齿形链传动系统振动声辐射研究
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摘要
齿形链传动是机械传动领域应用较为广泛的动力和运动传递装置，具有效率高、噪声小、可靠性高、运动精度高等特点，主要应用于高速、重载、低噪声和大中心距的传动工况下。但在齿形链传动过程中，链条围啮链轮时形成的多边形效应激励以及链节以一定相对速度啮入链轮产生的啮合冲击激励，是齿形链传动系统产生振动和噪声的根本原因，并随着齿形链传动向着高速、重载和变速变载的方向发展，以及对传动系统传递功率的不断增加，使得齿形链传动系统的振动和噪声问题变得尤为突出。这种振动和噪声问题客观上反映了传动系统的工作状态，也影响了其工作的可靠性和稳定性，在一定程度上限制了齿形链的推广和应用。因此，研究齿形链传动系统的振动和噪声对于提高齿形链传动装置的承载能力、减小振动和噪声、提高各种性能指标都具有十分重要的工程应用意义和理论研究价值。
本文对某轻型8×8轮式全地形车齿形链传动系统的振动和噪声进行了研究，分析齿形链与链轮啮合过程中产生振动和噪声的啮合冲击激励和多边形效应激励，建立齿形链传动系统的声学冲击模型，定量预估齿形链传动系统的冲击噪声；并进行齿形链传动系统的多体动力学动态激励仿真、有限元模态分析、实验模态分析、振动响应分析、声学边界元噪声辐射分析以及声强测试和噪声源识别等方面的研究。本文主要研究内容如下：
(1)分析引起齿形链传动系统振动和噪声的最主要两个动态激励：啮合冲击激励和多边形效应激励。计算在齿形链传动过程中链节与链轮啮合瞬间，链板以一定的相对速度与链轮啮合产生的冲击速度，并从齿形链传动特有的多边形效应出发，分析齿形链线速度、从动链轮角速度和附加动载荷的变化规律，从而从运动学角度得出齿形链传动运行不平稳，产生振动和噪声的原因。
(2)在分析标准齿形链和链轮的相关标准规范的基础上，从两圆柱冲击理论和声学理论的角度来进行齿形链传动系统的振动和噪声研究，建立齿形链传动系统的声学冲击模型，分析链节和链轮啮合时弹性变形产生的冲击力、冲击加速度、冲击作用时间和冲击速度的大小，推导出柱坐标下以速度势为参量小振幅声波传播的波动方程，给出链节和链轮冲击所产生的声压和声功率的计算表达式，并且进行齿形链传动系统冲击噪声实例计算。
(3)基于多体动力学理论以及接触分析理论，建立齿形链传动系统的多刚体动力学理论模型，并在分析齿形链和链轮结构形式以及齿形链传动系统装配体结构特征基础上，建立齿形链传动系统的虚拟样机模型。通过仿真分析在啮合冲击激励和多边形效应激励影响下，齿形链和链轮的啮合接触力、链轮扭转振动以及齿形链的横向振动与纵向振动的特性，得到链轮与齿形链的啮合接触力仿真数据，为齿形链传动系统动态响应分析提供准确可靠的激励载荷。
(4)从结构动力学和模态分析理论出发，建立齿形链传动系统装配体的有限元模型，进行齿形链传动系统自由状态的模态分析和有预应力的模态分析，分析整个齿形链传动系统的固有特性，考察预应力对系统结构的应力分布、强度、刚度以及固有频率和固有振型特性的影响。并采用敲击法进行实验模态测试分析，识别出齿形链传动系统的模态参数，验证有限元模型和模态分析计算的正确性，能否反映系统结构的固有特性。
(5)在分析振动响应分析理论及其求解方法基础上，将齿形链传动系统啮合动态激励仿真得到的时域啮合接触力通过FFT快速傅利叶变换，转化为频域载荷，使其作为激励边界载荷进行预应力有限元振动响应特性分析。然后将振动响应分析得到的结构体网格上的位移响应节点振动信息，通过四节点插值法将其转移到声学面网格上，并将转换后的振动位移定义为边界条件进行声学间接边界元数值计算，得到其外声场场点处声学量，进而进行声场的声学特性分析。
(6)利用声强测量技术对齿形链传动系统进行声强测量和噪声源识别。通过对声强数据的处理与分析得出声功率频谱和等声强线分布图，分析和识别出齿形链传动系统的主要噪声源，确定其噪声源的位置、主要噪声频率成分，为下一步修改齿形链传动系统结构，模型改进和降噪提供依据。
Silent chain drive, a kind of dynamic and motion transmission device which is widelyused in the field of mechanical drive, with the characteristics of high efficiency, little noise,high reliability, high kinematic accuracy and so on, is widely applied to the drivingconditions of high speed, heavy load, low noise and big center distance. As silent chain drivedevelops towards high speed, heavy load and variable speed and load, with the increasedrequirement for higher transmission power of the drive system, the vibration and noiseproblem of silent chain drive system has become especially predominant. Such vibration andnoise problem which objectively reflect the working condition of drive system and influenceits reliability and stability, to some extent, have limited the extension and application of thesilent chain. Therefore, it is extremely important to study vibration and noise of the silentchain drive system.
