OPTIMIZATION OF ADDITIVELY MANUFACTURED MULTI-MATERIAL LATTICE STRUCTURES USING GENERALIZED OPTIMALITY CRITERIA
Tino Stankovic Engineering Design and Computing Laboratory Dept. of Mechanical and Process Engineering
ETH Zurich, Switzerland [email protected]
Jochen Mueller Engineering Design and Computing Laboratory Dept. of Mechanical and Process Engineering
ETH Zurich, Switzerland [email protected]
Paul Egan Engineering Design and Computing Laboratory Dept. of Mechanical and Process Engineering
ETH Zurich, Switzerland [email protected]
Kristina Shea Engineering Design and Computing Laboratory Dept. of Mechanical and Process Engineering
ETH Zurich, Switzerland [email protected]
ABSTRACT Recent progress in additive manufacturing allows for printing
customized products with multiple materials and complex
geometries. Effectively designing such complex products for
optimal performance within the confines of additive
manufacturing constraints is challenging, due to the large
number of variables in the search space and uncertainties about
how the manufacturing processes affect fabricated materials
and structures. In this study, characteristics of materials, i.e.
Young’s modulus (E), ultimate tensile strength (UTS) and
density (𝜌), for a multi-material inkjet-based 3D-printer are
measured experimentally in order to generate data curves for a
computational optimization process in configuring multi-
material lattice structures. An optimality criteria method is
developed for computationally searching for optimal solutions
of a multi-material lattice with fixed topology and truss cross-
section sizes using the empirically obtained material
measurements. Results demonstrate the feasibility of the
approach for optimizing multi-material, lightweight truss
structures subject to displacement constraints.
1.0 INTRODUCTION AND MOTIVATION Additive manufacturing (AM) enables the automated and
continuous multi-material fabrication of three-dimensional (3D)
objects that are difficult to create with conventional
manufacturing technologies [1-3]. When additive
manufacturing technologies are utilized in combination with
pixel- and voxel-based optimization methods, it is possible to
control the distribution of materials within objects with great
precision. Such precision in creating products has the potential
to dramatically improve structural performance, and even
enable new functionalities when multiple materials are utilized
[4]. However, this freedom additionally leads to an increase in
complexity during product configuration, which can be a great
challenge for products that are already challenging to design
when only single materials are considered, such as lattice
structures [5]. Lattice structure design requires consideration of
member cross-sectional area, shape, and topology variables and
the search of a large design space that is often approached using
automated optimization approaches [6, 7]. Additionally,
solutions found by computational optimization must remain
printable according to Design for Additive Manufacturing
(DfAM) constraints such as the limitations in tolerances,
printable dimensions, and quality issues incurred by the
manufacturing process [8-11]. In this paper, we address these
DfAM challenges by developing an optimization approach for
configuring multi-material lattices that have manufacturing
constraints stemming from the limitations of an AM fabrication
process.
The development of high-performance, multi-material
lattices for complex shapes has particular applications in, e.g.,
developing customized helmets for impact resistance [12, 13].
Lattice structures are growing in interest due to their improved
strength-to-weight ratio compared with stochastic foams alone.
When combined with stochastic foams, hybrid lattice-foam
structures may show superior performance for both strength
and energy absorption under certain conditions [14]. A
complete DfAM process for designing a customized product,
such as a sports helmet with multi-material lattices, includes
phases for characterizing AM materials and processes,
Proceedings of the ASME 2015 International Design Engineering Technical Conferences & Computers and Information in Engineering Conference
IDETC/CIE 2015 August 2-5, 2015, Boston, Massachusetts, USA
DETC2015-47403
1 Copyright © 2015 by ASME
developing quantitative and simulation models based on this
characterization, optimizing designs with computational
methods, and then fabricating and testing the final multi-
material product (Fig. 1). Once testing is completed, findings
are informative for future product design cycles such as the
characterization of different AM materials or refinement of
quantitative models.
Due to the large scope of the DfAM methodology, we
focus on the computational design and optimization portion of
Figure 1 in this paper. However, considerations of the whole
approach inform the development of the optimization method,
such as how it utilizes information from AM characterized
materials and processes. Since the total volume of the helmet is
constrained based on consumer needs, design decisions
concerning material changes in the lattice are beneficial
because they can alter the product’s performance capabilities
without altering its dimensions. The use of AM for producing
the helmet is particularly beneficial, because it enables
customized helmet shapes on a per-consumer basis such that
the helmet conforms to a particular customer’s head shape and
has performance requirements that are tailored to particular
applications [13, 15, 16]. Because of these considerations for
the helmet, multi-material AM could greatly facilitate its design
in comparison with conventional manufacturing approaches.
There is a great need for effective optimization algorithms
for multi-material AM, since such optimization problems have
only been considered for a limited set of products and
applications [6]. Particularly with lattice approaches,
evolutionary based and other meta-heuristic methods have
difficulty with single material structures because they do not
scale well as the resolution and number of structural members
in an application increases. In the helmet example, the design
consists of hundreds to hundreds of thousands of members.
