Complete closed-form solution for pressurized heterogeneous thick spherical shells/Nevienalycio heterogeninio storasienio kevalo issamus uzdaros formos sprendimas.

Ghannad, Mehdi ; Nejad, Mohammad Zamani

1. Introduction

A thick-walled spherical shell subjected to pressure in radial direction is one of the classical problems in engineering mechanics. This problem was studied by several researchers in the past. Among them, Timoshenko and Goodier [1] obtained the analytical expressions of stresses and displacement in a thick-walled sphere subjected to internal and external pressure. In the recent past, there has been a strong increase in the interest in functionally graded materials. FGMs are composite materials that are microscopically nonhomogeneous but at macrolevel, the mechanical properties vary continuously from one surface to another by smoothly varying the volume fractions of the material constituents. Heterogeneous composite materials are FGMs with gradient compositional variation of the constituents from one surface of the material to the other which results in continuously varying material properties. These materials are advanced, heat resisting, erosion and corrosion resistant, and have high fracture toughness. The FGM spherical shells are widely used in many engineering fields such as aerospace, mechanical, naval, nuclear energy, chemical plant, electronics, and biomaterials and so on.

Closed-form solutions are obtained by Tutuncu and Ozturk [2] for cylindrical and spherical vessels with variable elastic properties obeying a simple power law through the wall thickness which resulted in simple Euler-Cauchy equations whose solutions were readily available Elastic analysis of internally pressurized thick-walled spherical pressure vessels of functionally graded materials was studied [3]. In the paper, two kinds of pressure vessels are considered: one consists of two homogeneous layers near the inner and outer surfaces of the vessel and one functionally graded layer in the middle; the other consists of the functionally graded material only. Based on the assumption that Poisson's ratio is constant and modulus of elasticity is an exponential function of radius, Chen and Lin [4] have analyzed stresses and displacements in FG cylindrical and spherical pressure vessels. A hollow sphere made of FGMs subjected to radial pressure was analyzed in [5]. Using plane elasticity theory and Complementary Functions method, Tutuncu and Temel [6] obtained axisymmetric displacements and stresses in functionally-graded hollow cylinders, disks and spheres subjected to uniform internal pressure. Zamani Nejad et al. [7] developed 3-D set of field equations of FGM thick shells of revolution in curvilinear coordinate system by tensor calculus. Deformations and stresses inside multilayered thick-walled spheres are investigated [8]. In the paper, each sphere is characterized by its elastic modules. Assuming the volume fractions of two phases of a FG material (FGM) vary only with the radius, Nie et. al. [9] obtained a technique to tailor materials for functionally graded (FG) linear elastic hollow cylinders and spheres to attain through the thickness either a constant hoop (or circumferential) stress or a constant in-plane shear stress.

In this study, a complete analytical solution for FGM thick-walled spherical shells subjected to internal and/or external pressures is presented. The analytical solution which is closed-form is obtained for real, double and complex roots of equation and distribution of stresses and displacement are compared with the solution using finite element method.

2. Basic formulations of the problem

Consider a thick hollow FGM sphere with an inner radius [R.sub.i], and an outer radius [R.sub.o], subjected to internal and external pressure [P.sub.i] and [P.sub.o], respectively.

The classical theory is based on the assumption that the straight sections perpendicular to the central axis of the sphere remains unchanged after loading and deformation. According to this theory, the deformations are axisymmetric and do not change along the circumference of sphere. In other words, the radial deformation is dependent only on radius [u.sub.R](R). The value of shear strains and shear stresses are zero. Therefore, normal stresses are principal stresses. In the spherical shells, because of dual central symmetry, both the values of circumferential and meridional strains and those of stresses are equal. Thus,

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (1)

The strains are expressed in terms of the radial displacement [u.sub.R] as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (2)

The equilibrium equation of the FGM hollow sphere, in absence of body forces, is expressed as

d[[sigma].sub.R]/dR + 1/R(2[[sigma].sub.R] - [[sigma].sub.[theta]] - [[sigma].sub.[phi]]) = 0 (3)

and the constitutive relations for nonhomogenous and isotropic materials are

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (4)

A and B are related to Poisson's ratio, (v = const.) as

A = [1 - [upsilon]]/(1 + [upsilon])(1 - 2[upsilon]), B = [upsilon]/(1 + [upsilon])(1 - 2[upsilon]) (5)

It is assumed that the nonhomogeneous modulus of elasticity E is power function of R as

E(R) = [E.sub.i][(R/[R.sub.i]).sup.n] (6)

where [E.sub.i] is the modulus of elasticity at the internal surface R = [R.sub.i], and n is the inhomogeneous constant determined empirically.

