空间不均匀湍流边界层激励下声呐腔自噪声统计能量分析

利用统计能量分析法建立了湍流边界层激励下水下航行器声呐腔自噪声水动力分量的计算模型。采用一种新的回转体模型模拟声呐罩，重点讨论空间分布不均匀的湍流边界层对声呐罩的输入功率的计算及统计能量分析参数的确定，利用Fluent软件计算边界层的分离点及一些重要参数。最后给出了一具体的算例。可作为空间不均匀湍流边界层激励下声呐腔自噪声的工程估算的参考。     

湍流脉动压力下椭球声呐腔水动力自噪声分析

运用统计能量法建立水下椭球壳形状的声呐腔模型。利用计算流体动力学软件计算不同航速下声呐罩表面湍流边界层的分离点,考虑了湍流脉动压力空间分布的不均匀性。分析航速以及不同吸声和阻尼处理方案对声呐腔水动力自噪声的影响。理论评估吸声处理的结果和数值计算的结果比较吻合。研究表明：航速越大,自噪声越大;透声窗面积所占总表面积的比例越小,吸声和阻尼处理的降噪效果越明显;吸声和阻尼处理在中高频段降噪效果更好。研究结果为水下声呐腔水动力自噪声预报和控制提供了参考。     

统计能量法计算声呐自噪声的水动力噪声分量

本文针对水下航行器舷侧的声呐基阵,采用统计能量法建立自噪声中水动力噪声分量的计算模型,并计算分析不同罩壁材料、吸声处理对声呐自噪声的影响.     

集成统计能量法计算声呐自噪声水动力噪声分量

针对舰船艏部非规则形状声呐罩的自噪声预报,借鉴集成模态法思路[1,2],采用虚拟弹性膜技术,建立集成统计能量法(Integro-SEA),并以矩形腔声呐罩为例验证计算精度.在此基础上,采用集成统计能量法计算舰船艏部声呐自噪声的水动力噪声分量,并修正计算艏部边界层转捩区湍流猝发声源对声呐自噪声的作用.研究表明:用经典SEA和集成SEA方法计算矩形腔声呐罩自噪声,偏差小于1dB,集成SEA方法加边界层转捩区声源修正,计算的舰船艏部声呐自噪声与实艇测试结果比较,在200Hz～6kHz的中频范围内相差2～3dB.     

结合均值导纳法的声呐腔自噪声统计能量分析

讨论了湍流边界层激励下声呐腔自噪声统计能量分析。采用圆柱一圆板组合结构模拟艏部声呐罩,重点讨论了湍流边界层输入功率计算,及利用均值导纳法求解多耦合结构之间的直接耦合损耗因子及问接耦合损耗因子,给出了详细的理论推导,最后给出了具体的算例。分析结果可作为湍流边界层激励下声呐腔自噪声工程估算的参考。     

船舶艏部声呐罩水动力噪声评估

文章针对非规则形状的艏部声呐罩,基于统计能量理论,建立了艏部声呐罩自噪声的理论模型,并分析了非透声窗吸声系数和过渡区声源对声呐罩噪声的影响。经对过渡区声源高频噪声影响的计算修正,大大提高了计算精度。试验验证表明,过渡区附近腔体自噪声计算结果与测试值相差小于5 dB,较好地反映了腔内自噪声分布规律。     

基于AutoSEA2的船舶典型动力源辐射噪声分析

利用以统计能量分析原理为基础的声仿真软件AutoSEA2建立典型动力源激励的某船分段3D模型,分析了动力源激励力的等效计算及此激励产生的辐射噪声.首先根据舱段的特点,划分子系统并建立耦合关系,得到了统计能量分析模型.然后利用动力设备基座的面导纳概念,将基座面板分别简化为有限简支矩形薄板和无限大薄板,计算并对比了在中高频段这两种简化方案下的激励力.根据确定的激励方案计算得到r该舱段的舱室噪声和水下辐射噪声,并与试验结果进行了比较.对比表明,依此激励计算得到的声振环境预示结果与试验结果吻合较好,证明了统计能量分析在高频区预示船舶声振环境的可靠性.     

