Numerical Simulation of a New Designed Mechanical Seals with Spiral Groove Structures

He, Tao; Zhang, Qiangqiang; Yan, Ying; Dong, Jintong; Zhou, Ping

doi:10.3390/lubricants11020070

Cited by 4 publications

(4 citation statements)

References 22 publications

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“…Combined with the engineering field and the research results of this paper, it is suggested to optimize the mechanical seal, which can be carried out from the following three aspects: As shown in the position marked as 1 in Figure 19, installing a spring compensation mechanism at the primary ring can slightly reduce the requirements of the mechanical seal on the matching accuracy. As shown in the position marked as 2 in Figure 19, a small casing part is used to locate the primary ring axially, and the flow channel area above the shaft sleeve is expanded. When a leak occurs, the leakage fluid can be smoothly discharged from the preset sewage outlet, 30 which is convenient for field personnel to observe and prevent more serious accidents. As shown in the position marked as 3 in Figure 19, replace this part with a fiber sealing material and press it to the left of the machine seal end cover with a spring. When a leak occurs, the leakage fluid can theoretically be guaranteed to flow out from the preset sewage outlet. …”

Section: Resultsmentioning

confidence: 99%

“…As shown in the position marked as 2 in Figure 19, a small casing part is used to locate the primary ring axially, and the flow channel area above the shaft sleeve is expanded. When a leak occurs, the leakage fluid can be smoothly discharged from the preset sewage outlet, 30 which is convenient for field personnel to observe and prevent more serious accidents. 3.…”

Section: Wear Mechanism Of Seal Ring End Facementioning

confidence: 99%

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Wear mechanism and leakage failure analysis of the mechanical seal end face of an oil transfer pump

Qiao,

Mo,

Mao

et al. 2023

Proceedings of the Institution of Mechanical Engineers, Part J:

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The John Crane 48 V mechanical seal is a long-distance oil transfer pump station shaft end seal; its sealing effect directly affects pipeline production safety. However, it has been found that there is oil leakage at the shaft end of the pump station. In order to explore the oil transfer pump mechanical seal abnormal leakage failure causes, to ensure the safety and stability of production, the end face of the 48 V mechanical seal was analyzed by white light interference and scanning electron microscope technology. The failure mechanism of the 48 V mechanical seal was explored from the perspective of the wear mechanism of moving and stationary rings. Results showed that the wear mechanism of the 48 V mechanical seal stationary ring was mainly abrasive wear, and substantial furrows, bulges, and depressions existed on the wear surface. The material removal mechanism was brittle spalling, and the roughness of the wear surface increased with the increase in wear depth and decreased with the increase in wear average width. Uneven wear occurred on the end face of the stationary ring of the mechanical seal, resulting in the leakage of the sealing medium from the end cover of the mechanical seal. The working condition could be improved by adding a spring compensation device to the stationary ring or increasing the gap between the stationary ring and the shaft sleeve.

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Section: Resultsmentioning

confidence: 99%

Section: Wear Mechanism Of Seal Ring End Facementioning

confidence: 99%

Wear mechanism and leakage failure analysis of the mechanical seal end face of an oil transfer pump

Qiao,

Mo,

Mao

et al. 2023

Proceedings of the Institution of Mechanical Engineers, Part J:

View full text Add to dashboard Cite

show abstract

“…By making use of the equality between the real and imaginary parts of the complex numbers, the steady-state fluid film pressure p 0 of the seal and the dynamic perturbation fluid film pressure p r and p i can be obtained. The specific derivation process is to substitute Equations ( 5)- (7) into Equation (3), ignoring the higher order terms, and obtaining the liquid-gas two-phase dynamic Reynolds equation, as shown in Equation (10):…”

Section: Control Equation Of Liquid-gas Two-phase Membranementioning

confidence: 99%

“…Xu [9] analyzed the influence of parameters such as the angle and height of the spiral groove on the liquid film pressure and deduced through simulation that the stability of hydrodynamic liquid film seals can be significantly improved by selecting an appropriate shaft angular velocity and height of the spiral groove. He [10] designed a new spiral groove structure that effectively improves the hydrodynamic performance of the liquid seal, resulting in a significant increase in dynamic stability. Wang [11] and Zhu [12] changed the influence of the cavitation excitation on the stability by changing the parameters of the seal end face.…”

