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Article(id=1217836116879790858, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1217836113499177684, articleNumber=null, orderNo=null, doi=10.19666/j.rlfd.202503063, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1741017600000, receivedDateStr=2025-03-04, revisedDate=null, revisedDateStr=null, acceptedDate=null, acceptedDateStr=null, onlineDate=1768284356564, onlineDateStr=2026-01-13, pubDate=1766592000000, pubDateStr=2025-12-25, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1768284356564, onlineIssueDateStr=2026-01-13, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1768284356564, creator=13701087609, updateTime=1768284356564, updator=13701087609, issue=Issue{id=1217836113499177684, tenantId=1146029695717560320, journalId=1210938733613449225, year='2025', volume='54', issue='12', pageStart='1', pageEnd='156', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1768284355759, creator=13701087609, updateTime=1768284424805, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1217836403174593046, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1217836113499177684, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1217836403174593047, tenantId=1146029695717560320, journalId=1210938733613449225, issueId=1217836113499177684, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=39, endPage=45, ext={EN=ArticleExt(id=1217836118217773863, articleId=1217836116879790858, tenantId=1146029695717560320, journalId=1210938733613449225, language=EN, title=Modal analysis and test verification of moving blades of the compressor in a heavy-duty gas turbine, columnId=1217836114430313173, journalTitle=Thermal Power Generation, columnName=Efficient low-carbon thermal system, runingTitle=null, highlight=null, articleAbstract=

The first stage blades of a heavy-duty gas turbine compressor are newly independently developed and designed, which use the advanced 3D modeling technology to design high-performance blade profiles. It is necessary to master the blades’ vibration characteristics to verify the reliability of the blades. The finite element method was used to analyze the vibration frequency of the blades under dynamic frequency testing conditions and actual operating conditions. Meanwhile, the radio telemetry technology has been introduced to verify the dynamic frequency of the blade. The dispersion effects caused by blade material and processing tolerances, as well as assembly tolerances were also considered. The results indicate that the theoretical analysis of blade vibration is consistent with the test characteristics, with a deviation of no more than 1.2%. The theoretical frequency avoidance margin of compressor blades under operating conditions can meet the deviation between numerical analysis methods and experimental testing methods, as well as the frequency influence caused by material, processing, and assembly factors, and still have a large safety margin. The research results provide guidance for the development of gas turbine compressor blades, as well as the upgrading, improvement, and vibration monitoring of blades throughout their entire lifecycle.

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某重型燃气轮机压气机第1级叶片为全新自主开发设计，采用了先进三维造型技术设计的高性能叶型，须掌握其振动特性来验证叶片的可靠性。采用有限元方法分析了动频测试工况以及实际运行工况下叶片的振动频率，并通过无线电遥测技术进行叶片的动频测试验证，同时考虑叶片材料与加工公差以及装配公差引起的分散度影响。结果表明，叶片振动频率的理论分析与测试特性一致，结果偏差不大于1.2%。压气机叶片在运行工况下的理论频率避开裕度能够满足数值分析方法与试验测试方法的偏差及材料、加工制造与装配因素引起的频率影响后仍具有较大安全余量。研究结果可为后续进行燃气轮机压气机叶片的开发以及全生命周期的升级改进与振动监测提供指导。

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周莉莉（1993），女，硕士，工程师，主要研究方向为燃气轮机部件强度校核与振动分析，。

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周莉莉（1993），女，硕士，工程师，主要研究方向为燃气轮机部件强度校核与振动分析，。

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周莉莉（1993），女，硕士，工程师，主要研究方向为燃气轮机部件强度校核与振动分析，。

