船舶声弹性力学理论及其应用

邹明松; 吴有生

doi:10.6052/1000-0992-16-031

船舶声弹性力学理论及其应用

doi: 10.6052/1000-0992-16-031

邹明松^{1, 2, 3, ,},
吴有生^{1, 2, 3}

1.
中国船舶科学研究中心, 江苏无锡 214082
2.
深海载人装备国家重点实验室, 江苏无锡 214082
3.
船舶振动噪声重点实验室, 江苏无锡 214082

详细信息

作者简介:
吴有生, 中国首批工程院院士, 船舶力学国际知名专家, 创造性地建立了广义三维线性船舶水弹性力学理论.长期投身于船舶水动力学与结构力学交叉领域的研究.在舰艇抗爆抗冲击技术领域、船舶水弹性力学/声弹性力学理论与工程应用领域、新型高性能船舶及深海装备的研究与设计方面都取得丰硕成果.现任国际水动力学学术会议执行委员会主席, 总装备部科技委兼职委员、国防科工局科技委委员与船舶分委员会副主任、中国船级社技术咨询与评议委员会主席、中国船舶重工集团军工专家咨询委员会副主任, 上海交通大学、武汉理工大学、哈尔滨工程大学等高校的兼职教授, 无锡市发展决策咨询顾问.现致力于我国海洋运载工程与科技发展战略及产业发展战略的研究, 促成了“蛟龙”号7 000 m载人深潜器的立项并进一步提出了发展深海装备技术的建议和设想

通讯作者:
邹明松, 浙江海宁人, 师从吴有生院士、司马灿研究员, 2014年获中国舰船研究院船舶与海洋结构物设计制造专业博士学位, 2016年获江苏省优秀博士学位论文.将船舶三维水弹性理论与水声信道理论相结合, 建立了船舶三维声弹性理论. 2015年应邀在圣彼德堡召开的第八届“当代海军与造船”国际会议上就相关研究作大会报告.现任中国船舶科学研究中心高级工程师, 硕士生导师, 主要从事船舶三维水弹性/声弹性理论、舰船减振降噪研究与设计以及结构设计的工作, 主持完成总装预研重大项目1项(被评为优秀) 以及其余各类科研项目多项.在国内外学术刊物和会议上发表论文30余篇, 担任国际SCI期刊Journal of Hydrodynamics和Ocean Engineering审稿人.曾获中船重工集团科学技术一等、二等奖、无锡市自然科学优秀学术论文特等奖等奖项.E-mail: zoumings@126.com

中图分类号: O427.5, U661.44
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出版历程
- 收稿日期: 2016-09-22
- 网络出版日期: 2017-01-18
- 刊出日期: 2017-02-24

Sono-elasticity of ships and the related applications

ZOU Mingsong^{1, 2, 3
, ,},
WU Yousheng^{1, 2, 3}

1.
China Ship Scientific Research Center, Wuxi 214082, Jiangsu, China
2.
State Key Laboratory of Deep-sea Manned Vehicles, Wuxi 214082, Jiangsu, China
3.
National Key Laboratory on Ship Vibration and Noise, Wuxi 214082, Jiangsu, China

More Information

Corresponding author: ZOU Mingsong

摘要

摘要: 船舶结构与水介质耦合动力学在改善船舶运动性能与结构安全性, 控制船舶振动噪声与提高水下声隐身性能, 进行船舶综合性能的优化设计等一系列工程问题中有广泛的应用需求与发展前景.本文综述了船舶水弹性力学、声弹性力学的理论方法、试验技术与应用技术的国内外研究进展; 介绍了在带航速三维水弹性力学理论(Wu 1984) 基础上, 作者所在课题组近年来发展的船舶三维声弹性理论、计算技术及工程应用的概况.简述了船舶三维声弹性理论的部分应用情况及发展方向.
- 船舶 /
- 流固耦合 /
- 水弹性力学 /
- 声弹性理论 /
- 计算技术 /
- 试验技术
Abstract: Dynamics of coupled fluid-structure interaction of ships has great demand for applications, and vast vistas in improving motion behavior and structural safety, controlling vibration and noise, and enhancing stealth capability of ships. In this paper, we summarize the status-of-the-art of theoretical and experimental developments of ship hydroelasticity and ship sono-elasticity, as well as applied techniques. We briefly describe the results obtained by the authors' research group in the three-dimensional sono-elasticity theory based on a three-dimensional hydroelasticity theory (Wu 1984), the improvements of computational techniques, and the extensions in engineering applications. Some future directions are also discussed.
- ships /
- fluid-structure interaction /
- hydroelasticity /
- sono-elasticity /
- computational techniques /
- experimental techniques

