Intze Overhead Water Tank Design by Working Stress - IS Method.pdf
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Performance studies on a direct drive turbine for wave power generation in a numerical wave tank
1. Performance Studies on a Direct Drive
Turbine for Wave Power Generation in
a Numerical Wave Tank
Professor Young-Ho LEE
Division of Mechanical & Energy System
Engineering,
College of Engineering,
Korea Maritime University, South Korea.
Deepak Prasad
Discipline of Mechanical Engineering,
University of the South Pacific, Fiji Islands.
Dr. M. R. Ahmed
Discipline of Mechanical Engineering,
University of the South Pacific, Fiji Islands.
2. Renewable Energy Sources
2
Wind Power Solar Power Biomass Hydro Power Ocean Energy
Thermal
Energy
Mechanica
l Energy
WaveTide
Fig. 1 Renewable energy sources
3. 3
Introduction
๏ฏ Wave energy:
๏ฎ Power flux โ 15 to 20 times more than wind and solar.
๏ฎ Estimated wave energy is in order of 1 to 10 TW.
๏ฎ Most consistent of all the intermittent sources and truly
renewable.
๏ฏ Wave tanks have been used over the years to provide:
๏ฎ helpful information on wave characteristics and
employed to conduct prototype testing. However it is:
๏ฏ Expensive, time consuming.
๏ฏ Due to time constraint all design variables can not be tested.
4. 4
Introduction
๏ฏ To overcome these problems much effort has been
focused on the development of Numerical Wave Tank
(NWT).
๏ฎ NWT allows for rapid design changes and
improvements in short time.
๏ฏ With improving computer capabilities it is possible for
these CFD packages to solve and give accurate
solutions of real life problems.
5. 5
Introduction
๏ฏ The current study employs a 3D NWT based on
Reynolds Averaged Navier-Stokes Equation (RANSE)
to generate waves using commercial CFD code
ANSYS-CFX.
๏ฏ A cross flow turbine is employed to generate power
from incoming waves.
๏ฏ Aim:
๏ฎ To simulate waves using a Numerical Wave Tank.
๏ฎ To validate the CFD code with the experimental data.
๏ฎ To study flow characteristics.
6. 6
Base Model
All Dimensions in mm
Fig. 2 Schematic of the entire model
Fig. 3 Schematic of the turbine and runner blade
Parameter Value
Blade entry angle, ฮฑ 30ยบ
Blade exit angle, ฮฒ 90ยบ
Outer Diameter, Do 260 mm
Inner Diameter, Di 165 mm
Number of Blades 30
Table 1 Turbine and runner parameters
7. ๏ฏ Full model calculation.
๏ฎ Numerical Wave Tank (NWT).
๏ฎ Front Guide Nozzle.
๏ฎ Augmentation Channel.
๏ฏ Front Nozzle.
๏ฏ Rear Nozzle.
๏ฏ Turbine.
๏ฎ Rear Chamber.
7
Test Section
Fig. 4 Schematic of the test section
8. CFX-Pre
Computational Domain
8
Simulation Type Transient Wave Maker Piston-Type (Specified Motion)
Turbulence Model k-Epsilon Opening 1 atm
Phase Water & Air @ 25ยฐC Walls No-Slip Condition
Surf. Tension
Coeff.
0.075 N/m Density (kg/m3
) Water = 997, Air 1.18
Opening
Moving mesh section
Wall Motion: Asin(ฯt)
Fig. 5 Computational domain.
NWT
Front Guide
Nozzle
Augmentation channel
Rear chamber
Table 2 ANSYS CFX-Pre conditions
9. 9
Wave Height & Velocity (NWT)
Point
Fig. 6 Water wave height in the numerical wave tank
Fig. 8 Velocity contour in the numerical wave tank
Fig. 7 Volume fraction showing the formation of
waves in the wave tank
10. 10
Front Guide Nozzle
Fig. 9 Velocity vector in front guide nozzle
๏ฏ There is a recirculation region
observed near the top left
corner, denoted by A when
water is flowing in.
๏ฏ Due to this, the flow was
directed towards the bottom
and hence higher velocity
recorded in region B.
๏ฏ When water was retreating,
higher velocity was observed
in region A.
11. 11
Front Guide Nozzle
Fig. 10 Average velocity in the front guide nozzle
at different rpm
๏ฏ It is observed that the velocity
increases as the rpm increases,
reaches a maximum and then
decreases.
