面向复杂空间管路的最远传递路径-最小能量损耗判别准则与其减振应用

李晖; 李韶亮; 孙凯华; 孙占彬; 王鑫; 张秉杰; 马辉

doi:10.13224/j.cnki.jasp.20240457

面向复杂空间管路的最远传递路径-最小能量损耗判别准则与其减振应用

doi: 10.13224/j.cnki.jasp.20240457

李晖^{1, 3,},
李韶亮⁴,
孙凯华¹,
孙占彬¹,
王鑫³,
张秉杰³,
马辉^{1, 2}

1.
东北大学机械工程与自动化学院，沈阳 110819
2.
东北大学航空动力装备振动及控制教育部重点实验室，沈阳 110819
3.
中国航发沈阳发动机研究所，沈阳 110015
4.
空军装备部驻北京地区第六代表室，北京 100621

基金项目: 国家自然科学基金（52175079，12472005）；航空发动机及燃气轮机重大专项基础研究项目（J2019-Ⅰ-0008-0008）；中央高校基本科研业务费专项资金（N2103026）

详细信息

作者简介:
李晖（1982-），男，教授、博士生导师，博士，主要从事复合结构减振降噪研究。E-mail：lh200300206@163.com

中图分类号: V233.1
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出版历程
- 收稿日期: 2024-07-05
- 网络出版日期: 2025-03-02

The farthest transfer path and minimum energy loss criterion for complex space pipelines and their vibration reduction applications

LI Hui^{1, 3
,},
LI Shaoliang⁴,
SUN Kaihua¹,
SUN Zhanbin¹,
WANG Xin³,
ZHANG Bingjie³,
MA Hui^{1, 2}

1.
School of Mechanical Engineering and Automation，Northeastern University，Shenyang 110819，China
2.
Key Laboratory of Vibration and Control of Aero-Propulsion Systems，Ministry of Education，Northeastern University，Shenyang 110819，China
3.
Shenyang Engine Research Institute，Aero Engine Corporation of China，Shenyang 110015，China
4.
The Sixth Representative Office of Air Force Equipment Department in Beijing，Beijing 100621，China

摘要

摘要:
提出了面向复杂空间管路的最远传递路径-最小能量损耗判别准则，在阐明该准则的内涵与确定依据的基础上，创建了复杂空间管路系统的有限元模型，并实现了振动传递路径的划分和不同传递路径对应的振动功率流曲线的预测。搭建了复杂空间管路系统振动传递测试平台，通过对比测试和有限元计算结果，发现前3阶固有频率的最大计算误差为3.5%，两种方法获得的模态振型结果吻合较好，且不同传递路径下输出端振动功率流曲线的变化趋势呈现较好的一致性，功率流峰值的最大误差不超过12.9%，由此证明了模型的正确性。此外，研究发现可利用该准则实现空间管路振动最远传递路径的排序，结合不同共振状态下获得的功率流损耗结果，可有效辨识主要振动传递路径。相关研究成果可为航空发动机复杂空间管路系统的减振、隔振、避振处理，提供一种新思路与手段。
- 振动功率流 /
- 复杂空间管路 /
- 判别准则 /
- 振动传递 /
- 减振应用
Abstract:
The criterion of the farthest transmission path minimum energy loss for complex space pipelines was proposed. Based on the clarification of the connotation and determination basis of such a criterion, a finite element model of complex space pipeline system was created, and the division of vibration transmission path and the prediction of vibration power flow curve corresponding to different transmission paths were also achieved. A complex pipeline vibration transmission testing platform was established. By comparing the calculation results between tests with finite element predictions, it was found that the maximum calculation error for the first three natural frequencies was 3.5%, both mode shape results matched well, and the variation trend of the vibration power flow curves at the output end of the pipeline system under different transmission paths obtained by the two methods demonstrated a good consistency, with the maximum error of the power flow peak only reaching 12.9%, which verified the correctness of the model. In addition, such a criterion can be employed to rank the farthest transmission path of the vibration of space pipelines, and after combining with the power flow loss results obtained under different resonance states, the main vibration transmission path can be effectively identified. The research results can provide a new ideal and approach for the vibration reduction, isolation, and avoidance of complex space piping systems in aero-engines.
- vibration power flow /
- complex space pipeline /
- criterion /
- vibration transmission /
- vibration reduction application

