Global and Local Dynamics of a Bistable Asymmetric Composite Laminated Shell

: As bistable composite laminated plate and shell structures are often exposed to dynamic environments in practical applications, the global and local dynamics of a bistable asymmetric composite laminated shell subjected to the base excitation is presented in this paper. Temperature difference, base excitation amplitude, and detuning parameters are discussed. With the change of temperature difference, the super-critical pitchfork bifurcation occurs. Three equilibrium solutions corresponding to three equilibrium conﬁgurations (two stable conﬁgurations and one unstable conﬁguration) can be obtained. With the increase of excitation amplitude, local and global dynamics play a leading role successively. The global dynamics between the two stable conﬁgurations behave as the periodic vibration, the quasi-periodic vibration, the chaotic vibration and dynamic snap-through when the excitation amplitude is large enough. The local dynamics that are conﬁned to a single stable conﬁguration behave as 1:2 internal resonance, saturation and permeation when the excitation amplitude is small. Dynamic snap-through and large-amplitude vibrations with two potential wells for the global dynamics will lead to a broad application prospect of the bistable asymmetric composite laminated shell in energy harvesting devices.


Introduction
Bistable composite laminates possess many distinctive features regarding their two stable equilibrium configurations, which have been proposed to generate new deformable and deployable structures in a series of engineering fields. When asymmetric composite laminates are cooled from higher manufacturing temperature to service temperature or room temperature, the residual thermal stress is produced. Due to the residual thermal stress and geometric nonlinearity, the bistable composite laminates have three equilibrium configurations, which are two stable equilibrium configurations and one unstable equilibrium configuration. One stable configuration is cylindrical with a dominant x-curvature and imperceptible y-curvature. Similarly, the other stable configuration is cylindrical with a dominant y-curvature and imperceptible x-curvature. What needs to be pointed out is that no energy is required to hold the two stable equilibrium configurations, and the two stable configurations can be converted to each other through snap-through, which is strongly nonlinear in nature when enough energy is applied.
In recent years, a flood of literature has been concerned with the statics of bistable plate and shell structures. Due to the residual thermal stress, the asymmetric composite laminates possess bistable characteristics [1][2][3][4][5]. Sorokin and Terentiev [6] found that the transformation between the two stable configurations is realized through snap-through. Dano and Hyer [7] used an approximate displacement field to calculate forces and moments for static snap-through. Cantera et al. [8] modeled bistable responses including the processes of snap-through based on the Rayleigh-Ritz method. Portela et al. [9] studied the bistable composite laminates, which were actuated by piezoelectric patches. Dano and Hyer [10] calculated the loads for snap-through and developed a driving scheme based on shape memory alloys (SMAs) by extending the previous model of asymmetric bistable composite laminates. Dano and Hyer [11] measured the force that was provided by a wire of SMA for static snap-through by way of experiment. Pirrera et al. [12] presented analytical models by path-following techniques and provided an optimal design for morphing structures with multi-stable states. Moore et al. [13] investigated the thermal response and stability of the asymmetric laminated plate and shell structures for static snap-through through a varying temperature field. Brampton et al. [14] found that the bistable laminates were easily affected by the uncertainties of material properties, which were highly dependent on moisture, temperature, ply thickness and curing temperature. Potter and Weaver [15] developed techniques to generate a wide range of required stable structures through designing thermal stresses. Diaconu et al. [16] proposed the concept of morphing applications based on the multiple configurations and the snap-through, which was also proposed by Mattioni et al. [17]. Hyer [18] found that the thin cross-ply laminates have two stable cylindrical shapes that are perpendicular to each other. Pirrera et al. [19] proposed displacement fields of bistable composites that can be expressed by refined higher-order polynomial functions. SMA and piezoelectric macro fiber composite materials (MFC) are currently commercially available for static snap-through [20][21][22]. Schultz et al. [23] applied a series of quasi-static voltages through MFC for static snap-through.
