Abstract
We introduce a topology optimization method for the stiffness-based design of structures made of plates. Our method renders topologies made distinctly of plates, thereby producing designs that better conform to manufacturing processes tailored to plate structures, such as those that employ stock plates that are cut and joined by various means. To force the structural members to be plates, we employ the geometry projection method to project an analytical description of a set of fixed-thickness plates onto a continuous density field defined over a 3-dimensional, uniform finite element grid for analysis. A size variable is assigned to each plate and penalized so that the optimizer can entirely remove a plate from the design. The proposed method accommodates the case where the plates in the topology are rectangular and solid, and the case where the boundaries of the plates can change and holes can be introduced. The latter case is attained by composition with a free density field. We present examples that demonstrate the effectiveness of our method and discuss future work.
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Notes
Units are not provided as the optimal topology for the compliance problem is solely dictated by the volume fraction under the aforementioned material assumptions.
We note that in our plate representation, as can be inferred from Fig. 2, if either the length l or the width w of the plate medial surface is zero, the plate collapses to a cylinder of radius t/2 with semi-spherical ends of the same radius; and if both l and w are zero, the plate collapses to a sphere of radius t/2.
Even though not observed in this example, it is also entirely possible that a plate can collapse into a cylindrical bar or a near-sphere.
References
Bangerth W, Hartmann R, Kanschat G (2007) deal.II – a general purpose object oriented finite element library. ACM Trans Math Softw 33(4):24/1–24/27
Bangerth W, Heister T, Heltai L, Kanschat G, Kronbichler M, Maier M, Turcksin B, Young TD (2015) The deal.II library, version 8.2. Archive of Numerical Software 3
Bell B, Norato J, Tortorelli D (2012) A geometry projection method for continuum-based topology optimization of structures. In: 12th AIAA Aviation Technology, Integration, and Operations (ATIO) Conference and 14th AIAA/ISSMO Multidisciplinary Analysis and Optimization Conference, p 5485
Bendsøe MP, Sigmund O (2003) Topology optimization: theory methods and applications. Springer, Berlin
Bourdin B (2001) Filters in topology optimization. Int J Numer Methods Eng 50(9):2143–2158
Bruns TE, Tortorelli DA (2001) Topology optimization of non-linear elastic structures and compliant mechanisms. Comput Methods Appl Mech Eng 190(26):3443–3459
Byrd RH, Lu P, Nocedal J, Zhu C (1995) A limited memory algorithm for bound constrained optimization. SIAM J Sci Comput 16(5):1190–1208
Chen J, Shapiro V, Suresh K, Tsukanov I (2007) Shape optimization with topological changes and parametric control. Int J Numer Methods Eng 71(3):313–346
Cheng G, Mei Y, Wang X (2006) A feature-based structural topology optimization method. In: IUTAM Symposium on Topological Design Optimization of Structures, Machines and Materials. Springer, pp 505–514
Cheng KT, Olhoff N (1981) An investigation concerning optimal design of solid elastic plates. Int J Solids Struct 17(3):305–323
Chung J, Lee K (1997) Optimal design of rib structures using the topology optimization technique. Proc IME C J Mech Eng Sci 211(6):425–437
Dems K, Mróz Z, Szelag D (1989) Optimal design of rib-stiffeners in disks and plates. Int J Solids Struct 25(9):973–998
Deng J, Chen W (2016) Design for structural flexibility using connected morphable components based topology optimization. Science China Technological Sciences 1–13
Díaz AR, Lipton R, Soto CA, etal (1995) A new formulation of the problem of optimum reinforcement of Reissner-Mindlin plates. Comput Methods Appl Mech Eng 123(1):121–139
Ding X, Yamazaki K (2004) Stiffener layout design for plate structures by growing and branching tree model (application to vibration-proof design). Struct Multidiscip Optim 26(1-2):99–110
Guo X, Zhang W, Zhong W (2014) Doing topology optimization explicitly and geometrically—a new moving morphable components based framework. J Appl Mech 81(8):081,009
Khosravi P, Sedaghati R, Ganesan R (2007) Optimization of stiffened panels considering geometric nonlinearity. J Mech Mater Struct 2(7):1249–1265
