了得網工業技術_輕質夾層板結構的聲振耦合理論（英文版）

編輯推薦

《輕質夾層板結構的聲振耦合理論（英文版）》涉及多個學科領域，面較廣，所以讀者群面也較大，可作為面向結構振動和聲學工程專業的高年級學生教學用書和參考書，也可供相關專業的研究人員、工程技術人員參考。

內容簡介

《輕質夾層板結構的聲振耦合理論（英文版）》的內容主要包括：第一部分，雙板空腔結構聲振耦合特性理論與實驗研究，主要針對高速機車、大型客機及高檔居民樓上所采用的雙層玻璃窗及雙層殼體結構的聲振耦合特性開展理論與實驗研究；第二部分，外部流場作用下板殼結構聲振耦合特性理論研究，重點考慮了飛機在巡航飛行狀態時外部平均流對飛機噴氣發動機產生的噪聲從艙外傳入艙內的物理過程；第三部分，正交加筋夾層板結構聲振耦合特性理論研究，重點分析討論了水面艦艇和潛水艇外殼結構經常使用的正交加筋夾層板結構的聲輻射特性和結構傳聲特性；第四部分，填充吸聲材料夾層板結構聲振耦合特性研究及優化設計，主要理論研究了航空航天飛行器中常用到的層芯空腔填充多孔纖維吸聲材料的加筋夾層板結構的聲振耦合特性及其結構優化設計；第五部分，研究展望，結合國家重大項目發展需求，展望了復雜周期加筋板殼結構在外部聲場及流場作用下的聲振耦合特性未來的研究趨勢，提出了值得進一步深入研究的幾個問題。

