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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Finite Element Study of Elastic Rods underThermal Loading
Jaspreet SinghDepartment of Mechanical EngineeringIndian Institute of Technology, Kanpur
16/07/20151 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Overview
1 Objectives
2 Literature Survey
3 Assumptions
4 Kinematics
5 Stress and Strain Measures
6 Order analysis
7 Derivation of governing equations
8 FEM formulation
9 Numerical Implementation
10 Coupling with heat equation
11 Results
12 Appendix
2 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Objectives
To determine the displacement, strains, stresses in an elasticrod subjected to thermal loads.
Explore the possibility of buckling under thermal loads.
Study the effect of temperature on buckling in response tomechanical loads.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Literature Survey
Theoretical aspects: Green, Dill and Antman.
Derivation of the equations of rod theory from 3-D elasticity.Order analysis.
Numerical implementation: Simo, Argyris and Bathe.
Snaps throughs, saddle points and discontinuities of derivativeslead to failure of standard algorithms.Non-commutative finite rotations.Non-conservative external loading.
Recent work
Holmes and Cisternas: 2-D model, uniaxial temperature field,calculation of buckling temperature.Coffin and Bloom: Analytical solution for simply supportedrod.Goriely et al: Finite growth strains, applications to arteries,growth of stems and bones etc.
4 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Assumptions
Large deformations, small strains.
Linearly isotropic elastic deformations.
Plane CS remains plane, warping is disallowed.
Dimensions of CS Length of rod and radii of curvature.
Additive decomposition of total strain into elastic and thermalcomponents.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Kinematics
6 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Any point in reference configuration:r(S , ζ1, ζ2, 0) = φ
0(S , 0) + ζ1E 1 + ζ2E 2.
Any point in current configurationr(S , ζ1, ζ2, t) = φ
0(S , t) + ζ1(1 + ε1)t1 + ζ2(1 + ε2)t2.
Evolution of centroidal axis:φ
0(S , t) = φ
0(S , 0) + u1e1 + u2e2 + u3e3.
Evolution of orthonormal frame:Λ(S , t) = t1 ⊗ E 1 + t2 ⊗ E 2 + t3 ⊗ E 3
Curvature:dE idS = ω0 × E i and
dt idS = ω × t i
7 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Stress and Strain Measures
P is the first Piola Kirchoff stress tensor such that
P = T 1 ⊗ E 1 + T 2 ⊗ E 2 + T 3 ⊗ E 3.
The spatial description of the stress measures is as follows:
Stress Strain
n =∫CS T 3 dA γ =
dφ0
dS − t3
= s1t1 + s2t2 + et3
m =∫CS(r − φ
0)× T 3 dA β = ω − Λω0
= k1t1 + k2t2 + k3t3
Material Analogs of n,m, γ and β are N,M, Γ and κ, respectively.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Order analysis
Let h, a, b and L denote the dimension of CS, radii of curvature inundeformed and current configuration and characteristic length ofthe rod.
ε = greatest(h/L, h/a, h/b, e, s1, s2, ε1, ε2)ζ1, ζ2, T i ∼ O(ε)
Theory is valid when ε 1.For additive decomposition to hold true it has been assumed
αT (S , ζ1, ζ2) ∼ O(ε)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Inclusion of Temperature
Note that, the temperature field is allowed to have mostgeneral form of T (S , ζ1, ζ2).
Up to first order, deformation gradient is written as
F = (1 + ε1)t1 ⊗ E 1 + (s1 − ζ2k3)t1 ⊗ E 3
(1 + ε2)t2 ⊗ E 2 + (s2 + ζ1k3)t2 ⊗ E 3
(1 + e + ζ2k1 − ζ1k2)t3 ⊗ E 3
= FiI t i ⊗ E I
F e = F (F θ)−1 =1
1 + αTF ≈ (1− αT )F
= (1− αT )(t i ⊗ E i + f ) where f ∼ O(ε)
= (1− αT )t i ⊗ E i + f
(1)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
T 3 = G (s1− ζ1k3)t1 +G (s2 + ζ2k3)t2 +E (e− ζ1k2 + ζ2k1−αT)t3
(2)Furthermore,
∫CS ζ1dA = 0,
∫CS ζ2dA = 0 and
∫CS ζ1ζ2dA = 0
n =
∫CS
T 3dA = GA1s1t1 + GA2s2t2 + (EAe − PT)t3
where PT (S) = E
∫CSαT (ζ1, ζ2,S) dA
(3)
m =
∫CS
(r − φ0)× T 3 dA
= [EI1k1 −MT1]t1 + [EI2k2 + MT2]t2 + GJk3t3
where MT1 = E
∫CSζ2αT dA and MT2 = E
∫CSζ1αT dA
(4)
Temperature field is, thus, completely decomposed into a bodyforce and body moment.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Using∫CS ζ1dA =
∫CS ζ2dA =
∫CS ζ1ζ2dA = 0 and∫
VolP : F dV =
∫ S
0
∫CS
S : E dAdS
=
∫ S
0[GAs1s1 + GAs2s2 + EAee
+ EI1k1k1 + EI2k2k2 + GJk3k3
−MT1k1 + MT2k2 − PTe]dS
=
∫ S
0[N.Γ + M.κ]dS
(5)
where∫CS ζ
21 dA = I2,
∫CS ζ
22 dA = I1 and
∫CS(ζ2
1 + ζ22 )dA = J.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Linearization of strain measures
Set of all possible configurations of the rod is given asC = (φ
0(S , t),Λ(S , t)) : φ
0∈ R3,Λ ∈ SO(3).
