端面双向自密封结构设计与验证研究

李开福; 管尤亮; 贾国涛; 姜荃; 刘云帆; 焦鹏

doi:10.11993/j.issn.2096-3920.2025-0020

端面双向自密封结构设计与验证研究

doi: 10.11993/j.issn.2096-3920.2025-0020

李开福^1,,
管尤亮^1, ,,
贾国涛^1,,
姜荃^1,,
刘云帆^1,,
焦鹏^2,

1.
中国船舶重工集团公司第705研究所昆明分部, 云南昆明 650032
2.
浙江大学特种装备研究所, 浙江杭州 310027

详细信息

作者简介:
李开福(1987-) 男硕士研究生, 高级工程师, 主要研究方向为密封结构设计及分析

通讯作者:
管尤亮(1998-) 男硕士研究生, 工程师, 主要研究方向为密封与腐蚀防护.

中图分类号: TJ630; U663
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出版历程
- 收稿日期: 2025-02-05
- 修回日期: 2025-03-21
- 录用日期: 2025-03-24
- 网络出版日期: 2025-09-12

Design and verification of end-face bidirectional self-sealing structure

LI Kaifu^1
,,
GUAN Youliang^{1
, ,},
JIG Guotao^1
,,
JIANG Quan^1
,,
LIU Yunfan^1
,,
JIAO Peng^2
,

1.
The 705 Research Institute, China Shipbuilding Industry Corporation, Kunming Yunnan 650032, China
2.
Institute of Advanced Equipment, Zhejiang university, Hangzhou 310027, China

摘要

摘要: 为实现水下大口径舱盖的端面双向密封, 并解决合盖过程密封圈反力大问题, 创新地结合舌形截面良好自密封优势和燕尾结构防脱出结构, 设计了5种规格的“高低舌”双向自密封圈, 采用ABAQUS对密封圈进行了应力、变形及接触压力等仿真分析, 并试制样机开展了内、外压密封试验与旋松、旋紧力矩测试。试验结果与有限元分析结果一致, “高低舌”形密封圈能在低反力下实现端面双向自密封, “舌形”结构倒角越大, 密封圈与密封面之间的接触应力值越高, 密封效果越好; 密封圈两侧“舌”高相差越小, 中间平台高度越低, 密封圈越容易被吸出; 降低密封圈的最大高度和中间平台高度能有效降低密封反力, 延长密封圈使用寿命。基于试验结果对密封圈进行改进优化并试制大口径密封圈, 合盖压紧千余次后仍能实现内气压、内水压和外水压的自密封。研究成果可为水下大型承压设备端面密封设计应用提供参考。
- 舌形密封圈 /
- 结构设计 /
- 有限元分析 /
- 密封性能
Abstract: In order to achieve the bidirectional sealing of the end face of underwater large-caliber hatch covers and solve the problem of large reaction force of the sealing ring during the closing process. Innovatively combining the good self-sealing advantage of the tongue-shaped cross-section and the anti-ejection structure of the dovetail structure, five specifications of "high-low tongue" bidirectional self-sealing rings were designed. The stress, deformation, contact pressure and other simulation analyses of the sealing rings were carried out using ABAQUS, and a prototype was trial-produced to conduct internal and external pressure sealing tests as well as loosening and tightening torque tests. The test results are consistent with the results of finite element analysis. The "high-low tongue" sealing ring can achieve bidirectional self-sealing of the end face under low reaction force. The larger the chamfer of the "tongue-shaped" structure, the higher the contact stress value between the sealing ring and the sealing surface, and the better the sealing effect; the smaller the difference in the height of the "tongue" on both sides of the sealing ring, the lower the height of the middle platform, and the easier it is for the sealing ring to be sucked out; reducing the maximum height and the middle platform height of the sealing ring can effectively reduce the sealing reaction force and extend the service life of the sealing ring. Based on the test results, the sealing ring was improved and optimized, and a large-caliber sealing ring was trial-produced. After closing and pressing the cover for more than a thousand times, it can still achieve self-sealing of internal air pressure, internal water pressure and external water pressure. The research results provide a reference for the design and application of end face sealing of large underwater pressure-bearing equipment.
- tongue seal ring /
- structural design /
- finite element analysis /
- sealing performance

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图 1 密封结构示意

Figure 1. Schematic diagram of the sealing structure

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图 2 缩比验证舱实物

Figure 2. Scaled-down validation chamber

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图 3 5种不同截面形状的密封圈及实物图

Figure 3. Five different cross-sectional shapes of sealing rings and actual pictures

