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Research Papers: Applications

A Helical Gear Pair Pocketing Power Loss Model

[+] Author and Article Information
David Talbot

Department of Mechanical
and Aerospace Engineering,
The Ohio State University,
Columbus, OH 43210
e-mail: talbot.11@osu.edu

Ahmet Kahraman, Satya Seetharaman

Department of Mechanical
and Aerospace Engineering,
The Ohio State University,
Columbus, OH 43210

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received August 3, 2013; final manuscript received January 8, 2014; published online February 24, 2014. Assoc. Editor: Xiaolan Ai.

J. Tribol 136(2), 021105 (Feb 24, 2014) (11 pages) Paper No: TRIB-13-1154; doi: 10.1115/1.4026502 History: Received August 03, 2013; Revised January 08, 2014

A new fluid dynamics model is proposed to predict the power losses due to pocketing of air, oil, or an air-oil mixture in the helical gear meshes. The proposed computational procedure treats a helical gear pair as a combination of a number of narrow face width spur gear segments staggered according to the helix angle and forms a discrete fluid dynamics model of the medium being pocketed in the gear mesh. Continuity and conservation of momentum equations are applied to each coupled control volume filled with a compressible fluid mixture to predict fluid pressure and velocity distributions from which the instantaneous pocketing power loss is calculated. The proposed model is exercised in order to investigate the fluid pressure and velocity distributions in time along with the pocketing power loss as a function of the speed, helix angle, and oil-to-air ratio.

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Figures

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Fig. 1

Transverse pocket geometry at different mesh positions

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Fig. 2

(a) Discretization of the helical gear interface into narrow gear slices, and (b) a discretized instantaneous helical gear pocket across the face width

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Fig. 3

(a) A coarse discretization of a transverse slice of the mesh pocket, and (b) a single quadrilateral for area analysis

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Fig. 4

An example variation of (a) the end area, (b) the backlash-side area, and (c) the contact-side area of the control volume j of a pocket i with the mesh position ϑ for β = 0

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Fig. 5

Multi-degree-of-freedom fluid dynamics model governing the helical gear pocketing problem

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Fig. 6

(a) Pressure, (b) end velocity, (c) contact-side velocity, and (d) backlash-side velocity time histories for the example spur gear pair (β = 0 deg) at Ω = 3000 rpm and ξ = 0.05

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Fig. 7

Side views of the spur gear pair of Fig. 6 at representative mesh positions. The pocket i of interest is marked with ⊗.

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Fig. 8

Pressure and exit velocity time histories of the example spur gear pair at Ω = 4000 rpm for (a) ξ = 0.01 and (b) ξ = 0.05

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Fig. 9

End exit velocity time histories of gear pairs with helix angles of (a) β = 0 deg, (b) β = 5 deg, (c) β = 15 deg, and (d) β = 30 deg at Ω = 3000 rpm and ξ = 0.05

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Fig. 10

Pressure time histories of gear pairs with helix angles of (a) β = 0 deg, (b) β = 5 deg, (c) β = 15 deg, and (d) β = 30 deg at Ω = 3000 rpm and ξ = 0.05

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Fig. 11

End exit velocity distributions of gear pairs with helix angles of (a) β = 0 deg, (b) β = 5 deg, (c) β = 15 deg, and (d) β = 30 deg at Ω = 3000 rpm and ξ = 0.05

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Fig. 12

Variation of pocketing power loss with the (a) helix angle at ξ = 0.05, and (b) oil-to-air ratio at β = 30 deg

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