Other algorithms that are well-suited for structural
optimization, such as the discrete optimality criteria method
[7], can be used for large discrete- and lattice-based structures,
but have not been formulated to solve multi-material structures.
Most often, the problem formulation for optimality criteria
methods are purely mass-based and consider dominant
displacement constraints only [7]. However, other more
constraint rich applications exist [17, 18] in addition to the
possibility for extending the method to solve multi-material
lattice problems explored here.
In this paper, we focus on developing a generalized
optimality criteria method [19] for the optimization of discrete,
multi-material mesoscale lattice structures for maximum
performance in a constrained volume. Through considering the
formulation of the optimization algorithm within the context of
a DfAM methodology (Fig. 1), the optimization approach is
developed to accept information about AM characteristics of
materials and processes that ensure that the final design found
by the algorithm can be directly fabricated with AM without the
need for post-processes. Experimental testing is conducted to
determine the properties of two AM materials that the
optimization algorithm may combine in different mixtures to
design lattices with varied properties. The optimization
algorithm is then used to search for optimal lattice designs
through altering material properties of elements within the
lattice. The paper concludes with initial results and a discussion
of future work, including fabricating and testing the optimized
AM structures.
2.0 BACKGROUND 2.1 Lattice Optimization Past studies using the size matching and scaling method
[20] have implemented an approach to design and optimize
meso-scale cellular lightweight structures. The method couples
a library of predefined unit cells, i.e. lattice configurations, with
a solid body finite element analysis that is applied over a design
domain to provide design response as a guide for unit cell
selection, scaling, and placement. The size matching and
scaling method has demonstrated better performance than
particle swarm based lattice optimization [21] and least squares
fitting method [21] when applied for predefined topology or
ground structure optimization.
The approach from Ning and Pellegrino [22] aims to
design and optimize the microstructure of lightweight sandwich
beam designs within a size distribution field using multiple
optimization steps. Starting with Delaunay triangulation, the 2D
topology search is reduced to a limited number of continuous
control variables. The first step in the optimization approach is
to use a genetic algorithm to optimize the topology and then
using the best found topology, lattice truss cross-section sizes
are optimized.
In generative design and optimization of macro scale
lattice structures a somewhat different approach to the previous
one is explored in previous work by one of the authors, the
generative synthesis of transmission towers [23]. The search for
the optimal topology, shape and member sizes is achieved
through a combination of graph grammars and simulated
annealing optimization to create spatially novel designs.
Figure 1.DfAM product design methodology
2 Copyright © 2015 by ASME
2.2 Multi-material Additive Manufacturing Unlike conventional manufacturing, additive
manufacturing (AM) is based on a fabrication process that joins
materials layer by layer to build a product based on CAD model
data. Effective AM design requires consideration of time-
required for product fabrication in addition to materials used
[24-26]. Multi-material applications are particularly relevant to
AM because they can enable a better optimization of the
mechanical properties of parts or provide additional
functionality [2] such as fabricated materials with desired
deformation behavior [27]. There is also the possibility of
including gradients of different materials in a part, which has
been investigated with optimization methods for the
manufacturing of heterogeneous 3D objects with consideration
to mechanics-manufacturing trade-offs [28]. Multiple-material
topology optimization has also been investigated in the context
of AM for 2D material structures [4]. These studies demonstrate
the potential in utilizing multi-material AM applications and the
need for further developing optimization methods in solving the
resulting complex design problems.
2.3 Optimality Criteria Methods In addition to already established lattice optimization
approaches, there is the opportunity to tailor optimization
approaches from other applications in discrete structural
optimization for lattice design, with optimality criteria being a
potentially highly effective approach. In the late 1960s’,
optimality criteria methods were developed to tackle large-scale
structural optimization of discrete member structures for the
aerospace industry [7, 17, 29, 30]. Early applications of
optimality criteria considered static load cases with
displacement constraints only, but the method was soon
extended to consider stress and buckling constraints in addition
to stability and for impact and frequency responses [31, 32]. To
balance computational efficiency with solution quality for
application to large-scale problems, a fully constrained design
method was developed [33]. This method is not gradient-based
and overcomes the requirement that the algorithm must be
customized for each unique problem formulation. However, the
method is only applied to displacement constraints. Another
successful application is the optimization of tall steel buildings
extending the optimality criteria by including commercial
standard sections in the optimization [34].
