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工程设计学报  2026, Vol. 33 Issue (1): 117-129    DOI: 10.3785/j.issn.1006-754X.2026.05.162
优化设计     
燃气调节阀低扭矩优化设计及试验研究
刘广奥1(),陈英龙1(),罗畅敏2,闫博1,高飞1
1.大连海事大学 船舶与海洋工程学院,辽宁 大连 116026
2.中国航发贵州红林航空动力控制科技有限公司,贵州 贵阳 551522
Optimization design and experimental study of gas control valve with low torque
Guang'ao LIU1(),Yinglong CHEN1(),Changmin LUO2,Bo YAN1,Fei GAO1
1.College of Naval Architecture and Ocean Engineering, Dalian Maritime University, Dalian 116026, China
2.AECC Guizhou Honglin Aviation Power Control Technology Limited Company, Guiyang 551522, China
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摘要:

针对燃气调节阀启闭过程中的高扭矩问题,开展多因素分析与结构优化设计研究,提出了结合拓扑优化、响应面法与非支配排序遗传算法II的低扭矩优化方法。通过建立调节阀启闭扭矩理论模型,明确了机械摩擦扭矩为主要影响因素,并重点分析了介质作用力、弹簧预紧力和格莱圈压缩率对扭矩与密封性能的耦合效应。在结构优化中,通过拓扑优化对阀座形态进行了重构,以减小有效的介质作用面积,降低摩擦阻力;随后,基于响应面回归模型构建了以机械摩擦扭矩和泄漏量为目标的多目标优化模型,并结合非支配排序遗传算法II实现了扭矩与密封性能的协同优化。试验结果表明:在5.2 MPa介质压力下,优化后调节阀的机械摩擦扭矩降低了71.8%,验证了所提出优化方法的准确性与可行性。研究结果为燃气调节阀的高性能设计与国产化奠定了理论基础。

关键词: 燃气调节阀低扭矩拓扑优化响应面法非支配排序遗传算法II    
Abstract:

To address the high torque issue of gas control valves during opening and closing, a multi-factor analysis and structural optimization design study is conducted, and a low-torque optimization approach integrating topology optimization, response surface methodology, and non-dominated sorting genetic algorithm II (NSGA-II) is proposed. By establishing a theoretical opening/closing torque model of the control valve, it was clarified that mechanical friction torque was the dominant influencing factor, and the coupling effect of medium-induced force, spring preload, and Glyd ring compression ratio on torque and sealing performance was analyzed in detail. In the structural optimization process, the valve seat shape was reconstructed through topology optimization to reduce the effective medium-acting area and frictional resistance. Subsequently, a multi-objective optimization model with mechanical friction torque and leakage rate as objectives was constructed based on the response surface regression model, and the torque and sealing performance were simultaneously optimized by combining the NSGA-II. The experimental results showed that under a medium pressure of 5.2 MPa, the mechanical friction torque of the optimized control valve was reduced by 71.8%, validating the accuracy and feasibility of the proposed optimization approach. The research results provide a theoretical basis for high-performance design and localization of gas control valves.

Key words: gas control valve    low torque    topology optimization    response surface methodology    non-dominated sorting genetic algorithm II
收稿日期: 2025-07-10 出版日期: 2026-03-01
CLC:  TH 134  
基金资助: 国家自然科学基金资助项目(52275053);国家重点研发计划资助项目(2021YFC2802403)
通讯作者: 陈英龙     E-mail: lga13723908272@163.com;chenyinglong@dlmu.edu.cn
作者简介: 刘广奥(2001—),男,硕士生,从事液压传动与控制研究,E-mail: lga13723908272@163.com,https://orcid.org/0009-0007-9512-3423
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引用本文:

刘广奥,陈英龙,罗畅敏,闫博,高飞. 燃气调节阀低扭矩优化设计及试验研究[J]. 工程设计学报, 2026, 33(1): 117-129.