Kreisselmeier G, Steinhauser R (1979) Systematic control design by optimizing a vector performance index, IFAC Symposium Computer Aided Design of Control Systems. Zürich, Switzerland
Lam Y, Santhikumar S (2003) Automated rib location and optimization for plate structures. Struct Multidiscip Optim 25(1):35–45
Le C, Norato J, Bruns T, Ha C, Tortorelli D (2010) Stress-based topology optimization for continua. Struct Multidiscip Optim 41(4):605–620
Norato J, Haber R, Tortorelli D, Bendsøe MP (2004) A geometry projection method for shape optimization. Int J Numer Methods Eng 60(14):2289–2312
Norato J, Bell B, Tortorelli D (2015) A geometry projection method for continuum-based topology optimization with discrete elements. Comput Methods Appl Mech Eng 293:306–327
Persson PO, Strang G (2004) A simple mesh generator in Matlab. SIAM Rev 46(2):329–345
Rozvany GI, Olhoff N, Cheng KT, Taylor JE (1982) On the solid plate paradox in structural optimization. J Struct Mech 10(1):1–32
Rozvany GIN (2013) Optimal design of flexural systems: beams, grillages, slabs, plates and shells. Elsevier
Sigmund O (1994) Design of material structures using topology optimization PhD thesis, DCAMM, Technical University of Denmark
Sigmund O (1997) On the design of compliant mechanisms using topology optimization*. J Struct Mech 25(4):493–524
Stolpe M, Svanberg K (2001) An alternative interpolation scheme for minimum compliance topology optimization. Struct Multidiscip Optim 22(2):116–124
Svanberg K (1987) The method of moving asymptotes- a new method for structural optimization. Int J Numer Methods Eng 24(2):359–373
Svanberg K (2002) A class of globally convergent optimization methods based on conservative convex separable approximations. SIAM J Optim 12(2):555–573
Wang F, Jensen JS, Sigmund O (2012) High-performance slow light photonic crystal waveguides with topology optimized or circular-hole based material layouts. Photonics Nanostruct Fundam Appl 10(4):378–388
Zhou M, Wang MY (2013) Engineering feature design for level set based structural optimization. Comput Aided Des 45(12):1524–1537
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Support from Caterpillar to conduct this work is gratefully acknowledged.
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In memoriam G. I. N. Rozvany
This work was supported by Caterpillar Inc.
A Appendix: Sensitivity analysis
A Appendix: Sensitivity analysis
1.1 A.1 Plates geometry projection sensitivities
From (15) and (18), we obtain the design sensitivity of the effective density for all plates as
where from (2), the design sensitivity of the density for a single plate is given by
We note that if z corresponds to α q then \(\partial _{\alpha _{q}} d_{q} = 0\) and from (16)
Otherwise, ∂ z ζ(α q , s) = 0 and ∂ z d q is given by the results of the following section (and it equals zero if z ∉ z q ).
An interest insight on the sensitivity of the geometry projection is that if one looks at ∂ z d q as the design sensitivity of the closest point on ∂ ω to x, then the first term in square brackets in (53) is a convective term and the second term is an advective term. This is in contrast to level set topology optimization methods which only employ convective sensitivities.
1.2 A.2 Distance function sensitivities
We proceed to derive sensitivities for the distance function with respect to the plate design parameters of (3). For simplicity, in this section we drop the q subscript and note that all quantities refer to a single plate. To simplify the derivation, we first perform the following algebraic manipulation of (4) to eliminate the square root on the right-hand side (RHS) of the equation:
Differentiating with respect to some design variable z, and since we have assumed the plate thickness to be constant, we have
The above expression reveals a requirement of our method. If d = −t/2, then the denominator on the RHS of (57) is zero and the derivative is not defined. However, if we require that the sample window for the projection in ( 2 ) is smaller than the plate thickness, i.e. that r < t/2, then ∂ d ρ from (54) will be 0 when |d| ≥ t/2, hence ∂ z d need not be computed. This also addresses the issue of the signed distance function potentially being not unique, i.e. if there are two portions of ∂ ω to which the signed distance from x is the same; this would occur, for example, if x lies on the medial surface and d ≥ t/2. This requirement of our method was also shown in Norato et al. (2015).
