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Elastic Analysis Of Thick Walled Pressure Vessel Consisting Of Functionally Graded Material Under Uniformly Varying Pressure Load
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Elastic Analysis of Thick Walled Pressure Vessel Consisting of
Functionally Graded Material Under Uniformly Varying Pressure
Load
Dharmendra Kumar *, Lalit Kumar Sahu**
*(Department of Mechanical Engineering), Christian College of Engg and Tech, Bhilai, Chhattisgarh, India
Email: kdks124@gmail.com
**(Department of Mechanical Engineering), Christian College of Engg and Tech, Bhilai, Chhattisgarh, India
Email: lalitmech08@gmail.com
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Abstract:
Functionally graded Materials (or also can say, Functionally Gradient materials) are characterized as an
anisotropic material whose physical properties varies continuously as the dimensions varies randomly or
strategically, to achieve the desired characteristic.Material modelling, geometric modelling and finite
element modelling is done for the truncated cone pressure vessel and then numerical problem is solved
using the finite element software ANSYS 18.1.The study is mainly focused on comprehensive overview of
the uniformly varying pressure loading, angular velocity and different material combination for
manufacturing of functionally graded materials; choosing the best material and range of uniformly varying
pressure and angular velocity for formulation of FGMs in this field are presented.
Keywords âPressure vessel, functionally graded material, ANSYS 18.1, finite element method.
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I. INTRODUCTION
Functionally graded materials are a class of
advanced composites formed of two or more
constituent phases with a gradual and continuously
variable chemical composition, microstructure and
material properties. They were initially introduced
by a group of Japanese scientists for the purpose of
addressing the needs of aggressive environment of
thermal shock in the space shuttle in 1984 [1]. Naki
Tutuncu 2007 [5] obtained solutions for stresses
and displacements in functionally-graded
cylindrical vessels subjected to internal pressure
alone are obtained using the infinitesimal theory of
elasticity. The material is assumed to be isotropic
with constant Poissonâs ratio and exponentially-
varying elastic modulus through the thickness.Zewu
Wang et al. [21] in this paper investigation of the
optimization design of the material distribution
properties for an FGM hollow vessel subjected to
internal pressure. By constructing an exponential
function and determining the material properties,
the general analytical solution of the stresses of the
FGM pressure vessel was given based on the Euler-
Cauchy formula. And then, an optimization model
for obtaining the optimal material distribution of
FGM vessel was proposed coupling the general
finite element (FE) code.M. Z. Nejad et. al. [17]
Stresses and the displacements in thick-walled
spherical shells made of functionally graded
materials subjected to internal shells made of
functionally graded materials subjected to internal
and external pressure are developed by an analytical
method. The mechanical properties, except
Poissonâs ratio, are assumed to obey the
exponential variations throughout the thickness.
The displacement and stresses distributions were
RESEARCH ARTICLE OPEN ACCESS
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compared with the solutions of the finite element
method (FEM) and good agreement was found.
II. PROBLEM FORMULATION
In pressure vessels reduction of weight is an
important criteria retaining or even enhancing its
stress bearing capacity. As Exponential law is
selected in the base paper therefore to solve the
problem through APDL - ANSYS Parametric
Design Language ANSYS 18.1 exponential law is
chosen and considered the case of rotating truncated
cone pressure vessel with uniformly varying
pressure loading, angular velocity and different
material combination. Analysis for stresses and
deformation will be carried out for FGM truncated
conical shell with axially varying properties used
for pressure vessels.
In an FGM the variation of material properties is
usually attained by adjusting the volumefractions of
two or more compatible constituents, and the
material used is in the base paper assumed to
befunctionally graded in the radial direction. Thus,
variations in the material properties such as
Youngâsmodulus and Poissonâs ratio may be
arbitrary functions of the radial coordinate. In the
base paper Youngâs modulus with exponentially-
varying propertiesand constant Poissonâs ratio is
considered as the variation of Poissonâs ratio ν is
small forengineering materials
Modulus of elasticity of FGM pressure vessel
follow the exponential law
đ¸( đ) = đ¸ đ ( )
Where r = r´/R,r´is the radial radius, r is the
normalized radial radius, and Îą is the elastic
gradedfactor of the FGM. E is the modulus of
elasticity, and Eois the modulus of elasticity of the
external wall.
A. Validation
The dimensions of the pressure vessel as taken
in base paper are Ri = 74 mm, Ro = 80.082
mm, height = 400 mm and that of a spherical
head are (Ri = 74 mm, Ro = 77.542 mm). Two
primary materials are Al2O3 alumina for
ceramic and stainless steel for metal,
respectively. And Eo=200 GPa, ν = 0.3, and
exponent factor is Îą = 1.5. The internal
pressure is 12 MPa. The complete problem of
the base paper was solved in ANSYS APDL,
in this project also ANSYS APDL 18.1 is used.
Geometry model was converted into FE model
by the discretization method that changes
continuous material variation into stepwise
variation.
Fig 1 Radial stress of cylindrical part of the FGM pressure vessel
Fig 2: Radial stress of spherical part of the FGM pressure vessel
III. RESULTS
The aim of this project is to make a comparative
study of the radial displacements, radial stresses,
circumferential stresses and von mises stresses
developed in atruncated cone pressure vessel made
of functionally graded material of different internal
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pressure, angular velocity and material subjected to
beta angle β = 10°.
Fig 3 Geometry modelling of half of the FGM pressure vessel with Beta 10°
Elastic analysis of rotating thick truncated conical
shells made of functionally graded materials with
beta angle 10° is carried out for four different cases
with constant internal pressure of 12 MPa,
uniformly varying pressure of 4-12 MPa, 4-24MPa,
and 4-36MPa.
