1 Introduction
2 Method
2.1 Simulation overview
2.2 Reduction of simulation effort
2.3 Critical operation conditions
3 Model description
Wind turbine (MBS model) | ||
Rated power output | \(P\) | \(850\,\textit{kW}\) |
Operational wind speed | \(v_{\mathrm{wind}}\) | \(4-25\,\frac{m}{s}\) |
Rated wind speed | \(v_{\mathrm{Wind}{,}\mathrm{nom}}\) | \(14\,\frac{m}{s}\) |
Number of planets | \(n_{P}\) | \(3\) |
Transmission ratio main shaft to first planetary stage | \(i_{PL}\) | 2.47 |
Planetary journal bearing (EHD model) | ||
Diameter | \(D\) | \(165\,\textit{mm}\) |
Relative bearing clearance | \(\psi\) | \(1.1\,\textit{permil}\) |
B/D-ratio | \(B/D\) | \(1.15\) |
Specific bearing load | \(\overline{p}\) | \(11.7\,\textit{MPa}\) |
Maximum edge recession of bearing profile (Fig. 3) | \(\Updelta D\) | 70 μm (50 μm)a |
Surface roughness of the planet | \(R_{pk{,}P}\) | \(0.5\mu m\) |
Surface roughness of the journal | \(R_{pk{,}J}\) | \(0.5\mu m\) |
Young’s modulus of journal bearing material | \(E_{J}\) | \(100\,\textit{MPa}\) |
Lubricant properties (EHD model) | ||
Lubricant | – | ISO VG 320 |
Lube operating temperature | \(T_{l}\) | \(60{^{\circ}}C\) |
Lubricant kinematic viscosity \((@40{^{\circ}}C)\) | \(\nu _{l}\) | \(320\,\textit{mm}^{2}/s\) |
Lubricant density \((@40{^{\circ}}C)\) | \(\rho _{l}\) | \(860\,\textit{kg}/m^{3}\) |
4 EHD results
Main shaft speed [1/min] | Main shaft torque [kNm] | |
---|---|---|
Operating point 1 | 5.0 | 20.0 |
Operating point 2 | 22.0 | 400.0 |