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Article(id=1261270373597832128, tenantId=1146029695717560320, journalId=1146123166801305609, issueId=1261262687258985194, articleNumber=null, orderNo=null, doi=10.12404/j.issn.1671-1815.2404704, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=research-article, receivedDate=1719158400000, receivedDateStr=2024-06-24, revisedDate=1744214400000, revisedDateStr=2025-04-10, acceptedDate=null, acceptedDateStr=null, onlineDate=1778639890335, onlineDateStr=2026-05-13, pubDate=1752768000000, pubDateStr=2025-07-18, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1778639890335, onlineIssueDateStr=2026-05-13, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1778639890335, creator=13701087609, updateTime=1778639890335, updator=13701087609, issue=Issue{id=1261262687258985194, tenantId=1146029695717560320, journalId=1146123166801305609, year='2025', volume='25', issue='20', pageStart='8317', pageEnd='8759', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1778638057769, creator=13701087609, updateTime=1778753106634, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1261745237240722095, tenantId=1146029695717560320, journalId=1146123166801305609, issueId=1261262687258985194, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1261745237240722096, tenantId=1146029695717560320, journalId=1146123166801305609, issueId=1261262687258985194, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=8707, endPage=8713, ext={EN=ArticleExt(id=1261270376521262027, articleId=1261270373597832128, tenantId=1146029695717560320, journalId=1146123166801305609, language=EN, title=Dynamics Analysis and Experiment of Cantilever High-speed Rotor of Turbofan Engine, columnId=1156262731079607234, journalTitle=Science Technology and Engineering, columnName=Papers·Aeronautics and Astronautics, runingTitle=null, highlight=null, articleAbstract=

Two schemes, hollow shaft and solid shaft were proposed for the cantilever high-speed rotor of a turbofan engine during the structural design stage. Based on the beam element finite element method, rotor dynamic analysis models with hollow shaft and solid shaft were established, and critical speed and vibration mode calculations were carried out. The calculation results show that hollow shaft structure is suitable for the rotor. Then, an analysis was conducted on the sensitivity of the unbalance response of a rotor with a hollow shaft to the unbalance amount at the characteristic position, providing a basis for the selection of balance surfaces in high-speed dynamic balance test. Finally, the dynamic characteristics test of the simulated rotor with hollow shaft within the full speed range and the high-speed dynamic balance test research at the working speed were completed. The rotor smoothly crossed the two orders bending critical speed and safely operated to the working speed, verifying the rationality of the rotor’s hollow shaft structure and dynamic design. Compared with the experimental results, the calculation error of the established finite element model is not more than 4.08%, which well reflects the dynamic characteristics of the rotor. After high-speed dynamic balancing, the deflection of the rotor at the working speed is significantly reduced, not less than 33.33%. The research results provide reference and technical support for the structural, dynamic design, and experimental research of real low-pressure rotors, and has important engineering value.

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针对某涡扇发动机悬臂高速转子在结构设计阶段,提出空心轴和实心轴两种方案,基于梁单元有限元法分别建立带空心轴和带实心轴的转子动力学分析模型,并开展了临界转速和振型计算。计算结果表明:转子宜选用空心轴结构;在此基础上,进行了带空心轴的转子不平衡响应对特征位置上的不平衡量的敏感程度分析,为高速动平衡试验的平衡面选择提供了依据;最后,完成了带空心轴模拟转子在全转速范围内的动力特性试验和工作转速下的高速动平衡试验。转子平稳越过两阶弯曲临界转速并安全运行至工作转速,验证了转子采用空心轴结构以及动力学设计的合理性;与试验结果比较,建立的有限元模型计算误差不大于4.08%,很好地反映了转子的动力特性;高速动平衡后转子在工作转速下的挠度大幅降低,不低于33.33%;研究成果为真实低压转子的结构、动力学设计和试验研究提供了参考和技术支持,具有重要的工程价值。

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聂卫健(1991—),男,汉族,江西抚州人,博士,高级工程师。研究方向:航空发动机转子动力学。E-mail:。

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聂卫健(1991—),男,汉族,江西抚州人,博士,高级工程师。研究方向:航空发动机转子动力学。E-mail:。

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聂卫健(1991—),男,汉族,江西抚州人,博士,高级工程师。研究方向:航空发动机转子动力学。E-mail:。

