in frequency, Averaged response function.

Repeat the computation, but now tighten the criteria for stability. Classify a given pole as stable in frequency if its natural frequency changes by less than 0.01% as the model order increases. Classify a given pole as stable in damping if the damping ratio estimate changes by less than 0.2% as the model order increases.

modalsd(frf,f,fs,MaxModes=20,SCriteria=[1e-4 0.002])

Figure contains an axes object. The axes object with title Stabilization Diagram, xlabel Frequency (kHz), ylabel Model Order contains 4 objects of type line. One or more of the lines displays its values using only markers These objects represent Stable in frequency, Stable in frequency and damping, Not stable in frequency, Averaged response function.

Restrict the frequency range to between 0 and 500 Hz. Relax the stability criteria to 0.5% for frequency and 10% for damping.

modalsd(frf,f,fs,MaxModes=20,SCriteria=[5e-3 0.1],FreqRange=[0 500])

Figure contains an axes object. The axes object with title Stabilization Diagram, xlabel Frequency (Hz), ylabel Model Order contains 4 objects of type line. One or more of the lines displays its values using only markers These objects represent Stable in frequency, Stable in frequency and damping, Not stable in frequency, Averaged response function.

Repeat the computation using the least-squares rational function algorithm. Restrict the frequency range from 100 Hz to 350 Hz and identify up to 10 physical modes.

modalsd(frf,f,fs,MaxModes=10,FreqRange=[100 350],FitMethod="lsrf")

Figure contains an axes object. The axes object with title Stabilization Diagram, xlabel Frequency (Hz), ylabel Model Order contains 4 objects of type line. One or more of the lines displays its values using only markers These objects represent Stable in frequency, Stable in frequency and damping, Not stable in frequency, Averaged response function.

Input Arguments

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Frequency-response functions, specified as a vector, matrix, or 3-D array. frf has size p-by-m-by-n, where p is the number of frequency bins, m is the number of response signals, and n is the number of excitation signals used to estimate the transfer function.

Example: tfestimate(randn(1,1000),sin(2*pi*(1:1000)/4)+randn(1,1000)/10) approximates the frequency response of an oscillator.

Data Types: single | double
Complex Number Support: Yes

Frequencies associated with the frequency-response functions, specified as a vector expressed in hertz.

The number of elements of f must equal the number of rows of frf.

Data Types: single | double

Sample rate of measurement data, specified as a positive scalar expressed in hertz.

Data Types: single | double

Name-Value Arguments

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Specify optional pairs of arguments as Name1=Value1,...,NameN=ValueN, where Name is the argument name and Value is the corresponding value. Name-value arguments must appear after other arguments, but the order of the pairs does not matter.

Example: modalsd(frf,f,Fs,MaxModes=20,FreqRange=[0 500]) computes up to 20 physical modes and restricts the frequency range to between 0 and 500 Hz.

Fitting algorithm, specified as one of these values:

Frequency range, specified as a two-element vector of increasing, positive values contained within the range specified in f.

Data Types: single | double

Maximum number of modes, specified as a positive integer.

Data Types: single | double

Criteria to define stable natural frequencies and damping ratios between consecutive model degrees of freedom, specified as a two-element vector of positive values. This argument contains the maximum fractional differences between poles to be classified as stable. The first element of the vector applies to natural frequencies. The second element applies to damping ratios.

Data Types: single | double

Output Arguments

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Natural frequencies identified as stable, returned as a matrix. The first i elements of the ith row contain natural frequencies. Poles that are nonphysical or not stable in frequency are returned as NaNs.

References

[1] Brandt, Anders. Noise and Vibration Analysis: Signal Analysis and Experimental Procedures. Chichester, UK: John Wiley & Sons, 2011.

[2] Ozdemir, Ahmet Arda, and Suat Gumussoy. "Transfer Function Estimation in System Identification Toolbox™ via Vector Fitting." Proceedings of the 20th World Congress of the International Federation of Automatic Control, Toulouse, France, July 2017.

[3] Vold, Håvard, John Crowley, and G. Thomas Rocklin. “New Ways of Estimating Frequency Response Functions.” Sound and Vibration. Vol. 18, November 1984, pp. 34–38.

Extended Capabilities

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Version History

Introduced in R2017a

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See Also

| | (System Identification Toolbox)