Incorporating Advanced Features in Large-Scale Noise and ... - HP
Incorporating Advanced Features in Large-Scale Noise and ... - HP
Incorporating Advanced Features in Large-Scale Noise and ... - HP
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<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong><br />
<strong>Noise</strong> <strong>and</strong> Vibration Simulations
Overview<br />
<strong>Large</strong>-scale l<strong>in</strong>ear dynamics <strong>in</strong> Abaqus is fully<br />
<strong>in</strong>tegrated with our nonl<strong>in</strong>ear offer<strong>in</strong>g<br />
Abaqus l<strong>in</strong>ear dynamics is on par with best-<strong>in</strong>-class<br />
commercial l<strong>in</strong>ear dynamics solvers<br />
Includ<strong>in</strong>g many <strong>in</strong>dustry-unique l<strong>in</strong>ear dynamics features<br />
Current l<strong>in</strong>ear dynamics capabilities are:<br />
Scalable to extreme model <strong>and</strong> frequency ranges<br />
General<br />
Applicable across a wide variety of <strong>in</strong>dustries<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
2
L<strong>in</strong>ear Problems with Nonl<strong>in</strong>ear Preload<strong>in</strong>g
L<strong>in</strong>ear Problems with Nonl<strong>in</strong>ear Preload<strong>in</strong>g<br />
Exp<strong>and</strong><strong>in</strong>g on traditional Abaqus doma<strong>in</strong>s<br />
Tires<br />
Suspension<br />
Brakes<br />
Powertra<strong>in</strong><br />
More accurate solution due to<br />
Nonl<strong>in</strong>ear geometry<br />
Inertial effects<br />
Structural-acoustic coupl<strong>in</strong>g<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
4
Hear<strong>in</strong>g Aid Structural-Acoustic Analysis<br />
Goal is to underst<strong>and</strong> ―feedback path‖<br />
to optimize attenuation<br />
Nonl<strong>in</strong>ear preloads<br />
Viscoelastic components<br />
Structural-acoustic response<br />
Frequency range from 700–7,000 Hz<br />
800 modes < 7 kHz; 3,000 modes < 10.5 kHz<br />
Model size: 1.2 M degrees of freedom<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
5
Hear<strong>in</strong>g Aid Structural-Acoustic Analysis<br />
Analysis steps:<br />
Apply preloads<br />
Analyze frequency response<br />
Includ<strong>in</strong>g viscoelastic effects<br />
– Direct frequency response<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
6
Front Corner Module Modal Analysis<br />
Goal is to capture accurate stiffness <strong>and</strong> modes<br />
Nonl<strong>in</strong>ear:<br />
L<strong>in</strong>ear:<br />
Shock spr<strong>in</strong>g<br />
Shock damper<br />
Shock bush<strong>in</strong>g<br />
Brake l<strong>in</strong><strong>in</strong>g/pads/contact<br />
Upper <strong>and</strong> lower arms<br />
Knuckle<br />
Anti-sway bar<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
7
Front Corner Module Modal Analysis<br />
Nonl<strong>in</strong>ear <strong>and</strong> l<strong>in</strong>ear analysis vs. test<br />
Mode<br />
Shock spr<strong>in</strong>g assembly frequency (Hz)<br />
Test preload<br />
prescribed<br />
L<strong>in</strong>ear analysis<br />
no preload<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
Abaqus<br />
preload<br />
prescribed<br />
8<br />
Suspension<br />
system test<br />
(Hz)<br />
Spr<strong>in</strong>g first axial 70 34 70 70<br />
Spr<strong>in</strong>g second axial 130 100 132 131<br />
Spr<strong>in</strong>g third axial 190 164 192 192
<strong>Large</strong>-<strong>Scale</strong> L<strong>in</strong>ear Dynamics Offer<strong>in</strong>g <strong>in</strong> Abaqus
Key L<strong>in</strong>ear Dynamics Performance Improvements<br />
Development of new l<strong>in</strong>ear architecture<br />
Mode-based steady-state <strong>and</strong> transient dynamics<br />
Initial <strong>in</strong>troduction of user <strong>in</strong>terface features<br />
Creation of Abaqus AMS eigensolver<br />
Substructure redesign<br />
Built on top of new l<strong>in</strong>ear architecture<br />
Added methods for damp<strong>in</strong>g matrix reductions (viscous <strong>and</strong><br />
structural)<br />
Structural-acoustics for large-scale N&V problems<br />
Applicable for full vehicle <strong>in</strong>terior acoustics <strong>and</strong> exterior<br />
acoustics analyses<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
10
Abaqus AMS Eigensolver<br />
Uses multi-level substructur<strong>in</strong>g technique to reduce<br />