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High speed rotor dynamic balance technology[M]. Beijing: Science Press, 2017., articleTitle=null, refAbstract=null)], funds=[Fund(id=1261270432641048960, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, awardId=CXPT-2022-031, language=CN, fundingSource=中国航发创新基金(CXPT-2022-031), fundOrder=null, country=null)], companyList=[AuthorCompany(id=1261270387816521771, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, xref=1, ext=[AuthorCompanyExt(id=1261270387833298988, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, companyId=1261270387816521771, language=EN, country=null, province=null, city=null, postcode=null, companyName=null, departmentName=null, remark=1 AECC Hunan Aviation Powerplant Research Institute, Zhuzhou 412002, China), AuthorCompanyExt(id=1261270387858464814, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, companyId=1261270387816521771, language=CN, country=null, province=null, city=null, postcode=null, companyName=null, departmentName=null, remark=1 中国航发湖南动力机械研究所, 株洲 412002)]), AuthorCompany(id=1261270389091590194, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, xref=2, ext=[AuthorCompanyExt(id=1261270389112561716, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, companyId=1261270389091590194, language=EN, country=null, province=null, city=null, postcode=null, companyName=null, departmentName=null, remark=2 Key Laboratory of Aero-engine Vibration Technology, Aero Engine Corporation of China, Zhuzhou 412002, China), AuthorCompanyExt(id=1261270389162893366, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, companyId=1261270389091590194, language=CN, country=null, province=null, city=null, postcode=null, companyName=null, departmentName=null, remark=2 中国航空发动机集团航空发动机振动技术重点实验室, 株洲 412002)]), AuthorCompany(id=1261270389490049085, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, xref=3, ext=[AuthorCompanyExt(id=1261270389527797824, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, companyId=1261270389490049085, language=EN, country=null, province=null, city=null, postcode=null, companyName=null, departmentName=null, remark=3 School of Energy and Power Engineering, Bei Hang University, Beijing 100191, China), AuthorCompanyExt(id=1261270389557157953, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, companyId=1261270389490049085, language=CN, country=null, province=null, city=null, postcode=null, companyName=null, departmentName=null, remark=3 北京航空航天大学能源与动力工程学院, 北京 100191)])], figs=[ArticleFig(id=1261270413535994103, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.1, caption=Structure of rotor, figureFileSmall=XTr62fepjEaJLC95hS5Rdw==, figureFileBig=/w5fbz7+6qxyLkSPCxDgeg==, tableContent=null), ArticleFig(id=1261270413909287163, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图1, caption=转子结构

