Abstract
Design optimization of beam structures is a significant topic as beams are an efficient load-carrying component in engineering applications. Most of the earlier researches concentrate on the structural optimization of beams with invariant cross-section topology, and design optimization of periodic beam structures, which cross-section topology varies along the axial direction, has not been extensively investigated. This work presents a novel approach based on the relaxed Saint-Venant solution to conduct microstructural topology optimization of periodic beam structures for minimum structural compliance. One benefit of adopting Saint-Venant solution based compliance formulation is that the strain energy induced by transverse shear loading is incorporated in the structural compliance, which is not reflected in that based on first-order homogenization of the asymptotic homogenization (AH) theory, so that a more reasonable objective function is adopted for the optimization problem. In addition, a material connectivity constraint, which is constructed by restraining the ratio of the strain energy calculated from relaxed Saint-Venant solution to that obtained from first-order homogenization of the AH theory, is further proposed to prevent material separation or to strengthen material connection through the thickness direction. The detailed sensitivity analysis of the objective function and the constraints are carried out with the adjoint method, and several numerical examples are given to show the validity of the relaxed Saint-Venant solution based compliance formulation and the effectiveness of the proposed material connectivity constraint.
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Funding
This work is supported by National Natural Science Foundation of China (Grant No. 12002159), a Project Funded by the Priority Academic Program Development of Jiangsu Higher Education Institutions (PAPD), Natural Science Foundation of Liaoning Province (2019-ZD-0021), the State Key Laboratory of Mechanics and Control of Mechanical Structures at NUAA (no. MCMS-E-0520 K02), and the Key Laboratory of Impact and Safety Engineering, Ministry of Education at Ningbo University (no. CJ201904).
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All the model and optimization parameters are provided in the numerical examples and detailed sensitivity derivation is described in Appendix. Detailed FE formulation of structural analysis is given and methods used to conduct filtering are available in the cited literature. The readers can replicate the results through the proposed method in this work.
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Appendices
Appendix 1 Sensitivity analysis of the strain energy e SV
In Appendix 1, we conduct sensitivity analysis of the strain energy eSV in (33) with the adjoint method. First, it is easy to deduce that
where x is the vector of design variables. Thus the sensitivity of e with respect to ith design variable xi can be written as:
We start with the first term at the right hand side of (64) by introducing the following Lagrangian \( {e}_{L_1} \) as:
where \( {{}^{\mathrm{n}}\boldsymbol{\uplambda}}_{\mathrm{m}}^1,{{}^{\mathrm{n}}\boldsymbol{\upmu}}_{\mathrm{m}}^p\left(p=1,2,3,4\right) \) are the master degrees of freedom of adjoint vectors nλ1, nμp(p = 1, 2, 3, 4), which satisfy the periodic boundary condition: \( {{}^{\mathrm{n}}\boldsymbol{\uplambda}}^1=\mathbf{T}{{}^{\mathrm{n}}\boldsymbol{\uplambda}}_{\mathrm{m}}^1,{{}^{\mathrm{n}}\boldsymbol{\upmu}}^p=\mathbf{T}{{}^{\mathrm{n}}\boldsymbol{\upmu}}_{\mathrm{m}}^p \). Conduct sensitivity analysis in (65), collate terms containing \( \frac{\partial {{}^{\mathrm{n}}\mathbf{V}}_{\mathrm{m}}^1}{\partial {x}_i},\frac{\partial {{}^{\mathrm{n}}\overset{\sim }{\mathbf{u}}}_{\mathrm{m}}^p}{\partial {x}_i}\left(p=1,2,3,4\right) \) and set them to zero. Then the term \( \frac{\partial e}{\partial {{}^{\mathrm{n}}\mathbf{V}}^1}\frac{\partial {{}^{\mathrm{n}}\boldsymbol{V}}^1}{\partial {x}_i} \) in (64) can be readily obtained as:
where the vectors nλ1, nμp(p = 1, 2, 3, 4) are determined by the following adjoint equations:
Similarly, the second term at the right hand side in (64) can be calculated as:
where the adjoint vectors nλ2, nνp(p = 1, 2, 3, 4) are determined by the following adjoint equations:
Examining the equations for nμp and nνp in (67) and (69), we define vectors nξα(α = 1, 2), whose FE formulations are as follows:
and vectors nμp and nνp can be accordingly expressed as:
Substitute (71) into (66) and (68), and collate relevant terms. The first two terms in (64) can be rearranged as:
where \( {}^{\mathrm{n}}\overset{\sim }{\mathbf{V}}={\mathbf{T}}_2\left({}^{\mathrm{n}}\mathbf{U}+l{}^{\mathrm{n}}\overset{\sim }{\mathbf{u}}\right) \).
Next we tackle the third term in (64) and introduce the Lagrangian \( {e}_{L_2} \) as:
Following the same procedure, the sensitivity can be obtained as:
where vectors nηp(p = 1, 2, 3, 4) are determined from
Thus substitute (72) and (74), the sensitivity of strain energy eSV can be arranged as:
where the terms \( \frac{\partial e}{\partial {x}_i},\frac{\partial e}{\partial^{\mathrm{n}}{V}^{\alpha }}\left(\alpha =1,2\right),\frac{\partial e}{\partial {{}^{\mathrm{n}}\overset{\sim }{u}}^p}\left(p=1,2,3,4\right) \) can be readily obtained as:
where \( {\mathbf{F}}^{\mathrm{ext}}={\mathbf{F}}^{\mathrm{EBT}}+\frac{l}{2}\mathbf{Q} \), and the sensitivity of the effective compliance matrix C can be readily obtained from that of the effective stiffness matrix D as:
The sensitivity of the strain energy eAH in (39) can be then obtained as
Appendix 2 Analytical strain energy formulation for the I-section base cell
We first derive the closed-form strain energy formulation \( {e}_{\mathrm{analytical}}^{\mathrm{SV}2} \) in (44) of the I-section base cell subject to the transverse shear force and the bending moment in Fig. 4(a). As the thickness of the flange and the web is assumed much smaller than the dimensions of the cross-section, where the mechanics of thin walled structures can be applied, the normal stress σ33, which admits linear distribution along x2 direction, and the shear flow q in Fig. 15(b), which admits linear and quadratic distribution on the flange and the web respectively, can be readily calculated through mechanics of thin-walled structures. The stress components on different parts of the I-section in Fig. 15(c) are given by:
where \( {I}_1=\frac{t_2{h}^3}{12}+\frac{h^2{bt}_1}{2} \) is the moment of inertia around x1 axis. Then the strain energy can be analytically calculated as:
For the I-section subject to bending moment \( {\left.{M}_1\right|}_{\omega^{-}}=\frac{l}{2},{\left.{M}_1\right|}_{\omega^{+}}=-\frac{l}{2} \), which is adopted to calculate analytical eAH, the normal stress σ33 is readily calculated as:
and the strain energy can be derived as:
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Xu, L., Qian, Z. Microstructural topology optimization of periodic beam structures based on the relaxed Saint-Venant solution. Struct Multidisc Optim 63, 1813–1837 (2021). https://doi.org/10.1007/s00158-020-02778-y
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DOI: https://doi.org/10.1007/s00158-020-02778-y