热力耦合作用下涡轮泵用镶装式机械密封端面变形规律研究

doi:10.11949/0438-1157.20241316

摘要/Abstract

摘要：

以液体火箭发动机涡轮泵用镶装式机械密封为研究对象，考虑密封静环的过盈配合作用及密封环与环座之间的接触，建立了其深冷工况下的热弹流润滑耦合模型，采用原始对偶内点优化方法（IPOPT）处理接触带来的变形求解问题，研究了静环镶装过盈量、转速和密封压力对深冷环境下涡轮泵镶装式机械密封端面变形行为及密封界面的热弹流润滑特性。结果表明，在密封环热力耦合作用及密封组件间的接触作用下，密封动静环端面间产生沿半径方向非单调变化的膜厚分布，深冷环境下的温度变形远大于密封压力的力变形；密封静环的初始过盈量在装配后的研磨去除影响工作状态下密封的液膜厚度分布，静环过盈量和深冷环境下的收缩变形是密封环结构设计中需重点考虑的因素。建立的考虑密封组件接触作用的流固热力耦合模型可为镶装式机械密封环的结构优化提供理论基础。

关键词: 涡轮泵, 镶装式机械密封, 深冷环境, 原始对偶内点优化

Abstract:

Taking the shrift-fit mechanical seals used in the turbo-pumps of liquid rocket engines as the research objective, taking the interference fit effect of the stationary seal ring as well as the contact between the seal ring and its seats into consideration, the thermoelastic-hydrodynamic lubrication coupling model under cryogenic conditions is established. The interior point optimizer method for nonlinear programming (IPOPT) was employed to address the problem of deformation solution arising from the boundary contact. Subsequently, the influences of the interference fit values of the stationary seal ring, rotational speeds, and sealing pressures on the end-face deformation and thermo-elasto-hydrodynamic lubrication characteristics of the shrift-fit mechanical seals of the turbo pump under the cryogenic environment were investigated. The results show that: under the thermal coupling of the sealing ring and the contact between the sealing components, a non-monotonic film thickness distribution is generated between the end faces of the dynamic and static sealing rings along the radial direction, and the temperature deformation in the cryogenic environment is much greater than the force deformation of the sealing pressure. Moreover, the initial interference fit value of the stationary seal ring exerts an impact on the liquid film thickness distribution of the seal in the working state after grinding and removal after the assembly process. Consequently, both the interference fit value of the stationary seal ring and the thermal deformation under the cryogenic environment are crucial factors to be considered in the structural design of the seal rings. The present thermos-mechanical coupling model, considering the contact effect of the sealing components, can provide theoretical foundation for the structural optimization of the shrift-fit mechanical seal ring.

Key words: turbo pump, shrink-fit mechanical seal, cryogenic condition, primal-dual interior point optimization

中图分类号:

TH 117.2

余嘉桐, 孟祥铠, 赵文静, 刘磊, 张力豪, 彭旭东. 热力耦合作用下涡轮泵用镶装式机械密封端面变形规律研究[J]. 化工学报, 2025, 76(6): 2900-2912.

Jiatong YU, Xiangkai MENG, Wenjing ZHAO, Lei LIU, Lihao ZHANG, Xudong PENG. Study on end face deflection of shrink-fit mechanical seals for turbo pump considering thermal-mechanical coupling effect[J]. CIESC Journal, 2025, 76(6): 2900-2912.

图/表 18

图1 机械密封结构示意图

Fig.1 Schematics of mechanical face seal

图2 密封环组件接触对

Fig.2 Seal ring components contact pair

图3 机械密封力和热边界条件

Fig.3 Thermal and mechanical boundary conditions of mechanical seal

图4 密封静环轴向位移

Fig.4 Axial displacement of sealed static ring

表1 端面轴向位移

Table 1 Axial displacements of end face

r/mm	轴向位移/mm		误差/%
r/mm	ANSYS结果	本文结果	误差/%
30	-17.367	-17.404	0.22
32	-13.816	-13.861	0.33
34	-10.398	-10.446	0.47
36	-7.032	-7.085	0.75
38	-3.61	-3.659	1.33
40	0.0163	0.0161	1.62
42	4.176	4.116	1.45
44	9.575	9.455	1.26

图5 计算流程[18, 25]

Fig.5 Computational procedure[18, 25]

表2 密封环材料物性参数［28-29］

Table 2 Physical parameters of seal rings［28-29］

参数	Inconel 718(-190℃)	静环石墨环
弹性模量E/GPa	212	27.7
泊松比	0.31	0.25
热膨胀系数α/(m·℃^-1)	12.63×10^-6	5.27×10^-6
热导率k/(W/(m·℃))	7.94	115

表3 密封端面几何参数

Table 3 Geometric parameters of seal face

参数	数值	参数	数值
螺旋槽根径r_g/mm	36	槽深h_g/μm	5
螺旋角γ/(°)	12	槽数N_g	12
端面外径r_o/mm	45	端面外径r_i/mm	30
螺旋槽周向开槽比α_g	0.5	螺旋槽径向开槽比α_w	0.5

图6 密封环变形、温度和液膜压力分布

Fig.6 Seal ring deflection, temperature and liquid film pressure distribution

图7 密封环端面热力变形

Fig.7 Thermal and mechanical deflection of seal rings

图8 液膜压力、液膜厚度和端面温度分布

Fig.8 Film pressure, thickness and temperature distribution

图9 不同过盈量下的动静环端面轴向变形分布

Fig.9 Axial deflection of seal ring end face at different interferences

图10 不同过盈量下的膜厚、膜温和膜压分布

Fig.10 Film thickness, temperature and pressure distribution at different interferences

表4 不同过盈量下的泄漏率

Table 4 Leakage rate for different amounts of interference

镶装过盈量/mm	泄漏率/(ml $∙$ h^-1)
0.18	4991.56
0.19	5486.42
0.20	6195.83
0.21	6596.20
0.22	7213.79

表4 不同过盈量下的泄漏率

Table 4 Leakage rate for different amounts of interference

镶装过盈量/mm	泄漏率/(ml $∙$ h^-1)
0.18	4991.56
0.19	5486.42
0.20	6195.83
0.21	6596.20
0.22	7213.79

图11 不同转速下的密封动静环端面轴向变形

Fig.11 Axial deflection of seal rings end face at different rotational speeds

图12 不同转速下的膜厚、膜温和膜压分布

Fig.12 Film thickness, temperature and pressure distribution at different rotational speeds

图13 不同密封介质压力下的动静环端面轴向变形分布

Fig.13 Axial deflection of seal ring end faces at different sealing pressures

图14 不同密封介质压力下的液膜厚度、温度和压力分布

Fig.14 Film thickness, temperature and pressure distribution at different sealing pressures

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