The theoretical formulation of an isoparametric element, from the Lagrange family. In addition, the MATLAB code of the FEM from the bilinear element with four nodes was also implemented.
Assignment developed in the scope of the finite element method course, lectured at FEUP (Faculdade de Engenharia da Universidade do Porto).
Isoparametric bilinear quadrilateral element _ ppt presentation
1. 2D Plane Elasticity – Isoparametric Bilinear Quadrilateral
Lagrange type Element
Filipe Giesteira Master student
Faculty of Engineering of University of Porto (FEUP)
Mechanical Engineering Department (DEMec)
Finite Element Method (MEF, Método dos Elementos Finitos)
Supervisor: Prof. Francisco Andrade Pires
Supervisor: Prof. José Dias Rodrigues
Finite Element Method (FEM) - Final Presentation
Faculty of Engineering of University of Porto
Building L / Room L317
Porto, 24th January 2019
Work Assignment No. 2.3
2. 2
Contents
➢ Introduction – Plane Elasticity Background Theory
➢ Weak & Strong Form – FEM Mathematical Formulation
➢ Finite Element Library – Isoparametric Bilinear Quadrilateral Element
➢ FEM Equations – Element Mechanical Properties
➢ BaPMEF FEM Tool – Script Capabilities and Limitations
➢ Validation Examples – Solutions of the Biharmonic Equation / Airy Functions
➢ Practical Applications
24-01-2019
3. 3
1. Introduction
1.1. Plane Elasticity Background Theory – Assumptions and Simplifications
24-01-2019
y
x
l
t
w
z
𝑢
Ԧ𝑣
𝑤
σzz x, y, z = ± Τt 2 = τyz x, y, z = ± Τt 2 =
τxz(x, y, z = ± Τt 2) = 0
t ≪ l ∧ t ≪ w ⇒ σzz x, y, z = τyz x, y, z =
τxz(x, y, z) = 0
t ≪ l ∧ t ≪ w ⇒ ൞
)σxx = fxx(x, y
σyy = fyy x, y
൯τxy = fxy(x, y
y
xl
tw
z
Ԧ𝑣
𝑢
𝑤
t ≫ l ∧ t ≫ w ⇒ σzz x, y, z = C te
ቊ
𝑤 𝑥, 𝑦, ± Τ𝑡 2 = 0
𝑤 𝑥, 𝑦, 0 = 0, 𝑏𝑦 𝑠𝑦𝑚.
⇒ 𝑤 𝑥, 𝑦, 𝑧 ≈ 0
𝑤 𝑥, 𝑦, 𝑧 = 0 ⇒
𝜀 𝑧𝑧(𝑥, 𝑦, 𝑧) = 0
𝛾𝑦𝑧(𝑥, 𝑦, 𝑧) = 0
𝛾𝑥𝑧(𝑥, 𝑦𝑧, 𝑧) = 0
)𝜀 𝑥𝑥 = 𝑓𝑥𝑥(𝑥, 𝑦
൯𝜀 𝑦𝑦 = 𝑓𝑦𝑦(𝑥, 𝑦
൯𝛾𝑥𝑦 = 𝑓𝑥𝑦(𝑥, 𝑦
൞
𝑓𝑥 = 𝑓𝑥 𝑥, 𝑦
𝑓𝑦 = 𝑓𝑦 𝑥, 𝑦
𝑓𝑧 = 0
➢ Plane Stress ➢ Plane Strain
15. 15
5. BapMEF FEM Tool
24-01-2019
5.1. Interface – Overview
Warnings and Notes
Input Boxes
Menu Windows
Helping graphic output during data input
Data Input
16. 16
5. BapMEF FEM Tool
24-01-2019
5.2. Data Input
Geometric Variables
Body Thickness Definition
Material Properties
Type of Plane Problem
17. 17
5. BapMEF FEM Tool
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5.3. Special Features
➢ Meshing procedure
18. 18
5. BapMEF FEM Tool
5.3. Special Features
➢ Definition of the Boundary Condition
Simple Support
Encastre
SymmetryFracture
Mechanics
20. 20
6. Validation Examples
24-01-2019
6.1. Constant Rectangular cross-section Beam – Pure Bending
𝑙
𝑙
𝒙 𝒛
𝑢 𝑥, 𝑦 = −
𝑀 𝑜
𝐸𝐼
𝑥𝑦 1 𝑢(𝑥, 𝑦) = −
12𝑀 𝑜
𝐸𝑡𝑤3 𝑥 −
𝑙
2
𝑦 −
𝑤
2
Physical Problem
Equivalent Problem
SimulatedBending Moments ??
Rotation DOF ??
