考虑塑性失稳准则的涡轮叶片断裂转速预测方法

孟卫华; 张志佾; 李坚; 李磊; 李维; 刘鹤; 王存福

doi:10.13224/j.cnki.jasp.20240700

考虑塑性失稳准则的涡轮叶片断裂转速预测方法

doi: 10.13224/j.cnki.jasp.20240700

孟卫华^{1, 2, 3,},
张志佾^{2, 3},
李坚^{2, 3},
李磊¹,
李维^{2, 3},
刘鹤⁴,
王存福⁴

1.
西北工业大学力学与交通运载工程学院，西安 710072
2.
中国航发湖南动力机械研究所，湖南株洲 412002
3.
中小型航空发动机联合研究中心，湖南株洲 412002
4.
厦门大学航空航天学院，福建厦门 361105

基金项目: 国家自然科学基金（12102375）

详细信息

作者简介:
孟卫华（1987-），男，高级工程师，博士生，研究领域为航空发动机强度及可靠性设计。E-mail：mengweihua1234@163.com

中图分类号: V252.2
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出版历程
- 收稿日期: 2024-10-14
- 网络出版日期: 2025-08-02

Turbine blade shedding predictive analysis method considering plastic instability criterion

MENG Weihua^{1, 2, 3
,},
ZHANG Zhiyi^{2, 3},
LI Jian^{2, 3},
LI Lei¹,
LI Wei^{2, 3},
LIU He⁴,
WANG Cunfu⁴

1.
School of Mechanics and Transportation Engineering，Northwestern Polytechnical University，Xi’an 710072，China
2.
Hunan Aviation Powerplant Research Institute，Aero Engine Corporation of China，Zhuzhou Hunan 412002，China
3.
United Research Center of Mid-Small Aero-Engine，Zhuzhou Hunan 412002，China
4.
School of Aerospace Engineering，Xiamen University，Xiamen Fujian 361005，China

摘要

摘要:
为满足发动机适航规章CCAR33.27对涡轮失去负载时转子完整性的设计要求，航空发动机通常采用涡轮叶片脱落超转保护设计避免轮盘破裂的非包容问题，故而准确预测涡轮叶片脱落转速在超转保护设计中至关重要。基于黏弹塑性本构方程和虚功原理，研究了一种应用有限元法预测涡轮叶片断裂转速的方法，并给出了对应的黏弹塑性失稳准则。通过实例应用，证明了相对于传统方法的计算结果，黏弹塑性失稳准则的方法计算精度更高，其计算精度由最大误差10.35%、7.64%提高到2.87%以内，且黏弹塑性失稳准则的方法工程适应性强。
- 涡轮叶片 /
- 超转保护 /
- 叶片断裂 /
- 断裂转速预测 /
- 失效准则
Abstract:
To meet the integrity requirements of the turbine rotor design on loss-of-load defined by the engine airworthiness regulation CCAR33.27, aero-engines usually adopt an overspeed protection design for turbine blade shedding to avoid non-containment issues under disk burst. Therefore, accurate prediction of turbine blade shedding speed is crucial in the overspeed protection design. According to the visco-elasto-plastic constitutive equations and the virtual work principle, the approach to predict the turbine blade shedding from the finite element analysis results was studied, and the corresponding visco-elasto-plastic instability criteria were provided. It was demonstrated through a practical application example that the proposed turbine blade shedding speed prediction considering visco-elasto-plastic instability criteria had higher precision. Compared with the traditional methods, the proposed method reduced the maximum prediction error from 10.35%, 7.64% to 2.87%. In addition, the prediction method based on visco-elasto-plastic instability criteria can be widely used in engineering applications.
- turbine blades /
- overspeed protection /
- blade shedding /
- prediction of blade shedding /
- failure criterion

HTML

图 1 叶片断裂的力学问题

Figure 1. Mechanical problem of blade shedding

下载: 全尺寸图片幻灯片

图 2 4种不同拉弯比例的叶片设计方案

Figure 2. Design settings of four groups of blades with different tension-bending ratios

