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开 本: 16开纸 张: 胶版纸包 装: 平装是否套装: 否国际标准书号ISBN: 9787030413222
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《轻质夹层板结构的声振耦合理论（英文版）》涉及多个学科领域，面较广，所以读者群面也较大，可作为面向结构振动和声学工程专业的高年级学生教学用书和参考书，也可供相关专业的研究人员、工程技术人员参考。
内容简介
《轻质夹层板结构的声振耦合理论（英文版）》的内容主要包括：第一部分，双板空腔结构声振耦合特性理论与实验研究，主要针对高速机车、大型客机及高档居民楼上所采用的双层玻璃窗及双层壳体结构的声振耦合特性开展理论与实验研究；第二部分，外部流场作用下板壳结构声振耦合特性理论研究，重点考虑了飞机在巡航飞行状态时外部平均流对飞机喷气发动机产生的噪声从舱外传入舱内的物理过程；第三部分，正交加筋夹层板结构声振耦合特性理论研究，重点分析讨论了水面舰艇和潜水艇外壳结构经常使用的正交加筋夹层板结构的声辐射特性和结构传声特性；第四部分，填充吸声材料夹层板结构声振耦合特性研究及优化设计，主要理论研究了航空航天飞行器中常用到的层芯空腔填充多孔纤维吸声材料的加筋夹层板结构的声振耦合特性及其结构优化设计；第五部分，研究展望，结合国家重大项目发展需求，展望了复杂周期加筋板壳结构在外部声场及流场作用下的声振耦合特性未来的研究趋势，提出了值得进一步深入研究的几个问题。
