APROJECT REPORT

ON

BALL TRACTION DRIVE Submitted By Mr. SACHIN PANHALE BO28872 Mr. JORDAN PEGADO B024098

Under The Guidance Of

PROF. LONDHE SANDEEP P.

Department Of Mechanical Engineering

MAHARASTRA INSTITUTE OF TECHNOLOGY,PUNEDEPARTMENT OF MECHANICLE ENGINEEARINGYASHWANTRAO CHAVAN MAHARASTRA OPEN

UNIVERSITY,NASHIK.

2010-2011

MAHARASTRA INSTITUTE OF TECHNOLOGY,PUNEYASHWANTRAO CHAVAN MAHARASTRA OPEN

UNIVERSITY,NASHIK.

CERTIFICATECERTIFICATE This is to certify that

Mr. SACHIN PANHALE Mr. JORDAN PEGADO

has done the project work on

BALL TRACTION DRIVEBALL TRACTION DRIVEhave submitted this project report in partial

fulfillment of The requirements for the degree

of”btech(mechanical)of the University of y.c.m.o.u.

For the academic year 2010-2011

PROF.A.U.PALANGE PROF.G.P.BORIKAR(Project Guide)(Project Guide) CO-ORDINATOR,BTECH MLEP

PROGRAM YCMOU,MIT,PUNE.

(External Examiner)(External Examiner)

Acknowledgement

It gives an immense pleasure to submit this Project report

entitled BALL TRACTION DRIVE .We have tried to our level best to

Perform & represent this topic to the point framework.

We wish to express our sincere thanks with profound

gratitude to my guide PROF.A.U.PALANGE for his valuable guidance and

constant encouragement without which it would have been impossible for

group and complete this project successfully.

We would like to extend our sincere and true thanks to my

PROF.G.P.BORIKAR CO-ORDINATOR,BTECH MLEP PROGRAM YCMOU,MIT,PUNE.

and all the staff members for impairing me the best of their knowledge and

guidance.

Last but not the least, I thank all my friends for their assistance

and help.

Sachin panhale B028872Jordan pegado B024098

INDEX

SR.NO. CONTENTS PAGE NO.

1 INTRODUCTION

2 CONSTRUCTION AND WORKING

3 DESIGN

4 PROCESS SHEET

5 ADVANTAGES

6 APPLICATION

7 DISADVANTAGES

8 CONCLUSION

9 COST ESTIMATION

10 REFERENCES

CHAPTER -- 1

INTRODUCTION

INTRODUCTION

Machine tools are precise and complex machines that are produce various types, which are used to produce various types of components by metal cutting for removing the metal from a work piece, a relative motion is necessary between the tool and job. The various motion characteristics of machine tools are work motions & auxiliary motions.

WORK MOTIONS

These motions affect the process of chip removal. These are transmitted either to cutting tool or to work or both. Working motions include.

a) Primary cutting motions.b) Feed motions.

AUXILIARY MOTION

These motions include, loading and claming the job, removing finished work clamping & swiveling units etc. all these motions are non- cutting motions these should be performed as fast as possible.

DRIVES IN MACHINE TOOLS

The primary motions of machine are power driven; similarly feed motions are also power driven on small machines.

The operating cycle of machine tools, including both working and auxiliary motions and it is obtained by means of drive and definite units and mechanisms. The drive of machine tools consists of

a) Source of energy

b) Devices for transmitting power from source to operating elements ( (spindles, slides tables etc.)

Machine tools are driven by either of these drive1) group drive 2) Individual drives

Each drive is selected on its own merits, but individual drives are more advantageous. In ‘electrical drives’ the direct motor drive the machine shaft through direct coupling.

In ‘ mechanical drive’ the transmission elements include belts and chains, toothed gearing or some multi purpose variable speed transmission.

The transmission elements between the input & output shaft can perform the following functions.

a) Convert rotary motion into translator motion.b) Convert rotary motion into rotary motion.c) Convert translator motion to translator motion.