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图 3 4种不同拉弯比例加工后叶片

Figure 3. Four groups of fabricated blades with different tension-bending ratios

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图 4 涡轮叶片试验件安装

Figure 4. Fixtures of the experimental pieces for turbine blades

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图 5 4种方案叶片断裂转速测量试验残骸

Figure 5. Fractured blades of the four shedding speed experiments

下载: 全尺寸图片幻灯片

图 6 方案1叶片应变随外载荷（转速）的变化趋势

Figure 6. Variation trend of blade strain with external load （speed） in group 1

下载: 全尺寸图片幻灯片

图 7 4种不同拉弯比例的叶片断裂转速下应力分布

Figure 7. Stress distributions under the blade shedding speed with four different tensile-bending ratios

下载: 全尺寸图片幻灯片

表 1 4种不同拉弯比例的叶片断裂转速测量值

Table 1. Measurement values of blade shedding speed with four different tension-bending ratios

方案	叶片编号	叶片质量/g	试验断裂转速/（r/min）
1	B	25.11	37539
	E	25.10	37539
	A	25.09	37648
	D	25.02	37648
	C	25.25	37160
	F	25.15	37160
2	N	25.01	35815
	S	25.01	35815
	R	25.05	36196
	O	25.06	36196
	P	25.08	36100
	T	25.11	36100
3	L	25.00	36441
	J	25.06	36441
	I	25.10	35779
	M	25.10	35779
	H	25.13	35354
	K	25.14	35354
4	U	25.04	35137
	Z	25.03	35137
	X	25.17	35019
	Y	25.10	35019
	V	25.21	34867
	W	25.29	34867

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表 2 应力指标对比

Table 2. Comparison of stress indicators

参数	方案1（γ=10%）	方案2（γ=20%）	方案3（γ=30%）	方案4（γ=40%）
第一主应力/MP$ \mathrm{a} $	1183	1205	1224	1248
第二主应力/MP$ \mathrm{a} $	543	552	560	572
第三主应力/MP$ \mathrm{a} $	−906	−815	−737	−668
平均应力/MP$ \mathrm{a} $	820	942	1047	1152
等效应力/MP$ \mathrm{a} $	1854	1785	1728	1683
应力三轴度	0.442	0.528	0.606	0.684

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表 3 预测与试验结果对比

Table 3. Comparison of predicted and experimental results

方案	叶片/ 试棒编号	试棒强度极限/MPa	试验断裂转速/（r/min）	修正平均应力法		弹塑性应变法		黏弹塑性失稳法
方案	叶片/ 试棒编号	试棒强度极限/MPa	试验断裂转速/（r/min）	断裂转速计算值/（r/min）	误差/%	断裂转速计算值/（r/min）	误差/%	断裂转速计算值/（r/min）	误差/%
1	B	994	37539	35006	6.75	36178	3.62	37344	0.52
	E	950	37539	35006	6.75	36178	3.62	37344	0.52
	A	931	37648	34654	7.95	35542	5.59	37147	1.33
	D	967	37648	34654	7.95	35542	5.59	37147	1.33
	C	1045	35815	34117	4.74	36178	2.64	37344	−0.49
	F	950	35815	34117	4.74	36178	2.64	37344	−0.49
2	N	969	37160	35006	5.80	34673	4.21	36843	−2.87
	S	979	37160	35006	5.80	34673	4.21	36843	−2.87
	R	937	36196	33549	7.31	34432	4.87	36287	−0.25
	O	954	36196	33549	7.31	34432	4.87	36287	−0.25
	P	938	36100	33567	7.02	33948	3.06	36287	−0.52
	T	973	36100	33567	7.02	33948	3.06	36287	−0.52
3	L	1042	36441	33150	9.03	34260	5.98	37009	−1.56
	J	1004	36441	33150	9.03	34260	5.98	37009	−1.56
	I	940	35779	32073	10.35	35224	1.55	35810	−0.09
	M	1015	35779	32073	10.35	35224	1.55	35810	−0.09
	H	985	35354	32297	8.65	32651	7.64	36057	−1.99
	K	953	35354	32297	8.65	32651	7.64	36057	−1.99
4	U	949	35137	32659	7.05	34691	3.90	35357	−0.63
	Z	1029	35137	32659	7.05	34691	3.90	35357	−0.63
	X	1018	35019	32138	8.20	33753	3.94	35562	−1.55
	Y	960	35019	32138	8.20	33753	3.94	35562	−1.55
	V	994	34867	32487	6.83	33575	3.71	35189	−0.92
	W	939	34867	32487	6.83	33575	3.71	35189	−0.92

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