In this paper, vibration and noise of a certain silent chain drive system that is light8×8wheeled all-terrain vehicle is studied, and the excitation of meshing impact and polygoneffect of vibration and noise produced in the meshing process of silent chain and sprocketare analyzed. The acoustic shock model of silent chain drive system is established, andimpulsive noise of the silent chain drive system is calculated quantitatively. The research ofdynamic incentive simulation of multibody dynamics, finite element modal analysis,experimental modal analysis, dynamic response analysis, noise radiation analysis of acousticboundary element, sound intensity testing and noise source identification of silent chaindrive system are described. The main research contents in this paper are as follows:
(1) The two main dynamic incentives, namely, meshing impact excitation and thepolygon effect, which produce vibration and noise in silent chain drive system, are analyzed.The biggest impact speed, generated in the meshing process of sprocket and chain plate at arelative speed when chain link and sprocket mesh instantly, is calculated. And starting fromthe polygon effect of silent chain drive itself, the change law of silent chain linear velocity,driven sprocket angular speed and additional dynamic load are analyzed, thus, from theperspective of kinematics, the causes of the unstable running, vibration and noise of thesilent chain are obtained.
(2) Based on the analysis of the relevant standards of silent chain and sprocket, from therespective of two cylindrical shock theory and acoustic theory, research on vibration andnoise of the silent chain drive system is carried out. The acoustic impact model of the silentchain drive system is established, and impact force, impact acceleration, impact time and impact velocity produced by elastic deformation when link and sprocket mesh are analyzed.The wave equation for small amplitude wave propagation with velocity potential parameterin cylindrical coordinate is deduced. The calculation expressions of sound pressure andsound power generated when link and sprocket impact are obtained, and an instance ofimpact noise of the silent chain drive system is calculated.
(3) Based on multi-body dynamics theory and the contact analysis theory, the theoreticalmodel of multi-rigid-body dynamics of silent chain drive system is established. And basedon the analysis of the structural style of the silent chain and sprocket and the architecturalfeature of the silent chain drive system assembly, the virtual prototype model of silent chaindrive system is established. Through simulation analysis of the meshing contact force ofsilent chain and sprocket, the torsional vibration of sprockets and the characteristics oftransverse and longitudinal vibration under the influence of the meshing impact and polygoneffect, the simulation data of the meshing contact force of the silent chain is obtained, whichprovides accurate and reliable incentive load for the dynamic response analysis of the silentchain drive system.
(4) From the structural dynamics and modal analysis theory, the finite element model ofthe silent chain drive system assembly is established. The modal analysis of the silent chaindrive system at a free state and finite element modal analysis of the prestressed assembly arecarried out. Then, the intrinsic characteristic of the silent chain drive system is analyzed, andthe effect of the prestress on the stress distribution, strength, stiffness inherent frequency andinherent vibration mode of the system are discussed. And experiment modal test and analysisis carried out by hammering method. The modal parameter of silent chain drive system isobtained. The correctness of finite element modal analysis and calculation is verified and itis discussed that whether the inherent characteristic of system structure can be reflected.
(5) Based on the analysis of harmonic response analysis theory and its solving method,the meshing contact force obtained by mesh dynamic simulation of the silent chaintransmission system is transformed to frequency domain load by FFT(fast fourier transform).The frequency domain load is used as incentive boundary load for the prestress finiteelement harmonic response analysis. And through four node interpolation method, thevibration information of displacement response node in the grid structure obtained byharmonic response analysis is transferred into the acoustic surface mesh. And define thevibration displacement as the boundary condition to carry out the acoustic boundary elementcalculation. The acoustic quantity of field point in the outer sound field is obtained, thus, theanalysis about the acoustic characteristic of the sound field is conducted.
