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Modal Analysis and Correlation
Structural Dynamics Agenda Topics
How to characterize structural behavior?
How does my structure naturally want to move?
How to validate simulation models?
Fundamentals
Modal Analysis
Modal Correlation
Natural Frequencies, Resonances, Damping
Curve fitting, data quality checks (MAC), mode shapes
Modal Assurance Criteria, Modal Contribution, Updating
structurestructure-borne
airair-borne
structurestructure-borne
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Why are structural dynamics important?
Product Development Process Troubleshoot
Cost of Change
Validate
Engineer
Concept
Detail Drawing
Prototype
Production
Field Failure
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Aircraft Flutter
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Tacoma Bridge Collapse
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Natural frequency of a traffic signal
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What is a natural frequency?
Natural Frequency Natural frequency is the frequency at which a system naturally vibrates once it has been forced into motion f(t)
x(t) m
k
c
ground
Single Degree of Freedom System
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k n natural frequency (rad/sec) m Siemens PLM Software
Natural Frequency
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Resonant Frequency
Amplitude
Resonance is the buildup of large amplitude that occurs when a structure is excited at its natural frequency
ω f = 0.4
ω f = 1.01
ω f =1.6
3 Single Degree of Freedom Systems with same mass, stiffness and damping
ω n = 1.01
Frequency
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Structural Damping Damping is any effect that tends to reduce the oscillations in a system
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c 2 km
d n 1
2 Siemens PLM Software
How do we determine the resonant behavior of a structure?
Frequency Response Functions Frequency Response Functions (FRFs) measure the system’s output in response to known an input signal
o u tp u t FRF input
RESPONSE
FORCE
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Time Frequency
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Frequency Response Functions Frequency Response Functions (FRFs) measure the system’s output in response to known an input signal
FRF
o u tp u t input RESPONSE
FORCE
dB
N2/Hz
-50.00
-100.00 0.00
Hz
1024.00
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What can an FRF tell you?
Mode Shape ➢ Requires Multiple FRFs
1.7 1.4 1.2 1.0
0.7 0.5 0.3 0.0 618
° Phase
Damping
g/N Amplitude
Resonant Frequency
-393 10 50
100 150 200 250 300 350 400 450 500 550 600 651 Hz
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What can an FRF tell you?
g/N Imag
1.6 1.4 1.3 1.2 1.1 1.0 0.9 0.8 0.7 0.6 0.5 0.4 0.3 0.2 0.1
g/N Real
-0.1 1
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-700e-3 10
50
100
150
200
250
300
350 Hz
400
450
500
550
600
651
Siemens PLM Software
Quality Factor
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Damping calculation – Active Picture 2776.18
(in/s2)/lbf Amplitude
2800.0 2400.0
2722.33 2355.74 2228.38
2000.0
Curve
Q (/) 14.15 | 17.29 | 15.85 | 19.89 | 16.30
1400.0
1381.96
1000.0
° Phase
400.0 0.0 618 75.94
84.21
60.54
71.35
49.80
-393
135.00
305.00
387.00
476.00
559.00
10
50
100
150
200
250
300
350
400
450
500
550
600
651
Hz Unrestricted © Siemens AG 2019 Page 21
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Other Damping Terms
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Mode Shape: Excitation in which a system is affected under a specific frequency. Has a particular shape in which it moves – each node moves sinusoidally with fixed phase relation to each other node
1st mode
2nd mode
3rd mode Unrestricted © Siemens AG 2019 Page 23
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Mode Shape: Excitation in which a system is affected under a specific frequency.
