Research Article | Open Access
T. S. Amer, M. A. Bek, I. S. Hamada, "On the Motion of Harmonically Excited Spring Pendulum in Elliptic Path Near Resonances", Advances in Mathematical Physics, vol. 2016, Article ID 8734360, 15 pages, 2016. https://doi.org/10.1155/2016/8734360
On the Motion of Harmonically Excited Spring Pendulum in Elliptic Path Near Resonances
The response of a nonlinear multidegrees of freedom (M-DOF) for a nature dynamical system represented by a spring pendulum which moves in an elliptic path is investigated. Lagrange’s equations are used in order to derive the governing equations of motion. One of the important perturbation techniques MS (multiple scales) is utilized to achieve the approximate analytical solutions of these equations and to identify the resonances of the system. Besides, the amplitude and the phase variables are renowned to study the steady-state solutions and to recognize their stability conditions. The time history for the attained solutions and the projections of the phase plane are presented to interpret the behavior of the dynamical system. The mentioned model is considered one of the important scientific applications like in instrumentation, addressing the oscillations occurring in sawing buildings and the most of various applications of pendulum dampers.
Dynamical system is considered a collection of particles in motion with finite numbers of DOF and can be determined through some processes during a period of time. Chaos theory studies the behavior of dynamical systems that are oversensitive to initial conditions and is considered one of the most important subjects in applied mathematics, physics, and engineering fields. It has several applications ranging from weather forecasts, technology, and physical and life sciences. The kinematical nonlinear systems are of great interest for many outstanding researchers during the last three decades. In [1, 2], the dynamical behavior of such systems is investigated as good models in applied mechanics. Tousi and Bajaj in  studied period doubling bifurcations and modulated motion in 2-DOF of a nonlinear system. Moreover, Maewal in  examined chaos of the forced response of an excited elastic beam through the numerical solutions of the governing system of his suggested model. In , the author used the MS method to construct the expansion of the parametric excitation of two internally resonant oscillators up to the first order. The author determined the solutions of the steady-state case and checked the corresponding stability. In , the authors transformed the governing system of the excited buckled beam to approximate one and examined the stability of the equilibrium solutions to obtain Hopf bifurcations and a sequence of period doubling one, leading to chaotic motion. The response of an excited weakly vibrating system with 2-DOF close to resonance is investigated in . The response of the considered system is checked using the averaging method and the numerical integration. In , Lee and Park investigated the excitation of spring pendulum using the MS technique and showed that the obtained approximate autonomous system has bifurcations. The effect of the higher-order expansions of this problem with internal resonance was examined in . In , the authors investigated the fourth-order approximate solution for the governing system and the stability of such system of a similar problem when the stiffness of the spring becomes nonlinear. In , the authors investigated the same problem besides any equilibrium state using MS method and they also examined the general manner of the system through utilizing the basin boundaries of attractors. They observed that these boundaries may be fractal and the damping coefficients have a great effect during the chaotic motion. The problem of the nonlinear behavior of a 2-DOF oscillating system coupled with nonlinear damper and nonlinear spring is studied in . The authors showed that, according to certain values for damping and stiffness coefficients, the oscillating amplitude for the examined model is reduced to give better design for the nonlinear absorber. In , Amer and Bek studied the response of the excited elastic pendulum in which the motion of the suspended point is considered in a circular path. The governing nonautonomous system is transformed to autonomous ones up to third order using the MS method. They found that the resulted system has bifurcations leading to chaos. Another pendulum model is examined in  when the suspended point moves in a prescribed path. The governing equations of motion have been obtained and solved analytically using the multiple scales method. The authors concentrated on predicting the resonance conditions and they studied these cases. This problem was generalized in  to study the vibrations of a rigid body as a pendulum model. Many interested examples for the motion of nonlinear systems can be found in [16–20] and the references herein. However, in  the authors investigated the motion of a spring pendulum which is moving in circular path. In [18, 19] they generalized their previous work by considering the effect of a damper to the motion.
