By Dirk Spreemann
Electromagnetic vibration transducers are noticeable as a great way of harvesting ambient strength for the availability of sensor tracking platforms. assorted electromagnetic coupling architectures were hired yet no finished comparability with admire to their output functionality has been conducted prior to now. Electromagnetic Vibration strength Harvesting Devices introduces an optimization process that is utilized to figure out optimum dimensions of the parts (magnet, coil and again iron). 8 various mostly utilized coupling architectures are investigated. the consequences express that right dimensions are of serious value for maximizing the potency of the strength conversion. A comparability yields the architectures with the easiest output functionality strength which can be ideally hired in functions. A prototype improvement is used to illustrate how the optimization calculations could be built-in into the design–flow. Electromagnetic Vibration strength Harvesting Devices ambitions the clothier of electromagnetic vibration transducers who needs to have a better in-depth knowing for maximizing the output functionality.
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Extra info for Electromagnetic Vibration Energy Harvesting Devices: Architectures, Design, Modeling and Optimization
Detailed analysis on this is given in [63, 64]. 005 0 ζe Fig. 41) where Zmax denotes the maximum relative displacement. 37) the normalized damping factor has been split into an electromagnetic and a parasitic part. 39) to obtain the displacement constrained output power: Pcs D m 4. 42) Consequently the maximum power for constrained condition is again obtained at resonance where ! D ! 5 Characterization and Handling of Machinery Induced Vibration Commonly the vibration source is assumed to perform a pure harmonic motion.
8) 16 2 Basic Analytical Tools for the Design of Resonant Vibration Transducers where Z is the amplitude of the relative oscillation and ' the phase between the excitation and the oscillation of the mass. By substituting Eq. 8 into Eq. k m! 2 Y m! 2 r/ 2 2 r d! D : m! 9) For the absolute motion x the steady–state amplitude and phase are (solution of Eq. d / 2 m! k m! 1 md ! 10) The curves are plotted in Fig. 2. In spite of the relative motion, the natural frequency of the absolute motion decreases with increasing damping.
34) The magnitude and phase response of the subsystems and the overall system for system with a resonance frequency of 100 Hz are shown in Fig. 10. The dashed curves indicate the influence of the inductance. In the resonance frequency range there is nearly no influence of the inductance observable. A block diagram of the underlying simulation model implemented in Matlab/Simulink® is shown in Fig. 11. 31) shows that the electromagnetic transduction mechanism can be represented by a dissipative velocity proportional damping element.