Has a particular shape in which it moves – each node moves sinusoidally with fixed phase relation to each other node
3rd mode Node: place where displacement is zero for a given mode shape Anti-node: position of maximum displacement Unrestricted © Siemens AG 2019 Page 24
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More interesting mode shapes…. Brake disc mode 1
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More interesting mode shapes…. Brake disc mode 2
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More interesting mode shapes…. Brake disc mode 3
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Some Math…
g/N
g/N Imag
1.6 1.0 0.5
-0.1 1 -700e-3
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10 100
200
300 400 Hz
500
651 Siemens PLM Software
FRFs determine mode shapes
1st Bending Mode
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FRFs determine mode shapes
1st Torsional Mode
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Experimental Modal Analysis The process of identifying the dynamic behavior of a system (structure) in terms of it’s modal parameters Modal parameters • Frequency • Damping • Mode Shape
▪ ▪ ▪ ▪
Troubleshooting Simulation and prediction Optimization Diagnostics and health monitoring
f(t)
x(t) m
k
c
ground
Single Degree of Freedom System Unrestricted © Siemens AG 2019 Page 31
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Experimental Modal Analysis Process 24
(m/s2)/N Amplitude
20
Curve Fit to Estimate Modal Parameters
16 14 10 8 4 0 0 25 50
100
150
200
250
300
350
400
450 500
Hz
Measure the Frequency Response Functions Response
Frequency Damping Mode Shapes Input
Input
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Linearity of the FRF
N2 Log
( ) Log
0.10
g/N
1.00
AutoPow er FOR:1:+X AutoPow er FOR:1:+X AutoPow er FOR:1:+X
10.0e-6 0.00 180.00 0.00
1.00e-6
Hz Linear
100.00
Linear
100.00
Hz
° Phase
F F F
FRF DRV:1:+X/FOR:1:+X FRF DRV:1:+X/FOR:1:+X (1) FRF DRV:1:+X/FOR:1:+X (2)
-180.00 0.00
Hz
100.00
0.00
Hz
100.00
3 different excitation levels
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Measurement Techniques
Measurement Equipment Excitation • Laboratory (shakers, hammer, force cell, …) • Operational excitations (road simulation, flight simulation, wind excitation, …)
• Unusual excitations (loudspeaker, gun shot, explosion, …)
Response • (Accelerometers, Laser,…)
Measurement system • Data acquisition system: SCADAS (minimum 2 channels) • Processing on PC (Test.Lab) Unrestricted © Siemens AG 2019 Page 35
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Excitation Techniques
Impact Testing
Shaker Testing
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Impact Testing
Response
Minimal equipment Easy and fast Good for wide range of structures Limited frequency range
Frequency
Input
Time
FRF
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Impact Testing: Various Tips
Which tip should I use?
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Impact Testing: Various Tips
0.00
Hz
Amplitude /
dB /Hz N2
0.02
0.00
-60.00
5000.00
0.02 0.00
Hz
0.00
-60.00
5000.00
0.00
Hz
dB /Hz N2
0.02
-4.00
Amplitude /
1.00
g/N Log
5.50
Rubber Tip
-4.00 dB /Hz 2 N
1.00
g/N Log
5.50
Nylon Tip
-4.00
Amplitude /
Metal Tip
1.00
g/N Log
5.50
0.00
-60.00
5000.00
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The Right Tools for the Job
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Roving Hammer vs. Roving Accelerometer?
Any Difference? Unrestricted © Siemens AG 2019 Page 42
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Modal Test Nine Point Modal x Three Directions • Force In the ‘Z’ Direction. (One Direction) • Triaxial Accelerometer Possible Inputs and Outputs A1x
A1y
A1z
A2x
A2y
A2z
…
A9x
A9y
A9z
F1x F1y F1z F2x F2y
F2z
… F9x F9y F9z Unrestricted © Siemens AG 2019 Page 43
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Modal Test Nine Point Modal x Three Directions • Force In the ‘Z’ Direction. (One Direction) • Triaxial Accelerometer Possible Inputs and Outputs A1x
A1y
A1z
A2x
A2y
A2z
…
A9x
A9y
A9z
F1x F1y F1z F2x F2y
F2z
…
One complete Row or one complete column required to calculate mode shape
F9x F9y F9z Unrestricted © Siemens AG 2019 Page 44
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Modal Test Nine Point Modal x Three Directions • Force In the ‘Z’ Direction. (One Direction) • Triaxial Accelerometer Possible Inputs and Outputs A1x
A1y
A1x/F1z
A1x/F1z
A1z
A2x
A2y