The primary motivation for the development of the
optimality criteria approach was to address the inability of
conventional mathematical programming methods to handle
optimization problems that exceed 200-300 design variables for
a generic case of a statically indeterminate structure with a non-
linear constraint set [7, 17]. Before optimality criteria was
developed as an approach, numerous alternative search
strategies and problem simplifications were applied to handle
these issues, but were not highly effective approaches. For
example, variable linking and problem order decrease
approaches are hard to implement due to the difficulty in
assessing the implications of these actions on the overall design
solution. The direct consequence of using optimality criteria is
a reduction of cost in required iteration steps to obtain a
significant improvement in the objective function, with respect
to the size of the variable vector [17]. The optimality criteria
approach additionally requires the calculation of a pseudo
energy function that is obtained when a finite element method
is applied to calculate a design response [35].
3.0 MOTIVATION FOR USING OPTIMALITY CRITERIA Findings from the literature suggest that the development
of a highly effective lattice structure optimizer that handles
many complex design cases is still an open question. Genetic
algorithms and similar approaches handle non-gradient
problems, but experience problems when the variable string
becomes too long. Simulating annealing in its simplest form
has a proof of convergence in theory if it runs for an infinite
duration of time, but requires many heuristics to be effective,
e.g. an appropriate cooling schedule definition. Least squares
fitting methods, e.g. design of experiments based responsive
surface methods, are another possible approach that alleviate
computational costs by using a surrogate approach, but they are
also limited in finding high quality solutions for large scale
structures of 10,000 or more members. With respect to the
complexity of discrete lattice structures that are produced using
AM technologies, the application of optimality criteria for
parametric optimization offers the benefit of decoupling the
variable vector size and required iteration steps which is
suggestive of its potential for effectively optimizing large-scale
lattice structures with multiple materials.
In order to assess the optimality criteria’s feasibility in
comparison to other optimization methods for complex lattice
structures, it is benchmarked against the canonical genetic
algorithm (GA) from our own genetic algorithm framework and
interior point (IP) optimization from the MATLAB
optimization toolbox. These methods are compared using a test-
case lattice with 74 members that occupies a space of 50x50x50
mm3 and is optimized for minimum mass when taking cross-
sectional area 𝐴𝑖 as the design variable. A recursive resizing
formula that is a special simplified case of optimality criteria is
applied and referred to as the fully stressed design (FSD)
approach. FSD is easily extendible for the lattice application,
fast in convergence, but is an oversimplification of optimality
criteria because it limits the possibilities to express multiple
constraints, load conditions, and the application of different
materials. Therefore, FSD is a viable approach for
benchmarking the feasibility of optimality criteria in
comparison to other methods, but is not suitable for complex
multi-material lattice structures subjected to different
constraints and loading conditions. The recursive sizing
formula for the cross-section area 𝐴𝑖 of a steel lattice structure
in the test case is as follows [7]:
𝐴𝑖𝜈+1 = (
𝑈𝑖𝐴𝑖𝜈
휀𝑖2𝜌𝑖𝑙𝑖
)
1 2⁄
(1)
where ν denotes the iteration step, 𝑈𝑖 the current strain energy
stored in the ith element, 𝜌𝑖 = 7860 kg/m3
the density, 𝑙𝑖 the
length of the ith element, and 휀𝑖2 the allowed strain per element
calculated for 𝐸 = 206 GPa and allowed stress |𝜎| ≤ 50
N/mm2. Buckling and displacement constraints are not taken
into account. The load F = 1000 N is distributed to all nodes of
the lattice top face in the direction of the negative z-axis, while
the bottom face nodes are fully constrained. The variable range
is defined as 0.01 ≤ 𝐴𝑖 ≤ 10 mm2. The results taking that
3 Copyright © 2015 by ASME
𝐴𝑖 = 𝐴 = 10 mm2 shown in Figure 2 indicate the benefits of
the optimality criteria method, as demonstrated by the FSD
approach having found the lightest structure (11.81 g), with less
computational time (less than 10 s) and iterations (20) in
comparison to both other methods.
Although there are many benefits in using optimality
criteria approaches with respect to computational time and
resources required to optimize large scale structures, its context
oriented basis lacks generality that hinders its efficient use [19].
The optimality criteria method is most commonly expressed to
meet the specific features of a design problem for a particular
application. In an effort to mitigate this, a generalized
optimality criteria was developed [19] by extending the
optimality criteria application to general multi-disciplinary
optimization problems by offering a methodological approach
in both recursive algorithm derivation as well as in the
application of compound scaling algorithm. The search strategy
is then based on a recursive sweep through the search space
while applying scaling procedures to estimate the location of
constraints boundaries [19]. This generalized formulation of the
optimality criteria is considered in this paper to be tested and
extended for multi-material lattice structure optimization
problems.
4.0 CHARACTERIZATION OF AM MATERIALS 4.1 Materials Testing Methods In order to optimize lattice structures according to AM
constraints, empirical studies are performed to characterize AM
materials that are input into the optimization model. To
facilitate multi-material lattice design, Young’s modulus (E),
ultimate tensile strength (UTS) and density (𝜌) are measured for
two different AM materials. The measurements are obtained
using the Stratasys Objet500 Connex3 due to the printer’s
capabilities for printing up to three different model materials at
the same time, thus enabling the fabrication of multi-material
lattices. The printer’s support material is a mixture of SUP705
support and a generic model material. The liquid material is
jetted onto the surface and immediately cured with UV light
positioned on the print head. A pinch roll ensures a smooth and
clean surface when jetting the next layers.
