Torque Transmission Law of Wind Turbine Drive System under the Excitation of Uneven Wind Load

Abstract

A random wind speed time history model based on Weibull distribution is constructed. According to the known mean and variance of wind speed, the time fitting curve of random wind speed is obtained through MATLAB simulation method. According to the wind speed range of the actual operation of the wind turbine, the obtained wind speed curve is transformed, and then according to the obtained relationship between the wind speed of the wind turbine and the input torque, the input time-varying torque of the actual operation of the wind turbine is obtained. Establish the rigid shaft model of the wind turbine gearbox, calculate the gearbox transmission ratios at all levels, and then obtain the torque output curves of the gearbox planetary stage, medium-speed stage, and high-speed stage under random wind speed input to study wind power the torque transmission law of the machine drive system. The ability to better analyse the transmission structure of the gearbox and the torque transmission law of key components has a certain significance for the design and manufacture of the wind turbine transmission chain.

Wind turbine gear reliability analysis considering dependent competing failure

“…The torque on the sun gear is obtained according to the connection between the input torque and the random wind speed. 37 According to the torque of the sun gear, the tangential loads 𝐹 𝑡 can be easily obtained to calculate the contact stress 𝜎 H , which can be formulated as 20,38…”

“…Then the contact stress of the gears needs to be obtained. The torque on the sun gear is obtained according to the connection between the input torque and the random wind speed 37 . According to the torque of the sun gear, the tangential loads $${F}_t$$ can be easily obtained to calculate the contact stress σ H , which can be formulated as 20,38 $$$$\begin{equation}{\sigma }_{\mathrm{H}} = {Z}_{\mathrm{E}}{Z}_{\mathrm{H}}{Z}_{\mathrm{\varepsilon }}{Z}_{{\beta}}\sqrt {\frac{{{K}_{\mathrm{A}}{K}_{\mathrm{V}}{K}_{{\mathrm{H\beta }}}{K}_{{\mathrm{H\alpha }}}{F}_t}}{{{d}_{\mathrm{1}}a}} \cdot \frac{{\left( {q \pm 1} \right)}}{q}} \end{equation}$$$$where Z E is the elastic coefficient; Z H is the node area coefficient; $${Z}_{\mathrm{\varepsilon }}$$ is the coincidence coefficient; $${Z}_{{\beta}}$$ is the helix angle coefficient; K A is the service coefficient; K V is the dynamic load coefficient; $${K}_{{\mathrm{H\beta }}}$$ is the tooth load distribution coefficient; $${K}_{{\mathrm{H\alpha }}}$$ is the tooth load distribution coefficient; $${F}_t$$ is the circumferential force on the pitch circle of the end face; d 1 is the pitch circle diameter of the pinion; a is the smaller tooth width in the meshing gears; q is the gear ratio.…”

Residual Strength Modeling and Reliability Analysis of Wind Turbine Gear under Different Random Loadings

“…The estimated calculation results of the wind speed mean, variance, and distribution parameters are shown in Table 4. The torque of the gear can be obtained from the random wind speed [44]. According to the torque of the gear, the tangential load can be easily obtained.…”