## Group Puri

Group Description |
ABAQUS benchmarks: pt.loaded fluid-filled shell. Srinivasan Puri ROM benchmark test matrices. http://sites.google.com/site/srinivaspuri/Home/rom-test-matrices The problem can be found in any ABAQUS Benchmark manual: Section 1.10.2, and is often known as the "acid-test" within the structural-acoustic community. A small description of the problem follows. The Abaqus/Standard Model: This problem involves the steady-state vibration of a point-loaded spherical shell coupled to an acoustic fluid that fills its interior. It is modeled using axisymmetric shell and acoustic elements. The closed form solution of Stepanishen and Cox (2000) is used for validation of the analysis. The basis of the coupled acoustic-structural vibration capability in Abaqus is described in "Coupled acoustic-structural medium analysis," Section 2.9.1 of the Abaqus Theory Manual, and "Acoustic, shock, and coupled acoustic-structural analysis," Section 6.9.1 of the Abaqus Analysis User's Manual. Problem description The model is a semicircular shell and fluid mesh of radius 2.286 m. A point load on the symmetry axis of magnitude 1.0 N is applied to the shell. The shells are 0.0254 m in thickness and have a Young's modulus of 206.8 GPa, a Poisson's ratio of 0.3, and a mass density of 7800.0 kg/m^{3}. The acoustic fluid has a density, of 1000 kg/m^{3} and a bulk modulus, of 2.25 GPa. The response of the coupled system is calculated for frequencies ranging from 100 to 1000 Hz in 5 Hz increments. There are two different finite element meshes used: one with explicitly defined acoustic-structural interaction elements and one that uses the *TIE option. The former model consists of 220 SAX1 elements surrounding a mesh of 15848 ACAX4 elements. Coupling is effected using 220 ASI2A elements. The latter model uses 80 SAX2 elements surrounding a mesh of 965 ACAX8 elements. For this mesh, coupling is effected using the *TIE option to generate the acoustic-structural interaction elements internally. A dummy part is included in the models to ensure that the analytical solution appears in the output database. This part consists of a single point mass, uncoupled from the model described above, with a displacement boundary condition on degree of freedom 1. This imposed displacement uses an amplitude table consisting of the Stepanishen/Cox analytical solution for the drive point admittance. The ANSYS Model & the Higher Dimensional Coupled System Matrices: We generate the required matrices in ANSYS by reading through the ABAQUS documentation and preparing the relevant finite element mesh in ANSYS. This particular model was done with ANSYS V10/V11. A detailed description can be found in and R. S. Puri, D Morrey, J. L. Cipolla (2007) and R. S. Puri (2008). In the ANSYS model, we sweep from 100-1000Hz in 1Hz increments as opposed to 5Hz increments in the ABAQUS model. This is simply for ease of comparison with analytical solutions - since we have closed form solutions at every 1Hz. increments for the undamped case. A diagram of the coupled Finite Element mesh along with the point loading condition/location & the sparsity plots of the coupled stiffness and mass matrices are given at http://sites.google.com/site/srinivaspuri/Home/rom-test-matrices For the undamped model, the matrices can be found in BM_Uda.zip in the Attachments section. For damped models, we have three sub test cases: Low Damping, Moderate Damping, High Damping. The higher dimensional matrices can be found in BM_Ld.zip ; BM_Md.zip ; BM_Hd.zip in the Attachments sections (see "contd.." sub page also). General file description are as follows: full* represents higher dimensional system. full.M: Coupled Mass matrix: Unsymm. (explicit zeros in Mzeros matrix) full.K: Coupled Stiffness matrix: Unsymm. full.E: Structural-Acoustic damping matrix (In this case, we vary only structural damping). full.B: Structural-Acoustic input vector (i.e forcing function for the freq domain simulation) full.C: Output measurement matrix. full.C.names: Description of the output measurement: Not required for model reduction. frequency.txt: Frequencies for frequency domain simulation. (100-1000Hz.) N10945_<ud/ld/md/hd>.txt: Results from direct inversion of the higher dimensional system: Coupled nodal displacements. TSSOAR_N10945_<ld/md/hd>.txt: Results from Two Sided Arnoldi projection: Coupled nodal displacements. closedform.txt: Velocity Results from analytical solution [modal expansion] for the problem. Key: <ud>: undamped; <ld>: low damping; <md>: moderate damping; <hd>: high damping. Coupled