1号、2号和5号分别代表1号轴承、2号轴承和5号轴承

, figureFileSmall=XTr62fepjEaJLC95hS5Rdw==, figureFileBig=/w5fbz7+6qxyLkSPCxDgeg==, tableContent=null), ArticleFig(id=1261270418070036742, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.2, caption=Finite element model, figureFileSmall=4RZWPHz2HqnFtuyrZM30FQ==, figureFileBig=Xoc0J7g6gTHitvT7lvjfvw==, tableContent=null), ArticleFig(id=1261270418602713355, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图2, caption=有限元模型, figureFileSmall=4RZWPHz2HqnFtuyrZM30FQ==, figureFileBig=Xoc0J7g6gTHitvT7lvjfvw==, tableContent=null), ArticleFig(id=1261270420267852048, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.3, caption=The first three orders vibration mode of the rotor (with hollow shaft), figureFileSmall=+uBz4jrQRcD1BJMkKEDnvA==, figureFileBig=U1tHvlHcWfKiTTrrB1bWQg==, tableContent=null), ArticleFig(id=1261270420460790035, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图3, caption=转子前三阶振型(带空心轴), figureFileSmall=+uBz4jrQRcD1BJMkKEDnvA==, figureFileBig=U1tHvlHcWfKiTTrrB1bWQg==, tableContent=null), ArticleFig(id=1261270420783751448, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.4, caption=The first three orders vibration mode of the rotor (with solid shaft), figureFileSmall=jqbDFx11PftecppT7jRq4g==, figureFileBig=9o9koTsu0FSo7OqeuvihSg==, tableContent=null), ArticleFig(id=1261270421052186909, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图4, caption=转子前三阶振型(带实心轴), figureFileSmall=jqbDFx11PftecppT7jRq4g==, figureFileBig=9o9koTsu0FSo7OqeuvihSg==, tableContent=null), ArticleFig(id=1261270423044481312, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.5, caption=Unbalanced response curve, figureFileSmall=6VEQxhQHlawraHIlCyBBVw==, figureFileBig=1agP+0jhJL1UJiQpKJCvRQ==, tableContent=null), ArticleFig(id=1261270424860614947, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图5, caption=不平衡响应曲线, figureFileSmall=6VEQxhQHlawraHIlCyBBVw==, figureFileBig=1agP+0jhJL1UJiQpKJCvRQ==, tableContent=null), ArticleFig(id=1261270425376514344, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.6, caption=Installation and test schematic diagram of rotor, figureFileSmall=LLnmXkYAe+jQ255JkXqPxw==, figureFileBig=vczx0cRkVq2NHTVAOY823Q==, tableContent=null), ArticleFig(id=1261270425556869420, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图6, caption=转子试验安装测试示意图, figureFileSmall=LLnmXkYAe+jQ255JkXqPxw==, figureFileBig=vczx0cRkVq2NHTVAOY823Q==, tableContent=null), ArticleFig(id=1261270425720447281, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.7, caption=Installation and test picture of rotor, figureFileSmall=W2oNHCdIlZ+7d/v5HK9a5w==, figureFileBig=xooDHJdtC1Wx7IHy6c2ISA==, tableContent=null), ArticleFig(id=1261270426152460598, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图7, caption=转子试验安装照片, figureFileSmall=W2oNHCdIlZ+7d/v5HK9a5w==, figureFileBig=xooDHJdtC1Wx7IHy6c2ISA==, tableContent=null), ArticleFig(id=1261270426349592893, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.8, caption=Rotor deflection curve, figureFileSmall=lXW9JBsTqNlKn/HmevjEqQ==, figureFileBig=bk0tBo7JQ5RG0n8RGc9D8w==, tableContent=null), ArticleFig(id=1261270426613834048, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图8, caption=转子挠度曲线, figureFileSmall=lXW9JBsTqNlKn/HmevjEqQ==, figureFileBig=bk0tBo7JQ5RG0n8RGc9D8w==, tableContent=null), ArticleFig(id=1261270426831937859, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Fig.9, caption=Rotor deflection curve, figureFileSmall=CGLF9fn+4JLE4jBo2yESfA==, figureFileBig=Cp3JjE9nci2nXz60MMVLsQ==, tableContent=null), ArticleFig(id=1261270427301699910, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=图9, caption=转子挠度曲线, figureFileSmall=CGLF9fn+4JLE4jBo2yESfA==, figureFileBig=Cp3JjE9nci2nXz60MMVLsQ==, tableContent=null), ArticleFig(id=1261270429197525324, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Table 1, caption=

Support stiffness

, figureFileSmall=null, figureFileBig=null, tableContent=
支点 1号 2号 5号
支承刚度/(107 N·m-1) 1.21 2.30 0.44
), ArticleFig(id=1261270429403046223, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=表1, caption=

支承刚度

, figureFileSmall=null, figureFileBig=null, tableContent=
支点 1号 2号 5号
支承刚度/(107 N·m-1) 1.21 2.30 0.44
), ArticleFig(id=1261270429587595604, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Table 2, caption=

The first three critical speeds of the rotor

, figureFileSmall=null, figureFileBig=null, tableContent=
类型 临界 第1阶 第2阶 第3阶
带空心轴 计算值/(r·min-1) 7 831 15 237 38 322
裕度/% >70 >40 >30
带实心轴 计算值/(r·min-1) 7 780 15 649 28 178
裕度/% >70 >40 <5
), ArticleFig(id=1261270429742784857, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=表2, caption=

转子前三阶临界转速

, figureFileSmall=null, figureFileBig=null, tableContent=
类型 临界 第1阶 第2阶 第3阶
带空心轴 计算值/(r·min-1) 7 831 15 237 38 322
裕度/% >70 >40 >30
带实心轴 计算值/(r·min-1) 7 780 15 649 28 178
裕度/% >70 >40 <5
), ArticleFig(id=1261270429944111456, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Table 3, caption=