To obtain the sensitivities with respect to the individual design parameters in (3), we therefore obtain the individual sensitivities on the RHS of (57). Let us start with the sensitivities with respect to the plate center point x c . We first note that
where we used the fact that the projection P ⊥ is symmetric and idempotent. Therefore,
From (5) and (6) we have that \(\nabla _{\mathbf {x_{c}}} \hat {\mathbf {x}} = - \textsf {I}\) and \(\nabla _{\mathbf {x_{c}}} \textsf {P}^{\perp } = \textsf {0}\) respectively, hence
To obtain \(\nabla _{\mathbf {x_{c}}} (H({\Delta }_{1}){{\Delta }_{1}^{2}})\) we first use the product rule:
The derivative of the Heaviside function is given by H ′(x) = δ(x), where δ(x) = {1 if x = 0, 0 otherwise } is the Dirac delta function. Therefore, ∂ z H(Δ1) is non-zero only when Δ1 = 0. However, since the first term on the RHS is multiplied by \({{\Delta }_{1}^{2}}\), we have that this term is always zero. Hence, using the chain rule we find
Similarly, for the third term in (57) we have
From (9), we have that
Clearly, \(\nabla _{\mathbf {x_{c}}} (l/2) = \vec {0}\), and so we need only look at \(\partial _{z} | \hat {x}^{\parallel }_{1} |\). Here we note another requirement of our method: the derivative of the absolute function |x| is not defined at x = 0. However, if l > 0 then H(Δ1) = 0 if \( | \hat {x}^{\parallel }_{1} | = 0 < l/2\), and from (62) and (64), \(2 {\Delta }_{1} H({\Delta }_{1}) \partial _{z} | \hat {x}^{\parallel }_{1} | = 0\). Hence, we require in our method that l > 0 and, using a similar argument, that w > 0. This requirement circumvents the problem that when l or w are zero the closest point on ∂ ω to \(\hat {\mathbf {x}}\) is no longer unique.
To compute \(\partial _{z} | \hat {x}^{\parallel }_{1} |\), we note that
Differentiating, we have
Since ∂ z (a⊗a) = 2Sym(a⊗∂ z a), where the Sym(A) operator returns the symmetric part of tensor A, we then have
A similar expression follows for \(\partial _{z} | \hat {x}^{\parallel }_{2} |\). With \(\nabla _{\mathbf {x_{c}}} \hat {\mathbf {e}}_{1} = \textsf {0}\) and using (7) and (8), we have
Combining (62), (64) and (69) we obtain
A similar derivation for the third term on the RHS of (57), and using (65), gives
Collecting (60), (70) and (71), and using (57) we finally obtain the sensitivity of the distance with respect to the center point of the plate as
To obtain sensitivities of the distance with respect to the Euler angles of the plate, we first note from (10) that
where
and we used the fact that R ψ , R θ and R ϕ are orthogonal, hence their inverses equal their transposes. It can be shown the above defined tensors A β , β ∈ {ψ, θ, ϕ} are skew-symmetric like the R β , i.e. \(\textsf {A}_{\beta }^{T} = -\textsf {A}_{\beta }\). As such, there is an axial vector w = Axial(A) = [A 32, A 13, A 21]T associated with each of these tensors such that
for any \(\mathbf {a} \in \mathbb {R}^{3}\), where ∧ denotes the wedge or cross product. It can be readily verified that the axial vectors for the A β of (73)–(75) are given by
For the sensitivity of the first term on the RHS of (57) with respect to β ∈ {ψ, θ, ϕ}, we use (59) and the fact that \(\partial _{\beta } \hat {\textbf {x}} = \vec {0}\) to obtain
where from (6) we have
With \(\partial _{\beta } \hat {\mathbf {e}}_{1}\) and \(\partial _{\beta } \hat {\mathbf {e}}_{2}\) given by one of (73–75), (84) becomes
From the above and from (83) we obtain the sensitivity of the first term on the RHS of (57) with respect to any of the three Euler angles as
where we used the fact that P∥ is symmetric. A similar procedure and Eqns. (62), (63), (64), (65), and (68) render the sensitivities of the second and third terms on the RHS of (57) with respect to any of the three Euler angles as
Combining (86), (87) and (88), and using (57) and (79) we finally obtain the sensitivity of the distance with respect to any of the Euler angles of a plate as
with w β given by one of (80–82).
