Exact solutions for the buckling of rectangular plates having linearly varying in-plane loading on two opposite simply supported edges
Introduction
For more than a century researchers in structural mechanics throughout the world have endeavored to obtain accurate theoretical results for the critical buckling loads of plates, as well as their corresponding buckling mode shapes. Several thousands of research papers on these topics have appeared in the international scientific and technical journals and in conference proceedings, most of them dealing with rectangular plates. Much of the useful results has been summarized in many texts and handbooks (Timoshenko and Gere, 1963, Volmir, 1967, Bulson, 1970, Japan Column Research Council, 1971, Szilard, 1974, Brush and Almroth, 1975, Trahair and Bradford, 1998).
Rectangular plates subjected to uniform in-plane stresses have been extensively analyzed in the buckling literature because the governing differential equation of equilibrium has constant coefficients, yielding exact solutions for buckling loads straightforwardly when two opposite edges of the plates are simply supported.
Of course, a plate may be loaded at two opposite edges by non-uniform, in-plane, axial forces (Nx), the first variation from the uniform loading being one which varies linearly. A special case of this is a pure, in-plane bending moment. In the non-uniform loading case the analysis is more formidable, and exact solutions are much more difficult to achieve. One finds considerable approximate results for plate buckling loads for such non-uniform stress fields, typically obtained by energy methods. Recently, for the case of linearly varying in-plane loadings some researchers have presented approximate results (Smith et al., 1999a, Smith et al., 1999b, Bradford et al., 2000, Smith et al., 2000). Exact solutions for S-F-S-F (Kang and Leissa, 2001) and S-C-S-C plates (Leissa and Kang, 2002) have also been obtained, where two opposite edges are simply supported and the other two are either free (F) or clamped (C).
Some researchers have also analyzed both the buckling and vibration of rectangular plates subjected to in-plane stress field (Kang and Leissa, 2001, Leissa and Kang, 2002, Bassily and Dickinson, 1972, Bassily and Dickinson, 1978, Dickinson, 1978, Kielb and Han, 1980, Kaldas and Dickinson, 1981). Bifurcation buckling may be regarded as a special case of the vibration problem; that is, determining the in-plane stresses which cause vibration frequencies to reduce to zero.
The present work presents exact solutions for the buckling loads and mode shapes for rectangular plates having two opposite edges simply supported when these edges are subjected to linearly varying in-plane normal stresses. The procedure is applied to all possible combinations of clamped, simply supported or free edge conditions applied continuously along the other unloaded edges. For the case of opposite edges being simply supported, a variables separable solution exists, which reduces the partial differential equation to an ordinary one having variable coefficients. This is solved by the classical power series method of Frobenius, and the convergence of the series is established. Comparisons are also made with results available in the published literature.
Section snippets
Analysis
Consider a rectangular plate of lateral dimensions a × b, as shown in Fig. 1, having its edges x = 0 and x = a simply supported and linearly varying in-plane stresses acting along these two edges, whereas the other two edges (y = 0 and y = b) may be either clamped (C), simply supported (S), or free (F), and have no in-plane stresses. Assuming that the plate is thin, has uniform thickness, and that its material is homogeneous, isotropic and linearly elastic, the differential equation of motion governing
Convergence
The exact solution functions given by Eq. (10) require summing an infinite series. Depending upon the degree of accuracy which one wants to have in numerical calculations, the upper limit of the summation is truncated at a finite number (N), which may be as large as needed. This procedure is no different than that followed in the evaluation of other transcendental functions arising in the exact solutions of other boundary value problems (e.g., trigonometric, hyperbolic, Bessel, Hankel).
To
Buckling loads and mode shapes
It is interesting to observe how the critical buckling load varies as α changes for each boundary condition. Examples of this are shown in Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Fig. 10, Fig. 11, where are plotted versus for the linearly varying edge loadings exhibited in Fig. 2 (α = 0, 0.5, 1, 1.5, 2), for plates having all nine possible combinations of clamped (C), simply supported (S) or free (F) edges at y = 0 and b; S-C-S-C, S-C-S-S, S-C-S-F, S-S-S-C, S-S-S-S,
Conclusions
The foregoing work has shown how an exact solution procedure may be followed to obtain a variety of interesting and useful results for buckling loads and some of their corresponding mode shapes of rectangular plates having two opposite edges simply supported, with those edges being subjected to linearly varying in-plane stresses. The procedure was applied to all possible combinations of clamped, simply supported or free edge conditions applied continuously along the other unloaded edges at y = 0
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