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我厂一电站4号汽轮机发电机组功率2.5万kw,1992年7月励磁机最外端的5号轴承垂直振动达120μm,水平振动90μm。电站判定为新换的励磁机转子不平衡,要求作现场动平衡处理。当时因电力紧张不能停机处理,厂状态监测组和汽机车间有关人员通过IRD890数据采集器分析,认为是轴承座不稳造成的。在紧固地脚螺拴无效情况下,决定在机组负荷减小一半时,在与轴承联接的底座和台板(与底座联接)间加斜垫铁点焊,作为增加刚度的临时措施。这样,轴承的振动降到40μm以下,机组正常运行到1992年9月,完成供电任务。从励磁机外端的5号轴承和靠近励磁机内端发电机的4号轴承频谱图1可见,图1(b)有一个接近
I plant a power plant on the 4th turbine power 25,000 kw, July 1992 exciter outermost 5 bearing vertical vibration up to 120μm, horizontal vibration 90μm. The power plant is judged as a new exchange of exciter rotor imbalance, required for on-site dynamic balancing treatment. At that time, because of the power shortage can not be shut down, the factory state monitoring team and steam turbine workshop personnel through the IRD890 data acquisition analysis, that is caused by bearing instability. In the case of ineffective tightening of anchor bolts, it is decided to add the oblique spot welding between the base plate and the base plate (connected with the base) of the bearing when the load of the generator is reduced by half, as a temporary measure to increase the rigidity. In this way, the bearing vibration down to 40μm below, the normal operation of the unit until September 1992, to complete the task of power supply. From the outer end of the exciter No. 5 bearing and the exciter near the end of the generator No. 4 bearing spectrum can be seen in Figure 1, Figure 1 (b) has a close