Arctic Duct type cooling system is assembled to the tractor cabin for the completeness of the driver mainly for farmer in agriculture field

1. KLE DR. M. S. SHESHGIRI COLLEGE OF
ENGINEERING AND TECHNOLOGY, BELAGAVI
590008
A FINAL PHASE PROJECT PRESENTATION ON,
DESIGN AND ANALYSIS OF COOLING SYSTEM FOR
TRACTOR CABINSubmitted by,
Abhishek Turamandi USN: 2KL17MDE01
Under The Guidance of
Dr. Deepak C. Patil
Department of Mechanical Engineering
2018-19
1

2. Technology Bucket: Agriculture and Rural Development
Company Name/ Ministry Name: Mahindra&Mahindra ( FarmEq)
Category: Hardware
Problem Code: MJ1
College Code:1-3514624425
2
 SMART INDIA HACKATHON PROJECT

3.  OBJECTIVES
3
 To provide a cheap and simpler means of automotive comfort
 Eco-friendly cooling system
 Evaporative cooling system consuming low power
 Cost effective
 Human comfort and safety during vehicle driving
 Design of a smart cabin and cooling system for a tractor

4.  LITERATURE SURVEY
4
[1] Shiv Kumar Kushwaha, A. C. Tiwari, “Evaporative cooling comfort in
agricultural tractor cabin”, Journal of the Brazilian Society of Mechanical
Sciences and Engineering, 2016, 38(3), 965-976.
 This paper focuses on providing comfort conditioning of tractor cab
 It tells evaporative cooling system ideally suited to the hot dry climate
 Results shows temperature reduced from 53 to 33 ˚c inside a tractor cabin in 15 min
duration
 4 L/h of water and 130W total energy consumption
 The energy for the unit is drawn from the battery which intern charged by alternator

5. 5
[2] Mr Dragan Ruzi,et.al, “Agricultural tractor cab characteristics relevant for
microclimatic conditions”, Faculty of Technical Sciences, 2011, 9(2),198, 323 – 330
 This paper focuses on microclimatic features of middle sized tractor cabs
 It tells cab material characteristic and cab design play the main role in heat transfer
 Aim of this paper is to identify and evaluate influences, in order to create the basis for
microclimatic and energy consumption reduction aspects of a tractor cab design
 The result showed cab glazing probably the most influencing factor
 Infrared reflective glass rejects almost half of solar radiation energy

6. 6
[3] J. K. Jain, D. A. Hindoliya, “Experimental performance of new evaporating
cooling pad materials”, Sustainable Cities and Society, 2011, 1(4), 252-256.
 This paper concludes that palash and coconut fibre's show great potential for use
 Performance of palash fibre's to be better than that of other materials tested
 Coconut fibre's are also easily available and found to be better than aspen fibre's
 Palash offers about half the pressure drop compared to that of aspen

7.  METHODOLOGY
7
 Modelling of tractor cabin and cooling system
 General arrangement drawing of tractor cabin and cooling system
 Adapting Evaporative cooling system
Analysis of tractor cabin and cooling system
 Thermal Analysis
 Linear Static Analysis

8.  GENERALARRANGEMENT DRAWING
8
Fig. 1: General Arrangement Drawing of Proposed Project Work as Per the Actual Dimension

9.  EVAPORATIVE COOLING SYSTEM
9Fig. 2: Schematic of the Evaporative Cooling System for Tractor Cabin

10. 10
Table 1: Benefits of Evaporative Cooling
Technology characteristics Value Comments
Unit energy savings 75% Average estimated energy savings over vapor
compression
Type of energy source(s) Electricity (solar)
Working fluid(s) Water Water is evaporated in open loop
Complexity/size Low Complexity is lower in Evaporative systems
compared to vapor compression units.
Technical maturity High
Indoor air quality
Environmental effects
Better
Low power plant
emission
0 % reduction
As compared with vapor-compression units

11.  APPLICATION
11
 In agriculture fields
 Construction sites
 Goods transportation
 Evaporative cooling system can also be used for JCB, Road roller, Mobile cranes.

12.  INDIVIDUAL PARTS DESIGN
12
 The duct is modeled to a square shape of dimension 250mm and extruded to length 250mm and thickness 5mm.
The Cap is modelled to square shape of dimension 260mm extruded to a length of 5mm and thickness 5mm,
which is press fitted to a duct which holds all inside components of the duct firmly.
Fig. 4:CapFig. 3:Duct
Software used: Unigraphics

13. 13
Fig. 5:Fins Fig. 6:Case fan Support
Software used: Unigraphics
 Function is to increase the heat transfer rate capability.
 Help to bring cool air into and blow hot air out of the case.

