Random Response and Crossing Rate of Fractional Order Nonlinear System with Impact

(e random response and mean crossing rate of the fractional order nonlinear system with impact are investigated through the equivalent nonlinearization technique. (e random additive excitation is Gaussian white noise, while the impact is described by a phenomenological model, which is developed from the actual impact process experiments. Based on the equivalent nonlinearization technique, one class of random nonlinear system with exact probability density function (PDF) solution of response is selected. (e criterion of the appropriate equivalent nonlinear system is the similarity with the original system on the damping, stiffness, and inertia. (e more similar, the higher the precision. (e optimal unknown parameters of the equivalent random nonlinear system in the damping and stiffness terms are determined by the rule of smallest mean-square difference. In the view of equivalent nonlinearization technique, the response of the original system is the same as that of the equivalent system with the optimal unknown parameters in analytical solution manner. (en, the mean crossing rate is derived from stationary PDF. (e consistence between the results from proposed technique and Monte Carlo simulation reveals the accuracy of the proposed analytical procedure.


Introduction
e impact can be found frequently in the structural and mechanical engineering, where there exists clearance between two bodies [1,2]. Due to the discontinuity, the dynamical behavior of the vibration system comprising impact is different from the usual smooth system and becomes extremely complex [3][4][5].
e impact process is usually modeled as a velocity jump at the time of impact occurring, which is expressed by _ x + � −r _ x − with 0 ≤ r ≤ 1. e rebound velocity _ x + equals to r by impact velocity _ x − and has an opposite direction of movement. e mapping of the velocity before and after impact is not continuous both in the size and orientation. Many research studies are devoted to reveal the dynamical behaviors of vibro-impact system [6,7]. To deal with the velocity jump at collision moment, several effective transformations of state variables are always helpful [7][8][9]. Based on these transformations, the vibro-impact system with viscoelastic damping and nonzero offset barrier is studied by the stochastic averaging [10]. Multivalue response of a nonlinear vibro-impact system under narrowband excitation is investigated [11]. e triple-valued response under a certain case is observed, which may have two or four steady-state solutions. Other research studies with respect to the vibro-impact system can be found in [12][13][14][15].
Based on the impact experiments of elastic-plastic structures, a phenomenological impact model is developed. Due to time duration of the elastic-plastic deformation process, the impact model of the velocity jump at collision moment is not appropriate in this case [16,17]. By using this phenomenological impact model, the stochastic averaging method has been adopted to obtain the stationary probability density function (PDF) of the vibro-impact system subjected to Gaussian white noises [18]. Due to the limitation on slight nonlinearity and weak excitations density, the equivalent nonlinearization technique has a remarkable advantage, i.e., it can be applicable to systems which are strongly nonlinearity.
is technique has been developed and used to complex nonlinear system in Hamiltonian framework [19][20][21][22][23]. Considering the significant advantage, the equivalent nonlinearization technique has been successfully adopted to evaluate the reliability and the reliability-based design of inelastic structure, and a simple equivalent nonlinear system that retains the dynamic characteristics of the first two modes and the global yielding behavior has been developed to replace the original system [24]. It can be expected that the equivalent nonlinearization technique is applicable to deal with the random systemincorporated inelastic impact described by the phenomenological impact model. Besides, the mean crossing rate, which always relates to predicting the extreme response statistics and the system reliability, is another important quantity which should be considered. e evaluation of the mean crossing rate has been of great interest among researchers. Naess and Karlsen [25] calculated the level crossing rate of second-order stochastic Volterra systems. Naess et al. [26] applied Monte Carlo simulation to predict the extreme response statistic of floating offshore structures subjected to random seas. Beck and Melchers [27] investigated time variant reliability of uncertain structure by using the ensemble crossing rate. As illustrated in [28], the mean crossing rate for a stationary stochastic process can be determined by the joint probability density of the stochastic process and its derivative process. It means that the equivalent nonlinearization technique is applicable to derive not only the system response but also the mean crossing rate. e random response and mean crossing rate of the nonlinear system with fractional order stiffness and impact are studied by using the equivalent nonlinearization technique. e paper is organized as follows. In Section 2, the fractional order nonlinear system with impact is established and the impact model is described. In Section 3, an equivalent nonlinearization technique is adopted and the approximate solution of system response is derived. In Section 4, the mean crossing rate is introduced and the analytical formula is expressed by the response PDF of system. In Section 5, examples are given to shown the proposed analytical technique and different system parameters are discussed. e conclusions are drawn in Section 6.