In summary, the static characteristics exhibiting two stable configurations and the static snap-through of these bistable composites have been presented fully. However, as morphing components for adaptive aerospace structures, morphing applications are operated in aeroelastic environments. These bistable composite laminates will inevitably be exposed to high-level dynamic perturbations. Under dynamic perturbations, snapthrough between the two stable configurations is very likely to be induced. The local dynamics through theoretical modeling of bistable composite laminated plate and shell structures have been investigated by Arrieta et al. [24,25]. Arrieta et al. [26] introduced a resonant control strategy for cantilevered wing-shaped piezoelectric bistable plates under aerodynamic loads. Bilgen et al. [27] tested bistable wing-shaped composite laminated plate and shell structures and studied the aerodynamic characteristics. A small amount of literature have dealt with dynamic snap-through through theoretical modeling [28][29][30]. Zhang et al. [31] researched dynamic snap-through based on the nonlinear plate and shell theory. Jiang et al. [32] researched the vibration energy harvesting for an unsymmetric cross-ply square composite laminated plate with a piezoelectric patch on the surface.
The bistable composite laminated plate and shell structures can be regarded as morphing structures due to having more than one natural equilibrium position that can be settled without demanding an external power [33]. The bistable composite laminated plate and shell structures prove to be a good candidate for broadband-frequency energy harvesters owing to the dynamic snap-through that exhibits large strains and in turn generates more power compared with the oscillation around a single well [34]. The snap-through of bistable composite laminated plate and shell structures using smart materials such as piezoelectric transducer (PZT) and microfiber composite (MFC) was studied [35]. A nonlinear anti-vibration mount was designed based on the high static and low dynamic stiffness (HSLDS) concept [36].
As mentioned above, the studies on dynamic snap-through of bistable composites have been basically focused on experiments. Theoretical studies on the global dynamics including dynamic snap-through have not been carried out in depth yet. So far, theoretical studies on the local dynamics including 1:2 internal resonance, saturation and permeation have not been involved.
In this paper, the global and local dynamics of a bistable asymmetric composite laminated shell subjected to the base excitation are investigated. The shell is supported at the center and are free at the four edges. When subjected to large dynamic excitation, the center is assumed to be fixed supported [37]. When subjected to small dynamic excitation, the center is assumed to be elastically supported [38]. The three equilibrium configurations corresponding to two stable configurations and one unstable configuration are determined. The global dynamics including the vibration around the two stable equilibrium configurations respectively and the snap-through between the two stable equilibrium configurations, as well as the local dynamics including 1:2 internal resonance, saturation and permeation are investigated.
The novelty of this work is that the global and local dynamics fully exhibit dynamic snap-through and large-amplitude vibrations with two potential wells of the bistable asymmetric composite laminated shell, which prove to be a good candidate for energy harvesters. Due to the dynamic snap-through and large-amplitude vibrations, bistable energy harvesters will exhibit large strains and in turn generate more power compared with conventional energy harvesters.

Equation of Motion for Global Dynamics
In this paper, a bistable composite laminated shell with asymmetric stacking sequence [0 N -90 N ] T subjected to the base excitation is considered, as shown in Figure 1. If the number of layers is too large, the bistable characteristic will disappear. The bistable shell with (0/0/0/90/90/90) is a suitable choice, while (0/90) is too thin to bear large loads. In the experimental environment, the exciter acts the base excitation on the center of the shell through a support bar.
The shell is assumed to be supported at the center and kept free at four edges, as shown in Figure 1a. The rectangular coordinate system oxyz is built in the center of the shell. The edge lengths in the x and y directions are 2L x and 2L y , respectively. studies on the local dynamics including 1:2 internal resonance, saturation and permeation have not been involved. In this paper, the global and local dynamics of a bistable asymmetric composite laminated shell subjected to the base excitation are investigated. The shell is supported at the center and are free at the four edges. When subjected to large dynamic excitation, the center is assumed to be fixed supported [37]. When subjected to small dynamic excitation, the center is assumed to be elastically supported [38]. The three equilibrium configurations corresponding to two stable configurations and one unstable configuration are determined. The global dynamics including the vibration around the two stable equilibrium configurations respectively and the snap-through between the two stable equilibrium configurations, as well as the local dynamics including 1:2 internal resonance, saturation and permeation are investigated.
The novelty of this work is that the global and local dynamics fully exhibit dynamic snap-through and large-amplitude vibrations with two potential wells of the bistable asymmetric composite laminated shell, which prove to be a good candidate for energy harvesters. Due to the dynamic snap-through and large-amplitude vibrations, bistable energy harvesters will exhibit large strains and in turn generate more power compared with conventional energy harvesters.

Equation of Motion for Global Dynamics
In this paper, a bistable composite laminated shell with asymmetric stacking sequence [0N-90N]T subjected to the base excitation is considered, as shown in Figure 1. If the number of layers is too large, the bistable characteristic will disappear. The bistable shell with (0/0/0/90/90/90) is a suitable choice, while (0/90) is too thin to bear large loads. In the experimental environment, the exciter acts the base excitation on the center of the shell through a support bar.