HTML全文

图 1 整体弹性材料船模的水池试验照片(CSSRC). (a) S175船型的船模试验, (b) 一艘驱逐舰的船模试验

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图 2 (a) 典型超大型浮动平台三维效果图, (b) 3个300m长半潜式模块柔性连接的超大型浮动平台示意图, (c) 等深海底与变深海底环境中0度浪向规则波作用下平台垂向动变形幅值沿全长分布的比较(Yang et al. 2015)

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图 3 船舶以12节航速迎浪航行, 不规则波海况为H_1/3=3.25 m, T₀₁=7.53 s (田超2007). (a) 1 500 t SWATH海洋调查船, (b) 横舱壁上von Mises应力分布的线性解, (c) 横舱壁上von Mises应力分布的考虑瞬时湿表面变化的非线性解

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图 4 环形实肋板连接的无限长双层加肋圆柱壳声辐射计算模型(吴文伟等2002)

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图 5 某实船9.8节航速下, 艏部声呐自噪声计算与实测比对(俞孟萨2007). (a) 艏部声呐罩外形, (b) 艏部声呐罩自噪声测量示意图, (c) 艏部声呐自噪声谱级计算与实测结果比对

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图 6 半径为0.5 m的单层弹性球壳水下声辐射考核算例(Zou et al. 2010). (a) 计算模型及坐标系示意图, (b) 无界流场环境中位于(r, θ) 处场点的声压级数值结果与解析解的比对

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图 7 Pekeris波导模型及其Green函数的近似级数表达式的验证(Zou et al. 2012). (a) 海水和海底为参数不同的理想声介质的Pekeris波导模型, (b) 源点和场点相对位置满足要求时, 近似Green函数计算精度考核

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图 8 外壳半径为0.65 m内壳半径为0.5 m的双层弹性球壳水下声辐射考核算例(邹明松和吴有生2012). (a) 计算模型及坐标系示意图, (b) 无界流场中(r=100, θ=π) 处场点的声压换算的声源级数值结果与解析结果的比对

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图 9 用MANS方法预报总长为22 m的圆柱壳模型水下声辐射的比较结果(邹明松2014). (a) 计算模型, (b) 1号点施加垂向单位力激励时无界流场中辐射噪声声源级的比对结果

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图 10 加筋圆柱壳模型水下声辐射全频域计算结果的比较(Zou & Wu 2015). (a) 半径为2.5m的加筋圆柱壳及激励点, (b) 用声弹性理论数值方法、MANS方法和SEA方法预报辐射噪声声源级的比对结果

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图 11 消除不规则频率的虚拟阻抗封闭曲面法. (a) 虚拟阻抗曲面及内外流场示意图, (b) 半径为0.5m的球体刚体平动对应的无量纲声抗(采用边长为b的立方体虚拟阻抗曲面, 其阻抗值取为流体特征阻抗)

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图 12 THAFTS-Acoustic 1.0软件后处理功能的示例. (a) 包络船体的圆柱面上的声压级云图, (b) 包络船体的圆柱面上的声强云图

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图 13 电磁激振机激励的半径为0.36 m的加筋圆柱壳的水下声辐射考核试验(邹明松2014). (a) 新安江水库开阔水域中试验模型吊放及水听器布置示意图, (b) 模型吊放现场照片, (c) 水听器场点1/3Oct声压谱级比对结果

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图 14 由两个舱室组成总长约19 m的实尺度船体水下声辐射考核试验(邹明松2014). (a) 船体在水池中的试验位置, (b) 移动扫描测量船体辐射声功率的由48对双水听器构成的环形声强传感器阵, (c) 在舱内机械设备激励下由船体辐射声功率换算的声源级比对结果(因水池环境限制, 有效测试频段在100 Hz以上)

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图 15 有限水深环境中一艘LNG船的低频声波驻波现象. (a) 计算对象, (b) 计算取不同水深h时, 船体一阶垂向弯曲振动对应的无量纲化附连水质量(Zou et al. 2013)

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图 16 一艘小水线面双体船在机械激励下的水下辐射噪声. (a) 典型模态(下潜体内外摆动) 振型示例, (b) 推进电机和主辅发电机激励下场点声压换算的声源级比对结果(Zou et al. 2014)

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图 17 不同水深潜深环境下船体水平剖面内的声场分布云图(邹明松2014). (a) 水深65m, 潜深30m; (b) 水深500m, 潜深250m

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图 18 潜水器尾部结构减振优化(Sun & Zou 2015). (a) 潜水器尾部结构横向摇摆的典型模态振型, (b) 尾部框架结构改进前后振动速度响应比对, (c) 潜水器试验照片

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