In the current work, we extend the previous work in  for the nonlinear behavior of kinematically excited spring pendulum in which its suspension point moves in an elliptic path. Our main aim is to reveal the resonances conditions and to outline on a case of simultaneously resonances. Among the perturbation methods, the MS method is used to obtain the modulation equations determining all possible steady-state solutions. The graphical representations for suggested physical parameters of the obtained steady-state solutions are presented. Some examples are given as limit cases from the motion of considered model in order to simulate the dynamical behavior of this model.
2. Description of the Problem
Let us consider a dynamical system which consists of a mass , suspended from one end of a massless linear spring having stiffness and statically stretched length . The other end is attached to the point that moves in an elliptical path in which and represent the lengths of the minor and the major axes of the ellipse, respectively; see Figure 1. Take into account that the corresponding point of (located on the auxiliary circle ) is the point (located on the ellipse) and this point moves with angular velocity . Let us denote the horizontal axis by and the downward one by , in which both of them have the same origin of the ellipse. Let be a moment acts about the point in a anticlockwise direction, indicates the acting force on the mass in the elongation’s direction of the spring, and refers to the damping force acts on along the pendulum length.
To gain over the governing system of motion, we consider the planar motion of our model. So after time the coordinates of the suspended point can be expressed as
Use the following Lagrange’s equations of the second type to obtain the equations of motion:where expresses Lagrange’s function and and represent the generalized coordinates and velocities of the mentioned model, respectively. The potential and kinetic energies of the considered system are given, respectively, asHere, denotes the gravity acceleration, is the spring elongation, and is the angle between the vertical and line directed through the mass .
In addition to the influence of the kinematic excitation on the examined system, the moments and (of the linear viscous damping) have an extra effect around . Furthermore, the force and the linear viscous damping are acting on the mass and directed along the pendulum arm in which and denote the viscous coefficients.
According to the nonconservative forces, the generalized forces take the formwhere and are forcing frequencies of and , respectively.
3. The Analytical Solution
The aim of this section is obtain the analytic solutions of the previous equations of motion using the MS method and to get the modulation equations in order to obtain the resonances conditions. So it is necessary to start with the approximations of and included in (5) using Taylor series up to the second terms as It should be noticed that this approximation is valid in a neighborhood of all positions of static equilibrium.
It is customary to define both of the damping coefficients and the amplitudes of external forces, in order to achieve the analysis procedure asin which represents a small parameter. Furthermore, let us assumeIn which the parameters included in the previous two equalities are of order 1. Let us introduce the following form for the amplitudes of vibrations:It is important to notice that these amplitudes are of order . So we seek the forms of the functions and aswhere ; represent the independent variables of the different time scales. Also, the differentiations are transformed into the formsSubstituting (7)–(11) into (5), using the operators (12), and then equating the coefficients of like powers of in both sides, one obtains the next sets of partial differential equations from second order.
The solutions of (13) take the formwhere are unknown complex functions that can be determined and are the corresponding complex conjugate.
Substituting (16) into (14) and then omitting the terms that produce the secular ones, we get the second-order approximations in the formwhere express about the complex conjugates of the preceding terms.
As we developed previously, substitute (16)-(17) into (15) and then remove secular terms to obtain the third-order approximations in the formThe unknowns and can be determined from the conditions of removing the secular terms.
4. Modulation Equations Near Resonances
The main task of this section is to determine the resonances cases. For this purpose, we note that solutions (17)-(18) have singularities when any of their denominators equals zero. So the secular terms appearing on the right sides of (14)-(15) make system (17)-(18) insignificant when some frequency conditions are hold. According to this discussion and to the previous solutions, the resonance cases can be classified as follows:(i)Principal (primary) external resonances occurring at and .(ii)The spring’s resonance arising from the kinematic excitation at .(iii)The pendulum resonance produced from kinematic excitation at .(iv)Internal resonance occurring at .(v)Combined resonances at and .
The behavior of the system will be very complicated if the natural frequencies satisfy the above resonance cases. Let us examine the first case of resonance categories and appearing simultaneously. Under the present circumstances and in order to investigate the resonances, one inserts the following detuning parameters and according towhere . This means that the detuning parameters describe the closeness of the excitation frequencies and to and , respectively.