A2z
…
A9x
…
A1x/F1z
A9y
A9z
F1x F1y F1z
A1x/F1z
A1x/F1z
A1x/F1z
A1x/F1z
A1x/F1z
A1x/F1z
F2x F2y
F2z
… F9x F9y F9z Unrestricted © Siemens AG 2019 Page 45
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Modal Test Nine Point Modal x Three Directions • Force In the ‘Z’ Direction. (One Direction) • Triaxial Accelerometer Possible Inputs and Outputs A1x
A1y
A1x/F1z
A1x/F1z
A1z
A2x
A2y
A2z
…
A9x
…
A1x/F1z
A9y
A9z
F1x F1y F1z
A1x/F1z
A1x/F1z
A1x/F1z
A1x/F1z
A1x/F1z
A1x/F1z
F2x F2y
F2z
…
Complete row possible to calculate mode shape ☺
F9x F9y F9z Unrestricted © Siemens AG 2019 Page 46
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Modal Test Nine Point Modal x Three Directions • Force In the ‘Z’ Direction. (One Direction) • Triaxial Accelerometer Possible Inputs and Outputs A1x
A1y
A1z
A2x
A2y
A2z
…
A9x
A9y
A9z
F1x F1y F1z
A1x/F1z
A1y/F1z
A1z/F1z
A1x/F2z
A1y/F2z
A1z/F2z
A1x/F9z
A1y/F9z
A1z/F9z
F2x F2y
F2z
… F9x F9y F9z Unrestricted © Siemens AG 2019 Page 47
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Modal Test Nine Point Modal x Three Directions • Force In the ‘Z’ Direction. (One Direction) • Triaxial Accelerometer Possible Inputs and Outputs A1x
A1y
A1z
A2x
A2y
A2z
…
A9x
A9y
A9z
F1x F1y F1z
A1x/F1z
A1y/F1z
A1z/F1z
A1x/F2z
A1y/F2z
A1z/F2z
A1x/F9z
A1y/F9z
A1z/F9z
F2x F2y
F2z
Incomplete!
… F9x F9y F9z Unrestricted © Siemens AG 2019 Page 48
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Shaker Testing
Response
Time Consuming to setup Control frequency range Control Force Amplitude Better for larger structures Typically fixed excitation point, multiple response points - measured in batches
Frequency
Input
Time
FRF
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Coherence Coherence is a value from 0 to 1 that shows how much of the output is really due to the input 1
/
0
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Coherence 1.00
/ Real
Coherence differs from 1 in case of: • Non-Linearity • Unmeasured sources • Node • Frequency range of excitation • Other noise
F F F F
Coherence Coherence Coherence Coherence
DRV:1:+X DRV:2:+X ENG:1:+Y FUSL:5:+X
0.00 0.00
Hz
100.00
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Pretrigger Pretrigger is the amount of “buffer time” measured before the impulse
▪ Lose initial part of the input signal ▪ Use a pretrigger to avoid distorted FRF
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DEMONSTRATION: Modal Impact Test
Acquisition parameters
Joseph did help us a lot … 4 3 2 1 0 -1 -2
Joseph Fourier
-3
(º1768 - †1830)
Théorie analytique de la chaleur (1822)
-4
• Fourier’s law of heat conduction 2.5 2
2u 2u u k 2 2 t x y
1.5 1 0.5 0 -0.5 -1 -1.5 -2 -2.5
Any signal can be described as a combination of sine waves of different frequencies
• Analyzed in terms of infinite mathematical series
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Fourier Transform Transforms from Time Domain to Frequency Domain • Fourier: “Any signal can be described as a unique combination of sine waves of different frequencies and amplitudes” • Complicated signals become easier to understand Amplitude
Amplitude
Amplitude
Time (seconds)
Frequency (Hz)
No information is lost when converting! Unrestricted © Siemens AG 2019 Page 62
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“What is leakage?”
When the spectral content of your signal does not correspond to an available spectral line.
f 1 Hz 5 V Sine Wave - 2.5 Hz
5 V Sine Wave - 3 Hz
5V
5V
1
2
3
4 Hz
63
5
6
1
2
3
4
5
6
Hz
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Periodic Signals
T
FFT stiches time over infinity
T = N t
Are these signals the same?
YES!
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Non-Periodic Signals
T
T = N t Are these signals the same?
NO!
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Time Frequency
! Unrestricted © Siemens AG 2019 Page 66
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DSP Error: Leakage
Smearing of spectral content across ALL FREQUENCIES
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Cause of leakage: Non Periodic Signals
T
T = N t
Sharp impulse leakage
Must be removed
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Windows: Minimize Leakage
Original signal
Window function
1
x
0
= Windowed signal
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Windows: Minimize Leakage
No longer have “impulse” in signal
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How to minimize leakage? Windows.