Φ = (φ0,Λ) ∈ C is perturbed to Φε = (φ
ε,Λε) ∈ C , according the
following scheme.
φε
= φ0
+ εη0
Λε = exp (εΘ)Λ
where η0
= ηie i and Θ = θiI e i ⊗ e I =
0 −ϑ3 ϑ2
ϑ3 0 −ϑ1
−ϑ2 ϑ1 0
ϑ = axial(Θ) = ϑie i
(6)
η = (η0, ϑ) ∈ TΦC , tangent space of C at Φ.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Under the described scheme the linearization of any quantity Q(Φ)is defined as
δQ(Φ, η) =d
dεQ(φ
ε,Λε)|ε=0 (7)
Thus the linearization of strain measures is
Γε = ΛTε φε − E 3
δΓ(Φ, η) =d
dεΓε|ε=0
= ΛT (dη
0
dS− ϑ×
dφ0
dS)
(8)
δκ(Φ, η) = ΛTϑ (9)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Governing equations
For a rod with length L0 loaded under distributed loads, n and mand contact loads N and M on the ends.
δWint =
∫ L0
0(N.δΓ + M.δκ)dS
=
∫ L0
0(n.(
dη0
dS− ϑ×
dφ0
dS) + m.
dϑ
dS)dS
(10)
δWext =
∫ L0
0(n.η
0+ m.ϑ)dS + [N.η
0+ M.ϑ]0,L0 (11)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Governing equations are as follows:
δWint − δWext = 0 (12)
dn
dS+ n = 0 (13)
dm
dS+
dφ0
dS× n + m = 0 (14)
Drichlet Boundary Conditions Neumann Boundary Conditions
η0
= 0 n = N
ϑ = 0 m = M
n = GAs1t1 + GAs2t2 + (EAe − PT)t3
m = (EI1k1 −MT1)t1 + (EI2k2 + MT2)t2 + GJk3t3.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
FEM formulation
6 dof/node i.e. p =[u1 u2 u3 ϑ1 ϑ2 ϑ3
]Number of elements =nel
G =nel∑e=1
Ge (15)
Number of nodes per element=n=2
η = (η0, ϑ) is the virtual displacement such that η
0= 0 and
ϑ = 0 at S = 0, L0.
η0
=n∑
i=1
Niηi
ϑ =n∑
i=1
Niϑi
(16)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
From Eq[10] and Eq[11]
G (Φ, η) =nel∑e=1
Ge
Ge(Φ, η) = δWint − δWext
=
∫ L0
0(n.(
dη0
dS− ϑ×
dφ0
dS) + m.
dϑ
dS)dS −
∫ L0
0(n.η
0+ m.ϑ)dS
(17)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Ge =
∫ L0
0(n.(
n∑i=1
N ′i ηi +n∑
i=1
Niϑi ×dφ
0
dS) + m.
n∑i=1
N ′iϑi )dS
−∫ L0
0(n.