Firstly: Second-Order Equations
Secondly: Third Order Equations
Now, we can determine the unknown functions , , , and from the previous solvability conditions (20)-(21). It is customary to express these functions in the following polar form: in which , and , represent the real functions of the solutions and and represent both of amplitudes and phases, respectively.
It is worthwhile to notice that definition (23) has a great advantage form due to the fact that the above modulation system is autonomous. Equating the real and imaginary parts in (24) and omitting the symbol for simplicity, then we have a system consisting of four first-order differential equations in the form
Moreover, the previous system of (25) characterizes the amplitudes and and the modified phases and for the examined simultaneously resonances cases.
The graphical representations of the numerical solutions for the original system of (5) are presented, after taking into consideration the system of (25), to describe the motion of our dynamical system at any time.
Figures 2 and 3 describe the time history of the motion for some selected parameters [kg·m2·s−1], [rad·s−1], [rad·s−1], [rad·s−1], [m], and [m]. It is not difficult to observe that Figure 2 displays the portrait of the solution against time and has the periodic or quasiperiodic behavior when time goes on, while Figure 3 describes the variation of the solution via and represents the typical resonance behavior.
5. Steady-State Solution
The scope of this section is to obtain the steady-state solutions of both the amplitudes and modified phases corresponding to the zero values of the previous system (25). After omission of the phases and from the steady-state solution, the formulas of frequency response equations take the following form.
For the Case of Parametric Resonance
For the Case of External Resonancein which and represent longitudinal amplitudes and fluctuating vibrations, respectively.
If two resonances occur at the same time, (26) and (27) ought to be a set of nonlinear equations in terms of and . So one can illustrate the possible steady-state solutions close to resonance through a plane which consists of the coordinates and .
The graphs displayed in Figures 4, 5, and 6 show the steady-state solutions of via when and take the values [rad·s−1], [rad·s−1], and [rad·s−1], respectively. The dashed lines represent the locus of the roots of (26), and the solid one identifies the solutions of (27). A closer look of these figures carefully shows that the concurrent points of both two curves identify the desired solutions of the system of (26) and (27). These points determine definitely the amplitudes of longitudinal and the fluctuating vibrations for the steady state. By the way, the steady states of oscillation may be stable or not. The geometrical representations of the system of (26) and (27) are obtained automatically using MATLAB program after taking into account the following parameters: [rad·s−1], [rad·s−1], [kg·m2·s−1], and [kg·m2·s−1].
This elucidates that the desired possible solutions can be expressed as functions of the oscillating system’s parameters. Moreover, the lowest number of possible solutions is one and the maximum is may be up to seven.
6. Stability Analysis
One of the important factors for the mentioned problem of the steady-state oscillations is to investigate their stability. For this task, we analyze the manner of the system in a region that is very close to the fixed points.
To discuss the stability for the particular solution of the steady state, we introduce the substitutionsinto (25). Here , , , and represent the solutions of (25) and , , , and denote perturbations which are assumed to be very small, compared to the predecessors. Then the linearized equations take the form
Take into consideration that the small perturbations , , , and are unknown functions. Every solution is a linear combination of , where , are constants and is the eigenvalue corresponding to the unknown perturbation, counted from the real parts of the roots. In this analysis, if the steady-state solutions (fixed points) , , , and are asymptotically stable, the real parts of the roots of the following characteristic equationof the set of (29), must be negative. Here , , , and take the form
However, according to the Routh-Hurwitz criterion , the fundamental conditions of the stability for the particular steady-state solutions will be
The used analysis to check the stability of the proposed solutions that are plotted in Figures 4, 5, and 6 can be interpreted as follows: the points characterized by black dots refer to the stable solutions, and those characterized by hollow circles refer to unstable ones. Figures 7–12 represent the variation of the solution against the solution for selected values of the effective parameters , , and on the motion when [rad·s−1].
This section is devoted to provide some examples about the motion of the considered model, especially when the axes of the ellipse become equal; that is, ; this elucidates that the motion of the pivot point will be on a circle. Moreover, the supported point becomes fixed; that is, (the major and minor axes take the zero value). In addition, the case can be studied when one length of ellipse’s axes vanishes ( or ) or more precisely the pivot point moves horizontally or vertically. So let us examine these cases.