目 录
1 Transmission of Sound Through Finite Multiple-Panel Partition
1.1 Simply Supported Finite Double-Panel Partitions
1.1.1 Introduction
1.1.2 Vibroacoustic Theoretical Modeling
1.1.3 Mathematic Formulation and Solution
1.1.4 Convergence Check for Numerical Results
1.1.5 Model Validation
1.1.6 Effects of Air Cavity Thickness
1.1.7 Effects of Panel Dimensions
1.1.8 Effects of Incident Elevation Angle and Azimuth Angle
1.1.9 Conclusions
1.2 Clamped Finite Double-Panel Partitions
1.2.1 Introduction
1.2.2 Modeling of the Vibroacoustic Coupled System
1.2.3 Model Validation
1.2.4 Finite Versus Infinite Double-Panel Partition
1.2.5 Effects of Panel Thickness on STL
1.2.6 Effects of Air Cavity Thickness on STL
1.2.7 Effects of Incident Angles on STL
1.2.8 Conclusions
1.2.9 Sound Transmission Measurements
1.2.10 Relationships Between Clamped and Simply Supported Boundary Conditions
1.2.11 Conclusions
1.3 Clamped Finite Triple-Panel Partitions
1.3.1 Introduction
1.3.2 Dynamic Structural Acoustic Formulation
1.3.3 The Principle of Virtual Work
1.3.4 Determination of Modal Coefficients
1.3.5 Sound Transmission Loss
1.3.6 Model Validation
1.3.7 Physical Interpretation of STL Dips
1.3.8 Comparison Among Single-, Double-, and Triple-Panel Partitions with Equivalent Total Mass
1.3.9 Asymptotic Variation of STL Versus Frequency Curve from Finite to Infinite System
1.3.10 Effects of Panel Thickness
1.3.11 Effects of Air Cavity Depth
1.3.12 Concluding Remarks
Appendices
Appendix A
Appendix B
References
2 Vibroacoustics of Uniform Structures in Mean Flow
2.1 Finite Single-Leaf Aeroelastic Plate
2.1.1 Introduction
2.1.2 Modeling of Aeroelastic Coupled System
2.1.3 Effects of Mean Flow in Incident Field
2.1.4 Effects of Mean Flow in Transmitted Field
2.1.5 Effects of Incident Elevation Angle in the Presence of Mean Flow on Both Incident Side and Transmitted Side
2.1.6 Conclusions
2.2 Infinite Double-Leaf Aeroelastic Plates
2.2.1 Introduction
2.2.2 Statement of the Problem
2.2.3 Formulation of Plate Dynamics
2.2.4 Consideration of Fluid-Structure Coupling
2.2.5 Definition of Sound Transmission Loss
2.2.6 Characteristic Impedance of an Infinite Plate
2.2.7 Physical Interpretation for the Appearance of STL Peaks and Dips
2.2.8 Effects of Mach Number
2.2.9 Effects of Elevation Angle
2.2.10 Effects of Azimuth Angle
2.2.11 Effects of Panel Curvature and Cabin Internal Pressurization
2.2.12 Conclusions
2.3 Double-Leaf Panel Filled with Porous Materials
2.3.1 Introduction
2.3.2 Problem Description
2.3.3 Theoretical Model
2.3.4 Validation of Theoretical Model
2.3.5 Influence of Porous Material and the Faceplates
2.3.6 Influence of Porous Material Layer Thickness
2.3.7 Influence of External Mean Flow
2.3.8 Influence of Incident Sound Elevation Angle
2.3.9 Influence of Sound Incident Azimuth Angle
2.3.10 Conclusion
Appendix
Mass-Air-Mass Resonance
Standing-Wave Attenuation
Standing-Wave Resonance
Coincidence Resonance
References
3 Vibroacoustics of Stiffened Structures in Mean Flow
3.1 Noise Radiation from Orthogonally Rib-Stiffened Plates
3.1.1 Introduction
3.1.2 Theoretical Formulation
3.1.3 Effect of Mach Number
3.1.4 Effect of Incidence Angle
3.1.5 Effect of Periodic Spacings
3.1.6 Concluding Remarks
3.2 Transmission Loss of Orthogonally Rib-Stiffened Plates
3.2.1 Introduction
3.2.2 Theoretical Formulation
3.2.3 Model Validation
3.2.4 Effects of Mach Number of Mean Flow
3.2.5 Effects of Rib-Stiffener Spacings
3.2.6 Effects of Rib-Stiffener Thickness and Height
3.2.7 Effects of Elevation and Azimuth Angles of Incident Sound
3.2.8 Conclusions
Appendices
Appendix A
Appendix B
References
4 Sound Transmission Across Sandwich Structures with Corrugated Cores
4.1 Introduction
4.2 Development of Theoretical Model
4.3 Effects of Core Topology on Sound Transmission Across the Sandwich Structure
4.4 Physical Interpretation for the Existence of Peaks and Dips on STL Curves
4.5 Optimal Design for Combined Sound Insulation and Structural Load Capacity
4.6 Conclusion
References
5 Sound Radiation, Transmission of Orthogonally Rib-Stiffened Sandwich Structures
5.1 Sound Radiation of Sandwich Structures
5.1.1 Introduction
5.1.2 Theoretical Modeling of Structural Dynamic Responses
5.1.3 Solutions
5.1.4 Far-Field Radiated Sound Pressure
5.1.5 Validation of Theoretical Modeling