[1] Silva Gomes, Mecânica dos Sólidos e Resistência dos Materiais
Change of Coordinate System
𝑦
𝑥
𝑦
𝑥
𝑤
𝑡
𝑤
𝑀 𝑜 = 𝑃 ∙ 𝑎
Original Coordinate System Coordinate System of the BaPMEF tool
21. 21
6. Validation Examples
24-01-2019
6.1. Constant Rectangular cross-section Beam – Pure Bending
Comparison of
the
displacements in
the x-direction,
determined by
the BaPMEF tool
against the
Analytical
solution
➢ Overall good match
between the Analytical
and Numeric Solution
➢ Null displacements
along the Neutral Axis
➢ Small mismatch near
the plate’s ends:
▪ Analytical
solution badly
behaved in plate’s
boundaries[1]
▪ Boundary
Conditions
difficult to model
in Plane Elasticity
Deformed
shape of
the mesh
22. 22
6. Validation Examples
24-01-2019
𝑡
𝑤
𝑢(𝑥, 𝑦) =
𝑃
6𝐺𝐼
𝑦 −
𝑤
2
3
−
𝑃𝑥2
2𝐸𝐼
𝑦 −
𝑤
2
− 𝑣
𝑃
6𝐸𝐼
𝑦 −
𝑤
2
3
+
𝑃𝑙2
2𝐸𝐼
−
𝑃𝑤2
8𝐺𝐼
𝑦 −
𝑤
2
𝑣(𝑥, 𝑦) = 𝑣
𝑃𝑥
2𝐸𝐼
𝑦 −
𝑤
2
2
+
𝑃𝑥3
6𝐸𝐼
−
𝑃𝑙2 𝑥
2𝐸𝐼
+
𝑃𝑙3
3𝐸𝐼
𝑢(𝑥, 𝑦) =
𝑃
6𝐺𝐼
𝑦 −
𝑤
2
3
−
𝑃𝑥2
2𝐸𝐼
𝑦 −
𝑤
2
− 𝑣
𝑃
6𝐸𝐼
𝑦 −
𝑤
2
3
+
𝑃𝑙2
2𝐸𝐼
𝑦 −
𝑤
2
𝑣(𝑥, 𝑦) = 𝑣
𝑃𝑥
2𝐸𝐼
𝑦 −
𝑤
2
2
+
𝑃𝑥3
6𝐸𝐼
−
𝑃𝑙2
2𝐸𝐼
+
𝑃𝑤2
8𝐺𝐼
𝑥 +
𝑃𝑙3
3𝐸𝐼
+
𝑃𝑤2 𝑙
8𝐺𝐼
𝜕𝑣
𝜕𝑥 𝑥=𝑙 ; 𝑦=0
= 0
𝜕𝑢
𝜕𝑦 𝑥=𝑙 ; 𝑦=0
= 0
Situation (ii) 1
Situation (i) 1
➢ Shear distributed Load
➢ There is no approximation in the definition of the BC
➢ It is also necessary to change the coordinate system
6.2. Constant Rectangular cross-section Beam – Cantilever Beam
under Tangential Traction at the end
[1] Silva Gomes, Mecânica dos Sólidos e Resistência dos Materiais
Problem Simulated
𝑦
𝑥
𝑞
𝑙
𝑤𝑃
𝒒 =
𝑷
𝒘 ∙ 𝒕
23. 23
6. Validation Examples
24-01-2019
➢ Good match between
the Numerical and
Analytical Solutions –
The Numeric Solution
is always in-between
the two Analytical
Solutions
➢ Null displacements
along the Neutral Axis
➢ Situation (i) is more
“rigid”
➢ Situation (ii) is more
“flexible”
6.2. Constant Rectangular cross-section Beam – Cantilever Beam
under Tangential Traction at the end
Horizontal Displacements
along the plate
Deformed Shape of the Mesh
24. 24
6. Validation Examples
24-01-2019
6.2. Constant Rectangular cross-section Beam – Cantilever Beam
under Tangential Traction at the end
➢ Good match between
the Numerical and
Analytical Solutions –
The Numeric Solution
is always in-between
the two Analytical
Solutions
➢ Null displacements
along the Neutral Axis
➢ Situation (i) is more
“rigid”
➢ Situation (ii) is more
flexible
Vertical Displacements along the plate
25. 25
6. Validation Examples
24-01-2019
6.2. Constant Rectangular cross-section Beam – Cantilever Beam
under Tangential Traction at the end
➢ H-type Mesh Refinement
Elements: Length=1 x Width=2 Elements: Length=2 x Width=2
Elements: Length=8 x Width=2 Elements: Length=25 x Width=10
27. 27
6. Validation Examples
24-01-2019
6.3. Constant Rectangular cross-section Beam – Simple Supported Beam
under Uniform Surface Traction
➢ It is also necessary to change the original Coordinate System of the Analytical Solution
➢ Analytical Solutions for the Stresses
𝜎 𝑥𝑥
1 =
𝑸
2𝐼
2
3
𝑦 −
𝑤
2
3
−
𝑤2
10
𝑦 −
𝑤
2
−
𝑸
2𝐼
𝑥 −
𝑙
2
2
−
𝑙2
4
𝑦 −
𝑤
2
𝜎 𝑦𝑦
1 = −
𝑸
2𝐼
𝑦 −
𝑤
2
3
3
−
𝑤2
4
𝑦 −
𝑤
2
−
𝑤3
12
𝜏 𝑥𝑦
1 =
𝑸
2𝐼
𝑦 −
𝑤
2
2
−
𝑤2
4
𝑥 −
𝑙
2
[1] Silva Gomes, Mecânica dos Sólidos e Resistência dos Materiais
Deformed Shape of the Mesh
28. 28
6. Validation Examples
6.3. Constant Rectangular cross-section Beam – Simple Supported Beam
under Uniform Surface Traction