Unbalanced response of rotors at different orders

, figureFileSmall=null, figureFileBig=null, tableContent=
阶数 单位不平衡量位置 不平衡响应/10-6 m
模拟
风扇盘		 模拟低压
涡轮盘		 1号平
衡凸台		 2号平
衡凸台
1阶 模拟风扇盘 0.17 0.14 0.19 0.21
模拟低压涡轮盘 0.14 0.46 0.34 0.55
1号平衡凸台 0.19 0.34 0.42 0.51
2号平衡凸台 0.21 0.55 0.51 0.76
2阶 模拟风扇盘 1.33 0.21 0.82 0.42
模拟低压涡轮盘 0.21 0.27 0.19 0.29
1号平衡凸台 0.82 0.19 0.69 0.38
2号平衡凸台 0.42 0.29 0.38 0.35
3阶 模拟风扇盘 0.49 0.02 0.36 0.22
模拟低压涡轮盘 0.02 0.21 0.21 0.28
1号平衡凸台 0.36 0.21 3.41 2.18
2号平衡凸台 0.22 0.28 2.18 1.98
), ArticleFig(id=1261270430120272230, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=表3, caption=

转子不同阶数下的不平衡响应

, figureFileSmall=null, figureFileBig=null, tableContent=
阶数 单位不平衡量位置 不平衡响应/10-6 m
模拟
风扇盘		 模拟低压
涡轮盘		 1号平
衡凸台		 2号平
衡凸台
1阶 模拟风扇盘 0.17 0.14 0.19 0.21
模拟低压涡轮盘 0.14 0.46 0.34 0.55
1号平衡凸台 0.19 0.34 0.42 0.51
2号平衡凸台 0.21 0.55 0.51 0.76
2阶 模拟风扇盘 1.33 0.21 0.82 0.42
模拟低压涡轮盘 0.21 0.27 0.19 0.29
1号平衡凸台 0.82 0.19 0.69 0.38
2号平衡凸台 0.42 0.29 0.38 0.35
3阶 模拟风扇盘 0.49 0.02 0.36 0.22
模拟低压涡轮盘 0.02 0.21 0.21 0.28
1号平衡凸台 0.36 0.21 3.41 2.18
2号平衡凸台 0.22 0.28 2.18 1.98
), ArticleFig(id=1261270430309015914, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Table 4, caption=

Comparison between test results and calculation results of critical speed

, figureFileSmall=null, figureFileBig=null, tableContent=
参数 第一阶 第二阶
计算结果/(r·min-1) 7 831 15 237
试验结果/(r·min-1) 7 524 15 375
计算误差/% 4.08 0.90
临界转速裕度/% 74.06 46.98
), ArticleFig(id=1261270430611005805, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=表4, caption=

临界转速试验结果与计算结果对比

, figureFileSmall=null, figureFileBig=null, tableContent=
参数 第一阶 第二阶
计算结果/(r·min-1) 7 831 15 237
试验结果/(r·min-1) 7 524 15 375
计算误差/% 4.08 0.90
临界转速裕度/% 74.06 46.98
), ArticleFig(id=1261270430812332398, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Table 5, caption=

High speed dynamic balancing process

, figureFileSmall=null, figureFileBig=null, tableContent=
D3测量值 平衡过程
转子挠度/μm 相位/(°)
86 102 初始状态
103 104 在1号凸台180°位置施加一定质量的配重后
70.5 80 根据计算,需在1号凸台353°位置加2.21倍配重,实际将180°位置的配重移至353°位置后
26.5 117 在1号凸台353°位置加2倍配重后
33.5 359 在1号凸台对应位置取材料后
), ArticleFig(id=1261270430933967217, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=表5, caption=

高速动平衡过程

, figureFileSmall=null, figureFileBig=null, tableContent=
D3测量值 平衡过程
转子挠度/μm 相位/(°)
86 102 初始状态
103 104 在1号凸台180°位置施加一定质量的配重后
70.5 80 根据计算,需在1号凸台353°位置加2.21倍配重,实际将180°位置的配重移至353°位置后
26.5 117 在1号凸台353°位置加2倍配重后
33.5 359 在1号凸台对应位置取材料后
), ArticleFig(id=1261270431143682422, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=EN, label=Table 6, caption=

High speed dynamic balance effect

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状态 D1 D2 D3 D4
平衡前/μm 84.5 30.0 86.0 83.0
平衡后/μm 23.0 20.0 33.5 16.0
平衡效果/% 72.78 33.33 87.88 80.72
), ArticleFig(id=1261270431479226745, tenantId=1146029695717560320, journalId=1146123166801305609, articleId=1261270373597832128, language=CN, label=表6, caption=