In the printer’s digital material mode, model materials are
mixed to create combinations of properties such as a hard and a
soft material with mixed properties in between. The potential to
mix materials is highly beneficial for lattice applications,
because with just two base material choices there is a broad
range of intermediate mixes of materials with unique
properties. In this study, materials of low and high strength are
tested that are referred to as VeroWhitePlus and
TangoBlackPlus by the manufacturer and chosen based on the
mechanical properties provided by the manufacturer. The
manufacturer reported that VeroWhitePlus has the following
mechanical properties, E = 2000-3000 MPa, UTS = 50-65 MPa,
𝜌 = 1.17-1.18 g/cm3, and that TangoBlackPlus has the
following mechanical properties, UTS = 0.8-1.5 MPa and 𝜌 =
1.12-1.13 g/cm3 [36]. Testing is conducted to verify these
values, in addition to measuring values for the mixed material
properties that are not provided by the manufacturer.
Testing samples are printed for each of the 14 possible
material gradings available for printing based on constraints
from the manufacturer and are inclusive of the two base
materials. Testing commenced on an Instron ElectroPuls E3000
tensile testing machine that enables the testing of the
mechanical properties according to the ASTM D638-10
standard. Additionally, materials are weighed with a Metler
Toledo XS205 DualRange scale. For each material grading,
only one measurement is collected due to negligible variations
in measurements of parts produced on the same machine in
controlled conditions [37]. 4.2 Materials Testing Results For all printed materials, the density of the material is
calculated as an independent variable to form plots with
dependent variables of the measured Young’s modulus (Fig. 3a)
and ultimate tensile strength (Fig. 3b). The plots in Figure 3
demonstrate that the densities of materials have an uneven
distribution over the range of 1.09 g/cm3 to 1.175 g/cm
3, with
most materials being close to the extremes. The plots also
include the manufacturer’s reported data as a basis of
comparison. The experimental measurements for the Young’s
modulus obtained are higher than those provided by the
manufacturer [36] (Fig. 3a). Generally, materials are bi-modally
distributed around Young’s modulus values of about 50 MPa
and 2800 MPa, and there is a lack of testable material mixtures
that may have fallen in intermediate ranges. The data suggests
that material properties are generally below 500 MPa for
densities below 1.14g/cm3, with a sharp increase to about 3000
𝑚 = 41.3 g
Genetic Algorithm
1600 iterations
Running time: ~1 min 𝑚 = 16.1 g
Interior Point
260 iterations
Running time: ~10 min 𝑚 = 11.81 g
Fully Stressed Design
20 iterations
Running time: ~ 4 s
Figure 2. Results of benchmarking algorithms with steel lattice test-case
4 Copyright © 2015 by ASME
MPa for materials with density above 1.14g/cm3. A curve was
fit to the data, since the optimization algorithm requires
continuous functions to calculate possible material properties.
For the optimization, a sigmoidal curve of shape
𝐸(𝜌) = 𝐴1 +𝐴2 − 𝐴1
1 + 10(𝐿𝑜𝑔(𝑥0)−𝜌).𝑝 (2)
is fit to the values (line, black), where A1 and A2 represent the
lower and upper asymptotes, p the hill slope, and x0 the center
point. Solving the equation for 𝜌, which is required for the
model-input, yields Equation 18 with an adjusted R-square of
0.99794.
𝜌(𝐸) = log 𝑥0 −log (
𝐴2 − 𝐴1
𝐸 − 𝐴1− 1)
𝑝 (3)
For the tensile strength, values associated to densities
below 1.14 g/cm3 span over a wider range in an almost linear
behavior (Fig. 3b). The tensile strength data provided by the
manufacturer agrees with the measured values at the densities
below 1.14 g/cm3. Between 1.14 g/cm
3 and 1.17 g/cm
3 no
strength values are found, whereas the ones above 1.17 g/cm3
tend to cumulate between 60 and 70 MPa. An exponential
function of shape:
𝑈𝑇𝑆(𝜌) = 𝐴𝐵𝜌 (4)
is fitted (adjusted R-square 0.99631), where A and B reflect
positions on the curve, respectively. Solving for 𝜌 yields
Equation (5):
𝜌(𝑈𝑇𝑆) = 𝑙𝑜𝑔𝑏 (𝑈𝑇𝑆
𝑎)
(5)
These material characterizations demonstrate the properties
and relations that can be utilized by the computational search
algorithm to only search designs with properties that are
possible to fabricate with this AM technology. Testing of these
materials also suggests that the printer can consistently
fabricate lattice elements of 1 mm in diameter and 10 mm in
length, which is an additional DfAM constraint for the
algorithm.
