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Article(id=1228282197036172041, tenantId=1146029695717560320, journalId=1227999626482147330, issueId=1228282191159952029, articleNumber=null, orderNo=null, doi=10.16579/j.issn.1001.9669.2025.10.007, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1706025600000, receivedDateStr=2024-01-24, revisedDate=1710691200000, revisedDateStr=2024-03-18, acceptedDate=null, acceptedDateStr=null, onlineDate=1770774896153, onlineDateStr=2026-02-11, pubDate=1760457600000, pubDateStr=2025-10-15, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1770774896153, onlineIssueDateStr=2026-02-11, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1770774896153, creator=13701087609, updateTime=1770774896153, updator=13701087609, issue=Issue{id=1228282191159952029, tenantId=1146029695717560320, journalId=1227999626482147330, year='2025', volume='47', issue='10', pageStart='1', pageEnd='157', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=1, specialIssue=null, createTime=1770774894751, creator=13701087609, updateTime=1770775890381, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1228286367227118244, tenantId=1146029695717560320, journalId=1227999626482147330, issueId=1228282191159952029, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1228286367227118245, tenantId=1146029695717560320, journalId=1227999626482147330, issueId=1228282191159952029, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=63, endPage=70, ext={EN=ArticleExt(id=1228282197724037918, articleId=1228282197036172041, tenantId=1146029695717560320, journalId=1227999626482147330, language=EN, title=Vibration characteristic analysis of rolling bearing outer ring looseness fault based on dynamics, columnId=1228282191914926752, journalTitle=Journal of Mechanical Strength, columnName=Vibration·Noise·Monitoring·Diagnosis, runingTitle=null, highlight=null, articleAbstract=

Rolling bearing looseness faults are likely to induce transmission system fault. Considering the factors such as nonlinear contact force of rolling bearings, rub-impact force, damping force between outer ring and housing, a six-degree-of-freedom nonlinear dynamics model was established under the fault of rolling bearing outer ring looseness, and the vibration characteristics of rolling bearing outer ring looseness were analyzed. The simulation results show that the characteristic frequency of the outer ring looseness fault is presented as the rotational frequency of the rotating shaft and its multiple components, and the actual tested wind power bearing ring fault data verifies the accuracy of the model. The results of this paper show that the rolling bearing outer ring looseness is caused by loosing between the outer ring and the housing, and the cyclic impact and friction between the outer ring and housing are formed under the unbalance force with the rotational speed of the shaft and its harmonics. The research results provide a theoretical basis for realizing the mechanism analysis of rolling bearing outer ring looseness and fault diagnosis of the rolling bearing.

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TENG Wei, E-mail:
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滚动轴承跑外圈故障容易诱发传动系统失效。考虑滚动轴承非线性接触力、碰摩力、外圈与轴承座之间的阻尼力等因素，建立了滚动轴承跑外圈故障下的六自由度非线性动力学模型，讨论了跑外圈故障时碰摩力和不平衡力的主导关系，分析了滚动轴承跑外圈故障时的振动特性。仿真结果表明，当发生轴承跑外圈故障时，其特征频率呈现为转轴的转动频率及其倍频成分，实际测试的风电轴承跑外圈故障数据验证了模型的准确性。研究结果表明，滚动轴承跑外圈故障是由于外圈和轴承座之间出现松动，在不平衡作用力驱使下外圈与轴承座之间产生以转频倒数为单位的周期性冲击与摩擦造成的，研究结果可为滚动轴承跑外圈的故障机制分析与故障诊断提供依据。

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滕伟，男，1981年生，山东乳山人，博士，教授；主要研究方向为能源电力装备状态监测、故障诊断与寿命预测；E-mail: 。
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贾向阳，男，1997年生，河南上蔡人，在读硕士研究生；主要研究方向为滚动轴承动力学建模、设备状态监测与故障诊断；E-mail：。

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贾向阳，男，1997年生，河南上蔡人，在读硕士研究生；主要研究方向为滚动轴承动力学建模、设备状态监测与故障诊断；E-mail：。

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贾向阳，男，1997年生，河南上蔡人，在读硕士研究生；主要研究方向为滚动轴承动力学建模、设备状态监测与故障诊断；E-mail：。