14. 14
Fig. 7: Cooling Pad
Software used: Catia V5
 The cooling pad is modelled to square shape of dimension 235mm extruded to a length 235mm and thickness
3mm.
 Palash or coconut fibre’s placed inside the slot which absorbs the water and get wetted.

15.  MODEL OF EVAPORATIVE COOLING SYSTEM
15
Fig. 8: Evaporative Cooling System 3D model
Software used: Unigraphics

16.  DRAFTING OF EVAPORATIVE COOLING SYSTEM
16
Fig. 9: Drafting of a Evaporative Cooling System
Software used: Catia V5

17.  EXPLODED VIEW OF MODEL
17
Fig. 10: Evaporative Cooling System Exploded View
Software used: Unigraphics

18.  MODEL OF A TRACTOR WITH EVAPORATIVE UNIT
18
Fig. 11: Tractor Cabin With Evaporative Cooling System 3D Model
Software used: Unigraphics

19.  CALCULATIONS
19
 Rate of Heat Transfer
I. From atmosphere to inner surface of the duct
𝑄1 = ℎ𝐴(𝑇𝑠 − 𝑇∞) (1)
Where,
𝑄-Rate of heat transfer in watts,
𝐴-Heat transfer area in 𝑚2,
(𝑇𝑠 − 𝑇∞)-Temperature difference between surface and
fluid in °C,
ℎ- Convective heat transfer coefficient in 𝑊 𝑚2 𝑘.
𝑸 𝟏 = 𝟐𝟐. 𝟖𝟓𝟐 𝑾
II. Fin of finite length with specified temperature at
its end.
𝑄 𝑓𝑖𝑛 = 𝑘𝐴 𝑐 𝑚(𝜃1 + 𝜃2)(
cos ℎ 𝑚 𝐿 −1
sin ℎ 𝑚 𝐿
) (2)
Where,
𝐴 𝑐-Cross sectional area of fin,
𝑘-Thermal conductivity of material of film,
(𝜃1 + 𝜃2)-Sum of temperature,
𝐿-length of the fin.
𝑸 𝒇𝒊𝒏 = 𝟎. 𝟔𝟒𝟒𝟖𝟔 𝑾
III. Forced Convection heat transfer rate
𝑄2 = ℎ 𝑎 𝐴 𝑇𝑠 − 𝑇∞ (3)
𝑸 𝟐 = 𝟏𝟏. 𝟔𝟖𝟓𝟕 𝑾

20. 20
IV. Heat Transfer Through Conduction
𝑄 = −𝑘𝐴
𝑑𝑇
𝑑𝑋
(4)
Where,
𝑘-Thermal conductivity of the material in W⁄mk ,
𝐴- Area measured normal to the direction of heat flow in
𝑚2
,
𝑑𝑇
𝑑𝑋
-Temperature gradient in that direction.
𝑸 = −𝟔. 𝟔𝟑 × 𝟏𝟎−𝟒
𝑾
 Flow Rate, Effectiveness, Cooling Load of the Cabin
I. Air flow rate
𝑉𝑎𝑖𝑟 = 𝑣 × 𝐴 (5)
Where, 𝑣- Avg air velocity from the fan at exit in 𝑚 𝑠 ,𝐴-
Area of the fan in 𝑚2
.
𝑽 𝒂𝒊𝒓 = 𝟏𝟏𝟑. 𝟎𝟕𝟓 𝑳 𝒔
II. Air mass flow rate
𝑀 𝑎𝑖𝑟 = 𝜌𝑉𝑎𝑖𝑟 (6)
Where, 𝜌- Density of air,𝑉𝑎𝑖𝑟- Velocity of air
𝑴 𝒂𝒊𝒓 = 𝟎. 𝟏𝟐𝟐𝟏 𝑲𝒈 𝒔
III. The effectiveness of the cooling system
𝜇 = (𝑇𝑖 𝑑𝑏𝑡
− 𝑇0′
𝑑𝑏𝑡
)/(𝑇𝑖 𝑑𝑏𝑡
−𝑇0′
𝑤𝑏𝑡
)
(7)
Where, 𝑇𝑖 𝑑𝑏𝑡
- Inlet air dry-bulb temperature, 𝑇0′
𝑑𝑏𝑡
-
Dry-bulb temperature of air at fan exit , 𝑇0′
𝑤𝑏𝑡
- Wet-
bulb temperature of air at fan exit.
𝝁 = 𝟕𝟑. 𝟔𝟖𝟒%
IV. Cooling load of the cabin
𝑀 𝑎𝑖𝑟 ℎ 𝑜′−ℎ 𝑜 (8)
Where, ℎ 𝑜′− Specific enthalpy of air at fan exit , ℎ 𝑜-
Specific enthalpy of air in the cabin at steady state.
𝐂𝐨𝐨𝐥𝐢𝐧𝐠 𝒍𝒐𝒂𝒅 = 𝟏. 𝟏𝟖𝟎𝟕 𝒌𝑾