๏ฏ This peak at 35 rpm is due to
better flow characteristic because
of small re-circulating region in the
front guide nozzle.
๏ฏ This also leads to better flow in the
augmentation channel.
12. 12
Turbine Power
Fig. 11 Comparison between experimental data and CFD results
Variable Unit Experiment CFD
H m 0.2 0.195
T s 2.0 2.0
ฮH m 0.071 0.065
Q m3
/s 0.03 0.032
PWave W/m 86.74 82.46
PWP W 20.85 20.36
Table 3 Comparing experimental and CFD results
๏ฏ For CFD, the peak power is 6.71 W compared to 6.8 W obtained experimentally.
๏ฏ The efficiency at 35 rpm is 44.73% and 45.33% respectively from CFD and experiments.
๏ฏ The difference is within 3%.
13. 13
Flow Characteristics
Fig. 12 Velocity vector in the augmentation channel at 35 rpm
๏ฏ The flow accelerates approaching
stage 1 as expected. (Nozzle effect)
๏ฏ The water passes through the turbine
passage at stage 1 while imparting
energy to the runner.
๏ฏ From the exit at stage 1 to the entry of
blades at stage 2, the flow again
accelerates a little.
๏ฏ At stage 2, the passing water imparts
energy to the runner once more before
flowing into the rear nozzle.
15. 15
Conclusion
๏ฏ Commercial CFD code ANSYS-CFX was successfully
used to generate waves in a NWT using a piston
type wave-maker.
๏ฏ The results of CFD simulation showed good
agreement with the experimental data. The difference
in result was within 3%.
๏ฏ The maximum turbine power was obtained at 35 rpm.
For CFD, the maximum power was 6.71 W compared
to 6.8 W obtained experimentally.
๏ฏ The efficiency at 35 rpm was 44.73% and 45.33%
respectively for CFD and experiment.
Editor's Notes
RENEWABLE ENERGY IS THE ENERGY OBTAINED FROM CURRENTS OF ENERGY OCCURRING IN THE NATURAL ENVIRONMENT.
THE MAJORITY OF THE RENEWABLE ENERGY TECHNOLOGIES IS DIRECTLY OR INDIRECTLY POWERED BY THE SUN.
APART FROM WIND AND SOLAR ENERGY, THE OCEAN CONTAINS VAST AMOUNT OF ENERGY.IN FORM OF THERMAL AND MECHANICAL ENERGY.
MECHANICAL ENERGY : TIDES AND WAVES.
The primary objective is to maximise the energy conversion.
NWT
LENGTH = 15M
HEIGHT = 1.5M
WIDTH = 1M
REAR CHAMBER WIDTH = 0.7M
EVERY COMPONENT IN THE AUGMENTATION CHANNEL HAS A WIDTH OF 0.7M
TURBINE SECTION INCLUDES = FRONT GUIDE NOZZLE, FRONT AND REAR NOZZLE, REAR CHAMBER AND INTERNAL FLUID REGION
A NUMERICAL WAVE TANK WAS USED TO SIMULATE THE SEA CONDITIONS
THE AUGMENTATION CHANNEL CONSISTS OF FRONT AND REAR NOZZLE AND TURBINE.
The computational domain was divided into 5 parts.
Moving mesh section โ wave maker
NWT
Front guide nozzle
Augmentation channel โ consists of front nozzle, rear nozzle and turbine
Rear Chamber
As expected, kinetic energy at the surface is more as shown in Fig. 8.
Front guide nozzle guides the flow into the channel.
Performance is really important to the flow downstream.
The front guide nozzle inlet is denoted by x/Lo = 0 and the exit as x/Lo= 1. Lo is the length of the front guide nozzle which is 700 mm.
The results show a gradual increase in velocity in the guide nozzle as desired.
The peak in efficiency basically indicates that the interaction between the turbine and flow is maximized at this optimum rotational speed. At this speed maximum energy is extracted hence higher turbine power and efficiency. For T = 2s, highest efficiency of 44.73% is obtained at rotational speed of 35 rpm.
At 35 rpm the velocity recorded in the front guide nozzle was the highest as previously highlighted in Fig. 10. This lead to better flow in the augmentation channel which ultimately meant higher energy extraction from the turbine.
The rear spiral wall ensures that the flow accelerates uniformly.