n∑i=1
Niηi + m.n∑
i=1
Niϑi )dS
=n∑
i=1
Gei =n∑
i=1
Pei .[ηi ϑi ]T
(18)
where
Pei =
∫ L0
0(
[Ni I 0
−Ni [φ′0×] Ni I
] [nm
]−[Ni I 00 Ni I
] [nm
])dS
Pe =[
Pe1 Pe2 . . . Pei . . . Pen
]T (19)
Pei is the residual force vector corresponding to i th node of eth
element.19 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Note that
[nm
]=
[Λ 00 Λ
]
GAs1
GAs2
EAe − PT
EI1k1 −MT1
EI2k2 + MT2
GJk3
(20)
Let
Ξ =
[Ni I 0
−Ni [φ′0×] Ni I
]C = diag[GA GA EA EI1 EI2 GJ]
Π =
[Λ 00 Λ
]NT =
[0 0 PT
]TMT =
[MT1 −MT2 0
]T(21)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Residual given by Eq[19] can be written in the conventional form as
Pei = f int − f ext
f int =
∫ L0
0(ΞΠ
GAs1
GAs2
EAeEI1k1
EI2k2
GJk3
)dS =
∫ L0
0(Ξ Π C
[Γκ
])dS
f ext =
∫ L0
0(Ξ Π
[NT
MT
]+
[Ni I 00 Ni I
] [nm
])dS
(22)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
To derive the stiffness matrix, variation of Eq[19] is taken.Contrary to virtual displacement herein perturbation u = (u0, ψ) isa physical perturbation.
∆n = ∆(ΛN) = [ψ×]n + ΛC1ΛT (u′0 − ψ × φ′0) (23)
∆m = ∆(ΛM) = [ψ×]m + ΛC2ΛTψ′ (24)
∆(φ′0× n) = −[n×]u′0 + [(n.φ′
0)I + n ⊗ φ′
0]ψ+
[φ′0×]ΛC1ΛTu′0 + [φ′
0×]ΛC1ΛT [φ′
0×]Tψ
(25)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
∆Pei =
∫ L0
0
( [ N ′i ∆nN ′i ∆m − Ni∆(φ′
0× n)
] )dS
=
∫ L0
0
n∑j=1
(Seij + Teij
).uj
(26)
Putting in the values from Eq[23], Eq[24] and Eq[25] yields therequisite stiffness matrix.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Numerical implementation
Problem: f int(u)− λf f ext(u) = 0
1: Define R = f int(un)− λnf ext(un) and use arclength method totrace the curve. n denotes the loadstep.
2: Break at nth loadstep, if λn > λf .3: Define R = f int(u)− λf f ext(u). Use un−1 as the initial guess
and use NR procedure to converge to the exact solutioncorresponding to λn = λf .
4: If NR iterations in step[3] do not converge, go back to step[1]and change the step size in the arclength method.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Coupling with heat equation
In the domain shown following problem for temperature field (T) issolved using FEM
∇2T = h in Ω
T = T 0 on ΓT
k∂T
∂n= q on Γq
(27)
Knowing the dimensions of the CS (say [−a, a]× [0, b] andζ ∈ [−a, a]), numerical integration is carried out to calculatePTm =
∫CS EαTmdA = b
∫ a−a EαTmdζ and
MTm = b∫ a−a EαTmζdζ for each iteration in every loadstep.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Validation of code
CS 1× 1 cm2, length 1m, E=200× 109 Pa and G=1012 Pa
error= 1N
√N∑
n=1(‖x fn − xen‖2 + ‖y fn − y en‖2)
N 2 3 5 7 10 25 50
3D 0.2741 0.1820 0.1290 0.1066 0.0882 0.0552 0.0390
2D 0.2740 0.1821 0.1291 0.1067 0.0882 0.0553 0.0390
26 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Error v/s Number of elements27 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Thermal buckling of a beam
A simply supported beam on both ends with E=200× 109,length=1, G=1014, area=10−4 and moment of inertia=10−8,α = 10−5 is considered. The hypothesis postulated is
e ∼ s ∼ O(ε) ∼ αT (28)
Hence, the formulation should give correct results upto∆T ∼ ε
α ≈ 1000K . The magnitude of e and s gives an idea aboutthe total strain.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Initial and Final Shapes of Rod29 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Midpoint deflection v/s Temperature30 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Shear Strain v/s Temperature31 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Total Axial strain (e) v/s Temperature32 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Elastic Axial Strain (e − αT ) v/s Temperature33 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Thermal Strain (αT ) v/s Temperature34 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Effect of temperature field on buckling loads
