Research Papers

Dynamic Response Analysis of Wind Turbine Gearbox Using Simplified Local Tooth Stiffness of Internal Gear System

[+] Author and Article Information
J. R. Cho

School of Mechanical Engineering,
Pusan National University,
Busan 609-735, Korea
Research and Development Institute of Midas IT,
Gyeonggi 463-400, Korea
e-mail: jrcho@pusan.ac.kr

K. Y. Jeong, M. H. Park, N. G. Park

School of Mechanical Engineering,
Pusan National University,
Busan 609-735, Korea

1Corresponding author.

Contributed by the Design Engineering Division of ASME for publication in the Journal of Computational and Nonlinear Dynamics. Manuscript received February 20, 2013; final manuscript received February 21, 2014; published online April 2, 2015. Assoc. Editor: Carlo L. Bottasso.

J. Comput. Nonlinear Dynam 10(4), 041001 (Jul 01, 2015) (9 pages) Paper No: CND-13-1046; doi: 10.1115/1.4026934 History: Received February 20, 2013; Revised February 21, 2014; Online April 02, 2015

This paper presents a dynamic finite element analysis model for a wind turbine gearbox in which a number of internal gears mesh with each other in a complex pattern. Differing from the conventional dynamic models in which the detailed gear teeth are fully modeled or gears and shafts are replaced with lumped masses, the tooth contact between a pair of gears is modeled using a spring element. The equivalent spring constant is determined by computing the stiffness of a gear tooth using a finite element analysis. The numerical accuracy of the proposed dynamic model is verified through a benchmark experiment of a gearbox with simple gear transmission system. In addition, the natural frequencies and dynamic responses of a 5 MW wind turbine gearbox that are obtained by the proposed modeling technique are given to support its validity and effectiveness.

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Fig. 1

Horizontal-axis wind turbine: (a) configuration; (b) detailed components (AGMA, 2003)

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Fig. 2

Wind-induced dynamic forces and moments acting on the wind turbine

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Fig. 3

A simple dynamic model by utilizing the mass lumping technique

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Fig. 4

A dynamic model considering the gear tooth contact

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Fig. 5

Finite element model for evaluating the tooth stiffness coefficient

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Fig. 6

A simple gear transmission system composed of three gear shafts (unit: mm)

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Fig. 7

First mode shapes of three different models: (a) full model (27.111 Hz); (b) simple model (28.625 Hz); (c) present model (27.258 Hz)

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Fig. 8

Second mode shapes of three different models: (a) full model (50.586 Hz); (b) simple model (44.855 Hz); (c) present model (50.301 Hz)

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Fig. 9

Comparison of the dynamic responses at point A: (a) time responses; (b) frequency responses

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Fig. 10

A three-stage 5 MW wind turbine gearbox: (a) internal gear system; (b) FEM model

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Fig. 11

Mode shapes: (a) first mode (18.256 Hz, vertical vibration); (b) second mode (33.251 Hz, torsional vibration); (c) third mode (47.321 Hz, horizontal vibration)

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Fig. 12

Dynamic responses at torque arms: (a) time responses; (b) frequency responses

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Fig. 13

Dynamic responses at gearbox case: (a) time responses; (b) frequency responses

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Fig. 14

Internal gear transmission and four evaluation points

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Fig. 15

Time responses: (a) at A; (b) at B; (c) at C; (d) at D

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Fig. 16

Frequency responses at four different points




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