STEPPED MECHANICAL DRIVES

With a constant speed motor, there is a need for some method of varying the speed over this range( Nmax- Nmin). In order to provide for a wide range of operating speeds together with adequate torque at lower spindle speed range be covered in a number of discrete speeds; ) stepped drives)The various stepped mechanical drives are as follows;

a) Step- cone pulley driveb) All geared drives

1) Change gear system2) Clutch type drive3) Sliding gear type drive 4) Sliding key gear box

NEED FOR STEPLESS DRIVE

There are many machines and mechanical units that under varying circumstances make it desirable to be able to drive at an barely perceptible speed, an intermediate speed or a high speed.

Thus an infinitely variable ( stepless ) speed variation in which it is possible to get any desirable speed. Some mechanical, hydraulic, drives serve as such stepless drives. However the torque Vs speed characteristic of these drives do not match torque at low speeds.

Hence the need of a stepless or infinitely variable speed drive with following characteristic :-

1) Stepless or infinitely varying speed.2) Wide range of speed variation i.e. ( Nmax- Nmin).3) Shifting from one speed to another should be shock less.4) Minimum number of controls for speed changing.5) Ease of operation.

STEPLESS MECHANICAL DRIVES

Stepless or infinitely variable main and feed drives have found considerable applications in modern machine tools. Their main advantages are as follows. The possibility of setting up the optimum cutting conditions ( speed & feeds ) with higher accuracy than with a stepped drive and the possibility of changing speeds of the main drives or feeds without stopping the machine. The stepless drives are of mechanical electrical, hydraulic or combined drive. They gave their own advantages and disadvantages. The selection will depend upon purpose of machine, range ratio power required & cost.

Mechanical stepless drives of

A) Friction type.b) Positive type.

I. FRECTION TYPE STEPLESS MECHANICAL DRIVES

These drives are based on the principle the driven link contacts the driving link either directly or through some intermediate element ( roller, disc, ring) . The driven & driving elements are held tightly together and the friction force developed will cause one element to rotate when other is

rotated. If the diameter is constant on both the elements ( driving & driven ) or on at least one of them is varied then the transmission ratio of the drive will vary accordingly.There are many designs of friction type devices, which will be discussed in following sections.

A) ROLLER AND DISC DRIVE

This is a very elementary friction drive. A single control lever permits smooth variation in speed ratios over a wide range from zero. When the roller is over the recessed portion of the disc to a maximum when the roller contacts the disc at its outer end the transmission ratio being given as :

i = r/R (R being variable )

Direction of rotation can be completely reversed by bringing the friction roller into contact with the disc or either side of the recessed center portion .The roller must be mounted on splinted shaft to move it across the face of disc , while being positively driven by the shift . Drawbacks of this driver are :

a) Uneven wear of the disc b) Rapid wear of roller c) Maintaining proper pressure between the contact surfaces is another

cause of trouble .

B) FRICTION CONE WITH FLAT BELT DRIVE

The principle of this drive is the same as that of stepped cone pulley

and belt system ,except that there are no fixed steps but rather it provides the possibility of very slight changes in speed ratios over a wide range of adjustments. Adjustment of speeds is obtained by means of a belt – shifting device shown. To prevent the belt from slipping, the cone angle is usually 10o. The drive is not suitable for large powers due to flexibility of belt.

C) SREADING CONICAL PULLEY DRIVE

The distance between the pairs of driving and driven cone pulley can be changed by axially moving one member in each pair .With this the diameter of contact of belt with the driving or driven pairs of cone pulleys can be varied together to obtain different transmission ratios . Instead of V-belt a hardened metal ring as the frictional member can be used .Mechanism very effectively used in the transmission of automobile ,commonly called a Variomatic drive; Two wheelers like Kinetic Honda ,TVS- Scooty , Honda –Active use this type of drive .

D) CONICAL DISC AND FRICTION ROLLER DRIVE Friction roller arranged between spherically- shaped cones or disc on the driving and driven shafts may be inclined in different positions .This will change the radius of contact between the roller and the driving and the driven discs and there by the transmission ratio. When the axis of the top and bottom rollers coincide vertically, the speed of the driving and driven pulleys will be same . The speed of the driven shaft is transmitted to the spindle through a V-belt drive. By changing the position of the roller along the spherical of cones (driving and drive ) spindle speeds can be infinitely varied from the minimum to maximum values. The range can be 4 to 8. by combining the friction drive (Svetozorav drive ) with a 3 stage geared head stock a still wide range of infinitely variable speed can be obtained .