基于AutoSEA的高速船静噪声预报与控制

高速船是在船舶航速上出现突破、慨念新颖的新一代船型。船舶高速化的同时却带来了严重的振动噪声问题。在船舶设计初期预估舱室噪声水平，及时采取预防措施显得至关重要。应用统计能量分析软件AutoSEA对高速船客舱区进行设计初期的噪声预报，并分析噪声传播路径，提出噪声控制的初步方案，模拟计算经采取控制措施后的客舱区噪声值。     

水下结构物自噪声统计能量分析

用统计能量分析方法,对湍流边界层脉动压力激励下水下结构物自噪声进行了分析,得到相应的自噪声工程估算关系。根据工程条件进行简化,得到忽略壳体内损耗和边界层伪声直接透射的高频情况下的工程估算公式。     

潜艇首部声呐平台区中、高频自噪声预报

潜艇首部声呐平台区结构复杂,激励也是随机和宽带的,其中,高频（500Hz～10kHz）自噪声预报通常采用SEA（统计能量分析）.由于缺乏实测和试验资料,各子系统间耦合因子和各结构的内损耗因子难以确定,只能近似估算.本文采用试验和SEA相结合的方法来预报其平台区自噪声.通过模型实验测出子系统在各种激励力下的动响应,进而求得子系统振动能量;采用经验公式计算各子系统模态密度,最后利用统计能量法来预报潜艇首部声呐平台区自噪声,得到了令人满意的结果.     

空间不均匀湍流边界层激励下声呐腔自噪声统计能量分析

  目的  为降低传统圆形声呐外表面流噪声,设计3种不同外形(圆形、椭圆形以及方形)的声呐,并对其外表面的水动力特性和流噪声进行研究。  方法  基于Fluent中的标准相似文献   

Simple Lagrangian formulation of bubbly flow in a turbulent boundary layer (bubbly boundary layer flow)

For the theoretical consideration of a system for reducing skin friction, a mathematical model was derived to represent, in a two-phase field, the effect on skin friction of the injection of micro air bubbles into the turbulent boundary layer of a liquid stream. Based on the Lagrangian method, the equation of motion governing a single bubble was derived. The random motion of bubbles in a field initially devoid of bubbles was then traced in three dimensions to estimate void fraction distributions across sections of the flow channel, and to determine local bubble behavior. The liquid phase was modeled on the principle of mixing length. Assuming that the force exerted on the liquid phase was equal to the fluid drag generated by bubble slip, an equation was derived to express the reduction in turbulent shear stress. Corroborating experimental data were obtained from tests using a cavitation tunnel equipped with a slit in the ceiling from which bubbly water was injected. The measurement data provided qualitative substantiation of the trend shown by the calculated results with regard to the skin friction ratio between cases with and without bubble injection as function of the distance downstream from the point of bubble injection.List of symbols B law of wall constant - C _f local coefficient of skin friction - C _f0 local coefficient of skin friction in the absence of bubbles - d _b bubble diameter [m] - g acceleration of gravity [m/s²] - k ₁ k₄ proportional coefficient - k _L turbulent energy of the liquid phase [m²/s²] - L representative length [m] - l _b mean free path of a bubble [m] - m _A added mass of a single bubble [kg] - m _b mass of a single bubble [kg] - N _x ,N _y ,N _z force perpendicular to the wall or ceiling exerted on a bubble adhering to that wall or ceiling [N] - P absolute pressure [Pa] - Q _G rate of air supply [/min] - q _L ⁽ⁱ⁾ turbulent velocity at the ith time increment [m/s] - R> _ex Reynolds number defined by Eq. 32 - T _*L integral time scale of the liquid phase [s] - U velocity of the main stream [m/s] - ,¯v,¯w time-averaged velocity components [m/s] - u,v,w turbulent velocity components [m/s] - û _L ,v_L root mean square values of liquid phase turbulence components in thex- and y-directions [m/s] - V volume of a single bubble [m³] - X,Y,Z components of bubble displacement [m] - x _s ,y _s ,z _s coordinate of a random point on a sphere of unit diameter centered at the coordinate origin - root mean square of bubble displacement in they-direction in reference to the turbulent liquid phase velocity [m] - local void fraction - _m mean void fraction in a turbulent region - regular random number - R _v increment of the horizontal component of the force acting on a single bubble, defined by Eq. 22 [N] - t time increment [s] - ₁ reduction of turbulent stress [N/m²] - _L rate of liquid energy dissipation [m²/s³] - _m coefficient defined by Eq. 30 - law of wall constant in the turbulent region in absence of bubbles - ₁ law of wall constant in the turbulent region in presence of bubbles     

湍流激励下简支平板振动特性的解析法研究

解析法基于随机激励理论,采用湍流脉动压力的Corcos模型作为输入,结合考虑流固耦合时平板的频响函数,求解得到平板振动速度的自功率谱密度。计算结果同已有文献吻合较好,证明了解析法的正确性。同时研究结果表明：湍流激励下平板的振动特性体现了平板本身的固有特性;随着来流速度的增大,平板振速的均方谱密度幅值按一定的数值关系增大。     

