An Improved Design of Spiral Groove Mechanical Seal

The coupling effect among the flow of fluid film, the frictional heat of fluid film and the thermal deformation of sealing rings is inherent in mechanical seals. The frictional heat transfer analysis was carded out to optimize the geometrical parameters of the sealing rings, such as the length, the inner radius and the outer radius. The geometrical parameters of spiral grooves, such as the spiral angle, the end radius, the groove depth, the ratio of the groove width to the weir width and the number of the grooves, were optimized by regarding the maximum bearing force of fluid film as the optimization objective with the coupling effect considered. The depth of spiral groove was designed to gradually increase from the end radius of spiral groove to the outer radius of end face in order to decrease the weakening effect of thermal deformation on the hydrodynamic effect of spiral grooves. The end faces of sealing rings were machined to form a divergent gap at inner radius, and a parallel gap will form to reduce the leakage rate when the thermal deformation takes place. The improved spiral groove mechanical seal possesses good heat transfer performance and sealing ability.

Influence Analysis of Secondary O-ring Seals in Dynamic Behavior of Spiral Groove Gas Face Seals

The current research on secondary O-ring seals used in mechanical seals has begun to focus on their dynamic properties. However, detailed analysis of the dynamic properties of O-ring seals in spiral groove gas face seals is lacking. In particular a transient study and a difference analysis of steady-state and transient performance are imperative. In this paper, a case study is performed to gauge the effect of secondary O-ring seals on the dynamic behavior（steady-state performance and transient performance） of face seals. A numerical finite element method（FEM） model is developed for the dynamic analysis of spiral groove gas face seals with a flexibly mounted stator in the axial and angular modes. The rotor tilt angle, static stator tilt angle and O-ring damping are selected to investigate the effect of O-ring seals on face seals during stable running operation. The results show that the angular factor can be ignored to save time in the simulation under small damping or undamped conditions. However, large O-ring damping has an enormous effect on the angular phase difference of mated rings, affecting the steady-state performance of face seals and largely increasing the possibility of face contact that reduces the service life of face seals. A pressure drop fluctuation is carried out to analyze the effect of O-ring seals on the transient performance of face seals. The results show that face seals could remain stable without support stiffness and O-ring damping during normal stable operation but may enter a large-leakage state when confronting instantaneous fluctuations. The oscillation-amplitude shortening effect of O-ring damping on the axial mode is much greater than that on the angular modes and O-ring damping prefers to cater for axial motion at the cost of angular motion. This research proposes a detailed dynamic-property study of O-ring seals in spiral groove gas face seals, to assist in the design of face seals.

Leakage and Stiffness Characteristics of Bionic Cluster Spiral Groove Dry Gas Seal

Spiral groove dry gas seal(S?DGS), the most widely used DGS in the world, encounters the problem of high leakage rate and inferior film stability when used in high?speed machinery equipment, which could not be well solved by optimization of geometrical parameters and molded line of spiral groove. A new type of bionic cluster spiral groove DGS(CS?DGS) is proved to have superior film stability than S?DGS at the condition of high?speed and low?pressure numerically. A bionic CS?DGS is experimentally investigated and compared with common S?DGS in order to provide evidence for theoretical study. The film thickness and leakage rate of both bionic spiral groove and common spiral groove DGS are measured and compared with each other and with theoretical values under different closing force at the condition of static pressure, high?speed and low?pressure, and the film stiffness and stiffness?leakage ratio of these two face seals are derived by the relationship between closing force and film thickness at the steady state. Experimental results agree well with the theory that the leakage and stiffness of bionic CS?DGS are superior to that of common S?DGS under the condition of high?speed and low?pressure, with the decreasing amplitude of 20% to 40% and the growth amplitude of 20%, respectively. The opening performance and stiffness characteristics of bionic CS?DGS are inferior to that of common S?DGS when rotation speed equals to 0 r/min. The proposed research provides a new method to measure the axis film stiffness of DGS, and validates the superior performance of bionic CS?DGS at the condition of high?speed and low?pressure experimentally.

