Input Power in Infinite Beam Structure
1. INTRODUCTION
An energy harvesting device is modeled as a single degree of freedom mass-spring-damper system which are either mass excited or base excited where the energy harvested by the device is analogous to the energy dissipated by the damper. The performance of this linear device is optimized when the natural frequency of the device is tuned to match the ambient frequency [1] and a slight mistune will bring a vast deterioration in the device performance. This thus creates a limitation on the linear generator since ambient frequency varies with time. In order to overcome this limitation, researchers introduce nonlinearity into the system in the form of hardening spring. The theoretical study on the energy harvesting devices engaging a hardening spring has been keenly conducted by Quinn et al. [2] and Ramlan et al. [3]. A hardening spring system has a response that is less sensitive to the change in frequency which makes it fit for applications with varying ambient frequency. The response of the system with such a spring is able to widen the bandwidth to a much frequency range than the linear system, which provides some advantages in harvesting the vibrationmechanical energy from ambient sources since ambient frequency varies with time. Currently, the degree of nonlinearity of devices employing a hardening spring is considered very weak. Hence, the electromechanical coupling for this weak nonlinear system is assumed to be similar to the one with a linear spring. A conclusive evident is seek theoretically to quantify the degree of nonlinearity in hardening system so that the validity of using linear electromechanical coupling on hardening nonlinear system can be established.2. METHODOLOGY
Approximate solution of harmonic balance method and multiple scale method is pursued to quantify the degree of nonlinearity of a hardening system. The equation of motion for a base-excited hardening Duffing oscillator is given by [4] � + � + � + � = −�� 1 where = − � is the relative displacement between the seismic mass, x, and the housing, y, and y = Y cos � , � is the linear spring constant and � is the nonlinear spring constant with � denoting a hardening system. Equation 1 can be expressed in non-dimensional form as + + + � = Ω cos Ω� + ∅ 2 wher e = � � , = � � , � = � � 2 � , Ω = � , � = � � , ∅ = phase angle between excitation and response2.1 Harmonic Balance Method
Single harmonic and two harmonic steady state solutions of equation 1 is seek using harmonic balance method as conversed by Hamdan and Burton [5]. The single-mode approximation for the steady state response is assumed to have the solution in the form of � = �� � 3 where A is the steady state response amplitude. In single-mode solution, only the fundamental harmonic approximation is obtained and the third harmonics is neglected. Next, the two-mode approximation for the steady state response is assumed to have the solution in the form of � = cos � + cos � + sin � 4 where is the first harmonic amplitude and and is the third harmonic amplitude. In two-mode solutions, the amplitude of first harmonic and third harmonic is acquired.Parts
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» INTRODUCTION Proceeding Of Mechanical Engineering Research Day 2015 (MERD’15).
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» Input Power in Infinite Beam Structure
» Averaging Over Frequency Bands
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