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Window Types – Specific Characteristics Hanning
Flat top
AKA No Window
Freq. domain
Time domain
Rectangular, uniform
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Amplitude Errors
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Energy Errors
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Window Types – Specific Characteristics
Windows distort the amplitude and total energy content of the data. They also smear the frequency content. This smearing cannot be corrected. Unrestricted © Siemens AG 2019 Page 77
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Windows
Windows limit spectral resolution Hanning: 1.5 f Up to 15% amplitude
Flattop: 3.4 f Up to 0.02% amplitude
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Exponential Window for Response
• •
Exponential Window Increases Apparent Damping Values When Applied. Avoid Applying The Exponential Window Unless Absolutely Necessary.
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Driving Points
Measuring of Frequency Response Functions Excitation Degrees of Freedom (DOF)
1
2
Natural Modes of vibration
1
3
2
3
Response DOF
Mode 1
1 Mode 2
2
3 Mode 3
Driving point FRFs Unrestricted © Siemens AG 2019 Page 81
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Driving Point FRF Selection and verification of excitation locations • Are all modes present in driving point FRF ? • At nodal point: mode is not excited • Spatially separated
Good excitation point
Bad excitation point
Measure Driving Points for a number of positions and compare FRFs Unrestricted © Siemens AG 2019 Page 83
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Driving Point Survey
FRF Point:1
Survey Location Point:1
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Driving Point Survey
FRF Point:1
FRF Point:2
Survey Location Point:2
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Driving Point Survey
FRF Point:1
FRF Point:2
FRF Point:3
Survey Location Point:3
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Driving Point Survey
FRF Point:1
FRF Point:2
FRF Point:3
FRF Point:4
Survey Location Point:4
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Driving Point Survey
FRF Point:1
FRF Point:2
FRF Point:3
FRF Point:4
FRF Point:5 Survey Location Point:5
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Driving Point Survey
FRF Point:1
FRF Point:2
Which is the FRF Point:3 appropriate excitation point? FRF Point:4
FRF Point:5 Survey Location Point:6
FRF Point:6
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Driving Point Survey
FRF Point:1
FRF Point:2
FRF Point:3
FRF Point:4
FRF Point:5 Survey Location Point:6
FRF Point:6
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Tips for modal testing
Boundary Conditions – What are your Goals?
Real boundary conditions • Flexibility of fixtures • Added damping, stiffness, mass • Environmental Conditions
“Free-free” suspension • Soft spring, elastic cord • Pneumatic suspension • Correlation with FEM •Can Obtain Rigid Body Modes
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Boundary Conditions – simulating free-free Pneumatic suspension
Elastic cords
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Boundary Conditions Some Practical Examples – Operational Conditions
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Rigid Body Modes – Rigid Body Properties Free-Free Boundary Condition • Approximation of a true “Free System” (FEM) • Rigid Body Modes Are No Longer Zero – Negligible Effect on Flexible Mode
Rigid body mode frequency < 10 % of first flexible mode Unrestricted © Siemens AG 2019 Page 95
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SDOF Peak Picking
Calculation of mode shape
1st Bending Mode
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Calculation of mode shape
1st Torsional Mode
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Experimental Modal Analysis
How do we know we have enough measurement points for our test?
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DEMONSTRATION: SDOF Peak Picking on Plate (6 points)
MDOF Curve Fitting
Structure with High Modal Separation
Amplitude
SDOF peak picking is only suitable for data with well-separated modes
No influence from surrounding modes
Frequency Unrestricted © Siemens AG 2019 Page 103
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Amplitude
Structure with Low Modal Separation
MDOF curve fitter is required to separate closely-spaced modes
Large influence from surrounding modes
Frequency
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Modal Parameter Estimation
Goal of modal parameter estimation
H () i 1
vi liT j i
v l
• What is the model order? • How many modes to curve-fit?
