Technical Brief

Dynamic Analysis of a Geared Infinitely Variable Transmission

[+] Author and Article Information
X. F. Wang, Z. R. Li, W. D. Zhu

Department of Mechanical Engineering,
University of Maryland,
Baltimore County,
1000 Hilltop Circle,
Baltimore, MD 21250

1Corresponding author.

Contributed by the Design Engineering Division of ASME for publication in the JOURNAL OF COMPUTATIONAL AND NONLINEAR DYNAMICS. Manuscript received December 1, 2015; final manuscript received June 1, 2016; published online December 5, 2016. Assoc. Editor: Dan Negrut.

J. Comput. Nonlinear Dynam 12(3), 034502 (Dec 05, 2016) (12 pages) Paper No: CND-15-1406; doi: 10.1115/1.4033896 History: Received December 01, 2015; Revised June 01, 2016

Dynamic analysis of a geared infinitely variable transmission (IVT) that can generate a continuous output-to-input speed ratio from zero to a certain value is studied for vehicle and wind turbine applications. With the IVT considered as a multirigid-body system, the Lagrangian approach is used to analyze its speeds and accelerations, and the Newtonian approach is used to conduct force analysis of each part of the IVT. Instantaneous input and output speeds and accelerations of the IVT have variations in one rotation of its input shaft. This work shows that the instantaneous input speed has less variation than the instantaneous output speed when the inertia on the input side is larger than that on the output side and vice versa. The maximum torque on the output shaft that is a critical part of the IVT increases with the input speed.

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Fig. 4

Simplified model of a driver in a new coordinate system

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Fig. 5

Kinematic relation between the crank gear and sun gear

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Fig. 3

Schematic of the kinematic model of a driver

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Fig. 2

Kinematic relation of a driver

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Fig. 6

Velocity relation of a planetary gear system

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Fig. 7

Velocity relations of the input shaft, the planetary gear, and the carrier

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Fig. 10

Force analysis of the driver

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Fig. 12

Layout of the crank gears and transmission gears

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Fig. 13

Force analysis of the transmission gear 5 and crank gear 5

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Fig. 15

Force analysis of the transmission gear 3 and crank gear 3

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Fig. 8

Relation between θ1 and φ1

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Fig. 18

Force analysis of a sun gear

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Fig. 19

Force analysis of a planetary gear

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Fig. 20

Force analysis of the planetary shaft

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Fig. 11

Force analysis of the joint

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Fig. 22

Output-to-input speed ratio of the four-driver system

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Fig. 14

Force analysis of the transmission gear 4 and crank gear 4

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Fig. 16

Force analysis of the transmission gear 2, the crank gear 2, and the sun gear 2

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Fig. 9

Force analysis of the output gear

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Fig. 17

Force analysis of the transmission gear 1, the crank gear 1, and the sun gear 1

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Fig. 21

Force analysis of a carrier

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Fig. 23

Dynamic input and output speeds for the vehicle application

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Fig. 24

Dynamic input and output speeds for the wind turbine application

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Fig. 25

Relation between the input speed and maximum torque on the output shaft



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