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Article(id=1243306316584825037, tenantId=1146029695717560320, journalId=1240685776644648972, issueId=1243306309064442584, articleNumber=null, orderNo=null, doi=10.3969/j.issn.1007-7294.2025.05.013, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1731772800000, receivedDateStr=2024-11-17, revisedDate=null, revisedDateStr=null, acceptedDate=null, acceptedDateStr=null, onlineDate=1774356925388, onlineDateStr=2026-03-24, pubDate=1747670400000, pubDateStr=2025-05-20, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1774356925388, onlineIssueDateStr=2026-03-24, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1774356925388, creator=13701087609, updateTime=1774356925388, updator=13701087609, issue=Issue{id=1243306309064442584, tenantId=1146029695717560320, journalId=1240685776644648972, year='2025', volume='29', issue='5', pageStart='681', pageEnd='848', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=0, createTime=1774356923595, creator=13701087609, updateTime=1774357065180, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1243306902965301262, tenantId=1146029695717560320, journalId=1240685776644648972, issueId=1243306309064442584, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1243306902965301263, tenantId=1146029695717560320, journalId=1240685776644648972, issueId=1243306309064442584, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=820, endPage=829, ext={EN=ArticleExt(id=1243306316865843413, articleId=1243306316584825037, tenantId=1146029695717560320, journalId=1240685776644648972, language=EN, title=Experimental study on a new turbine device for marine risers’ vibration suppression and energy harvesting, columnId=1242129251223274417, journalTitle=Journal of Ship Mechanics, columnName=Structural Mechanics, runingTitle=null, highlight=null, articleAbstract=

Marine risers are critical facilities connecting offshore oil and gas platforms to subsea wellheads, and vortex-induced vibration is the main cause of fatigue damage to risers. Therefore, a vibration suppression-energy harvesting turbine device was designed for risers to suppress vortex-induced vibration and harvest energy. Then experiments were conducted with the length of the blade of the turbine device’s impeller as a variable. On one hand, the vibration suppression and energy harvesting performance of the turbine device were verified; on the other hand, the influence of the impeller’s length of the blade on the device’s vibration suppression-energy harvesting performance was investigated. The results show that the overall vibration suppression efficiency of the turbine device is ideal, capable of reaching over 50%, with the best vibration suppression efficiency being 96.08%. The vibration suppression performance of the device increases positively with the increase in the impeller’s length of the blade, while the energy harvesting performance shows a negative trend. When the length of the blade is 12d, the vibration suppression-energy harvesting performance of the device increases synchronously with the increase in the incoming flow velocity.

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海洋立管是连接海上油气平台与海底井口的关键设施，而涡激振动是引发立管疲劳损伤的主要原因。本试验研究设计一种立管抑振-俘能涡轮装置，用于抑制立管涡激振动并实现能量俘获。以涡轮装置的叶片长度为变量开展试验，一方面验证涡轮装置的抑振性能和俘能性能，另一方面研究叶片长度对于涡轮装置抑振-俘能性能的影响。结果表明：涡轮装置的整体抑振效率可达50%以上，最佳抑振效率为96.08%，抑振效果理想；装置的抑振性能会随叶片长度的增加而呈现正增长，俘能性能则呈现负增长；当叶片长度为12d时，装置的抑振-俘能性能随来流流速的增加而同步增强。

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通讯作者，E-mail：
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苏泰宁（2000-），男，硕士研究生

刘震（1992-），女，讲师，通讯作者，E-mail：。

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苏泰宁（2000-），男，硕士研究生

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苏泰宁（2000-），男，硕士研究生

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刘震（1992-），女，讲师，通讯作者，E-mail：。

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刘震（1992-），女，讲师，通讯作者，E-mail：。

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Related parameters of the riser model and turbine devices

, figureFileSmall=null, figureFileBig=null, tableContent=
立管模型数值涡轮装置数值
有效长度L2000 mm高度L60 mm
水下长度L1800 mm壳壁厚d1 mm
外径D16 mm间距190 mm
壁厚δ1 mm数量3
长细比λ125叶片长度γ8/12/16/20 mm
质量比m*1.56叶片倾角α45°
模型材料PPMMA叶片数量5
), ArticleFig(id=1243306334767133302, tenantId=1146029695717560320, journalId=1240685776644648972, articleId=1243306316584825037, language=CN, label=表1, caption=