高速动平衡效果

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状态 D1 D2 D3 D4
平衡前/μm 84.5 30.0 86.0 83.0
平衡后/μm 23.0 20.0 33.5 16.0
平衡效果/% 72.78 33.33 87.88 80.72
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涡扇发动机悬臂高速转子动力学分析与试验
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聂卫健 1, 2 , 邓旺群 1, 2 , 杨晓光 3 , 王阁 1, 2 , 袁巍 1, 2
科学技术与工程 | 论文·航空、航天 2025,25(20): 8707-8713
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科学技术与工程 | 论文·航空、航天 2025, 25(20): 8707-8713
涡扇发动机悬臂高速转子动力学分析与试验
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聂卫健1, 2 , 邓旺群1, 2, 杨晓光3, 王阁1, 2, 袁巍1, 2
作者信息
  • 1 中国航发湖南动力机械研究所, 株洲 412002
  • 2 中国航空发动机集团航空发动机振动技术重点实验室, 株洲 412002
  • 3 北京航空航天大学能源与动力工程学院, 北京 100191

    • 聂卫健(1991—),男,汉族,江西抚州人,博士,高级工程师。研究方向:航空发动机转子动力学。E-mail:。

Dynamics Analysis and Experiment of Cantilever High-speed Rotor of Turbofan Engine
Wei-jian NIE1, 2 , Wang-qun DENG1, 2, Xiao-guang YANG3, Ge WANG1, 2, Wei YUAN1, 2
Affiliations
  • 1 AECC Hunan Aviation Powerplant Research Institute, Zhuzhou 412002, China
  • 2 Key Laboratory of Aero-engine Vibration Technology, Aero Engine Corporation of China, Zhuzhou 412002, China
  • 3 School of Energy and Power Engineering, Bei Hang University, Beijing 100191, China
出版时间: 2025-07-18 doi: 10.12404/j.issn.1671-1815.2404704
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摘要
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针对某涡扇发动机悬臂高速转子在结构设计阶段,提出空心轴和实心轴两种方案,基于梁单元有限元法分别建立带空心轴和带实心轴的转子动力学分析模型,并开展了临界转速和振型计算。计算结果表明:转子宜选用空心轴结构;在此基础上,进行了带空心轴的转子不平衡响应对特征位置上的不平衡量的敏感程度分析,为高速动平衡试验的平衡面选择提供了依据;最后,完成了带空心轴模拟转子在全转速范围内的动力特性试验和工作转速下的高速动平衡试验。转子平稳越过两阶弯曲临界转速并安全运行至工作转速,验证了转子采用空心轴结构以及动力学设计的合理性;与试验结果比较,建立的有限元模型计算误差不大于4.08%,很好地反映了转子的动力特性;高速动平衡后转子在工作转速下的挠度大幅降低,不低于33.33%;研究成果为真实低压转子的结构、动力学设计和试验研究提供了参考和技术支持,具有重要的工程价值。

涡扇发动机  /  高速转子  /  动力学分析  /  有限元  /  高速动平衡

Two schemes, hollow shaft and solid shaft were proposed for the cantilever high-speed rotor of a turbofan engine during the structural design stage. Based on the beam element finite element method, rotor dynamic analysis models with hollow shaft and solid shaft were established, and critical speed and vibration mode calculations were carried out. The calculation results show that hollow shaft structure is suitable for the rotor. Then, an analysis was conducted on the sensitivity of the unbalance response of a rotor with a hollow shaft to the unbalance amount at the characteristic position, providing a basis for the selection of balance surfaces in high-speed dynamic balance test. Finally, the dynamic characteristics test of the simulated rotor with hollow shaft within the full speed range and the high-speed dynamic balance test research at the working speed were completed. The rotor smoothly crossed the two orders bending critical speed and safely operated to the working speed, verifying the rationality of the rotor’s hollow shaft structure and dynamic design. Compared with the experimental results, the calculation error of the established finite element model is not more than 4.08%, which well reflects the dynamic characteristics of the rotor. After high-speed dynamic balancing, the deflection of the rotor at the working speed is significantly reduced, not less than 33.33%. The research results provide reference and technical support for the structural, dynamic design, and experimental research of real low-pressure rotors, and has important engineering value.

