Abstract
The non-planar vibration response of a beam with initial geometric imperfections is investigated through the development of a geometrically nonlinear beam model. The equations of motion are derived through the application of Lagrange’s equation and accounting for the interaction of the initial deviations from straightness and the transverse bending deformations. The experimental frequency response of a nuclear fuel rod supported by two prototypical spacer grids is described by the response in the driven direction and the response in the non-driven direction. The beam model also includes a hysteretic restoring moment at the ends to represent the constraint of the spacer grid and the associated reduction in resonant frequency as the applied force is increased. A pseudo-arc-length continuation algorithm is used to solve the equations of motions and calculate the periodic solution. Comparison between the nonlinear beam model response and the experimental data shows good agreement around the resonant frequency of the first bending mode for both the driven and companion modes.
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The authors acknowledge the financial assistance of the NSERC CRDPJ 530933-18 Grant and the technical support of Framatome Canada Ltd.
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The work was funded through the Natural Sciences and Engineering Research Council of Canada Grant CRDPJ 530933-18.
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BP contributed to the conceptualization, data curation, formal analysis, investigation, methodology, software, visualization, writing—original draft, and writing—review and editing. MA contributed to conceptualization, formal analysis, funding acquisition, investigation, project administration, supervision, writing—original draft, and writing—review and editing.
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Appendix A: Convergence study
Appendix A: Convergence study
A convergence study was made to validate the number of terms in the expansions for the axial and two transverse displacement fields. The nonlinear frequency response was checked to confirm that the model response did not change as more terms were added to the expansions. The nonlinear response is of primary interest due to the sensitivity of the hysteresis model to rotations at the ends of the beam. In the first study, the number of terms in the transverse displacement expansions is M = 7, M = 11, M = 13, and M = 15. In each case, the number of terms in the expansion for the axial displacement is kept equal to the number of terms in the expansions for the transverse displacements. The damping ratio is also kept at a constant value of 1%. The model response for an applied force of 0.1 N and 1.0 N is shown in Fig. 10, and the corresponding resonant frequencies are provided in Table 4. The frequency of the resonance peak of the response changes by less than 0.5% between M = 13 and M = 15.
In the second study, the number of terms in the expansion for the axial displacement is varied while keeping the number of terms in the transverse displacement expansions constant at M = 15. The result was that, when N is greater than 3, the solution is insensitive to additional terms. Therefore, the numerical model with M = 15 and N = 15 is determined to be converged.
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Painter, B., Amabili, M. Non-planar vibrations of beams with geometric imperfections and hysteretic boundary conditions. Nonlinear Dyn 111, 19749–19761 (2023). https://doi.org/10.1007/s11071-023-08916-7
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DOI: https://doi.org/10.1007/s11071-023-08916-7