Dynamic Coupling Correlation of Gas Film in Dry Gas Seal with Spiral Groove

In working state, the dynamic performance of dry gas seal, generated by the rotating end face with spiral grooves, is determined by the open force of gas film and leakage flow rate. Generally, the open force and the leakage flow rate can be obtained by finite element method, computational fluid dynamics method and experimental measurement method. However, it will take much time to carry out the above measurements and calculations. In this paper, the approximate model of parallel grooves based on the narrow groove theory is used to establish the dynamic equations of the gas film for the purpose of obtaining the dynamic parameters of gas film. The nonlinear differential equations of gas film model are solved by Runge-Kutta method and shooting method. The numerical values of the pressure profiles, leakage flux and opening force on the seal surface are integrated, and then compared to experimental data for the reliability of the numerical simulation. The results show that the numerical simulation curves are in good agreement with experimental values. Furthermore, the opening force and the leakage flux are proved to be strongly correlated with the operating parameters. Then, the function-coupling method is introduced to analyze the numerical results to obtain the correlation formulae of the opening force and leakage flux respectively with the operating parameters, i.e., the inlet pressure and the rotating speed. This study intends to provide an effective way to predict the aerodynamic performance for designing and optimizing the groove styles in dry gas seal rapidly and accurately.

Numerical Analysis of a Spiral-groove Dry-gas Seal Considering Micro-scale Effects

A dry-gas seal system is a non-contact seal technology that is widely used in different industrial applications.Spiral-groove dry-gas seal utilizes fluid dynamic pressure effects to realize the seal and lubrication processes,while forming a high pressure gas film between two sealing faces due to the deceleration of the gas pumped in or out.There is little research into the effects and the influence on seal performance,if the grooves and the gas film are at the micro-scale.This paper investigates the micro-scale effects on spiral-groove dry-gas seal performance in a numerical solution of a corrected Reynolds equation.The Reynolds equation is discretized by means of the finite difference method with the second order scheme and solved by the successive-over-relaxation（SOR） iterative method.The Knudsen number of the flow in the sealing gas film is changed from 0.005 to 0.120 with a variation of film depth and sealing pressure.The numerical results show that the average pressure in the gas film and the sealed gas leakage increase due to micro-scale effects.The open force is enlarged,while the gas film stiffness is significantly decreased due to micro-scale effects.The friction torque and power consumption remain constant,even in low sealing pressure and spin speed conditions.In this paper,the seal performance at different rotor face spin speeds is also described.The proposed research clarifies the micro-scale effects in a spiral-groove dry-gas seal and their influence on seal performance,which is expected to be useful for the improvement of the design of dry-gas seal systems operating in the slip flow regime.

Flow Dynamics of a Spiral-groove Dry-gas Seal

The dry-gas seal has been widely used in different industries. With increased spin speed of the rotator shaft, turbulence occurs in the gas film between the stator and rotor seal faces. For the micro-scale flow in the gas film and grooves, turbulence can change the pressure distribution of the gas film. Hence, the seal performance is influenced. However, turbulence effects and methods for their evaluation are not considered in the existing industrial designs of dry-gas seal. The present paper numerically obtains the turbulent flow fields of a spiral-groove dry-gas seal to analyze turbulence effects on seal performance. The direct numerical simulation （DNS） and Reynolds-averaged Navier-Stokes （RANS） methods are utilized to predict the velocity field properties in the grooves and gas film. The key performance parameter, open force, is obtained by integrating the pressure distribution, and the obtained result is in good agreement with the experimental data of other researchers. Very large velocity gradients are found in the sealing gas film because of the geometrical effects of the grooves. Considering turbulence effects, the calculation results show that both the gas film pressure and open force decrease. The RANS method underestimates the performance, compared with the DNS. The solution of the conventional Reynolds lubrication equation without turbulence effects suffers from significant calculation errors and a small application scope. The present study helps elucidate the physical mechanism of the hydrodynamic effects of grooves for improving and optimizing the industrial design or seal face pattern of a dry-gas seal.