Fractional Order Nonlinear
System with Impact e present paper is concerned with a vibro-impact system with right-side barrier under additive excitations described by Gaussian white noise, as shown in Figure 1. e motion equation governing the mechanical behavior of the system is where X is the system displacement and overhead dot indicates differentiation with respect to time t, ζ is the viscous damping coefficient, and W(t) is Gaussian white noise in sense of Stratonovitch [29] with zero mean and correlation function R(τ) � 2 Dδ(τ). e system stiffness here is fractional order nonlinear. e physical value α is larger than 1 and not an integer for many materials due to the nonlinear stress-strain relationship [30].
is nonlinear stiffness has been studied by Cvetivanin and Zukuvic [31,32]. In Figure 1, we consider the elastic force obeys the fractional order law. k 1 and k 3 in system (1) are the linear and nonlinear coefficients, respectively. Specially, parameter k 1 can be positive for a beam, while negative for a beam with sufficient axial load [33].
Impact force g(x, _ x), which depends on both the velocity and displacement, is governed by the phenomenological impact model when collision occurs [17]. is impact model is efficient to describe the collision for the elastic-plastic materials. e distance of clearance between the mass and barrier is δ r . e impact force g(x, _ x) will be given for two different cases (the dissipative collision and the conservative collision), respectively. e criterion to distinguish the dissipative and conservative collision is the relation of the maximal right-side displacement a 1 of the impact mass and the elastic limit x 0 . e dissipative collision for a 1 > x 0 , while conservative collision for a 1 < x 0

For Dissipative Collision.
e impact force g(x, _ x) can be explicitly derived for the loading phase g + and unloading phase g − as follows: for _ x > 0(loading phase), where s p , p, and q are material parameters that are determined through experiments, Δ r is the plastic deformation induced by the dissipative impact, k 2 and s 2 represent the stiffness coefficients of the loading phase and unloading phase, respectively, and a 2 represents the maximal left-side displacement of the impact mass. e relation of impact force versus relative displacement for dissipative collision is depicted in Figure 2.

For Conservative Collision.
e impact force g(x, _ x) becomes simple and only depends on the system displacement. e impact forces g(x, _ x) can be written as

Equivalent Nonlinearization Technique
As mentioned above, the equivalent nonlinearization technique has some advantages compared with the stochastic averaging technique, especially for the effectiveness to the strong nonlinearity and its concision. To utilize the equivalent nonlinearization technique, the first and critical step is the selection of the equivalent nonlinear system family. e original system solution is approximately expressed by that of the equivalent system family. e more similar, the higher the accuracy. ere are no rigorous rules for selecting the equivalent system family. General speaking, an efficient rule is to make inertia, stiffness, and damping of the original and equivalent system close. e above rules, which confine the selection of the equivalent nonlinear system, guarantee the accuracy of the results from the equivalent nonlinearization technique. e phenomenological impact model is depicted for two different cases. In the conservative collision case, the loading path coincides with the unloading path, while in the dissipative collision case, the loading path is deviated from the unloading path beyond the elastic limit and the nonzero area encircled by the two paths indicates the dissipative mechanism of the inelastic impact. In other words, in case of the dissipative collision case, the impact is not only to store the potential energy due to its elasticity but also to dissipate energy as a damping. So, in the selection of the equivalent nonlinear system family, the conservative and dissipative components of inelastic impact should be considered.
It is reasonable to reflect the conservative component of inelastic impact based on the loading path: In the case of the conservative collision, equation (5) is the exact expression of the impact process, but it is not suitable for the dissipation collision. In order to reflect the inconsistency of loading and unloading paths, one intuitive and convenient selection of equivalent stiffness to reflect the conservative component of inelastic impact is (1 + S e )g(x), in which S e is a correction coefficient.
Obviously, the linear damping is the simplest reflection of the dissipative component of the inelastic impact, but is not appropriate since the dissipative component will not play a role in conservative collision and depend on the system state in dissipative collision. To avoid the irrationality of linear damping, quasi-linear damping with damping coefficient depending on the system states is a good alternative and can be selected as e selection of ζ e (H) _ X has two remarkable advantages: (i) due to the similar properties between the impact process and hysteretic behavior [34], ζ e (H) _ X can reflect the dissipative component well and (ii) the solvability of the equivalent nonlinear system including ζ e (H) _ X is guaranteed. Based on the above analysis, the original system is replaced by the nonlinear system family, which has the stationary PDF with normalization constant N as In equivalent nonlinear system (6), the constant S e and the function ζ e (H) are both unknown and should be determined through some criterions. Unfortunately, to derive the optimal function ζ e (H) is almost impossible. A practical way is to expand the function ζ e (H) in a power series: where H * denotes the system energy critical value of elastic impact and inelastic impact, i.e., H * � (1/2)k 1 x 2 0 + (1/α + 1)k 3 x 2 0 |x 0 | α−1 + (k 2 /1 + p)(x 0 − δ r ) 1+p , and b i are undetermined constant parameters. Now, the equivalent system of the original system comes down to determine unknown parameters S e and b i , i � 1, 2, . . ..
Because of the infinite number of b i , equation (9) is unsolvable and should be truncated. If only b 1 is kept and b i (i ≥ 2) are ignored, parameters S e and b i can be solved from equation (9) and can be written as where h(g) represents Heaviside step function. In equations (9) and (10), the joint PDF depends on the unknown parameters S e and b i , so the undetermined parameters S e and b i should be obtained through iterative technique.