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tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1228282197036172041, language=EN, label=Fig.16, caption=Envelope spectrum of the field data, figureFileSmall=ktc1y3yeBETkNb5Q5gy13Q==, figureFileBig=R9o4JIak7c4WAULvJNaKpQ==, tableContent=null), ArticleFig(id=1228282215637910031, tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1228282197036172041, language=CN, label=图16, caption=现场数据包络谱, figureFileSmall=ktc1y3yeBETkNb5Q5gy13Q==, figureFileBig=R9o4JIak7c4WAULvJNaKpQ==, tableContent=null), ArticleFig(id=1228282215751156242, tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1228282197036172041, language=EN, label=Tab.1, caption=

Main parameters of SKF6330

, figureFileSmall=null, figureFileBig=null, tableContent=
参数 Parameter值 Value
节圆直径Pitch Circle Diameter Dp/mm235
滚动体直径Roller diameter Db/mm85
内圈直径Inner diameter Di/mm152
外圈直径Outer diameter Do/mm320
滚动体个数Roller number Z9
接触角Contact angle α/（°）0
), ArticleFig(id=1228282215860208152, tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1228282197036172041, language=CN, label=表1, caption=

SKF6330 主要参数

, figureFileSmall=null, figureFileBig=null, tableContent=
参数 Parameter值 Value
节圆直径Pitch Circle Diameter Dp/mm235
滚动体直径Roller diameter Db/mm85
内圈直径Inner diameter Di/mm152
外圈直径Outer diameter Do/mm320
滚动体个数Roller number Z9
接触角Contact angle α/（°）0
), ArticleFig(id=1228282215935705627, tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1228282197036172041, language=EN, label=Tab.2, caption=

Main parameters of the simulation model

, figureFileSmall=null, figureFileBig=null, tableContent=
质量Mass刚度Stiffness阻尼Damping
mo =13.8 kgko =5.5×108 N/mco =1 200 N·s/m
mi =25 kgkf =2×108 N/mcf =1 200 N·s/m
mb =3.5 kgkb =17.5×108 N/m—
), ArticleFig(id=1228282216015397406, tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1228282197036172041, language=CN, label=表2, caption=

仿真模型的主要参数

, figureFileSmall=null, figureFileBig=null, tableContent=
质量Mass刚度Stiffness阻尼Damping
mo =13.8 kgko =5.5×108 N/mco =1 200 N·s/m
mi =25 kgkf =2×108 N/mcf =1 200 N·s/m
mb =3.5 kgkb =17.5×108 N/m—
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基于动力学的滚动轴承跑外圈故障振动特性分析
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贾向阳 1 , 滕伟 1 , 孔令行 2 , 彭迪康 1 , 马志勇 1 , 柳亦兵 1
机械强度 | 振动·噪声·监测·诊断 2025,47(10): 63-70
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机械强度 | 振动·噪声·监测·诊断 2025, 47(10): 63-70
基于动力学的滚动轴承跑外圈故障振动特性分析
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贾向阳1 , 滕伟1 , 孔令行2, 彭迪康1, 马志勇1, 柳亦兵1
作者信息
  • 1.华北电力大学　电站能量传递转换与系统教育部重点实验室，北京　102206
  • 2.中国电力科学研究院有限公司，北京　100192

    • 贾向阳，男，1997年生，河南上蔡人，在读硕士研究生；主要研究方向为滚动轴承动力学建模、设备状态监测与故障诊断；E-mail：。

通讯作者:

滕伟，男，1981年生，山东乳山人，博士，教授；主要研究方向为能源电力装备状态监测、故障诊断与寿命预测；E-mail: 。
Vibration characteristic analysis of rolling bearing outer ring looseness fault based on dynamics
Xiangyang JIA1 , Wei TENG1 , Lingxing KONG2, Dikang PENG1, Zhiyong MA1, Yibing LIU1
Affiliations
  • 1.Key Laboratory of Power Station Energy Transfer, Conversion and System, Ministry of Education, North China Electric Power University, Beijing 102206, China
  • 2.China Electric Power Research Institute Co., Ltd., Beijing 100192, China
出版时间: 2025-10-15 doi: 10.16579/j.issn.1001.9669.2025.10.007
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摘要
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滚动轴承跑外圈故障容易诱发传动系统失效。考虑滚动轴承非线性接触力、碰摩力、外圈与轴承座之间的阻尼力等因素，建立了滚动轴承跑外圈故障下的六自由度非线性动力学模型，讨论了跑外圈故障时碰摩力和不平衡力的主导关系，分析了滚动轴承跑外圈故障时的振动特性。仿真结果表明，当发生轴承跑外圈故障时，其特征频率呈现为转轴的转动频率及其倍频成分，实际测试的风电轴承跑外圈故障数据验证了模型的准确性。研究结果表明，滚动轴承跑外圈故障是由于外圈和轴承座之间出现松动，在不平衡作用力驱使下外圈与轴承座之间产生以转频倒数为单位的周期性冲击与摩擦造成的，研究结果可为滚动轴承跑外圈的故障机制分析与故障诊断提供依据。