Now suppose that r = R/[R.sub.t], thus Eqs. (2) to (4) and (6) may be rewritten as

[[epsilon].sub.R] = d[u.sub.r]/dr, [[epsilon].sub.[phi]] = [[epsilon].sub.[theta]] = [u.sub.r]/r (7)

[d[[sigma].sub.R]/dr] + [2/r] ([[sigma].sub.R] - [[sigma].sub.[phi]]) = 0 (8)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (9)

E(r) = [E.sub.i][r.sup.n] (10)

Substitution of Eqs. (7) and (10) into Eq. (9), and the use of Eq. (8) lead to the equation

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (11)

After simplification, Eq. (11) is expressed as

[[d.sup.2][u.sub.r]/[dr.sup.2]] + (n + 2/r) [[du.sub.r]/dr] + [2/[r.sup.2]] (n [B/A] - 1) [u.sub.r] = 0 (12)

Eq. (12) is the nonhomogeneous Euler-Caushy equation

[r.sup.2][u".sub.r] + (n + 2)r[u'.sub.r] + (n[v.sup.*] - 1)[u.sub.r] = 0 (13)

where ' and " denote first and second differentiation with respect to r and the value of [v.sup.*] = B/A is obtained based on Eq. (5).

Substituting [u.sub.r](r) = [r.sup.m] in Eq. (13), the characteristic equation is obtained as follows

[m.sup.2] + (n + 1)m + 2(n[[upsilon].sup.*] - 1) = 0 (14)

The roots of characteristic equation are

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (15)

These roots may be (i) real, (ii) double, (iii) complex.

[FIGURE 1 OMITTED]

3. Solution for heterogeneous thick sphere

Now, differential Eq. (13) for real, double and complex roots will be solved. Following that, in each of the cases, parametric equations of radial stress, meridional stress and radial displacement will be derived.

3.1. Real roots

In this case, [DELTA] > 0 and we have

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (16)

The solution of Eq. (13) is as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (17)

With substitution of Eqs. (17) into Eq. (7) and then use of Eq. (9), radial and meridional stresses are obtained as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (18)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (19)

For a sphere subjected to internal and external pressure, constants [C.sub.1] and [C.sub.2] are determined using boundary conditions as

[[sigma].sub.R][|.sub.r=1] = -[P.sub.i], [[sigma].sub.R][|.sub.r=k] = -[P.sub.o] (20)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (21)

thus where k = [R.sub.o]/[R.sub.i].

With substituting [C.sub.1] and [C.sub.2] into Eqs. (17) and (9), [[sigma].sub.R], [[sigma].sub.[phi]] and [u.sub.R] are obtained as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (22)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (23)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (24)

Now, given the Eq. (5), Eqs. (23) and (24) may be rewritten as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (25)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (26)

The value of effective stress based on von Mises and Tresca failure theories is as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (27)

In [2], radial and meridional stresses are obtained only for [DELTA] > 0 case. The equation of radial stress has been obtained correctly while the equation of meridional stress has been derived incorrectly.

3.2. Double roots

In Eq. (15), if [DELTA] = 0, then the equation will have double roots.

[m.sub.1] = [m.sub.2] = m = -[n + 1/2] (28)

In this case, the solution of Eq. (13) is as follows.

