1. MULTI SPINDLE
VARIABLE DISTANCE
NUT RUNNER
PROJECT GUIDE:
Dr.S.Prasanna Raj Yadav-Associate Professor
Members:
1. V. Malola Krishnan(310618114058)
2. S.Kumara Guru (310618114055)
3. Mohammed Jibran(31061811066)
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2. ABSTRACT
• The current trends of technology moves towards a faster and
sustainable future with automation the main goal.
• The growth of Indian manufacturing depends on its
productivity rate and quality.
• Existing model of multi-spindle nut runner has various
drawbacks due to its fixed distance which limits its
applications.
• This model focuses on minimalizing the drawbacks and
thereby improving overall efficiency.
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3. INTRODUCTION
• Vehicles are now a essential part of humans day to day life
• For cars the nut running set up is a T-Wrench and car jacker
which causes difficulty among many users .
• The main disadvantage is the waste of time and energy.
• In Indian market there is no automotive tool to replace the
manual work done.
• The time and work involved is a big hurdle for users
• To overcome this, A tool has to be designed to minimize the
effort and time required by conventional tools.
• Thereby a design to remove all four nuts at once has been
designed to address the issue.
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4. INTRODUCTION
• The main issue when it comes to long distance travelling in
cars is the replacement of tires in case of punctures.
• . This project focuses on the minimization of human effort and
time consumed for fixing all four nuts of the four wheeler tire
with a single stroke of lever by using multiple operated
spanners
• This is done by using a planetary gear mechanism, One pinion
gear(input) and 4 spur gears(Output).
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7. DESIGN CALCULATIONS
• Normal load acting on pinions tooth
(Wn) = WT /cosΦ = 3070 / cos 20(Pressure angle)=7522
• Weight of gear
(Wg) = 0.00118* Tg*b*m2 = 0.00118*24*10*2.452 =1.7 N
• Therefore resultant load on gear,
(WR) = (Wn^2+ Wg^2+2* Wg* Wn*cosΦ)^0.5
= (75222+1.72+2*7522*1.7*cos20)^0.5
WR =7523 N
• Assuming pinion is overhung on shaft at 30 mm Bending
moment on shaft due to WR is M Then we take
M = WR* 30 = 7523*30 =225707 N-mm 7
8. DESIGN CALCULATIONS
• Twisting moment on shaft due to WT is T
T = WT * Dg / 2 = 3070*59 /2 = 90565 N
• Equivalent twisting moment is
Te= (M2+ T2) ^0.5 = (2257072 +905652) ^ 0.5
Te= 243198 N-mm
• Let Dg be the diameter of gear shaft Then
Te= π*τ* dg 3 /16 (τ is taken from data hand book)
dg ^3 =243198*16/(π*250)
dg= 18mm (say)
This implies that the bore diameter required to withstand the
maximum input torque is 18mm 8
9. GEAR PARAMETERS
• From the calculations assuming standard spur gear industrial
module m= 2.5 mm and Number of teeth Z= 24,Z=22 and pitch
circle diameter of a car=118 mm and Gear ratio=1.5
• Gears:
Diameter of the pinion (Dp) = 54mm
Number of teeth’s on pinion (Tp) =22
Diameter of the gear (DG) =64 mm
Number of teeth’s on gear (TG) =26
• Bearings:
Type of Bearing = Ball bearing
Bore diameter = 16mm
Diameter of the bearing =40mm
NOTE:Since Mild steel is used E=2* (10^5)
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10. MATERIAL SELECTION
• FOR SPUR AND PINION GEAR:
MILD STEEL GEARS (EN8)
• HANDLE:
Mild steel (SS 400)
• BEARINGS:
Bearing number 6202-Bearing steel
• FLEXIBLE SHAFT:
Material not mentioned
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11. COST ESTIMATION
Sl.No Name of the Component Number of
components
Cost of each
component(Rs.)
Total
Cost(Rs.)
1 Spur Gear 4 150 600
2 Pinion Gear 1 150 150
3 Ball Bearings 5 60 300
4 Flexible shafts 4 250 1000
5 Frame 1 70 70
TOTAL COST 2120 11
12. WEIGHT ESTIMATION
Sl.No Name of the Component Number of
components
Weight of each
component(Kg)
Total weight
1 Spur Gear 4 0.485 2.54
2 Pinion Gear 1 0.775 0.775
3 Ball Bearings 5 0.04 0.04
4 Flexible shafts 4 0.3 1.2
5 Frame 1 2 2
TOTAL WEIGHT 6.555
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13. WORKIN PRINCIPLE
• The device works on the principle of gear transmitted power.
• The fundamental law of gearing has to be followed in
designing of any gear driven mechanism which is , “For a pair
of gear to transmit constant angular velocity ratio, the tooth
profiles of these mating gears must be designed in such a way
that the common normal (line n-n) or the line of action passes
through a fixed point, or also known as the pitch point, on the
line of centers.”
• Input is given via a single pinion gear through a automated
drilling machine or manually through a spanner
• The input is transmitted via 4 spur gears
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14. WORKING PRINCIPLE
• The spur gears each connected to flexible shafts transmit
power through ball bearings by shafts.
• The flexible shaft is mounted on nuts and that is used to
tighten or remove nuts.
• OBJECTIVE:
• The objective is to design and fabricate the wheel nut runner
for 100mm PCD with the following properties,
• 1. To make the wheel nut removal tool lighter.
• 2. To use less expensive materials.
• 3. To reduce the production cost.
• 4. To apply the less human effort.
• 5. To make the multi spindle nut runner applicable for variable
distanced nuts. 14
18. CONCLUSION
• Existing models are focused on removing one nut at a time
which is very time consuming
• The cost of automated single nut runner is almost equivalent
of our model.
• Very less space is required to store the model as compared to
conventional screw jack and T wrench
• Skill required to operate is very low
• Removing of car tyres is a tedious process this project does
not eliminate all the difficulties in removing car tyres but
reduces the disadvantages in existing models
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