* i
H i * i
j
(m/s2)/N Log
n
0.10
Solutions • Stabilization diagram • Mode indicator functions 24.09
10.0e-12 0.00
42.72 Hz
80.00
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Modal Parameter Estimation – Assume 1 Mode f1 = 50 Hz
Amplitude
d1 = 20 %
25
50
75
Frequency
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Modal Parameter Estimation – Assume 2 Modes
f2 = 75 Hz
d1 = 10 %
d2 = 10 %
Amplitude
f1 = 25 Hz
25
50
75
Frequency
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Modal Parameter Estimation – Assume 3 Modes
f2 = 50 Hz
f3 = 75 Hz
d1 = 5 %
d2 = 5 %
d3 = 5 %
Amplitude
f1 = 25 Hz
25
50
75
Frequency
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Modal Parameter Estimation – Stabilization Diagram ▪ Compare modal parameters at current order with previous order ▪ Increase the model order until modes stabilize
n : new pole : frequency : damping : all
Model Order
o f d s
Amplitude
Stability
0 Frequency
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DEMONSTRATION: MDOF Curve Fitting on Flat Plate
Mode Indicator Function Mode Indicator Function (MIF) helps identify the modes for a system where multiple reference FRFs were measured ▪ commonly used to detect the presence of repeated roots
Double “dip” indicates two modes at same frequency
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Why are rigid body modes seen at high frequencies?
Modal Assurance Criterion Modal Assurance Criterion (MAC) describes how similar the shapes are for a given mode pair using a scale of 0 to 1 (e.g. 0% to 100%)
1 .5 0
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MAC Example
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MAC = 100% correlation Siemens PLM Software
MAC Example
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MAC = 0.015 (1.5% correlation) Siemens PLM Software
MAC Example
6 Points
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764 Hz and 385 Hz - MAC = 0.96 (96% correlation) Siemens PLM Software
MAC Example
15 Points
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764 Hz and 385 Hz - MAC = 0.03 (3% correlation) Siemens PLM Software
MAC for flat plate with 6 DOFs
1
.5
0
Unrestricted © Siemens AG 2019 Page 118
Spatial Aliasing – not enough response points Siemens PLM Software
DEMONSTRATION: SDOF Peak Picking on Plate (15points)
MAC for flat plate with 15 DOFs
1
.5
0
No High Off Diagonal Correlations Unrestricted © Siemens AG 2019 Page 120
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Polymax MDOF Curve Fitting
LSCE versus LMS PolyMAX LSCE
LMS PolyMAX
-For smaller models
+Large number of responses
-High computational load
+Fast, efficient computation
-High damping is a problem
+High damping no problem
-High modal density
+High modal density
-Not for broadband analysis
+Broadband analysis
-Unclear stabilization diagram
+Crystal-clear stabilization diagram
Not all MDOF curve fitters are created equal ! Unrestricted © Siemens AG 2019 Page 122
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Modal Parameter Estimation - LSCE
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Modal Parameter Estimation – LMS Test.Lab PolyMax
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DEMONSTRATION: PolyMAX Modal Analysis
PolyMAX Validation Studies
Validation Study of PolyMAX Algorithm
FE model of a full trimmed car body • Synthesized a set of FRFs to use for curve fitting • FRFs generated for 780 DOF / 2 references • 0.125 Hz frequency resolution • 300 modes in 0-100 Hz band, including local modes
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PolyMax Validation – Identifying Modes Number of modes found • PolyMAX: 189/300 modes • LSCE(Time MDOF): 101/300 modes • 0 – 60 Hz band • PolyMAX: 90/105 modes • LSCE: 70/105 modes Possibly more modes found if more FRFs used (local modes)
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PolyMax Validation – Comparing Mode Shapes
MAC matrix
▪ MAC matrix
LSCE (X) – FE (Y)
▪ PolyMAX (X) – FE (Y)
PolyMAX yields good correlation to higher frequency Unrestricted © Siemens AG 2019 Page 129
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PolyMax Validation – “Noisy” FRFs 1.00
/ Amplitude
(
Log
(m/s2)/N
)
1.00
10.0e-6 4.00
Hz Linear
20.00
180.00 4.00
Linear
20.00
F F
° Phase
Hz
Coherence w ing:vvd:+Z/Multiple Coherence back:vde:+Y/Multiple
0.05
-180.00 Hz
Multiple Coherence
Hz
FRFs
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PolyMax Validation – “Noisy” FRFs
LSCE Unrestricted © Siemens AG 2019 Page 131
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PolyMax Validation – “Noisy” FRFs