平板湍流边界层流向—法向平面发卡涡的PIV实验研究

湍流边界层流动精细涡结构的分析对于水下航行体表面减阻乃至降噪机理的深入研究都具有重要意义.文章应用粒子图像测速技术(PIV),对Reθ=1 743和5 400时的平板湍流边界层的流向—法向平面流场进行了测试研究.一方面,直接对瞬时速度场精细涡结构进行提取分析,通过Galilean分解和λci准则识别出流向—法向平面中的发卡涡及发卡涡包.研究表明,发卡涡和雷诺应力的分布特征具有高度相关性;发卡涡包产生了流向动量的法向不规则分层分布特征.另一方面,文中通过对500个瞬时速度场子样进行时间平均分析,获得了不同雷诺数下平均速度以及湍流度分量的法向分布规律.此外,文中还对发卡涡的几何尺寸和漩涡强度λci进行了统计分析.研究表明,在y+＜50范围内无量纲化的漩涡强度λciδ/uт沿法向迅速衰减,且在不同雷诺数下变化曲线基本一致;在y+ ＞50后λciδ/uт衰减平缓,且低雷诺数下的值较大.     

Effect of microbubbles on the structure of turbulence in a turbulent boundary layer

The time-averaged velocity and turbulence intensity distributions were measured by a laser Doppler velocimeter in a turbulent boundary layer filled with microbubbles. The void fraction distribution was also measured using a fiber-optic probe. The velocity decreased in the region below 100 wall units with an increase in bubble density. This led to a decrease in the velocity gradient at the wall, which was consistent with a decrease in shearing stress on the wall. The turbulence intensity in the buffer layer increased at a low microbubble density, and then began to decrease with an increasing microbubble density. Based on the present measurements, the mechanism of turbulence reduction by microbubbles is discussed and a model is proposed. Received for publication on Dec. 3, 1999; accepted on April 18, 2000     

Distribution of void fraction in bubbly flow through a horizontal channel: Bubbly boundary layer flow, 2nd report

A method of enveloping the hull with a sheet of microbubbles is discussed. It forms part of a study on means of reducing the skin friction acting on a ship's hull. In this report, a bubble traveling through a horizontal channel is regarded as a diffusive particle. Based on this assumption, an equation based on flow flux balance is derived for determining the void fraction in approximation. The equation thus derived is used for calculation, and the calculation results are compared with reported experimental data. The equation is further manipulated to make it compatible with a mixing length model that takes into account the presence of bubbles in the liquid stream. Among the factors contained in the equation thus derived, those affected by the presence of bubbles are the change of mixing length and the difference in the ratio of skin friction between cases with and without bubbles. These factors can be calculated using the mean void fraction in the boundary layer determined by the rate of air supply into the flow field. It is suggested that the ratio between boundary layer thickness and bubble diameter could constitute a significant parameter to replace the scale effect in estimating values applicable to actual ships from corresponding data obtained in model experiments.List of symbols a ₁ proportionality constant indicating directionality of turbulence - B law-of-the-wall constant - C _f local skin-friction coefficient in the presence of bubbles - C _f0 local skin-friction coefficient in the absence of bubbles - d _b bubble diameter (m) - g acceleration of gravity (m/s²) - j _g flow flux of gas phase accountable to buoyancy (m/s) - j _t flow flux of gas phase accountable to turbulence (m/s) - k ₄ constant relating reduction of liquid shear stress by bubble presence to decrease of force imparted to bubble by its displacement due to turbulence - l _b mixing length of gas phase (m) - l _m mixing length of liquid phase (m) - l _mb diminution of liquid phase mixing length by bubble presence (m) - Q _G rate of air supply to liquid stream (l/min) - q _/g velocity of bubble rise (m/s) - 2R height of horizontal channel (m) - T _* integral time scale (s) - U _m mean stream velocity in channel (m/s) - U friction velocity in channel (m/s) - V volume of a bubble (m³) - u, ¯ v time-averaged stream velocities inx- andy-directions, respectively (m/s) - u, v turbulent velocity components inx- andy-directions, respectively (m/s) - v root mean square of turbulence component in they-direction (m/s) - root mean square of bubble displacement iny-direction with reference to turbulent liquid phase velocity (m) - y displacement from ceiling (m) - local void fraction - _m mean void fraction in boundary layer - _m constant relating local void fraction to law-of-the-wall constant - _t reduction of turbulent stress (N/m²) - law-of-the-wall constant in turbulent liquid region in absence of bubbles - ₁ law-of-the-wall constant in turbulent liquid region in presence of bubbles - ₂ law-of-the-wall constant in gas phase - _m constant indicating representative turbulence scale (m) - viscosity (Pa × s) - v kinematic viscosity (m²/s) - density (kg/m³) Suffixes G gas - L liquid - 0 absence of bubbles