基于流固热全耦合数值方法的超高压干气密封的热力变形影响分析及变形协调研究

doi:10.11949/0438-1157.20250646

摘要/Abstract

摘要：

超高压干气密封作为极端工况下的非接触式密封，其性能显著受高温高压环境中的热力变形影响，热力变形研究对密封的长期稳定运转至关重要。针对高温高压高转速极端工况下，建立流-固-热多物理场全耦合的性能分析模型，研究热力耦合变形对密封性能的影响，展开变形协调分析与优化研究，探究优化后的结构对密封性能的综合影响，得到超高压干气密封的适宜操作范围。建立高压密封试验装置，试验验证了模型的准确性。研究表明，当动环轴向厚度之比M_d为1.05~1.10，静环轴向厚度之比M_f =1.20时，间隙近乎为理想平行型间隙，密封性能最好；当平衡直径处泛塞圈摩擦力与弹簧弹力之比S_f为0.60~0.80时，密封性能达到最佳；适宜操作的压力范围为0~14MPa；线速度范围为30~160m/s，温度范围为50~200℃，为超高压干气密封结构参数和工况参数的设计提供了理论参考。

关键词: 超高压干气密封, 流-固-热耦合, 热力变形, 变形协调

Abstract:

As a non-contact seal under extreme working conditions, the performance of ultra-high-pressure dry gas seal is significantly affected by thermal deformation in high temperature and high pressure environment, and the study of thermal deformation is crucial for the long-term stable operation of the seal. Aiming at the extreme working conditions of high temperature and high pressure with high rotational speed, establish a performance analysis model of fluid-solid-thermal multi-physical field coupling, study the influence of thermal coupling deformation on the sealing performance, and carry out the deformation coordinated analysis and optimisation study to investigate the comprehensive influence of the optimised structure on the sealing performance, and obtain the suitable operating range of the ultra-high-pressure dry gas seals. A high-pressure sealing test device is established, and the accuracy of the model is verified in the test. The study shows that when the ratio of the axial thickness of the dynamic ring M_d is 1.05~1.10, and the ratio of the axial thickness of the static ring M_f = 1.20, the gap is nearly ideal parallel gap, and the sealing performance is the best; when the ratio of the friction force of the flooded ring at the equilibrium diameter to the elasticity of the spring S_f is 0.60~0.80, the sealing performance reaches the optimum. The suitable operating pressure range is 0~14MPa, linear velocity range is 30~160m/s, and temperature range is 50~200 ℃, which provides theoretical references for the design of the structural parameters and working conditions of the ultra-high-pressure dry gas seal.

Key words: ultra-high-pressure dry gas seal, fluid-solid-thermal coupling, thermal deformation, deformation compatibility

中图分类号:

TQ 028.8

张家豪, 弓志超, 李双喜, 王克俭, 李方俊. 基于流固热全耦合数值方法的超高压干气密封的热力变形影响分析及变形协调研究[J]. 化工学报, DOI: 10.11949/0438-1157.20250646.

Jiahao ZHANG, Zhichao GONG, Shangxi LI, Kejian WANG, Fangjun LI. Thermal deformation influence analysis and deformation coordination research of ultra-high pressure dry gas seal based on fluid solid thermal fully coupled numerical method[J]. CIESC Journal, DOI: 10.11949/0438-1157.20250646.

图/表 35

图1 多物理场耦合分析流程图

Fig. 1 Flowchart of multi-physics field coupling analysis

图2 超高压干气密封部件结构示意图

Fig. 2 Schematic diagram of the structure of ultra-high pressure dry gas seal components

表1 超高压干气密封结构参数

Table 1 Structural parameters of ultra-high pressure dry gas seal

参数名称/mm	数值	参数名称/mm	数值
动环端面外径r_o,r	66.2	动环端面内径r_i,r	51.5
动环背部距压紧环最小距离L_i1,min	48.6	动环背部距压紧环最大距离L_i1,max	49
静环端面外径r_o,s	65.5	静环端面内径r_i,s	52
动环端面厚度L_i	14	静环端面厚度L_s	11
压紧环内径r_i,y	39	动环背部泛塞圈密封内径r_i,q	59.8
平衡直径r_i,p	55.5	弹簧作用中心处内径r_i,t	67
泛塞圈轴向最大长度L_f1,max	3.55	泛塞圈径向最大长度L_f2,max	5
泛塞圈唇口长度L_f3	2.2	泛塞圈底部最小长度L_f4,min	1.9
泛塞圈极限压缩宽度L_f5,max	3.1	泛塞圈单边最大压缩量δ_f,max	0.225
泛塞圈弹簧内径R_i,f	1.0	泛塞圈单边壁厚L_f6	0.675

图3 端面螺旋槽示意图

Fig. 3 Schematic diagram of end face groove type

图4 密封环受力分析及位移边界约束条件

Fig. 4 Seal ring force analysis and displacement boundary constraint conditions

表2 超高压干气密封环境参数

Table 2 Ultra high pressure dry gas seal environmental parameters

参数名称（高压侧）	数值	参数名称（低压侧）	数值
密封介质	空气	密封介质	空气
工作压力p₁/MPa	0~16	工作压力p₂/MPa	常压
工作温度T₁/K	0~600	工作温度T₂/K	常温
转速n₁/r·min^-1	0~25000	转速n₂/r·min^-1	0~25000

