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首页> 外文期刊>International Journal of Mechanical Sciences >Exact solutions for vibration and buckling of a SS-C-SS-C rectangular plate loaded by linearly varying in-plane stresses
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Exact solutions for vibration and buckling of a SS-C-SS-C rectangular plate loaded by linearly varying in-plane stresses

机译:通过线性改变面内应力加载的SS-C-SS-C矩形板的振动和屈曲的精确解

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摘要

Exact solutions are presented for the free vibration and buckling of rectangular plates having two opposite edges (x = 0 and a) simply supported and the other two (y = 0 and b) clamped, with the simply supported edges subjected to a linearly varying normal stress σ{sub}x = -N{sub}0[1 - α (y/b)]/h, where h is the plate thickness. By assuming the transverse displacement (w) to vary as sin(mπx/a), the governing partial differential equation of motion is reduced to an ordinary differential equation in y with variable coefficients, for which an exact solution is obtained as a power series (the method of Frobenius). Applying the clamped boundary conditions at y = 0 and b yields the frequency determinant. Buckling loads arise as the frequencies approach zero. A careful study of the convergence of the power series is made. Buckling loads are determined for loading parameters α = 0, 0.5, 1, 1.5, 2, for which α = 2 is a pure in-plane bending moment. Comparisons are made with published buckling loads for α =0, 1, 2 obtained by the method of integration of the differential equation (α = 0) or the method of energy (α = 1, 2). Novel results are presented for the free vibration frequencies of rectangular plates with aspect ratios a/b = 0.5, 1, 2 subjected to three types of loadings (α = 0, 1, 2), with load intensities N{sub}0/N{sub}(cr) = 0, 0.5, 0.8, 0.95, 1, where N{sub}(cr) is the critical buckling load of the plate. Contour plots of buckling and free vibration mode shapes are also shown.
机译:对于矩形板的自由振动和屈曲,给出了精确的解决方案,该矩形板具有两个简单支撑的相对边缘(x = 0和a),并且另外两个夹具(y = 0和b)被夹紧,并且简单支撑的边缘承受线性变化的法线应力σ{sub} x = -N {sub} 0 [1-α(y / b)] / h,其中h是板厚。通过假设横向位移(w)随sin(mπx/ a)变化,将控制的运动偏微分方程简化为y中具有可变系数的常微分方程,为此,可以得到幂级数的精确解( Frobenius的方法)。在y = 0和b处应用钳制边界条件将得出频率行列式。当频率接近零时,会产生屈曲载荷。仔细研究了幂级数的收敛性。确定屈曲载荷用于载荷参数α= 0、0.5、1、1.5、2,其中α= 2是纯面内弯矩。通过微分方程的积分方法(α= 0)或能量的方法(α= 1,2),对已公布的屈曲载荷α= 0、1、2进行了比较。提出了矩形板自由振动频率的新结果,长宽比a / b = 0.5,1,2承受三种类型的载荷(α= 0,1,2),载荷强度为N {sub} 0 / N {sub}(cr)= 0、0.5、0.8、0.95、1,其中N {sub}(cr)是板的临界屈曲载荷。还显示了屈曲和自由振动模式形状的等高线图。

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