5.0 OPTIMALITY CRITERIA
The method derived in this section aims to extend the
optimality criteria method to solve multi-material lattice
optimization problems. In the context of additive
manufacturing, this allows for structures optimized for different
performance considerations subjected to conflicting
requirements, e.g. prescribed displacement of the lattice within
a helmet (Fig 1.), which allows customization, absorbs required
energy, and is preferably lightweight. Thus, the optimization
model aims to achieve a lightweight design subject to
displacement constraints given a lattice topology, shape and
member sizes and a range of available materials subjected to a
set of loads and boundary conditions.
5.1 Generalized Optimality Criteria Using Multi-materials with Fixed Truss Cross-section Size and Displacement Constraints
Assuming a mass minimization problem with 𝐴 being a
constant cross-sectional area of a round strut, then the objective
function is stated as:
minimize 𝐹(𝐱) = ∑ 𝐴𝑙𝑖𝜌𝑖(𝑥𝑖)
𝑛
𝑖=1
(6)
where, 𝑙𝑖 is the length of each of the corresponding members,
and 𝜌𝑖 is the material density that is material dependent over
Young’s moduli 𝑥𝑖 as:
𝜌𝑖 = 𝜌𝑖(𝑥𝑖) (7)
where the dependency is obtained through material testing.
Although equation (6) is general with respect to the type of
variable 𝑥𝑖, the rest of the expressions are derived taking the
material Young’s modulus as a continuous variable and using a
linear elastic model of the lattice structure behavior, as a
simplification. In the context of engineering applications of AM
lattice structures, e.g. the helmet in Figure 1 that contains
~100,000 truss members, the motivation for this simplification
in a first instance is justified due to the design’s complexity.
(a)
(b)
Figure 3. Empirical AM Data for (a) Young’s modulus and (b) ultimate tensile strength as a function of density.
1.08 1.10 1.12 1.14 1.16 1.18
0
500
1000
1500
2000
2500
3000 Young's modulus
Young's modulus (Objet)
Fit of E
Young's
modulu
s (
MP
a)
Density [g/cm3]
1.08 1.10 1.12 1.14 1.16 1.18
0
10
20
30
40
50
60
70 UTS
UTS (Objet)
Fit of UTS
UT
S (
MP
a)
Density [g/cm3]
5 Copyright © 2015 by ASME
Thus, to express the constraints as global constraints, e.g. as
functions of the whole lattice, a flexibility coefficient 𝐸𝑖𝑗
associated with the ith member and jth constraint is defined
with respect to the virtual energy of the system [7] as:
𝐸𝑖𝑗 = 𝑥𝑖{𝑟}𝑖𝑇[𝑘]𝑖{𝑠𝑗}𝑖 (8)
where {𝑟}𝑖𝑇 is a displacement vector, [𝑘]𝑖 is the ith truss element
stiffness matrix and {𝑠𝑗}𝑖 is the displacement vector
corresponding to constraint dependent virtual load vector. As
both 𝐴 and 𝐸 participate linearly in the stiffness of truss
members for a linear elastic material model, then the
displacement constraint with respect to the flexibility
coefficient 𝐸𝑖𝑗 , constraint boundary 𝑧�̅� and Young’s modulo 𝑥𝑖
is expressed as:
𝑧𝑗 =𝐸𝑖𝑗
𝑥𝑖
≤ 𝑧�̅� (9)
The displacement constraint gradient matrix can then follow
from (9) as:
𝑁𝑖𝑗 =𝜕𝑧𝑗
𝜕𝑥𝑖
=𝐸𝑖𝑗
−𝑥𝑖2
(10)
with 𝑁𝑖𝑗 being the derivative of the jth constraint 𝑧𝑗 with
respect to the ith variable 𝑥𝑖. Given Equation (6), the gradient
of the objective function ∇𝐹𝑖 is expressed as
∇𝐹𝑖 =𝜕𝐹
𝜕𝑥𝑖
= 𝐴𝑙𝑖
𝜕𝜌𝑖
𝜕𝑥𝑖
(11).
