Abstract
In this work, we formulate and investigate a nonlinear initial boundary-value problem for an array of N elastically coupled hybrid microcantilever beams that are subject to electrodynamic excitation. The equations of motion for the individual viscoelastic element consist of two fields: the base component which is common to all cantilevers and the unrestrained component which is excited electrodynamically. The coupling of the elements is obtained via an equivalent linear stiffness that is estimated from experimental measurements of a 5-element array. We employ a Galerkin ansatz to obtain a modal dynamical system that consistently incorporates a quintic nonlinearity due to the combined effects of cubic viscoelasticity and quadratic electrodynamics. We validate the periodic response of a 5-element array with moderate damping and construct numerically a comprehensive bifurcation structure for a 25-element array. The analysis reveals an intricate structure for small damping that includes both quasiperiodic and nonstationary chaotic-like energy transfer between the elements of the array. It is noteworthy that an array with a larger coupling stiffness, corresponding to a smaller distance between adjacent elements, yields a chaotic bifurcation structure for a larger value of viscoelastic damping.
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Acknowledgements
This research was supported in part by the Technion Russell Berrie Nanotechnology Institute and the Israel Science Foundation (136/16) and the Spanish Ministry of Economy Project TEC2015-66337-R. PNK thanks the Technion and the Israel-Council for Higher Education for their support of his postdoctoral fellowship.
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Appendices
Appendix A: Nonlinear damping of a single field cantilever
Following [27], the equations of motion for a beam can be written as
Neglecting rotary inertia (\(j_{3}=0\)) the equilibrium of moments with respect to y direction for a beam [27] are given by
where \(F_{1}\), \(F_{2}\) are the resultant stresses, \(M_{3}\) is the moment, \(\varTheta _{3}\) is the rotational angle, and e is axial strain for the displacements U and W. The axial strain e is defined as a function of the displacements U and W [27] as
and the bending curvature \(\rho _{3}\) is defined as a function of rotational angle \(\varTheta _{3}\) as
where the displacements U and W are related to rotational angle \(\varTheta _{3}\) as [27]
The viscoelastic constitutive law incorporating a Voigt–Kelvin strain-rate-dependent damping is
where
Considering isotropic materials for the beam, assuming that the reference line coincides with the centroidal line and using Eq. (7.7), the moment equation can be written as
Assuming that the beam is inextensible (\(e=0\)) Eq. (7.8) becomes
For inextensible condition of the beam (\(e=0\)), Eqs. (7.4) and (7.6) are rewritten as
Integrating Eq. (7.10) once with respect to x and using the boundary conditions \(U=0\) at \(x=0\), we obtain
Integrating Eq. (7.1) once with respect to x and using the boundary condition \(F_{x}=0\) at \(x=L\), yields
Differentiating Eq. (7.12) twice with respect to t and interchanging the order of integration and differentiation, we obtain
Hence,
Substituting Eqs. (7.11) and (7.14) into Eq. (7.13) yields
The bending curvature \(\rho _{3}\) and the rotational angle \(\varTheta _{3}\) are related using Eqs. (7.5) and (7.11) as
Substituting Eq. (7.16) into Eq. (7.9) yields
Substituting \(M_{3}\) from Eq. (7.17) into Eq. (7.3) with \(e=0\) yields
Substituting Eqs. (7.15) and (7.18) into Eq. (7.2) and using Eq. (7.11), yields equation of motion
Expanding the terms in Eq. (7.19) for small W upto cubic terms yields
where W, \(\rho A\), and EI are the beam transverse displacements, longitudinal mass density, and bending stiffness, respectively. For rectangular cross section, the area is \(A=HB\) and the bending moment of inertia is \(I=BH^3/12\), where B and H are the beam width and thickness as shown in Fig. 1. D is internal material damping based on a Voigt–Kelvin model [13], respectively. The electrodynamic excitation \(Q_{V}\) is given by
where \({V}_{f}=V_\mathrm{dc}+V_\mathrm{ac}\cos (\varOmega t)\), d is distance between beam and bottom substrate \(\epsilon _{0}=8.854\times 10^{-12}\) is permitivity of free space. The corresponding boundary conditions of a microbeam are as follows
We nondimensionalize the governing equations with the variables \(w={W}/{d}\), \(s={x}/{L}\) and \(\tau ={t}/{T_{s}}\) where \(T_{s}^2=({\rho AL^4}/{EI})^2\) and \(\omega _{s}=1/T_{s}\). The non-dimensionalized equations of motion are given by
The nondimensionalize boundary conditions are as follows
The equivalent non-dimensionalized parameters in Eq. (7.23) are
We premultiply Eq. (7.23) by denominator term and derive the modal dynamic equations by applying Galerkin’s method. We substitute the assumed solutions as \(w(s,\tau ) = q(\tau )\phi (s)\) into Eq. (7.23), and applying Galerkin’s method, we obtain ordinary differential equation which is of the form
where the various integral coefficients in Eq. (7.26) are given in Eq. (7.27).