II )POSITIVE DRIVE

The positive infinitely variable ( PIV ) drive is a variant of , Spreading

conical pulley friction drive,)in which a chain a used in place of belt and conical faces of the alloy steel wheels are grooves . The wheels mounted on the splined shafts are free to move laterally .A control hand wheel moves the control levers about central pivots to change the ratio of the effective wheel diameters .The chain links are slideable transverse slots that from the power the transmitting teeth .A shoe mechanism ,with spring tension ,applied pressured to the slack slide of the chain to keep it in adjustment . All moving parts run in oil with automatic splash lubrication .

The range ratio of mechanical stepless drives depended upon the principle and construction of the device .It may range from about 2 to 4 to about 10 to 25 .In most cases, range ratio -4 to 6

PROBLEM DEFINITION

There are many machines and mechanical units that under varying circumstances make it desirable to be able to drive at an barely perceptible ,speed an intermediate speed or a high speed .

Thus an infinitely variable (stepless ) speed variation in which it is

possible to get any desirable speed . Some mechanical ,hydraulic ,drives serve as such stepless drives. However the torque Vs speed characteristic of these drives do not match torque at low speeds.

Hence the need of a stepless or infinitely variable speed drive with following characteristic : -

1.)Stepless or infinitely varying speed.2) Wide range of speed variation i.e. ( Nmax – Nmin).3) shifting from one speed to another should be shock less.4) Minimum number of controls for speed changing.5) Ease of operation.

CHAPTER- 2

CONSRUCTION & WORKING

HEYNAU FREE BALL TRACTION DRIVE

The heynau free ball traction drive unit consists of an input disc or cone, a single adjustable free ball, and an output friction disc or cone.

OPERATING FEATURES

1.The drive is a constant horsepower device, but can be used as an constant torque at maximum output speeds over the entire adjustment range.

2.Standard speed ratios are 5:1 or 9:1.

3. The output speeds can be up to 5400 rpm.

4. The drive is 85% efficient.

5.Speed accuracy is +/-1% of the output speed at constant load.

6. The drive is available in size 1/8hp to ½ hp.

7.Speed adjustment is permissible at rest or while running.

8. The unit can be run in either direction of rotation.

9. The output rotation is in the same direction as input.10. The input and output are offset but parallerl.

PRINCIPLE OF OPERATION

The major components of the Heynau drive are steel ball ( 1) positioned between two axially displaced hollow cone discs ( 2&3) and acts as a power transmission element.

When the load is applied the transmission ball is pulled into a triangle formed by the two hollow cone disks by an amount equal to the elastic deformation of the parts under load. Thus the contact pressure is directly.

Proportional to the output torque. Torque- dependent pressure devices are unnecessary.Clockwise or counterclockwise rotation is permissible. The output speed of the Heynau drive is infinitely variable and is achieved by adjusting the position of the steel ball b rotating the speed-setting spindle knob ( 4) . Speed setting is permissible both at rest and in motion. In the upper adjustment position. Ratio of 3 : 1 reduction is created between input and output shaft. In the lower adjustment position the ratio is 1:3 increasers. The total speed range covered is 9:1. For a speed range of 6:1, higher input horse power is possible since the output horse power is determined by the lower output speed.

The movement of the transmission ball is positively controlled when adjusting for high or low speeds. When adjusting to the lower speeds, the transmission ball takes up a position against the speed setting spindle because of its tendency to move toward the middle of the higher cones. Power must be transmitted through the unit only in the direction shown by the arrow on the outer housing. In the case of very low input speeds. A minimum amount of load must be applied at the output shaft to achieve the desired output speed. The drive may be used in any. Mounting position and can be made hermetically sealed.

CHAPTER- 3

DESIGN

DESIGN

Design consists of application of scientific principles, technical information and imagination for development of new or improvised machine or mechanism to perform a specific function with maximum economy and efficiency.