立管模型和涡轮装置的相关参数

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立管模型数值涡轮装置数值
有效长度L2000 mm高度L60 mm
水下长度L1800 mm壳壁厚d1 mm
外径D16 mm间距190 mm
壁厚δ1 mm数量3
长细比λ125叶片长度γ8/12/16/20 mm
质量比m*1.56叶片倾角α45°
模型材料PPMMA叶片数量5
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新型海洋立管抑振-俘能涡轮装置试验研究
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苏泰宁 1, 2 , 刘震 1, 2 , 李朋 1, 2 , 韩新宇 1, 2
船舶力学 | 结构力学 2025,29(5): 820-829
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船舶力学 | 结构力学 2025, 29(5): 820-829
新型海洋立管抑振-俘能涡轮装置试验研究
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苏泰宁1, 2, 刘震1, 2 , 李朋1, 2, 韩新宇1, 2
作者信息
  • 1.山东科技大学　土木工程与建筑学院，山东　青岛　266590
  • 2.青岛市海洋土木工程材料与结构重点实验室，山东　青岛　266590

    • 苏泰宁（2000-），男，硕士研究生

    刘震（1992-），女，讲师，通讯作者，E-mail：。

通讯作者:

通讯作者，E-mail：
Experimental study on a new turbine device for marine risers’ vibration suppression and energy harvesting
Tai-ning SU1, 2, Zhen LIU1, 2 , Peng LI1, 2, Xin-yu HAN1, 2
Affiliations
  • 1.College of Civil Engineering and Architecture, Shandong University of Science and Technology, Qingdao 266590, China
  • 2.Qingdao Key Laboratory of Marine Civil Engineering Materials and Structures, Qingdao 266590, China
出版时间: 2025-05-20 doi: 10.3969/j.issn.1007-7294.2025.05.013
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摘要
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海洋立管是连接海上油气平台与海底井口的关键设施，而涡激振动是引发立管疲劳损伤的主要原因。本试验研究设计一种立管抑振-俘能涡轮装置，用于抑制立管涡激振动并实现能量俘获。以涡轮装置的叶片长度为变量开展试验，一方面验证涡轮装置的抑振性能和俘能性能，另一方面研究叶片长度对于涡轮装置抑振-俘能性能的影响。结果表明：涡轮装置的整体抑振效率可达50%以上，最佳抑振效率为96.08%，抑振效果理想；装置的抑振性能会随叶片长度的增加而呈现正增长，俘能性能则呈现负增长；当叶片长度为12d时，装置的抑振-俘能性能随来流流速的增加而同步增强。

海洋立管  /  涡激振动  /  抑振效率  /  俘能性能

Marine risers are critical facilities connecting offshore oil and gas platforms to subsea wellheads, and vortex-induced vibration is the main cause of fatigue damage to risers. Therefore, a vibration suppression-energy harvesting turbine device was designed for risers to suppress vortex-induced vibration and harvest energy. Then experiments were conducted with the length of the blade of the turbine device’s impeller as a variable. On one hand, the vibration suppression and energy harvesting performance of the turbine device were verified; on the other hand, the influence of the impeller’s length of the blade on the device’s vibration suppression-energy harvesting performance was investigated. The results show that the overall vibration suppression efficiency of the turbine device is ideal, capable of reaching over 50%, with the best vibration suppression efficiency being 96.08%. The vibration suppression performance of the device increases positively with the increase in the impeller’s length of the blade, while the energy harvesting performance shows a negative trend. When the length of the blade is 12d, the vibration suppression-energy harvesting performance of the device increases synchronously with the increase in the incoming flow velocity.

