This project aim is to produce electricity using the concept of rotating wind turbine. Wind caused by moving train is used to generate electricity. The idea is to design wind turbine that can be installed between the slippers on the track. As a train passes by, wind pressure drives the turbine to generate the electricity, this device could be placed along railway line and make good use of waste resources. An electrical power generation system comprises of variable capacitors and power sources. Power sources is used in the form of generator to prime variable capacitor that effectively multiplies the priming energy of power source by extracting energy from passing vehicle

1. PROJECT REPORT ON
“CASEMENT TYPE WIND TURBINE”
PRESENTED BY-
1. KISHOR CHIKANE B-121020910
2. KAUSTUBH KHANDAGALE B-121020904
3. ANKUSH DHAMNE B-121020849
4. ASHUTOSH KADAM B-121020890
GUIDED BY-
Prof. S.U. JAGTAP
RMDSSOE Mechanical Engineering

2. INTRODUCTION
• India has 5th rank in world for producing wind energy.
• Nowadays in India we are using more and more renewable energy
sources for reducing pollution and to minimize fuel consumption.
• Wind turbine is a rotating machine which converts the kinetic energy of
wind into mechanical energy. This Mechanical energy we are using in
pumps.

3. OBJECTIVES
• Design a device for capturing wind pressure &
generate electricity.
• Design the turbine blade and various components.

4. SCOPE
• As alternative energy source.
• For decreasing energy crisis.
• Assuming 1kW of Wind Power per household of 5 persons. Each
from renewable resources 43,000MW of additional Wind Power will
be needed for urban India by 2025 (assuming 1kW of Wind Power
per household) much of this can be delivered using small wind
turbines Power generation with the help of wind energy is one of the
interesting R&D criteria.

5. ENERGY SCENARIO

6. METHODOLOGY
• The main purpose of the wind turbines is to convert the kinetic
energy of the wind into mechanical energy by the blades and then
into electrical energy by the generator.
• As train passes over the track, rotation of blades takes place.
• In power generation system by using Blade’s rotation electricity
produced.

7. METHODOLOGY

9. WHY VERTICALAXIS WIND TURBINE?

10. LITERATURE REVIEW
• Chirag Soni ,Smit Thakkar- They investigated effect of different design
parameter on performance evaluation of VAWT also proved that 3 blade
VAWT more efficient than 2 or 4 blade.
• Sandip S. Wangikar -In this paper they concluded that wind speed and
shutter angle affects the performance of turbine significantly.
• Ahmet Duran Sahin -Wind energy history, wind-power meteorology, the
energy–climate relations, wind-turbine technology, wind economy, wind
hybrid applications

11.  INPUT PARAMETERS
• Wind speed.
• Blade angle.
OUTPUT PARAMETERS
• Shaft speed.
• Torque.
• Mechanical work.

12. ADVANTAGES
• To build power generation system.
• Minimize use of fossil fuel.
• Minimize production of greenhouse gas.

13. Design and Calculations
 Design of blade and casement.
Design power output for CTWT is 15 Watt.
P=15Watt
Swept area calculated as
S=2RL
Where S=Swept are in m2
R=radius of rotor in m
L=Length of blade in m
 Swept Area=S =
2𝑃
𝐶 𝑃 𝜌𝑉 𝑤𝑖𝑛𝑑
3
S=
2
∗
15
0
.
25
∗
1
.
2
∗73
S=0.29 m2
So we assume
 R=270mm=0.27m
 L=400mm=0.4m
 W=width =1mm

14. Material for frame and blade
For the first trial of CTWT, the mild steel is taken as easily available in required form and at minimum cost.
Material=C40
Properties- 1)Syt=540 N/mm2
2)Sut=340 N/mm2
Consider FOS=2
Force acting on blade-
The inertia force caused by the angular velocity of the rotor are given by
F=rG*ω2*mblade
Where rG=distance from axis to center of gravity=270/2=135mm
ω=angular velocity of rotor
=V/rG =7/0.135=51.85
ω=52 rad/sec
mblade=(volume of blade+volume of casement)*ρsteel
Volume of blade=270*400*1 =108000mm3
=0.108*10-3m3

15. Voume of casement=[(170*5*2)+(270*10*2)]*2
=14200mm3=0.0142*10-3m3
mblade=(0.108+0.0142)*10-3*7800
=0.9531 kg
F = rG*ω2*mblade
=0.135*522*0.9531
=811.81 N
Check for design
Blade:-
Due to wind force acting on the frame there are chances of bending the frame is to be checked
for bending failure criteria. Permissible bending stresses for given material σb=Syt/FOS
σb=340/2=170 N/mm2
Area of blade subjected to wind force
A=270*400
=108000mm2
σ(induced)=F/A=811.81/108000 =0.007516 N/mm2< σb
• Thus induced bending stresses are negligible and very less than the permissible bending stresses
therefore the blade design is safe and dimension of the frame taken are right.

