Design method and test verification of simulated specimen of aeroengine disc center hole
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摘要:
依据涡轮盘有限元计算结果,确定盘心考核位置处的应力状态,并将周向应力和轴向应力比值以及轮盘中心孔处周向应力沿径向的应力梯度作为设计指标,保证模拟件应力状态与实际轮盘一致。针对轮盘中心孔考核位置,本文共设计两类模拟件:一是反映双轴应力状态的多轴模拟件,二是反映应力梯度的平板缺口模拟件。分别采用两种试验件,结合轮盘实际载荷条件开展低循环疲劳试验,并对试验结果进行统计分析。进而,采用多轴疲劳寿命预测模型及考虑应力梯度影响的寿命预测模型对两种试验件的疲劳寿命进行评估,双轴模拟件的预测结果均在2倍分散带内,平板缺口模拟件的预测结果均在3倍分散带内,此寿命预测结果对实际轮盘设计具有参考价值。
Abstract:According to the finite element simulation results of the turbine disc, the stress state at the inspection position of the disk center was determined, and the ratio of the circumferential stress and axial stress and the radial stress gradient of the circumferential stress at the disc center hole were taken as the design indexes to ensure the consistency of stress state of the simulated specimen with the actual disc. Two kinds of simulators, namely, the multi axial simulators reflecting the biaxial stress state, and the plate notch simulators reflecting the stress gradient, were designed for the inspection position of the center hole of the wheel disc. Low cycle fatigue tests were carried out by using these two kinds of specimens under actual load conditions of the disc, and the test results were statistically analyzed. Furthermore, the multi-axial fatigue life prediction model and the life model considering the influence of stress gradient were used to evaluate the fatigue life of these two simulated specimens. The scatter bands of the prediction results of biaxial simulated specimen were within 2 and those of the flat notch simulated specimen were within 3. The results could provide engineering reference for the life evaluation of aeroengine structures.
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Key words:
- turbine disc /
- simulated specimen /
- structural strength /
- multi-axial fatigue /
- stress gradient
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表 1 Udimet 720Li材料属性
Table 1. Material properties of Udimet 720Li
温度/℃ 弹性模型/GPa 泊松比 线膨胀系数/10−5 热导率/(W/(m·℃)) 比热容/(J/(kg·℃)) 密度/(kg/m3) 500 197.6 0.347 1.38 17.7 510.6 8148 表 2 不同直梁宽度对应力比值的影响
Table 2. Influence of different straight beam width on stress ratio
直梁宽度${H_3}$/mm 应力比值 2.9 −0.264 3.5 −0.304 3.2 −0.237 3.3 −0.227 3.4 −0.220 表 3 不同异形孔圆角对应力比值的影响
Table 3. Influence of different special-shaped hole fillet on stress ratio
异形孔圆角${R_3}$/mm 应力比值 3.5 −0.218 4.0 −0.222 4.5 −0.220 表 4 不同工作段宽度对应力比的影响
Table 4. Influence of different working section width on stress ratio
工作段宽度${B_1}$/mm 应力比值 2.0 −0.171 1.5 −0.087 表 5 不同缺口半径
Table 5. Different notch radius
净截面宽度/mm 缺口半径/mm 8 0.1 8 0.3 8 0.5 表 6 不同缺口净截面宽度
Table 6. Different net section width of notches
净截面宽度/mm 缺口半径/mm 8 0.1 16 0.1 22 0.1 表 7 轮盘中心孔多轴应力模拟件试验数据
Table 7. Test data of multiaxial stress simulator of the disc center hole
试件
编号温度/
℃载荷比 最大载荷/
kN寿命/
104次S1 500 0.05 20.13 150.6 S2 500 0.05 20.13 154.5 S3 500 0.05 20.13 173.0 S4 500 0.05 20.13 210.6 S5 500 0.05 20.13 119.9 S6 500 0.05 20.13 119.8 S7 500 0.05 20.13 105.1 S8 500 0.05 20.13 91.2 S9 500 0.05 20.13 130.8 表 8 轮盘中心孔应力梯度模拟件试验数据
Table 8. Test data of stress gradient simulator of the disc center hole
试件编号 温度/
℃载荷比 截面积/
mm2最大载荷/
kN寿命/
104次P1 500 0.05 13.65 13.73 146.0 P2 500 0.05 14.34 14.42 75.0 P3 500 0.05 13.95 14.03 109.5 P4 500 0.05 14.34 14.43 292.4 P5 500 0.05 14.07 14.16 163.4 P6 500 0.05 14.39 14.48 227.6 P7 500 0.05 12.58 12.66 137.4 P8 500 0.05 12.39 12.47 101.0 P9 500 0.05 12.83 12.91 267.4 表 9 轮盘中心孔多轴应力模拟件应力应变结果
Table 9. Stress and strain results of multiaxial stress simulator of the disc center hole
加载状态 应力/MPa 应变 最大 1073.1 0.0058308 最小 53.654 0.0002915 表 10 轮盘中心孔应力梯度模拟件应力应变结果
Table 10. Stress and strain results of the simulator of the stress gradient in the disc center hole
加载状态 应力/MPa 应变 最大 1063.6 0.005375 最小 53.2 0.000269 -
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