基于位置特征和螺旋方向的柱面气膜密封槽型控漏能力评价

为探究轴套侧开槽新型柱面气膜密封在控制泄漏方面的能力,首先,采用有限差分法对不同位置特征和螺旋方向的新型柱面气膜密封槽型建立数值模型,通过对比各槽型气膜压力分布和密封性能参数,揭示位置特征和螺旋方向对不同槽型密封特性的影响机理。然后,针对反向“人”字槽型进行了参数化分析,探究螺旋槽角度、槽长坝长比、槽宽台宽比、槽深比对反向“人”字槽泄漏量、浮升力、摩擦力等密封性能参数的影响规律,同时对特定结构参数组合的反向“人”字槽逆流泵送控制泄漏的能力进行评价。结果表明:气膜厚度阶梯变化和偏心收敛楔效应在密封面形成高压气膜区域,有效阻止轴向泄漏,实现轴套侧开槽柱面气膜密封主泄漏通道的密封,且随着转速的增加,新型柱面气膜密封沿轴向间隙的泄漏量呈现下降趋势,该特性对于泄漏控制具有重要意义,特别是在高速运转的工况下。此外,通过合理的槽型参数调控可以使压差流造成的沿轴向间隙密封气体泄漏正好被反向“人”字槽逆流泵送作用导致的密封气体流动补偿,从而实现反向“人”字槽型柱面气膜密封的气体零泄漏甚至负泄漏,为柱面气膜密封槽型结构设计提供理论参考。

衍生T形槽干气密封稳态性能研究

目的 设计具备双向旋转特点的动压型干气密封端面结构,并展现良好的开启性能,以T形槽为优化对象,衍生出一种新型槽型结构。方法 借助有限元软件,计算并对比经典T形槽与衍生槽型在流场特性和稳态性能方面的差异,探讨不同参数对2种槽型干气密封稳态性能的影响规律,揭示衍生槽型的密封机理。结果 衍生槽型的开启力高于经典T形槽,泄漏率也会增加。随着工况参数的升高,2种槽型的稳态性能参数近似线性增加,且差异逐渐增大,最小差异达到6.6%。随着槽深的增加,泄漏率方面的差距在逐渐减小,为扩大衍生槽型的控漏效果,槽深应>5μm。开设有引流槽型结构的衍生槽型稳态性能顺序为发散型>直口型>收敛型,但在文中的工况下,数值差别较小,最大仅为1.2%。结论 相比于经典T形槽,衍生槽型具有更强的动压效应,开启性能明显提升。另外,通过开设不同形式的引流槽可以改变气膜的流动特性和干气密封性能。

基于视觉算法的射孔弹传爆孔封口片自动封贴装置的应用与研究

视觉检测对实现自动化贴标提供了重要的关键信息,基于高斯滤波、高斯拉普拉斯(LOG)边界识别及圆的定位算法,识别了射孔弹弹壳压环孔圆,获得了压环孔的圆心位置。通过压环孔圆心位置(x,y)坐标计算射孔弹起爆槽偏移角度,将导爆索槽的角度及中心圆孔位置信息传送到PLC,控制伺服电机,完成导爆索槽封口片的自动化封贴。

超高速干气密封微织构气膜润滑特性研究

针对航天航空领域,设备超高速、高压运转,干气密封稳定性问题,依据槽型织构优化设计,提出一种槽底微织构螺旋槽干气密封结构,以解决密封在超高速旋转过程中气膜稳定性问题。基于气体润滑理论,建模、划分网格,再导入FLUENT软件对流场进行仿真模拟;改变工况参数和槽型结构参数后,在超高速、高压工况下,相比于普通螺旋槽,槽底微织构螺旋槽干气密封的动压效果有显著提升。结果表明,槽深h_(g)=6μm,膜厚h_(0)=2μm,微织构槽深δ=2μm、微织构槽宽取3.97 mm,微织构槽位于螺旋槽底中间位置时,槽底微织构螺旋槽相比于普通螺旋槽可产生明显的动压效应。

扩压式自泵送流体动压机械密封综合性能研究

扩压式自泵送流体动压机械密封作为1种新的密封结构形式具有优异的密封性能和广泛的应用前景.分别设计出具有等截面型扩压环槽、发散型扩压环槽、收敛型扩压环槽和圆弧型扩压环槽4种扩压式自泵送流体动压机械密封,引入综合评价因子η,通过Fluent数值模拟分别对其综合密封性能进行了分析.基于最佳的扩压环槽结构,通过正交试验,对密封面结构参数进行优化.结果表明:等截面型扩压式自泵送流体动压机械密封综合密封性能最优;在试验参数范围内,螺旋槽数Ng和密封环外径rk对泄漏率均有影响,且螺旋槽数Ng影响最为显著.密封环外径rk和螺旋角α对开启力均有影响,其中密封环外径rk的影响更为显著,随密封环外径的增大,开启力迅速增大.依据正交试验分析结果,对密封面结构参数进行了优化,在其他边界条件均不变的情况下,新的因素水平组合得到的泄漏率最低为0.784361 ml/h,此时开启力大小为3.958962 kN.