Case 1 (). In this case, we observe that the suspended point moves in a circular path of radius . Figure 13 is drawn at [rad·s−1], [rad·s−1], [rad·s−1], [m], and [m]. Parts (a, b) and (c, d) of this figure portrait the time history of the solutions at and , respectively, while parts (e) and (f) display the projections of the phase planes at the same values of . Therefore, the present results are in a good agreement with the known previous results as in  (in the absence of the damping force ) and [18, 19] (with the consideration of ).
In this case the modulations of amplitudes for both solutions and after a short period of time tend to be more systematic, that is, harmonically, as indicated in parts (a), (b), (c), and (d). On the other hand, the shape of oscillations refers to the effectiveness of nonlinearity. The longitudinal vibration resorts to the sawtooth shape when time goes on till the end of time interval; this is due to the increasing of the nonlinearity parameters. The vibrations of the dynamical model tend to be steady state as shown from the time history plots.
Case 2 (). In this case we shall concentrate on the solutions when the supported point will be fixed. Figure 14 summarizes the results obtained at [rad·s−1], [rad·s−1], [rad·s−1], , and [m]. The effectiveness of increasing time is on the solutions and is illustrated in parts ((a), (b)) and ((c), (d)) of Figure 14 at [rad·s−1] and [rad·s−1], respectively. The variation of the solution via solution is presented in parts (e) and (f) of the same figure. The results of this case are in high consistency with the obtained ones in  (in the presence of the linear viscous damping).
Case 3 (). The task of this case is to interpret the motion of the dynamical system when the pivot point moves horizontally. So the dynamical motion will be in a horizontal axis of length through a long period . The graphs displayed in parts (a) and (b) of Figure 15 show the variation of the solutions and with the time when [rad·s−1], [rad·s−1], [rad·s−1], [rad·s−1], and [m]. On the other hand, part (c) of the same figure explicates the variation of versus at the same values of and .
Case 4 (). One of the important concepts is to study the dynamical motion when the supported point moves vertically on an axis of length during a long period . Several figures have been plotted to illustrate the dynamical movement of the nonlinear pendulum during time and to show the variation of the considered solutions with each other like parts (a) and (b) of Figure 16 for the time history evaluation and part (c) for the variation of the attained solutions. These plots are calculated during the period of time from to s at [rad·s−1], [rad·s−1], [rad·s−1], [rad·s−1], and [m].
It must be notice that the steady-state solutions at are trivial ones as shown from parts (a) and (b) from this figure.
The analytical solutions of the derived original system (represents a nonlinear 2-DOF equations (5)) up to the third approximation are obtained using the MS method. The determination of all possible resonances that might occur is presented. One of these possible resonances, namely, the principal external resonances when and , is studied. Moreover, the modulation equations are obtained and solved numerically. The possible amplitudes have been deduced in (26) and (27) for the parametric and for the external resonances, respectively. These amplitudes are represented graphically through different plots. The substantial conditions for the stability analysis of the investigated system have been achieved according to Routh-Hurwitz method in order to obtain the possible fixed points. The projections of the phase plane of both solutions and are represented graphically under certain parameters to show the effect of the different parameters on the motion. Some special cases from this work are presented in order to simulate the dynamic behavior of the considered model. Therefore, the present results are in high consistency with the known previous results as in [17–20]. One of the important applications of the considered model is the treatment of the seismic waves for the ground vibrations caused by seismic sources like earthquakes and volcano eruptions.
The authors declare that they have no competing interests.
- J. Miles, “Resonant motion of a spherical pendulum,” Physica D: Nonlinear Phenomena, vol. 11, no. 3, pp. 309–323, 1984.
- J. Miles, “Resonantly forced motion of two quadratically coupled oscillators,” Physica D. Nonlinear Phenomena, vol. 13, no. 1-2, pp. 247–260, 1984.
- S. Tousi and A. K. Bajaj, “Period-doubling bifurcations and modulated motions in forced mechanical systems,” ASME Journal of Applied Mechanics, vol. 52, no. 2, pp. 446–452, 1985.