The shell is assumed to be supported at the center and kept free at four edges, as shown in Figure 1a. The rectangular coordinate system oxyz is built in the center of the shell. The edge lengths in the x and y directions are 2Lx and 2Ly, respectively. The base excitation Y is applied to the supporting bar, through which the vibration exciter and shell are connected. The total thickness of the shell is 2H, the thickness of the single layer is h, n = 2N is the quantity of layers and asymmetric stacking sequence is [0N-90N]T, as shown in Figure 1b. The bistability is led by asymmetric residual thermal stress that can be expressed by the thermal expansion coefficient α and temperature difference ΔT between the manufacturing temperature and room temperature.
In global dynamics, when the dynamic excitation has large enough amplitudes, the snap-through with large amplitudes will occurs. The extra stiffness caused by the exciter can be ignored.
Global or local dynamics depend on whether the dynamic excitation induces the bistable shell to vibrate between two stable configurations or around a stable configuration. Both global and local dynamics have complex nonlinear vibrations, which are very likely to destroy the bistable shell.
When subjected to the base excitation with large amplitudes, the bistable shell vibrates between the two stable configurations, which is dominated by vibrations around the two stable equilibrium configurations respectively and dynamic snap-through between the two stable equilibrium configurations. In this section, all nonlinear vibrations and dynamic snap-through with two potential wells are defined as global dynamics.
In order to establish the bistable shell model, the following assumptions are introduced (1) The bistable plate model takes the zero plane before curing as the datum plane, while the bistable shell model takes the static surface that represents a stable equilibrium configuration after curing as the datum plane. (2) The bistable plate and shell models are converted to each other by the static displacement generated after curing. (3) The middle plane is assumed to be a neutral surface.
For global dynamics, the displacement field is expressed as: The base excitation Y is applied to the supporting bar, through which the vibration exciter and shell are connected. The total thickness of the shell is 2H, the thickness of the single layer is h, n = 2N is the quantity of layers and asymmetric stacking sequence is [0 N -90 N ] T , as shown in Figure 1b. The bistability is led by asymmetric residual thermal stress that can be expressed by the thermal expansion coefficient α and temperature difference ∆T between the manufacturing temperature and room temperature.
In global dynamics, when the dynamic excitation has large enough amplitudes, the snap-through with large amplitudes will occurs. The extra stiffness caused by the exciter can be ignored.
Global or local dynamics depend on whether the dynamic excitation induces the bistable shell to vibrate between two stable configurations or around a stable configuration. Both global and local dynamics have complex nonlinear vibrations, which are very likely to destroy the bistable shell.
When subjected to the base excitation with large amplitudes, the bistable shell vibrates between the two stable configurations, which is dominated by vibrations around the two stable equilibrium configurations respectively and dynamic snap-through between the two stable equilibrium configurations. In this section, all nonlinear vibrations and dynamic snap-through with two potential wells are defined as global dynamics.
In order to establish the bistable shell model, the following assumptions are introduced (1) The bistable plate model takes the zero plane before curing as the datum plane, while the bistable shell model takes the static surface that represents a stable equilibrium configuration after curing as the datum plane. (2) The bistable plate and shell models are converted to each other by the static displacement generated after curing. (3) The middle plane is assumed to be a neutral surface.
For global dynamics, the displacement field is expressed as: v(x, y, z, t) = v s (x, y) w(x, y, t) = w s (x, y) where u s , v s and w s are the initial displacements and u 0 , v 0 and w 0 are the displacements of any point in the neutral plane along the x, y and z directions. What needs to be emphasized here is that according to the precise description for the neutral surface in Reference [39], the neutral surface of the bistable asymmetric composite laminated shell is a surface with little warping, which can be thought of as a saddle. However, the precise neutral surface cannot be accurately determined but can only be assumed to be a plane according to Reference [37] at present.