作者簡介

1Transmission of Sound Through Finite Multiple-Panel Partition
1.1Simply Supported Finite Double-Panel Partitions
1.1.1Introduction
1.1.2Vibroacoustic Theoretical Modeling
1.1.3Mathematic Formulation and Solution
1.1.4Convergence Check for Numerical Results
1.1.5Model Validation
1.1.6Effects of Air Cavity Thickness
1.1.7Effects of Panel Dimensions
1.1.8Effects of Incident Elevation Angle and Azimuth Angle
1.1.9Conclusions
1.2Clamped Finite Double-Panel Partitions
1.2.1Introduction
1.2.2Modeling of the Vibroacoustic Coupled System1Transmission of Sound Through Finite Multiple-Panel Partition
1.1Simply Supported Finite Double-Panel Partitions
1.1.1Introduction
1.1.2Vibroacoustic Theoretical Modeling
1.1.3Mathematic Formulation and Solution
1.1.4Convergence Check for Numerical Results
1.1.5Model Validation
1.1.6Effects of Air Cavity Thickness
1.1.7Effects of Panel Dimensions
1.1.8Effects of Incident Elevation Angle and Azimuth Angle
1.1.9Conclusions
1.2Clamped Finite Double-Panel Partitions
1.2.1Introduction
1.2.2Modeling of the Vibroacoustic Coupled System
1.2.3Model Validation
1.2.4Finite Versus Infinite Double-Panel Partition
1.2.5Effects of Panel Thickness on STL
1.2.6Effects of Air Cavity Thickness on STL
1.2.7Effects of Incident Angles on STL
1.2.8Conclusions
1.2.9Sound Transmission Measurements
1.2.10Relationships Between Clamped and Simply Supported Boundary Conditions
1.2.11Conclusions
1.3Clamped Finite Triple-Panel Partitions
1.3.1Introduction
1.3.2Dynamic Structural Acoustic Formulation
1.3.3The Principle of Virtual Work
1.3.4Determination of Modal Coefficients
1.3.5Sound Transmission Loss
1.3.6Model Validation
1.3.7Physical Interpretation of STL Dips
1.3.8Comparison Among Single-, Double-, and Triple-Panel Partitions with Equivalent Total Mass
1.3.9Asymptotic Variation of STL Versus Frequency Curve from Finite to Infinite System
1.3.10Effects of Panel Thickness
1.3.11Effects of Air Cavity Depth
1.3.12Concluding Remarks
Appendices
Appendix A
Appendix B
References
2Vibroacoustics of Uniform Structures in Mean Flow
2.1Finite Single-Leaf Aeroelastic Plate
2.1.1Introduction
2.1.2Modeling of Aeroelastic Coupled System
2.1.3Effects of Mean Flow in Incident Field
2.1.4Effects of Mean Flow in Transmitted Field
2.1.5Effects of Incident Elevation Angle in the Presence of Mean Flow on Both Incident Side and Transmitted Side
2.1.6Conclusions
2.2Infinite Double-Leaf Aeroelastic Plates
2.2.1Introduction
2.2.2Statement of the Problem
2.2.3Formulation of Plate Dynamics
2.2.4Consideration of Fluid-Structure Coupling
2.2.5Definition of Sound Transmission Loss
2.2.6Characteristic Impedance of an Infinite Plate
2.2.7Physical Interpretation for the Appearance of STL Peaks and Dips
2.2.8Effects of Mach Number
2.2.9Effects of Elevation Angle
2.2.10Effects of Azimuth Angle
2.2.11Effects of Panel Curvature and Cabin Internal Pressurization
2.2.12Conclusions
2.3Double-Leaf Panel Filled with Porous Materials
2.3.1Introduction
2.3.2Problem Description
2.3.3Theoretical Model
2.3.4Validation of Theoretical Model
2.3.5Influence of Porous Material and the Faceplates
2.3.6Influence of Porous Material Layer Thickness
2.3.7Influence of External Mean Flow
2.3.8Influence of Incident Sound Elevation Angle
2.3.9Influence of Sound Incident Azimuth Angle
2.3.10Conclusion
Appendix
Mass-Air-Mass Resonance
Standing-Wave Attenuation
Standing-Wave Resonance