Euler Column, fixed at(A) and subjected to a compressive load (P)at (B) is considered. The temperature profile is given asT (S , ζ) = T0ζ/b where ζ ∈ [−b, b] is the coordinate on the CS([−b, b]× [0, a]) measured from the neutral axis, 2b is thethickness of the cross section, a is the out of the plane dimensionof CS. α = 10−5, E=200× 109 Pa, G= 1014 Pa, length= 1m,area= 10−4 m2 and moment of inertia = 10−8 m4. T0 is theparameter whose effect on buckling load is considered.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Buckling of Euler Column36 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Angular beam subjected to constant temperature field
A curved rod fixed at both ends with length=2 m, α = 10−5,thedimensions of CS 10−2 × 10−3 m2, E = 200× 109Pa, G = E/2subjected to a constant temperature rise (T (S , ζ1, ζ2) = T ) isconsidered. The objective of the problem is to explore the effect ofthe radius of curvature on buckling temperature. The problem issolved for φ = π/24, π/12, π/6, π/3, π/2, 2π/3 and π.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Thermal buckling of a curved rod38 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Thermal buckling of a curved rod39 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Non-uniform temperature distribution
Here, α = 10−5, Tmax = 200, E = 200× 109 Pa, G = 1015 Pa,area A = 10−4 m2 and moment of inertia I = 10−8 m2. Thetemperature boundary conditions are specified on the two ends(AC, BD) of the beam while the lateral surfaces (AB, CD) areconsidered to be insulated. At every loadstep, the temperature’matrix’ is λT/Tmax∀λ ∈ [0,Tmax ]. Here, Tmax = 200.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Temperature profile in the beam41 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Initial and final shapes of the rod42 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Figure: Midpoint deflection v/s load parameter (λ)43 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Thank You
44 / 57
Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Kinematics
The complete description of rod parametrized by S ∈ [0, L0]requires specification of
Locus of the centroids (Centroidal Axis),φ
0(S , t) : S ∈ [0, L0], t ∈ R+ 7−→ R3.
Orthonormal frame attached to each cross-section (CS)[t1, t2, t3], t i (S , t)1 : S ∈ [0, L0], t ∈ R+ 7−→ R3 .
t = 0 denotes the reference configuration wherein rod isassumed to be smooth arbitrary curve.
[e1, e2, e3] is the fixed spatial frame.
1 i, I = 1, 2, 3
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Reference Configuration
Curvilinear coordinates: (ζ1, ζ2, S)
Centroidal axis: φ0(S , 0)
Orthonormal frame at each CS:[t1(S , 0), t2(S , 0), t3(S , 0)] = [E 1(S), E 2(S), E 3(S)]
Any point on rod in reference configuration
r(S , ζ1, ζ2, 0) = φ0(S , 0) + ζ1E 1 + ζ2E 2
φ0(S , 0) =
∫ S
0E 3dS
(29)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Curvature tensor Ω0(S) : S ∈ [0, L0] 7→ so(3) 2
dE i
dS= Ω0E i = ω0 × E i (30)
such that, ω0 = χ01E 1 + χ0
2E 2 + χ03E 3 is the axial vector of
Ω0 = ΩiIE i ⊗ E I .
2so(3) is the space of all skew symmetric tensors.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Current configuration
Centroidal axis φ0(S , t)
φ0(S , t) = φ
0(S , 0) + u1e1 + u2e2 + u3e3 (31)
Orthonormal frame at each CS [t1, t2, t3] such that
t I = Λ(S , t)E I
Λ(S , t) = t1 ⊗ E 1 + t2 ⊗ E 2 + t3 ⊗ E 3
= ΛiI e i ⊗ E I
(32)
such that Λ(S , t) : S ∈ [0, L0], t ∈ R+ 7→ SO(3)3
3SO(3) is the space of all orthonormal tensors.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Any point on the rod
r(S , ζ1, ζ2, t) = φ0(S , t) + ζ1(1 + ε1)t1 + ζ2(1 + ε2)t2 (33)
Curvature tensor Ω(S) : S ∈ [0, L0] 7→ so(3)
dt idS
= Ωt i = ω × t i (34)
such that, ω = χ1t1 + χ2t2 + χ3t3 is the axial vector ofΩ = ΩiI t i ⊗ t I .
From Eq[4]dΛ
dS= Ω Λ (35)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Notation
For any vector a ∈ R3, a = a1e1 + a2e2 + a3e3 is the spatialdescription and a = ΛTa = b1E 1 + b2E 2 + b3E 3 is thecorresponding material description. For a tensor A,A = ΛTA Λ.
For any tenor A ∈ so(3) ∃ a ∈ R3 such that Ah = a× h,known as axial vector, denote by a = axial(A).