5.1.6 Influences of Inertial Effects Arising from Rib-Stiffener Mass
5.1.7 Influence of Excitation Position
5.1.8 Influence of Rib-Stiffener Spacings
5.1.9 Conclusions
5.2 Sound Transmission Through Sandwich Structures
5.2.1 Introduction
5.2.2 Analytic Formulation of Panel Vibration and Sound Transmission
5.2.3 The Acoustic Pressure and Continuity Condition
5.2.4 Solution of the Formulations with the Virtual Work Principle
5.2.5 Virtual Work of Panel Elements
5.2.6 Virtual Work of x-Wise Rib-Stiffeners
5.2.7 Virtual Work of y-Wise Rib-Stiffeners
5.2.8 Combination of Equations
5.2.9 Definition of Sound Transmission Loss
5.2.10 Convergence Check for Space-Harmonic Series Solution .
5.2.11 Validation of the Analytic Model
5.2.12 Influence of Sound Incident Angles
5.2.13 Influence of Inertial Effects Arising from Rib-Stiffener Mass
5.2.14 Influence of Rib-Stiffener Spacings
5.2.15 Influence of Airborne and Structure-Borne Paths
5.2.16 Conclusions
Appendices
Appendix A
Appendix B
References
6 Sound Propagation in Rib-Stiffened Sandwich Structures with Cavity Absorption
6.1 Sound Radiation of Absorptive Sandwich Structures
6.1.1 Introduction
6.1.2 Structural Dynamic Responses to Time-Harmonic Point Force
6.1.3 The Acoustic Pressure and Fluid-Structure Coupling
6.1.4 Far-Field Sound-Radiated Pressure
6.1.5 Convergence Check for Numerical Solution
6.1.6 Validation of Theoretical Modeling
6.1.7 Influence of Air-Structure Coupling Effect
6.1.8 Influence of Fibrous Sound Absorptive Filling Material
6.1.9 Conclusions
6.2 Sound Transmission Through Absorptive Sandwich Structure
6.2.1 Introduction
6.2.2 Analytic Formulation of Panel Vibration and Sound Transmission
6.2.3 Application of the Periodicity of Structures
6.2.4 Solution by Employing the Virtual Work Principle
6.2.5 Model Validation
6.2.6 Effects of Fluid-Structure Coupling on Sound Transmission
6.2.7 Sound Transmission Loss Combined with Bending Stiffness and Structure Mass: Optimal Design of Sandwich
6.2.8 Conclusions
Appendices
Appendix A
Appendix B
Appendix C
References
1.1 Simply Supported Finite Double-Panel Partitions
1.1.1 Introduction
1.1.2 Vibroacoustic Theoretical Modeling
1.1.3 Mathematic Formulation and Solution
1.1.4 Convergence Check for Numerical Results
1.1.5 Model Validation
1.1.6 Effects of Air Cavity Thickness
1.1.7 Effects of Panel Dimensions
1.1.8 Effects of Incident Elevation Angle and Azimuth Angle
1.1.9 Conclusions
1.2 Clamped Finite Double-Panel Partitions
1.2.1 Introduction
1.2.2 Modeling of the Vibroacoustic Coupled System
1.2.3 Model Validation
1.2.4 Finite Versus Infinite Double-Panel Partition
1.2.5 Effects of Panel Thickness on STL
1.2.6 Effects of Air Cavity Thickness on STL
1.2.7 Effects of Incident Angles on STL
1.2.8 Conclusions
1.2.9 Sound Transmission Measurements
1.2.10 Relationships Between Clamped and Simply Supported Boundary Conditions
1.2.11 Conclusions
1.3 Clamped Finite Triple-Panel Partitions
1.3.1 Introduction
1.3.2 Dynamic Structural Acoustic Formulation
1.3.3 The Principle of Virtual Work
1.3.4 Determination of Modal Coefficients
1.3.5 Sound Transmission Loss
1.3.6 Model Validation
1.3.7 Physical Interpretation of STL Dips
1.3.8 Comparison Among Single-, Double-, and Triple-Panel Partitions with Equivalent Total Mass
1.3.9 Asymptotic Variation of STL Versus Frequency Curve from Finite to Infinite System
1.3.10 Effects of Panel Thickness
1.3.11 Effects of Air Cavity Depth
1.3.12 Concluding Remarks
Appendices
Appendix A
Appendix B
References
2 Vibroacoustics of Uniform Structures in Mean Flow
2.1 Finite Single-Leaf Aeroelastic Plate
2.1.1 Introduction
2.1.2 Modeling of Aeroelastic Coupled System
2.1.3 Effects of Mean Flow in Incident Field
2.1.4 Effects of Mean Flow in Transmitted Field
2.1.5 Effects of Incident Elevation Angle in the Presence of Mean Flow on Both Incident Side and Transmitted Side
2.1.6 Conclusions
2.2 Infinite Double-Leaf Aeroelastic Plates
2.2.1 Introduction
2.2.2 Statement of the Problem
2.2.3 Formulation of Plate Dynamics
2.2.4 Consideration of Fluid-Structure Coupling
2.2.5 Definition of Sound Transmission Loss
2.2.6 Characteristic Impedance of an Infinite Plate
2.2.7 Physical Interpretation for the Appearance of STL Peaks and Dips
2.2.8 Effects of Mach Number
2.2.9 Effects of Elevation Angle
2.2.10 Effects of Azimuth Angle