Considering von Kármán's large deformation, we obtain the following straindisplacement relations: The stress-strain relationship of each of the first four layers taking the thermal effect which leads to the residual stress into account is given as follows Similarly, the stress-strain relationship of each of the back four layers given as follows where α xx , α yy and α xy are thermal expansion coefficients and ∆T is temperature difference between manufacturing temperature and room temperature. The relationship between the stiffness coefficients Q ij and E 11 , E 22 , G 12 , G 13 and G 23 can be expressed as The stress resultants are represented as follows where A ij are defined as extensional stiffnesses, D ij are defined as the bending stiffnesses and B ij are defined as the bending-extensional coupling stiffnesses, which are defined in terms of the lamina stiffnesses Q ij as The equivalent thermal force and moment resultants related to thermal stress are expressed by In the light of the Hamilton's principle, the equations of motion for global dynamics are derived by using Equations (1)-(9) as follows ∂N yy ∂y Substituting Equations (4)- (14) into Equations (15)- (17), Equations (15)-(17) are converted as follows As the boundary condition and static cylindrical shape, the static transverse displacements of the shell are symmetrical along the axes x and y respectively and the static in-plane and twist displacements are antisymmetrical along the axes x and y respectively. Therefore, according to Reference [19], the static displacements u s , v s and w s can be set as where u n,m−n , v n,m−n and w n,m−n are coefficients related to curvatures.
For global dynamics without the extra stiffness caused by the exciter, dynamic displacements for the central fixed support according to Equations (21)-(23) are given Symmetry 2021, 13, 1690 The in-plane vibrations and torsional vibrations are negligible relative to the transverse vibrations. Dropping in-plane and torsional vibration terms and combining Equations .. Y.
The coefficients in Equations (27) and (28) can be determined by material properties shown in Table 1 and step-by-step numerical calculations from Equations (1)-(28). 6.977 It should be pointed out that thermal expansion coefficients α 1 and α 2 , length L x , width L y and thickness h are the main factors of the static bifurcation, which is the supercritical pitchfork bifurcation. In order to obtain two stable equilibrium configurations with ideal initial curvatures, appropriate parameters α 1 , α 2 , L x , L y and h should be selected. The material properties collected in Table 1 are selected based on the above principles.
Dimensionless variables are introduced By using Equation (29), dimensionless equations can be derived .. ..

Three Equilibrium Configurations
Due to the residual thermal stress, the bistable composite laminated shell has three equilibrium configurations, which are two stable equilibrium configurations and one unstable equilibrium configuration. In order to determine the three equilibrium configurations, the time derivatives and dynamic load in Equations (27) and (28) are dropped. Making u 0 = v 0 = w 0 = 0, the static equations can be derived as follows: A 66 Substituting Equations (21)-(23) into Equations (32)-(34) and taking two degrees of freedom, a set of static nonlinear equations are derived: Changing the variable parameter ∆T, a series of static solutions for the equilibrium configurations can be derived, which form static bifurcation diagrams shown in Figure 2. In Figure 2, (a) donates the static bifurcation curve of w 1 which represents x-curvature, (b) donates the static bifurcation curve of w 2 which represents y-curvature.
The asymmetric composite laminated plate starts almost flatly at the elevated manufacturing temperature, point A in Figure 2. As the elevated manufacturing temperature increases, small curvatures develop. The curvatures are equal in magnitude but opposite in symbol, which indicates that the composite laminated plate warps, forming a shallow saddle shell. At point B, the curve of curvature-temperature relationship bifurcates into three paths BC, BD and BE, which represent curvatures in three cases. Along the path BC, the y-curvature increases while the x-curvature decreases. That is to say, the y-curvature dominates along the path BC, leading to one stable cylindrical equilibrium configuration. Along the path BE, the x-curvature increases while the y-curvature decreases. That is to say, the x-curvature dominates along the path BE, leading to another one stable cylindrical equilibrium configuration. Along the path BD, the x and y-curvatures increase slightly and remain equal in magnitude but opposite in symbol. Point D corresponds to the unstable saddle equilibrium configuration. It is concluded from Figure 2 that the number of equilibrium solutions varies from 1 to 3 with the change of parameter ∆T. The static bifurcation called supercritical pitchfork bifurcation occurs in the formation process of the bi-stability. The asymmetric composite laminated plate starts almost flatly at the elevated manufacturing temperature, point A in Figure 2. As the elevated manufacturing temperature increases, small curvatures develop. The curvatures are equal in magnitude but opposite in symbol, which indicates that the composite laminated plate warps, forming a shallow saddle shell. At point B, the curve of curvature-temperature relationship bifurcates into three paths BC, BD and BE, which represent curvatures in three cases. Along the path BC, the y-curvature increases while the x-curvature decreases. That is to say, the y-curvature dominates along the path BC, leading to one stable cylindrical equilibrium configuration. Along the path BE, the x-curvature increases while the y-curvature decreases. That is to say, the x-curvature dominates along the path BE, leading to another one stable cylindrical equilibrium configuration. Along the path BD, the x and y-curvatures increase slightly and remain equal in magnitude but opposite in symbol. Point D corresponds to the unstable saddle equilibrium configuration. It is concluded from Figure 2 that the number of

Equation of Motion for Local Dynamics
When subjected to the base excitation with small amplitudes, the bistable shell vibrates around just one stable configuration, which are defined as local dynamics. All vibrations confined to a single stable configuration behave as 1:2 internal resonance, saturation and penetration.
