Finite ElementModeling for Static Bending Behaviors of Rotating FGM Porous Beams with Geometrical Imperfections Resting on Elastic Foundation and Subjected to Axial Compression

'e static bending analysis of the FG porous beam resting on the two-parameter elastic foundation is initially carried out using a combination of Reddy’s high-order shear deformation theory and the finite element technique, where the initial geometrical imperfection and rotation movement in one fixed axis are calculated. 'rough the power-law distribution function with porosities, material characteristics vary constantly from one surface to the next in the direction of thickness, and the beam is concurrently impacted by an acting force perpendicular to the beam axis and an axial compressive force.'e stiffness matrix of the beam element changes as a result, and the static bending response of this beam is significantly different from that of ordinary beams. Comparison cases with published findings are used to verify the computational theory. 'e calculations clearly reveal many innovations for rotating beams that are influenced by many different kinds of loads, which may be used to the designing, manufacturing, and usage of these structures in reality.


Introduction
With the advancement of science and technology, a vast array of novel materials has been created and used to manufacturing in vital sectors with high economic efficiency, such as military, high-speed rail, and nuclear technology, to name a few. Functionally graded materials (FGM) are one of the most popular novel materials in recent years. ey are made up of two or more component elements, although the most frequent are ceramic and metal combined in certain proportions. As a result, FGM components offer all of the benefits of both ceramics and metals, including heat resistance, friction and abrasion resistance, and more strength than conventional steels. However, several flaws may emerge during the manufacturing process, the most frequent of which is the appearance of tiny porosities in the material. e presence of these microscopic porosities has a major impact on the efficiency of the structures' operating performance. As a consequence, mechanical professionals are also highly willing to investigate the mechanical behavior of structures constructed of FGM materials with porosities, and some significant research results have been obtained. To explore the nonlinear static deflections of functionally graded porosity under heat influence, Akbas [1] used the complete Lagrangian finite element technique within the two-dimensional continuum model in the Newton-Raphson method. According to Timoshenko beam theory, Mojahedin et al. [2] performed a thermoelastic study of functionally graded porous beams under in-plane thermal loading, which was applied as a uniform temperature distribution throughout the whole beam. Eltaher et al. [3] investigated the mechanical bending and vibration of functionally graded porous nanobeams using the Euler-Bernoulli and finite element methods (FEM). Hamed et al. [4] employed Euler-Bernoulli beam theory and the finite element method to model the mechanical bending behaviors of functionally graded porous nanobeams. Based on a novel improved quasi-3D shear deformation theory, Fahsi et al. [5] employed the Navier solution to investigate the bending, buckling, and free vibration responses of a functionally graded porous beam resting on an elastic basis. Based on a trigonometric shear deformation theory and finite element technique, Anirudha et al. [6] investigated the bending, vibration, and buckling properties of functionally graded porous graphene-reinforced nanocomposite curved beams. Polit et al. [7] utilized Navier's solutions and a higher-order shear deformation theory to investigate the static bending and elastic stability of thick functionally graded graphene platelets reinforced porous nanocomposite curved beams. Masjedi et al. [8] used an orthogonal Chebyshev collocation approach to investigate the large deflection behavior of functionally graded porous beams under conservative and nonconservative (follower) loading situations. Gao et al. [9] investigated the nonlinear bending of a functionally graded porous nanobeam exposed to various physical stresses using a two-step perturbation technique and the nonlocal strain gradient theory. Using a modified mixed finite element beam model, Zghal et al. [10] investigated the effect of porosity on bending static analysis of functionally graded beams. Hamed et al. [11] examined the mechanical responses of a thin/thick sandwich functionally graded beam with a porous core using a parabolic higherorder shear deformation theory. Using the extended differential quadrature approach, Nan et al. [12] developed the governing differential equations and boundary conditions of functionally gradient piezoelectric nanobeams with porosities. Based on Euler-Bernoulli beam theory, Timoshenko beam theory, and Reddy's third-order shear deformation theory, Enayat et al. [13] provided a size-dependent mechanical study of functionally graded porous nanobeams resting on Pasternak foundation in the thermal environment. Zhao et al. [14] investigated the static bending and free vibration of a size-dependent porous axially functional gradient flexoelectric Euler-Bernoulli nanobeam using the extended differential quadrature technique. Pajand et al. [15] proposed an economical and high-performance four-node isoparametric beam element for thermo-mechanical nonlinear analysis of functionally graded porous beams. Karamanli and Vo [16] used a finite element model based on a quasi-3D theory and the modified strain gradient theory to simulate the bending, vibration, and buckling behaviors of bidirectional FG porous microbeams.
Some mechanical parts may be involved in rotational motions in technological procedures, such as revolving railway bridges and rotor blades. As a result, mechanical behavior studies of these components with rotational movements are crucial in computational design, which has piqued the curiosity of experts all over the world. e following are some notable publications to consider. e findings of the mechanical reactions of spinning nanobeams utilizing the differential quadrature technique were presented by Pradhan and Murmu [17]. Based on a dynamic model, Li et al. [18] investigated the influence of bending and stretching on the free-vibration responses of a rotating FGM beam. Das [19] studied the in-plane and out-of-plane mechanical responses of rotating FGM beams using the Ritz technique and Timoshenko theory. Chen et al. [20] provided the findings of a vibration study of spinning microbeams that took into consideration the geometrical imperfection at the outset. In [21], the author also discussed the bending of beams rotating around a fixed axis, as well as the influence of temperature on FGM material without porosities. In this work, the author looks at materials having pore-type defects as well as the effect of compressive forces along the beam's axis. As a result, material objects and external loads acting on the structure are considerably different. Compared to the previous study [21], this will significantly modify the beam structure's response.
Based on the foregoing review, it is clear that no publications exists that deal with the bending analysis of rotating FG porous beams resting on an elastic foundation, in which the beam is simultaneously impacted by an axial compressive load and a force applied perpendicular to the beam axis. As a result, this work is a unique investigation that adds substantial value to engineering methods. As a result, the focus of this research is on the static bending behaviors of the aforementioned structures using Reddy's high-order shear deformation theory (HSDT) and the FEM. e remainder of this work is structured in the following manner. e effects of the initial geometrical imperfection and the loads in both the thickness and longitudinal dimensions are examined in the finite element formulas for the bending issue of rotating porous FGM beams resting on elastic foundations in Section 2. In Section 3, there are examples of verification. e bending reactions of rotating porous FGM beams are investigated numerically and discussed in Section 4. Section 5 summarizes the novel aspects of this work.