Hence an careful design approach has to be adopted. The total design work, has been split up into two parts;

SYSTEM DESIGN MACHANICAL DESIGN

SYSTEM DESIGN

System design mainly concerns with various physical constrains, deciding basic working principle, space requirements, arrangements of various components etc.

Following parameters are looked upon in system designa) Selection of system based on physical constraints. The mechanical

design has direct norm with the system design hence system is designed such that distinctions and dimensions thus obtained in mechanical design can be well fitted in to it.

b) Arrangement of various components made simple to utilize every possible space.

c) Ease of maintenance and servicing achieved by means of simplified layout that enables quick decision assembly of components.

d) Scope of future improvement.

MACHANICAL DESIGN

In mechanical design the components are listed down and stored on the basis of their procurement in two categories.

Design parts Parts to be purchased .

For designed parts detailed design is done and dimensions there obtained are compared to next dimensions which are already available in market. This simplities the assembly as well as the post production and maintenance work. The various tolerances on work are specified. The process charts are prepared and passed to manufacturing stage.

The parts to be purchased directly are selected from various catalogues and are specified so as to have case of procurement.

In mechanical design at the first stage selection of appropriate material for the part to be designed for specific application is done.

This selection is based on standard catalogues or data books;

eg:- ( PSG DESIGN DATA BOOKS ) ( SKF BEARING CATALOGUE ) etc.

APROACH TO MECHANICAL DESIGN OF ‘TWIN WORM SYSTEM’

In design the of parts we shall adopt the following approach;

Selection of appropriate material.

Assuming an appropriate dimension as per system design. Design check for failure of component under any possible

system of forces;

Our present model is an demonstrative set up in order to show the motion and power transmission capabilities of the proposed ‘ TWIN WORM SYSTEM ‘

Thus selection a drive motor as follows

DRIVE MOTOR

TYPE :- SINGLE PHASE AC MOTOR.POWER :- 1/ 15 HP ( 50 WATTS)VOLTAGE :- 230 VOLTS, 50 Hz.CURRENT : 0.5 AMPS.SPEED : - MIN= 0 rpm

MAX = 6000 rpm

Operating Speed = 4000 rpmMotor Torque

P = 2 NT ---------- 60

T = 60 x50 ---------

2 x4000T = 0.119 N-m

Power is transmitted from the motor shaft to the input shaft of drive by means of an open belt drive.Motor pulley diameter = 20 mmIP – shaft pulley diameter = 110 mmReduction ratio = 5IP_ shaft speed = 4000/5 = 800 rpmTorque at IP_ shaft = 5x 0.119 = 0.6 Nm

DESIGN OF OPEN BELT DRIVE

Motor pulley diameter = 20 mmIP_ shaft pulley diameter = 110mmReduction ratio =5Coefficient of friction = 0.23Maximum allowable tension in belt = 200 NCentre distance = 120A = 180 – sin 1) D-d)/2CA = 180 – sin 1( 110- 20)/2x200

A = 136A = 2.37Now,E /sin( 8/2) = e 0.2x2.37sin (40/2) = 4Width (b2) at base is given by b2 = 6-2 ( 4tan 20) = 3.1Area of cross section of belt = ½ { 6 +3.1} x4A= 18.2 mm2Now mass of belt/ m length = 0.23 kg/mV= nDN ( 60x1000) = 4.188m/secTc = mV2

Tc = 4.034 NT1 = Maximum tension in belt – TcT1 = 195.966 = 196 NT1/T2= e =4T2 = 49 NResult tableTension in tight side or belt ( T1)= 196 NTension in slack side of belt (T2)=49NRefer load Diagram

Ra +Rb = 245 + 12.96Ra+ Rb = 257.96 N --------- (A){ Ma = 0

So, Rb = 902.512 N -----------(B)Ra = -644.552 NMaximum bending moment = 13958.516NEquivalent torsional moment = Te = T2 +M2Te = 13971.405 NEquivalent bending moment = ½ M+ Te= 20770.48 N- mm

MATERIAL SELECTION : --

Ref.: PSG ( 1.10 & 1.12) + (1.17)

DESIGNATION ULTIMATE TENSILE STRENGTHN/mm2

YEILD STRENGTHN/ mm2

EN24 800 680

ASME CODE FOR DESIGN OF SHAFT.

