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Research Papers: Alternative Energy Sources

Effect of Capped Vents on Torque Distribution of a Semicircular-Bladed Savonius Wind Rotor

[+] Author and Article Information
Umang H. Rathod

Centre for Energy,
Indian Institute of Technology Guwahati,
Guwahati 781039, Assam, India
e-mail: umang174351003@iitg.ac.in

Parag K. Talukdar

Department of Mechanical Engineering,
Indian Institute of Technology Guwahati,
Guwahati 781039, Assam, India
e-mail: t.parag@iitg.ernet.in

Vinayak Kulkarni

Associate Professor
Department of Mechanical Engineering,
Indian Institute of Technology Guwahati,
Guwahati 781039, Assam, India
e-mail: vinayak@iitg.ernet.in

Ujjwal K. Saha

Professor
Department of Mechanical Engineering,
Indian Institute of Technology Guwahati,
Guwahati 781039, Assam, India
e-mail: saha@iitg.ernet.in

Contributed by the Advanced Energy Systems Division of ASME for publication in the Journal of Energy Resources Technology. Manuscript received February 20, 2019; final manuscript received May 11, 2019; published online May 29, 2019. Assoc. Editor: Dr. Ryo Amano.

J. Energy Resour. Technol 141(10), 101201 (May 29, 2019) (15 pages) Paper No: JERT-19-1095; doi: 10.1115/1.4043791 History: Received February 20, 2019; Accepted May 12, 2019

To address the problem of the imminent energy crisis, pollution from fossil fuels, and global warming, it is necessary to incorporate renewable technologies. In that context, the drag-based Savonius wind turbine has tremendous potential to extract wind energy and can be operated as a standalone system at remote areas where the conventional electricity cannot be provided. The present study primarily focuses on the performance evaluation of a conventional semicircular-bladed Savonius rotor with capped vents (CVs) or nozzle chamfered vents. The rotor blades having vent ratios of 7%, 14%, and 21% are tested in a wind tunnel, and subsequently, their performances are compared with a rotor without CVs under identical test conditions. Computational fluid dynamics (CFD) simulations have also been carried out to compliment the surprising experimental results and also to analyze the flow physics around the rotor blades. From the understanding of torque distribution, it has been noticed that the performance of the rotor with CV deteriorates compared with the conventional semicircular-bladed rotor. The vents are found to decrease the positive torque and increase the negative torque by disturbing the pressure distribution of the conventional semicircular-bladed Savonius rotor.

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Figures

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Fig. 1

A typical two-bladed Savonius rotor: (a) illustration of rotor parts and (b) geometric details

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Fig. 3

Roadmap of the present study

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Fig. 2

Types of vent augmented blades: (a) blades with capped vents and (b) blades with simple vents

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Fig. 9

Schematic of torque measurement systems: (a) dynamic torque measurement set-up and (b) static torque measurement set-up

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Fig. 8

Mounted turbine set-up

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Fig. 7

Schematic of wind tunnel facility

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Fig. 13

Grid independency test of the 2D domain for the conventinal blade at Re = 1.12 × 105

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Fig. 5

Design parameters of capped vents

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Fig. 4

Experimental local torque coefficient (CLT) distribution for λopt [28]

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Fig. 10

Error analysis for the conventional blade at Re = 1.12 × 105

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Fig. 11

Overall 2D computational domain and boundary conditions

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Fig. 12

Mesh pattern in the 2D domain: (a) mesh near the interface and (b) inflation layers on the blade surface

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Fig. 14

Variation of numerical CT with time for the conventional blade at Re = 1.12 × 105

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Fig. 16

Model validation with the experimental data for the conventional blade at Re = 1.12 × 105

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Fig. 17

Variation of numerical CT in one revolution at Re = 1.12 × 105

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Fig. 18

Polar distribution of numerical aerodynamic coefficients: (a) polar distribution of CD, (b) polar distribution of CL, and (c) polar distribution of CR

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Fig. 15

Experimental torque and power characteristics at different Reynolds numbers: (a) Re = 1.12 × 105, (b) Re = 0.92 × 105, (c) Re = 0.77 × 105, and (d) Re = 0.61 × 105

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Fig. 19

Simulated streamline patterns for the conventional blade at θ = 90 deg and Re = 1.12 × 105: (a) conventional blade, (b) 7% CV blade, (c) 14% CV blade, and (d) 21% CV blade

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Fig. 23

Experimental static torque coefficient (CST) distribution at Re = 1.12 × 105

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Fig. 24

Blockage corrected values of CP for the conventional blade at uncorrected Re = 1.12 × 105

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Fig. 20

Pressure coefficient distribution (CPr) on returning blade at θ = 9 deg: (a) present simulation data at Re = 1.12 × 105 and (b) reported experimental data [28]

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Fig. 21

Pressure coefficient distribution (CPr) on the advancing blade at θ = 90 deg: (a) present simulation data at Re = 1.12 × 105 and (b) reported experimental data [28]

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Fig. 22

Numerical local torque coefficient (CLT) distribution at Re = 1.12 × 105

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