turbofan engine  /  high-speed rotor  /  dynamics analysis  /  finite element  /  high-speed dynamic balance
聂卫健, 邓旺群, 杨晓光, 王阁, 袁巍. 涡扇发动机悬臂高速转子动力学分析与试验. 科学技术与工程, 2025 , 25 (20) : 8707 -8713 . DOI: 10.12404/j.issn.1671-1815.2404704
Wei-jian NIE, Wang-qun DENG, Xiao-guang YANG, Ge WANG, Wei YUAN. Dynamics Analysis and Experiment of Cantilever High-speed Rotor of Turbofan Engine[J]. Science Technology and Engineering, 2025 , 25 (20) : 8707 -8713 . DOI: 10.12404/j.issn.1671-1815.2404704
正文
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转子系统是旋转机械重要的部件,很多学者开展了相关研究,包括动力学分析[1-3]、故障研究[4-5]以及动力特性试验[6]等。航空发动机是十分精密的旋转机械,在其转子结构设计阶段,需综合考虑支承布局、结构形式、质量分布等多种因素,以满足转子动力学设计要求[7]。因此,常会进行多种不同结构形式的转子设计,并通过计算和对比分析,并经过试验验证选取一种合理的结构。现代中小型航空发动机的转子朝着高转速、大长径比、复杂结构的方向发展,建立能反映转子真实动力特性的计算模型是进行分析的基础。早期多采用传递矩阵法[8-9],这种方法需要依次建立转轴界面状态参数的传递矩阵关系,矩阵阶数不随转子系统的自由度增加而增加,使得对计算机的内存要求不高。近年,经过诸多学者不断改进,衍生发展了传递矩阵-直接积分法[10]、整体传递矩阵法[11]及子结构传递矩阵法[12]等方法。然而,随着航空科学技术的发展,转子工作条件和边界条件越来越复杂,传递矩阵法因计算误差较大无法满足工程需求。
因转子结构复杂,加工精度要求高、工艺复杂、费用昂贵,在研制初期直接采用真实转子开展动力学试验的风险较大,一旦试验失败,将造成经济损失,同时也影响发动机研制周期。因此,先设计动力特性基本一致的模拟转子,开展理论分析[13-15]和试验研究[16],将研究成果应用于真实转子的结构设计和动力学设计。此外,由于加工和装配等因素,使得转子在试验过程中容易因不平衡量较大发生振动故障,需进行高速动平衡以减小振动,针对高速动平衡,中国航发湖南动力机械研究所开展了多型高速柔性转子动平衡试验[17-18],可以提供一定的参考。但不同结构的转子对不平衡量的敏感程度和动平衡方法又有所差异,需要根据分析和实际试验情况进行。
鉴于此,针对传递矩阵法及其衍生方法计算误差较大问题,提出基于梁单元的二维有限元建模方法,分别建立带空心轴和带实心轴的转子动力学分析模型,开展前三阶临界转速、振型计算和转子不平衡响应分析,基于计算结果优选出的带空心轴转子,完成全转速范围内的动力特性试验和工作转速下的高速动平衡试验研究,验证计算结果的准确性和转子结构设计和动力学设计的合理性,为真实低压转子的结构、动力学设计和试验研究提供参考和技术支持,具有重要的工程价值。
1 转子结构
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带空心轴和带实心轴的模拟低压转子结构如图1所示。两个模拟低压转子除低压轴的结构形式不一样之外,其他结构均一致。整个转子由模拟风扇盘、模拟低压涡轮盘和低压轴等主要零部件组成,模拟风扇盘、模拟低压涡轮盘的转动惯量、质量参数与真实盘保持一致,转子采用0-2-1的支承方式,模拟风扇盘悬臂。
2 动力学分析
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2.1 有限元模型
基于梁单元的二维单元有限元建模方法,首先建立各部件(模拟风扇盘、低压轴、模拟低压涡轮盘以及轴承)的独立模型,分别用梁单元、轴承单元模拟转子的主体和支承,然后在各部件模型之间建立刚性连接单元。同时,针对模拟低压转子的结构特点,在模型前处理时对转子的结构进行一些简化,对细小结构(如倒圆角、小孔等)简化处理,使单元网格具有更好的均匀性,提高计算精度。建立的带空心轴和带实心轴的模拟低压转子有限元模型,如图2所示,带空心轴的模拟低压转子共计557个梁单元、3个轴承单元和14个刚性连接单元,带实心轴的模拟低压转子共计485个梁单元、3个轴承单元和14个刚性连接单元。各支点的支承刚度如表1所示。