表3 超高压干气密封材料参数

Table 3 Parameters of ultra-high pressure dry gas sealing materials

材料属性	动静环（SIC）		静环（M160K）
弹性模量E/（GPa）	400	14	198
泊松比 $ς$	0.45	0.3	0.29
导热系数k/(W·m^-1·℃^-1)	90~110	140	17
固体比热容C_pt(J·kg^-1·℃^-1)	690	640	500
热膨胀系数α/(×10^-6/℃))	4.0	5	16.7
密度ρ（kg·m^-3）	3080	1750	8446

表3 超高压干气密封材料参数

Table 3 Parameters of ultra-high pressure dry gas sealing materials

材料属性	动静环（SIC）		静环（M160K）
弹性模量E/（GPa）	400	14	198
泊松比 $ς$	0.45	0.3	0.29
导热系数k/(W·m^-1·℃^-1)	90~110	140	17
固体比热容C_pt(J·kg^-1·℃^-1)	690	640	500
热膨胀系数α/(×10^-6/℃))	4.0	5	16.7
密度ρ（kg·m^-3）	3080	1750	8446

图5 多物理场分析模型

Fig. 5 Multi-physics field analysis model

图6 耦合分析模型网格无关性验证

Fig. 6 Verification of mesh-independence of coupled analysis models

图7 耦合分析模型计算验证

Fig. 7 Computational validation of the coupled analysis model

图8 不同动静环轴向厚度比下动静环端面最大变形分析云图

Fig. 8 Maximum deformation of dynamic and static ring end face under different dynamic and static ring axial thickness ratios

图9 动环轴向厚度之比对密封端面变形协调的影响

Fig. 9 Influence of the ratio of the axial thickness of the dynamic ring on the coordination of the seal end face deformation

图10 静环轴向厚度之比对密封端面变形协调的影响

Fig. 10 Influence of the ratio of the axial thickness of the static ring on the coordination of the deformation of the seal end face

图11 动环背部泛塞圈密封位置之比md 对密封端面变形协调的影响

Fig.11 Influence of the ratio md of the sealing position of the backside of the dynamic ring pan plug ring on the coordination of seal end face deformation

图12 静环背部泛塞圈密封位置之比mf 对密封端面变形协调的影响

Fig. 12 Influence of the ratio mf of the sealing position of the backside of the static ring pan plug ring on the coordination of the sealing end face deformation

图13 不同泛塞圈结构压缩量对密封端面变形协调的影响

Fig. 13 Influence of different compression amount of pan plug ring structure on the coordination of seal end face deformation

图14 平衡直径处泛塞圈与弹簧的组合结构对静环影响示意图

Fig.14 Schematic diagram of the effect of the combined structure of the pan plug ring and spring on the static ring at the equilibrium diameter

图15 平衡直径处泛塞圈的结构、压缩量与弹簧弹力的组合结构对密封变形协调的影响

Fig. 15 Influence of the structure of the pan plug ring at the equilibrium diameter, the structure of the combination of compression and spring elasticity on the coordination of seal deformation

图16 不同介质压力下的开启力分布

Fig. 16 Distribution of opening force under different media pressure

图17 压力对开启力和闭合力的影响

Fig. 17 Effect of pressure on opening and closing forces

图18 压力对泄漏和薄膜刚度的影响

Fig. 18 Effect of pressure on leakage and film stiffness

图19 不同端面线速度下的膜压分布

Fig. 19 Membrane pressure distribution at different end-face linear velocities

图20 不同端面线速度对开启力的影响

Fig. 20 Effect of different end face linear velocities on opening force

图21 不同端面线速度下对泄漏量和薄膜刚度的影响

Fig. 21 Effect on leakage and film stiffness at different end-face linear velocities

图22 不同温度下的膜压分布

Fig. 22 Membrane pressure distribution at different temperatures

图23 温度对开启力的影响

Fig. 23 Effect of temperature on opening force

图24 温度对泄漏量和薄膜刚度的影响

Fig. 24 Effect of temperature on leakage and film stiffness

图25 超高压干气密封试验系统

Fig. 25 Ultra high pressure dry gas seal test system

图26 超高压干气密封试验图

Fig. 26 Ultra high pressure dry gas seal test diagram

表4 试验验证具体操作条件

Table 4 Specific operating conditions for experimental verification

序号	具体操作条件
1	不同弹簧力（0.6N、0.8N、1.0N）、不同气体压力（1~10MPa）的变化下的泄漏试验
2	不同压缩量（0.1mm、0.15mm、0.2mm）、不同气体压力（1~10MPa）的变化下的泄漏试验
3	常温（25℃）、不同线速度（20~140m/s）下的泄漏试验
4	高温（200℃）、不同线速度（20~140m/s）下的泄漏试验
5	高温（200℃）、不同线速度（20m/s、60m/s、120m/s）、不同气体压力（1~10MPa）的变化下的泄漏试验

图27 不同弹簧力对泄漏量的影响

Fig. 27 Effect of different spring forces on the amount of leakage

图28 不同压缩量对泄漏量的影响

Fig. 28 Effect of varying compression on leakage

图29 常温（25℃）泄漏试验

Fig. 29 Leakage test at room temperature (25°C)

图30 高温（200℃）泄漏试验

Fig. 30 High temperature (200°C) leakage test

图31 动态压力泄漏试验

Fig. 31 Dynamic Pressure Leakage Test

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