Research On The Dynamic Modeling Method Of The Horizontal Axis Wind Turbine's Driving Chain

Transmission as an important component of the wind turbine, the design's success orfailure is directly related to the overall performance of the wind turbine. For the earlyrealization of the localization of wind turbine drive system technology, the domesticis specialized in organizing power transmission design, manufacture, and all aspectsof the research study. Analysis of the dynamic characteristics of wind drive system isan important part of the study. Therefore, in-depth study of theory and methods ofdynamic analysis of the transmission system, the establishment of a system's overallaccurate dynamic model, in order to better grasp the dynamic characteristics of thetransmission system, improve the overall performance of the transmission system.In this paper, two driving chains`dynamics of the doubly-fed variable speedconstant frequency wind turbines is as the research object. Build and analyse twodynamic models. The content and research conclusions of this article are as follows:First, analyzed the structure of the wind turbine drive systems, compared theadvantages and disadvantages of several transmission chains. Focus on analysis of thechange of excitation of the doubly-fed VSCF wind turbine that is three-pointsuspension or four-point suspension drive system, considering a different numberbearing and distribution of the entire transmission system of. It can be seen from theresults that the three-point suspension type static has no large centralized power, butthe load has a greater impact on the gear box planetary bodies; the four-pointsuspension type static has large centralized power, but the load has a greater impacton the first two bearing.Introduce the principle of Lagrange equation. With the Lagrange energy method, Iderived the differential equation of the beam element and established the dynamicmodel after parameterized the shafting, simplified into a finite element scheme.Deduced the relative displacement relationship between the wind turbine gearboxplanet carrier component, and finally the differential algebraic equations derive forthe pure differential equations, and to facilitate the kinetic equations. I derived thedifferential algebraic equations become pure differential equations, and thencontribute to the dynamic equations. To establish the kinetic equation of the planetary transmission using theNewton's second law. Deduced the direct displacement relationship of the variousgears of the planetary transmission system and established the relationship of thegeneralized coordinates and local coordinates. Provide a theoretical basis for theLagrangian energy dynamics model and dynamic model of Newton's second law.Considering the lateral vibration and torsional vibration of the system, according toNewton's second law to establish the kinetic equation of the planetary transmission,obtained and analyzed the frequency of the system and the corresponding vibrationmodes.Using the Lagrange equation, elastic kinetic analysis, multi-body dynamicstheory, the lumped parameter method and finite element, established the kineticequation.First proposed element method to derive the relation of the local coordinates,provide a theoretical basis for deriving three suspension and four-point suspensiontransmission system of local coordinates for the generalized coordinates.During themodeling process, I first considered the impact of the bearing deformation, theposition, the number, the changing bearing position on the inherent characteristics ofthe entire transmission system.Used the finite element method to analyze and compare the deformation of thetwo transmission spindle structure and the top ten order modal, after analyzing thedynamics of the entire transmission chain using Lagrange principle. I imposedconstraint and load on the aligning bearing, using the mass21unit. Analyzed andcompared the dynamic characteristics of the entire transmission system. It can be seenfrom the analysis of results and the inherent characteristics of Chapter IV, force anddeformation of the three-point bearing spindle are greater than the four-pointsupport`s. The requirements of Gear box planetary gear bearing must be higher. Themodal deformation of the four-point bearing spindle is larger than the three-pointbearing spindle`s.