滚动轴承  /  外圈跑圈  /  动力学模型  /  故障特征

Rolling bearing looseness faults are likely to induce transmission system fault. Considering the factors such as nonlinear contact force of rolling bearings, rub-impact force, damping force between outer ring and housing, a six-degree-of-freedom nonlinear dynamics model was established under the fault of rolling bearing outer ring looseness, and the vibration characteristics of rolling bearing outer ring looseness were analyzed. The simulation results show that the characteristic frequency of the outer ring looseness fault is presented as the rotational frequency of the rotating shaft and its multiple components, and the actual tested wind power bearing ring fault data verifies the accuracy of the model. The results of this paper show that the rolling bearing outer ring looseness is caused by loosing between the outer ring and the housing, and the cyclic impact and friction between the outer ring and housing are formed under the unbalance force with the rotational speed of the shaft and its harmonics. The research results provide a theoretical basis for realizing the mechanism analysis of rolling bearing outer ring looseness and fault diagnosis of the rolling bearing.

Rolling bearing  /  Outer ring looseness  /  Dynamical model  /  Fault characteristic
贾向阳, 滕伟, 孔令行, 彭迪康, 马志勇, 柳亦兵. 基于动力学的滚动轴承跑外圈故障振动特性分析. 机械强度, 2025 , 47 (10) : 63 -70 . DOI: 10.16579/j.issn.1001.9669.2025.10.007
Xiangyang JIA, Wei TENG, Lingxing KONG, Dikang PENG, Zhiyong MA, Yibing LIU. Vibration characteristic analysis of rolling bearing outer ring looseness fault based on dynamics[J]. Journal of Mechanical Strength, 2025 , 47 (10) : 63 -70 . DOI: 10.16579/j.issn.1001.9669.2025.10.007
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0　引言
