Abstract
Most engineering artifacts are designed and analyzed today within a 3-D computer aided design (CAD) environment. However, slender objects such as beams are designed in a 3-D environment, but analyzed using a 1-D beam-element, since their 3-D analysis exhibits locking and/or is computationally inefficient. This process is tedious and error-prone. Here, we propose a dual-representation strategy for designing and analyzing 3-D beams, directly within a 3-D CAD environment. The proposed method exploits classic 1-D beam physics, but is implemented within a 3-D CAD environment by appealing to the divergence theorem. Consequently, the proposed method is numerically and computationally equivalent to classic 1-D beam analysis for uniform cross-section beams. But, more importantly, it closely matches the accuracy of a full-blown 3-D finite element analysis for non-uniform beams.
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The authors wish to acknowledge the support of the National Science Foundation under grants OCI-0636206, and CMMI-0726635, CMMI-0745398.
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Appendix: boundary integration for the timoshenko beam
Appendix: boundary integration for the timoshenko beam
In Timoshenko beam theory, the displacements are approximated via (32), where u 0(x), w 0(x) and θ 0(x) are the axial, bending and rotation of a transverse normal about the y-axis. To avoid locking, we use the shape functions associated with the T2CL6 Timoshenko beam element described in [18]. This beam element (see Fig. 16) has a total of ten degrees of freedom with one degree of freedom w α that is eliminated.
The unknown functions u 0(x), w 0(x), and θ 0(x) are approximated in this beam element via:
where:
are the usual quadratic shape-functions while the shape function for the w 0(x):
is obtained by applying the constraint discussed in [18] to avoid locking. Notice that w 0(x) is approximated via a polynomial that is one order higher than θ 0(x).
Further, the beam stresses are given by:
where k and G are the shear correction factor and shear modulus, respectively. Accounting for the axial and shear strain energies, it is easy to show that the stiffness matrix is now given by:
i.e.,
Reducing the integration to the boundary results in the boundary form of the Timoshenko T2CL6 stiffness matrix:
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Samad, W.A., Suresh, K. CAD-integrated analysis of 3-D beams: a surface-integration approach. Engineering with Computers 27, 201–210 (2011). https://doi.org/10.1007/s00366-010-0191-9
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DOI: https://doi.org/10.1007/s00366-010-0191-9