LMS PolyMAX Unrestricted © Siemens AG 2019 Page 132
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PolyMax Validation – FRF Synthesis with PolyMax
g/N
( ) Log
10.0e-3
( ) Log
g/N
0.10
100e-6 4.00
Hz Linear
20.00
1.00e-6 4.00
Hz Linear
20.00
180.00 4.00
Linear
20.00
180.00 4.00
Linear
20.00
Hz
° Phase
° Phase
Hz
-180.00
-180.00 Hz
Left wing
Hz
Back of the plane
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PolyMax Validation – Lightly Damped Structures
Stabilization
FRF synthesis
) Log (
(m/s2)/N
1.00
10.0e-6 10.00 180.00 10.00
Hz Linear
64.00
Linear
64.00
° Phase
Hz
-180.00 10.00
Hz
64.00
PolyMAX alleviates the need to use a different curve fitter algorithm for heavy and lightly damped structures Unrestricted © Siemens AG 2019 Page 134
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Advanced Techniques
#1 – Automatic Mode Expansion
Test Mesh
STL File Unrestricted © Siemens AG 2019 Page 136
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DEMONSTRATION: Modal Expansion
Multi-Run Modal: Transmission
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Multi-Run Modal: Transmission
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Multi-Run Modal: Transmission
MOVE 1
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Multi-Run Modal: Transmission
MOVE 1
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Multi-Run Modal: Transmission
MOVE 1 MOVE 2
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Multi-Run Modal: Transmission
MOVE 1 MOVE 2
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Multi-Run Modal: Transmission
MOVE 1 MOVE 2
MOVE 3
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Multi-Run Modal: Transmission
MOVE 1 MOVE 2
MOVE 3
Are the frequencies of the structure the same between Move 1, Move 2 and Move 3? Unrestricted © Siemens AG 2019 Page 145
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Multi-Run Modal: Transmission
Could one versus all accelerometers make a difference?
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Multi-Run Modal: Transmission
Which one of these mode shapes is more likely to be affected by accelerometer mass loading? Unrestricted © Siemens AG 2019 Page 147
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Multi-Run Modal: Transmission
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Multi-Run Modal: Transmission
Does placing at top versus bottom have different frequency shift effect? Unrestricted © Siemens AG 2019 Page 149
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MOVE 3 A/F
MOVE 2 A/F
MOVE 1 A/F
Multi-Run Modal: Transmission
Hz
Hz
Which Frequency is right? Unrestricted © Siemens AG 2019 Page 150
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Multi-Run Modal: Transmission 1.18
1.00
Amplitude
g/N Amplitude
MOVE 1
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Sum FRF SUM 0.01 404.43 404.43
Siemens PLM Software
Hz
915.01 0.00 915.01
Multi-Run Modal: Transmission
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Multi-Run Modal: Transmission 1.00
ALL MOVES
EVEN THIS ONE IS EFFECTED
Amplitude
g/N Amplitude
0.89
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Sum FRF SUM 0.01 404.43 404.43
Siemens PLM Software
Hz
915.01 0.00 915.01
Multi-Run Modal: Transmission – All Data Sets
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Multi-Run Modal: Transmission – Single Data Set
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MOVE 1 A/F
Multi-Run Modal: Transmission
MOVE 2 A/F
Partial Shape 1
MOVE 3 A/F
Partial Shape 2
Partial Shape 3
Hz
Hz
Complete Shape Unrestricted © Siemens AG 2019 Page 156
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Multi-Run Modal: Transmission
ANALYZE ALL MOVES AT ONCE
ANALYZE EACH MOVE SEPARATELY AND COMBINE (MULTI-RUN)
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DEMONSTRATION: Multi Run Modal
Correlation
“Old” Product Design Cycle Product Design Process
TIME
Functional Activities Unrestricted © Siemens AG 2019 Page 161
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“Modern” Product Design Process Product Design Process ▪ Simulate product performance before prototypes are available
TIME ▪ Use single prototype & testing for validation
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Pretest & Correlation: Process Improvement
Product 1
Product 2
TIME
TIME
Correlation
Correlation
Pretest
Pretest
Analysis
Analysis FE Modeling
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Process Improvement Siemens PLM Software
Pretest & Correlation: Motivation COST !