Finite Element Model of Rotating Porous
FGM Beam e goal of this work is to compute a FG beam using the model illustrated in Figure 1. e structure is embedded in a two-parameter elastic foundation with k w and k s coefficients, and the beam has length L, breadth b, and thickness h. e beam is formed of FGM material with a pore-defect of the material with a porosity volume fraction α and has an initial geometric imperfection w imp (x) in the z-direction. e entire mechanical system rotates at a constant speed ϕ around one fixed axis T, one side of the beam is offset from the axis r, and the beam is compressed axially by the load N 0 .
FG beams are often composed of two or more distinct materials with smooth material characteristics in one or two dimensions. is research focuses on beams consisting of two materials, ceramic and metal, which change depending on the thickness of the beam, with the volume of ceramic (V c ) and metal (V m ) stated as follows [22][23][24][25][26][27][28]: where n denotes the volume fraction gradient index and its fluctuation, z is the thickness coordinate variable with −h/2 ≤ z ≤ h/2, and subscripts c and m denote the ceramic and metal components, respectively.

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Based on the power-law distribution, material characteristics such as Young's modulus E, mass density ρ, and Poisson's ratio ] vary in the z-direction as [22][23][24][25][26][27][28] where α is a porosity volume fraction (α < 1). Different beam theories, ranging from classical beam theory (CBT) to higher-order shear deformation theory, can be utilized to create computational equations for beam structures (HSDT). is study employs Reddy's third-order shear deformation theory, which necessitates more complex calculation formulas and takes longer to calculate than lower-order theories. is theory, on the contrary, does not require a shear correction factor since it fulfills the zerostress boundary condition on the upper and lower surfaces of the beam, while still properly describing the structure's mechanical response. For thin to thick beams, especially thick beams, Reddy's third-order shear deformation theory can be used, which more precisely describes the mechanical reaction than classical theories and the first-order shear deformation theory. e displacement field has the following expression [29] at any location (x, z) within the beam: where u 0 (x, 0) and w 0 (x, 0) are the displacements of the point with the x coordinate in the neutral axis, respectively, whereas φ x indicates the y-axis transverse normal rotation. Individual derivatives are used to compute the longitudinal and shear strain components as follows: Advances in Materials Science and Engineering 3 where w imp represents the beam's initial geometrical imperfection (see Figure 1) and ε imp represents the strain component caused by the first geometrical imperfection. e following is how Hook's law is used to determine stress components: A weak form of the static bending model for FGM beams is as follows: In this case, the weak form of elastic energy is represented as follows: e weak form of elastic energy is expressed as follows in this case: where k w and k s are the elastic foundation's two coefficients. e weak form of the potential energy generated by the rotational movement of the FGM beam spinning around one axis Δ at the speed ϕ is computed as [20,30] in which the centrifugal force F ϕ [20] is where ρ is the density of the material. e axial compressive load acting on the beam's weak form is computed as [30] δU Axi � where N 0 denotes the beam's compressive load (see Figure 1). e external evenly distributed load F 0 acting on the FGM beam causes the weak form, which is computed as where b and h are the beam's width and thickness, respectively (see Figure 1). To create the beam's equilibrium in the finite element formula, the beam must be divided into finite elements; this work uses the two-node beam element, with each node having four degrees of freedom:

