共查询到18条相似文献,搜索用时 203 毫秒
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国产660 MW超临界机组高中压转子弯曲处理 总被引:1,自引:0,他引:1
当加工汽轮机转子的锻件毛坯材质存在较大的残余内应力,汽轮机组投运后,随着时间的累积,会因残余内应力的逐渐释放造成转子弯曲变形,从而引发机组强烈振动.某国产660 MW超临界机组高中压转子“残余内应力释放性”弯曲变形,引发振动不断攀升,通过分析转子振动变化趋势并揭缸检查,采取现场动平衡调试补偿措施,将转子振动降至合格范围.总结现场处理此类故障的经验并提出合理化建议,为同类型故障的处理提供参考. 相似文献
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当加工汽轮机转子的锻件毛坯材质存在较大的残余内应力,汽轮机组投运后,随着时间的累积,会因残余内应力的逐渐释放造成转子弯曲变形,从而引发机组强烈振动。某国产660 MW超临界机组高中压转子“残余内应力释放性”弯曲变形,引发振动不断攀升,通过分析转子振动变化趋势并揭缸检查,采取现场动平衡调试补偿措施,将转子振动降至合格范围。总结现场处理此类故障的经验并提出合理化建议,为同类型故障的处理提供参考。 相似文献
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针对某发电厂300 MW汽轮机组过临界时高中压转子振动幅度逐渐增大的问题,介绍该机组的振动特征,分析认为振动的原因为转子存在较大残余内应力,造成高中压转子发生永久性弯曲,提出对转子采取高速动平衡的处理措施. 相似文献
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正水轮发电机转子引起的振动是水电厂最为常见的问题,它危及机组的安全运行,一直来受到制造厂的重视和发电厂的关注。水口水电站一号机自1993年8月投运后,存在上机架径向振动超标,上导摆度偏大的振动问题。在振动测试中,发现转子一加励磁,上机架振动就明显增大。在转子动态气隙测试中,发现转子存在较大偏心。由此可见,机组振动的主要原因是转子不平衡磁拉力过大。经过深入研究和精心工作,在后期的机组大修期间,制定并实施了3项消振措 相似文献
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东方300 MW机组高中压转子振动故障诊断 总被引:4,自引:0,他引:4
东方300MW机组在运行过程中高中压转子出现过低频振动,对张家口发电厂、华能德州电厂等7个电厂8台机组的振动原因进行了分析,分析认为运行启动方式对振动有影响,并阐明了机组产生振动故障的原因和对策 。 相似文献
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600 MW超临界机组汽轮机高、中压转子蒸汽参数高,转速高,工作环境恶劣,在运行过程中产生很大的应力变化,某600MW超临界机组由于某些原因导致转子断油烧瓦,严重影响到机组的安全运行.为了掌握转子的应力状态,保障转子安全运行,采用有限元软件ANSYS APDL对转子在冷态启动工况下进行有限元计算.基于工程热力学计算,求解转子各级的对流放热系数,将其作为边界条件加载到有限元模型上,进行温度场的计算和分析,然后通过采用热结构间接耦合法对转子的应力场进行计算分析,得到转子冷态启动过程的应力分布和应力集中的部位.计算结果表明,受损转子切削处理后等效应力小于屈服应力,但在调节级根部凹槽、挡油环与轴颈附近应力水平较大,此结论可为受损转子的安全性评估及寿命管理提供技术支撑. 相似文献
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某电厂8号机组带负荷后振动过大,通过试验分析,查明振动原因是由于发电机转子冷却水管冷却不均匀、低压转子和励磁机转子质量不平衡,引起运行时发电机转子产生热弯曲以及4号、8号轴承振动超标。采取对发电机转子内冷水管反冲洗和调整轴系平衡等措施,机组振动得以消除。 相似文献
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样条配点法在汽轮机转子矫直分析中的应用 总被引:1,自引:0,他引:1
对转子钢进行了短时蠕变和高温强度实验,得到了该材料在直轴温度范围内的蠕变方程和强度与温度关系曲线。对直轴过程的温度场进行了分析,得到了转轴径向温差的分布规律。利用样条函数配点法,编制了汽轮机转子的矫直分析软件。数值结果表明分析方法是有效的,可求出转轴在加载后不同时刻的矫直量和矫直后的残余应力,为任意弯曲形状的转子提供优化的矫直方案。 相似文献
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The work is dedicated to the study of vibration activity of double-span rotor of turbine unit (TU) consisting of a high-pressure rotor and a rotor of medium-low pressure rotor combined with it (HPR—MLPR system) at the lowest critical rotational frequencies at rundown. When using the design model of the system, it was assumed that the rotors were installed on anisotropic elastic-damper supports, tied among themselves by a rigid clutch, and having the initial curvature (nonremovable initial deflection) and the residual unbalances in both spans. Two types of bearings were considered–elliptical and six-shoe segmental bearings. It was believed that the initial deflection during operation or as a result of noncompliance of start-up conditions initially gets only HPR and the axis shape of unloaded HPR is known and it is a flat curve. The resultant curve of nonremovable deflection of the HPR–MLPR system occurring after installing the shafting into the bearings was also considered flat and located in the same plane as the initial deflection of HPR. The cases of additional presence with the rotors of concentrated residual unbalances in the middle of each span are considered. The case of availability with both rotors of the shafting antisymmetric point unbalances on each of the spans was not considered in this work. The values of each of the factors of vibration activity (of the initial deflection of HPR and residual unbalances of both rotors) were chosen to be equal to the maximum permissible established by the active in the practice of TU operation limitations on the maximum values of the initial deflection of thermally unstable rotor and its residual unbalances. The influence of location of residual unbalances in relation to the initial deflection curve of HPR–MLPR system on the total amplitudes of transient vibrations caused by both excitation factors in the reference points of the system at TU rundown was investigated. It was established that, at the unfavorable relations between directions of curvature of the rotors of HPR–MLPR system and their residual unbalances with segmental bearings, touching in the diaphragm seals in the middle of HPR span is possible. 相似文献
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