marine riser  /  vortex induced vibration  /  vibration suppression efficiency  /  energy harvesting performance
苏泰宁, 刘震, 李朋, 韩新宇. 新型海洋立管抑振-俘能涡轮装置试验研究. 船舶力学, 2025 , 29 (5) : 820 -829 . DOI: 10.3969/j.issn.1007-7294.2025.05.013
Tai-ning SU, Zhen LIU, Peng LI, Xin-yu HAN. Experimental study on a new turbine device for marine risers’ vibration suppression and energy harvesting[J]. Journal of Ship Mechanics, 2025 , 29 (5) : 820 -829 . DOI: 10.3969/j.issn.1007-7294.2025.05.013
正文
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0　引言
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海洋立管用于连接海上平台和海底井口，是海洋油气开发系统中的关键设备。当海流流经立管时，周期性流体作用会导致立管产生涡激振动现象（vortex-induced vibration, VIV）[1-5]，特别是当漩涡脱落的频率接近立管的固有频率时，还会发生“锁振现象”[6-7]，使立管产生剧烈振动从而加速其疲劳破坏，因而抑振装置的研发成为了国内外研究热点。目前，立管的抑振方式可分为主动抑振和被动抑振。主动抑振是通过实时监测立管的受力状况及其周围流场的变化，直接对立管或其周围流场施加干扰，从而达到立管抑振的效果，例如Zhang等[8]利用压电振动器嵌入结构使其产生振动，进而改变结构与流体间的作用，影响旋涡的泄放；Shaharuddi等[9]将模糊迭代原理与控制原理相结合，利用立管与系统的共振达到抑振的效果；Li等[10]在立管的上游设置喷气装置以干扰流场，实现了立管抑振；Liu等[11]在立管的下游设置喷气装置，确定了喷气装置的最优抑振效果的布置间距。被动抑振则是通过改变立管的形状以扰乱其周围流场、干扰涡激振动过程中旋涡的形成及泄放，从而达到立管抑振的效果；Trim等[12]测评了不同螺距/鳍高比的螺旋列板在均匀流和剪切流下的抑振效果，结果表明螺旋列板的螺距/鳍高比与其抑振效果成正相关，当装置覆盖率在82%以上时，抑振效率可达90%以上；Li等[13]进行了离散的螺旋列板抑振试验，结果表明离散的螺旋列板能够更好地破坏旋涡的空间相关性和压力场分布；Lou等[14]测试了分流板对立管阵列的抑振效果，并确定了立管阵列的最优抑振间距。
海洋中蕴藏着丰富的可再生能源，其中海流能的能量密度约为风能的4倍、太阳能的300倍[15]，能量密度高且开发成本低，具有良好的市场应用前景[16]。近年来，国内外学者借助结构的涡激振动实现海流能的俘获，根据能量转化方式，涡激振动能量的俘获装置主要分为压电式装置[17-19]和电磁式装置[20-22]。压电式装置是利用流体流过压电材料时使其发生变形而产生的电压变化从而实现电能转换，例如包括悬臂梁式[23]、鳗鱼式[24-25]、树式[26-28]等，应用于微小型传感器等电子设备的供电系统，能量转化率较低，仅在μW或mW量级，现阶段难以实现大规模开发。电磁式装置则是利用振子的涡激振动带动永磁体切割磁场从而实现电能转换。例如，Wang等[20]通过利用旋涡脱落使顶梁结构发生形变，设计了一种电磁式能量俘获装置，其能量俘获功率达到μW量级；Bernitsas等[21-22]设计了VIVACE装置，显著提高了能量转换效率并有利于大规模开发，为涡激振动能量的俘获做出了重要贡献。