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Plant Maintenance Engineering, 2018, 13(7): 49-50., articleTitle=Static frequency test and vibration safety analysis of turbine blade, refAbstract=null), Reference(id=1217836133526983066, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, doi=null, pmid=null, pmcid=null, year=2019, volume=null, issue=2, pageStart=28, pageEnd=30, url=null, language=null, rfNumber=［25］, rfOrder=45, authorNames=倪秋华, 高伟, 张华芳, journalName=机械工程师, refType=null, unstructuredReference=倪秋华, 高伟, 张华芳, 等. 某台600 MW汽轮机叶片静频测试及振动安全性分析[J]. 机械工程师, 2019(2): 28-30., articleTitle=某台600 MW汽轮机叶片静频测试及振动安全性分析, refAbstract=null), Reference(id=1217836133623452064, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, doi=null, pmid=null, pmcid=null, year=2019, volume=null, issue=2, pageStart=28, pageEnd=30, url=null, language=null, rfNumber=［25］, rfOrder=46, authorNames=NI Qiuhua, GAO Wei, ZHANG Huafang, journalName=Mechanical Engineer, refType=null, unstructuredReference=NI Qiuhua, GAO Wei, ZHANG Huafang, et al. 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Mechanical Engineer, 2019(2): 28-30., articleTitle=Static frequency test and vibration safety analysis of a 600 MW steam turbine blade, refAbstract=null)], funds=[Fund(id=1217836127654957244, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, awardId=2024003, language=EN, fundingSource=Enterprise Innovation Development and Energy Level Enhancement Project of Shanghai State Owned Assets Supervision and Administration Commission(2024003), fundOrder=null, country=null), Fund(id=1217836127747231939, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, awardId=2024003, language=CN, fundingSource=上海市国资委企业创新发展和能级提升项目(2024003), fundOrder=null, country=null)], companyList=[AuthorCompany(id=1217836120189096821, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, xref=null, ext=[AuthorCompanyExt(id=1217836120193291126, tenantId=1146029695717560320, journalId=1210938733613449225, 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figureFileBig=a3YWTwnERc8pXKiCwTodIQ==, tableContent=null), ArticleFig(id=1217836124907688036, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=CN, label=图8, caption=叶片的某阶共振频谱, figureFileSmall=Uht5PDUnjWmV0QPg47Ur3g==, figureFileBig=a3YWTwnERc8pXKiCwTodIQ==, tableContent=null), ArticleFig(id=1217836126233088109, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=EN, label=Fig.9, caption=Comparison of frequency test results and theoretical analysis results of the compressor blade during the process of increasing and decreasing speed, figureFileSmall=mgfJvKdquYRLqSraCd9PUQ==, figureFileBig=8/vhmctRew6IuwzV64RH1g==, tableContent=null), ArticleFig(id=1217836126350528627, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=CN, label=图9, caption=压气机动叶在升、降转速过程频率测试结果与理论分析结果对比, figureFileSmall=mgfJvKdquYRLqSraCd9PUQ==, figureFileBig=8/vhmctRew6IuwzV64RH1g==, tableContent=null), ArticleFig(id=1217836126459580534, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=EN, label=Tab.1, caption=

Frequency analysis results and safety margin of the compressor blades under operating conditions

, figureFileSmall=null, figureFileBig=null, tableContent=
转速/(r·min–1)频率/Hz
第一阶第二阶第三阶
2 850120.6270.9323.9
3 000124.2275.3324.2
3 090126.4278.0324.3
上安全裕度16.99.1
下安全裕度18.415.510.3
), ArticleFig(id=1217836126581215360, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=CN, label=表1, caption=

运行工况下压气机动叶的频率分析结果及避开裕度

, figureFileSmall=null, figureFileBig=null, tableContent=
转速/(r·min–1)频率/Hz
第一阶第二阶第三阶
2 850120.6270.9323.9
3 000124.2275.3324.2
3 090126.4278.0324.3
上安全裕度16.99.1
下安全裕度18.415.510.3
), ArticleFig(id=1217836126656712838, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=EN, label=Tab.2, caption=

Frequency analysis results of compressor blade under dynamic frequency test condition

, figureFileSmall=null, figureFileBig=null, tableContent=
转速/(r·min–1)频率/Hz
第一阶第二阶第三阶
50077.0225.0324.8
1 00082.7230.3324.9
1 50091.1238.7325.2
2 000101.4249.8325.5
2 500112.7262.9326.0
3 000124.5275.2326.6
), ArticleFig(id=1217836126740598924, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=CN, label=表2, caption=

