Amplitude modulated dynamics of a resonantly excited autoparametric two degree-of-freedom system

Forced, weakly nonlinear oscillations of a two degree-of-freedom autoparametric vibration absorber system are studied for resonant excitations. The method of averaging is used to obtain first-order approximations to the response of the system. A complete bifurcation analysis of the averaged equations is undertaken in the subharmonic case of internal and external resonance. The locked pendulum mode of response is found to bifurcate to coupled-mode motion for some excitation frequencies and forcing amplitudes. The coupled-mode response can undergo Hopf bifurcation to limit cycle motions, when the two linear modes are mistuned away from the exact internal resonance condition. The software packages AUTO and KAOS are used and a numerically assisted study of the Hopf bifurcation sets, and dynamic steady solutions of the amplitude or averaged equations is presented. It is shown that both super-and sub-critical Hopf bifurcations arise and the limit cycles quickly undergo period-doubling bifurcations to chaos. These imply chaotic amplitude modulated motions for the system.     

Pseudolinear vibroimpact systems: Non-white random excitation

Response analyses of vibroimpact systems to random excitation are greatly facilitated by using certain piecewise-linear transformations of state variables, which reduce the impact-type nonlinearities (with velocity jumps) to nonlinearities of the common type — without velocity jumps. This reduction permitted to obtain certain exact and approximate asymptotic solutions for stationary probability densities of the response for random vibration problems with white-noise excitation. Moreover, if a linear system with a single barrier has its static equilibrium position exactly at the barrier, then the transformed equation of free vibration is found to be perfectly linear in case of the elastic impact. The transformed excitation term contains a signature-type nonlinearity, which is found to be of no importance in case of a white-noise random excitation. Thus, an exact solution for the response spectral density had been obtained previously for such a vibroimpact system, which may be called pseudolinear, for the case of a white-noise excitation. This paper presents analysis of a lightly damped pseudolinear SDOF vibroimpact system under a non-white random excitation. Solution is based on Fourier series expansion of a signum function for narrow-band response. Formulae for mean square response are obtained for resonant case, where the (narrow-band) response is predominantly with frequencies, close to the system's natural frequency; and for non-resonant case, where frequencies of the narrow-band excitation dominate the response. The results obtained may be applied directly for studying response of moored bodies to ocean wave loading, and may also be used for establishing and verifying procedures for approximate analysis of general vibroimpact systems.     

Subharmonic response of single-degree-of-freedom linear vibroimpact system to narrow-band random excitation

The subharmonic response of a single-degree-of-freedom linear vibroimpact oscillator with a one-sided barrier to the narrow-band random excitation is investigated. The analysis is based on a special Zhuravlev transformation, which reduces the system to the one without impacts or velocity jumps, and thereby permits the applications of asymptotic averaging over the period for slowly varying the inphase and quadrature responses. The averaged stochastic equations are exactly solved by the method of moments for the mean square response amplitude for the case of zero offset. A perturbation-based moment closure scheme is proposed for the case of nonzero offset. The effects of damping, detuning, and bandwidth and magnitudes of the random excitations are analyzed. The theoretical analyses are verified by the numerical results. The theoretical analyses and numerical simulations show that the peak amplitudes can be strongly reduced at the large detunings.     

窄带随机噪声作用下单自由度非线性碰撞系统的响应

研究了单自由度非线性单边碰撞系统在窄带随机噪声激励下的次共振响应问题。用Zhuravlev变换将碰撞系统转化为速度连续的非碰撞系统,然后用随机平均法得到了关于慢变量的随机微分方程。在没有随机扰动情形,得到了系统响应幅值满足的代数方程;在有随机扰动的情形下,给出了系统响应稳态矩计算的迭代公式。讨论了系统阻尼项、非线性项、随机扰动项和碰撞恢复系数等参数对于系统响应的影响。理论计算和数值模拟表明,系统响应幅值将在激励频率接近于次共振频率时达到最大。而当激励频率逐渐偏离次共振频率时,系统响应迅速衰减。     