[u.sub.r](r) = ([C.sub.1] + [C.sub.2] ln r)[r.sup.m] (29)

With substitution of Eq. (29) into Eq. (7) and then use of Eq. (9), radial and meridional stresses are obtained as follows

[[sigma].sub.R] = [E.sub.i][r.sup.n+m-1]{[[C.sub.1] (Am + 2B) + [C.sub.2][A + (Am + 2B)lnr]} (30)

[[sigma].sub.[phi]] = [E.sub.i][r.sup.n+m-1]{[[C.sub.1] (Bm + A + B) + [C.sub.2][A + (Bm + A + B)lnr]} (31)

To determine the unknown constants [C.sub.1] and [C.sub.2], using boundary conditions (20), yields

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (32)

With substituting [C.sub.1] and [C.sub.2] into Eqs. (29) to (31), [[sigma].sub.R], [[sigma].sub.[phi]] and [u.sub.R] are obtained as follows

[[sigma].sub.R] = -[[r.sup.n+m-1]/ln k][[P.sub.i]ln [k/r] + [k.sup.l-m-n][P.sub.o]lnr (33)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (34)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (35)

Given the Eq. (5), Eqs. (34) and (35) may be rewritten as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (36)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (37)

3.3. Complex roots

In Eq. (15), if [DELTA] < 0, then the equation will have complex roots.

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (38)

In this case, the solution of Eq. (13) is as follows

[u.sub.r](r) = [[C.sub.1] cos(y ln r) + [C.sub.2] sin(y ln r)][r.sup.z] (39)

With the substitution of Eq. (39) into Eq. (7) and then use of Eq. (9), radial and meridional stresses are obtained as follows

[[sigma].sub.R] = [E.sub.i][r.sup.n+z-1]{[C.sub.1][(Az + 2B)cos(y ln r) - Ay sin (y ln r)] + [C.sub.2][[Ay + 2B] sin (y ln r) + Ay cos (y ln r)]} (40)

[[sigma].sub.[phi]] = [E.sub.i][r.sup.n+z-1]{[C.sub.1][(Az + 2B)cos(y ln r) - Ay sin (y ln r)] + [C.sub.2][[Ay + 2B] sin (y ln r) + Ay cos (y ln r)]} (41)

Using boundary conditions (20), constants [C.sub.1] and [C.sub.2] are obtained as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (42)

where

D = [[(Az + 2B).sup.2] + [A.sup.2][y.sup.2]] (43)

With substituting [C.sub.1] and [C.sub.2] into Eq. (39) to (41), [[sigma].sub.R], [[sigma].sub.[phi]] and [u.sub.R] are obtained as follows

[[sigma].sub.r] = - [r.sup.n+z-1]/sin(y ln k)[sun(y ln [k/r])[P.sub.i] + sin(y ln r)[P.sub.o][k.sup.l-n-z]] (44)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (45)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (46)

Given the Eqs. (5), (45) and (46) may be rewritten as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (47)

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (48)

where

D = [[(1-[upsilon])z + 2[upsilon]].sup.2] + [[(1 - [upsilon])y].sup.2] (49)

4. Solution for thick homogenous spheres

In thick homogenous and isotropic spheres, modulus of elasticity and Poisson's ratio are both constant. By substituting n = 0 into Eq. (6), homogenous materials are obtained. In this case, Euler-Caushy equation (Eq. (13)) in terms of the displacement is as

[r.sup.2][u".sub.r] + 2r[u'.sub.r-] - 2[u.sub.r] = 0 (50)

The characteristic equation and the roots of characteristic equation are as follows:

[m.sup.2] + m - 2 = 0 [??] [m.sub.1,2] = +1, -2 (51)

It could be observed that roots of the characteristic equation are the real (roots are in set of [DELTA] > 0).

[u.sub.r](r) = [C.sub.1]r + [[C.sub.2]/[r.sup.2]] (52)

Using the boundary conditions are given in Eq. (20), the constants of C1 and C2 become

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (53)

Substituting [C.sub.1] and [C.sub.2] in Eq. (52) and using Eqs. (7) and (9). Thus

[[sigma].sup.H.sub.R] = [1/[k.sup.3] - 1][([P.sub.i] - [k.sup.3][P.sub.o]) - ([P.sub.i] - [P.sub.o]) [k.sup.3]/[r.sup.3]] (54)

[[sigma].sup.H.sub.[phi]] = [1/[k.sup.3] - 1][([P.sub.i] - [k.sup.3][P.sub.o]) - ([P.sub.i] - [P.sub.o]) [k.sup.3]/2[r.sup.3]] (55)

[u.sup.H.sub.R] = [R.sub.i]r/E([k.sup.3] - 1) [([P.sub.i] - [k.sup.3][P.sub.o]/A + 2B) + (([P.sub.i] - [P.sup.o]/A - B) [k.sup.3]/2[r.sup.3]] (56)

The values of the radial and meridional stresses in homogeneous and isotropic thick-walled spheres subjected to constant pressure, with the same dimensions and different values of modulus of elasticity are equal.