海洋立管作为海洋工程中典型的大长细比结构，其在涡激振动能量的俘获方面也存在优势，现有研究多数仅针对如何进一步提高涡激振动能量的俘获效率。然而，涡激振动产生的能量对立管而言本质上属于一种“消极振动能量”，不仅会加速立管疲劳破坏，同时还会对海洋生态造成不可逆的影响。相比之下，抑振装置的扰流振动能量则属于一种“积极振动能量”，对抑振装置“积极振动能量”的俘获，能够在实现俘获立管涡激振动能量的基础之上，进一步实现立管抑振，延长立管的服役周期。这对处在深海环境中的油气开发系统而言具有重要的工程应用价值，同时对系统自身的能源生态优化也具有积极意义，而目前关于俘获抑振装置“积极振动能量”的研究仍较少。综上所述，本文设计一种新型立管抑振-俘能涡轮装置，装置可在来流作用下绕立管轴向旋转。在利用装置外部的叶轮产生扰流效果实现立管抑振的基础上，装置内部的电磁俘能结构可以实现对抑振装置“积极振动能量”的俘获。本文以涡轮装置的叶片长度为变量，在波流联合水槽中开展海洋立管抑振-俘能涡轮装置试验研究，一方面验证装置的抑振性能和俘能性能，另一方面研究叶片长度对装置抑振-俘能性能的影响，并在试验范围内确定装置抑振-俘能性能的最优叶片长度。
1　试验设置
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本次试验在中国海洋大学工程水动力学试验室的波流联合水槽中进行，水槽两侧由钢柱支撑，底部由钢板和横梁构成，表面覆盖钢化玻璃，用于支撑装置的安装和固定，水槽长30 m，宽1 m，最大工作水深1 m，试验水深设置为0.8 m，最大水流速度0.8 m/s，图1给出了试验整体布置图。试验流速设置为0.1~0.6 m/s，每隔0.05 m/s设置一级，共11级，图1给出了试验整体布置图。为了方便分析，下文将各级流速换算为约化速度，计算公式如下。
式中，U为外流流速，D为立管外径，fn为结构在静水中的固有频率。
沿立管轴向由上到下共设置六个测点（#1~#6），其上共设置24个应变传感器，分别对称固定在立管CF1、CF2与IL1、IL2四个方向，立管上下两端均采用万向节进行铰接固定，如图2所示，并依靠图1中的顶张力施加系统对立管施加顶张力。本次试验采用了美国Micron optics公司的布拉格光栅光纤传感器来获取立管横向和顺流向的振动信号，同时采用了单相电量综合测量智能隔离变送器，可实时显示电流强度，用于采集不同工况下的电流数据。
本次试验设计了一种立管抑振-俘能涡轮装置，可通过装置叶轮的旋转产生扰流作用从而抑制立管涡激振动。根据电磁感应原理，还可以通过涡轮发电进一步将装置的旋转能动能转化为电能，图3、图4分别给出了涡轮装置在立管模型上的布置图以及涡轮装置的分解图。本文围绕涡轮装置的“叶片长度”参数，共设置四类工况，分别为“γ=8d”、“γ=12d”、“γ=16d”、“γ=20d”（d为涡轮装置的壳壁厚，d=1 mm），涡轮装置的关键参数以及工况采用的四种叶轮外壳如图5（（a）~（d））所示，涡轮装置以及立管模型的其他参数详见表1。
2　涡轮装置的抑振性能分析
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图6给出了不同工况下立管沿CF方向的无量纲位移均方根曲线，根据试验过程中所观察到的光滑工况下立管的模态转换现象，将流速依次划分为阶段一（Ur=2.56~6.42）、模态转换阶段（Ur=7.71~10.24）和阶段二（Ur=11.56~15.41）。
通过对比发现在光滑工况下，光滑管在阶段一内的位移幅值存在明显起伏，并在流速Ur=5.13时达到了第一个峰值，数值为0.47D。通过观察右侧对应该流速下光滑管的展向位移曲线，可以看出光滑管符合一阶振型频率，说明此时光滑管处在一阶锁振区间。随后进入模态转换区间，同样观察右侧对应Ur=10.27时光滑管的展向位移曲线符合二阶振型频率，随后光滑管进入阶段二，位移幅值呈现上升趋势且相较于阶段一更加明显。而对比各类抑振工况，抑振管在阶段一内相较于光滑管在振幅达到峰值时，其所对应的最大振幅仅为0.05D，随后振幅仍随着来流流速的增加而呈现出稳定单调递增的趋势。观察右侧抑振管的展向位移曲线，可以看出抑振工况下立管的振型频率始终为一阶主导，且在整个试验流速区间内并未观察到明显的位移突变。除了所观测到的模态转换现象以外，当多阶模态共同主导立管振动过程时，都普遍存在振幅降低的现象，例如Xu等[29]在分析倾斜圆柱结构在外流速U=0.40 m/s时的模态转化临界速度下涡激振动特性时，抑振前后立管4号测点沿CF方向的位移振幅相近，类似的现象也在其他试验中有所体现[30]。