Transition from Planar to Whirling Oscillations in a Certain Nonlinear System

A single-mass two-degrees-of-freedom system is considered, witha radially oriented nonlinear restoring force. The latter is smooth andbecomes infinite at a certain value of a radial displacement. Stabilityanalysis is made for planar oscillation, or motion along a givendirection. As long as this motion is periodic, the nonlinearity in therestoring force provides a periodic parametric excitation in thetransverse direction. The linearized stability analysis is reduced tostudy of the Mathieu equation for the (infinitesimal) motions in thetransverse direction. For the case of free oscillations in the givendirection an exact solution is obtained, since a specific analyticalform is used for the (strongly nonlinear) restoring force, which permitsexplicit integration of the equation of motion. Stability of the planarmotion in this case is shown to be very sensitive to even slightdeviations from polar symmetry in the restoring force (as well as to theamplitude of oscillations in the given direction). Numerical integrationof the original equations of motion shows the resulting motion to be awhirling type indeed in case of the transversal instability. For thecase of a sinusoidal forcing in the given direction solution for the(periodic) response is obtained by Krylov–Bogoliubov averaging. Thisresults in the transmitted Ince–Strutt chart – namely, stabilitychart for transverse direction on the amplitude-frequency plane of theexcitation in the original direction.     

Response statistic of strongly non-linear oscillator to combined deterministic and random excitation

The principal resonance of a van der Pol-Duffing oscillator to the combined excitation of a deterministic harmonic component and a random component has been investigated. By introducing a new expansion parameter , the method of multiple scales is adapted for the strongly non-linear system. Then the method of multiple scales is used to determine the equations of modulation of response amplitude and phase. The behavior and the stability of steady-state response are studied by means of qualitative analysis. The effects of damping, detuning, bandwidth, and magnitudes of random excitations are analyzed. The theoretical analyses are verified by numerical results. Theoretical analyses and numerical simulations show that when the intensity of the random excitation increases, the non-trivial steady-state solution may change from a limit cycle to a diffused limit cycle. Under some conditions the system may have two steady-state solutions. Random jump may be observed under some conditions. The results obtained in the paper are adapted for a strongly non-linear oscillator that complement previous results in the literature for the weakly non-linear case.     

Localized modes in a variety of driven long Josephson junctions with phase shifts

We study both analytically and numerically the localized modes in long Josephson junctions with phase shift formations, so-called \(0{-}\pi {-}0\) and \(0{-}\kappa \) junctions. The system is described by an inhomogeneous sine-Gordon equation with a variety of time-periodic drives. Perturbation technique, together with multiple-scale expansions, is applied to obtain the amplitude of oscillations. It is observed that the obtained amplitude equations decay with time due to radiative damping and emission of high harmonic radiations. It is also observed that the energy taken away from the internal mode by radiation waves can be balanced by applying either direct or parametric drives. The appropriate external drives are applied to re-balance the dissipative and radiative losses. We discuss in detail the excitation by direct and parametric drives with frequencies to be either in the vicinity or double the natural frequency of the system. It is noted that the presence of external applied drives stabilizes the nonlinear damping, producing stable breather modes in long Josephson junctions. It is also noted that in the presence of parametric drives, the amplitudes of the driving forces are much more sensitive than in the case of external ac drives; that is, in the case of parametric drives, a small change in the amplitudes of the driving forces can make a drastic change in the system behavior and the system becomes unstable as compared to the case of the direct ac driving. Furthermore, we noticed that, in the presence of external driving, the driving effect is stronger for the case of driving frequency nearly equal to the system frequency as compared to that of the driving frequency nearly equal to twice the frequency of the oscillatory mode.     

Bifurcations in the Mean Angle of a Horizontally Shaken Pendulum: Analysis and Experiment

A pendulum excited by high-frequency horizontal displacement of its pivot point will vibrate with small amplitude about a mean position. The mean value is zero for small excitation amplitudes, but if the excitation is large enough the mean angle can take on non-zero values. This behavior is analyzed using the method of multiple time scales. The change in the mean angle is shown to be the result of a pitchfork bifurcation, or a saddle-node bifurcation if the system is imperfect. Analytical predictions of the mean angle as a function of frequency and amplitude are confirmed by physical experiment and numerical simulation.     