Appendix B: IBVP for a two field cantilever
We consider a microcantilever beam with step-like heterogeneity of its width subjected to electrodynamic excitation along out-of-plane direction as shown in Fig. 1a. The two field equations of motion governing the microcantilever beam as found in [15, 27] are thus
where \(W_{i}\), \(\rho A_{i}\), and \(EI_{i}\) are the beam transverse displacements, longitudinal mass density, and bending stiffness, respectively. For rectangular cross sections, the area is \(A_{i}=HB_{i}\) and the bending moment of inertia is \(I_{i}=B_{i}H^3/12\), where \(B_{i}\) and H are the beam width and thickness as shown in Fig. 1 and D is internal material damping based on a Voigt–Kelvin model [13]. The electrodynamic excitation \(Q_{V}\) along out-of-plane direction is given by
where \({V}_{f}=V_\mathrm{dc}+V_\mathrm{ac}\cos (\varOmega t)\), d is distance between beam and bottom substrate, \(\epsilon _{0}=8.854\times 10^{-12}\) is permitivity of free space. The corresponding fixed boundary conditions of the microbeam are as follows
The continuity conditions between two fields at \(x=L_{1}\) in Fig. 1 are
We nondimensionalize the governing equations with the variables \(w_{i}={W_{i}}/{d}\), \(s={x}/{L}\) and \(\tau ={t}/{T_{s}}\) where \(T_{s}^2=({\rho A_{1}L^4}/{EI_{1}})^2\) and \(\omega _{s}=1/T_{s}\). The non-dimensionalized equations of motion are given by
The nondimensionalize boundary conditions and continuity conditions are as follows
The equivalent non-dimensionalized parameters in Eqs. (7.33)–(7.35) are written as
1.1 Modal dynamical system
We neglect damping and forcing terms from Eqs. (7.33) and (7.34) which yields the two field equations of motion for the unforced and undamped vibrations \(w_{i,\tau \tau }+w_{i,ssss}=0\)\((i=0 \ldots 2)\). Substituting \(w_{i}=q\phi _{i} (i=1 \ldots 2)\) into resulting equations yields the classical Euler–Bernoulli beam dispersion relationship \(\omega _{n}^2=z_{n}^4\). Substituting \(w_{i}=q\phi _{i}\)\((i=1 \ldots 2)\) into Eq. (7.35) yields
To obtain the mode shapes for two field system, we assume mode shapes of the form
where \(A_{j}\) and \(B_{j}\) are constants to be determined by the boundary and continuity conditions in Eq. (7.37). Substitution of Eq. (7.38) into Eq. (7.37) yields an algebraic linear system of equations, which has a nontrivial solution if the determinant of the following coefficient matrix vanishes.
where \(C\alpha =\cos (z_{n}\alpha )\), \(S\alpha =\sin (z_{n}\alpha )\), \(CH\alpha =\cosh (z_{n}\alpha )\), \(SH\alpha =\sinh (z_{n}\alpha )\),\(C1=\cos (z_{n})\), \(S1=\sin (z_{n})\), \(CH1=\cosh (z_{n})\), \(SH1=\sinh (z_{n})\). We find the determinant of Eq. (7.39) and solve it for \(z_{n}\) for different values of \(\alpha \) and \(\beta \). We substitute back \(z_{n}\) into Eq. (7.38), and using Eq. (7.37), we solve the simultaneous equations to find the constants \(A_{j}\) and \(B_{j}\) which satisfies the orthogonality condition for various values of \(\alpha \) and \(\beta \). The nondimensional wave numbers for different \(\alpha \) and \(\beta \) are shown in Table 4.
We premultiply Eqs. (7.33) and (7.34) by denominator in Eq. (7.34) and derive the modal dynamic equations by applying Galerkin’s method. We substitute the assumed solutions as \(w_{i}(s, \tau ) = q(\tau )\phi _{i}(s) (i=1 \ldots 2)\) into Eqs. (7.33) and (7.34), and applying Galerkin’s method, we obtain ordinary differential equation which is of the form
where the various integral coefficients in Eq. (7.40) are as follows
Appendix C: Properties of the array
This appendix includes dimensions, material properties, and physical parameters for \(\kappa =3.3\times 10^5\) (estimated value) and for \(\kappa =1.3\times 10^6\) given in Table 5.
Appendix D: Integral coefficients for the array
This appendix includes integral coefficients of Eq. (2.13). All integral coefficients evaluated for \(\alpha =0.075\), \(\beta =0.22\) and for \(\alpha =0.075\), \(\beta =0.12\) are given in Table 6.
Note that for identical beams \(J_{nj}\) are equal and \(\phi _{n-1}=\phi _{n}=\phi _{n+1}\) for all n.
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Kambali, P.N., Torres, F., Barniol, N. et al. Nonlinear multi-element interactions in an elastically coupled microcantilever array subject to electrodynamic excitation. Nonlinear Dyn 98, 3067–3094 (2019). https://doi.org/10.1007/s11071-019-05074-7
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DOI: https://doi.org/10.1007/s11071-019-05074-7