the system<br />
Automated approach to component modal synthesis<br />
Global eigenvectors computed only at requested output po<strong>in</strong>ts<br />
Damp<strong>in</strong>g operators projected very efficiently with<strong>in</strong> the<br />
eigensolver<br />
Dramatically improves performance for problems<br />
with many (thous<strong>and</strong>s) of modes<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
11
Full Car Body Frequency Response (Abaqus 6.9)<br />
8 M degrees of freedom structural model<br />
Frequency extraction up to 450 Hz (3,200 modes)<br />
Damp<strong>in</strong>g: Dashpots, connector damp<strong>in</strong>g<br />
Structural response solve time:<br />
4.5 hours AMS<br />
30 m<strong>in</strong>utes for load case with 300 frequency po<strong>in</strong>ts<br />
Coupled structural-acoustic frequency<br />
response analysis<br />
3,200 structural modes + 300 acoustic modes<br />
Structural-acoustic response solve time:<br />
4.5 hours AMS<br />
38 m<strong>in</strong>utes for load case with 300 frequency po<strong>in</strong>ts<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
12
Performance Improvements: AMS Eigensolver<br />
Fully trimmed car body model<br />
9.2 M degrees of freedom<br />
~10,000 modes<br />
Eigenvalue extraction:<br />
23 hours <strong>in</strong> Abaqus 6.8<br />
3 hours <strong>in</strong> Abaqus 6.9<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
13
Structural-Acoustic Frequency Response Analysis<br />
Trimmed car body model<br />
2.9 M degrees of freedom<br />
4,400 modes to 600 Hz (<strong>in</strong>clud<strong>in</strong>g 300 acoustic)<br />
Frequency response analysis<br />
to 400 Hz:<br />
Abaqus 6.8: 7.75 hours<br />
4.5 AMS<br />
3.25 SSD<br />
Abaqus 6.9: 4.0 hours<br />
2.25 AMS<br />
1.75 SSD<br />
For this model NASTRAN solves <strong>in</strong> ~4 hours<br />
us<strong>in</strong>g 4 CPUs<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
14
Frequency-Dependent Materials<br />
Frequency dependency is historically not solvable<br />
with modal approaches<br />
Abaqus readily h<strong>and</strong>les the relevant physics<br />
Typical application—a full vehicle with lam<strong>in</strong>ated<br />
steel panel<br />
Only a small portion of the operator (the frequencydependent<br />
material) needs to be computed <strong>and</strong><br />
projected<br />
Frequency dependency is projected at a few<br />
frequency po<strong>in</strong>ts, <strong>and</strong> results are <strong>in</strong>terpolated<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
15
System Model with Lam<strong>in</strong>ated Steel Component<br />
1.5 M degrees of<br />
freedom<br />
400 modes<br />
~0.05 mm rubber<br />
Operators computed at 10, 40, 100, 300 Hz<br />
Abaqus 6.7: Direct frequency response analysis—<br />
32 hours<br />
Abaqus 6.8: Eigenvalue extraction <strong>and</strong> modal response—<br />
20 m<strong>in</strong>utes<br />
~100× speed-up with mode-based approach<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
16<br />
~0.5 mm steel<br />
~0.5 mm steel
Frequency Response Results—Lam<strong>in</strong>ated Steel<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
Red: Direct response results<br />
Blue: Modal response results<br />
17
Body-<strong>in</strong>-Prime Model with Lam<strong>in</strong>ated Steel<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
10× greater response<br />
Red: Lam<strong>in</strong>ated steel panel<br />
Blue: Steel panel<br />
18
Unsymmetric Dynamic Substructures<br />
Stiffness matrix can be unsymmetric<br />
Viscous damp<strong>in</strong>g matrix can be unsymmetric<br />
Important use case: Substructure representation of roll<strong>in</strong>g<br />
tires<br />
Substructure generation for the base state obta<strong>in</strong>ed from the steadystate<br />
transport analysis of a rotat<strong>in</strong>g tire <strong>in</strong> contact with the road<br />
Stiffness matrix can be unsymmetric due to the contact friction<br />
Viscous damp<strong>in</strong>g matrix can be unsymmetric due to the Coriolis<br />
terms<br />
Abaqus workflow for tires:<br />
Nonl<strong>in</strong>ear static<br />
analysis of a stationary<br />
tire <strong>in</strong>clud<strong>in</strong>g <strong>in</strong>flation<br />
<strong>and</strong> contact footpr<strong>in</strong>t<br />
calculation<br />
Steady-state<br />
transport analysis of<br />
a roll<strong>in</strong>g tire<br />