Stochastic Response and Mean Crossing Rate Evaluation
As discussed in the above section, by substituting the parameters S e and b i into the PDF in equation (7), the joint PDF of the original system can be approximated to that of the equivalent system. en, the PDF of original system states X and _ X, the marginal PDF, can be written directly. Except the stochastic responses analysis, another quantity of particular importance is the mean crossing rate, which associates with the extreme response prediction, system safety, and reliability. e mean crossing rate, denoted as ] a c (t), can be described as the mean number of a stochastic process Y(t) crossing a critical value a c per unit time. e mean crossing rate ] a c (t) which usually depends on the time except Y(t) is a stationary stochastic process. Particularly, in the special case of Y(t) which is a meansquare differentiable stationary stochastic process with continuous time and state, the mean crossing rate of Y(t) can be defined as [28,35] where υ a c is independent of the time and a c represents the critical excursion value of system displacement, p(a c , _ y) � p(y, _ y)| y�a c , in which p(y, _ y) is the stationary joint probability density of stochastic variances Y(t) and _ Y(t). Similar to the mean crossing rate, the mean upcrossing and down-crossing rates, which represent the mean number of a stochastic process Y(t) up-crossing and down-crossing a critical value a c of system displacement per unit time, respectively, can be defined as Since p(y, _ y) is an even function of stochastic variance _ Y, the mean up-crossing and down-crossing rate satisfies Considering the relation in equation (13), only the mean up-crossing rate is discussed in this paper.

Numerical Results and Discussion
Some numerical calculations are carried out to validate the proposed analytical technique. System parameters are selected as k 1 � 1, k 2 � 5, k 3 � 1, α � 1.5, δ r � 0.1, x 0 � 0.125, 2 D � 0.04, ζ � 0.01, s p � 0.2, p � 1.39, and q � 1.8 [17], unless otherwise mentioned. Figures 3(a) and 3(b) relate the displacement PDF p(x) and the velocity PDF p( _ x) under different fractional orders α. It can be clearly seen that the analytical results (solid lines) agree with the Monte Carlo simulation (MCS) results of the original system (1) (circles). As the fractional order α increases from α � 1.5 to α � 3.5 and α � 5.5, the displacement PDF is to be more flat and the velocity PDF is slightly changed. It means that the displacement is sensitive to the fractional order α, while the velocity is not. Figures 4(a) and 4(b) plot the displacement and velocity PDFs of the nonlinear system under different Gaussian white noise intensities 2 D. e bigger intensity 2 D means large displacement and velocity response, which is consistent with our intuition. e influences of the nonlinear stiffness coefficients k 3 are shown in Figures 5(a) and 5(b). e high nonlinear stiffness k 3 restricts the system displacement response. However, such restriction has little effects on the velocity response, where the curves of the velocity PDF almost coincide. en, the bistable system (k 1 � −1) is studied. e displacement and velocity PDFs of the nonlinear system under different fractional order α is given in Figures 6(a) and 6(b). e displacement PDF has two peaks, while velocity PDF only has one peak. e system with small fractional order α (i.e., α � 1.5) has a flat PDF.  Figures 8(a) and 8(b). Strong nonlinear stiffness coefficient k 3 reduces the displacement response.
Besides the system responses, the mean up-crossing rate plays an important role in the system reliability. Figure 9 gives relation of the mean up-crossing rate υ + a c and the critical value of excursion a c and fractional order α. e results from the proposed technique agrees well with those from the Monte Carlo simulation(MCS). To give a clear view, Figure 10 plots the curve of the mean up-crossing rate υ + a c with critical value of excursion a c under α � 1.5. e mean up-crossing rage monotonously decrease with the excursion a c . e mean up-crossing rate υ + a c of the bistable system is plotted in Figures 11 and 12. e mean up-crossing rate υ + a c increases first and then decreases with the increased critical value of excursion a c . e comparison between the proposed technique and the Monte Carlo simulation (MCS) shows that the accuracy is not high, but acceptable. ese can be clearly observed in Figure 12, where the fractional order α equals to 5.5.

Conclusions
e random response and mean crossing rate of the nonlinear system with fractional order stiffness and impact has been investigated through equivalent nonlinearization technique. e impact is described by an empirical model developed from impact experiment of elastic and plastic materials. By using the equivalent nonlinearization technique, the original vibro-impact system is equivalently replaced by a nonlinear system. rough minimizing the mean-square value of the system difference, one optimal system is chosen from the equivalent nonlinear system family.
en, the joint PDF of system displacement and velocity are analytically obtained through the equivalent nonlinear system. e agreement between the analytical results and MCS validates effectiveness of the proposed technique. e proposed technique is also adopted to derive the mean crossing rate of the vibro-impact system, and the acceptable precision of the results illustrates the effectiveness of the proposed technique to evaluate the mean crossing rate. It is necessary to emphasize that, in comparison with the stochastic averaging technique, the present technique can extend the applicable range of system parameters to which the stochastic averaging technique is invalid.

Data Availability
e data used to support the findings of this study are available from the corresponding author upon request.

Conflicts of Interest
e authors declare that they have no conflicts of interest.