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1.大功率交流传动电力机车系统集成国家重点实验室,湖南 株洲 412001
2.中车株洲电力机车有限公司 产品研发中心,湖南 株洲 412001
3.西南交通大学 牵引动力国家重点实验室,四川 成都;610031
朱 涛(1984—),男,博士,博士/硕士生导师,副研究员,主要从事列车碰撞动力学与被动安全防护、机车车辆结构剩余寿命评估方法与预测、载荷识别理论和轮轨力预测方法、机车车辆结构强度与轻量化设计方法; E-mail: zhutao034@swjtu.edu.cn
纸质出版日期:2022-11-10,
收稿日期:2021-03-26,
修回日期:2021-08-03,
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曾燕军, 金希红, 朱涛, 等. 电力机车车体关键部件疲劳全寿命评估方法[J]. 机车电传动, 2022,(6):10-16.
ZENG Yanjun, JIN Xihong, ZHU Tao, et al. Life-cycle assessment method for key parts of an electric locomotive body[J]. Electric drive for locomotives, 2022,(6):10-16.
曾燕军, 金希红, 朱涛, 等. 电力机车车体关键部件疲劳全寿命评估方法[J]. 机车电传动, 2022,(6):10-16. DOI: 10.13890/j.issn.1000-128X.2022.06.002.
ZENG Yanjun, JIN Xihong, ZHU Tao, et al. Life-cycle assessment method for key parts of an electric locomotive body[J]. Electric drive for locomotives, 2022,(6):10-16. DOI: 10.13890/j.issn.1000-128X.2022.06.002.
针对电力机车车体在线路循环激励作用下的疲劳裂纹失效问题,对关键部件进行了动应变测试,结合标准载荷,研究了其疲劳全寿命。首先,以某电力机车车体为研究对象,对关键部件进行了线路动应变测试,并对测试数据进行低通滤波;其次,对滤波结果进行雨流计数,基于国际焊接协会(International Institute of Welding,IIW)标准确定测点焊缝材料参数,并按照Palmgren-Miner线性累积损伤理论进行了关键部件疲劳裂纹萌生寿命计算;然后,以车体枕梁和垂向减振器安装座的底架局部结构为例,建立了关键部件裂纹扩展仿真子模型,并基于EN 12663标准确定了子模型载荷工况;最后,在垂向减振器动应变测点位置插入初始裂纹,基于断裂力学方法计算了疲劳裂纹扩展寿命,从而获取了车体垂向减振器安装座疲劳全寿命数据。研究结果表明,电力机车车体垂向减振器安装座在既有线路上的疲劳裂纹萌生寿命为6.86×10
7
公里;具有2 mm表面半长、0.8 mm深的初始半椭圆型表面裂纹的电力机车车体,在EN 12663标准要求的载荷条件下,至少还能承受4.18×10
7
次载荷循环才会完全丧失承载能力。研究结果为必要的车体结构改进提供了可靠的试验和仿真依据,为评定机车运营中车体的安全可靠性提供了极强的指导作用和参考价值。
In respect of the fatigue crack failure of the electric locomotive body under the cyclic excitation
the dynamic strain test was carried out on the key parts
and the fatigue life of the locomotive body was researched based on standard loads. Firstly
the body of an electric locomotive was taken as the research object
the dynamic strain test of the key parts was carried out
and the test data were filtered by low-pass filter. Secondly
the rainflow counting was carried out on the filtering results
and the parameters of the welding material at the measuring point were determined based on the IIW (International Institute of Welding) standard. The fatigue crack initiation life of the key parts was calculated according to the Palmgren-Miner linear cumulative damage theory. Then
the body bolsters and the local structure of the underframe of the vertical damper holder were taken as examples
the sub-model of crack propagation simulation of key parts was established
and the load conditions of the sub-model were determined based on the EN 12663 standard. Finally
the initial crack was inserted at the dynamic strain measuring point of the vertical damper
and the fatigue crack propagation life was calculated based on the fracture mechanics
thereby obtaining the fatigue life data of the vertical damper holder of the body. The results show that the fatigue crack initiation life of the vertical damper holder is 6.86×10
7
km. Under the load conditions required by the EN 12663 standard
the electric locomotive body with an initial semi-elliptical surface crack of 2 mm in half length and 0.8 mm in depth can bear at least 4.18×10
7
load cycles before it completely loses its bearing capacity. The research results provide reliable test and simulation basis for the necessary improvement of the body structure
as well as a strong guidance and reference value for the evaluating the safety and reliability of the body in locomotive operation.
车辆工程电力机车车体动应变测试损伤累积断裂力学裂纹扩展仿真
vehicle engineeringelectric locomotivebodydynamic strain testdamage accumulationfracture mechanicscrack propagation simulation
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