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图 4 模型边界条件

Figure 4. Conditions of model boundary

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图 5 模型网格划分情况

Figure 5. Mesh division of model

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图 6 合盖时1#密封圈的仿真结果

Figure 6. Simulation results of 1# sealing ring when the cover is closed

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图 7 合盖时2#密封圈的仿真结果

Figure 7. Simulation results of 2# sealing ring when the cover is closed

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图 8 合盖时3#密封圈的仿真结果

Figure 8. Simulation results of 3# sealing ring when the cover is closed

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图 9 合盖时4#密封圈的仿真结果

Figure 9. Simulation results of 4# sealing ring when the cover is closed

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图 10 合盖时5#密封圈的仿真结果

Figure 10. Simulation results of 5# sealing ring when the cover is closed

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图 11 舱盖法兰和舱体法兰不同间隙下合盖所需压紧力和最大接触应力

Figure 11. Under different clearances between hatch flange and cabin flange

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图 12 内水压密封试验过程

Figure 12. Internal water pressure sealing test process

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图 13 不同密封圈合盖旋紧和旋松力矩对比

Figure 13. Comparison of tightening and loosening torques for different sealing rings

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图 14 优化改进情况

Figure 14. Optimization and improvement

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表 1 密封圈关键特征尺寸

Table 1. Key characteristics of sealing ring mm

密封圈编号	1#	2#	3#	4#	5#
圈中心高	12.0	11.5	11.5	12.0	11.0
外舌高	17.0	17.0	15.0	15.0	15.0
内舌高	13.8	13.8	14.0	14.0	14.0
外舌半径	14.0	14.0	15.0	16.0	12.0
内舌半径	10.0	18.0	12.0	10.0	8.0
圈中心宽	3.0	0.0	0.0	4.0	3.0
外台阶宽	3.0	3.0	3.0	2.0	2.0
内台阶宽	2.0	2.0	3.5	3.5	3.5

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表 2 不同间隙下舱盖法兰和舱体法兰合盖所需的压紧力

Table 2. Pressure of the hatch and barrel flange cover under different clearance kN

密封圈编号	间隙值
密封圈编号	1.5 mm	1.0 mm	0.5 mm	0 mm
1^#	0.92	2.12	6.62	16.32
2^#	0.79	1.98	4.70	12.12
3^#	0.56	1.01	2.64	13.73
4^#	0.45	0.97	2.79	11.94
5^#	0.35	0.52	1.52	4.73

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表 3 不同间隙下舱盖法兰和舱体法兰合盖的最大接触应力

Table 3. Maximum contact stress of hatch cover and barrel flange cover under different clearance MPa

密封圈编号	间隙值
密封圈编号	1.5 mm	1.0 mm	0.5 mm	0 mm
1#	1.92	1.97	3.80	7.77
2#	1.93	1.99	3.77	6.66
3#	1.61	1.37	2.44	3.39
4#	0.86	0.81	1.01	2.62
5#	1.40	1.51	3.32	3.22

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表 4 5种密封圈的内压试验结果

Table 4. The results of the inner pressure seal test of five sealing rings

编号	充满水后	内水压 0 MPa-6.0 MPa	内气压 0 MPa-0.3 MPa	检查密封圈
1#	无泄漏	无压降	无压降	无损伤
2#	无泄漏	无压降	无压降	无损伤
3#	无泄漏	无压降	无压降	无损伤
4#	有泄漏	无压降	无压降	吸出脱落
5#	无泄露	无压降	无压降	吸出脱落

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表 5 五种密封圈的外水压密封试验结果

Table 5. The results of the outer water pressure seal test of five sealing rings

编号	0 MPa升压至6.0 MPa	6.0 MPa降压至0 MPa	检查密封圈	备注
1#	无压降	无压降	无损伤	难合盖
2#	无压降	无压降	无损伤	/
3#	无压降	无压降	无损伤	/
4#	无明显压降	无明显压降	吸出脱落	积水少
5#	无压降	无压降	吸出脱落

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表 6 合盖旋紧、旋松力矩测试结果)

Table 6. The results of the test result of the close and spinning torque N·m

编号	旋紧				旋松
编号	最小值	最大值	均值	标准差	最小值	最大值	均值	标准差
1#	535.0	603.0	569.0	48.1	393.0	436.0	414.5	30.4
2#	441.0	499.0	470.0	41.0	322.0	353.0	337.5	21.9
3#	392.0	460.0	426.0	48.1	291.0	313.0	302.0	15.6
4#	361.0	413.0	387.0	36.8	278.0	298.0	288.0	14.1
5#	320.0	378.0	349.0	41.0	228.0	259.0	243.5	21.9

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