System Matrix Properties: Type: Second order, SISO. Format: Matrix Market. Dimension: 23412 x 23412. Mass Matrix: Coupled, Unsymmetric. Stiffness Matrix: Coupled, Unsymmetric. Damping Matrix: Undamped & Structurally Damped Symmetric. Approximation Properties: State Variable to be approximated: Coupled Displacement at driving point location. Eigen Solution: 50 coupled vectors for say Coupled Lanczos projection procedure ; Uncoupled approach: 50 structural and uncoupled acoustic modes till 4000Hz for AMLS projection. Arnoldi Vectors: 100 for undamped via One Sided or Two Sided Arnoldi Process [OSA-TSA]; 110 for damped via Two-Sided Second Order Arnoldi Process [SOAR]. Matrix Extraction Information: [1.0] Undamped Matrices: BM_Uda.zip : No issues to report. You should be able to generate the plots in Figure: 3 and Figure: 4 with minimal effort. [1.1] Damped Matrices: BM_<Ld/Md/Hd>.zip : No issues with Mass and Stiffness Matrices. The damping matrices for the weakly non-linear test cases are assembled from the total Dynamic matrix in ANSYS. That is, ANSYS writes the dynamic, coupled structural-acoustic "supermatrix" as follows: [A] {x} = F ; -- Equation (1) where, [A] is the dynamic "super matrix" which is computed as follows: [A] = -Omega^{2} [M] + i*Omega [E] + [K] ; -- Equation (2) which is directly written to the ANSYS FULL file. It follows from above that the damping matrix can be "back calculated" by using the following relationship: [E] = [Ai] / Omega ; -- Equation (3) where, [Ai] represents the imaginary part of the dynamic coupled structural-acoustic "super matrix". Unfortunately, at this moment, there is no other direct way to extract the damping matrix including linearly varying damping. Shortly speaking, the damping matrix [E] for the coupled structural-acoustic system can be extracted by dividing the imaginary part of the "super matrix" with a high enough frequency. Remarks on Matrix Extraction for Damped Test Cases: For the damped cases, the [E] matrices for the benchmark models were extracted at around 1000Hz, which is close to the end frequency of the analysis range. This above extraction procedure sometimes results in a "non-symmetric" damping matrix rather than a symmetric one, which can be attributed to the very small "round-off" differences at different frequencies. Note also that this "unsymmetricity" is not always the case. In many cases (e.g. ones with lower dimension), the damping matrices are indeed symmetric. Saying that, we note that this should not yield any issues/differences in the dimension reduction process. Please let me know if you do encounter any difficulties or questions on the matrices/reduction process. Results for the linearly damped cases can be found in R. S. Puri (2008). References: Stepanishen, P., and D. L. Cox, "Structural-Acoustic Analysis of an Internally Fluid-Loaded Spherical Shell: Comparison of Analytical and Finite Element Modeling Results," NUWC Technical Memorandum 00-118, Newport, Rhode Island, 2000. Puri, R. S., D. Morrey, and J. L. Cipolla (2007), A comparison between One-sided and Two-sided Arnoldi based model order reduction techniques for fully coupled structural acoustic analysis. In 153rd Meeting of the Acoustical Society of America, The Journal of Acoustical Society of America, Volume 121. R.S. Puri (2008), Krylov Subspace Based Direct Projection Techniques For Low Frequency, Fully Coupled, Structural Acoustic Analysis and Optimization, Ph.D. Thesis, School of Technology, Department of Mechanical Engineering and Mathematical Sciences, Oxford Brookes University, Oxford, UK. E. B. Rudnyi and J. G. Korvink (2006), Model Order Reduction for Large Scale Engineering Models Developed in ANSYS. Lecture Notes in Computer Science, v. 3732, pp. 349-356. If you run into any trouble, do ping me: srinivaspuri[at]gmail[dot].com |
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**all 4**collection matricesId | Name | Group | Rows | Cols | Nonzeros | Kind | Date | Download File |
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2272 | ABACUS_shell_hd | Puri | 23,412 | 23,412 | 218,484 | Model Reduction Problem | 2009 | MATLAB Rutherford Boeing Matrix Market |

2271 | ABACUS_shell_md | Puri | 23,412 | 23,412 | 218,484 | Model Reduction Problem | 2009 | MATLAB Rutherford Boeing Matrix Market |

2270 | ABACUS_shell_ld | Puri | 23,412 | 23,412 | 218,484 | Model Reduction Problem | 2009 | MATLAB Rutherford Boeing Matrix Market |

2269 | ABACUS_shell_ud | Puri | 23,412 | 23,412 | 218,484 | Model Reduction Problem | 2009 | MATLAB Rutherford Boeing Matrix Market |