The value of effective stress based on von Mises and Tresca failure theories is as follows

[[sigma].sup.H.sub.eff] = [3/2([k.sup.3] - 1)] [absolute value of ([P.sub.i] - [P.sub.o]) [[k.sup.3]/[r.sup.3]]] (57)

Radial displacement (Eq. (56)) may be rewritten as follows

[MATHEMATICAL EXPRESSION NOT REPRODUCIBLE IN ASCII] (58)

5. Results and discussion

Consider a heterogeneous thick-walled sphere, subjected to internal and/or external constant uniform pressures of 80 MPa, with the internal radius of [R.sub.i] = 40 mm and the outer radius of [R.sub.o] = 60 mm. The modulus of elasticity [E.sub.i] at internal radius has the value of 200 GPa. It is also assumed that the Poisson's ratio, v, has a constant value of 0.3.

5.1. Homogeneous sphere

Radial and meridional stresses in homogeneous and isotropic spheres are independent of the mechanical properties; whereas, radial displacement is dependent on mechanical properties. Figs. 2 to 4 are plotted according to the internal pressure [P.sub.i] = 80 MPa and/or external pressure [P.sub.o] = 80 MPa.

[FIGURE 2 OMITTED]

[FIGURE 3 OMITTED]

[FIGURE 4 OMITTED]

[FIGURE 5 OMITTED]

Distribution of compressive radial stress based on Eq. (54) is shown in Fig. 2. When both the internal and external pressures are applied, and their values are equal, the radial stress will be constant along the wall.

In Fig. 3, distribution of meridional stress based on Eq. (55) is shown. Along the wall, the meridional stress will be tensile while just the internal pressure is present; whereas, it will be compressive when just the external pressure is there. When the internal and external pressures are equal, the meridional stress will be compressive and constant in value along the wall. The meridional stress is more in the case of external pressure compared to that of the other two cases. In Fig. 4, distribution of radial displacement based on Eq. (56) is shown. In the case where only the internal pressure is present, the radial displacement is expansionary; whereas, in other two cases it is contractionary. The highest value of radial displacement occurs in the case of the external pressure. Distribution of effective stress based on Eq. (57) is shown in Fig. (5). It is observed that, when [P.sub.i] = [P.sub.o], the value of effective stress for homogeneous sphere is equal to zero.

5.2. Heterogeneous sphere

In nonhomogeneous and isotropic spheres, radial and meridional stresses are dependent on mechanical properties by means of n; while radial displacement depends on them by means of both n and Ei. Modulus of elasticity through the wall thickness is assumed to vary as E(R) = [E.sub.i][(R/[R.sub.i]).sup.n] in which the range -2 [less than or equal to] n [less than or equal to] 2 is used in the present study.

[FIGURE 6 OMITTED]

In Fig. 6, for different values of n modulus of elasticity along the radial direction is plotted. It is apparent from the curve that a positive n means increasing stiffness in the radial direction whereas a negative value of n results in a decrease in stiffness in the radial direction.

5.2.1. Internal pressure

Here the nonhomogeneous sphere is only under internal pressure, [P.sub.i] = 80 MPa.

Fig. 7 shows the distribution of the compressive radial stress along the radius. The value of stress in inner and outer layers is the same, and for both layers [[sigma].sub.R]/[[sigma].sup.H.sub.R] is one. Along the radius, for n < 0, the radial stress decreases whereas for n > 0 the radial stress increases. The decrease and increase of the stress depend on [absolute value of n].