图7（a）、（b）分别给出了抑振前后立管在各级约化速度下的功率谱密度。可以看出，抑振工况下立管的振动能量相较于光滑管在整体上出现了显著降低，尤其是在阶段一、阶段二内的各级流速下，二者最大相差近2个量级。由于在模态转换阶段内各工况下立管的位移幅值相差甚微，此时讨论抑振的意义不大，故本文将不再对该阶段内涡轮装置的抑振效率展开分析。综上所述，下文将针对立管出现了振幅大、能量高的阶段一和阶段二做进一步分析。为了能更加直观地体现各类工况下装置对立管涡激振动的抑制效果，本文引入了抑振效率（η），计算公式如下：
式中，y为光滑管的位移均方根值，y1为抑振管的位移均方根值。
图8（a）、（b）分别给出了阶段一、阶段二的不同工况下涡轮装置的抑振效率随约化速度的变化，并分别附上各级流速所对应抑振效率的具体数值。经分析，不同工况在阶段一、阶段二的抑振效率可分别维持在70%和50%以上，表明了涡轮装置的抑振性能稳定，最大抑振效率可达96.08%，抑振效果明显。将四类工况分为γ=8d与γ=12d、16d、20d两组，通过图中标识的红色箭头，可以看出两组数据产生了明显的分层现象，前者数据在整体上明显低于后者，这表明涡轮装置的抑振效率会随叶片长度的增加而逐步提高，且叶片长度越小，提高的幅度就越明显。另外，从图中还能看出涡轮装置的抑振效率在达到γ=12d以后提升较为缓慢，但整体上还是会随着涡轮装置叶片长度的增大而逐步提高，这一点由图8（b）红框内部的数据体现得较为明显。
3　涡轮装置的俘能性能分析
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图9给出了各类工况（8d、12d、16d、20d）下涡轮装置的俘能均方根值（IRMS，单位：mA）随约化速度的变化，并以各类工况数据的回归线斜率来表示相应工况在约化速度Ur=6.42~15.41区间内的俘能增长速率（下文简称“俘能增速”），四类工况的俘能增速分别对应图9中k1~k4。为了方便后续分析，将图9划分为两个区域：区域一（Ur=6.42~10.27）和区域二（Ur=11.56~15.41）。另外，由于在约化速度较低时，外流对涡轮装置的激励过小，本次试验未采集到明显的俘能数据，故图9中横轴（Ur）的起始点取为Ur=6.42。
分析图9可知，在γ=20d工况下，涡轮装置所产生的俘能效果覆盖了由Ur=6.42至Ur=15.41共8级流速，相较于本次试验所设置的11级流速，覆盖率达到了72.7%（下文简称“俘能覆盖率”）。
相较之下，γ=8d工况下装置只在区域二内采集到电流，俘能覆盖率仅为36.4%；γ=12d与γ=16d工况下的俘能覆盖率则分别对应54.5%及45.4%，介于前两类工况之间，这表明叶片长度越大的装置对来流激励越敏感，从而使其在流速较低时也能采集到一定的电流数据。但就俘能增速而言，通过观察不同工况对应的回归线斜率，可以看出γ=20d工况下涡轮装置俘能效果所覆盖的流速区间虽广，但整体上的俘能增速却偏低，在Ur=14.13~15.41区间内的数据还存在负增长的现象。相比之下，γ=8d工况下涡轮装置的俘能覆盖率虽小，但其俘能增速却是γ=20d工况下的近五倍，且相较于γ=12d、16d工况也存在明显差距。
为了综合考量涡轮装置的俘能性能，图10给出了俘能增速和俘能均值随装置叶片长度的增加而产生的变化。其中，俘能均值为图9中各工况下装置在各级约化速度下的俘能数值的均值（在图10中记作“AVG（IRMS/mA）”）。从中可以看出，二者均存在随叶片长度的增大而递减的趋势，其中各工况下的俘能均值虽变化程度较轻，但俘能增速的变化却在叶片长度取到γ=8d时显著提高。由上文分析可知涡轮装置的叶片长度越大，其抑振效率提升越高，产生的扰流效果越强，正因如此也使得涡轮装置在俘能过程中所受来流的影响越明显，进而导致涡轮装置的俘能增速随着叶片长度的增大而呈现出负增长。由此可以认为，处在相同且足够高的流速区间内，叶片长度越小的涡轮装置所能俘获的能量越多，就俘能性能而言更有优势。
4　涡轮装置的抑振与俘能综合分析