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作为旋转机械中最重要的支撑部件之一，滚动轴承广泛应用于精密机床、车辆、航空航天、风力发电等领域。滚动轴承在长期的工作中易发生故障[1]，如点蚀、磨损、跑外圈等。其中轴承跑外圈故障对设备造成的负面影响巨大，轴承跑外圈是指轴承外圈与配合的轴承座发生了蠕动，逐步磨损后配合松动，进而加剧配合零件的磨损，降低机器精度。另外，轴承跑外圈引起的相对运动会造成振动超标、异响、轴承座温度升高、输入转矩增加等现象，这些缺点进一步对旋转设备的运行和可靠性产生不利影响[2]。开展滚动轴承跑外圈故障动力学模型研究，对于揭示跑外圈故障机制、开展轴承故障特征提取具有重要意义。
国内外学者对滚动轴承动力学的研究主要聚焦在局部故障、分布式故障、滚动体打滑等故障的基础上建立动力学模型，对其故障机制、振动特性做出详尽的分析[3][4]104266[5]763-769。滚动轴承跑外圈的故障现象也引起了工业界和学术界的广泛关注。风能专委会[6]对风电机组轴承跑外圈问题进行了分析并提出建议，对于轴承跑外圈问题往往以调整间隙的方法解决。远景能源有限公司[7]提出的轴承外圈止动装置及其制造、安装与方法专利已初步应用于风电齿轮箱。
通常认为，轴承与轴承座的配合间隙与滚动轴承跑外圈故障存在密切联系。ZHANG等[8]针对转子-轴承系统，提出配合间隙为变量的碰摩力学模型，并分析了碰摩对耦合弯曲扭转系统动态特性的影响。LIU等[9]通过建立动力学模型，分析了轴承座和滚动轴承外圈之间的装配间隙对外圈振动特性的影响，结果表明，过盈配合下外圈高频振动不明显，间隙配合会增加外圈的高频振动。HONG等[10]对转子的间歇性碰摩进行了试验研究，发现间歇性碰摩会增加转子的模态频率和临界转速，从而增加转子系统的不稳定性。ZHAO等[11]受到转子容易发生碰摩故障的启发，提出了一种基于数据驱动和NOFRF（非线性输出频率响应函数）的轴承-转子健康评估方法，对具有摩擦冲击的轴承转子的振动和稳定性进行了动力学分析。WANG等[12]针对轴承外圈与轴承座配合松动故障，建立了转子-滚动轴承动力学模型，通过试验和仿真分析，得到了配合松动故障的振动响应呈周期性冲击的特点。ZHOU等[13]考虑到旋转机械发生的碰摩故障会导致其振动响应出现周期性调制的特点，通过动力学仿真和真实数据，证明了这种周期性调制携带着与摩擦相关的内在故障信息，揭示了调制模式和傅里叶频谱之间的关系。石怀涛等[14]基于全陶瓷球轴承在一定温域下，轴承外圈和轴承座之间配合间隙会发生变化的性质，将配合间隙随温度变化引入全陶瓷球轴承-轴承座动力学模型，发现了轴承振动随温度升高而增加的现象，且其振动呈非线性变化的趋势。CHEN等[15]419-440考虑到轴承外圈和轴承座之间的配合间隙，建立了具有轴承配合间隙故障的动力学模型，通过仿真和试验，说明了配合间隙、转子不平衡度的增加会加剧周期性冲击，而轴承外圈紧固力矩增加则抑制冲击振动的发生。TENG等[16]针对某风电机组发电机轴承跑外圈故障进行了诊断，认为滚动轴承跑外圈的故障特征体现在外圈振动信号的频谱会出现转频10次以上的谐波。
上述研究在松动情况下积累了丰富的动力学建模经验，但存在以下两点不足：①动力学模型未从数据层面对导致跑外圈故障的碰摩力进行刻画与分析，没有从故障机制角度解释碰摩力对跑外圈振动特性的直接影响，作为跑外圈故障的直接影响因素，碰摩力还需进一步的分析；②缺乏详尽的轴承跑外圈故障现象下的振动特性与激励力的关联关系描述，忽略了在不同跑外圈故障程度下，对外圈所受不平衡力和碰摩力主导关系的讨论。这导致跑外圈理论模型与工业界的振动现象吻合性不足，使得跑外圈的故障诊断往往依赖于经验方法，缺乏从故障机制层面建立可以信赖的理论依据。
针对上述问题，本文对滚动轴承跑外圈行为进行剖析，建立轴-滚动轴承-轴承座的动力学模型，详细刻画径向相对位移与配合间隙之间的相对关系对跑外圈故障下碰摩力的影响，讨论跑外圈故障时不平衡力和碰摩力的主导关系，从机制上解释轴承跑外圈故障时的故障特征，并以现场故障数据验证本文模型的正确性。本文研究结果可为滚动轴承跑外圈的故障机制分析与故障诊断提供依据。
1　滚动轴承外圈跑圈动力学模型
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图1所示为滚动轴承的基本结构。滚动轴承在理想情况下是由基孔制配合的内圈和轴径、基轴制的外圈和轴承座相互装配而成的。健康工况下要求内圈与轴之间，外圈与轴承座座孔之间紧密配合，不允许有相互打滑的情况出现，当出现打滑现象时称为跑圈。跑圈现象会造成轴承及其配合件加速磨损，产生噪声，影响机器正常运转，严重者导致传动系统失效。当轴承座和外圈因安装不当、磨损等原因出现松动时，可能会造成相对较小的残余不对中，进而导致径向振动增加，即对系统造成不平衡的影响[17]。因此可将滚动轴承跑外圈动力学建模按照碰摩力模型、轴承接触力模型、阻尼力模型三部分展开。
