Tribology & Mechanical Machine Elements
Research-Grade Journal Bearing Lubricator
Analyze lubrication oil film pressure distributions using a numerical 2D Finite Difference Reynolds Solver. Incorporates 3D shaft misalignment, THD temperature viscosity decay feedback, and Swift-Stieber boundary conditions.
Lubrication State
Hydrodynamic
16.95 μm film
Rotor Stiffness K_xx
807.2 N/μm
Dynamic fluid load
Friction Power Loss
1 W
Viscous heating drag
Parameters
Machine Presets
Lubricant Engine Oil
Speed sweep controls
Thermohydrodynamic Lubrication Governing Physics
2D Reynolds Hydrodynamics
d/dx( h^3 dP/dx ) + d/dz( h^3 dP/dz ) = 6 * mu * U * dh/dx
Swift-Stieber Cavitation
P = 0 and dP/d_theta = 0 at Film Rupture
THD Oil Viscous Heating
Q_heat = (mu * U^2) / h^2
Fluid Viscosity Decay
mu = mu_0 * exp( -beta * (T - T_0) )
the 2D steady-state oil film pressure distribution is resolved numerically using a 24x12 mesh Gauss-Seidel solver.
Thermohydrodynamic (THD) oil heating decreases local oil viscosity, reducing film load capacity.
Shaft angular misalignments skew the 3D clearance profile, triggering severe side-edge pressure hotspots.
Bearing Numerical Solver Visualization
Minimum Film Thickness
16.95μm
Stiffness Coefficient (K_yy)
1210.8N/μm
Power Dissipation
0.6W
Peak Oil Hotspot Temp
45.1°C
Dynamic Film Thickness & Power Loss vs Spindle Speed
Spindle Speed Sweep Telemetry
| Spindle Speed (RPM) | Sommerfeld Number (S) | Min Film Thickness (μm) | Power Dissipated (W) |
|---|---|---|---|
| 500 RPM | 0.0259 | 29.10 μm | 6 W |
| 1500 RPM | 0.0776 | 21.91 μm | 15 W |
| 2500 RPM | 0.1294 | 18.24 μm | 21 W |
| 3500 RPM | 0.1811 | 15.88 μm | 27 W |
| 4500 RPM | 0.2329 | 14.18 μm | 34 W |
| 5500 RPM | 0.2846 | 12.89 μm | 42 W |
| 6500 RPM | 0.3364 | 11.86 μm | 51 W |
| 7500 RPM | 0.3881 | 11.02 μm | 60 W |
| 8500 RPM | 0.4399 | 10.31 μm | 71 W |