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图11给出了涡轮装置的抑振-俘能综合性能随约化速度的变化情况，其中，左图为涡轮装置的“抑振数据”与“俘能数据”两类信息的汇总。通过观察其中数据的变化规律，本文选取了在高约化速度Ur=11.56~15.41区间内涡轮装置的抑振与俘能性能均较为理想的数据（即左图中红框内数据），将其整理后如右图所示，并进一步对该图中涡轮装置的抑振-俘能综合性能展开分析。在右图中，不同工况均包含按照流速由小到大并用箭头依次相连的四个数据点（最低流速所对应的数据点记作“起始点”，也即约化速度Ur=11.56时的数据点），其横轴和纵轴的数值分别对应该点的抑振效率（η）和电流均方根值（IRMS）。因数据较为杂乱，为了方便后续分析，本文用绝对斜率“AP”（absolute slope）表示各数据点相对于起始点连线的斜率，用相对斜率“RP”（relative slope）表示相邻数据点连线的斜率，并将相邻两条连线之间的夹角变化量的绝对值记作“∠”（单位：°，下文简称“连线夹角”）。右图已将AP、RP、∠三类数据汇总在黑、红、蓝、绿色四个方框中，依次对应8d、12d、16d和20d工况。
从整体上看，一组较为理想的数据点变化状况是相对于该组数据的起始点沿右上方运动，即AP≥0，而观察右图可以发现几乎所有工况下数据点的运动趋势均符合这一状况，表明了不同工况下涡轮装置的抑振-俘能性能在整体上均会随流速的提高而有所增强。通过进一步分析，对比不同工况下AP数值的变化，联系上文可知：叶片长度越小的涡轮装置越倾向于能量俘获，AP越大；反之则更倾向于立管抑振，AP越小。因此，理想状态下数据点的增长趋势还应大致围绕AP=1，代表了涡轮装置的抑振-俘能性能可随流速的增加而同步增强，而在工况由γ=20d变化到γ=8d的过程内，对应的AP值逐渐趋于AP=1，呈现出一定规律性，可见叶片长度这类参数的确能够同时影响涡轮装置的抑振性能和俘能性能的增减幅度。而从各组数据点的相对变化（RP）来看，理想状态下的涡轮装置，尤其是在来流流速较高的情况下，不应存在抑振或俘能性能之中的某一环节相较于前一级流速有明显减弱的现象，即RP<0，下文称其为回弹现象，观察发现大多数工况均存在该现象。然而，图中γ=8d工况虽存在回弹现象，但其相邻数据点连线夹角的变化却最为平缓，而与之相比，γ=16d、20d工况虽也在流速达到Ur=15.41时产生该现象，但其连线夹角的变化却存在明显突变，这表明不同工况下产生回弹现象的成因可能不同。为做进一步分析，图12给出了在流速Ur=15.41时不同工况立管的位移时程变化。
由图12可以看出，γ=8d工况下立管的振幅大且均匀，相比之下，另外三类工况则在不同程度上出现了振幅收缩、振幅不均匀的现象。这是由于涡轮装置旋转所产生的扰流效果在一定程度上干扰了立管两侧旋涡的正常形成和泄放过程，扰乱了立管原本规律的涡激振动，使立管的振动过程呈现出一定的随机性。在γ=8d工况下所产生的回弹现象正是由于涡轮装置的叶片长度过小，在来流流速较高时不足以产生较强的扰流效果来破坏立管规律的涡激振动，而通过上文可知γ=8d工况尤其在来流流速较高时的俘能增速明显优于其他工况，故该工况下数据点会倾向于沿图11右图中的纵轴（IRMS）运动从而产生回弹现象。不同于γ=8d工况，γ=16d、20d两类工况下产生回弹现象的原因是两类工况所采用涡轮装置的叶片长度均较大，所产生的扰流效果足以破坏立管原本规律的涡激振动，显著降低了立管振幅。这从图12中对应工况的位移时程可以看出，抑振性能的提升较为明显，故γ=16d、20d两类工况下的数据点会倾向于沿图11中的横轴（η）运动。然而各数据点的抑振效率必须满足η<1，此时涡轮装置的最高抑振效率已经达到96.08%，故该工况下的数据点在来流流速较高的情况下势必会向着远离横轴（η）的方向运动，从而导致两类工况在图11的连线夹角在流速Ur=15.41时发生突变，出现了数据回弹的现象。这表明在试验范围内，叶片长度过大或过小均不利于涡轮装置在较高流速下抑振或俘能性能的充分发挥。