动频测试工况下压气机动叶的频率分析结果

, figureFileSmall=null, figureFileBig=null, tableContent=
转速/(r·min–1)频率/Hz
第一阶第二阶第三阶
50077.0225.0324.8
1 00082.7230.3324.9
1 50091.1238.7325.2
2 000101.4249.8325.5
2 500112.7262.9326.0
3 000124.5275.2326.6
), ArticleFig(id=1217836126866428054, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=EN, label=Tab.3, caption=

Dynamic frequency test results of the compressor blades

, figureFileSmall=null, figureFileBig=null, tableContent=
阶次升转速过程降转速过程
转速/(r·min–1)频率/Hz转速/(r·min–1)频率/Hz
第一阶2 051102.62 029101.5
1 32088.01 30587.0
80280.279479.4
51477.150976.4
第二阶2 674267.42 658265.8
2 175253.82 164252.5
1 606240.91 596239.4
1 163232.61 157231.4
第三阶2 787325.22 778324.1
2 439325.22 423323.1
1 951325.21 936322.7
1 501325.21 489322.6
), ArticleFig(id=1217836127059366042, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=CN, label=表3, caption=

压气机动叶的动频测试结果

, figureFileSmall=null, figureFileBig=null, tableContent=
阶次升转速过程降转速过程
转速/(r·min–1)频率/Hz转速/(r·min–1)频率/Hz
第一阶2 051102.62 029101.5
1 32088.01 30587.0
80280.279479.4
51477.150976.4
第二阶2 674267.42 658265.8
2 175253.82 164252.5
1 606240.91 596239.4
1 163232.61 157231.4
第三阶2 787325.22 778324.1
2 439325.22 423323.1
1 951325.21 936322.7
1 501325.21 489322.6
), ArticleFig(id=1217836127181000864, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=EN, label=Tab.4, caption=

Comparison of theoretical frequency and test frequency of blades at design speed

, figureFileSmall=null, figureFileBig=null, tableContent=
项目第一阶第二阶第三阶
理论设计值124.5277.2326.6
测试频率（升速）125.5275.5325.1
测试频率（降速）124.3272.9324.8
测试-理论（升速）1.0–1.7–1.5
测试-理论（降速）0.2–4.3–1.8
理论设计裕度[–18.4, 16.9][–15.5, 9.1][–10.3, +∞)
允许频率范围>106.1
<141.4		>261.7
<286.3		>316.3
), ArticleFig(id=1217836127294247079, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=CN, label=表4, caption=

设计转速下叶片理论频率与测试频率对比

, figureFileSmall=null, figureFileBig=null, tableContent=
项目第一阶第二阶第三阶
理论设计值124.5277.2326.6
测试频率（升速）125.5275.5325.1
测试频率（降速）124.3272.9324.8
测试-理论（升速）1.0–1.7–1.5
测试-理论（降速）0.2–4.3–1.8
理论设计裕度[–18.4, 16.9][–15.5, 9.1][–10.3, +∞)
允许频率范围>106.1
<141.4		>261.7
<286.3		>316.3
), ArticleFig(id=1217836127407493292, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=EN, label=Tab.5, caption=

Static frequency test results of the compressor blade

, figureFileSmall=null, figureFileBig=null, tableContent=
项目第一阶第二阶第三阶
静频范围/Hz[74.5, 75.5][218.8, 222.5][323.0, 334.9]
整圈静频均值/Hz75.0220.9324.7
静频分散度/%1.41.73.6
频率波动范围/Hz[–0.5, 0.5][–2.1, 1.6][–1.7, 10.2]
), ArticleFig(id=1217836127503962293, tenantId=1146029695717560320, journalId=1210938733613449225, articleId=1217836116879790858, language=CN, label=表5, caption=