Section: Introductionmentioning

confidence: 99%

Stability Analysis of Hydrodynamic Mechanical Seals in Multifrequency Excitation

Sun

Liu

et al. 2023

Coatings

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The dynamic characteristics of the complex relationship among the sealing system, excitation, and response have a considerable impact on the operational reliability of hydrodynamic mechanical seals, which is a critical issue in the field of sealing theory and technology. Scholars at home and abroad have established dynamic models and calculated the displacement responses of dynamic and static rings in the time domain based on the force on these rings so that the response results can be used for system stability analysis. Neither are the excitation characteristics of cavitation load extracted, nor are the distance response and system leakage rate of the dynamic and static rings analyzed under coupled cavitation and random excitation. In this study, under different operating conditions of the hydrodynamic mechanical seal system, the liquid film evaporation load and seismic load are applied to study the frequency domain response of the distance between the dynamic and static rings and the system leakage rate. The following conclusions have been obtained: Assuming that the chamber pressure is 0.5 MPa and the spring specific pressure is 0.055 MPa, during stable operation, the distance between the moving and stationary rings at 1500 rpm~3000 rpm speeds is 1.12 μm~3.05 μm. For a specific spring pressure of 0.055 MPa, medium pressures of 0.2 MPa~1.0 MPa, and spindle speeds of 1500 rpm~3000 rpm, the excitation force is 30 N, and the frequency is 30 Hz, And the seismic load is assumed to be sinusoidal, the excitation force is 6 N, the fundamental frequency is 120 Hz, and the system leak rate is in 0.1 mL/min~1.3 mL/min. Under multi-frequency excitation coupling, the distance between the dynamic and static rings will decrease as the pressure of the medium in the sealing cavity increases, and this will increase with the increase in the rotating speed. The leakage rate of the system will increase with the increase in the rotating speed and the pressure of the medium, and the test value is largely consistent with the theoretical value.

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Theoretical study on the pressure expansion mechanism of diffused self-pumping hydrodynamic mechanical seal

Zheng,

Sun,

et al. 2023

Physics of Fluids

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The pressure expansion performance is the key and basis for the diffused self-pumping hydrodynamic mechanical seal to achieve its good cooling performance, self-cleaning performance, and sealing performance. Using the moment of momentum theorem and Stodola's formula, the pressurization effect of the spiral groove on the fluid was analyzed, and the energy head equation of the work done by the spiral groove on the fluid is established. According to the principle of conservation of energy, the energy equation and Bernoulli equation of the work done by the spiral groove on the fluid are derived, the mathematical expression of the conversion of fluid kinetic energy into hydrostatic pressure in the diffuser groove was established, the energy change and energy distribution problems of the fluid after the work of the spiral groove are clarified, and the pressure expansion mechanism is revealed. Through numerical simulation, the relationship between the fluid pressure at the sealing interface, the position and size of the high-pressure field, the opening force, and the leakage rate under different rotational speeds and the structural parameters of the diffuser groove were explored. Finally, the pressure expansion performance of the ordinary self-pumping hydrodynamic mechanical seal and diffused self-pumping hydrodynamic mechanical seal is compared. The results show that the diffuser groove can effectively convert part of the fluid kinetic energy into pressure energy, improve the opening force of the sealing interface, and have a good pressurization effect on the sealing end face. With the widening of the diffuser groove, the pressure peak of the sealing interface increases, the high-pressure field area continues to expand and tends to expand toward the outer diameter of the seal ring, and the opening force also increases significantly; increasing the depth of the diffuser groove will cause the pressure peak of the sealing interface to become smaller, and the area of the high-pressure field will also decrease rapidly, which is not conducive to improving the opening force of the sealing end face.

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Numerical Simulation of a New Designed Mechanical Seals with Spiral Groove Structures

Cited by 4 publications

References 22 publications

Wear mechanism and leakage failure analysis of the mechanical seal end face of an oil transfer pump

Wear mechanism and leakage failure analysis of the mechanical seal end face of an oil transfer pump

Stability Analysis of Hydrodynamic Mechanical Seals in Multifrequency Excitation

Theoretical study on the pressure expansion mechanism of diffused self-pumping hydrodynamic mechanical seal

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