We now proceed to obtain the sensitivities of the distance with respect to the length and width of the plate. With \(\partial _{l} \hat {\textbf {x}} = \partial _{w} \hat {\textbf {x}} = \vec {0}\) from (5) and ∂ l P⊥ = ∂ w P⊥=0 from (6), we have from (59)
Also, \(\partial _{l} \hat {\mathbf {e}}_{1} = \partial _{l} \hat {\mathbf {e}}_{2} = \partial _{w} \hat {\mathbf {e}}_{1} = \partial _{w} \hat {\mathbf {e}}_{2} = \vec {0}\) from (10). Consequently, from (68) we find that \(\partial _{l} | \hat {x}^{\parallel }_{1} | = \partial _{w} | \hat {x}^{\parallel }_{1} | = \partial _{l} | \hat {x}^{\parallel }_{2} | = \partial _{w} | \hat {x}^{\parallel }_{2} | = 0\), and so from (64) and (65) we have that ∂ l Δ1 = ∂ w Δ2 = −1/2 and ∂ w Δ1 = ∂ l Δ2 = 0. Therefore, from (62) and (63) we find
From (90–91) we finally obtain the sensitivities of the distance with respect to the length and width of the plate as
Finally, we recall that the distance does not depend on the size variable α, therefore
To summarize, the sensitivities of the distance with respect to the design parameters of a plate are given by (72), (89), (93), (94) and (95). The derivations in this section not only lead to succinct, elegant expressions, but most importantly they substantially reduce the amount of floating point operations needed to compute the distance sensitivities and therefore they are highly preferred over a naive differentiation.
A final remark is worth noting: the appearance of the Heaviside function in these sensitivities does not render them discontinuous, because H(Δ1) and H(Δ2) are multiplied by Δ1 and Δ2 respectively wherever they appear in the sensitivities; therefore, even though H(Δ1) and H(Δ2) jump from zero to one when Δ1 and Δ2 go from being negative to zero, Δ1 = 0 and Δ2 = 0, and therefore the corresponding terms in the sensitivities are still zero. This is consistent with Norato et al. (2015), where it was shown that the sensitivities are continuous across branches of the distance function to a bar.
1.3 A.3 Composite Density Sensitivities (Plates with Holes)
From (20), the sensitivities of the composite density are given by
In the afore expression, \(\partial _{z} \tilde {\rho }\) is given by (53) and \(\partial _{\bar {\chi }} \zeta (\bar {\chi },s)\) can be obtained from (55). The sensitivities of the filtered free density are more readily expressed in the discretized version of the filter (50). Using the quotient rule and after some simplification, we have
If z corresponds to a plate design parameter (i.e. if z ∈ z q ), then ∂ z χ(y) = 0 and \(\partial _{z} \tilde {\rho }\) can be computed from (53); on the other hand, if z corresponds to one of the elemental free densities χ j , then \(\partial _{z} \tilde {\rho } = 0\), and since
then in this case the entire (97) reduces to
1.4 A.4 Placement Bound Constraints Sensitivities
The sensitivities of the j-th component of the aggregate placement bound constraints of (33) and (34) are respectively given by
where the superscript (i) corresponding to corner i = 1, … , 4 and the subscript q corresponding to plate q have been dropped for brevity, with the understanding that the above expressions lead to 24 equations per plate. The ∂ z c j can be obtained from (25) as
with w β given by one of (80–82). Clearly ∂ z c j = 0 if z ∉ z q since the locations of the corners of the medial surface of a plate only depend on the design parameters of that plate.
1.5 A.5 Compliance and volume fraction sensitivities
Using adjoint sensitivity analysis (cf., for example, Bendsøe and Sigmund (2003)), the compliance sensitivity can be found as
The corresponding expression on the finite element discretization with element-wise discretized densities is given by
where N e l is the number of elements in the mesh, U i and \(\mathbf {K}_{i_{o}}\) are the vector of nodal displacements and solid stiffness matrix for element i respectively, and \(\partial _{z} \breve {\rho }_{i}\) can be computed from the composite density sensitivity of (96) for design with variable topology plates, or from the effective density of (53) for design with solid, rectangular plates.
The design sensitivity of the volume fraction in (36) is simply given by
and the corresponding expression on the finite element discretization is
where V i is the volume of element i. As before, we note the important difference that (109) is computed with s = 0, whereas (107) is computed with s > 0.
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Zhang, S., Norato, J.A., Gain, A.L. et al. A geometry projection method for the topology optimization of plate structures. Struct Multidisc Optim 54, 1173–1190 (2016). https://doi.org/10.1007/s00158-016-1466-6
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DOI: https://doi.org/10.1007/s00158-016-1466-6