压气机动叶的静频测试结果

, figureFileSmall=null, figureFileBig=null, tableContent=
项目第一阶第二阶第三阶
静频范围/Hz[74.5, 75.5][218.8, 222.5][323.0, 334.9]
整圈静频均值/Hz75.0220.9324.7
静频分散度/%1.41.73.6
频率波动范围/Hz[–0.5, 0.5][–2.1, 1.6][–1.7, 10.2]
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重型燃气轮机压气机动叶片的模态分析和测试验证
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周莉莉 , 张山子 , 赵连会
热力发电 | 高效低碳热力系统 2025,54(12): 39-45
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热力发电 | 高效低碳热力系统 2025, 54(12): 39-45
重型燃气轮机压气机动叶片的模态分析和测试验证
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周莉莉 , 张山子, 赵连会
作者信息
  • 上海电气燃气轮机有限公司，上海　200240

    • 周莉莉（1993），女，硕士，工程师，主要研究方向为燃气轮机部件强度校核与振动分析，。

Modal analysis and test verification of moving blades of the compressor in a heavy-duty gas turbine
Lili ZHOU , Shanzi ZHANG, Lianhui ZHAO
Affiliations
  • Shanghai Electric Gas Turbine Co, Ltd, Shanghai 200240, China
出版时间: 2025-12-25 doi: 10.19666/j.rlfd.202503063
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摘要
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某重型燃气轮机压气机第1级叶片为全新自主开发设计，采用了先进三维造型技术设计的高性能叶型，须掌握其振动特性来验证叶片的可靠性。采用有限元方法分析了动频测试工况以及实际运行工况下叶片的振动频率，并通过无线电遥测技术进行叶片的动频测试验证，同时考虑叶片材料与加工公差以及装配公差引起的分散度影响。结果表明，叶片振动频率的理论分析与测试特性一致，结果偏差不大于1.2%。压气机叶片在运行工况下的理论频率避开裕度能够满足数值分析方法与试验测试方法的偏差及材料、加工制造与装配因素引起的频率影响后仍具有较大安全余量。研究结果可为后续进行燃气轮机压气机叶片的开发以及全生命周期的升级改进与振动监测提供指导。

重型燃气轮机  /  压气机叶片  /  振动分析  /  动频测试  /  分散度

The first stage blades of a heavy-duty gas turbine compressor are newly independently developed and designed, which use the advanced 3D modeling technology to design high-performance blade profiles. It is necessary to master the blades’ vibration characteristics to verify the reliability of the blades. The finite element method was used to analyze the vibration frequency of the blades under dynamic frequency testing conditions and actual operating conditions. Meanwhile, the radio telemetry technology has been introduced to verify the dynamic frequency of the blade. The dispersion effects caused by blade material and processing tolerances, as well as assembly tolerances were also considered. The results indicate that the theoretical analysis of blade vibration is consistent with the test characteristics, with a deviation of no more than 1.2%. The theoretical frequency avoidance margin of compressor blades under operating conditions can meet the deviation between numerical analysis methods and experimental testing methods, as well as the frequency influence caused by material, processing, and assembly factors, and still have a large safety margin. The research results provide guidance for the development of gas turbine compressor blades, as well as the upgrading, improvement, and vibration monitoring of blades throughout their entire lifecycle.