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
F e =
1 + ε1 − αT 0 00 1 + ε2 − αT 0
s1 − ζ2k3 s2 + ζ1k3 1 + e + ζ2k1 − ζ1k2
= F e
iI t i ⊗ E I
(36)
The elastic Green-Langrange strain tensor is written as:
E e =1
2((F e)TF e − I) (37)
Following constitutive relation is used
S = 2µE e + λtrE eI (38)
where S is second Piola Kirchhoff stress.
S = σkmG k ⊗ Gm ≈ σkmE k ⊗ Em (39)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Assume σ11 = σ22 = 0. This gives
σ31 = σ13 = G (s1 − ζ1k3)
σ32 = σ23 = G (s2 + ζ2k3)
σ33 = E (e − ζ1k2 + ζ2k1 − αT )
(40)
P = F S = (t i ⊗ E i + O(ε))S = σkmtk ⊗ Em + O(ε2) (41)
This gives
T 3 = G (s1− ζ1k3)t1 +G (s2 + ζ2k3)t2 +E (e− ζ1k2 + ζ2k1−αT )t3
(42)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Strain Measures
From Eq[18], the strain measures obtained are as follows:
Γ = ΛTγ = ΛTdφ
0
dS− E 3 = s1E 1 + s2E 2 + eE 3
κ = ΛTβ = k1E 1 + k2E 2 + k3E 3
(43)
Spatial counterparts can be obtained as follows
γ = ΛΓ = s1t1 + s2t2 + et3 =dφ
0
dS− t3
β = Λκ = k1t1 + k2t2 + k3t3
(44)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Stress measures
The material counterparts of the same are given as
N = GAs1E 1 + GAs2E 2 + (EAe − PT)E 3
M = (EI1k1 −MT1)E 1 + (EI2k2 + MT2)E 2 + GJk3E 3
(45)
The spatial description of the stress measures is given for reference.
n = Λ N = GAs1t1 + GAs2t2 + (EAe − PT)t3
m = Λ M = (EI1k1 −MT1)t1 + (EI2k2 + MT2)t2 + GJk3t3
(46)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Simplifications in 2D
Continuous functions β(S) : S ∈ [0, L0] 7→ R andθ(S) : S ∈ [0, L0] 7→ R are enough to describe the orthonormalframe and curvature of the rod in reference and currentconfigurations, respectively.t1 is tangent to the centroidal axis.
E 1 = cosβe1 + sinβe2
E 2 = − sinβe1 + cosβe2
t1 = cos(β + θ)e1 + sin(β + θ)e2
t2 = − sin(β + θ)e1 + cos(β + θ)e2
ω0 = βSe3 ω = (βs + θS)e3
κ = θSe3∫ S2
S1
ωdS = (θ + β)|S2S1
e3
(47)
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Derivation of governing equations for rods withtemperature field
1: Calculate contravariant base vectors G 1,G 2,G 3 from Eq[1].2: Calculate covariant base vector g
1, g
2, g
3from Eq[5].
3: Calculate deformation gradient F = gi⊗ G i .
4: Calculate F e = F (F θ)−1 where F θ = (1 + αT (S , ζ1, ζ2))I5: Retain only first order terms and neglect higher order terms.6: Use the constitutive relation to calculate P.7: Calculate the stress measures as described.
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Objectives Literature Survey Assumptions Kinematics Stress and Strain Measures Order analysis Derivation of governing equations FEM formulation Numerical Implementation Coupling with heat equation Results Appendix
Bibliography
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J.C. Simo and L. Vu-Quoc. A three dimensional finite strain rod model. Part II: Computational aspects .
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J. Cisternas and P. Holmes. Buckling of extensible thermoelastic rods . Mathematical and Computer
Modelling, 36:233-243, 2002.
S S Antman. Nonlinear problems of elasticity (2nd edn). Springer, 1989.
A.E. Green, F.R.S., N. Laws A general theory of rods. Proc. R. Soc. Lond. A 1966 293, 145-155.
J.H. Argyris and Sp Symeonidis. Nonlinear finite element analysis of elastic systems under nonconservative
loading- Natural formulation. Part 1 Quasistatic problems . Computer Methods in Applied Mechanics andEngineering, 26:75-123, 1981.
K. J. Bathe, S. Bolourchi. Large displacement analysis of 3-D beam structures . Internation Journal for
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D. W. Coffin and F. Bloom Elastica solution for the hygrothermal buckling of a beam. International Journal
of Non-Linear Mechanics, 34: 935-947, 1999.
Crisfield M.A. A fast incremental/iterative solution procedure that handles snap-through. Computer and
Structures, 13(1):5562, 1981.
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