According to [7, 17, 19], the optimality criteria is defined
by the optimality conditions that are satisfied at the optimum
point providing a system of n equations with m active
constraints:
∑ 𝑒𝑖𝑗𝜆𝑗
𝑚
𝑗=1
= 1 (12)
where 𝑒𝑖𝑗 is the ratio of sensitivity derivates of the constraints
and the objective function and 𝜆𝑗 is the Lagrangian multiplier
corresponding to the jth constraint. The ratio of sensitivity
derivates defined with respect to (6-11) is given as:
𝑒𝑖𝑗 =𝑁𝑖𝑗
∇𝐹𝑖
= −
𝐸𝑖𝑗
𝑥𝑖2
𝐴𝑙𝑖𝜕𝜌𝑖
𝜕𝑥𝑖
(13)
However, the solution of Equation (12) requires an
independent set of active m constraints such that 𝑒𝑖𝑗𝜆𝑗 is of full
rank. Thus, according to [19], Equation (12) is expanded by
multiplication with 𝑒𝑖𝑗T 𝐴𝑖𝑗 where 𝐴𝑖𝑖 = ∇𝐹𝑖𝑥𝑖 resulting in the
following expressions written in vector notation:
𝐇𝛌 = 𝐖
(14)
with
𝐇 = 𝐞T𝐀 𝐞 (15)
𝐖 = 𝐞T𝐀 𝟏
Equations (12) and (14) yield a set of Lagrangian
multipliers that if all negative indicate an independent set of
constraints. The necessary condition is that 𝐇 is non-singular
and that 𝐀 is positive definite. If Equation (14) yields both
positive and negative Lagrangian multipliers, then the positive
multipliers indicate constraint dependency requiring their
deletion from the active constraint set and recalculation of (14)
repeating the procedure until multipliers are all negative.
5.1.1 Resizing
After the multipliers are obtained by solving Equation (14),
the algorithm either resizes if the active set of constraints are
satisfied with at least one of the constraints being at the
constraint boundary, or applies a compound scaling [19] until
the condition for resizing is met. Each resizing step completes
an optimization cycle requiring a number of iteration steps to
bring constraints to the feasible region and at least one of them
to the constraint boundary. The resizing formula derived from
the optimality condition (12) is given with respect to cycle 𝜈
and a cycle step size factor 𝛼 = 2 as:
𝑥𝑖𝜈+1 = 𝑥𝑖
𝜈 [∑ 𝑒𝑖𝑗λ𝑗
𝑚
𝑗=1
]
1/𝛼
(16)
Equation (16) takes only positive sums into the
consideration. If there are no positive members then the
corresponding variable is set to its lowest possible value as
defined by the boundary �̅�𝑖.
5.1.2 Scaling
The purpose of scaling is to move constraints to the
feasible search space in such a way that at least one constraint
is on the constraint boundary. Scaling identifies the most
critical constraint and calculates the scaling factor Λ and by
applying the equation
𝑥𝑖′ = Λ𝑥𝑖 (17)
moves the constraint to its boundary [7].
The assumption that has to hold is that all of the other
constraints are also moved to the feasible space. However, this
is not guaranteed for a nonlinear constraint set. Compound
scaling as defined in [19], on the other hand, is more robust as
it scales the variables by analyzing the first order Taylor
approximation in the constraint response due to change in the
variable vector. Each of the variables are classified as active or
passive contributors to the constraint response change that
enables the calculation of scaling factor vector Λ. For details on
compound scaling please refer to [38].
6 Copyright © 2015 by ASME
5.1.3 Optimization Stopping Conditions The overall progress of scaling versus resizing is in the
direction of objective function reduction, otherwise a stopping
condition should halt the optimization progress as the Kuhn-
Tucker conditions provide only the necessary conditions for a
local optimum. the stopping conditions are most often empirical
rather than mathematically defined [19]. However, as the
optimality criteria assumes the location of an optimum is
somewhere on the constraint boundaries, then for purposes of
this study we define the stopping condition when Equation (12)
holds over all of the constraints with a margin of error given as
휀 ≤ 0.05. This effectively allows specifying certain behavior of
the lattice structure as the goal of the optimization process.
6.0 RESULTS 6.1 Optimization Example
The illustrative example to test the method is a cubic lattice
having an individual cubic cell 10x10x10 mm3 in size and
cross-section truss diameter of 1 mm for each of the members
as shown in Figure 4. The idea is to achieve a defined
compliance of the top face middle node 1 while not allowing
significant movement of nodes 2-5. The number of cells
equates 64 with 604 truss members in total:
Figure 4. Lattice topology
Boundary conditions for this example are specified
according to Figure 5, the load is applied to nine middle nodes
on the top face in the opposite direction of z-axis. The Node 1
has displacement constraint 𝛿1 ≤ 2 mm, the rim nodes 2-5 have
prescribed displacement constraint 0.25 mm per node, in
total 𝛿2 ≤ 1 mm, which is calculated as a linear combination of
four points taken with an equal weight factor. Finally, all of the
bottom face nodes are fully constrained. All of the displacement
constraints are calculated in the direction of the applied loads.