Fig 4 Comparison of radial displacement for varying internal pressure of
truncated cone pressure vessel
Fig. 4 show the variation of radial displacement
along the axial direction for different internal
pressure of angle of beta 10°. The value of radial
displacement is nearly equal to zero at the top and
reaches maximum at the bottom, which confirms
the constrained boundary condition applied on the
model.From the comparison of radial displacements
for variable internal pressure, it is observed that
variable internal pressure has a considerable effect
on the radial displacement. As the internal pressure
increases radial displacement also increases.
Fig. 5 show the variation of the radial stress along
the axis for different internal pressure. The value of
radial stress doesnât show a steep curve for the two
cases i.e. 12MPa constant and 4-12MPa but as the
difference in pressure increases radial stress is
maximum at the bottom and minimum at the top for
cases 4-24MPa and 4-36MPa ofinternal pressure,
which is due to fix-free boundary condition applied
on the truncated cone pressure vessel.The value of
maximum radial stress is for uniformly varying 4-
36 MPa.
Fig. 6 show the variation of the circumferential
stress along the axial direction for different internal
pressure. Circumferential stress induced in the
truncated cone pressure vesselare tensile and
compressive both in nature. Magnitude of the
compressive stress is higher than the tensile
stress.The value of maximum stress is for uniformly
varying 4-36 MPa.
Fig 5 Comparison of radial stress for varying internal pressure of truncated
cone pressure vessel
-5.00E-02
0.00E+00
5.00E-02
1.00E-01
1.50E-01
2.00E-01
0
40.155
80.31
120.47
160.62
200.78
240.93
281.09
321.24
361.4
401.55
Radialdeformation
Axial profile line
UX 4-24 MPa UX 4-12 MPa
UX 4-36 MPa UX 12 MPa const
-25
-20
-15
-10
-5
0
0 100 200 300 400 500
Radialstress
Axial profile line
SX 4-24 MPa SX 4-12 MPa
SX 4-36 MPa SX 12 MPa const
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Fig 6 Comparison of circumferential stress for varying internal pressure of
truncated cone pressure vessel
Fig. 7 show the variation of the von mises stress
along the axial direction of the shell for different
internal pressure. Von mises stress induced in the
disks is completely tensile in nature. It is maximum
at the bottom for internal pressure as pressure is
gradually increased from top to bottom. Maximum
stress is noticed for uniformly varying 4-36 MPa.
Fig 7 Comparison of von mises stress for varying internal pressure of
truncated cone pressure vessel
Fig 8 Comparison of displacement vector sum of 3 different material for
truncated cone pressure vessel
In this section different metals like ASTM A516,
ASTM SB2092014T6 commonly known as 2014
T6 alloy, ASTM B367Gr6 commonly known as Ti-
5Al-2.5Sn used for fabrication of pressure vessel is
studied under FGM. To avoid the complexity of
analyzing all the graphs only displacement is
considered in this case also strain is a dependent
variable on material therefore, by varying different
metal deformation or strain will change. A
comparative analysis will help to choose the best
material as per application from low pressure vessel
to high pressure vessel and also economical.Fig.
8shows the variation of the displacement vector
sumalong the axial direction for different internal
pressure. These are three commonly used material
for pressure vessel and it is found that ASTM A
516 is found to have a minimum deformation than
Ti 5Al 2.5 Sn followed by 2014 T6 Al alloy i.e. the
later ones can be used for low pressure vessels.
Elastic analysis of rotating thick truncated conical
shells made of functionally graded materials with
beta angle 10° and constant internal pressure of 12
MPa is carried out for three different cases of
angular velocity of 1rad/sec, 2 rad/sec and 5 rad/sec.
Fig. 9 show the variation of the displacement vector
sumalong the radius for different internal pressure.
Three angular velocity used are 1 rad/sec, 2 rad/sec,
5 rad/sec for pressure vessel and it is found that all
the three angular velocities are exhibiting nearly
-50
0
50
100
150
200
250
300
350
400
450
500
Circumferentialstress
Axial profile line
SZ 4-24 MPa SZ 4-12 MPa
SZ 4-36 MPa SZ 12 MPa const
0
100
200
300
400
500
0 100 200 300 400 500
Vonmisesstress
Axial profile line
SEQV 4-24 MPa SEQV 4-12 MPa
SEQV 4-36 MPa SEQV 12 MPa const
0.00E+00
5.00E-02
1.00E-01
1.50E-01
2.00E-01
2.50E-01
0 2 4 6 8
USUM ASTM A516
USUM 2014 T6 Al alloy
USUM Ti 5al 2.5Sn
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same values thus angular velocity has very
negligible effect and can be used with all pressure
vessels.
Fig. 10 show the variation of the von mises stress
along the radius for different internal pressure. Von
mises stress induced in the disks is completely
tensile in nature. It is found that all the three
angular velocities are exhibiting nearly same values
thus angular velocity has very negligible effect can
be used with all pressure vessels.
Fig 9 Comparison of displacement vector sum of 3 different angular velocity
for truncated cone pressure vessel
Fig 10 Comparison of von mises stress of 3 different angular velocity
for truncated cone pressure vesselexample of a book in a series in [2]
IV. CONCLUSIONS
The results obtained may be concluded as:
1. As the internal pressure increases radial
stress, circumferential stress, von mises stress and
radial displacement also increases.
2. As the angular velocity increases
circumferential stress, von mises stress and radial
displacement remains same therefore angular
velocity has very negligible effect in a pressure
vessel.
3. Three different pressure vessel grade
material were analyzed and within the given
boundary conditions ASTM A516 is found to be
capable of withstanding the maximum pressure.
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