For local dynamics around one of the two stable equilibrium configurations, the above relationships will have to be redefined.
The nonlinear strain-displacement relations are rewritten as follows: where R 1 and R 2 are radii of curvatures of one of the two stable equilibrium configurations corresponding to the initial curvatures ∂ 2 w s ∂x 2 and ∂ 2 w s ∂y 2 determined above.
Using Equations (7), (8), (37) and (38), the strain energy can be rewritten as follows: The kinetic energy can be rewritten as follows: By using Chebyshev polynomials, u 0 , v 0 and w 0 are expanded as follows: where R u (x,y), R v (x,y) and R w (x,y) are boundary functions, U(x,y), V(x,y) and W(x,y) are spatial functions and r(t) is a temporal function. The boundary functions can be expressed as follows: where α = u, v, w. p, q, r, s depends on the constraint boundaries of the bistable shell and are equal to either 0 or 1. Different values of the boundary functions are shown in Table 2. Table 2. Different values of the boundary functions.
As the four edges of the shell are free, R α (x,y) = 0. The shape functions are expressed as: where T m and T n are the m-th and n-th order Chebyshev polynomial of the first kind, respectively. As the vibration exciter itself is composed of a series of spring components, when the shell is subjected to the base excitation with small amplitudes by the vibration exciter, the local dynamics confined to one stable configuration occur and the vibration behavior of the system is similar to that of a spring-mass system. That is to say, the local dynamics around one stable configuration need to take additional spring stiffness due to the vibration exciter into account [38,40]. Therefore, the additional stiffness is applied to the supporting bar, through which the shell and vibration exciter are connected. In this case, it is assumed that the center of the shell is elastically supported and the four edges are free.
The additional elastic potential energy due to the vibration exciter is given by: where k b is the additional stiffness caused by the supporting bar. The total strain energy is thus: The Rayleigh-Ritz method is used, and the following equation is applied: where K and M represent stiffness matrix and mass matrix respectively, p is n-dimensional displacement vector and n = 3MN. The eigenvalues of matrix (52) are solved to derive the natural frequencies and the eigenvalues are brought back to matrix (52) to obtain the corresponding eigenvectors, so as to calculate the shape functions: Then the corresponding modal functions can be determined: According to Hamilton's principle, the equations for the local dynamics can be obtained: ∂N xx ∂x where: In order to analyze local dynamics with the extra stiffness caused by the exciter around one of the two stable equilibrium configurations, the initial curvatures ∂ 2 w s ∂x 2 and ∂ 2 w s ∂y 2 of the second stable equilibrium configuration according to the previous section are transformed into the radii of curvatures R 1 and R 2 of the cylindrical shell. The Rayleigh-Ritz method is used to determine the modal shapes for the boundary conditions of central elastic support, as shown in Figure 3.
In order to analyze local dynamics with the extra stiffness caused by the exciter around one of the two stable equilibrium configurations, the initial curvatures ∂ 2 w s ∂x 2 and ∂ 2 w s ∂y 2 of the second stable equilibrium configuration according to the previous section are transformed into the radii of curvatures R 1 and R 2 of the cylindrical shell. The Rayleigh-Ritz method is used to determine the modal shapes for the boundary conditions of central elastic support, as shown in Figure 3.
Substituting Equations (56)-(58) into Equations (59)-(61), selecting the first two modal functions and using the Galerkin approach, two degree of freedom ordinary differential equations are determined as: ..

