Abstract
Two ways of incorporating moderate rotations of planes normal to the axis of a straight beam into the Euler–Bernoulli and the Timoshenko micropolar beam theories are presented. In the first case, the von Kármán nonlinear strains are used to incorporate the moderate rotations of normal planes into the beam theories. In the second case, appropriate approximations are made on the nonlinear Cosserat deformation gradient to reflect the condition of moderate rotations of the normal planes. The governing nonlinear differential equations and corresponding natural boundary conditions in both cases are derived using the principle of virtual displacements. A weak-form Galerkin displacement finite element formulation is presented for the developed nonlinear beam theories. The phenomenon of locking usually encountered in beam displacement finite elements is eliminated using higher-order finite elements with nodes located at spectral points. Finally, numerical examples are presented to illustrate the effect of coupling number and bending characteristic length scale on deflections and microrotations when a micropolar beam is modeled with the developed nonlinear beam theories.
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10 October 2020
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Notes
We use superscript E to denote terms corresponding to the Euler–Bernoulli micropolar beam theory.
We use superscript T to denote terms corresponding to the Timoshenko micropolar beam theory.
GLL points are proven to be effective in eliminating the Runge effect in Lagrange interpolation functions, however that is not guaranteed for Hermite interpolation functions. In the present work, we used a maximum of 8 nodes per element, located at spectral points and no Runge effect was observed for Hermite interpolation functions used in Euler–Bernoulli micropolar beam theories.
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Acknowledgements
The authors gratefully acknowledge the support of this research, in parts, through the Oscar S. Wyatt Endowed Chair and a grant from the National Science Foundation (NSF Proposal 1952873).
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Appendices
Appendix A Constitutive relations
The constants in the constitutive relations of Tables 3 and 4 are defined as
where A is the cross section area of the beam.
Appendix B Finite element stiffness matrices
1.1 Appendix B.1 Euler–Bernoulli beam theory
We use the following notation in representing the element stiffness and tangent stiffness matrices of Euler–Bernoulli beam theories.
where \(M,N = \{1,2,3\}\), \(i,j = \{1,2,\dots n\}\) and \(I,J = \{1,2,\dots 2n\}\), where n is the number of nodes in a typical finite element.
1.1.1 Appendix B.1.1. von Kaŕmán micropolar Euler–Bernoulli Beam
The components of the element tangent stiffness matrix are the same as the components of the element stiffness matrix, except for the following terms:
1.1.2 Appendix B.1.2. Micropolar nonlinear Euler–Bernoulli beam
1.2 Appendix B.2. The Timoshenko beam theory
We shall use the following notation in representing the element stiffness and tangent stiffness matrices of the Timoshenko beam theory:
where \(M,N = \{1,2,3,4\}\), \(i,j = \{1,2,\dots n\}\), where n is the number of nodes in a typical finite element.
1.2.1 Appendix B.2.1. The von Kaŕmán nonlinear Timoshenko beam
Similarly, the components of the element tangent stiffness matrix are given by
except for the following terms:
1.2.2 Appendix B.2.2. The micropolar nonlinear Timoshenko beam
Similarly, the components of the element tangent stiffness matrix are given by
except for the following terms:
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Nampally, P., Reddy, J.N. Geometrically nonlinear Euler–Bernoulli and Timoshenko micropolar beam theories. Acta Mech 231, 4217–4242 (2020). https://doi.org/10.1007/s00707-020-02764-x
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DOI: https://doi.org/10.1007/s00707-020-02764-x