而通过图11也能看出，γ=12d工况下相邻数据点连线的夹角虽与γ=16d、20d工况时一样存在突变，但在流速达到Ur=15.41时夹角变化却恢复到较小的数值（∠=0.18°），不同于其他工况下存在RP<0或夹角突变较大的情况，γ=12d工况下立管的位移时程变化既表现为γ=8d工况下立管振幅的大而均匀，又存在γ=16d、20d两类工况下立管振幅收缩和不均匀的现象，且呈交替出现。这表明γ=12d工况下涡轮装置在来流流速较高时产生了较强的扰流效果，交替出现的大而均匀的振幅也让该工况下的涡轮装置兼顾了一定的俘能性能，从而避免了装置在来流流速较高时出现的抑振或俘能性能明显减弱的现象，达到涡轮装置抑振-俘能性能可随来流流速增高而同步增强的效果。
5　结论
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本文设计了一种新型立管抑振-俘能涡轮装置，可同时实现立管的抑振与涡激振动能量的俘获。通过试验研究分析了该装置的抑振性能、俘能性能，以及四类叶片长度（8d、12d、16d、20d）对涡轮装置的抑振-俘能性能的影响，主要结论如下：
（1）涡轮装置的抑振性能较为理想，整体的抑振效率在试验约化速度区间内基本维持在50%以上，最大抑振效率可达96.08%。涡轮装置的叶片长度越大，整体抑振效率越高。
（2）涡轮装置的俘能覆盖率会随装置的叶片长度的增加呈正增长，而俘能增速与俘能均值则会随涡轮装置的叶片长度的增加呈负增长。在约化速度Ur=6.42~15.41区间内，且在相同俘能覆盖率前提下，涡轮装置的叶片长度越小，装置俘获的能量越多，即俘能性能更有优势。
（3）从数据点连线的绝对斜率、相对斜率以及连线夹角变化三方面展开分析，发现当来流流速较高时（Ur>11.56），叶片长度过大或过小均不利于涡轮装置抑振-俘能性能的充分发挥。当叶片长度γ=12d时，可避免涡轮装置在来流流速较高时出现抑振或俘能性能明显减弱的现象，从而达到涡轮装置抑振-俘能性能随来流流速增高而同步增强的效果。
基金
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  • 山东省自然科学基金资助项目(ZR2022QE118; ZR2023ME040)
文献
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doi: 10.3969/j.issn.1007-7294.2025.05.013
  • 接收时间：2024-11-17
  • 首发时间：2026-03-24
  • 出版时间：2025-05-20
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  • 收稿日期：2024-11-17
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山东省自然科学基金资助项目(ZR2022QE118; ZR2023ME040)
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    1.山东科技大学　土木工程与建筑学院，山东　青岛　266590
    2.青岛市海洋土木工程材料与结构重点实验室，山东　青岛　266590

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2种不同金属材料的力学参数
科
Family		 属数
Number of
genus		 种数
Number of
species		 占总种数比例
Percentage of
total species (%)		 属
Genus		 种数
Number of
species		 占总种数比例
Percentage of total
species (%)
鹅膏菌科Amanitaceae 2 11 5.26 鹅膏菌属 Amanita 10 4.78
小菇科 Mycenaceae 2 12 5.74 丝盖伞属 Inocybe 5 2.39
多孔菌科 Polyporaceae 8 14 6.70 蜡蘑属 Laccaria 5 2.39
红菇科 Russulaceae 3 23 11.00 小皮伞属 Marasmius 6 2.87
小菇属 Mycena 11 5.26
光柄菇属 Pluteus 5 2.39
红菇属 Russula 17 8.13
栓菌属 Trametes 5 2.39
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