Vibrations and Impedances of Rectangular Plates with Free Boundaries

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T07 RS03 Structural acoustics and vibration. T07 RS05 Fatigue, fracture and joint interfaces. T10 RS04 Signal processing in acoustics and vibration. T07 RS02 Vibration and control of nonlinear mechanical systems. T02 SS01 Actuators and sensors for active control. T03 SS01 Acoustic simulation, test and control in spacecraft.

T06 SS04 Advances in machinery noise and vibration control.

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T01 RS02 Measurement techniques and sensors. T10 RS01 Signal processing techniques for acoustic array systems and inverse problems. T02 RS01 Active control of sound and vibration. T14 SS04 Physical modeling of musical instruments and singing voice. T14 SS01 Vibroacoustics of musical instruments. Simulation of a damped nonlinear beam based on modal decomposition and Volterra series. T12 SS02 Ship and harbour noise and vibration. T14 SS02 Tools for musical instrument design and making. T10 RS02 Fault diagnosis and prognosis. T07 RS06 Optimal design and uncertainty quantification.

Vibrations and Waves in Continuous Mechanical Systems

T01 SS01 Sound and vibration measurements and analysis. T11 SS03 Measurement and prediction of sound insulation. T08 SS01 Passive sound absorbing and insulating materials. T05 SS02 Nonlinear acoustics and vibrations. T05 SS03 Sound propagation in curvilinear spacetime. T08 SS04 Characterization of acoustical materials. T12 SS01 Technology for underwater sound measurement and monitoring. T02 SS02 Algorithms for active control.

T05 RS01 Ultrasound and Ultrasonic measurements techniques and sensors. T09 RS01 Psychological and physiological acoustics. T06 SS03 Noise and vibration in small, medium and large industries. T05 SS01 Wave propagation in complex media. T03 SS04 Aircraft cabin noise and vibration control. T14 SS03 Biomechanical control of musical instrument. T01 RS04 Instrumentation for sound and vibration measurements and analyses. T01 RS01 Acoustic imaging and acoustic detection. Broadband forbidden transmission by multiple CPA-based detuned Helmholtz resonators.

Free Vibration Characteristics of Thermally Loaded Rectangular Plates

Branco Fernando G. T13 SS01 Education in acoustics: catching attention or teaching in minutes using traditional or nontraditional media and methods.

January ; 1 : 22— A general formulation of the sound radiation from fluid-loaded rectangular baffled plates with arbitrary boundary conditions has been developed by Berry et al. JASA, Vol. In this paper, an extension of this formulation to inviscid, uniform subsonic flow is considered. The analysis is based on a variational formulation for the transverse vibrations of the plate and the use of the extended, to uniformly moving media, form of the Helmholtz integral equation.

The formulation shows explicitly the effect of the flow in terms of added mass, and radiation resistance.

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Furthermore, it avoids the difficult problem of integration in the complex domain, typical of the wavenumber transform approaches to fluid-loading problems. Comparison of the acoustic radiation impedance with existing studies supports the validity of the approach. The details of the formulation and its numerical implementation is exposed and a discussion of the flow effects on the radiation impedance of a rectangular piston is presented. It is shown that subsonic mean flow increases the modal radiation resistance at low frequencies and affects added mass more strongly than it affects radiation resistance.

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The panels are excited by a 1N harmonic point load at the central node on the free edge opposite to the clamped edge and the SPL is measured at a distance of 0. With similar considerations, the SPL values are computed using the present numerical model and validated by comparing with those experimentally obtained data. The comparison of the experimental and numerical results for SPL of the vibrating flat panel with M1 and M2 material properties are shown in Figure 6 a and b , respectively. It is observed that in both the cases the present numerical values of SPL follow closely the experimental results including the occurrence of peaks and depressions up to the excitation frequency of Hz, after which slight deviation is noticed.

The reason for the deviation may be due to the limitations in applying displacement boundary condition on the structure and the absence of anechoic chamber during experimentation. The coincidence frequencies in Hz for each thickness value are Therefore, a frequency range of , Hz is considered to observe the sonic and subsonic behaviour of plates. The variation of the radiation efficiency and the radiated sound power with the excitation frequency for different values of thickness ratio is shown in Figure 7 a and b , respectively.

Vibrations of a Rectangular Membrane

It can be observed that the average radiation efficiency increases with increasing thickness ratio. This leads to shifting of natural modes of vibration to lower frequencies and higher coincidence frequencies in the considered frequency range. Also, it is worthy to note that the radiation efficiency exceeds 1 close to the first coincidence frequency and asymptotically decreases to 1 after the second coincidence frequency in most of the cases. The radiated sound power increases with increasing plate thickness ratio.

A similar trend is observed for the sound pressure level in near and far-fields for modes 1,1 and 2,1 of the plates as shown in the SPL directivity plots in Figure 7 c and d , respectively. The plate has the same coincidence frequencies The average sound power level follows an increasing trend with decreasing aspect ratio with the resonance peaks shifting to lower frequencies as shown in Figure 8 b. It is also worthy to note that the radiation efficiency exceeds unity indicating that radiated acoustic power is more than the vibration energy of the plates.

The first coincidence frequency is the same equal to It is interesting to note that the first natural frequencies of the configurations are very close to the first coincidence frequency. It can clearly be observed from Fig. It is can be seen that for every value of modular ratio the curves closely follow each other over the entire frequency range with the peaks and valleys occurring at almost same values of excitation frequency.


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The radiation efficiency crosses unity around the first natural frequency for all configurations of modular ratio and approaches unity after crossing the maximum value of second coincidence frequency. It is well known that, the lay-up scheme of any laminated composite structure significantly governs the stiffness and thus affects the vibration and sound radiation behaviour greatly. The SPL is obtained at a point 1m directly above the excitation location on the plate. It is observed from Figure 10 that the SPL at the field point and the radiated sound power is greatly influenced by the lay-up scheme of the vibrating plate.

It can also be seen that the peaks occur at higher frequencies for cross-ply laminations in comparison to the angle-ply schemes. The stiffness increases as the number of constraints increases or the degree of freedom decreases and this may have a substantial effect on the sound radiation characteristic of the structure. The first and the second coincidence frequencies are The influence of the number of constraints at the support is well reflected in the results.

It is observed that, over low excitation frequency range i. In this section, a case study has been presented to compare the vibro-acoustic behaviour of the laminated flat panel of different composite materials those are widely used in their key areas of application. Four different composite materials namely, graphite-epoxy, boron-epoxy, kevlar-epoxy and glass-epoxy are considered for the present analysis and their properties are listed in Table 7.

For the computation purpose a simply supported rectangular 0. The SPL directivity pattern for modes 1,1 and 2,1 , the radiation efficiency and the radiated sound power level values are computed for various composite materials using the present scheme and shown in Figure 12 a - d , respectively. In general, the RMS values of a vibrating structure are considered to judge its suitability for a particular application.