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As a result, each displacement component is approximated as follows using the Lagrange (N i ) and Hermit (H i ) shape functions and the node displacement vector q e : Equation (14) may be rewritten in a more concise manner as When strain components are represented using the nodal displacement vector, the following results are obtained: As a result, the element FGM beam's weak form of elastic energy is represented as follows: Advances in Materials Science and Engineering 5 In matrix form, the above equation is written as where the stiffness matrix of the elements is computed as follows: e axial compressive load N 0 and the weak form of the elastic foundation, centrifugal inertia force, have the following expression: where Finally, the work done by evenly distributed load F 0 operating on the FGM beam element is used to derive the force vector acting on the beam element:

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where the element's nodal force vector is computed as e equation for the static bending of FG porous beams is defined by substituting equations (18), (20), and (22) into (6): e beam element stiffness matrix is thus related to the rotational speed, elastic foundation coefficients k w and k s , and geometrical imperfection coefficient w 0 of the FGM beam, which is completely different from conventional beams; as a result, the static bending response of this beam differs from published results. Furthermore, by constructing computational formulas utilizing third-order shear deformation theory, this study eliminates the requirement for a shear correction factor, which helps to correctly characterize the mechanical reactions of FG beam systems. e boundary requirements for this calculation for beams are as follows: (i) Two sides of the beam are simply supported (denoted as S-S); each side meets the following constraints: (ii) e beam is clamped on two sides (designated C-C), with each side meeting the following requirements:

Examples of Verification
is section compares the static deflections of the FG beams predicted by this study with those calculated by other methods to validate the reliability of the computational theory proposed in Section 2.

Example 1.
e static deflections of the FGM porous beam under an evenly distributed static load are compared in this example. E m � 70 GPa, E c � 380 GPa, and ] c � ] m � 0.3 are the material characteristics of the beam, which are fully simply supported. For this problem, the top surface of the beam is metal and the bottom surface is ceramic; the uniformly distributed static load is P 0 � 10 6 N/m 2 , the length is L, and the thickness h � L/5. e formula normalizes the nondimensional maximum deflection, w � 100E m h 3 /P 0 L 4 w max . Table 1 shows the comparison findings, which were calculated using the mixed beam model (MBM) in [10]. e results of the comparison demonstrate that, as the number of components grows, the result converges to the necessary value and also converges on the published value, as shown in [10]. Because the 8-element mesh size assures accuracy, this mesh will be utilized for the computations in Section 4.

Example 2.
e bending behavior of the S-S functionally graded Al/ZrO 2 beam is then compared in this problem. L/h � 16, E m � 70 GPa, E c � 200 GPa, and ] c � ] m � 0.3 are the geometrical and material characteristics of the beam, which has a metal (Al) top surface and a ceramic bottom surface (ZrO 2 ). e nondimensional maximum deflection of the beam is computed as w � w max /5q 0 L 4 /384E Al I (with I � bh 3 /12) when the load is evenly distributed. Table 2 lists the nondimensional maximum deflections produced from this research using the Ritz technique [31], where incremental mesh size is used in this case. e 10-element mesh size ensures the requisite precision, as can be observed by the readers. As a result, this mesh will be used in the following investigations.
Example 3. Finally, the findings of nondimensional maximum deflections of the FGM beam resting on the Winkler-Pasternak two-parameter elastic foundation are shown in this case. e length L, breadth b, thickness h, and K w � K 1 L 4 /EI and K s � K 2 L 2 /EI (with I � bh 3 /12) are the geometrical and material characteristics of the beam. A evenly distributed load, q 0 , is applied to the beam. Tables 3 and 4 show nondimensional maximum deflections w � EI /P 0 L 4 w max , the differential quadrature method (DQM) [32], and precise solutions [32,33].