Fig. 8 shows the distribution of the tensile meridional stress along the radius. The value of stress in inner and outer layers is not the same, and for both layers [[sigma].sub.[phi]]/[[sigma].sup.H.sub.[phi]], is not one. The value of the meridional stress is more than the homogeneous material for n < 0 in the inner half of the wall thickness while it is less than that in the outer half. This will be reverse, where n > 0. The curve associated with n = 1 shows that the variation of meridional stress along the radial direction is minor and is almost constant across the radius which can be an advantage in terms of stress control. It is observed that in the range of the inner layer of the sphere, the graphs converge and behave similarly.

[FIGURE 7 OMITTED]

[FIGURE 8 OMITTED]

[FIGURE 9 OMITTED]

[FIGURE 10 OMITTED]

Fig. 9 shows the distribution of the radial displacement of the sphere along the radius. [u.sub.R]/[u.sup.H.sub.R] is not one at any point. For n < 0 the radial displacement of the sphere is more than where the material is homogeneous and it is the reverse for n > 0. Yet this ratio remains almost constant along the wall thickness.

The graph of effective stress based on Eq. (27) is shown in Fig. 10. It must be noted from this figure that at the same position, almost for (R/[R.sub.i]) < 1.18, there is a decrease in the value of the effective stress as n increases, whereas for (R/[R.sub.i]) > 1.18 this situation was reversed.

5.2.2. External pressure

In this section, the nonhomogeneous sphere is only under external pressure, [P.sub.o] = P = 80 MPa.

The distribution of the compressive radial stress of the sphere along the radius is shown in Fig. 11. The value of the stress in the inner and outer layers of the sphere is the same and [[sigma].sub.R]/[[sigma].sup.H.sub.R] = 1. In the sphere wall the radial stress increases for n < 0 and decreases for n > 0. The magnitude of decrease or increase of the stress depends on |n|. The distribution of the compressive meridional stress of the sphere along the radius is shown in Fig. 12. The value of the stress is not the same in the inner and outer layers and [[sigma].sub.[phi]]/[[sigma].sup.H.sub.[phi]] does not equal to one. The value of the meridional stress is more than the homogeneous material for n < 0 in the inner half of the wall thickness while it is less than that in the outer half. This will be reverse, where n > 0. The meridional stress is almost constant along the radius for n = 1. It is observed that in the range of the inner layer of the sphere, the graphs converge and behave similarly.

[FIGURE 11 OMITTED]

[FIGURE 12 OMITTED]

Fig. 13 shows the distribution of the radial displacement of the sphere along the wall thickness. [u.sub.R]/[u.sup.H.sub.R] does not equal one at any point. The value of the radial displacement is more than the homogeneous material for n < 0 while it is less than that for n > 0. Yet this ratio remains almost constant along the wall thickness.

[FIGURE 13 OMITTED]

5.2.3. Internal and external pressure

The nonhomogeneous sphere is subjected to the internal and external pressures, [P.sub.i] = [P.sub.o] = P = 80 MPa.

The distribution of the compressive radial stress of the sphere along the wall thickness is shown in Fig. 14. The value of the radial stress in the inner and outer layers of the sphere is the same and [[sigma].sub.R]/[[sigma].sup.H.sub.R] = 1. In the sphere wall, the radial stress is more than the radial stress of the homogeneous sphere for n < 0 and is the reverse for n > 0. In the homogeneous sphere, radial stress is almost constant along the wall thickness.

[FIGURE 14 OMITTED]

The distribution of the compressive meridional stress of the sphere along the wall thickness is shown in Fig. 15. The value of the meridional stress is not the same in the inner and outer layers of the sphere and [[sigma].sub.[phi]]/[[sigma].sup.H.sub.[phi]] does not equal to one. The value of the meridional stress is more than the homogeneous material for n < 0 in the inner half of the wall thickness while it is less than that in the outer half. This will be reverse, where n > 0. The meridional stress is almost constant along the radius for n = 0. It is observed that in the range of the inner layer of the sphere, the graphs converge and behave similarly. Fig. 16 shows the distribution of the radial displacement of the sphere along the wall thickness. [u.sub.R]/[u.sup.H.sub.R] is not one at any point. In the sphere wall, the radial displacement is more than the radial displacement of the homogeneous sphere for n < 0 and is the reverse for n > 0. In the homogeneous sphere, radial displacement is almost constant along the wall thickness.

