Derive the frequency equation for uniform pinned-clamped beam (Fig. 16.16)
The initial parameters and kinematical conditions are shown in Fig.16.16. At the right support the displacement and slope are zero. Therefore we need to use expressions for displacement and slope at any section x
\begin{aligned}& Y(x)=Y_0 S(k x)+\theta_0 \frac{1}{k} T(k x)+\frac{M_0}{k^2 E I} U(k x)+\frac{Q_0}{k^3 E I} V(k x) \\& \theta(x)=Y_0 k V(k x)+\theta_0 S(k x)+\frac{M_0}{k E I} T(k x)+\frac{Q_0}{k^2 E I} U(k x)\end{aligned} (a)
Taking into account initial conditions \left(Y_0=0, M_0=0\right) expressions for right fixed support are
\begin{aligned}& Y(l)=\theta_0 \frac{T(k l)}{k}+Q_0 \frac{V(k l)}{k^3 E I}=0 \\& \theta(l)=\theta_0 S(k l)+Q_0 \frac{U(k l)}{k^2 E I}=0\end{aligned} (b)
Thus, the homogeneous linear algebraic equations with respect to \theta_0 and Q_0 are obtained. This system has a nontrivial solution if and only if the following determinant, which represents the frequency equation, is zero
\left[\begin{array}{cc}\frac{T(k l)}{k} & \frac{V(k l)}{k^3 E I} \\S(k l) & \frac{U(k l)}{k^2 E I}\end{array}\right]=0 \rightarrow T(k l) U(k l)-S(k l) V(k l)=0 (c)
According to Krylov-Duncan relationships (16.26, second row), we can present this equation in the trigonometric form
\begin{aligned} & S T-U V=\frac{1}{2}(\cosh k x \sin k x+\sinh k x \cos k x) \\ & T U-S V=\frac{1}{2}(\cosh k x \sin k x-\sinh k x \cos k x) \\ & S^2-U^2=\cosh k x \cos k x ; \quad T^2-V^2=2\left(S U-V^2\right)=\sinh k x \sin k x \\ & U^2-T V=\frac{1}{2}(1-\cosh k x \cos k x) ; \quad S^2-T V=\frac{1}{2}(1+\cosh k x \cos k x) \\ & T^2-S U=S U-V^2=\frac{1}{2} \sinh k x \sin k x ; \quad 2 S U=T^2+V^2 \end{aligned} (6.26)
\cosh k l \sin k l-\sinh k l \cos k l=0 \rightarrow \tan k l=\tanh k l
The roots of this transcendental equation are \lambda_1=k_1 l=3.9266, \quad \lambda_2=k_2 l=7.0686, \cdots
The frequencies vibration are \omega_i=k_i^2 \sqrt{\frac{E I}{m}}=\frac{\lambda_i^2}{l^2} \sqrt{\frac{E I}{m}}, \quad i=1,2, \cdots Corresponding first and second modes (eigenfunctions) are shown in Fig. 16.16. The nodal points N of eigenfunctions for the first mode are located at the supports; for second modeat the supports and additional point N in the span. For third form the nodal points at the span located at x / l=0.308 and 0.616 (Table A.24).
Table A.24 Frequency equation, eigenvalue and nodal points for one-span uniform beams, k^4=\frac{m \omega^2}{E I} | |||||
# | Type of beam | Frequency equation | n | Eigenvalue \lambda_n | Nodal points \xi=x / l of mode shape X |
1 | Pinned-pinned | \sin k_n l=0 | 1 | 3.14159265 | \begin{aligned} & 0 ; 1.0 \\ & 0 ; 0.5 ; 1.0 \\ & 0 ; 0.333 ; 0.667 ; 1.0\end{aligned} |
2 | 6.28318531 | ||||
3 | 9.42477796 | ||||
2 | Clamped-clamped | \cos k_n l \cosh k_n l=1 | 1 | 4.73004074 | \begin{aligned} & 0 ; \quad 1.0 \\ & 0 ; 0.5 ; 1.0 \\ & 0 ; 0.359 ; 0.641 ; 1.0 \\ & \end{aligned} |
2 | 7.85320462 | ||||
3 | 10.9956079 | ||||
3 | Pinned-clamped | \tan k_n l-\tanh k_n l=0 | 1 | 3.92660231 | \begin{array}{llll} 0 ; & 1.0 & \\ 0 ; & 0.440 ; & 1.0 & \\ 0 ; & 0.308 ; & 0.616 ; & 1.0 \end{array} |
2 | 7.06858275 | ||||
3 | 10.21017612 | ||||
4 | Clamped-free | \cos k_n l \cosh k_n l=-1 | 1 | 1.87510407 | \begin{aligned} & 0 \\ & 0 ; \quad 0.774 \\ & 0 ; \quad 0.5001 ; \quad 0.868 \\ & \end{aligned} |
2 | 4.69409113 | ||||
3 | 7.85475744 | ||||
5 | Free-free | \cos k_n l \cosh k_n l=1 | 1,2 | 0 | \begin{aligned} & \text { Rigid-body modes } \\ & 0.224 ; \quad 0.776 \\ & 0.132 ; \quad 0.500 ; \quad 0.868 \end{aligned} |
3 | 4.73004074 | ||||
4 | 7.85320462 | ||||
6 | Pinned-free | \tan k_n l-\tanh k_n l=0 | 1 | 0 | Rigid-body mode \begin{array}{lll} 0 ; & 0.736 & \\ 0 ; & 0.446 ; & 0.853 \end{array} |
2 | 3.92660231 | ||||
3 | 7.06858275 |