Figure 5. Optimization boundary conditions and loads
Taking equations (2) and (3), it is possible to express the mass
𝐹(x), as a function of Young’s moduli:
𝐹(𝐱) = ∑ 𝐴𝑙𝑖
𝑛
𝑖=1
[𝑐 −log (
�̿�𝑖 − �̅�𝑖
𝑥𝑖 − �̅�𝑖− 1)
𝑝] (18)
as well as define the objective function’s gradient ∇𝐹𝑖:
∇𝐹𝑖 = −�̅�𝑖 − �̿�𝑖
𝑝 ln (10)(�̅�𝑖 − 𝑥𝑖)2(
�̅�𝑖 − �̿�𝑖
�̅�𝑖 − 𝑥𝑖− 1)
𝐴𝑙𝑖 (19)
where 𝐴 = 0.7854 mm2, the cross-sectional area of each of the
truss members, 𝑙𝑖 is member length, and �̿�𝑖 = 3250 MPa and
�̅�𝑖 = 8.3 MPa are the upper and the lower variable boundaries,
with 𝑐 = 1.16 and 𝑝 = 57.46 as the curve fitting coefficients
obtained from the material properties testing; see Section 4.2.
Finally, based on the Equations (13), (18) and (19), the
sensitivity derivates of the constraints and the objective
function are given as:
𝑒𝑖𝑗 =𝐸𝑖𝑗
𝑥𝑖2
�̅�𝑖 − �̿�𝑖
𝑝 ln (10)(�̅�𝑖 − 𝑥𝑖)2(
�̅�𝑖 − �̿�𝑖
�̅�𝑖 − 𝑥𝑖− 1)
𝐴𝑙𝑖⁄ (20)
The exit criteria for the optimization is set to find a
constraint intersection point with 5% accuracy based on their
target response ratios and is given as follows:
|𝛿1̅
𝛿1
−𝛿2̅
𝛿2
| ≤ 0.05 (21)
The starting point is selected in the upper region of the
Young’s moduli variable span as 𝑥0𝑖= 3000 MPa. Finally, the
optimization problem used as an illustrative example is
formulated as follows:
minimize 𝐹(𝐱) = ∑ 𝐴𝐿𝑖𝜌𝑖(𝑥𝑖)
𝑛
𝑖=1
(22) Subject to:
𝛿1(𝑥𝑖) ≤ 2 mm
𝛿2(𝑥𝑖) ≤ 1 mm
8.3 ≤ 𝑥𝑖 ≤ 3250 MPa 6.2 Optimization Example Results
The method itself was implemented in MATLAB together
with the FEM analysis. The running time was ~7.5 minutes on
a laptop with 8GB of RAM and an INTEL i7 CPU. The results
of the optimization as specified by the equation (22) and are
summarized as follows:
a) The constraint intersection point satisfying Equations
(12) and (21) is identified with 5% accuracy in the 27th
resizing cycle (167th
step).
10x10x10 mm3
64 cellsDstrutt = 1 mm
1
2
5
4
3
1
2
5
4
3 Fixed nodes
Load = 10 N
z - axis
7 Copyright © 2015 by ASME
b) The values of displacement constraints are: for the
middle point 𝛿1(𝑥𝑖) = 1.923 mm while the cumulative
displacements of four rim points equals 𝛿2(𝑥𝑖) = 1.0
mm. The individual displacements per node are given
as follows:
Node 2 δ22 = 0.25 mm,
Node 3 δ23 = 0.283 mm,
Node 4 δ24 = 0.25 mm,
Node 5 δ25 = 0.216 mm.
c) The minimum mass obtained is 𝐹(𝐱) = 5.886 g
The optimization of the mass over the iteration step history
is depicted according to two images in Figure 6. The left hand
side image shows the first three optimization cycles shown with
the line connected points for which the ×-symbols denote the
outcome of the resizing formula application according to
Equation (16). The o-symbols show the compound scaling
progression for each of the cycles leading to the condition at
which at least one of the constraints is an active constraint
while the other is in the feasible region. The right image in
Figure 6 depicts the overall optimization history.
The resulting structure is shown in Figure 7 where the
material is shown graduated from TangoBlackPlus (black) to
VeroWhitePlus (white). The image shows the impact of the
constraints on the overall distribution of the material, e.g. less
compliant vertical side edges of the lattice structure. The
overall structure also exhibits a symmetry over the spatial
diagonals of each of the cells, which was not constrained. The
horizontal members that are connected to the two support
points are excluded from the optimization as they introduce
singularities in Equation (13), resulting in total 548 structural
members. The structure is comprised of 366 elements with E =
8.3 MPa, 85 elements with 8.3 < 𝐸 ≤ 10 MPa, 73 elements in
the region of 10 < 𝐸 ≤ 544 MPa and finally 24 elements above
2900 MPa. Figure 8 shows the results of the optimization using
the same objective function in Equation (22) but with a
different starting point, 𝑥0i= 10 MPa. The resulting mass,
𝐹(𝐱) = 5.847 g, is slightly less than the previous result,
however, with a different layout of material, i.e. 417 elements
have E = 8.3 MPa, 112 elements in total have 8.3 < 𝐸 ≤ 10
MPa, and 19 elements are in the region of 10 < 𝐸 ≤ 324 MPa.