➢ Good match between the Numerical and Analytical
Solutions for the Vertical Displacement in the y-direction
3D Surface Plot of the vertical displacements along the plate 2D Plot of the vertical displacements along the Neutral Axis
29. 29
6. Validation Examples
6.3. Constant Rectangular cross-section Beam – Simple Supported Beam
under Uniform Surface Traction
➢ Overall good match between the Numerical and Analytical
Solutions for the Normal Stress in the x-direction
➢ Effect of the local Supports
3D Surface Plot of the Stress in the x-direction along the plate 2D Plot of the Stress in the x-direction along the Neutral Axis
30. 30
6. Validation Examples
6.3. Constant Rectangular cross-section Beam – Simple Supported Beam
under Uniform Surface Traction
➢ Overall good match between the Numerical and Analytical
Solutions for the Normal Stress in the y-direction
➢ Pronounced effect of the local Supports
3D Surface Plot of the Stress in the y-direction along the plate 2D Plot of the Stress in the y-direction along the Neutral Axis
31. 31
6. Validation Examples
6.3. Constant Rectangular cross-section Beam – Simple Supported Beam
under Uniform Surface Traction
➢ Overall good match between the Numerical and Analytical
Solutions for the Normal Stress in the x-direction
➢ Effect of the local Supports
3D Surface Plot of the Shear Stress along the plate 2D Plot of the Shear Stress along the Neutral Axis
32. 32
7. Practical Applications
24-01-2019
7.1. Fracture Mechanics – Plate with Centered Crack
2a
𝑊
𝐿
𝑞
𝑞
𝑊
𝑡
a
𝑤 =
𝑊
2
𝑙 =
𝐿
2
Physical Problem
Equivalent Problem Simulated
➢ There is no approximation in the definition of the BC
➢ It is also necessary to change the original Coordinate
System of the Analytical Solutions
➢ Application of the Mesh Refinement Control
Mesh Control mode and Zoom of the Stresses in y-direction near the crack tip
34. 34
7. Practical Applications
24-01-2019
7.1. Fracture Mechanics – Plate with Centered Crack
➢ Crack Opening Shape
➢ Plate infinitely higher than the crack length – overlap between solution (i), (ii), and (iii)
➢ Solution (i), (ii), and (iii) are only valid near the crack tip – overlap between all solution near the crack tip
Vertical Displacements – Plane Stress Vertical Displacements – Plane Strain
Overlap Solution
(i), (ii), and (iii)
Crack tip
region
35. 35
7. Practical Applications
24-01-2019
7.1. Fracture Mechanics – Plate with Centered Crack
➢ Stresses along the plate, starting near the
crack tip
➢ Plate infinitely higher than the crack length
– overlap between solution (i), (ii), and (iii)
➢ Solution (i), (ii), and (iii) are only valid near
the crack tip – overlap between all solution
near the crack tip
Stress in the y-direction near the crack tip
Stress in the y-direction far from the crack tip
36. 36
7. Practical Applications
24-01-2019
7.2. BaPMEF vs. Abaqus®
15 Τ𝑁 𝑚𝑚2
𝑷
5 Τ𝑁 𝑚𝑚2
150 [𝑁]
500 [𝑁]
50 [𝑁]
100 [𝑚𝑚]
100 [𝑚𝑚]
30 [𝑚𝑚] 30 [𝑚𝑚]
20 [𝑚𝑚] 20 [𝑚𝑚]
10 Τ𝑁 𝑚𝑚2
BaPMEF
➢ Commercially
Available FEA Software
– Abaqus ®
➢ Plane Strain Problem
➢ Generic Loading – No
Analytical Solution
Available
➢ Gravity Body Forces
➢ Surface Tractions acting
along the whole
boundary
➢ Surface Tractions acting
on each Element
Problem
Simulated
in Abaqus
Problem Simulated
in BaPMEF
Gravity Force