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图 1 用于分析振动传递特性的复杂空间管路系统的有限元模型

Figure 1. Finite element model of complex space piping systems for analyzing vibration transmission characteristics

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图 2 复杂空间管路系统振动传递路径及其对应的有限元节点示意图

Figure 2. Schematic diagram of vibration transmission paths and corresponding finite element nodes in complex space pipeline systems

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图 3 管路振动传递测试系统

Figure 3. Vibration transmission test system of pipelines

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图 4 管路系统前3阶固有频率

Figure 4. The first 3 natural frequencies of the pipeline system

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图 5 管路系统前3阶模态振型

Figure 5. The first 3 mode shapes of pipeline system

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图 6 计算和测试获得的不同传递路径下管路系统输出端的振动功率流曲线及相应的最大计算误差

Figure 6. Calculated and measured vibration power flow curves at the output end of pipeline system under different transmission paths and the related maximum calculation errors

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图 7 计算和测试获得的S1路径下振动功率流分布曲线图

Figure 7. Calculation and testing of vibration power flow distribution curve under S1 path

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图 8 计算和测试获得的S2路径下振动功率流分布曲线

Figure 8. Calculation and testing of vibration power flow distribution curve under S2 path

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图 9 计算和测试获得的S3路径下振动功率流分布曲线图

Figure 9. Calculation and testing of vibration power flow distribution curve under S3 path

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图 10 计算和测试获得的S4路径下振动功率流分布曲线

Figure 10. Calculation and testing of vibration power flow distribution curve under S4 path

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图 11 计算和测试获得的S5路径下振动功率流分布曲线图

Figure 11. Calculation and testing of vibration power flow distribution curve under S5 path

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图 12 计算和测试获得的S6路径下振动功率流分布曲线

Figure 12. Calculation and testing of vibration power flow distribution curve under S6 path

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图 13 计算和测试获得的S7路径下振动功率流分布曲线

Figure 13. Calculation and testing of vibration power flow distribution curve under S7 path

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图 14 不同共振激振状态下计算和测试获得的管路系统在不同传递路径下的振动功率流损耗图

Figure 14. Vibration power flow loss diagram of pipeline system under different transmission paths calculated and tested under different resonance excitation states

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表 1 复杂空间管路系统各部分材料与几何参数^[21]

Table 1. Materials and geometric parameters of the different parts of the complex space pipeline system^[21]