- A. Maewal, “Chaos in a harmonically excited elastic beam,” Journal of Applied Mechanics, vol. 53, no. 3, pp. 625–632, 1986.
- A. H. Nayfeh, “Parametric excitation of two internally resonant oscillators,” Journal of Sound and Vibration, vol. 119, no. 1, pp. 95–109, 1987.
- A. M. Abou-Rayan, A. H. Nayfeh, D. T. Mook, and M. A. Nayfeh, “Nonlinear response of a parametrically excited buckled beam,” Nonlinear Dynamics, vol. 4, no. 5, pp. 499–525, 1993.
- A. K. Bajaj and S. Tousi, “Torus doublings and chaotic amplitude modulations in a two-degree-of-freedom resonantly forced mechanical system,” International Journal of Non-Linear Mechanics, vol. 25, no. 6, pp. 625–641, 1990.
- W. K. Lee and H. D. Park, “Chaotic dynamics of a harmonically excited spring-pendulum system with internal resonance,” Nonlinear Dynamics, vol. 14, no. 3, pp. 211–229, 1997.
- W. K. Lee and H. D. Park, “Second-order approximation for chaotic responses of a harmonically excited spring-pendulum system,” International Journal of Non-Linear Mechanics, vol. 34, no. 4, pp. 749–757, 1999.
- M. Eissa, S. A. El-Serafi, M. El-Sheikh, and M. Sayed, “Stability and primary simultaneous resonance of harmonically excited non-linear spring pendulum system,” Applied Mathematics and Computation, vol. 145, no. 2-3, pp. 421–442, 2003.
- A. Alasty and R. Shabani, “Chaotic motions and fractal basin boundaries in spring-pendulum system,” Nonlinear Analysis: Real World Applications, vol. 7, no. 1, pp. 81–95, 2006.
- S. J. Zhu, Y. F. Zheng, and Y. M. Fu, “Analysis of non-linear dynamics of a two-degree-of-freedom vibration system with non-linear damping and non-linear spring,” Journal of Sound and Vibration, vol. 271, no. 1-2, pp. 15–24, 2004.
- T. S. Amer and M. A. Bek, “Chaotic responses of a harmonically excited spring pendulum moving in circular path,” Nonlinear Analysis: Real World Applications, vol. 10, no. 5, pp. 3196–3202, 2009.
- R. Starosta, G. Sypniewska-Kamińska, and J. Awrejcewicz, “Asymptotic analysis of kinematically excited dynamical systems near resonances,” Nonlinear Dynamics, vol. 68, no. 4, pp. 459–469, 2012.
- J. Awrejcewicz, R. Starosta, and G. S. Kaminska, “Asymptotic analysis of resonances in nonlinear vibrations of the 3-dof pendulum,” Differential Equations and Dynamical Systems, vol. 21, no. 1-2, pp. 123–140, 2013.
- F. R. Gantmacher, Applications of the Theory of Matrices, John Wiley & Sons, New York, NY, USA, 2005.
- R. Starosta and J. Awrejcewicz, “Asymptotic analysis of parametrically excited spring pendulum,” in SYROM 2009, I. Visa, Ed., pp. 421–432, Springer, Berlin, Germany, 2009.
- R. Starosta, G. S. Kaminska, and J. Awrejcewicz, “Parametric and external resonances in kinematically and externally excited nonlinear spring pendulum,” International Journal of Bifurcation and Chaos, vol. 21, no. 10, pp. 3013–3021, 2011.
- J. Awrejcewicz and R. Starosta, “Resonances in a kinematically driven nonlinear system-Asymptotic analysis,” MESA, vol. 1, no. 1, pp. 1–10, 2010.
- J. Awrejcewicz, R. Starosta, and G. Sypniewska-Kamińska, “Asymptotic analysis and limiting phase trajectories in the dynamics of spring pendulum,” in Applied Non-Linear Dynamical Systems, vol. 93 of Springer Proceedings in Mathematics & Statistics, pp. 161–173, Springer, 2014.
Copyright © 2016 T. S. Amer et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.