Global Dynamics
To study the global dynamics, the fifth-order Runge-Kutta algorithm is adopted to solve Equations (30) and (31), which demonstrates the bifurcation diagram, the phase portrait, the time-history graph and the Poincaré map. For convenience in this study, the overbars in Equations (30) and (31)  When the Poincaré map shows a closed curve, quasi-periodic vibration is determined. When the Poincaré map shows a large cluster of points, chaotic vibration is determined. w 1 represents the vibration for curvature in the x direction while w 2 represents the vibration for curvature in the y direction. Through the comparative study of w 1 and w 2 , the vibrations of the bistable shell can be determined. When f = 0.2, w 1 and w 2 remain almost zero around the equilibrium position (0, 0), that is to say, the bistable shell vibrates slightly around the first stable equilibrium configuration, which is the periodic vibration according to Poincaré map shown in Figure 4. When f = 0.35, w 1 increases rapidly while w 2 remain almost zero around the equilibrium position (0, 0),that is to say, the bistable shell vibrates violently around the first stable equilibrium configuration, which is the chaotic vibration according to Poincaré map shown in Figure 5. When f = 0.425, in a phase after the start, w 1 increases rapidly while w 2 remain almost zero around the equilibrium position (0, 0), at a certain moment, w 1 increases from 0 to 0.2 and remains almost constant while w 2 increases from 0 to 0.2 and vibrates violently around the equilibrium position (0.2, 0.2), that is to say, dynamic snap-through occurs, which is the chaotic vibration according to the Poincaré map shown in Figure 6. When f = 0.43, w 1 and w 2 vibrate violently around the equilibrium position (0.2, 0.2), that is to say, the bistable shell vibrates violently around the second stable equilibrium configuration, which is the chaotic vibration according to the Poincaré map shown in Figure 7. When f = 0.5, w 1 and w 2 change repeatedly between 0 and 0.2 simultaneously, namely, the constant dynamic snap-through occurs between the two stable equilibrium configurations, which is the chaotic vibration according to the Poincaré map shown in Figure 8. When f = 0.8, w 1 vibrates slightly while w 2 remain almost zero around the equilibrium position (0, 0), that is to say, the bistable shell vibrates slightly around the first stable equilibrium configuration, which is the quasi-periodic vibration according to the Poincaré map shown in Figure 9. When f = 0.9, w 1 and w 2 remain almost 0.2 around the equilibrium position (0.2, 0.2), that is to say, the bistable shell vibrates slightly around the second stable equilibrium configuration, which is the periodic vibration according to the Poincaré map shown in Figure 10.     Figure 6. The snap-through and chaotic motion between the two stable equilibrium configurations when f = 0.425, (a) donates the time-history on the plane (t, w 1 ), (b) donates the phase portrait on the plane w 1 ,    Figure 9. The quasi-periodic motion around the first stable equilibrium configuration when f = 0.8, (a) donates the timehistory on the plane (t, w 1 ), (b) donates the phase portrait on the plane w 1 , In order to understand the influence of excitation amplitude f on global dynamics more comprehensively, make f locate in a range of 0~1.2 and bifurcation diagrams can be obtained shown in Figure 11. In order to understand the influence of excitation amplitude f on global dynamics more comprehensively, make f locate in a range of 0~1.2 and bifurcation diagrams can be obtained shown in Figure 11. In Figure 11, when f is located in the interval 0~0.25, w1 and w2 vibrate slightly around the equilibrium position (0, 0), when f is located in the interval 0.25~0.43, w1 and w2 vibrate violently around the equilibrium position (0, 0), when f is located in the interval 0.43~0.72, w1 and w2 vibrate violently between the equilibrium positions (0, 0)and (0.2, 0.2) and when f is located in the interval 0.72~1.2, w1 and w2 vibrate slightly around the equilibrium position (0, 0) or (0.2, 0.2).
Combined with the vibration and Poincaré map shown in Figures 4-10 respectively, we can find from Figure 11 that the vibration of the bistable shell changes from the periodic vibration around the first stable equilibrium configuration  the quasi-periodic vibration around the first stable equilibrium configuration  the chaotic vibration around the first stable equilibrium configuration  the snap-through and chaotic vibration between the two stable equilibrium configurations the constant snap-through and chaotic vibration between the two stable equilibrium configurations  the quasi-periodic vibration around the second stable equilibrium configuration  the periodic vibration around the second stable equilibrium configuration when the excitation amplitude f changes from In Figure 11, when f is located in the interval 0~0.25, w 1 and w 2 vibrate slightly around the equilibrium position (0, 0), when f is located in the interval 0.25~0.43, w 1 and w 2 vibrate violently around the equilibrium position (0, 0), when f is located in the interval 0.43~0.72, w 1 and w 2 vibrate violently between the equilibrium positions (0, 0)and (0.2, 0.2) and when f is located in the interval 0.72~1.2, w 1 and w 2 vibrate slightly around the equilibrium position (0, 0) or (0.2, 0.2).