▪ Minimize Failures
▪ FEA accuracy degrades as mode order increases ▪ Simulation results are used for design decisions in Acoustics, NVH, Durability, Loads, etc…
▪ Reduce Warranty Issues ▪ Improve customer satisfaction
▪ Shorten Product Design Cycle • Single prototype for validation
▪ Achieve “Design Right First Time”
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Modal Assurance Criterion ▪ Modal Assurance Criterion (MAC) describes how similar the shapes are for a given mode pair using a scale of 0 to 1
1 .5 0
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MAC Example
MAC = 100% Unrestricted © Siemens AG 2019 Page 166
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MAC Example
MAC = 1.5% Unrestricted © Siemens AG 2019 Page 167
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MAC Example
6 Points
764 Hz and 385 Hz - MAC = 96% Unrestricted © Siemens AG 2019 Page 168
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MAC Example
15 Points
764 Hz and 385 Hz - MAC = 3% Unrestricted © Siemens AG 2019 Page 169
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Application Case: Exhaust System
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Exhaust Mode at 15 Hz
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Exhaust Mode at 15 Hz
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Exhaust Modes at 15 and 130 Hz
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Exhaust Modes at 15 and 130 Hz
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6 Exhaust Modes up to 137 Hz
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FEA Model Pretest, Correlation, Updating Tools Simcenter Testlab
Simcenter3D
•
•
• • •
View and Animate Modes from Simulation (Nastran, Abaqus, Ansys, etc) and Test View and overlay FRFs (Nastran) from Simulation and Test Modal Data Acquisition (Shakers, Impact) Mode Shape Correlation (MAC)
•
• • • •
View and Animate Modes from Simulation (Nastran, Abaqus, Ansys, etc) and Test (Universal file and Testlab) View and overlay FRFs (Nastran) from Simulation and Test (Universal File) Pretest Analysis Mode Shape Correlation (MAC) MAC Contribution Updating via Solution 200 in Nastran
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Application Case: Pretest Analysis Step 1: Use FE model to pick some initial accelerometer locations
Supported FEA Software: •NASTRAN •ANSYS •Abaqus •IDEAS •Universal File Format
Initial Accel locations
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Application Case: Pretest Analysis Step 2: Use MAC to assure that accelerometer locations are sufficient to uniquely identify all modes from FEM Normal Modes Analysis MAC: Modal Assurance Criterion A measure of how well mode shapes are correlated. In this case, the MAC diagram shows large off-diagonal terms, indicating that several modes are non-uniquely identified. Thus, more accelerometers are required to guarantee a good test.
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Application Case: Pretest Analysis Step 3: Use Pretest to automatically locate additional accelerometers to meet requested MAC criterion.
• 5 accelerometers have been added to the exhaust model as shown to reach the target offdiagonal MAC of <0.15
Additional Accel’s
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Application Case: Pretest Analysis Step 3: Use Pretest to automatically locate additional accelerometers to meet requested MAC criterion.
• New MAC diagram shows all modes uniquely identified. This is indicated by reduction of offdiagonal terms.
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Simcenter3D Pretest and Correlation
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Application Case: Pretest Analysis Step 5: Create wireframe geometry for Modal Test and export to Simcenter Testlab software. • A Testlab project file is created containing the exhaust geometry, as well as the FE mode shapes & frequencies. • Reduced FE modes provide the test engineer with the ability to visually check the shapes.
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Application Case: Modal Test Perform the modal test on the physical structure. • The test engineer mounts accelerometers, and collects modal data by exciting the structure with shakers or an impact hammer in the locations as indicated by Pretest.
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Application Case: Correlation Step 1: Use the Correlation Manager to import the Test and FE Models, and define correlation parameters.
Parameters: ▪
MAC threshold value for matching of FE/Test mode pairs
▪
Coordinate system translations and rotations
▪
Frequency range for both FE and Test
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Application Case: Correlation Step 2: Use Correlation Tools to evaluate how well FE and Test models correlate.
Global MAC plot shows: • Good mode shape: correlation of modes 1-8 • Mode swapping between modes 11 and 13 for FE and Test models • MAC <0.75 for modes 9-13
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Application Case: Correlation Step 2: Use Correlation Tools to evaluate how well FE and Test models correlate.
Relative Frequency Difference plot shows: • Small frequency differences • < 6% for modes 1-9
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Are results close enough? Although initial inspection might lead us to assume this is good correlation, further analysis yields a different conclusion… • Correlation of fundamental modes does not guarantee correlation throughout operating frequency band • Higher order modes are relevant to acoustic, vibration, and durability performance – they are well within the operating frequency range • Ignoring higher order mode correlation could lead to bad engineering decisions, for example: - Poor Exhaust Hangar locations leading to Noise and Vibration Issues - Vibration fatigue due to Engine or Road excitation at resonant frequencies CONCLUSION: All modes in operating frequency band should be correlated!