高压混相激光脸浅槽机械密封润滑状态转变特性及密封性能分析

以激光脸浅槽微接触式密封为研究对象,求解考虑混相介质特性和密封端面粗糙度效应的雷诺方程,通过分形接触理论求解微凸体接触力,利用不同微凸体接触状态下求解出的液膜承载系数对混相微接触式机械密封混合润滑状态进行分级,探究了压力及转速等工况条件和开槽形式对密封的润滑状态转变的影响规律.结果表明:混相微接触式机械密封混合润滑状态可分为弹性混合润滑状态、弹塑性混合润滑状态和塑性混合润滑状态3个级别;随着转速升高,液膜承载力不断增大,微凸体接触力逐渐趋向于0,密封环分开实现非接触,此时液膜承载系数为1;压差和槽深越大、混相介质气相容积比越高,矩形槽角度和周期数越小,临界转速越大,润滑状态更稳定,摩擦副分离越困难.

发电机轴承油槽密封结构对油雾泄漏的影响

大型水电站轴承油槽总是不可避免地发生油雾泄漏问题,改善密封结构通常是解决水电站轴承油槽甩油雾问题最简单有效的措施.为了降低油雾泄漏对发电机内部造成的污染,文中围绕某抽水蓄能电站发电机轴承油槽甩油雾问题,对油槽密封盖进行改型,并开展密封腔油雾多相流数值模拟研究.通过Mixture模型和SST k-ω模型解析了原密封结构和2种改进密封结构的流场分布特性,并评估了不同密封结构下的油雾泄漏情况.研究结果表明:相比于原设计模型,改进模型Ⅰ,Ⅱ的油雾泄漏量平均减少了18.9%,88.6%,改进模型Ⅱ抑制油雾效果最为显著;高压气体的注入会破坏密封腔原有的环形涡流,从而抑制油雾逸出;对于下部密封腔而言,提高进口压力,减小进口流速都有助于改善密封性能.文中的研究可为油槽密封改良以及轴承油雾泄漏控制措施提供一定的参考,提升电站的经济效益以及运行的安全稳定性.

型槽参数对斜直线槽液膜密封性能的影响

为进一步探索斜直线型槽对密封性能的影响机制,基于质量守恒边界并定义液膜密度比,建立斜直线槽液膜密封动压润滑模型;采用有限差分离散方程,对比分析液膜空化理论与实验值,验证计算模型与程序准确性;研究斜直线型槽参数包括槽数、槽深、径向和周向槽宽比对密封性能的影响。结果表明:不同倾斜角时,在临界范围内,增加槽数或增大槽深均有助于提升液膜承载力、增大泄漏量并有效降低液膜空化,尤其在较大倾斜角下;在一定范围内,虽均增大径向和周向槽宽比可提升液膜承载力、促进液膜空化发生及增大泄漏量,但影响规律不尽相同。以提升液膜承载力为目标,得出的最优型槽参数为槽数42、槽深25μm、径向和周向槽宽比分别为0.7和0.6。

空化效应对斜线槽机械密封性能的影响

润滑膜的空化效应对流体动压型机械密封的密封性能影响显著。以煤油基磁流体润滑斜线槽上游泵送机械密封为研究对象,考虑空化热效应以及黏温效应,建立润滑液膜特性的数值分析模型,以液膜中的气相体积分数为指标,研究工况和结构参数对密封性能的影响规律,并与仅考虑黏温效应的模型进行对比。结果表明:因空化热模型考虑液膜介质饱和蒸汽压力随温度变化,考虑空化热效应时的开启力、泄漏率和气相体积分数均小于仅考虑黏温效应下的对应值,但2种条件下各参数的变化趋势基本一致;转速和槽径比增大,空化效应增强,而进口压力、膜厚、径向夹角和槽数的增大会削弱空化效应;转速、槽深、径向夹角、槽径比增加,会导致泄漏率增加,而进口压力和槽数的增加能够提升密封性能。