heavy-duty gas turbine  /  compressor blades  /  vibration analysis  /  dynamic frequency test  /  dispersion
周莉莉, 张山子, 赵连会. 重型燃气轮机压气机动叶片的模态分析和测试验证. 热力发电, 2025 , 54 (12) : 39 -45 . DOI: 10.19666/j.rlfd.202503063
Lili ZHOU, Shanzi ZHANG, Lianhui ZHAO. Modal analysis and test verification of moving blades of the compressor in a heavy-duty gas turbine[J]. Thermal Power Generation, 2025 , 54 (12) : 39 -45 . DOI: 10.19666/j.rlfd.202503063
正文
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随着全球对清洁能源和高效能源转换设备的需求不断增加，燃气轮机（燃机）凭借其高效、清洁、成本较低的优势，在能源转换和电力供应领域起到至关重要的作用[1-2]。但其存在的叶片振动问题是导致燃机故障的主要原因之一[3-4]，压气机叶片作为燃机中的核心部件，承受着离心载荷、气动压力载荷以及振动交变载荷等作用，在叶片设计阶段必须对叶片的振动特性进行充分研究，掌握叶片的共振特性以保证结构可靠性。
针对叶片的振动特性，大量学者开展了一些相关研究。付娜等[5]和王春洁等[6]采用ANSYS软件对非旋转态和旋转态下叶片-轮盘耦合系统的振动固有特性进行了计算分析。杨博宇等[7]研究了3种不同转速产生的离心力对叶片频率的影响趋势。张亮等[8]基于ANSYS Workbench对某燃机叶片的主要振动阶次进行了详细的模态及应力分析。然而，现有燃机压气机叶片的振动特性分析主要集中在航空发动机领域，对重型燃机压气机叶片的振动分析较少。重型燃机与航空发动机由于在运行规律、工作环境和寿命等方面均有较大不同，在结构的设计上存在较大的差异。重型燃机对结构的长寿命与耐久性及结构的可靠性具有更高的要求[9]。在进行重型燃机压气机叶片的设计时，往往需要对叶型进行定制化设计，以满足气动与强度振动的需求。
由于叶片的理论计算频率与真实频率往往存在偏差。同时，叶片在加工和装配过程中的公差会影响叶片的固有频率[10]。因此，开展叶片的固有频率试验对掌握叶片的振动特性具有重要的意义。叶片的固有频率测试主要分为静频测试（非旋转状态）和动频测试（旋转状态）2种。马义良等[11]对带围带和凸台阻尼拉筋的汽轮机叶片开展了动频测试，并对叶片进行了调频优化。葛存飞等[12]基于WiFi通信的动态应变遥测方法和基于单喷嘴压缩空气射流激振方法的汽轮机叶片动频试验系统，对整圈自锁阻尼围带和拉筋的汽轮机低压末级叶片进行了动频测试，并探索了围带厚度对动频分散度的影响。谷伟伟等[13]采用无线电非接触测试方法在动平衡舱内测试了带凸肩自锁结构汽轮机低压末级长叶片的振动频率，并采用有限元计算了不同凸肩接触状态下叶片频率。钟小萍等[14]通过无线电遥测技术对300 MW等级汽轮机低压转子末级自由叶片和整圈连接叶片进行了动频测试试验。王斌等[15]对发动机压气机叶片的振动特性进行了研究，并对叶片进行了静频测试验证。付曦等[16]通过静频试验验证3种不同拟合精度叶片的可靠性。
虽然已有关于叶片振动频率测试的研究，但测试研究对象多数是带凸肩或围带的汽轮机叶片，对燃气轮机压气机叶片的振动测试多以静频试验为主，动频测试较少。本文采用数值模拟与试验验证相结合的方式研究某重型燃机新设计压气机第1级叶片的振动特性，通过有限元方法计算叶片在动频测试工况及实际运行工况下的频率，并借助无线电遥测技术对压气机叶片在动频测试工况下的频率值进行验证，进一步结合静频测试结果考虑了叶片材料、加工制造、装配等因素的分散度影响。结果表明，新设计的压气机叶片满足振动设计要求。
1　叶片振动特性数值分析
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为了适应大流量、跨音速的流动特点，同时满足进口级压气机叶片的气动性能及振动强度要求，某重型燃机压气机第1级叶片采用先进的叶片设计技术进行了全新自主开发，叶片为自由叶片，叶型采用了跨音叶型设计以及三维复合弯掠与端弯的设计技术，叶身最大高度为658 mm，叶根采用燕尾型结构，在满足灵活拆装的同时适应检修周期长的特点，叶根沿轴向的长度接近320 mm。压气机第1级叶片几何模型如图1所示。叶根与轮盘通过锁片进行限位固定，确保了整体结构的稳定与可靠。