2.2 临界转速分析
带空心轴和带实心轴的转子临界转速及其裕度计算结果如表2所示。
临界转速裕度计算公式为
$\mathrm{临}\mathrm{界}\mathrm{转}\mathrm{速}\mathrm{裕}\mathrm{度}=\frac{\left|\mathrm{额}\mathrm{定}\mathrm{工}\mathrm{作}\mathrm{转}\mathrm{速}-\mathrm{临}\mathrm{界}\mathrm{转}\mathrm{速}\right|}{\mathrm{额}\mathrm{定}\mathrm{工}\mathrm{作}\mathrm{转}\mathrm{速}}\times 100\mathrm{\%}$
由表2可知,转子采用空心轴时,只需要跨两阶临界转速工作,但采用实心轴时,需要跨3阶临界转速工作,并且第3阶转速的裕度不足5%,工作转速十分靠近第3阶临界转速,第三阶模态是影响转子工作转速振动的主要模态,给转子动力特性试验带来很大的困难;带空心轴和带实心轴模拟低压转子前两阶临界转速接近,但第3阶临界转速相差较大,表明低压轴的结构形式对前两阶临界转速基本没有影响,但对第3阶临界转速的影响显著;从临界转速裕度角度来看,采用实心轴的转子第3阶临界转速裕度不足5%,导致工作转速靠近临界转速,在此转速下长时间工作容易导致振动大,引发严重碰磨等故障。因此,从临界转速分布及其裕度角度考虑,低压轴宜选用空心结构。
2.3 振型分析
带空心轴和带实心轴转子前三阶振型计算结果分别如图3和图4所示。
由图3、图4可知,不论是带空心轴,还是带实心轴,转子前三阶振型都为弯曲振型,表现出典型的高速柔性转子特性;带空心轴与带实心轴的转子的前三阶振型基本一致,表明低压轴结构形式对转子前三阶振型基本没有影响。
2.4 不平衡响应分析
根据前述的理论分析结果,转子选用空心轴结构,基于此开展不平衡响应分析,获取转子在临界转速和工作转速下的不平衡响应对特征位置上的不平衡量敏感程度,为高速动平衡试验选择平衡面提供理论依据。分别在转子4个特征位置(模拟风扇盘、模拟低压涡轮盘、1号平衡凸台、2号平衡凸台)上依次施加1 g·mm的单位不平衡量,计算得到转子在工作转速范围内的不平衡响应,如图5所示。
从图5可知,单位不平衡量引起的4个特征位置的1阶、2阶和工作转速下的不平衡响应值,如表3所示。
由表3可知,2号平衡凸台上的单位不平衡量引起4个特征位置的1阶不平衡响应都最大,可见,转子的1阶不平衡响应对2号平衡凸台上的不平衡量最敏感,因此,如转子的1阶不平衡响应超过允许值,可优先选择2号平衡凸台上作为平衡面;模拟风扇盘上的单位不平衡量引起3个特征位置的2阶不平衡响应最大,其次是1号平衡凸台,可见,转子的2阶不平衡响应对模拟风扇盘上的不平衡量最敏感,其次是1号平衡凸台,因此,如果转子的2阶不平衡响应超过允许值,可优先选择模拟风扇盘作为平衡面,其次选1号平衡凸台;1号、2号平衡凸台上的单位不平衡量都能引起4个特征位置在工作转速下的较大不平衡响应,尤其引起低压轴上的很大不平衡相应,因此,如果转子在工作转速下的不平衡响应超过允许值,选择1号或2号平衡凸台上作为平衡面就能非常有效地控制转子挠度。
3 动力学试验
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3.1 动力特性试验
通过动力学试验,对计算结果进行验证。试验在位于中国航发湖南动力机械研究所的航空发动机振动技术重点实验室的卧式高速旋转试验器上进行,试验器主要包括驱动系统、真空系统、润滑系统和测试系统等组成,试验过程中,由真空系统提供满足试验条件的真空环境,润滑系统提供轴承润滑。试验数据由实验室测试系统(laboratory measurement system,LMS)测得。
转子通过轴承座安装在刚性支座上,刚性支座通过T型螺栓与试验平台连接紧固。试验过程中,测量转子的挠度,带空心轴转子的安装及测试参数如图6所示,试验中,通过振动位移传感器D1~D4测量转子轴中间部位①、②、③的转子挠度,D1测量位置①垂直方向挠度,D2测量位置③垂直方向挠度,D3、D4分别测量位置②垂直和水平方向的挠度,转子安装实物照片如图7所示。
通过试验得到各位移随转速的变化曲线,如图8所示。基于试验结果(取4个测点的测量值平均值),得到计算结果的误差,如表4所示。
计算误差的计算公式为