16. Casement:-
• Due to wind force acting on the casement there are chances of bending the casement is to
be checked for bending failure criteria. Permissible bending stresses for given material
σb=Syt/FOS
σb=340/2=170 N/mm2
Area of the frame subjected to wind force,
A=(170*5)+(270*5) =2200mm2
σ(induced)=F/A=811.81/2200
=0.3690< σb
Thus induced bending stresses are negligible and very less than the permissible bending
stresses therefore the casement design is safe and dimension of the casement taken are
right.

17. Design of shaft
• Material selection
The material for shaft is selected as C50. It is easily available and cost effective as compared
with alloy steel
Properties:-1) Yield strength Syt=720 N/mm2
2) Ultimate tensile strength Sut=380 N/mm2
3) FOS=2
Design calculation for shaft
Shaft is designed as per ASME (American Society of Mechanical Engineering), maximum
shear stress is given by,
σsmax=0.3* Syt or 0.18* Sut (choose whichever is minimum)
σsmax=0.3* Syt =0.3*380=114 N/mm2
σsmax=0.18* Sut = 0.18*720=129.6 N/mm2

18. thus we choose
σsmax=114 N/mm2
• Torque acting on the shaft:
Torque (T)= wind force * distance from shaft
T= 811.81*135
T=109594.35 Nmm
• Bending moment of the shaft:
The self-weight of blade is acting on shaft in vertical condition and the wind force is acting radially
inward i.e. horizontally on the shaft. Therefore it is necessary to calculate the bending moment in vertical
as well as horizontal condition and take the resultant two moments.
Mv=0.9531*9.81*200 =1869.9 Nmm.
Mh=811.81*135=109593 Nmm.
Resultant bending moment,
MR=√(Mv2+Mh2)
=109608.95 Nmm.
Tmax=√[(MR*Kb)2+(T*Kt)2]
Where Kb=combined shock and fatigue factor for bending=1.5
Kt= combined shock and fatigue factor for tension=1

19. Tmax=√[(109608*1.5)2+(109594.35*1)2]
=197591.06 Nmm
The relation between Tmax, maximum permissible shear stresses
and the diameter of shaft is given by
T/ Tmax=2J/D
J/D=0.2773
J=Polar moment of shaft
=π(D4-d4)/32
Where D=outer diameter of shaft in mm
d=inner diameter of shaft in mm=0.6D
D=1.47mm
Therefore we can take, D=20mm and d=15mm

20. Design of bearing
• Selection of deep groove ball bearing from manufacturing catalogue.
• Radial force acting on bearing=Fr=811.81 N
• Axial force acting on bearing=Fa=0.9531*9.81=9.35 N
• Diameter of shaft is 20mm hence we select bearing 6004 from V.B.Bhandari.
• C0=Equivalent dynamic load carrying capacity=5000N.
• For selection of radial factor(X), thrust factor(Y),
Fa/ C0=0.00187
Fa/V*Fr=0.0115<e

21. • Hence we select
• X=1, Y=0
• Equivalent dynamic load N is given by,
• Pe=(XVFr+YFa)Ka
Where V=1
Ka=load application factor=1.2
• Pe=(1*811.81+0)*1.2 =974.16 N
• Assume life of bearing 50 million revolution.
• L10=(C/Pe)a
a=3 …..for ball bearing
50=(C/974.16)3
• C=3588.83≤C0
• So the bearing 6004 having dynamic load carrying capacity 5000 is selected from
manufacturing catalogue.

22. CTWT PARTS
DC geared motor
• A geared DC Motor has a gear assembly
attached to the motor.
• The gear assembly helps in increasing the
torque and reducing the speed.
• This DC geared motor has maximum capacity of 1000 rpm.

23. CTWT PARTS
 Spur gears
• A pair of spur and pinion gear are used .
• Gear have 96 teeths.
• Pinion have 12 teeths.
• Gear pair is manufactured from Nylon.

24. Deep groove ball bearing
• The purpose of a ball bearing is to reduce rotational friction
and support radial and axial loads.
• Deep-groove bearings can support higher loads.
• The bearing used in CTWT is 6004 deep grove ball bearing.
CTWT PARTS

25. Supporting plate
• A mild steel plate of 5 mm thickness is
used as supporting structure for the shaft.
Hollow Shaft
• A shaft is a rotating machine element.
• The material used for ordinary shafts
is mild steel
CTWT PARTS

26. Galvanized blades
• Three blades are used in CTWT
• Blades are manufactured from Galvanized steel.
• Galvanized steel is corrosion resistant.
CTWT PARTS

27. Air Blower
• An Air blower is a mechanical device for moving
air or other gases.
• Air blowers are constant displacement devices or constant volume
devices, meaning that, at a constant fan speed.
• Blower used is of 2000 rpm .