参数类型	具体参数
管路系统材料参数	E=2.04×10⁵ MPa，$\mu $=0.285，$\rho $=7800 kg/m³
单管几何参数	D₁=D₂=D₅=D₆=8 mm，d₁=d₂=d₅=d₆=6 mm，D₃=D₄=12 mm，d₃=d₄=10 mm， D₇=D₈=20 mm，d₇=d₈=17 mm
管接头几何参数	a₁₁=a₃₁=a₇₁=a₉₁=9.2 mm，a₁₂=a₃₂=a₇₂=a₉₂=3.5 mm，a₁₃=a₃₃=a₇₃=a₉₃=16.5 mm，a₁₄=a₃₄=a₇₄=a₉₄=15.7 mm，a₂₁=a₂₄=a₈₁=a₈₄=5 mm，a₂₂=a₈₂=10.2 mm，a₂₃=a₈₃=22 mm，a₄₁=a₆₁=14 mm，a₄₂=a₆₂=3 mm，a₄₃=a₆₃=15 mm，a₄₄=a₆₄=16.5 mm，a₅₁=a₅₄=5 mm，a₅₂=15 mm，a₅₃=22.6 mm，b₁₁=b₃₁=b₇₁=b₉₁=18 mm，b₁₂=b₃₂=b₇₂=b₉₂=16 mm，b₁₃=b₃₃=b₇₃=b₉₃=21 mm，b₁₄=b₃₄=b₇₄=b₉₄=8 mm，b₂₁=b₂₄=b₇₄=b₉₄=8 mm，b₂₂=b₈₂=11 mm，b₂₃=b₈₃=15 mm，b₄₁=b₆₁=21 mm，b₄₂=b₆₂=16 mm，b₄₃=b₆₃=26 mm，b₄₄=b₆₄=12 mm，b₅₁=b₅₄=12 mm，b₅₂=16.4 mm，b₅₃=22 mm，a₁₀₁=a₁₂₁=14 mm，a₁₀₂=a₁₂₂=3 mm，a₁₀₃=a₁₂₃=24 mm，a₁₀₄=a₁₂₄=23.7 mm，a₁₁₁=a₁₁₄=5 mm，a₁₁₂=19.6 mm，a₁₁₃=24 mm，b₁₀₁=b₁₂₁=34 mm，b₁₀₂=b₁₂₂=30 mm，b₁₀₃=b₁₂₃=36 mm，b₁₀₄=b₁₂₄=20 mm，b₁₁₁=b₁₁₄=20 mm，b₁₁₂=26 mm，b₁₁₃=33 mm，Φ_Ⅰ=Φ_Ⅲ=Φ_Ⅶ=Φ_Ⅸ=55 mm，Φ_Ⅱ=Φ_Ⅷ=6 mm，Φ_Ⅳ=Φ_Ⅵ=8 mm，Φ_Ⅴ=10 mm，Φ_Ⅹ=Φ_Ⅻ=14 mm，Φ_Ⅺ=17 mm
卡箍约束刚度参数	K_x1=K_x2=K_x3=K_x4=K_x5=K_x6=K_x7=K_x8=K_y9=K_y10=K_y11=K_y12=K_y13=K_y14=K_y15=1×10¹² N/m，K_y1=K_y2=K_y3=K_y4=K_y9=K_y10=K_y11=K_y12=8.74×10⁶ N/m，K_y5=K_y6=K_y7=K_y8=11.68×10⁶ N/m， K_y13=K_y14=K_y15=2.65×10⁶ N/m，K_z1=K_z2=K_z3=K_z4=K_z9=K_z10=K_z11=K_z12=7.50×10⁶ N/m， K_z5=K_z6=K_z7=K_z8=10.76×10⁶ N/m，K_z13=K_z14=K_z15=2.14×10⁶ N/m，K_θx1=K_θx2=K_θx3=K_θx4=K_θx5=K_θx6=K_θx7=K_θx8=K_θx9=K_θx10=K_θx11=K_θx12=K_θx13=K_θx14=K_θx15=1×10⁵ （N·m）/rad，K_θy1=K_θy2=K_θy3=K_θy4=K_θy9=K_θy10=K_θy11=K_θy12=89.01 （N·m）/rad，K_θy5=K_θy6=K_θy7=K_θy8=139.01 （N·m）/rad，K_θ13=K_θy14=K_θy15=21.23 （N·m）/rad，K_θz1=K_θz2=K_θz3=K_θz4=K_θz9=K_θz10=K_θz11=K_θz12=75.79 （N·m）/rad，K_θz5=K_θz6=K_θz7=K_θz8=128.04 （N·m）/rad，K_θz13=K_θz14=K_θz15=20.82 （N·m）/rad，S_x1=S_x2=S_x3=1×10¹² N/m，S_y1=S_y2=10.67×10⁶ N/m，S_y3=3.89×10⁶ N/m，S_z1=S_z2=3.02×10⁶ N/m，S_z3=1.65×10⁶ N/m，S_θx1=S_θx2=S_θx3=1×10⁵ （N·m）/rad，S_θy1=S_θ2=531.18 （N·m）/rad，S_θy3=152.82 （N·m）/rad， S_θz1=S_θz2=139.24 （N·m）/rad，S_θz3=58.37 （N·m）/rad，m_sk1=m_sk2=0.033 kg，m_sk3=0.056 kg

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