联合载荷下燃油泵调节器声振特性分析

胡学满; 侯亮; 卜祥建; 周毅博

doi:10.13224/j.cnki.jasp.20220849

联合载荷下燃油泵调节器声振特性分析

doi: 10.13224/j.cnki.jasp.20220849

胡学满^{1, 2,},
侯亮^1,*, ,,
卜祥建¹,
周毅博³

1.
厦门大学机电工程系，福建厦门 361102
2.
北京航空航天大学交通科学与工程学院，北京 100191
3.
中国航发控制系统研究所，江苏无锡 214063

基金项目: 国家自然科学基金面上项目（51975495）；厦门市重大科技项目（3502Z20191019）；中央引导地方科技发展专项（2020L3002）

详细信息

作者简介:
胡学满（1995-），男，博士生，主要从事复杂装备振动噪声方面的研究。E-mail：huxueman@buaa.edu.cn

通讯作者:
侯亮（1974-），男，教授、博士生导师，博士，主要从事大批量定制、创新设计、振动与噪声和工业大数据等方面的研究。E-mail：hliang@xmu.edu.cn

中图分类号: V233.2
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出版历程
- 收稿日期: 2022-11-06
- 网络出版日期: 2024-03-06

Vibration and noise analysis of fuel pump regulator under combined load

HU Xueman^{1, 2
,},
HOU Liang^{1,*
, ,},
BU Xiangjian¹,
ZHOU Yibo³

1.
Department of Mechanical and Electrical Engineering，Xiamen University，Xiamen Fujian 361102，China
2.
School of Transportation Science and Engineering，Beihang University，Beijing 100191，China
3.
Aero Engine Control System Institute，Aero Engine Corporation of China，Wuxi Jiangsu 214063，China

摘要

摘要:
为了探究高集成燃油泵调节器在结构载荷和流体载荷联合作用下的动力学特性，比较其工作状态与非工作状态的响应差异。根据液压系统工作原理，建立液压模型，获得极限工况下燃油主要作用区域的压强。基于Ploymax法识别结构系统的阻尼，由响应控制原理和系统特征重构激励点载荷，并结合大质量法（large mass method, LMM）实现载荷形式的转化。利用声固耦合法求解组合边界下系统的模态和振动响应，采用间接边界元法（indirect boundary element method, IBEM）计算声学响应。研究表明：相比于非流固耦合结果，耦合自由模态变化程度小，考虑机匣振动及燃油预应力作用下的耦合振动噪声峰值响应在低频段明显降低，第一阶频率降低17.3%，该频率下最高噪声值降低约14.3 dB，600 Hz以后响应有增大趋势。
- 燃油泵调节器 /
- 联合载荷 /
- 液压系统 /
- 大质量法 /
- 流固耦合 /
- 振动噪声
Abstract:
To investigate the dynamics of a highly integrated fuel pump regulator under combined structural and fluid loads, and compare the difference in responses between its working and non-working states, a hydraulic model was established to obtain the pressure of main action area under extreme conditions according to the principle of the hydraulic system. The structural damping was identified by the Ploymax method. The excitation load was reconstructed by the response control principle and system characteristics, and the load form was transformed by the large mass method (LMM). The acoustic-structure interaction method was used to solve the modal and vibration responses under the combined boundary, and the indirect boundary element method (IBEM) was used to calculate the acoustic response. The results indicated that the change of free mode without fuel prestress was little, and the peak response of vibration and noise considering casing vibration and fuel prestress was significantly reduced at low frequency, the first order frequency was reduced by 17.3%, and the maximum noise value at this frequency was reduced by about 14.3 dB, and the response had a tendency of increase beyond 600 Hz, compared with results of non-fluid-structure interaction.
- fuel pump regulator /
- combined loads /
- hydraulic system /
- large mass method /
- fluid-structure interaction /
- vibration and noise

HTML

图 1 燃油泵调节器声振特性分析流程

Figure 1. Process of vibration and noise analysis of fuel pump regulator

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图 2 液压系统原理

Figure 2. Principle of hydraulic system

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图 3 燃油模型

Figure 3. Modal of fuel

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图 4 预应力作用区域二次筛选

Figure 4. Secondary screening of prestress action area

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图 5 参考谱

Figure 5. Reference spectrum

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图 6 载荷谱

Figure 6. Load spectrum

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图 7 流固耦合振动的简化大质量数学模型

Figure 7. Simplified LMM model of FSI vibration

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图 8 振动系统

Figure 8. Vibration system

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图 9 实验装置

Figure 9. Experimental site

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图 10 燃油泵调节器响应计算值与实验值对比

Figure 10. Comparison of the calculated and experimental results of the fuel pump regulator’s response

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图 11 容器响应计算值与实验值对比

Figure 11. Comparison of calculated and experimental results of vessel

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图 12 结构振型对比

Figure 12. Comparison of structural mode

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图 13 LVDT保护罩顶端响应对比

Figure 13. Comparison of LVDT cover response

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图 14 电插座响应幅值对比

Figure 14. Amplitude comparison of electrical socket

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图 15 边界元模型和场点模型

Figure 15. Boundary element and field point model

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图 16 声压级云图

Figure 16. Cloud chart of sound pressure level

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图 17 外场噪声指向性

Figure 17. Directivity of external noise

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表 1 流体压强信息

Table 1. Fluid pressure information

序号	作用位置	压强/MPa
1	压差入口-壳体	6.8
2	弹簧腔-阀芯	6.3
3	计后腔-壳体	6.3
4	计量衬套	6.8
5	计前腔-壳体	6.8
6	油滤腔-壳体	7

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表 2 工作模态参数

Table 2. Parameters of working modal

阶数	频率/Hz		模态阻尼比/%
阶数	实验模态	仿真模态	模态阻尼比/%
1	293	298.6	2.76
2	351	375.9	3.58
3	567	505.4	4.00
4	711	654.1	3.42
5	911	870.5	3.20
6	980	910.0	1.27

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表 3 结构模态频率对比

Table 3. Comparison of structural modal frequencies

阶次	模态频率/Hz		绝对变化/ Hz	相对变化/ %
阶次	耦合前	耦合后	绝对变化/ Hz	相对变化/ %
1	519.6	519.6	0	0
2	535.0	531.7	−3.3	−0.6
3	659.2	647.8	−11.4	−1.7
4	808.4	803.2	−5.2	−0.6
5	852.7	855.5	2.8	0.3
6	974.4	990.6	16.2	1.7

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表 4 振动响应对比（Z方向）

Table 4. Comparison of vibration response （Z direction）

位置名称	绝对差值最值频率点/Hz		有效值/ （m/s²）
位置名称	最小值	最大值	有效值/ （m/s²）
LVDT保护罩顶部	15.6	633	11.3
保护罩远端	521	301	3.0
壳体中部	229	301	2.8
泵头	229	389	1.2
电插座	15.6	389	3.7
进口盖板	589	389	6.0
压差活门端盖	15.6	389	2.4

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