Since the loads on most shafts in connected machinery are not constant, it is necessary to make proper allowance for the harmful effects of load fluctuations.

According to ASME code permissible values of shear stress may be calculated form various relation.

Fs max= 0.18 fult =0.18x800= 144 N/mm2

ORFs max = 0.3 fyt

= 0.3 x680 = 204N/mm2

Considering minimum of the above values ;

= fs max = 144 Nmm 2This is the allowable value of shear stress that can be induced in the shaft material for safe operation.

Considering failure of shaft under torsionTe= / 16{f6 d3 }D3= 16 x13791.405/ITx144D = 7.87mm

The input shaft is driven by the motor by means of an open belt pulley hence the input shaft carries an pulley at its one end which is fastened to it by means of an grub screw. Hence it should have an sliding fit on shaft. To achieve a tolerance of h6H7 on pulley we need to bore the pulley hole, and minimum hole possible using given tooling is 16mm , hence adopting the shaft diameter to be 16mm.D= 16mmCheck for bending failure of shaftMe = / 32{fs d3 }Fs act = 20770.48x32/ x163

Fs act = 51.65N < Fs allowable

Thus shaft is safe in bending

DESIGN ( SELECTION OF BALL BRG)

In selection of ball bearing the main governing factor is the system design of the drive ie; the size of the ball bearing is of major importance;Hence we shall first select an appropriate ball bearing first select an appropriate ball bearing first taking into consideration convenience of mounting the planetary pins and then we shall check for the actual life of ball bearing.

BALL BEARING SELECTION. Series 60

ISI No Brg Basic Design No. (SKF )

D D1 D D2 B Basic capacity

C N Co N25B Co2

6205 25 31 46 52 15 7100 11000

P= X Fr + Yfa.

Where ;P = Equivalent dynamic load, ( N)X = Radial load constantFr = Radial load (H)Y = Axial load contactFa = Axial Load (N)In our case ;Radial load Fr = Ra = 644.52 NAxial Load ( Fa)Fa = OP x Fr

= 1x 644.52+O= 644.52 N

L =(C/P)pHere p =3 for single row ball bearingsL = 60n Lh =60x1000 x800 = 48 mrev

--------- ---------------- 10 10

C = 2342AS; required dynamic of bearing is less than the rated dynamic capacity of bearing is safe.

CHAPTER 4

PROCESS SHEET

Part Name : L. H. BERING HOUSE Material Specification : - EN9 Raw material size : - DIA 120 x50 Quantity – 02 No’sSr NO

Operation Jigs & Fixtures

M/c Tools

Cutting Tools

Measuring Instrument

Setting Time

M/c Time

Total time

1) Clamp stock

3 jaw chuck

Lathe - - 15 - 15

2) Facing b/s side to 40mm

----,,----

---,,----

Facing tool

Vernier - 40 40

3)

Drilling 0 15mm through thickness (1 No’s)

---,,-----

----,,---

Twist drill

10 15 25

4)

Boring o41mm thickness (1No’s)

----,,----

----,,---

Boring tool

Bore gauge

15 25 40

5) Counter boring o 47mm through thickness 35 (1No’s)

----,,----

----,,---

- - 5 15 20

6) Counter boring o48mm through thickness21

----,,----

----,,--

5 15 20

(1No’s) 7) Counter

boring o 52mm through thickness 15 (1No’s )

-----,,---

----,,--

5 15 20

8) Od turning dia 70mm through 21 mm

----,,----

----,,--

5 20 25

9) Drilling dia 8.5 mm holes, 3 no’s on 96pcd

-----,,---

Drilling M / c

15 24 39

PART NAME :- RH_BEARING HOUSING Material specification :- EN9 Raw material size :- DIA 120x 50 Quantity – 02 No’sSr No