$\mathrm{计}\mathrm{算}\mathrm{误}\mathrm{差}=\frac{\left|\mathrm{计}\mathrm{算}\mathrm{结}\mathrm{果}-\mathrm{试}\mathrm{验}\mathrm{结}\mathrm{果}\right|}{\mathrm{试}\mathrm{验}\mathrm{结}\mathrm{果}}\times 100\mathrm{\%}$
相比于试验结果,临界转速计算误差不大于4.08%,计算模型很好地反映了转子真实动力特性;经试验验证,采用空心轴结构的转子的临界转速裕度大于20%,能够满足临界转速的要求;转子能够运行至工作转速,初步验证了转子结构整体设计的合理性。
3.2 高速动平衡试验
通过前述不平衡响应分析,为高速动平衡平衡面的选择提供了依据,但因无法预知转子实际的不平衡量,故计算结果得到的不平衡响应幅值具有一定的差异,为此,需要开展实际的高速动平衡试验。由图8可知,由D1、D3和D4传感器测得的转子在工作转速下的挠度均不小于83 μm,转子虽可以运行至工作转速,但在工作转速下的挠度比过临界时的挠度还大,不宜在该转速下长时间工作,因此,需要进行高速动平衡。
根据转子实际复杂结构,总结其动平衡难点如下。
(1)转子采用空心轴结构形式,加工精度很难达到要求,存在初始不平衡量。
(2)转子长径比大于20,振型带来的附加不平衡量较大。
(3)转子上平衡面仅有1号凸台和2号凸台,且凸台高度仅有1.5 mm,动平衡去材料量十分有限。
基于前面的不平衡响应分析,在工作转速附近进行动平衡,选择1号凸台作为平衡面,平衡转速选择26 000 r/min,测量面选择D3。平衡过程如表5所示。
高速平衡后,各位移传感器测得的转子挠度随转速变化曲线如图9所示。
对比图8和图9可知,高速动平衡后,各传感器测得的工作转速下的转子挠度均有所下降。对比高速动平衡前后各测点工作转速下的转子挠度值(表6),平衡后,工作转速下转子挠度降幅不低于33.33%,高速动平衡取得良好效果。
4 结论
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针对不同结构的低压轴转子开展了临界转速、振型计算和转子不平衡响应分析,完成了优选的带空心轴结构转子在全转速范围内的动力特性试验和工作转速下的高速动平衡试验研究,为真实低压转子的结构、动力学设计和试验研究提供了参考和技术支持,具有重要的工程价值,得出如下主要结论。
(1)从临界转速分布及其裕度角度考虑,低压轴须采用空心轴的结构形式;并经试验验证了转子结构设计和动力学设计的合理性。
(2)低压轴结构形式对转子的前两阶临界转速几乎没有影响,对第3阶临街转速的影响较为显著,此外,对前3阶振型没有实质性影响。
(3)相比于试验结果,基于梁单元有限元模型的转子临界转速计算误差小于5%,建立的有限元模型很好地反映了转子的真实动力特性,能够较好地满足工程需要。
(4)不平衡响应分析可为高速动平衡时平衡面的选取提供理论依据,但仍需开展试验达到减振的目的,针对转子的高速动平衡效果不低于33.33%,效果良好。
基金
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  • 中国航发创新基金(CXPT-2022-031)
文献
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2025年第25卷第20期
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doi: 10.12404/j.issn.1671-1815.2404704
  • 接收时间：2024-06-24
  • 首发时间：2026-05-13
  • 出版时间：2025-07-18
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  • 收稿日期：2024-06-24
  • 修回日期：2025-04-10
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中国航发创新基金(CXPT-2022-031)
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    1 中国航发湖南动力机械研究所, 株洲 412002
    2 中国航空发动机集团航空发动机振动技术重点实验室, 株洲 412002
    3 北京航空航天大学能源与动力工程学院, 北京 100191
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