1.1　碰摩力模型
当轴承外圈出现跑圈故障时，外圈和轴承座之间会出现相对滑动。图2显示了轴承外圈和轴承座之间的受力状态，跑圈时由于轴承外圈和轴承座之间的配合松动，轴承外圈相对轴承座的中心会发生偏移。图2中，O1为轴承座中心；O2为轴承外圈中心；Q为外圈和轴承座碰摩接触点的位置；Qn为法向冲击力；Qt为切向摩擦力；Qnx、Qtx分别为法向冲击力和切向摩擦力在x方向上的分量；Qny、Qty分别为法向冲击力和切向摩擦力在y方向上的分量。
在t时刻，xo、yo分别为轴承外圈在x、y方向上的位移；xb、yb分别为轴承座在x、y方向上的位移；c为轴承外圈与轴承座间的配合间隙。则在x、y方向上外圈相对于轴承座的位移[5]763-769分别为
在x、y方向，外圈相对于轴承座的速度分别为
在跑外圈工况下中，外圈和轴承座之间的径向相对位移r可表示为
当径向相对位移r大于外圈与轴承座之间的配合间隙c时，轴承外圈与轴承座就会出现碰摩现象，假设此时法向冲击力Qn与x轴的夹角为θ，则有
假设外圈和轴承座之间的摩擦因数为f，碰摩时在切向方向上会产生切向摩擦力，受力情况如图2所示。在现场的实际轴承跑外圈故障中，往往能观察到外圈和轴承座有明显的擦伤痕迹，这是由于外圈和轴承座之间出现相对运动，引起的法向冲击和切向摩擦所造成的擦伤。假设外圈和轴承座之间的摩擦符合库仑摩擦定律，轴承座相对于外圈的冲击力和摩擦力方向为正方向，则法向冲击力[15]426-427可表示为
式中，kr为轴承座径向刚度。将法向冲击力进行分解，投影到x、y方向上，即
此时，外圈相对于轴承座的切向速度Δv和摩擦力Qt分别为
由式（8）可知，摩擦力Qt与相对速度Δv方向一致。如果Δv>0，说明摩擦力Qt与正方向相同，反之则相反。
将切向摩擦力进行分解，投影到x、y方向上，即
综上所述，在跑外圈故障下，外圈所受的力在x、y方向上可以表示为
式（10）表明轴承外圈在x、y方向上所受的力具有很强的非线性。除此之外，根据赫兹接触理论，轴承外圈会受到滚动体施加的载荷，因此需要对滚动轴承进行接触力分析。
1.2　轴承接触力模型
由于轴上部件重力和负载的作用，外圈滚道可被区分为承载区和非承载区，当滚动体处于不同的位置时，其变形量会对滚动体的径向接触变形量产生影响。
式（11）用来描述第j个滚动体的径向接触变形量，其可视为内圈相对于外圈在x、y方向上的相对振动响应、径向间隙e、第j个滚动体角位置δj的函数[18]183-184，为
式中，j=1、2、3、…、Z，Z为滚动体的数量。其中，第j个滚动体在t时刻的角位置为保持架转速、时间t和滚动体初始角位置的函数[18]183-184，为
式中，ωc为保持架转速；ϕ0为第1个滚动体的初始角位置。其中[18]183-184，
式中，Db、Dp、α分别为滚动体的直径、轴承的节径和接触角；ωs为轴旋转角频率；n为轴的转速。
根据赫兹接触理论，第j个滚动体与外圈滚道之间的非线性接触力fj [18]183-184可表示为
式中，kb为滚动体与内、外圈的总接触刚度系数。
将非线性接触力fj投影到x、y方向，可得到在x、y方向上的非线性接触力[18]184-185为
由于只有接触物体时才会产生弹性变形，即当接触变形量δj>0时才会有接触力的产生，所以为了判断外圈滚道是否受到了接触力影响，引入开关函数βj对其进行描述[4]104266，为
滚动轴承在运转过程中，经过承载区的滚动体个数发生变化，每个滚动体与内、外圈之间的非线性接触力也随角位置变化而变化。因此，所有滚动体对外圈的接触力在x、y方向上的力分别为
1.3　阻尼力模型
在轴承运转过程中，由于锁紧螺母或轴承端盖与轴承外圈之间产生干摩擦，轴承外圈因此干摩擦产生摩擦阻尼，假设此摩擦阻尼为黏性阻尼，外圈所受到的阻尼力为
式中，Fdx、Fdy分别为外圈所受阻尼力在x、y方向上的分力。
1.4　滚动轴承跑外圈动力学建模
图3所示为根据集中参数法建立的轴-滚动轴承-轴承座动力学模型，mo、mi、mb分别为外圈质量、内圈轴系质量、轴承座质量；ko、kf分别为轴承外圈和轴承座之间的刚度、轴承座的刚度；co、cf分别为轴承外圈和轴承座之间的阻尼、轴承座的阻尼。