Nonlinear stochastic analysis of subharmonic response of a shallow cable

The paper deals with the subharmonic response of a shallow cable due to time variations of the chord length of the equilibrium suspension, caused by time varying support point motions. Initially, the capability of a simple nonlinear two-degree-of-freedom model for the prediction of chaotic and stochastic subharmonic response is demonstrated upon comparison with a more involved model based on a spatial finite difference discretization of the full nonlinear partial differential equations of the cable. Since the stochastic response quantities are obtained by Monte Carlo simulation, which is extremely time-consuming for the finite difference model, most of the results are next based on the reduced model. Under harmonical varying support point motions the stable subharmonic motion consists of a harmonically varying component in the equilibrium plane and a large subharmonic out-of-plane component, producing a trajectory at the mid-point of shape as an infinity sign. However, when the harmonical variation of the chordwise elongation is replaced by a narrow-banded Gaussian excitation with the same standard deviation and a centre frequency equal to the circular frequency of the harmonic excitation, the slowly varying phase of the excitation implies that the phase difference between the in-plane and out-of-plane displacement components is not locked at a fixed value. In turn this implies that the trajectory of the displacement components is slowly rotating around the chord line. Hence, a large subharmonic response component is also present in the static equilibrium plane. Further, the time variation of the envelope process of the narrow-banded chordwise elongation process tends to enhance chaotic behaviour of the subharmonic response, which is detectable via extreme sensitivity on the initial conditions, or via the sign of a numerical calculated Lyapunov exponent. These effects have been further investigated based on periodic varying chord elongations with the same frequency and standard deviation as the harmonic excitation, for which the amplitude varies in a well-defined way between two levels within each period. Depending on the relative magnitude of the high and low amplitude phase and their relative duration the onset of chaotic vibrations has been verified.     

Transverse vibrations of rotating shafts: Probability density and first-passage time of whirl radius

Transverse vibrations are considered for a single mass/two-degrees-of-freedom rotating shaft with linear internal or “rotating” damping and nonlinear external damping. The shaft is excited by external random forces. Analysis of resulting random vibrations is based on stochastic averaging method which yields separated (in the linear approximation) equations for complex amplitudes of forward and backward whirling motions. The former of these motions is shown to be dominant at rotation speeds in the vicinity of the instability threshold. Using this approximation an analytical solution is obtained for probability density of squared radius of the shaft's whirl. This solution can be used to detect on-line shaft's instability from its observed response. Solution is also obtained for expected time for reaching given level by the squared whirl radius of the shaft.     

Vibration of a Non-Linear Self-Excited System with Two Degrees of Freedom under External and Parametric Excitation

Vibration analysis of a non-linear parametrically self-excited system with two degrees of freedom under harmonic external excitation was carried out in the present paper. External excitation in the main parametric resonance area was assumed in the form of standard force excitation or inertial excitation. Close to the first and second free vibrations frequency, the amplitudes of the system vibrations and the width of synchronization areas were determined. Stability of obtained periodic solutions was investigated. The analytical results were verified and supplemented with the effects of digital and analog simulations.     

Resonant response of a non-linear vibro-impact system to combined deterministic harmonic and random excitations

The resonant resonance response of a single-degree-of-freedom non-linear vibro-impact oscillator, with cubic non-linearity items, to combined deterministic harmonic and random excitations is investigated. The method of multiple scales is used to derive the equations of modulation of amplitude and phase. The effects of damping, detuning, and intensity of random excitations are analyzed by means of perturbation and stochastic averaging method. The theoretical analyses verified by numerical simulations show that when the intensity of the random excitation increases, the non-trivial steady-state solution may change from a limit cycle to a diffused limit cycle. Under certain conditions, impact system may have two steady-state responses. One is a non-impact response, and the other is either an impact one or a non-impact one.     

Quasi-harmonic analysis of the behaviour of a hardening Duffing oscillator subjected to filtered white noise

The behaviour of a hardening Duffing oscillator subjected to narrow band random excitation is examined. The influence of possible jumps, between competing states, on the probability distribution of the response amplitude is addressed. A quasi-harmonic approximation of system behaviour is adopted which is capable of reproducing the observed concave shape of probability functions and compares well with predictions obtained via stochastic averaging techniques and with digital simulations.     

