Characteristics Analysis of Spherical Spiral Groove Bearings Considering Fluid Inertia

doi:10.12068/j.issn.1005-3026.2025.20240077

Abstract

Abstract:

Spherical spiral groove bearings （SSGBs） serve as an important bearing and vibration control structure of the rotor system in a flywheel energy storage device， and their stiffness and damping directly affect the vibration behavior of the rotor system， thus controlling the performance and efficiency of the flywheel energy storage device. To study the lubrication characteristics of the bearings， based on the Reynolds equation considering fluid inertia in the spherical coordinate system， the perturbation pressure equation was derived by using the perturbation method. Then， the partial differential equations were solved by using the finite volume and the finite difference methods to obtain the pressure distribution of the oil film. Furthermore， the pressure， load-carrying capacity， and dynamic characteristics of the oil film considering the fluid inertia and disregarding fluid inertia were analyzed by numerical calculations. The results show that when the rotational speed and eccentricity are larger， the fluid inertia has an obvious influence； the oil film pressure， load-carrying capacity， and damping considering fluid inertia are larger， and the stiffness is smaller.

Key words: spherical spiral groove bearing, fluid inertia, dynamic characteristic, oil film pressure, perturbation method

CLC Number:

V 231.9

Zhong LUO, Hao-tian HAO, Xuan-rui WU, Bao-bing LIANG. Characteristics Analysis of Spherical Spiral Groove Bearings Considering Fluid Inertia[J]. Journal of Northeastern University(Natural Science), 2025, 46(11): 90-97.

Figures/Tables 16

Fig.1 Schematic diagram of SSGB

Fig.2 Schematic diagram of rotor eccentricity

Fig.3 Schematic diagram of grid division

Fig.4 Flowchart of calculation

Table 1 Bearing parameters

参数	数值
轴承半径R/mm	10
初始油膜厚度h₀/μm	10
槽深h_g/μm	20
槽台宽度比γ	1
螺旋槽起始角θ_g/(°)	47
螺旋角β/(°)	70
动力粘度μ/(Pa∙s)	0.8
润滑油密度ρ/(kg∙m^-3)	910
大气压p_a/Pa	101×10³
槽数	5
轴承起始角θ_a/(°)	0.01
偏心率ε	0.2

Fig.5 Oil film pressure distribution at 200 r/min

Fig.6 Oil film pressure distribution at 8 000 r/min

Fig.7 The oil film thickness when ε=0.2

Fig.8 Relationship between oil film force and rotational speed

Fig.9 Relationship between oil film force and eccentricity

Fig.10 Direct stiffness of oil film at different

Fig.11 Direct damping of oil film at different speeds

Fig.12 Cross stiffness at different rotational speeds

Fig.13 Direct stiffness of oil film at different

Fig.14 Direct damping of oil film at different eccentricities

Fig.15 Cross stiffness of oil film at different eccentricities

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