Coincidence Resonance
References
3Vibroacoustics of Stiffened Structures in Mean Flow
3.1Noise Radiation from Orthogonally Rib-Stiffened Plates
3.1.1Introduction
3.1.2Theoretical Formulation
3.1.3Effect of Mach Number
3.1.4Effect of Incidence Angle
3.1.5Effect of Periodic Spacings
3.1.6Concluding Remarks
3.2Transmission Loss of Orthogonally Rib-Stiffened Plates
3.2.1Introduction
3.2.2Theoretical Formulation
3.2.3Model Validation
3.2.4Effects of Mach Number of Mean Flow
3.2.5Effects of Rib-Stiffener Spacings
3.2.6Effects of Rib-Stiffener Thickness and Height
3.2.7Effects of Elevation and Azimuth Angles of Incident Sound
3.2.8Conclusions
Appendices
Appendix A
Appendix B
References
4Sound Transmission Across Sandwich Structures with Corrugated Cores
4.1Introduction
4.2Development of Theoretical Model
4.3Effects of Core Topology on Sound Transmission Across the Sandwich Structure
4.4Physical Interpretation for the Existence of Peaks and Dips on STL Curves
4.5Optimal Design for Combined Sound Insulation and Structural Load Capacity
4.6Conclusion
References
5Sound Radiation, Transmission of Orthogonally Rib-Stiffened Sandwich Structures
5.1Sound Radiation of Sandwich Structures
5.1.1Introduction
5.1.2Theoretical Modeling of Structural Dynamic Responses
5.1.3Solutions
5.1.4Far-Field Radiated Sound Pressure
5.1.5Validation of Theoretical Modeling
5.1.6Influences of Inertial Effects Arising from Rib-Stiffener Mass
5.1.7Influence of Excitation Position
5.1.8Influence of Rib-Stiffener Spacings
5.1.9Conclusions
5.2Sound Transmission Through Sandwich Structures
5.2.1Introduction
5.2.2Analytic Formulation of Panel Vibration and Sound Transmission
5.2.3The Acoustic Pressure and Continuity Condition
5.2.4Solution of the Formulations with the Virtual Work Principle
5.2.5Virtual Work of Panel Elements
5.2.6Virtual Work of x-Wise Rib-Stiffeners
5.2.7Virtual Work of y-Wise Rib-Stiffeners
5.2.8Combination of Equations
5.2.9Definition of Sound Transmission Loss
5.2.10Convergence Check for Space-Harmonic Series Solution .
5.2.11Validation of the Analytic Model
5.2.12Influence of Sound Incident Angles
5.2.13Influence of Inertial Effects Arising from Rib-Stiffener Mass
5.2.14Influence of Rib-Stiffener Spacings
5.2.15Influence of Airborne and Structure-Borne Paths
5.2.16Conclusions
Appendices
Appendix A
Appendix B
References
6Sound Propagation in Rib-Stiffened Sandwich Structures with Cavity Absorption
6.1Sound Radiation of Absorptive Sandwich Structures
6.1.1Introduction
6.1.2Structural Dynamic Responses to Time-Harmonic Point Force
6.1.3The Acoustic Pressure and Fluid-Structure Coupling
6.1.4Far-Field Sound-Radiated Pressure
6.1.5Convergence Check for Numerical Solution
6.1.6Validation of Theoretical Modeling
6.1.7Influence of Air-Structure Coupling Effect
6.1.8Influence of Fibrous Sound Absorptive Filling Material
6.1.9Conclusions
6.2Sound Transmission Through Absorptive Sandwich Structure
6.2.1Introduction
6.2.2Analytic Formulation of Panel Vibration and Sound Transmission
6.2.3Application of the Periodicity of Structures
6.2.4Solution by Employing the Virtual Work Principle
6.2.5Model Validation
6.2.6Effects of Fluid-Structure Coupling on Sound Transmission
6.2.7Sound Transmission Loss Combined with Bending Stiffness and Structure Mass: Optimal Design of Sandwich
6.2.8Conclusions
Appendices
Appendix A
Appendix B
Appendix C
References