(6) Sound intensity measurement technology is adopted to measure the sound intensityand identify the noise source of the silent chain drive system. Through the processing and analysis of the data of sound intensity, the distribution diagrams of the sound powerspectrum and isacoustic line are obtained. From the diagrams above, the main noise sourceof the silent chain drive system is analyzed and identified, and the location of noise sourceand the main noise frequency components are obtained, which provide a basis for modifyingthe structure of the silent chain drive system, improving the analysis model and reducing thenoise.
本文对某轻型8×8轮式全地形车齿形链传动系统的振动和噪声进行了研究，分析齿形链与链轮啮合过程中产生振动和噪声的啮合冲击激励和多边形效应激励，建立齿形链传动系统的声学冲击模型，定量预估齿形链传动系统的冲击噪声；并进行齿形链传动系统的多体动力学动态激励仿真、有限元模态分析、实验模态分析、振动响应分析、声学边界元噪声辐射分析以及声强测试和噪声源识别等方面的研究。本文主要研究内容如下：
(1)分析引起齿形链传动系统振动和噪声的最主要两个动态激励：啮合冲击激励和多边形效应激励。计算在齿形链传动过程中链节与链轮啮合瞬间，链板以一定的相对速度与链轮啮合产生的冲击速度，并从齿形链传动特有的多边形效应出发，分析齿形链线速度、从动链轮角速度和附加动载荷的变化规律，从而从运动学角度得出齿形链传动运行不平稳，产生振动和噪声的原因。
(2)在分析标准齿形链和链轮的相关标准规范的基础上，从两圆柱冲击理论和声学理论的角度来进行齿形链传动系统的振动和噪声研究，建立齿形链传动系统的声学冲击模型，分析链节和链轮啮合时弹性变形产生的冲击力、冲击加速度、冲击作用时间和冲击速度的大小，推导出柱坐标下以速度势为参量小振幅声波传播的波动方程，给出链节和链轮冲击所产生的声压和声功率的计算表达式，并且进行齿形链传动系统冲击噪声实例计算。
(3)基于多体动力学理论以及接触分析理论，建立齿形链传动系统的多刚体动力学理论模型，并在分析齿形链和链轮结构形式以及齿形链传动系统装配体结构特征基础上，建立齿形链传动系统的虚拟样机模型。通过仿真分析在啮合冲击激励和多边形效应激励影响下，齿形链和链轮的啮合接触力、链轮扭转振动以及齿形链的横向振动与纵向振动的特性，得到链轮与齿形链的啮合接触力仿真数据，为齿形链传动系统动态响应分析提供准确可靠的激励载荷。
(4)从结构动力学和模态分析理论出发，建立齿形链传动系统装配体的有限元模型，进行齿形链传动系统自由状态的模态分析和有预应力的模态分析，分析整个齿形链传动系统的固有特性，考察预应力对系统结构的应力分布、强度、刚度以及固有频率和固有振型特性的影响。并采用敲击法进行实验模态测试分析，识别出齿形链传动系统的模态参数，验证有限元模型和模态分析计算的正确性，能否反映系统结构的固有特性。
(5)在分析振动响应分析理论及其求解方法基础上，将齿形链传动系统啮合动态激励仿真得到的时域啮合接触力通过FFT快速傅利叶变换，转化为频域载荷，使其作为激励边界载荷进行预应力有限元振动响应特性分析。然后将振动响应分析得到的结构体网格上的位移响应节点振动信息，通过四节点插值法将其转移到声学面网格上，并将转换后的振动位移定义为边界条件进行声学间接边界元数值计算，得到其外声场场点处声学量，进而进行声场的声学特性分析。
(6)利用声强测量技术对齿形链传动系统进行声强测量和噪声源识别。通过对声强数据的处理与分析得出声功率频谱和等声强线分布图，分析和识别出齿形链传动系统的主要噪声源，确定其噪声源的位置、主要噪声频率成分，为下一步修改齿形链传动系统结构，模型改进和降噪提供依据。
Silent chain drive, a kind of dynamic and motion transmission device which is widelyused in the field of mechanical drive, with the characteristics of high efficiency, little noise,high reliability, high kinematic accuracy and so on, is widely applied to the drivingconditions of high speed, heavy load, low noise and big center distance. As silent chain drivedevelops towards high speed, heavy load and variable speed and load, with the increasedrequirement for higher transmission power of the drive system, the vibration and noiseproblem of silent chain drive system has become especially predominant. Such vibration andnoise problem which objectively reflect the working condition of drive system and influenceits reliability and stability, to some extent, have limited the extension and application of thesilent chain. Therefore, it is extremely important to study vibration and noise of the silentchain drive system.
