Performance Analysis of savonius hydro turbine using CFD simulation

International Research Journal of Engineering and Technology (IRJET) e-ISSN: 2395-0056
Volume: 10 Issue: 03 | Mar 2023 www.irjet.net p-ISSN: 2395-0072
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Performance Analysis of savonius hydro turbine using CFD simulation
Niteen Choudhary1, Purushottam Sahu2, Ghanshyam Dhanera3
1Reseach scholar, BM College of Technology, Indore
2Professor and HEAD BM College of Technology, Indore
3 Professors, BM College of Technology, Indore
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Abstract - The primary goal of this study is to experimentally analyse the turbine's maximumefficiency. Thegoalofthisresearchisto
analyse the performance of a Savonius turbine utilised as a hydro turbine using computational fluid dynamics (CFD) simulations and
experimental data. This project is primarily based on the renewable energy system.
Key Words: Fluid dynamics, hydro turbine, modelling, performance, and simulation, along with computational fluid dynamics
1. INTRODUCTION
The current era is the era of energy. Energy can be produced by the wind, tides, sun, geothermal heat, biomass, includingfarmand
animal waste, as well as human excrement, which is known as unconventional energy. All of these resources are renewable or
limitless and don't harm the environment. Additionally,theydon'tdemandheavyuse. Currently,theworldusesupto20,000billion
Kwh of energy, of which 70% is generated by conventional sources and the remaining 30% by sources such as hydropower,
geothermal, biomass, solar, wind, and atomic energy. About 16% of this 30% is created through the kinetic energy of falling or
streaming water, which is then converted into power.
2. Lift Force Performance Model 3.1
Let's assume that (L) is the lifting force, which acts in the direction of the fluid flow's normal. This is explicableusing thegoverning
equation.
L=1/2 C_(L) ρAV^2……………………………………… (4.1) Where A is the area of the blade air foil, is the lift coefficient, and is thedensity
of water. Pull Force Drag force is the name for the force that operates in the directionof flow.Drepresentsthedragforce.Thisforce
is mostly caused by the fluid's viscosity.Thiscanbestated usingtheformula D=1/2AC_d(U-V).^2………………………………(4.2)where
speed is V, drag force is D, fluid velocity is U, and drag coefficient is Cd.
Where speed is V, the fluid's velocity is U, the drag force is D, and the drag coefficient is Cd.
Typically, the lift and drag coefficient values are estimated provisionallyandcomparedtotheReynoldsnumber.In Fig.3.2, a region
of a sharp edge at span I is indicated, together with the associated speeds, powers, and edges. The edge of the relative liquid speed
to the plane of revolution is denoted by, and the relative liquid vector at span r is denoted by Vrel. L and D, which are guided
opposite and parallel to the related liquid as appeared, speak to the resulting lift and drag powers.
Fig 3.1 Forces Act on Blade [26]

Fig 3.2 Forces on the Blade [5]
For the highest level of skill, careful consideration of the rotor edges' geometry and shape change is essential. Despite the factthat
fresh airfoils are rarely made for use on rotors, turbines have frequently used airfoilsthatareinspiredbyaeroplanewings.Airfoils
use the concept of lift rather than drag to harness the power of the air. Cutting edges that use lift (powers against the direction of
the stream) are more efficient than drag machines. In general, using lift has resulted in some bent and altered shapes.
3. ANALOGOUS SIMULATION- I
The geometry for the two-bladed Savonius turbine used in this project was developed in Solid Works andimported intotheANSYS
15 workbench, where additional operations including meshing and simulations were carried out.
Modelling and Grid Size
Table 3.1 Geometry Parameters
Parameters Dimensions in mm
Diameter of blade (D) 50
Main domain 110
Aspect ratio (e) 5
The two basic components of the computational domain are the core domain and the outer domain. Two rotors with the right
dimensions and an appropriate aspect ratio make up the main domain. Here, the motionless outer domain contrasts with the
spinning primary domain. The computational domain's geometry is depicted in the following fig.

Fig 5.1Computational Domain Along With Boundary Conditions[25]
3.2 NUMERICAL SIMULATION- II
The range of the aspect ratio has been picked from 5 to 25, and a number of geometries have been optimised for this numerical
simulation. After creating all of the geometry in Solid Works, it is imported into ANSYS 15 for additional numerical simulation.
The geometry of the same size with the same rotor diameter but different blade positions and produce a workablesolution.Inthis
case, all of the geometry is calculated using the same procedure as in the previous chapter.
Below figures show the 5 different geometry having different aspect ratio.
Fig 6.1 Savonius Hydro-Turbine with Position Fig 6.2 Savonius Hydro-Turbine with Position e =10
Results and Discussions
8.3.1 Velocity contour of savonius hydro-turbine at Aspect Ratio e=25 and canal width 0.636D, 2.5D, 5D, and 15D
Fig 8.7 Velocity Contour at 2.5D Canal Width
Fig 8.8 Velocity Contour at 5D Canal Width
Velocity Inlet
Pressure Outlet
Bottom Wall
Top Wall
Interference
Savonius Turbine

