Title: An Approach to Properly Account for Structural Damping, FrequencyDependent StiffnessDamping, and to
1An Approach to Properly Account for Structural
Damping, Frequency-Dependent Stiffness/Damping,
and to Use Complex Matrices in Transient Response
2Or (more simply)Some Uses for Fourier Transforms
in Transient Analysis
3Overview
- Transient Response analysis has a number of
limitations - It requires an approximation be used to model
structural damping - It does not support frequency-dependent elements
- It does not allow complex matrices
- Obtaining steady-state solutions to multiple
rotating imbalances can take very long
4Fourier Transforms in Transient
- All of these limitations can be overcome by using
Fourier Transforms - In 1995 Dean Bellinger presented a paper of
Fourier Transforms - His paper, plus the Application Note on Fourier
Transforms, provides the documentation on this
approach
5Fourier Transforms in Transient
- The user interface is simple
- Set up your file for transient response
- Change the solution to 108 or 111
- Add a FREQ command to CASE CONTROL
- Add a FREQ1 entry to the BULK DATA
- Use a constant DF 1/T
- Where T the duration/period of the transient
event - Make sure that the duration/period of the load is
correct (TLOAD1/2 duration is T)
6Fourier Transforms in Transient
- Verify the transformation by plotting the applied
load (sample input in paper) - Sample three simultaneous sine inputs (1hz,
2hz, and 3hz) with a 1.0 second duration
7Applied Load in Transient
8Load after Fourier Transform
Duration of TLOAD2 Is 1.0, therefore, DF1./1.1.
9Load after Fourier Transform
Poorly selected Input for FREQ1 Although DF is
1.0, the Starting frequency is .5, Resulting in
a poor transformation
wrong input freq1,99,.5,1.,3 DLOAD,1,1.,1.,10,1.
,20,1.,30 T 1.0 TLOAD2,10,25,,,0.,1.,1.,-90. T
LOAD2,20,25,,,0.,1.,2.,-90. TLOAD2,30,25,,,0.,1.,3
.,-90. DAREA,25,1,1,1. TSTEP,20,100,.01,
10Compare the Results
Original Load
Good Fourier Transform
Bad Fourier Transform
11Structural Damping
- Handled correctly, it forms a complex stiffness
matrix - Ktotal K(1iG) iSKeGe
- Unfortunately, transient response does not allow
complex matrices, so we must approximate
structural damping using -
- Btotal B KG/W3 SkeGe/W4
- Where w3 and w4 are the dominant frequency of
response
12Structural Damping
- If the actual response is at a frequency less
than w3, the results have too little damping, if
it is at a frequency greater than w3, the results
have too much damping - This means that unless you are performing a
steady-state analysis, your damping will not be
handled correctly - Using Fourier Transforms allows you to apply
structural damping properly
13Multi-Frequency Steady-State
- Many structures (engines, compressors, etc) have
multiple rotating bodies - In many cases, they are not all rotating at the
same frequency - In order to handle this in conventional Transient
analysis, it requires a very long integration
interval to reach the steady-state response - With Fourier transforms, it is easy to solve for
the steady-state solution
14Multi-Frequency Steady-State
- As an example, let us look at a typical jet
engine model with 3 rotating imbalances
15Multi-Frequency Steady-State
- All right, how about this model?
Model courtesy of Pratt and Whitney
16Multi-Frequency Steady-State
- Although rotating imbalances in jet engines occur
at much higher frequencies, for this example, I
will use .5hz, 1.0hz, and 2.0hz
Rotating in opposite direction
dynamic loading dload,101,1.,1.,1002,1.,1003,1
.,2002 ,1.,2003,1.,3002,1.,3003 tload2,1002,12,,
,0.,10.,1.,-90. tload2,1003,13,,,0.,10.,1.,0. forc
e,12,660001,,10.,,2., force,13,660001,,10.,,,2.
tload2,2002,22,,,0.,10.,2.,90. tload2,2003,23,,,0.
,10.,2.,0. force,22,670001,,10.,,4., force,23,6700
01,,10.,,,4.
tload2,3002,32,,,0.,10.,.5,0. tload2,3003,33,,,0.,
10.,.5,90. force,32,680001,,10.,,1., force,33,6800
01,,10.,,,1. eigrl,10,,,10 tabdmp1,1,crit ,0.,.0
1,1000.,.01,endt tstep,103,100,.02 set
delta F1/T freq1,102,.5,.5,5
17Multi-Frequency Steady-State