Combined with the vibration and Poincaré map shown in Figures 4-10 respectively, we can find from Figure 11 that the vibration of the bistable shell changes from the periodic vibration around the first stable equilibrium configuration → the quasi-periodic vibration around the first stable equilibrium configuration → the chaotic vibration around the first stable equilibrium configuration → the snap-through and chaotic vibration between the two stable equilibrium configurations→ the constant snap-through and chaotic vibration between the two stable equilibrium configurations → the quasi-periodic vibration around the second stable equilibrium configuration → the periodic vibration around the second stable equilibrium configuration when the excitation amplitude f changes from 0 to 1.2.
From another point of view, it is seen from Figure 11 that the vibration of the bistable asymmetric composite laminated shell changes from the vibration with small amplitude around the first stable equilibrium configuration → the oscillation with large amplitude around the first stable equilibrium configuration → the oscillation with large amplitude between the two stable equilibrium configurations → the oscillation with large amplitude around the second stable equilibrium configuration → the vibration with small amplitude around the second stable equilibrium configuration. Figures 8 and 11 exhibit the global dynamics. The global dynamics consist of the vibrations around the two stable equilibrium configurations respectively, which can be taken as the local dynamics and dynamic snap-through between the two stable equilibrium configurations. In other words, Figures 8 and 11 exhibit dynamic snap-through and nonlinear vibrations with two potential wells.

Local Dynamics
For convenience, the overbars are dropped in Equations (63) and (64). Considering the case of primary parametric and 1:2 internal resonance, the resonant relations are given by: where σ 1 and σ 2 are two detuning parameters. Small parameter variable ε is introduced: Using Equations (68) and (69) and the method of multiple scales, Equations (63) and (64) are averaged as follows: where a 1 and a 2 represent the amplitude of w 1 and w 2 respectively and ϕ 1 and ϕ 2 and φ 2 represent the phase angle of w 1 and w 2 respectively. Let the derivatives at the left end of Equations (70)-(73) be zero as follows: The solutions of Equations (74)-(77) are divided into two sets by whether a 1 is zero or not.
When a 1 = 0, the first set of solutions is: When a 1 = 0, the second set of solutions satisfies the following relation: Solving Equation (79) and considering Equation (78), a series of solutions can be determined shown in Figures 12-17.
The solutions of Equations (74)-(77) are divided into two sets by whether 1 a is zero or not. When 0 1  a , the first set of solutions is: Solving Equation (79) and considering Equation (78), a series of solutions can be determined shown in Figures 12-17.   Figure 13. When σ 1 = σ 2 = 0, the force-amplitude characteristic curve of the system. Figure 12 shows the force-amplitude curve for σ 2 = 0. In Figure 12 GC and dotted line KF represent the amplitude a 2 of the second mode. When the base excitation amplitude f 2 increases gradually from zero, a 1 changes along AK and a 2 changes along AB. When f 2 = 5.8, a 1 transfers from AK to DE by snap-through and a 2 transfers from AB to BC. When the base excitation amplitude f 2 decreases gradually from 8, a 1 changes along EF and a 2 changes along CG. When f 2 = 2, a 1 transfers from EF to JA by snap-through and a 2 transfers from CG to HA by snap-through. When a 2 goes along CG, no matter how f 2 changes, a 2 remains constant, that is to say, the response of the second mode enters saturation state. This is because the energy applied to the second mode is transferred to the first mode, which means that permeation takes place. Saturation and permeation are the peculiar phenomena of forced vibration of nonlinear multi-degree of freedom system related to 1:2 internal resonance. Figure 13. When σ1=σ2=0, the force-amplitude characteristic curve of the system. Figure 12 shows the force-amplitude curve for σ2 = 0. In Figure 12 a remains constant, that is to say, the response of the second mode enters saturation state. This is because the energy applied to the second mode is transferred to the first mode, which means that permeation takes place. Saturation and permeation are the peculiar phenomena of forced vibration of nonlinear multi-degree of freedom system related to 1:2 internal resonance.   Figure 13 shows the force-amplitude curve for σ1 = σ2 = 0. Similar to Figure 12, with the change of base excitation amplitude f2, saturation and permeation occur.   Figure 13 shows the force-amplitude curve for σ1 = σ2 = 0. Similar to Figure 12, with the change of base excitation amplitude f2, saturation and permeation occur.   Figure 14 is the frequency-amplitude curve of the first mode with respect to σ1. It can be seen from Figure 14 that when σ1 changes from negative to positive, the system shows the softening and hardening nonlinearity successively. Figure 15 is the frequency-amplitude curve of the second mode with respect to σ1. Different from Figure 14, with the change of σ1, the system shows only linear characteristics. Figure 16 is the frequency-amplitude curve of the first mode with respect to σ2. It can be seen from Figure 16 that with the change of σ2, the system shows the hardening nonlinearity. Figure 17 is the frequency-amplitude curve of the second mode with respect to σ2. It can be seen from Figure 17 that when σ2 changes from negative to zero, the system shows the linear characteristics with negative slope, while when σ2 changes from zero to positive, the system shows the linear characteristics with positive slope.