21. 21
V. Water consumption
𝑀 𝑊 = 𝑀 𝑎𝑖𝑟(𝑊𝑖 − 𝑊𝑜) (9)
Where, 𝑊𝑖=Humidity ratio of inlet air, 𝑊𝑜=Humidity
ratio of air at fan exit
𝑴 𝑾 = 𝟐. 𝟔𝟗𝟒𝟓 𝑲𝒈 𝒉𝒓
 Shear Force and Bending Moment Diagram
 Pump Design
𝑄 𝑤 =
𝜂 𝑤2−𝑤1
1000
(10)
Where, (𝑤2−𝑤1)- Moisture content, 𝑄 𝑤- Cabin water
requirement.
𝑄 𝑤 = 12.375 𝐿 𝑠𝑒𝑐
Power requirement =
𝑄 𝑤×𝐻
75×𝜂
(11)
𝐏𝐨𝐰𝐞𝐫 𝐫𝐞𝐪𝐮𝐢𝐫𝐞𝐦𝐞𝐧𝐭 =0.125 hp

22.  PARTS MESHING
22
Fig. 12: Duct
Software used: Hyper mesh 12
Fig. 13: Cap Fig. 14: Fan
 Hypermesh preprocessing software popularly known as meshing software, reduce time and engineering analysis
setup cost through high-performance finite element modeling, simplify the modeling process for complex
geometry.

23.  HYPER MESH PROCEDURE
23
Assigning the materials
Material Properties
Fig. 15: Assigning the material to the duct
Fig. 16: Assigning the thickness to the midsurface of duct

24. 24
Creating Load Collectors
Fig. 18: Number of modes extraction
Load Step
Fig. 17: Constraining all the degrees of freedom
Fig. 19: Assigning the load step

25. 25
Running the Analysis Result
Fig. 20: Creating load step
Fig. 21: Post processing

26.  ANALYSIS RESULTS
26
Software used: Hyper mesh 12
Fig. 22: Grid Temperature of the Duct
 Thermal Analysis

27. 27
Fig. 23.: Element fluxes of the Duct
 Thermal Analysis

28. 28
Fig. 24: First mode shape of the duct
 Modal Analysis

29. 29Fig. 25: First 10 mode shape result of the duct
 Modal Analysis

30. 30Fig. 26: First mode shape of tractor cabin rear frame
 Modal Analysis

31. 31Fig. 27: First 10 mode shape result of tractor cabin rear frame
 Modal Analysis

32. 32
Fig. 28: Contour plot of Displacement
 Linear Static Analysis

33. 33Fig. 29 : Contour plot of Element Stresses
 Linear Static Analysis

34.  CONCLUSION
34
 Thermal heat transfer rate is calculated analytically and the same is verified using FEA
analysis.
 Concentrated stress zones and low stress zones are identified in tractor cabin rear frame
by conducting structural analysis, linear stress distribution at concentrated stress zones is
achieved.
 Installation cost for mounting evaporative cooling unit to the tractor cabin frame is less
as linear static analysis results values are less in number than theoretical calculation.

35. 35
 It is confirmed that evaporative cooling model is not deviating with tractor cabin rear
frame model in terms of vibrational damping capacity by conducting modal analysis for
10 modes.
 Good quality pads such as palash and coconut fibre's most suitable because they are
abundantly available and widely used in domestic application. Also pad maintenance is
not frequent, and they have long life.

36.  REFERENCES
36
[1] Shiv Kumar Kushwaha, A. C. Tiwari, “Evaporative cooling comfort in agricultural tractor
cabin”, Journal of the Brazilian Society of Mechanical Sciences and Engineering, 2016,
38(3), 965-976.
[2] J. K. Jain, D. A. Hindoliya, “Experimental performance of new evaporating cooling pad
materials”, Sustainable Cities and Society, 2011, 1(4), 252-256.
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[5] Bhatti MS, “Evolution of automotive air conditioning”, ASHRAE J 41, Riding in comfort,
1999, 2, 44-50.

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37

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39. THANK YOU
39