In this paper, vibration and noise of a certain silent chain drive system that is light8×8wheeled all-terrain vehicle is studied, and the excitation of meshing impact and polygoneffect of vibration and noise produced in the meshing process of silent chain and sprocketare analyzed. The acoustic shock model of silent chain drive system is established, andimpulsive noise of the silent chain drive system is calculated quantitatively. The research ofdynamic incentive simulation of multibody dynamics, finite element modal analysis,experimental modal analysis, dynamic response analysis, noise radiation analysis of acousticboundary element, sound intensity testing and noise source identification of silent chaindrive system are described. The main research contents in this paper are as follows:
(1) The two main dynamic incentives, namely, meshing impact excitation and thepolygon effect, which produce vibration and noise in silent chain drive system, are analyzed.The biggest impact speed, generated in the meshing process of sprocket and chain plate at arelative speed when chain link and sprocket mesh instantly, is calculated. And starting fromthe polygon effect of silent chain drive itself, the change law of silent chain linear velocity,driven sprocket angular speed and additional dynamic load are analyzed, thus, from theperspective of kinematics, the causes of the unstable running, vibration and noise of thesilent chain are obtained.
(2) Based on the analysis of the relevant standards of silent chain and sprocket, from therespective of two cylindrical shock theory and acoustic theory, research on vibration andnoise of the silent chain drive system is carried out. The acoustic impact model of the silentchain drive system is established, and impact force, impact acceleration, impact time and impact velocity produced by elastic deformation when link and sprocket mesh are analyzed.The wave equation for small amplitude wave propagation with velocity potential parameterin cylindrical coordinate is deduced. The calculation expressions of sound pressure andsound power generated when link and sprocket impact are obtained, and an instance ofimpact noise of the silent chain drive system is calculated.
(3) Based on multi-body dynamics theory and the contact analysis theory, the theoreticalmodel of multi-rigid-body dynamics of silent chain drive system is established. And basedon the analysis of the structural style of the silent chain and sprocket and the architecturalfeature of the silent chain drive system assembly, the virtual prototype model of silent chaindrive system is established. Through simulation analysis of the meshing contact force ofsilent chain and sprocket, the torsional vibration of sprockets and the characteristics oftransverse and longitudinal vibration under the influence of the meshing impact and polygoneffect, the simulation data of the meshing contact force of the silent chain is obtained, whichprovides accurate and reliable incentive load for the dynamic response analysis of the silentchain drive system.
(4) From the structural dynamics and modal analysis theory, the finite element model ofthe silent chain drive system assembly is established. The modal analysis of the silent chaindrive system at a free state and finite element modal analysis of the prestressed assembly arecarried out. Then, the intrinsic characteristic of the silent chain drive system is analyzed, andthe effect of the prestress on the stress distribution, strength, stiffness inherent frequency andinherent vibration mode of the system are discussed. And experiment modal test and analysisis carried out by hammering method. The modal parameter of silent chain drive system isobtained. The correctness of finite element modal analysis and calculation is verified and itis discussed that whether the inherent characteristic of system structure can be reflected.
(5) Based on the analysis of harmonic response analysis theory and its solving method,the meshing contact force obtained by mesh dynamic simulation of the silent chaintransmission system is transformed to frequency domain load by FFT(fast fourier transform).The frequency domain load is used as incentive boundary load for the prestress finiteelement harmonic response analysis. And through four node interpolation method, thevibration information of displacement response node in the grid structure obtained byharmonic response analysis is transferred into the acoustic surface mesh. And define thevibration displacement as the boundary condition to carry out the acoustic boundary elementcalculation. The acoustic quantity of field point in the outer sound field is obtained, thus, theanalysis about the acoustic characteristic of the sound field is conducted.
(6) Sound intensity measurement technology is adopted to measure the sound intensityand identify the noise source of the silent chain drive system. Through the processing and analysis of the data of sound intensity, the distribution diagrams of the sound powerspectrum and isacoustic line are obtained. From the diagrams above, the main noise sourceof the silent chain drive system is analyzed and identified, and the location of noise sourceand the main noise frequency components are obtained, which provide a basis for modifyingthe structure of the silent chain drive system, improving the analysis model and reducing thenoise.
引文
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