Fig 8.9 Velocity Contour at 15D Canal Width
8.3.2 Pressure contour of savonius hydro-turbine at Aspect Ratio e=25 at different canal width
Fig 8.12 Pressure contour at 5Dcanal width
Fig 8.13 Pressure contour at 15D canal width

Fig 8.14 Pressure contour at 10D canal width
Fig 8.15 Pressure contour at 2.5D canal width
Fig 8.16 Pressure contour at 0.636D canal width
Fig 8.17 Cp Vs Blockage comparison

8.4 Closure
The fig 9.17 shows how the Cp is varying with respect to canal width it is an obvious observation that if the canal widthistoosmall
the total force of water which is coming with a free stream velocity is dropped on the rotor and then while increasing the width of
the inlet area the fluctuation is continue and at a middle position able to get the optimumCpinthiscasethefeasible solutioncanbe
able to get at 5D. The width is minimize at the last position where it is unable to rotor from above it is clearly observe that while
reducing the width of the canal the Cp is decreasing gradually.
Fig 6.101 Comparison between Cp vs TSR with an aspect ratio of 5
The performance of a Savonius hydro turbine CFD simulation is examined in the current work at low velocities in the range of 0.6
m/s inside an open canal. For the same settings, results from both experiments and CFD work are compared. The research results
are summarised in the following conclusions:
1. The findings of the torque and power performance measurements of the Savonius hydro turbine indicate that the
maximum Cp can be attained at a specific location with a low free stream velocity with less fluctuation in the turbine.
2. The location determined by this work is the most practical since it allows for a maximum power co-efficient that is far
higher than that of any other position.
3. Free stream water velocity of 0.6 m/s would be ideal for the current work because it can be achieved with less fluctuating
torque and power.
4. As the overlap ratio increases, it is seen that the areas that cover a larger percentage produce high Cp at a specific point,
which indicates that the power extracted through a Savonius hydro turbine is increasing gradually.
5. The Cp is observed to start decreasing at e=30 as the overlap ratio is further raised, indicating that e=25 is the practical
point for the blade.
REFERENCES
[2] Zied Driss,Olfa Mlayeh Dorra Driss, Makram Maaloul, Mohamed Salah Abis “Numerical simulation and
experimental valisation of the turbulent flow around a small incurved Savonius wind rotor” Energy at science direct
(2014)
4. CONCLUSION
[1] N.K. Sarma, A Biswas, R.D. Misra ,“Experimental and computational evaluation of Savonius hydrokinetic turbine
for low velocity condition with comparison to Savonius wind turbine at the same input power” Energy conversion and
Management at science direct(2014)
The above fig 8.17 shows that as the blockage is reduce the value of Cp is increased and at 5D width of the canal the optimum Cp
can be achieved.

[3] Patel C.R., Patel V.K., Prabhu S.V., Eldho T.I.,“Investigation of Overlap Ratio for Savonius Type Vertical Axis Hydro
Turbine” International Journal of Soft Computing and Engineering (IJSCE) ISSN 2231-2307, Volume-3, Issue-2, May
(2013)
[4] N.H. Mahmoud, A.A. El-Haroun , E. Wahba , M.H. Nasef “An experimental study on improvement of Savonius rotor
performance” Alexandria Engineering Journal(2010)
[5] U.K. Saha, M. Jaya Rajkumar, “On the performance analysis of Savonius rotor with twisted blades” Renewable Energy
31 (2006) 1776–1788
[6] Joao Vicente Akwaa, Horacio Antonio Vielmob, Adriane Prisco Petry,“A review on the performance of Savonius wind
turbines” Renewable and Sustainable Energy Reviews(2012)
[7] Sukanta Roya, Ujjwal K. Sahab ,“Computational study to assess the influence of overlap ratio on static torque
characteristics of a vertical axis wind turbine” Chemical, Civil and Mechanical Engineering Tracks of 3rd Nirma
University International Conference (NUiCONE 2012)
[8] Mabrouki, Zied Driss, Mohamed Salah Abis, “Performance Analysis of aWater Savonius Rotor Effect of the Internal
Overlap Ibrahim”Sustainable Energy, 2014, Vol. 2, No. 4, 121-125 Available online at
http//pubs.sciepub.com/rse/2/4/1 © Science and Education Publishing DOI10.12691/rse-2-4-1
[9]. F. O. Rourke, F. Boyle, and A. Reynolds, “Renewable energy resources and technologies applicable to Ireland,”
Renewable and Sustainable Energy Reviews, vol. 13, no. 8, pp. 1975–1984, 2009. View at Publisher • View at Google
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