L<strong>in</strong>ear dynamic<br />
analysis of a s<strong>in</strong>gle<br />
tire<br />
Generation of an<br />
unsymmetric<br />
dynamic<br />
substructure for a<br />
rotat<strong>in</strong>g tire<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
19<br />
Us<strong>in</strong>g tire substructures<br />
<strong>in</strong> the full vehicle<br />
simulations
Example: Frequency Response of a Tire at 60 km/h<br />
FE model: 430 K degrees of freedom<br />
Substructure: 180 dynamic modes, 2 reta<strong>in</strong>ed nodes<br />
FE model compared with tire substructure models<br />
Significantly different results for rotat<strong>in</strong>g vs. stationary<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
20
Full Vehicle with Rotat<strong>in</strong>g Tire Effects<br />
3.4 M degrees of freedom<br />
Structural material damp<strong>in</strong>g<br />
3,200 modes extracted<br />
Rotat<strong>in</strong>g tire effect taken <strong>in</strong>to account us<strong>in</strong>g<br />
unsymmetric substructure<br />
AMS eigenvalue extraction <strong>and</strong> modal frequency<br />
response analysis<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
21
Rotat<strong>in</strong>g Tire Effects<br />
Stationary tire (blue) vs.<br />
roll<strong>in</strong>g tire (red)<br />
Roof vertical deflection<br />
Tire patch lateral<br />
response<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
Dramatic<br />
differences<br />
22
Body Model <strong>Incorporat<strong>in</strong>g</strong> Lam<strong>in</strong>ated Steel<br />
Structural-acoustic<br />
Mode-based frequency<br />
response<br />
Range to 300 Hz<br />
Comparison between steel <strong>and</strong> lam<strong>in</strong>ated steel parts<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
EXAMPLE: Lam<strong>in</strong>ated steel<br />
location/distribution<br />
23
Body Model <strong>Incorporat<strong>in</strong>g</strong> Lam<strong>in</strong>ated Steel<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
24
Summary of Capabilities<br />
Performance<br />
Currently best <strong>in</strong>tegrated offer<strong>in</strong>g<br />
Competitive with best multi-vendor solutions<br />
Functionality<br />
Full set of <strong>in</strong>dustrial l<strong>in</strong>ear dynamics capabilities<br />
<strong>Advanced</strong> mechanics<br />
Lead<strong>in</strong>g-edge capabilities that can be used with even the largest<br />
l<strong>in</strong>ear dynamics models<br />
This comb<strong>in</strong>ation of features readily <strong>in</strong>corporates<br />
nonl<strong>in</strong>ear effects not otherwise captured <strong>in</strong><br />
traditional NV analyses<br />
<strong>Incorporat<strong>in</strong>g</strong> <strong>Advanced</strong> <strong>Features</strong> <strong>in</strong> <strong>Large</strong>-<strong>Scale</strong> <strong>Noise</strong> <strong>and</strong> Vibration Simulations<br />
25
<strong>HP</strong> 8-server Workgroup System Rack<br />
Abaqus/St<strong>and</strong>ard (Structural Analysis)<br />
Server Options:<br />
4-8 ProLiant DL160 (Xeon) or DL165 (Opteron) server nodes, each us<strong>in</strong>g<br />
2 processors<br />
8-12 cores per compute node<br />
Four 72GB SAS drives per compute node<br />
Optional blade workstation with <strong>HP</strong> RGS for pre/post process<strong>in</strong>g<br />
Optional head node with extra memory for very large jobs<br />
Total Memory for Cluster:<br />
Nonl<strong>in</strong>ear dynamics jobs – multiple compute node jobs:<br />
2GB/core suitable for runn<strong>in</strong>g jobs:<br />
Less than 2.5MDOF on 2 nodes<br />
2.5MDOF to 5MDOF on 4 nodes<br />
Greater than 5MDOF on 8 nodes<br />
4GB/core for above jobs, if runn<strong>in</strong>g on fewer nodes<br />
L<strong>in</strong>ear dynamics jobs - s<strong>in</strong>gle compute node jobs: 4GB/core<br />
Optional head node or blade workstation: up to 4GB/core<br />
Cluster Interconnect: Integrated Gigabit Ethernet or Inf<strong>in</strong>iB<strong>and</strong><br />
(recommended for jobs us<strong>in</strong>g more than 2 nodes)<br />
Storage:<br />
4 <strong>in</strong>ternal 72GB SAS drives striped RAID0 on each node<br />
Optional <strong>HP</strong> SFS G3 Cluster File System<br />
Operat<strong>in</strong>g Environment: 64-bit L<strong>in</strong>ux OR Microsoft <strong>HP</strong>C Server 2008<br />
Workloads: Ideally suited for one model greater than 5MDOF or 2-4<br />
simultaneous models less than 5MDOF<br />
26
Thank you