28. Tachometer
• A tachometer is an instrument measuring the rotation speed
of a shaft
• The Tachometer was used to calculate the rpm of Casement
Type Wind Turbine shaft

29. OBSERVATION
Wind Speed (m/s)
Casement angle
(Ɵ) Shaft speed(rpm) Torque (N.mm)
Power (W)
5 10 18 164.64 0.310
7 10 21 219.52 0.482
9 10 23 329.28 0.793
11 10 27 356.72 1.009
13 10 30 411.6 1.293
15 10 32 466.28 1.562
17 10 33 521.36 1.801
19 10 40 548.8 2.298
• Experiment data for Ɵ=100

30. Wind Speed (m/s) Casement angle (Ɵ) Shaft speed(rpm) Torque (N.mm)
Power (W)
5 30 23 219.52 0.528
7 30 24 301.84 0.758
9 30 26 384.16 1.045
11 30 30 439.04 1.379
13 30 34 466.48 1.660
15 30 35.5 548.8 2.040
17 30 37 576.24 2.232
19 30 44 658.56 3.034
• Experiment data for Ɵ=300

31. Wind Speed (m/s) Casement angle (Ɵ) Shaft speed(rpm) Torque (N.mm)
Power (W)
5 45 25 246.96 0.646
7 45 27 329.28 0.931
9 45 28 411.6 1.266
11 45 32 493.92 1.655
13 45 35.5 521.36 1.938
15 45 38 576.24 2.293
17 45 39 603.68 2.465
19 45 45 686 3.232
• Experiment data for Ɵ=450

32. RESULT
• Main effect plots for shaft speed (rpm) for Ɵ=10
0
5
10
15
20
25
30
35
40
45
5 7 9 11 13 15 17 19
shaftspeed(rpm)
wind speed (m/s)

33. • Main effect plots for shaft speed (rpm) for Ɵ=30
0
5
10
15
20
25
30
35
40
45
50
5 7 9 11 13 15 17 19
shaftspeed(rpm)
wind speed (m/s)

34. 0
5
10
15
20
25
30
35
40
45
50
5 7 9 11 13 15 17 19
shaftspeed(rpm)
wind speed (m/s)
• Main effect plots for shaft speed (rpm) for Ɵ=45

35. • Main effect plots for torque (N.mm) for Ɵ=10
0
100
200
300
400
500
600
5 7 9 11 13 15 17 19
torque(N.mm)
wind speed (m/s)

36. • Main effect plots for torque (N.mm) for Ɵ=30
0
100
200
300
400
500
600
700
5 7 9 11 13 15 17 19
torque(N.mm)
wind speed (m/s)

37. 0
100
200
300
400
500
600
700
800
5 7 9 11 13 15 17 19
torque(N.mm)
wind speed (m/s)
• Main effect plots for torque (N.mm) for Ɵ=45

38. • Main effect plots for power (W) for Ɵ=10
0
0.5
1
1.5
2
2.5
5 7 9 11 13 15 17 19
power(W)
wind speed (m/s)

39. • Main effect plots for power (W) for Ɵ=30
0
0.5
1
1.5
2
2.5
3
3.5
5 7 9 11 13 15 17 19
power(W)
wind speed (m/s)

40. 0
0.5
1
1.5
2
2.5
3
3.5
5 7 9 11 13 15 17 19
power(W)
wind speed (m/s)
• Main effect plots for power (W) for Ɵ=45

41. Cost Estimation
PARTS MATERIAL COST(Rs)
Shaft(800mm) Mild steel 200
Single strip(1500mm) Mild steel 200
L strip(2000mm) Mild steel 200
Bearing 6004 - 200
Blades (900*400) Galvanized steel 460
Frame Cast Iron 600
Drive gear (96 teeth) Nylon 250
Driven gear (12 teeth) Nylon 100
D.C. geared motor - 300
Total cost - 2510

42. REFERENCES
• Michael Borg,MaurizionCollu, “A comparison on the dynamics of floating
of a vertical axis wind turbine on three different floating support
structure”, Cranfield University,Cranfield MK43 0AL, United kingdom.
• Sandeep S. Wangikar, , “Effect of some design parameter on performance
of a Shutter Type Vertical Axis Wind Turbine”, Proceedings of the ASME
2012 Gas Turbine India Conference GTINDIA 2012, December 1,2012,
Mumbai, Maharashtra, India, pp.1-6.
• Brijesh M. Garala, “A FUTURE ENERGY SOLUTION FOR DOMESTIC
POWER REQUIREMENT”, Department of Mechanical Engineering Om
Engineering College Junagadh, Gujarat, ISSN: 2456-1479

43. Working Video

45. THANK YOU!