为能够合理地匹配试验信号中的低频成分，以上参数可以进行适当的调整。在该模型中，引入的质量-弹簧-阻尼系统可以仿真x、y方向的高频成分的振动响应。其中，xo、yo分别为外圈的振动响应，xi、yi分别为内圈的振动响应，xb、yb分别为轴承座的响应。调整以上参数，使得建模仿真中得到的高频振动响应与实际的振动响应相匹配。
在跑外圈故障工况下，内圈及轴的运转中心相对轴承座的中心会出现偏离，因此会出现偏心现象，此时需要引入不平衡力，内圈及轴的动力学方程为
对于轴承外圈，动力学方程为
对于轴承座，动力学方程为
2　滚动轴承外圈跑圈故障仿真分析
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2.1　仿真条件
在Matlab软件中，采用4阶龙格-库塔法对建立的滚动轴承跑外圈动力学模型进行求解，仿真步长为1/512 00。模拟轴承型号为SKF6330，其具体参数如表1所示。构建的动力学模型主要参数如表2所示。其中，刚度数据根据轴承材料与结构形态并参照文献[18]184-185计算得到，模拟轴转速为1 430 r/min，与第3节现场故障数据转速一致，输出外圈在y方向上的加速度信号，并根据输出仿真信号进行故障分析。
2.2　仿真结果分析
取转子-滚动轴承-轴承座模型的外圈拧紧力矩引起的摩擦效应等效黏性阻尼为1 200 N·s/m，滚动轴承径向间隙为0.3 mm，计算此时外圈y方向上的振动响应，选取仿真稳定期间，即跑外圈故障下振动稳定期间的结果进行分析，仿真结果如图4~图6所示。其中，图5、图6分别代表y方向振动加速度信号的频谱图和包络谱图。由图4可以看出，在y方向振动加速度信号时域图中出现了一系列的周期性脉冲，该时间间隔为0.042 s，对应的频率为23.8 Hz，与动力学模型设定的转频值相等。在频谱图和包络谱中均出现了转频fr的倍频成分。
图7为外圈y方向所受到的碰摩力时域图，图8为其对应的频谱图。由图7可以看出，外圈y方向所受的碰摩力为类正弦曲线，伴随着轴承跑外圈，外圈和轴承座发生周期性碰摩，其周期间隔为0.042 s，对应的频率为23.8 Hz，与轴的转频值相等。图8、图9所示为碰摩力的频谱分析和包络分析结果。由图8、图9均可以看到转频的倍频成分。
结合外圈y方向的振动加速度和碰摩力结果，可以认为，滚动轴承跑外圈故障引起的振动响应是由于外圈与轴承座发生了周期性碰摩产生的周期性冲击。在滚动轴承与轴承座之间发生配合松动时，间隙的存在使得滚动轴承受到的不平衡力失去约束，在不平衡力的驱使下，轴承外圈会被周期性地抬起，轴承外圈不再与轴承座紧密接触，而是在接触点处发生碰摩，即发生周期性的冲击和摩擦。
2.3　不同故障程度下的模拟分析
考虑到跑外圈故障是由于外圈与轴承座配合松动引起的，为此计算了外圈与轴承座不同松动间隙下的振动响应，间隙分别为0.1、0.2、0.3、0.4、0.5、0.6、0.7、0.8、0.9 mm，然后计算了外圈振动加速度的均方根（Root Mean Square, RMS）。为证明以上松动间隙下的跑外圈动力学仿真的正确性，分别计算了仿真数据的包络谱，如图10所示。由图10可以看到，包络谱均出现了10次以上的转频谐波成分，并且随着松动间隙的增大，转频谐波成分的峰值呈上升趋势。这也说明随着故障程度加深，振动现象呈持续加剧的态势。
图11为不同松动间隙下对应的RMS值。由图11可知，随着松动间隙的增加，外圈和轴承座之间的振动响应的有效值呈上升态势，与假定的松动程度加剧相符合。图12为间隙为0.11 mm时的振动响应。由图12可以观察到与图4存在一定差异，其原因是轴承跑外圈时由于间隙的存在，外圈受到不平衡力作为激励，使得外圈发生偏移，与轴承座发生碰摩。当间隙较小时，作用于外圈的不平衡激励也在减小，并且外圈受到的碰摩力相对于不平衡激励更小，即不平衡力占据了故障现象的主要原因，其振动响应呈类似正弦曲线的响应，而没有周期性的剧烈冲击。
3　现场数据分析验证