1.1　叶片计算模型
基于叶片与轮盘周期对称的特点，采用单个叶片与对应的轮盘扇区作为研究对象来分析整圈叶片轮盘系统的振动特性。采用全四面体单元SOLID 187划分网格，网格模型如图2所示，叶盘扇区模型共54万节点。轮盘的扇区面施加周期对称边界条件，轮盘进气端截面施加轴向与周向约束。
1.2　模态计算结果
采用ANSYS软件开展动频测试工况（室温，不考虑压力载荷）和机组实际运行工况下的叶片模态分析。对叶片在实际运行工况下的振动频率进行考核，该燃气轮机设计转速为50 Hz，考虑电网频率波动，要求叶片在95%~103%转速内关键振型避开相应的激振频率并保持一定的安全裕度。
压气机叶片低阶模态振型如图3所示。根据压气机叶片振动考核标准，进入考核范围的关键振型为前3阶振型，分别为一阶弯曲（第一阶）、二阶弯曲（第二阶）和一阶扭转（第三阶）振型，叶片对应的坎贝尔图如图4所示，运行工况下压气机动叶的频率分析结果及避开裕度见表1。由图4和表1可见，压气机动叶在满足振动设计要求后仍具有较大的频率裕度。其中，第三阶频率对应的下裕度为10.3 Hz，上裕度极大。动频测试工况下，叶片的模态振型与运行工况下一致，在不同转速下压气机动叶的频率分析结果见表2。由表2可见，叶片的频率随着转速的增加而增大。这是由于在离心力作用下，叶片产生动力钢化效应[7]所致。
2　叶片振动特性测试
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2.1　测试系统
采用无线电遥测技术开展燃机压气机叶片的动频测试，测试在全尺寸燃机转子上进行。整圈叶片在装配前首先进行称重排序，选择4片叶片作为测试叶片。根据有限元分析得到的叶片振型，确定电阻丝应变片的数量和布置位置。图5为其中1片测试叶片上应变片和引线端子的理论设计方案与实际布置情况。使用应变量电测法进行试验测试，该方法是叶片振动试验中广泛使用且成熟的方法[17-22]。将电池、发射天线与发射机制成的微型发报机安装在前轴头平衡孔中，通过引线将应变片与微型发报机连接，形成工作电路。在旋转状态下，使用氮气喷枪激励叶片，叶片振动并产生应变，从而造成感应元件阻值发生变化，经过变换电路产生电压信号，经发报机调制发射。该频射信号由固定在动平衡台轴承座挡油板上的天线环接收，并经由高频电缆传送至接收机。通过示波器、频谱分析仪等设备对叶片振动数据进行存储、显示与分析[11]。转子的转速数据通过转速表收集。试验相关设备如图6所示，放置于动平衡试验舱中的带测试叶片的燃机转子如图7所示。
2.2　测试过程
测试开始前，对动平衡室抽真空。真空度达到要求后转子开始升转速，保证升速速率不高于130 r/min。在转速达到500 r/min时稳定片刻，确认数据采集设备的信号稳定。继续升转速并开启氮气激励，达到3 000 r/min后维持转速并关闭激励，检查设备与信号状态。随后打开氮气激励并开始降转速，降至500 r/min时关闭激励。继续将转速降至零后，动平衡室破真空，完成叶片动频率测试过程。
2.3　测试结果分析
通过频谱分析仪对升转速与降转速过程的测试数据进行分析，叶片的某阶共振频谱如图8所示。图8上下部分峰值点分别显示了该阶对应的共振频率与共振转速，及相应的响应值与阻尼衰减系数。不同转速下的叶片振动频率列于表3。由表3可见，在相同转速下，叶片在升速过程中的频率值略高于降速过程，这是由于在降速过程中环境温度升高，对叶片刚度产生了一定影响。
3　对比验证
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3.1　动频测试工况
对比分析动频试验结果与动频测试工况的模拟结果，不同转速对应的叶片理论模态频率值由数值计算结果线性插值获得，图9为压气机动叶在升、降转速过程的频率测试结果与理论分析结果。由图9可见，叶片振动的理论分析与测试特性一致，结果相对偏差不大于1.2%，这是数值计算方法与试验测试方法综合影响的结果。数值计算方面，对边界条件进行了一定程度的简化，模态分析中接触刚度和实际叶片与轮盘之间的接触刚度存在差异。动频试验方面，信号噪声影响、传感器精度以及数据处理方法等因素会对测试结果产生影响。
在升转速过程中，压气机动叶前三阶模态频率的测试值与理论值的相对偏差均不超过0.4%。其中，第一阶频率最大绝对偏差为0.3 Hz；第二阶频率最大绝对偏差为0.6 Hz；第三阶频率最大绝对偏差为1.2 Hz。在降转速过程中，第一阶频率最大相对偏差为1.2%；第二阶和第三阶频率相对偏差均不超过1.0%。其中，第一阶频率最大绝对偏差为1.0 Hz，第二阶频率最大绝对偏差为1.7 Hz，第三阶频率最大绝对偏差为3.1 Hz。
