高速涡轮泵动静压混合式气体隔离密封扰动性能

doi:10.11949/0438-1157.20240760

摘要/Abstract

摘要：

隔离密封对高速涡轮泵燃料密封极为重要，但其在工作时存在供气压力波动、外界振动强烈等问题，会严重影响密封性能。对动静压隔离密封气膜扰动工况，基于有限元数值分析方法建立了动态变化扰动分析模型，采用Fluent动网格技术和MATLAB求解端面气膜扰动刚度及扰动阻尼，对比静压式与动静压混合式气体隔离密封的扰动性能，讨论气膜厚度、工作压力及扰动幅值等参数对扰动性能的影响，得到其变化规律，并试验验证了动静压密封的抗扰动性能。结果表明：扰动频率的增加使得扰动刚度整体呈现先减小后增大的趋势，扰动阻尼随扰动频率的增加迅速降低，在10~100 Hz时逐渐趋于平稳。供气压力与扰动刚度、扰动阻尼呈正相关。工作转速增大，扰动刚度在低频段增大、在中高频段减小，扰动阻尼全频减小。扰动幅值增大，扰动刚度在中低频段几乎不变、在高频段减小，扰动阻尼略有增大。工作膜厚与扰动刚度、扰动阻尼呈负相关。动静压式混合密封有效提升了密封装置中低频下的稳定性能，避免了密封处于低压、低转速时抗扰动能力不足的问题。

关键词: 隔离密封, 气体, 动静压, 扰动刚度, 扰动阻尼

Abstract:

The isolation seal is extremely important for high speed turbine pump fuel seals, but it has problems such as gas supply pressure fluctuations and strong external vibration at work, which will seriously affect the sealing performance. Any compromise in these areas could have a detrimental impact on the sealing performance. Accordingly, the conditions for disturbance of the dynamic and static pressure isolation seal gas membrane have been established on the basis of a finite element numerical analysis. A dynamic change of disturbance analysis model has been constructed by using Fluent dynamic mesh technology and MATLAB to solve the end face gas membrane disturbance stiffness and disturbance damping. This has been compared with the static pressure and dynamic and static pressure. The mixed gas isolation seal disturbance performance has been discussed in terms of the gas membrane thickness, working pressure and disturbance amplitude, and other parameters. The influence of the gas film thickness and perturbation amplitude on the perturbation performance has been investigated, and a rule of change has been established. Finally, the anti-perturbation performance of dynamic and static pressure seals has been tested and verified. The results indicate that an increase in perturbation frequency leads to a decrease in overall perturbation stiffness, which then increases. Additionally, perturbation damping decreases rapidly with the increase in perturbation frequency, reaching a stable value between 10 Hz and 100 Hz. The supply pressure of gas is found to be positively correlated with both the stiffness and damping of the perturbation. As the speed increases, the stiffness of the perturbation increases in the low-frequency band and decreases in the middle and high-frequency bands. The damping decreases across the entire frequency spectrum. As the perturbation amplitude is increased, the perturbation stiffness remains almost unchanged in the middle and low frequency bands, while it decreases in the high frequency band. The perturbation damping increases slightly, while the working film thickness is negatively correlated with the perturbation stiffness and the perturbation damping. Hybrid dynamic and static pressure seals effectively improve the stability of the sealing device in low frequency, avoiding the problem of insufficient anti-disturbance ability when the seal is in low pressure and low speed.

Key words: isolating seal, gas, dynamic and static pressure, perturbation stiffness, perturbation damping

中图分类号:

TB 42

李双喜, 刘安, 刘志远, 张江腾, 李世聪. 高速涡轮泵动静压混合式气体隔离密封扰动性能[J]. 化工学报, 2025, 76(1): 311-323.

Shuangxi LI, An LIU, Zhiyuan LIU, Jiangteng ZHANG, Shicong LI. Disturbance performance of dynamic and static pressure hybrid gas isolation seal of high-speed turbopumps[J]. CIESC Journal, 2025, 76(1): 311-323.

图/表 21

图1 动静压隔离密封结构示意图

Fig.1 Schematic diagram of dynamic-hydrostatic hybrid seal

图2 密封结构尺寸

Fig.2 Dimensional drawing of seal structure

表1 静环端面结构参数

Table 1 Static ring end face structure parameters

参数	数值	参数	数值
内侧槽槽根径d₁/mm	57	稳压槽内径d₄/mm	71
外侧槽槽根径d₂/mm	91	稳压槽外径d₅/mm	77
节流孔直径d_g/mm	0.2	稳压槽深度H₁/mm	0.2
节流孔个数N₁	8	稳压槽中心圆直径d₃/mm	74

表2 螺旋槽结构参数

Table 2 Structural parameters of groove

参数	数值
螺旋角α/(°)	15
槽深 H_g/μm	8
槽堰比 γ	0.5
槽坝比 β	0.7
槽数 N_g	2×8

表3 密封动静环组件结构参数

Table 3 Dynamic-hydrostatic hybrid seal assembly structure parameters

参数	数值	参数	数值
动环内径d₆/mm	40	静环内径d₈/mm	51
动环外径d₇/mm	97	静环外径d₉/mm	97
动环厚度B₁/mm	13	静环厚度B₂/mm	22.5

图3 动静压隔离密封扰动性能分析物理模型

Fig.3 Geometric model of dynamic-hydrostatic hybrid seal

图4 扰动性能求解流程

Fig.4 Disturbance performance solution flow

图5 仿真模型验证

Fig.5 Validation of simulation model

图6 一个扰动周期下气膜压力场分布变化

Fig.6 Variation of air film pressure field distribution for one perturbation cycle

图7 不同扰动频率下承载力变化曲线

Fig.7 Change curve of bearing capacity under different disturbance frequencies

图8 位移与承载力函数间相位差

Fig.8 Phase difference between displacement and bearing capacity function

图9 不同扰动频率下扰动刚度及扰动阻尼

Fig.9 Disturbance stiffness and damping at different disturbance frequencies

图10 密封形式对比

Fig.10 Comparison of sealing forms

图11 两种密封扰动刚度和扰动阻尼对比结果

Fig.11 Comparison results of perturbation stiffness and perturbation damping of two kinds of seals

图12 扰动刚度及扰动阻尼与供气压力间变化关系

Fig.12 Variation of perturbation stiffness and perturbation damping versus supply pressure

图13 扰动刚度及扰动阻尼与工作膜厚间变化关系

Fig.13 Variation of perturbation stiffness and perturbation damping versus film thickness

图14 扰动刚度及扰动阻尼与工作转速变化关系

Fig.14 Variation of disturbance stiffness and disturbance damping versus operating speed

图15 扰动刚度及扰动阻尼与扰动幅值间变化关系

Fig.15 Variation of disturbance stiffness and disturbance damping versus disturbance amplitude

图16 试验系统原理

Fig.16 Test system principle

图17 静环表面形貌

Fig.17 Surface morphology of static ring

图 18 膜厚调控试验结果

Fig. 18 Film thickness control test results

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