Figure 7. Optimization results - starting point E0 = 3000 MPa
Figure 8. Optimization results - starting point E0 = 10 MPa 7.0 DISCUSSION Both Young’s modulus and tensile strength values found in this
study are considerably higher than the manufacturer provided
values, which can be linked to a large number of in- and out-of-
process parameters available for the PolyJet 3D-printing
process [37]. No information, besides the use of the ASTM
D638-10 standard, is available on the testing procedure of the
manufacturer. A higher Young’s modulus and shorter elongation
at break makes VeroWhitePlus fragile compared to
TangoBlackPlus. In testing these materials, a strut length of 10
mm and print diameter of 1 mm is utilized for test samples,
Figure 6. The optimization mass over iteration steps history for starting point E0 = 3000 MPa
6.1
6.2
6.3
6.4
0 5 10 15 20 25 30
F[g
]
Iterration steps
5.8
5.9
6
6.1
6.2
6.3
6.4
0 50 100 150 200
F[g
]
Iterration steps
8 Copyright © 2015 by ASME
which is indicative of the minimum lattice element size the
printer can fabricate consistently. Further empirical studies
could investigate what other variables affect the minimum
lattice element diameter and length a printer may fabricate.
A limitation in material characterization occurred due to
the manufacturer limiting the possible densities for printing
because the mixing ratios provided by the manufacturer are
purely based on equal color gradients [36]. It is possible that
adding a small amount of black material to a white base
material has a large visual effect, whereas adding the same
amount of white material to a black base material has a
negligible effect. These considerations could be a potential
reason why the values of the high-density white base material
are closer together in terms of density than the ones with a
black base material and why there are few density
measurements available at densities that are representative of
near equal mixes of materials. As densities correlate with
mechanical strength, a mix of materials spread over a wider
range of densities would be preferable and is theoretically
possible. For this study, however, exact mechanical properties
of other mixing ratios other than the ones presented are not
available and therefore estimated by the fit curve used in the
optimization model.
7.2 Optimality Criteria Method Application The optimality criteria method extended to multi-material
optimization of a lattice structure under displacement
constraints achieved a mass reduction just under 10% compared
to the initial starting mass. This result can be rendered as
acceptable as the overall material density range is itself narrow
spanning from approximately 1.10-1.18 g/cm3, as shown in
Figure 7. This result is achieved considering the following
model simplifications:
a) Young’s modulus is considered as a continuous
variable. While this is theoretically possible on the
Polyjet machine, the current machine only allows
discrete combinations. Either including Young’s
modulus as a discrete variable in the optimization or
applying a second optimization to map the continuous
variable values back to the discrete available values
will be considered in future work.
b) The substitution of cross-sectional area for Young’s
modulus is applied for displacement constraints only.
Future extensions to stress constraints require the
consideration of the stress constraint boundary as
𝜎 = 𝜎(𝐸) since they change with the material. It is
difficult to assess how this will affect the scaling
procedure. Additionally, the stress constraints are
calculated individually per member, which puts a
heavy load on computational resources requiring
additional strategies for constraint management [30].
c) Optimality criteria methods require some knowledge
of the constraint behavior with respect to their activity
and optimum location to be successfully implemented.
This will be investigated in the future to develop a
generalized method for complex-shaped, multi-
material lattices for fabrication with AM.
8.0 CONCLUSION In this paper, an optimization approach using optimality
criteria is developed to facilitate effective design of complex,
multi-material products for optimal performance within the
confines of additive manufacturing constraints. The
optimization approach is developed in the context of designing
multi-material lattice structures as part of a larger DfAM
methodology and product design cycle. An optimality criteria
approach is utilized due to its effective use for optimizing large-
scale discrete structures and the possibility to extend it for
multi-material applications. In order to adhere to DfAM
considerations, empirical measurements are conducted to
characterize the properties of two AM printable materials. The
materials consisted of a low strength and high strength material
that can be combined to form mixtures of materials with
intermediate properties. These measured material properties are
used to develop a curve fit for Young’s modulus that is used by
the optimization algorithm for configuring multi-material
lattices.
The successful application of the extended optimality
criteria method reduced the mass of a multi-material lattice up
to 10% in spite of the limited density range of materials. The
optimization time for a 604 element lattice on a laptop required
only ~7.5 minutes of running time to complete 27 optimization
cycles in 167 steps. These results and the study as a whole
demonstrate the feasibility of optimality criteria in developing
specific design optimization algorithms that adhere to DfAM
constraints and enable the design of highly complex structures
for multi-material AM. Extending the method beyond
displacement constraints requires handling of dynamic stress
constraints and the introduction of a discrete material selection
procedure to adhere to current constraints of the AM machine.
These two points, extension to topology optimization and the
printing and empirical testing of the optimized designs will be
addressed in future work.
ACKNOWLEDGMENTS Partial funding for this research is provided by ETH Zurich
through the Seed Project, SP-MaP 02-14, "Additive Manufacturing of
Complex-Shaped Parts with Locally Tunable Materials".
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