基于结构变形理论的深海连接器O形圈密封性能研究

深海连接器是保证海洋装备能够正常运行的信号传输设备,而深海连接器的正常运行在很大程度上依赖于O形圈的密封性能。为此,对深海高压环境导致O形圈发生形变,从而严重影响O形圈的密封性能问题进行了研究。首先,基于结构变形理论,分析了环境压力对于密封结构变形和O形圈压缩量的影响变化;然后,基于有限元法建立了O形密封圈的非线性动密封模型,分析研究了模型网格划分对于模拟结果准确性的影响;接着,分析了结构变形与环境压力之间的关系曲线;最后,研究分析了材料性能、环境压力与密封结构尺寸对于动密封性能的影响。研究结果表明:当网格的实际值为47745,测定值为21685、37934、50707时,其模拟计算结果的误差值均小于2%;密封结构变形和O形圈压缩量的模拟值与理论值的曲线趋势基本一致;材料性能与环境压力的变化会影响动密封性能,在密封结构尺寸中,增大沟槽圆角半径可以增强O形圈的动密封性能。该研究结果可为深海高压环境下O形密封圈的设计与优化提供参考与理论支持。

电动机脂润滑密封深沟球轴承的密封性能

以电动机用脂润滑密封深沟球轴承为研究对象,基于滚动轴承动力学以及流体力学理论建立脂润滑密封深沟球轴承动力学微分方程组,求解多相流模型并分析了轴承结构参数对其密封性能的影响,试验结果表明:润滑脂泄漏速率随着外沟曲率半径增大先减小后增大,随着径向游隙增大而增大,随着保持架兜孔直径、引导间隙增大而减小;密封寿命随着外沟曲率半径、保持架兜孔直径、引导间隙增大而增大,随着径向游隙增大而减小;润滑脂填脂率对润滑脂泄漏速率影响显著,填脂率过大使泄漏加快,填脂率过小易导致球接触区域润滑不良,最佳填脂率为30%,此时密封寿命最长。

多相混输泵用超高压机械密封性能研究

针对超高压混输泵机械密封易磨损失效的问题,介绍了端面槽加工和涂层应用两种策略,用热流固耦合分析方法,分析了浅槽微接触式机械密封在实际应用中的温度分布和端面变形情况,阐述了表面涂层技术的应用,进行了一系列机械密封性能的试验研究。研究结果不仅证实了这些技术在提高机械密封寿命和可靠性方面的有效性,还证实了端面开槽和涂层技术在降低摩擦、改善耐磨性能方面的显著效果。为超高压混输泵机械密封系统的设计和优化提供了重要的理论依据及实践指导。

引流-泵送槽液体润滑端面密封性能研究

为进一步探究机械密封端面组合槽型对密封综合性能的影响规律,建立了基于质量守恒和能量守恒的引流-泵送槽液体端面润滑密封的准三维热流体动力润滑模型,并验证了其准确性,采用SUPG有限单元法对液膜压力、温度以及密封环端面温度进行迭代耦合求解,由此对密封端面状态与密封性能参数影响规律开展分析。通过端面场分析,揭示了引流槽“动力润滑散热”与泵送槽“空化泵送减漏”的作用机理。在p_(s)=1 MPa,n=3000 r/min,h_(0)=1.5μm工况条件下,增加引流槽周向长度,增大泵送径向位置比,调节引流径深比至0.52~0.60,泵送槽周向长度与径向宽度比至(13.5~14.5)/(1~2),引流槽深至4~6μm,泵送槽深至2~3μm,可有效提高密封端面的动压承载、润滑散热能力并减小端面泄漏量。研究结果可为该类密封的设计提供参考。

基于湍流模型的螺旋槽机械密封端面流动特性分析

为了研究高转速液膜润滑螺旋槽机械密封湍流流动特性,基于k-ω湍流模型,计算了密封端面液膜相对速度、压力与湍动能分布,并分析了不同转速与膜厚下密封开启力、泄漏率与端面各流动熵产损失占比。结果表明:槽区位置流体速度小,密封堰区流体速度大;液膜压力分布呈周期性,在螺旋槽背面前1/2流向位置处产生了空化;螺旋槽入口湍动能较大,在螺旋槽深度方向上,越靠近密封动环螺旋槽底壁面,流体湍动能越大;流体膜区域总熵产损失明显大于螺旋槽区域,总壁面熵产损失占比≥60%,总湍流流动损失占比≥30%;随着转速增加,开启力与泄漏率增大,壁面熵产损失增加,直接熵产损失降低,当转速≥10000 r/min时,湍流与脉动熵产损失相对稳定,占比35.64%~37.24%;随着膜厚增加,开启力降低,泄漏率增大,壁面熵产损失先增大后减小再增大,直接熵产损失降低,当膜厚≥4μm时,湍流与脉动熵产损失相对稳定,占比40.26%~42.15%。研究结果可为高转速低能耗机械密封结构设计提供理论指导。