2.2.11 Effects of Panel Curvature and Cabin Internal Pressurization
2.2.12 Conclusions
2.3 Double-Leaf Panel Filled with Porous Materials
2.3.1 Introduction
2.3.2 Problem Description
2.3.3 Theoretical Model
2.3.4 Validation of Theoretical Model
2.3.5 Influence of Porous Material and the Faceplates
2.3.6 Influence of Porous Material Layer Thickness
2.3.7 Influence of External Mean Flow
2.3.8 Influence of Incident Sound Elevation Angle
2.3.9 Influence of Sound Incident Azimuth Angle
2.3.10 Conclusion
Appendix
Mass-Air-Mass Resonance
Standing-Wave Attenuation
Standing-Wave Resonance
Coincidence Resonance
References
3 Vibroacoustics of Stiffened Structures in Mean Flow
3.1 Noise Radiation from Orthogonally Rib-Stiffened Plates
3.1.1 Introduction
3.1.2 Theoretical Formulation
3.1.3 Effect of Mach Number
3.1.4 Effect of Incidence Angle
3.1.5 Effect of Periodic Spacings
3.1.6 Concluding Remarks
3.2 Transmission Loss of Orthogonally Rib-Stiffened Plates
3.2.1 Introduction
3.2.2 Theoretical Formulation
3.2.3 Model Validation
3.2.4 Effects of Mach Number of Mean Flow
3.2.5 Effects of Rib-Stiffener Spacings
3.2.6 Effects of Rib-Stiffener Thickness and Height
3.2.7 Effects of Elevation and Azimuth Angles of Incident Sound
3.2.8 Conclusions
Appendices
Appendix A
Appendix B
References
4 Sound Transmission Across Sandwich Structures with Corrugated Cores
4.1 Introduction
4.2 Development of Theoretical Model
4.3 Effects of Core Topology on Sound Transmission Across the Sandwich Structure
4.4 Physical Interpretation for the Existence of Peaks and Dips on STL Curves
4.5 Optimal Design for Combined Sound Insulation and Structural Load Capacity
4.6 Conclusion
References
5 Sound Radiation, Transmission of Orthogonally Rib-Stiffened Sandwich Structures
5.1 Sound Radiation of Sandwich Structures
5.1.1 Introduction
5.1.2 Theoretical Modeling of Structural Dynamic Responses
5.1.3 Solutions
5.1.4 Far-Field Radiated Sound Pressure
5.1.5 Validation of Theoretical Modeling
5.1.6 Influences of Inertial Effects Arising from Rib-Stiffener Mass
5.1.7 Influence of Excitation Position
5.1.8 Influence of Rib-Stiffener Spacings
5.1.9 Conclusions
5.2 Sound Transmission Through Sandwich Structures
5.2.1 Introduction
5.2.2 Analytic Formulation of Panel Vibration and Sound Transmission
5.2.3 The Acoustic Pressure and Continuity Condition
5.2.4 Solution of the Formulations with the Virtual Work Principle
5.2.5 Virtual Work of Panel Elements
5.2.6 Virtual Work of x-Wise Rib-Stiffeners
5.2.7 Virtual Work of y-Wise Rib-Stiffeners
5.2.8 Combination of Equations
5.2.9 Definition of Sound Transmission Loss
5.2.10 Convergence Check for Space-Harmonic Series Solution .
5.2.11 Validation of the Analytic Model
5.2.12 Influence of Sound Incident Angles
5.2.13 Influence of Inertial Effects Arising from Rib-Stiffener Mass
5.2.14 Influence of Rib-Stiffener Spacings
5.2.15 Influence of Airborne and Structure-Borne Paths
5.2.16 Conclusions
Appendices
Appendix A
Appendix B
References
6 Sound Propagation in Rib-Stiffened Sandwich Structures with Cavity Absorption
6.1 Sound Radiation of Absorptive Sandwich Structures
6.1.1 Introduction
6.1.2 Structural Dynamic Responses to Time-Harmonic Point Force
6.1.3 The Acoustic Pressure and Fluid-Structure Coupling
6.1.4 Far-Field Sound-Radiated Pressure
6.1.5 Convergence Check for Numerical Solution
6.1.6 Validation of Theoretical Modeling
6.1.7 Influence of Air-Structure Coupling Effect
6.1.8 Influence of Fibrous Sound Absorptive Filling Material
6.1.9 Conclusions
6.2 Sound Transmission Through Absorptive Sandwich Structure
6.2.1 Introduction
6.2.2 Analytic Formulation of Panel Vibration and Sound Transmission
6.2.3 Application of the Periodicity of Structures
6.2.4 Solution by Employing the Virtual Work Principle
6.2.5 Model Validation
6.2.6 Effects of Fluid-Structure Coupling on Sound Transmission
6.2.7 Sound Transmission Loss Combined with Bending Stiffness and Structure Mass: Optimal Design of Sandwich
6.2.8 Conclusions
Appendices
Appendix A
Appendix B
Appendix C
References
前 言
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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.
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
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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