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Tapered Roller Bearing on Conical Raceway: Combined Radial & Axial Contact Benchmark
100Cr6 bearing steel conical outer raceway cup (15°) and precision tapered roller (3° semi-cone angle) under 24 kN compressive preload.
Verify the contact pressure distribution and elastic approach between a precision tapered roller and conical raceway under combined preloading, evaluating subsurface shear stress against Lundberg-Palmgren bearing fatigue life theory.
1. Geometry & FEA Mesh
- •2 disconnected B-Rep solid bodies: conical outer cup raceway block (body1) and precision tapered roller (body2)
- •Material: 100Cr6 / AISI 52100 high-carbon bearing steel (E = 210 GPa, ν = 0.30, density 7830 kg/m³)
- •Mesh: 2nd-order quadratic tetrahedral mesh (TET10) with 7,828 nodes and 4,594 elements (23,484 DOFs)
- •Frictionless Mortar contact formulation along conforming contact saddle (width 2b0 = 3 mm, length 24 mm)
2. Loads & Boundary Conditions
- •Raceway base planar face at Z = -20 mm fixed in all 6 DOFs (Ux = Uy = Uz = 0)
- •Roller crown pad loaded with compressive preload Fz = -24.0 kN
- •Roller side guide flats and end faces constrained against lateral and longitudinal tilt (Ux = Uy = 0)
3. Simulation Results & Findings
- ✓Elastic roller approach and deflection |u| = 0.0251 mm (25.1 microns) along the normal compression axis
- ✓Peak contact pressure p_c = 333.0 MPa along the roller contact generatrix, in close agreement with Hertzian analytical theory
- ✓Von Mises stress σ_vm = 726.6 MPa located subsurface beneath the raceway contact band
Provides bearing manufacturers and drivetrain engineers with validated Hertzian contact simulations to optimize roller crowning, reduce edge stress concentrations, and maximize bearing fatigue life.
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