在设计转速（3 000 r/min）状态下，叶片频率的测试结果与理论分析结果的对比，及允许的频率范围见表4。其中，第一阶频率的最大绝对偏差为1.0 Hz，第二阶频率最大绝对偏差为4.3 Hz，第三阶频率最大绝对偏差为1.8 Hz。频率的偏差均在运行工况下的设计裕度内。
3.2　材料与加工分散度影响
以上结果考虑了理论设计方法与动频试验方法之间的差异，以及叶片与轮盘真实接触状态与设计接触状态之间的偏差。实际上，叶片的材料偏差、加工公差以及装配公差会使叶片的实际频率存在一定的分散度。
叶片的频率分散度Δf定义为：
Δf=fmax−fmin(fmax+fmin)/2
式中：fmax和fmin分别为叶片相应振型对应的振动静频最大值和最小值[23-24]。规定叶片的频率分散度Δf < 8%为合格[25]。
表5列出了压气机动叶通过静频测试方法测量得到的静频结果及分散度。由表5可见，压气机动叶的频率分散度满足要求。同时，对叶片的频率波动范围进行统计分析，波动范围上限设定为频率最大值与平均值的偏差，下限设置为频率最小值与平均值的偏差。压气机动叶的频率波动范围分别为：第一阶[–0.5, 0.5] Hz，第二阶[–2.1, 1.6] Hz，第三阶[–1.7, 10.2] Hz。
因此，叠加整圈叶片的材料与加工分散度，以及叶片与轮盘装配公差的影响后，压气机叶片在设计转速下频率范围分别为：升转速过程，第一阶[125.0, 126.0] Hz，第二阶[273.4, 277.1] Hz，第三阶[323.4, 335.3] Hz；降转速过程，第一阶[123.8,124.8] Hz，第二阶[270.8, 274.5] Hz，第三阶[323.1, 335.0] Hz。均符合表4列出的设计转速下允许频率范围，叶片满足振动设计要求。
4　结论
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本文通过数值模拟结合频率测试技术研究了某重型燃机自主开发压气机第一级动叶的振动特性，主要结论如下。
1）在动频测试工况下，压气机第一级叶片在升转速和降转速过程中的频率理论值与测量值随转速的变化趋势一致，结果相对偏差不大于1.2%。升转速过程中，叶片前三阶模态频率的测试与理论值的相对偏差均不超过0.4%；在降转速过程中，第一阶频率最大相对偏差为1.2%，第二阶和第三阶频率相对偏差均不超过1.0%。
2）在运行转速工况下，叠加叶片的材料与加工公差、叶片与轮盘的安装公差，以及理论设计方法与试验测试方法的偏差影响之后，叶片的频率仍有足够的安全裕度，叶片满足振动设计要求。
3）本研究相应的压气机叶片设计方法及振动分析与测试验证方法，对重型燃气轮机压气机叶片的开发设计及全生命周期的升级改进和振动监测具有重要的指导意义。
基金
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  • 上海市国资委企业创新发展和能级提升项目(2024003)
文献
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2025年第54卷第12期
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doi: 10.19666/j.rlfd.202503063
  • 接收时间：2025-03-04
  • 首发时间：2026-01-13
  • 出版时间：2025-12-25
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  • 收稿日期：2025-03-04
基金
Enterprise Innovation Development and Energy Level Enhancement Project of Shanghai State Owned Assets Supervision and Administration Commission(2024003)
上海市国资委企业创新发展和能级提升项目(2024003)
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    上海电气燃气轮机有限公司，上海　200240
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2种不同金属材料的力学参数
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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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