Wind-driven nonlinear oscillations of cables

The objective of this paper is the study of the dynamics of damped cable systems, which are suspended in space, and their resonance characteristics. Of interest is the study of the nonlinear behavior of large amplitude forced vibrations in three dimensions. As a first-order nonlinear problem the forced oscillations of a system having three-degrees-of-freedom with quadratic nonlinearities is developed in order to consider the resonance characteristics of the cable and the possibility of dynamic instability. The cables are acted upon by their own weight in the perpendicular direction and a steady horizontal wind. The vibrations take place about the static position of the cables as determined by the nonlinear equilibrium equations. Preliminary to the nonlinear analysis the linear mode shapes and frequencies are determined. These mode shapes are used as coordinate functions to form weak solutions of the nonlinear autonomous partial differential equations.In order to investigate the behavior of the cable motion in detail, the linear and the nonlinear analyses are discussed separately. The first part of this paper deals with the solution to the self adjoint boundary-value problem for small-amplitude vibrations and the determination of mode shapes and natural frequencies. The second problem dealt with in this paper is the determination of the phenomena produced by the primary resonance of the system. The method of multiple time scales is used to develop solutions for the resulting multi-dimensional dynamical system with quadratic nonlinearity.Numerical results for the steady state response amplitude, and their variation with external excitation and external detuning for various values of internal detuning parameters are obtained. Saturation and jump phenomena are also observed. The jump phenomenon occurs when there are multi-valued solutions and there exists a variation of kinetic energy among solutions.Notation A=diag(a _i ,i=1, 2, 3) amplitude matrix (diagonal) - A _n,A undeformed area, deformed area - B span of hanging cables - D sag for static conditions - E Young's modulus - vector of external force - diagonal matrix - symmetric coefficient matrix - H ^* =HR I unit matrix - diagonal matrix - L original length of cables before hanging - M the symmetric stiffness matrix - N integer - P damping constant matrix (diagonal) - R linear mode shape matrix (diagonal) - S sway of hanging cables - T tension of cables - T _o tension of cables for static conditions - T _o(0) tension of the lowest point for static conditions - V eigenfunction matrix - b=y ^T R coefficient vector - b - c,c ₁,c ₂,c ₃ vector, and the components in thex ₁,x ₂,x ₃ directions respectively, in terms of cosine functions. - e, e _o strain, and static strain of elongation - e ₁ time-dependent perturbation ine - f wind force in the sway direction - f, f ₀,f ₁ vector of external force - g gravity constant - h time-dependent amplitude vector - m mass density per unit length of the undeformed cable - r=(R ₁,R ₂,R ₃) ^T vector of modal shapes - s undeformed arc length - t time - u ₁ linear scalar in z - u ₂ quadratic scalar in z - v ₁,v ₂,v ₃ eigenfunctions inx ₁,x ₂, andx ₃ directions, respectively - x=(x ₁,x ₂,x ₃) ^T Cartesian position vector and components - y=(y ₁,y ₂,y ₃) ^T static position vector and components - error vector - matrix operator - =diag[₁, ₂, ₃] internal frequency matrix and components - excitation frequency - global matrix of coordinate functions - T _o(0)/mgL - mgL/EA _o - yy ^T - s/L - = diag[₁, ₂, ₃] phase angle matrix and components of characteristic modes - phase angle of excitation force - ₁, ₂ time-dependent amplitude vectors in timet _o and timet ₁ - _ij,i=1, 2...N,j=1, 2, 3 theith coordinate function of thejth component - _i = diag[_i1, _i2, _i3] theith matrix of coordinate functions - global vector of modal amplitudes - ₁ external detuning parameter - _i,i=2, 3 internal detuning parameter - _i,i=1, 2, 3 phase angles     

Amplitude reduction of primary resonance of nonlinear oscillator by a dynamic vibration absorber using nonlinear coupling

The paper presents the characteristics of a new type of nonlinear dynamic vibration absorber for a main system subjected to a nonlinear restoring force under primary resonance. The absorber is connected to the main system by a link in order to be excited with twice the frequency of the motion of the main system. The natural frequency of the absorber is tuned to be twice the natural frequency of the main system, in contrast to autoparametric vibration absorber, whose natural frequency is tuned to be one-half the natural frequency of the main system. The presented absorber is not excited through the autoparametric resonance, i.e., no trivial equilibrium state exists. Therefore, the absorber always oscillates because of the motion of the main system and cannot be trapped by Coulomb friction acting on the absorber, in contrast to the autoparametric vibration absorber. Under small excitation amplitude, this absorber does not produce an overhang in the frequency response curve, which occurs because of the use of the conventional autoparametric vibration absorber; the overhang renders the response amplitude larger than that in the case without an absorber. In addition, the absorber removes the hysteresis in the frequency response curve caused by the nonlinearity of the restoring force acting on the main system. Regarding large excitation amplitude, the response amplitude in the main system can be decreased by increasing the damping of the absorber, but that decrease is limited by the nonlinearity in the restoring force acting on the main system. This paper also describes experimental validation of the absorber under small excitation amplitude using a simple apparatus.     