Guang'ao LIU,Yinglong CHEN,Changmin LUO,Bo YAN,Fei GAO. Optimization design and experimental study of gas control valve with low torque[J]. Chinese Journal of Engineering Design, 2026, 33(1): 117-129.

链接本文:

https://www.zjujournals.com/gcsjxb/CN/10.3785/j.issn.1006-754X.2026.05.162        https://www.zjujournals.com/gcsjxb/CN/Y2026/V33/I1/117

图1  燃气调节阀整体结构
图2  阀杆密封结构
图3  计量模块总装1—底部盖板;2—组合弹簧;3—压紧座;4—阀座;5—密封圈;6—上端盖;7—阀体;8—轴承;9—阀杆;10—V形阀芯;11—格莱圈;12—阀底座。
图4  燃气调节阀密封结构
图5  燃气调节阀内部流道
图6  不同阀芯开度下的流道压力分布云图
图7  不同阀芯开度下的流致扭矩
图8  燃气调节阀试验台
图9  燃气调节阀低扭矩优化流程
图10  阀座结构优化流程
图11  优化前阀座的应力分布
图12  优化后阀座的应力分布
设计变量下限中心值上限
阀座前后端面积差A/mm20129258
弹簧预紧力B/N200250300
格莱圈压缩率C/%1012.515
表1  设计变量取值范围
图13  前后端面积差不同的阀座
试验序号A/mm2B/NC/%Tm/(N·m)Lr/(L/min)
112925012.56.170
212925012.56.820
3025010.03.675.80
412930015.09.870
512930010.06.810.60
625830012.517.280
725825010.015.340.80
812920010.05.671.32
9030012.54.845.00
1012920015.08.481.20
11025015.04.326.45
12020012.53.128.20
1312925012.56.560
1425820012.516.761.00
1525825015.021.870
表2  响应面试验方案设计及结果
方差来源均方自由度离差平方和FP
模型470.95952.33149.35<0.000 1
A382.261382.261 090.9<0.000 1
B2.8312.838.080.036 1
C21.32121.3260.850.000 6
AB0.360 010.360 01.030.357 3
AC8.6418.6424.670.004 2
BC0.016 910.016 90.048 20.834 9
A253.53153.53152.77<0.000 1
B20.166 710.166 70.475 90.521 0
C23.7913.7910.800.021 8
残差1.7550.350 4
失拟度1.4530.484 53.250.244 3
总离差472.7014
决定系数0.996 3
调整系数0.989 6
表3  机械摩擦扭矩响应面回归模型方差分析结果
方差来源均方自由度离差平方和FP
模型111.06912.3483.33<0.000 1
A70.39170.39475.33<0.000 1
B4.6714.6731.510.002 5
C0.110 510.110.745 90.427 3
AB1.2111.218.170.035 5
AC0.469 210.469 23.170.135 2
BC0.0610.060.405 30.552 3
A233.84133.84228.54<0.000 1
B21.0111.016.810.047 7
C20.240 110.240 11.620.258 9
残差0.740 450.148 1
失拟度0.740 430.246 8
总离差111.8014
决定系数0.993 4
调整系数0.981 5
表4  泄漏量响应面回归模型方差分析结果
图14  燃气调节阀机械摩擦扭矩和泄漏量的响应面
参数数值
种群数量100
最大迭代次数300
交叉概率0.8
函数容差1×10-4
变异概率0.1
表5  NSGA-II的相关参数
图15  机械摩擦扭矩与泄漏量的Pareto 最优解集
方案A/mm2B/NC/%

Tm/

(N·m)

Lr/

(L/min)

1137.23239.9212.236.640
2129.96252.8111.676.120
3124.34263.1311.746.010
表6  燃气调节阀的候选优化方案
图16  优化后的阀座结构1—波形弹簧;2—密封圈Ⅰ;3—压紧座;4—阀座;5—O形圈;6—轴套;7—密封圈Ⅱ。
图17  优化前后燃气调节阀的机械摩擦扭矩对比
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