Nonlinear sealing force of a seawater balance valve used in an 11000-meter manned submersible

doi:10.1007/s11465-022-0726-y

Front. Mech. Eng.

2023, Vol. 18

Issue (1) : 10 https://doi.org/10.1007/s11465-022-0726-y

RESEARCH ARTICLE

Nonlinear sealing force of a seawater balance valve used in an 11000-meter manned submersible

Zhenyao WANG, Yinshui LIU, Qian CHENG, Runzhou XU, Yunxiang MA, Defa WU(

)

School of Mechanical Science and Engineering, Huazhong University of Science and Technology, Wuhan 430074, China

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Abstract

Balance valve is a core component of the 11000-meter manned submersible “struggle,” and its sealing performance is crucial and challenging when the maximum pressure difference is 118 MPa. The increasing sealing force improves the sealing performance and increases the system’s energy consumption at the same time. A hybrid analytical–numerical–experimental (ANE) model is proposed to obtain the minimum sealing force, ensuring no leakage at the valve port and reducing energy consumption as much as possible. The effects of roundness error, environmental pressure, and materials on the minimum sealing force are considered in the ANE model. The basic form of minimum sealing force equations is established, and the remaining unknown coefficients of the equations are obtained by the finite element method (FEM). The accuracy of the equation is evaluated by comparing the independent FEM data to the equation data. Results of the comparison show good agreement, and the difference between the independent FEM data and equation data is within 3% when the environmental pressure is 0–118 MPa. Finally, the minimum sealing force equation is applied in a balance valve to be experimented using a deep-sea simulation device. The balance valve designed through the minimum sealing force equation is leak-free in the experiment. Thus, the minimum sealing force equation is suitable for the ultrahigh pressure balance valve and has guiding significance for evaluating the sealing performance of ultrahigh pressure balance valves.

Keywords seawater balance valve sealing performance hybrid ANE model FEM minimum sealing force equation

Corresponding Author(s): Defa WU

Just Accepted Date: 02 September 2022 Issue Date: 10 April 2023

Cite this article:

Zhenyao WANG,Yinshui LIU,Qian CHENG, et al. Nonlinear sealing force of a seawater balance valve used in an 11000-meter manned submersible[J]. Front. Mech. Eng., 2023, 18(1): 10.

URL:

https://academic.hep.com.cn/fme/EN/10.1007/s11465-022-0726-y
https://academic.hep.com.cn/fme/EN/Y2023/V18/I1/10

Fig.1 System schematic of seawater hydraulic variable ballast system.

Fig.2 Detailed structure of the balance valve and force analysis of the ball.

Fig.3 Sealing principle of the valve port under different sealing forces.

Fig.4 Contact state at the valve port under different sealing forces.

Fig.5 Contact zone and analysis zone of the valve port.

Fig.6 Contact stress and deformation of the ball and valve seat in the analysis zone.

Tab.1 Materials of the ball and valve seat

Fig.7 (a) Physical and (b) simulation models of the ball and the valve seat.

Tab.2 Property parameters of Si₃N₄ and 17-4PH

Fig.8 Meshing setting of the simulation model of the contact state between ball and valve seat.

Fig.9 Grid independence analysis of the simulation model.

Fig.10 Radial deformation under different ball diameters and sealing forces: (a) stainless steel–stainless (S?S) contact, (b) stainless steel–ceramic (S?C) contact, and (c) ceramic–ceramic (C?C) contact.

Fig.11 Comparison between the equation data and the independent FEM data with different half cone angles of the valve seat. FEM: finite element method.

Fig.12 Contact stress under different ball diameters and sealing forces: (a) stainless steel–stainless (S?S) contact, (b) stainless steel–ceramic (S?C) contact, and (c) ceramic–ceramic (C?C) contact.

Fig.13 Comparison between the equation data and the independent FEM data with different half cone angles of the valve seat. FEM: finite element method.

Fig.14 Process of calculating the minimum sealing force.

Tab.3 Parameters of the balance valve

Fig.15 Experimental schematic of the sealing performance.

Fig.16 Sealing experiment of the balance valve: (a) deep-sea simulation device, (b) experimental bench, and (c) seawater hydraulic variable ballast system and balance valve.

Abbreviations
ANE	Analytical–numerical–experimental
FEM	Finite element method
SHVBS	Seawater hydraulic variable ballast system
Variables
a	Half of contact width between the ball and the valve seat
C₁	A correction factor
C₂, C₃	Unknown coefficients used to account for the simplification of the model
d	Inlet diameter
d_b	Diameter of the ball
D	Push rod diameter
E	Young’s modulus of the ball or valve seat
E^*	Equivalent elastic modulus of the ball and valve seat
E₁, E₂	Elastic moduli of the ball and the valve seat, respectively
E_b, E_c	Elastic modulus of the bearing and the cylinder, respectively
E_r	Relative error
F	Sealing force between the ball and the valve seat
F_h	Hydraulic force caused by the area difference between the push rod and the inlet
F_h1, F_h2	Hydraulic forces generated by the push rod area and the inlet area, respectively
F_min	Minimum sealing force between the ball and the valve seat
F_s	Spring force
G	Shear modulus of the ball or valve seat
IT	Machining accuracy of the valve seat
K	Bulk modulus of the ball or valve seat
l	Length of the cylinder in the contact zone
p	Setting pressure inside the deep-sea simulation device
p_e	Environmental pressure
P	Normal load on the valve seat
Q	Rated flow of the balance valve
r	Contact circle between the ball and the valve seat
R	Radius of the ball
x	Position at the contact zone
δ	Radial deformation of the valve seat
Δ	Roundness error of the valve seat
ν₁, ν₂	Poisson’s ratios of the ball and the valve seat, respectively
ν_b, ν_c	Poisson’s ratios of the bearing and the cylinder, respectively
σ	Total contact stress between the ball and the valve seat
σ₁	Compensated contact stress generated by the spring force
σ₂	Net contact stress
σ_max	Maximum contact stress between the ball and the valve seat
σ_s	Tensile yield strength of the ball or valve seat
σ_sc	Compressive yield strength of the ball or valve seat
θ	Half cone angle of the valve seat
γ	Structural parameters of the bearing
ρ	Density of the ball or valve seat
ξ	Functional relationship between roundness error and spring force

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