DESIGN SENSITIVITY ANALYSIS OF STRUCTURE-INDUCED NOISE AND VIBRATION

A continuum design sensitivity analysis (DSA) method for dynamic frequency responses of structural-acoustic systems is developed using the adjoint variable and direct differentiation methods. A variational approach with a non-self-adjoint operator for complex variables is used to retain the continuum elasticity formulation throughout derivation of design sensitivity results. It is shown that the adjoint variable method is applicable to the variational equation with the non-self-adjoint operator. Sizing design variables such as the thickness and cross-sectional area of structural components are considered for the design sensitivity analysis. A numerical implementation method of continuum DSA results is developed by postprocessing analysis results from established finite element analysis (FEA) codes to obtain the design sensitivity of noise and vibration performance measures of the structural-acoustic systems. The numerical DSA method presented in this paper is limited to FEA and boundary element analysis (BEA) is not considered. A numerical method is developed to compute design sensitivity of direct and modal frequency FEA results. For the modal frequency FEA method, the numerical DSA method provides design sensitivity very efficiently without requiring design sensitivities of eigenvectors. The numerical method has been tested using passenger vehicle problems. Accurate design sensitivity results are obtained for analysis results obtained from established FEA codes.

[1]  Donald J. Nefske,et al.  Structural-acoustic finite element analysis of the automobile passenger compartment: A review of current practice , 1982 .

[2]  Zheng-Dong Ma,et al.  Reduction of vehicle interior noise using structural-acoustic sensitivity analysis methods , 1991 .

[3]  H. Saunders,et al.  Modern Automotive Structural Analysis , 1982 .

[4]  E. Dowell,et al.  Acoustoelasticity - General theory, acoustic natural modes and forced response to sinusoidal excitation, including comparisons with experiment , 1977 .

[5]  G. R. Cowper,et al.  Gaussian quadrature formulas for triangles , 1973 .

[6]  G. Gladwell,et al.  On energy and complementary energy formulations of acoustic and structural vibration problems , 1966 .

[7]  D. L. Flanigan,et al.  Application of Acoustic Modeling Methods for Vehicle Boom Analysis , 1984 .

[8]  Zenon Mróz,et al.  Optimal Design of Elastic Structures Subjected to Dynamic, Harmonically‐Varying Loads , 1970 .

[9]  Kyung K. Choi,et al.  Implementation of Design Sensitivity Analysis with Existing Finite Element Codes , 1987 .

[10]  R. H. Macneal,et al.  A New Method for Analyzing Fluid-Structure Interaction Using MSC-NASTRAN , 1979 .

[11]  Tomasz Lekszycki,et al.  Optimal Design of Viscoelastic Structures under Forced Steady-State Vibration , 1981 .

[12]  Masataka Yoshimura Design Sensitivity Analysis of Frequency Response in Machine Structures , 1984 .

[13]  Kyung K. Choi,et al.  Sizing Design Sensitivity Analysis of Dynamic Frequency Response of Vibrating Structures , 1992 .

[14]  Tomasz Lekszycki,et al.  On Optimal Support Reaction in Viscoelastic Vibrating Structures , 1983 .

[15]  Torsten Brama Acoustic design criteria in a general system for structural optimization , 1990 .

[16]  Earl H. Dowell,et al.  Master Plan for Prediction of Vehicle Interior Noise , 1979 .