It can be found from Figures 12-17 that when only the base excitation amplitude is changed, the system may have saturation and penetration, and when only the detuning parameter σ1 or σ2 is changed, the first mode of the system shows nonlinear characteristics (softening and hardening nonlinearity) while the second mode shows linear characteristics.  Figure 13 shows the force-amplitude curve for σ 1 = σ 2 = 0. Similar to Figure 12, with the change of base excitation amplitude f 2 , saturation and permeation occur. Figure 14 is the frequency-amplitude curve of the first mode with respect to σ 1 . It can be seen from Figure 14 that when σ 1 changes from negative to positive, the system shows the softening and hardening nonlinearity successively. Figure 15 is the frequency-amplitude curve of the second mode with respect to σ 1 . Different from Figure 14, with the change of σ 1 , the system shows only linear characteristics. Figure 16 is the frequency-amplitude curve of the first mode with respect to σ 2 . It can be seen from Figure 16 that with the change of σ 2 , the system shows the hardening nonlinearity. Figure 17 is the frequency-amplitude curve of the second mode with respect to σ 2 . It can be seen from Figure 17 that when σ 2 changes from negative to zero, the system shows the linear characteristics with negative slope, while when σ 2 changes from zero to positive, the system shows the linear characteristics with positive slope.

Conclusions
It can be found from Figures 12-17 that when only the base excitation amplitude is changed, the system may have saturation and penetration, and when only the detuning parameter σ 1 or σ 2 is changed, the first mode of the system shows nonlinear characteristics (softening and hardening nonlinearity) while the second mode shows linear characteristics.

Conclusions
In this paper, the global and local dynamics of a bistable asymmetric composite laminated shell subjected to the base excitation are investigated. The shell is supported at the center and are free at the four edges. When subjected to the base excitation with small amplitude, the shell vibrates around just one stable configuration, which is dominated by the local dynamics while when subjected to the base excitation with large amplitude, the shell vibrates between the two stable configurations, which is dominated by the global dynamics. The vibrations around the two stable equilibrium configurations and the dynamic snap-through between the two stable equilibrium configurations constitute the global dynamics. The 1:2 internal resonance, saturation and penetration appear in the local dynamics, which is confined to a single stable configuration. We can draw the following main conclusions: (1) Choosing difference temperature ∆T as the controlling parameter, the super-critical pitchfork bifurcation can be obtained. When ∆T is set to a specific value, three equilibrium configurations corresponding to two stable equilibrium configurations and one unstable equilibrium configuration are determined. (2) The global dynamics behave as the snap-through between the two stable equilibrium configurations and the vibrations around the two stable equilibrium configurations respectively. (3) The dynamic snap-through of the bistable system often occurs in chaos. In other words, the bistable system is often accompanied by the chaotic vibration in the process of the dynamic snap-through. (4) In the global dynamics, the vibrations behave as the periodic vibration, the quasiperiodic vibration and the chaotic vibration. (5) In the local dynamics, saturation and permeation occur in the process of the 1:2 internal resonance.
Due to the dynamic snap-through and large-amplitude vibrations, the bistable asymmetric composite laminated shell prove to be a good candidate for energy harvesters. Bistable energy harvesters will exhibit large strains and in turn generate more power compared with conventional energy harvesters.
In the near future, we will pay attention to another application of the asymmetric laminates via the concept of 4D printing of composites, which is advanced and significant [41].  Data Availability Statement: The study did not report any data.