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MAC Contribution Step 2: Use Correlation Tools to evaluate how well FE and Test models correlate. MAC Contribution Display: • Shows DOFs making most negative contribution to MAC In this case: • 9 DOFs can be removed to improve MAC from 85% to 95% for Mode Pair 1, 1
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MAC Contribution
TEST
FE
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MAC Contribution
TEST
FE
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MAC Contribution
TEST
FE
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MAC Contribution
MAC WILL NOT CHANGE MUCH
TEST
FE
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MAC Contribution
MAC WILL CHANGE A LOT
TEST
FE
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Application Case: Sensitivity & Updating Step 4: Sensitivity Analysis and FE Model Updating Sensitivity Analysis: •Consideration of physical exhaust system leads engineer to consider effect of weld on this junction (ignored in the FE model) FE Model Updating: • Manual updating • Element thickness increased locally in weld location • Amount of thickness increase guided by MAC and Frequency correlation
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Application Case: Sensitivity & Updating Sensitivity: Ranks the contribution of various parameters of the FE model to its modal behavior. Updating: Changing the FE model to improve it’s correlation to Test results. Sensitivity & Updating Options: • Manual inspection & manual updating using correlation indicators •Sensitivity Analysis & Nastran SOL200 FE Model updating
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Application Case: Results MAC Correlation
• Improved from 0.69 to 0.8 • Mode swapping eliminated
Frequency Correlation • Improved from max 15% error to 6%
• Improved from max 23 Hz error to only 8 Hz
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Application Case: Summary Pretest Analysis was used to ensure reliable Modal Test results: • Automated wireframe creation • Optimized accelerometer/exciter locations • FE mode visualization
Correlation Analysis leveraged Modal Test results to obtain a reliable Finite Element Model
• Full frequency and mode shape correlation • Insight was provided into physical parameters of model causing correlation issues • FE Model was Updated to improve reliability • Critical Design decisions (exhaust hangar location, fatigue life estimation, etc.) were made based on complete and correct information
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Pretest & Correlation: Conclusion Modal Tests must validate product designs
• Reliability of test results depend upon accelerometer and shaker/impact placement
FE/Test Correlation is Key to “Design Right First Time” • Fundamental mode correlation is not enough • Higher order modes are most difficult to correlate
Simcenter3D Pretest & Correlation Increases Reliability of FE Models and Test Results • FE Models accurate over entire operating frequency range • Test results capturing all modes uniquely • Design decisions based on the complete and correct information
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QUIZ
What can an FRF tell you? 16.0
(m/s2)/N Amplitude
Resonant Frequency
Damping
14.0 13.0 12.0 11.0 10.0 9.0 8.0 7.0 6.0 5.0 4.0 3.0 2.0 0.0 10.00
Hz Linear
950.00
180 10.00
Linear
950.00
Mode Shape ➢ Requires Multiple FRFs
° Phase
Hz
-180 10
100 150 200 250 300 350 400 450 500 550 600 650 700 750 800 850
950
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What is this? 10.4
g/lbf Amplitude
ss ss ss ss ss ss ss ss ss ss ss ss ss ss ss ss ss df sd dd df f df f o
sv sv sd sv sv sf os s fs s s s s s s s s s s s s s s s o f o
s s s s s s s s s s s s s s s s s s s s s s s s s s s s s s s s s s v v ov o v v s o o
s s s s s s s s s s s s s s s s s s s s s s v o
o
s s s s s s s s s s s s s s s s s s s s s s s d f s o
s s s s s s s s s s s s s s s s s s s s s s o
s s f s d v f s s s f s s s v s d s v s df f s ss o s s s s s f s ss s dv s df s ss s sv s f o s d s s d d f v d d f f f s f o o o o
o o
d d d d d o
o o
32 31 30 29 28 27 26 25 24 23 22 21 20 19 18 17 16 15 14 13 12 11 10 9 8 7 6 5
63.3e-3 85.1
Linear Hz
837
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What is MAC abbreviation for?
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What is MAC abbreviation for?
Modal Assurance Criterion
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What is MAC abbreviation for?
Modal Assurance Criterion
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IS THIS A “GOOD” MAC?
205 copyright LMS International - 2005
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