Research Papers: Alternative Energy Sources

A Novel Geometry for Vertical Axis Wind Turbines Based on the Savonius Concept

[+] Author and Article Information
Michele Mari, Mauro Venturini

Dipartimento di Ingegneria,
Università degli Studi di Ferrara,
Via Giuseppe Saragat, 1,
Ferrara 44122, Italy

Asfaw Beyene

Department of Mechanical Engineering,
San Diego State University,
5500 Campanile Drive,
San Diego, CA 92182-5102

Contributed by the Advanced Energy Systems Division of ASME for publication in the JOURNAL OF ENERGY RESOURCES TECHNOLOGY. Manuscript received May 13, 2017; final manuscript received May 17, 2017; published online July 18, 2017. Editor: Hameed Metghalchi.

J. Energy Resour. Technol 139(6), 061202 (Jul 18, 2017) (9 pages) Paper No: JERT-17-1221; doi: 10.1115/1.4036964 History: Received May 13, 2017; Revised May 17, 2017

In this study, we present the results of a two-dimensional fluid-dynamic simulation of novel rotor geometry with spline function which is derivative of the traditional S-shape Savonius blade. A computational fluid dynamic (CFD) analysis is conducted using the Spalart–Allmaras turbulent model, validated using experimental data released by Sandia National Laboratory. Results are presented in terms of dimensionless torque and power coefficients, assuming a wind speed of 7 m/s and height and rotor diameter of 1 m. Furthermore, analysis of the forces acting on the rotor is conducted by evaluating frontal and side forces on each blade, and the resultant force acting on the central shaft. A qualitative representation of the vorticity around the traditional and spline rotor is shown to prove that the novel blade allows less turbulent flow through the rotor.

Copyright © 2017 by ASME
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Fig. 1

Geometry and boundaries of the 2D model

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Fig. 2

Grid independence analysis—instant CT values versus rotor azimuth position (TSR = 1)

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Fig. 3

Mesh quality rating

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Fig. 4

CFD model compared to Sandia National Laboratory data

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Fig. 5

Relative deviation of CFD model prediction from experimental data

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Fig. 6

Spline20, β = 20 deg; spline30, β = 30 deg; and spline40, β = 40 deg

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Fig. 7

Torque coefficient CT

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Fig. 8

Power coefficient CP

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Fig. 9

Relative performance improvement of spline-curved blades versus circular-shaped rotor

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Fig. 10

Torque coefficient for circular and spline40 geometry as a function of rotor azimuth position (TSR = 1.0)

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Fig. 11

Circular rotor; azimuth position: 0 deg; and TSR = 1.0

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Fig. 12

Spline40 rotor; azimuth position: 0 deg; and TSR = 1.0

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Fig. 13

Vorticity contour of circular (top) and spline40 (bottom) rotor; azimuth position: 0 deg; and TSR = 1.0

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Fig. 14

Side (CFx), frontal (CFy), and resultant (CR) force coefficients of circular and spline40 rotor versus TSR

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Fig. 15

Forces acting on rotor blades

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Fig. 16

Semilog plot of the ratio of frontal forces at TSR 1.2

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Fig. 17

Semilog plot of the ratio of side forces at TSR 1.2




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