Influence of Rotational
Speed. e influence of rotational speed on the structure's maximum deflection will be discussed in this section. Consider a beam with with L/h � 10    and α � 0.2, geometrical imperfection coefficient m � 0.001, K * w � 20 and K * s � 5, and the distance ratio r/L � 1. e rotational speed ω rises from 0 to 10, and the volume fraction exponent n rises from 0 to 8. Figure 2 shows the dependency of the maximum deflection on the rotational speed and the volume fraction exponent, while Figure 3 shows the dependence on the rotational speed and the distance ratio r/L. Figures 4-5 show the deflection line of the beam as a function of the distance ratio r/L and the rotating speed. As a result of the numerical data, the following conclusions may be drawn: (i) As the rotating speed increases, the maximum deflection of the beam reduces, demonstrating that the centrifugal force changes the beam stiffness. is also implies that the rotational speed improves the beam's bearing capacity. When the speed parameter of the beam is between 0 and 20, the maximum deflection of the beam falls rapidly; when the value is more than 20, the maximum deflection decreases gently. (ii) As the rotating speed and the r/L ratio rise, the maximum deflection value lowers as well. At the same time, the maximum deflection position shifts to the right in relation to the midbeam position, which is entirely different from beams with no rotating movement. is demonstrates that the rotation speed and r/L ratio have an impact on the form of the deflection curve of the beam. (iii) As the volume exponent n is increased, the amount of metal material composition in the beam increases, reducing the stiffness of the beam and lowering the maximum deflection of the beam.

Effect of the Axial Compressive
Load. e impact of the axial compressive load on the static bending response of porous FG beams is investigated in this section. e compressive load N * is chosen for this purpose, with a value ranging from 0 to 1. Figure 6 shows the greatest deflections of the FG beam based on the value of N * related to the various rotating speeds. e maximum deflection of the beam rises as the N * increases; however, the rotating speed has a major impact on the increase of the maximum deflections of the beam. When the compression force N * rises for a small rotation speed, the maximum deflection of the beam increases substantially, but when N * increases for a higher rotation speed, the maximum deflection of the beam increases just little. Figure 7 shows that, as the compressive load N * increases, the maximum deflection of the porous FG beam increases, but the increase in maximum deflection is not the same when the material volume exponent is different; with n having a larger value, the proportion of metal in the beams is increased and the beam is softer, so the compressive load influence is most clearly manifested.

Effect of the Porosity Volume Fraction.
e coefficient α takes values from 0 to 0.5 to clearly illustrate the impact of the porosity volume fraction on the static bending response of FG beams, and the results of calculating the maximum deflection of the FG beams depend on α and the rotational speed are presented in Figure 8.
ese results show that when the porosity volume fraction increases, the beam gets softer, resulting in a higher maximum deflection. e increase in deflection, however, is most noticeable when the rotational speed of the beam is low due to the impact of centrifugal force. Figure 9 depicts the deflection curve of this beam as a function of varied porosity volume fraction values. e porosity volume fraction increases not only the maximum deflection of the beam but also the position of the maximum deflection, as the reader can see. e greatest deflection tends to deflect to the right, away from the rotation axis of the beam, implying that the coefficient has an impact on the form of the deflection response of FG beams.

Effect of the Elastic Foundation.
Change the elastic foundation parameter K * w to a value between 0 and 100; the coefficient K * s � 5 remains unchanged. Figure 10 shows the deflection curve for several values of the elastic foundation parameter K * w . e results of this calculation demonstrate that when the elastic foundation's coefficient rises, the maximum deflection of the beam lowers and the position of the maximum deflection of the beam changes as well. is shift, however, is not substantial or obvious, indicating that the elastic foundation coefficient impacts the maximum value of the beam deflection but has minimal effect on the point where the maximum deflection occurs.

Conclusions
e static bending of a porous FG beam resting on a twoparameter elastic foundation is initially simulated using the third-order shear deformation theory and finite element technique, in which the beam rotates around one fixed axis and an initial geometrical defect is taken into consideration. Some novel points may be drawn from the numerical results as follows: (i) As the rotating movement's speed increases, the presence of centrifugal force lowers the beam's maximum deflection. However, when the rotational speed is between 0 and 20, the change in the maximum deflection of the beam is most noticeable, and when it is more than 20, the influence of this speed on the deflection response is minimal. (ii) e maximum deflection of the beam increases as the axial compressive load N * increases, although the impact of N * on the maximum deflection of the beam is most clearly exhibited when the speed of rotation is modest. (iii) e maximum deflection reduces as the elastic foundation coefficient is increased and the porosity volume percentage is reduced. When the values of these parameters are modified, the deflection curve is likewise adjusted.

Data Availability
e data used to support the findings of this study are included in the article.

Conflicts of Interest
All authors declare that there are no conflicts of interest regarding the publication of this paper.