Dynamical responses of airfoil models with harmonic excitation under uncertain disturbance

In this paper, we investigate nonlinear dynamical responses of two-degree-of-freedom airfoil (TDOFA) models driven by harmonic excitation under uncertain disturbance. Firstly, based on the deterministic airfoil models under the harmonic excitation, we introduce stochastic TDOFA models with the uncertain disturbance as Gaussian white noise. Subsequently, we consider the amplitude–frequency characteristic of deterministic airfoil models by the averaging method, and also the stochastic averaging method is applied to obtain the mean-square response of given stochastic TDOFA systems analytically. Then, we carry out numerical simulations to verify the effectiveness of the obtained analytic solution and the influence of harmonic force on the system response is studied. Finally, stochastic jump and bifurcation can be found through the random responses of system, and probability density function and time history diagrams can be obtained via Monte Carlo simulations directly to observe the stochastic jump and bifurcation. The results show that noise can induce the occurrence of stochastic jump and bifurcation, which will have a significant impact on the safety of aircraft.     

Tuning the primary resonances of a micro resonator,using piezoelectric actuation

Microbeam dynamics is important in MEMS filters and resonators. In this research, the effect of piezoelectric actuation on the resonance frequencies of a piezoelectrically actuated capacitive clamped-clamped microbeam is studied. The microbeam is sandwiched with piezoelectric layers throughout its entire length. The lower piezoelectric layer is exposed to a combination of a DC and a harmonic excitation voltage. The DC electrostatic voltage is applied to prevent the doubling of the excitation frequency. The traditional resonators are tuned using DC electrostatic actuation, which tunes the resonance frequency only in backward direction on the frequency domain. The proposed model enables tuning the resonance frequencies in both forward and backward directions. For small amplitudes of harmonic excitation and high enough quality factor, the frequency response curves obtained by the shooting method are validated with those of the multiple time scales technique. Unlike the perturbation technique, which imposes limitation on both the amplitude of the harmonic excitation and the quality factor to be applicable, the shooting method can be applied to capture the periodic attractors regardless of how big the amplitude of harmonic excitation and the quality factor are.     

A method for analysis of non-linear vibrations caused by modulated random excitation

A method for analyzing the response of a class of weakly non-linear and lightly damped systems to a separable non-stationary random excitation is presented. The random excitation is represented as the product of a slowly varying modulating deterministic function and a broad-band stationary process. Using an averaging procedure a first order equation governing the time evolution of the response amplitude is derived. The Fokker-Planck equation which describes the diffusion of the probability density function of the response amplitude is considered. A particularly convenient basis of orthonormal functions, as well as, necessary formulae for the determination of an approximate solution of the Fokker-Planck equation by means of the Galerkin technique are presented. Furthermore, based on this solution an equation is given for the determination of the statistical moments of the response amplitude.     

Finite-amplitude self-oscillations in a rotating Hagen-poiseuille flow

The nonlinear stability of a viscous incompressible flow in a circular pipe rotating about its own axis is investigated. A solution of the initial—boundary value problem for the unsteady three-dimensional Navier—Stokes equations is found by means of the Bubnov—Galerkin method [1–5]. A series of methodological investigations were made. The nonlinear evolution of the periodic self-oscillating regimes is studied, and their characteristic stabilization times, amplitudes, and other integral and fluctuational characteristics are found. The secondary instability of these finite-amplitude wave motions is examined. It is established that the secondary instability is initially weak and linear in character; the corresponding growth times are approximately an order greater than for the primary perturbations. There is the possibility of a sharp, explosive restructuring of the motion when the secondary perturbations reach a certain critical amplitude. A survival curve [5] is constructed, which makes it possible to determine the preferred perturbation, distinguishable from the rest if the initial perturbation amplitudes are equal, and the critical amplitude values starting from which the other perturbations may prevail even over the preferred one. The range of these surviving perturbations is obtained. It is shown that as a result of the non-linear interaction of several perturbations at low levels of supercritlcality periodic motion in the form of a single traveling wave is generated.Translated from Izvestiya Akademii Nauk SSSR, Mekhanika Zhidkosti i Gaza, No. 4, pp. 22–28, July–August, 1985.     

On stability of the Hill equation with damping

We consider the Hill equation with damping describing the parametric oscillations of a torsional pendulum excited by varying the moment of inertia of the rotating body. Using the method of a small parameter, we analytically calculate a fundamental system of solutions of this equation in the form of power series in the excitation amplitude with accuracy O(²) and verify conditions for its stability. In the first-order approximation in , we prove that the resonance domain exists only if the excitation frequency is sufficiently close to the double natural frequency of the pendulum; the corresponding equation of the stability boundary is obtained.Published in Neliniini Kolyvannya, Vol. 7, No. 2, pp. 169–179, April–June, 2004.