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以某风场2 MW风电机组中发电机轴承为例，该轴承型号为SKF6330，仿真轴承型号与其型号一致。该轴承的故障工单显示发电机轴承外圈出现了擦伤现象，如图13所示。其振动数据由安装在发电机轴承座上的加速度传感器采集所得，采样频率为51 200 Hz，采样时间为2 s，采样期间发电机转速为1 430 r/min，即发电机轴旋转频率为23.8 Hz，机组处于正常并网发电状态，并未因数据采集做任何特殊控制处理。图14~图16为滚动轴承跑外圈时的时域、频谱和包络谱分析图。图14显示外圈的振动信号出现周期性脉冲，由此可以分析出发电机轴的每一次旋转都形成了剧烈振动，且相邻的两个周期性脉冲之间的时间间隔为0.042 s，对应频率为23.8 Hz，与发电机转频一致，表明在发电机轴的一次旋转过程中外圈和轴承座之间的碰摩。在图15的频谱中显示，除了100 Hz的电磁干扰，振动能量几乎覆盖了所有的频段。在图16中可以观察到发电机轴转频的倍频成分。
通过以上分析可知，在相同的轴承型号和工况下，现场数据分析结果和仿真模型分析结果一致，其振动幅值也在同一数量级，验证了动力学模型的准确性。
4　结论
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针对滚动轴承跑外圈现象，考虑了轴承外圈和轴承座之间的碰摩效应、外圈与轴承端盖之间摩擦阻尼引起的摩擦效应、滚动轴承内部的接触力等对外圈振动特性的影响，建立了轴-滚动轴承-轴承座跑外圈故障的动力学模型，结合实测的风电轴承跑外圈数据对模型进行了验证，并对不同程度的跑外圈故障振动特性进行了分析，得出具体结论如下：
1）通过仿真数据与跑外圈故障现场数据的对比，发现两者的故障特征一致性较好，验证了动力学模型的准确性。
2）当松动间隙较小时，作用于外圈的不平衡力占据主导，振动特性呈正弦曲线响应；随着松动间隙的增加，不平衡力激励下的碰摩力占据主导，使得振动特性呈周期性冲击，且仿真数据的有效值呈上升趋势，与假设松动加剧现象相符合，这说明跑外圈故障程度随松动间隙的增大而呈加深态势。
3）滚动轴承跑外圈故障出现的周期性振动冲击，是由于跑外圈故障时外圈和轴承座之间的松动引起的配合间隙过大，在不平衡力的驱使下外圈和轴承座产生周期性的冲击和摩擦，引起外圈强烈的振动响应。这会对轴承寿命和传动系统可靠性产生严重影响。
基金
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  • 国家自然科学基金项目(51775186)
  • 国家电网有限公司总部管理科技项目(5108-202218280A-2-298-XG)
文献
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2025年第47卷第10期
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文章信息
doi: 10.16579/j.issn.1001.9669.2025.10.007
  • 接收时间：2024-01-24
  • 首发时间：2026-02-11
  • 出版时间：2025-10-15
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出版历史
  • 收稿日期：2024-01-24
  • 修回日期：2024-03-18
基金
National Natural Science Foundation of China(51775186)
国家自然科学基金项目(51775186)
State Grid Corporation Headquarters Management Science and Technology Project(5108-202218280A-2-298-XG)
国家电网有限公司总部管理科技项目(5108-202218280A-2-298-XG)
作者信息
    1.华北电力大学　电站能量传递转换与系统教育部重点实验室，北京　102206
    2.中国电力科学研究院有限公司，北京　100192

通讯作者:

滕伟，男，1981年生，山东乳山人，博士，教授；主要研究方向为能源电力装备状态监测、故障诊断与寿命预测；E-mail: 。
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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
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