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Chapter 1 Transmission of Sound Through Finite Multiple-Panel Partition
Abstract This chapter is organized as three parts: in the .rst part， the vibroacoustic performance of a rectangular double-panel partition with enclosed air cavity and simply mounted on an in.nite acoustic rigid baf.e is investigated analytically. The sound velocity potential method rather than the commonly used cavity modal function method is employed， which possesses good expandability and has signif-icant implications for further vibroacoustic investigations. The simply supported boundary condition is accounted for by using the method of modal function， and double Fourier series solutions are obtained to characterize the vibroacoustic behav-iors of the structure. Results for sound transmission loss (STL)， panel vibration level， and sound pressure level are presented to explore the physical mechanisms of sound energy penetration across the .nite double-panel partition. Speci.cally， focus is placed upon the in.uence of several key system parameters on sound transmission， including the thickness of air cavity， structural dimensions， and the elevation angle and azimuth angle of the incidence sound. Further extensions of the sound velocity potential method to typical framed double-panel structures are also proposed.
In the second part， the air-borne sound insulation performance of a rectangular double-panel partition clamp mounted on an in.nite acoustic rigid baf.e is inves-tigated both analytically and experimentally， and compared with that of a simply supported one. With the clamped (or simply supported) boundary accounted for by using the method of modal function， a double series solution for the sound transmission loss (STL) of the structure is obtained by employing the weighted residual (Galerkin) method. Experimental measurements with Al double-panel partitions having air cavity are subsequently carried out to validate the theoretical model for both types of the boundary condition， and good overall agreement is achieved. A consistency check of the two different models (based separately on clamped modal function and simply supported modal function) is performed by extending the panel dimensions to in.nite where no boundaries exist. The signi.cant discrepancies between the two different boundary conditions are demonstrated in terms of the STL versus frequency plots as well as the panel de.ection mode shapes.Chapter 1 Transmission of Sound Through Finite Multiple-Panel Partition
Abstract This chapter is organized as three parts: in the .rst part， the vibroacoustic performance of a rectangular double-panel partition with enclosed air cavity and simply mounted on an in.nite acoustic rigid baf.e is investigated analytically. The sound velocity potential method rather than the commonly used cavity modal function method is employed， which possesses good expandability and has signif-icant implications for further vibroacoustic investigations. The simply supported boundary condition is accounted for by using the method of modal function， and double Fourier series solutions are obtained to characterize the vibroacoustic behav-iors of the structure. Results for sound transmission loss (STL)， panel vibration level， and sound pressure level are presented to explore the physical mechanisms of sound energy penetration across the .nite double-panel partition. Speci.cally， focus is placed upon the in.uence of several key system parameters on sound transmission， including the thickness of air cavity， structural dimensions， and the elevation angle and azimuth angle of the incidence sound. Further extensions of the sound velocity potential method to typical framed double-panel structures are also proposed.
In the second part， the air-borne sound insulation performance of a rectangular double-panel partition clamp mounted on an in.nite acoustic rigid baf.e is inves-tigated both analytically and experimentally， and compared with that of a simply supported one. With the clamped (or simply supported) boundary accounted for by using the method of modal function， a double series solution for the sound transmission loss (STL) of the structure is obtained by employing the weighted residual (Galerkin) method. Experimental measurements with Al double-panel partitions having air cavity are subsequently carried out to validate the theoretical model for both types of the boundary condition， and good overall agreement is achieved. A consistency check of the two different models (based separately on clamped modal function and simply supported modal function) is performed by extending the panel dimensions to in.nite where no boundaries exist. The signi.cant discrepancies between the two different boundary conditions are demonstrated in terms of the STL versus frequency plots as well as the panel de.ection mode shapes.
In the third part， an analytical model for sound transmission through a clamped triple-panel partition of .nite extent and separated by two impervious air cavities is formulated. The solution derived from the model takes the form of that for a clamp-supported rectangular plate. A set of modal functions (or more strictly speaking， the basic functions) are employed to account for the clamped boundary conditions， and the application of the virtual work principle leads to a set of simultaneous algebraic equations for determining the unknown modal coef.cients. The sound transmission loss (STL) of the triple-panel partition as a function of excitation frequency is calculated and compared with that of a double-panel partition. The model predictions are then used to explore the physical mechanisms associated with the various dips on the STL versus frequency curve， including the equivalent “mass-spring” resonance， the standing-wave resonance， and the panel modal resonance. The asymptotic variation of the solution from a .nite-sized partition to an in.nitely large partition is illustrated in such a way as to demonstrate the in.uence of the boundary conditions on the soundproo.ng capability of the partition. In general， a triple-panel partition outperforms a double-panel partition in insulating the incident sound， and the relatively large number of system parameters pertinent to the triple-panel partition in comparison with that of the double-panel partition offers more design space for the former to tailor its noise reduction performance.
1.1 Simply Supported Finite Double-Panel Partitions
1.1.1 Introduction
Double-leaf partition structures have found increasingly wide applications in noise control engineering due to their superior sound insulation capability over single-leaf con.gurations. Typical examples include transportation vehicles， grazing windows and partition walls in buildings， aircraft fuselage shells， and so on [1–12].
Considerable efforts have been devoted to understanding and predicting the transmission of sound across single-leaf [13–15] and double-leaf [16–29] partitions. In fact， research about the former is often a prerequisite for studying the latter. For instance， Lomas [14] developed Green function solution for the steady-state vibration of an elastically supported rectangular plate coupled to a semi-in.nite acoustic medium. An important feature of the investigation is the treatment of the elastic support boundary condition which was taken into account by assuming the rotational motion along the boundary control

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