[FIGURE 15 OMITTED]

[FIGURE 16 OMITTED]

In Table, the values of effective stress resulting from analysis of sphere through PET and FEM under internal pressure and/or external pressure in the middle layer are given.

6. Conclusions

It can be concluded that for both positive and negative values of n, the meridional stress in the nonhomogeneous sphere decreases in one half and increases in the other. In the nonhomogeneous sphere compared to the homogeneous one, with no external pressure, the radial stress increases and the radial displacement decreases for positive n. For negative n both radial stress and radial displacement increase in the spheres subjected to external pressure. The radial stress and radial displacement decrease for positive n. Decrease or increase of the radial stress and radial displacement depend on [ABSOLUTE VALUE OF N]. According to the requirements for decreasing of the displacement and stress in the nonhomogeneous spheres, the positive or negative values of n could be applied.

References

[1.] Timoshenko, S.P.; Goodier, J.N. 1970. Theory of Elasticity, 3rd Edition, New York: McGraw-Hill, 395p.

[2.] Tutuncu, N.; Ozturk, M. 2001. Exact solutions for stresses in functionally graded pressure vessels, Composites Part B-Engineering 32(8): 683-686. http://dx.doi.org/10.1016/S1359-8368(01)00041-5.

[3.] You, L.H.; Zhang, J.J.; You, X.Y. 2005. Elastic analysis of internally pressurized thick-walled spherical pressure vessels of functionally graded materials, International Journal of Pressure Vessels and Piping 82(5): 347-354. http://dx.doi.org/10.1016/jijpvp.2004.1L00L

[4.] Chen, Y.Z.; Lin, X.Y. 2008. Elastic analysis for thick cylinders and spherical pressure vessels made of functionally graded materials, Computational Materials Science 44(2): 581-587. http://dx.doi.org/10.1016/j.commatsci.2008.04.018.

[5.] Li, X-F.; Peng, X-L.; Kang, Y-A. 2009. Pressurized hollow spherical vessels with arbitrary radial nonhomogeneity, AIAA Journal 47(9): 2262-2265. http://dx.doi.org/10.2514/L41995.

[6.] Tutuncu, N.; Temel, B. 2009. A novel approach to stress analysis of pressurized FGM cylinders, disks and spheres, Composite Structures 91(3): 385-390. http://dx.doi.org/10.1016/j.compstruct.2009.06.009.

[7.] Nejad, M.Z.; Rahimi, G.H.; Ghannad, M. 2009. Set of field equations for thick shell of revolution made of functionally graded materials in curvilinear coordinate system, Mechanika 3(77): 18-26.

[8.] Borisov, A.V. 2010. Elastic analysis of multilayered thick-walled spheres under external load, Mechanika 4(84): 28-32.

[9.] Nie, G.J.; Zhong, Z.; Batra, R.C. 2011. Material tailoring for functionally graded hollow cylinders and spheres, Composites Science and Technology 71(5): 666-673. http://dx.doi.org/10.1016/j.compscitech.2011.0L009.

Mehdi Ghannad, Mechanical Engineering Faculty, Shahrood University of Technology, Shahrood, Iran E-mail: ghannad. [email protected]

Mohammad Zamani Nejad, Mechanical Engineering Department, Yasouj University, Yasouj P. O. Box: 75914-353, Iran E-mail: [email protected]

http://dx.doi.org/10.5755/j01.mech.18.5.2702

Received May 30, 2011

Accepted October 12, 2012

Table
Comparison of values of effective stress resulting from PET and FEM
in the middle layer

 n = -2 n = -1 n = 0 n = +1 n = +2

[P.sub.i] = 80 MPa PET 77.81 82.90 87.31 90.88 93.51
 FEM 77.95 83.01 87.39 90.92 93.53
[P.sub.o] = 80 MPa PET 73.31 80.89 87.31 92.35 95.85
 FEM 73.48 81.01 87.39 92.38 95.86
[P.sub.i] = PET 4.50 2.02 0 1.47 2.34
[P.sub.o] = 80 MPa
 FEM 4.47 2.00 0 1.46 2.33