Operation

Jigs and Fixtures

M / c Tool

Cutting Tool

Measuring Instrument

Setting Time

M /c Time

Total Time

1 Clamp stock

3 Jam chuck

Lathe - - 15 - 15

2 Facing b / s sides to 40 mm

----,,----

----,,-- Facing tool

Vernire - 40 40

3 Drilling o 15 mm through thickness

----,,----

----,,-- Twist drill

10 15 25

4

Boring o 41 mm through thickness (1 No’s )

----,,----

----,,-- Boring tool

Bore gauge

15 25 40

5 Counter boring o 47 mm through thickness 35 (1 No’s)

-----,,----

----,,-- 5 15 20

6 Counter boring o

----,,----

----,,-- 5 15 20

48 mm through thickness 21 (1No’s)

7 Counter boring o 52 mm through thickness 15 ( 1 No’ s )

-----,,---

----,,-- 5 15 20

8

Od turning dia 70 mm through 21 mm

----,,-----

----,,-- 5 20 25

9

Drilling dia 8.5 mm holes ,3 no’ on 96 pcd

-----,,----

Drilling M /c

15 24 39

Part Name :- DIAL BARREL Material Specification Raw material size :- 0 70 x 50 Quantity - 01 No’s Sr No

Operation

Jigs and Fixtures

M /c Tool

Cutting Tool

Measuring Instrument

Setting Time

M /c Time

Total Time

1 Clamp stock

3-Jaw chuck

Lathe

- - 25 - 25

2 Facing one side

---,,---- ,, - - - 15 15

3 Turning OD o 66m through 38 m length

----,,---- ----,,--

Turning tool

Vernier 10 22 32

4 Drilling o 15 hole through thickness

- Twist drill

10 15 25

5 Boring o 44 through out length

- - Boring tool

----,,------ 10 20 30

6 Counter boring o 50

- 10 35 40

Through 34 length

7 Facing other side to total length 38

Facing tool

10 15 25

8 Chamfer 1 x 45 degree

Crank Tool

5 5 10

Part Name :- DIAL Material Specification :- EN 9 Raw material size :- 0 80x50 Quantity - 01No’s Sr No

Operation

Jigs and Fixtures

M /c Tool

Cutting Tool

Measuring Instrument

Setting Time

M /c Time

Total Time

1 Clamp Stock

3-Jaw chuck

Lathe

- - 25 - 25

2 Facing one side

-----,,----

,, - - - 15 15

3 Turning OD o 70 m through 40 mm length

----,,-----

----,,--

Turning tool

Vernier 10 22 32

4 Drilling o 15 hole through thickness

- Twist drill

10 15 25

5 Boring o 58 through out length

- - Boring tool

- 10 20 30

6 Counter boring o

- 10 35 45

65 Through 3.5 length

7 Facing other side to total length 40

Facing tool

10 15 25

8 Taper turning as per dwg

Crank Tool

10 15 20

Part Name :- CARRIER Material Specification :-EN 9 Raw material Size :-HEX 70 AF X 70 Quantity - 01 No’s Sr No

Operation

Jigs and Fixtures

M /c Tool

Cutting Tools

Measuring Instrument

Setting Time

M /c Time

Total Time

1 Clamp stock

3-Jaw Chuck

Lathe

- - 25 - 25

2 Facing one side

----,,-----

,, - - - 15 15

3 Turning OD o 65 m through 40 m length

-----,,----

----,,--

Turning tool

Vernier 10 22 32

4 Turning OD o 48 m through 36.5 mm length

----,,-----

----,,--

Turning tool

Vernier 10 22 32

5 Drilling o 15 hole through thickness

- - Twist drill

10 15 25

6 Boring o 34 through 43 length

- - Boring tool

-----,,---- 10 20 30

7 Counter 10 35 45

boring o 18 Through 10 length

7 Internal Threading m 36x 2 pitch

Threading tool

30 45 75

8 Chamfer 5 x 45 degree

Crank Tool

5 5 10

CHATER – 5

ADAVANTAGES

ADVANTAGES

1) Properly balanced power transmission.2) Easy to maintain proper pressure between the contact surfaces thereby

resulting in trouble free operation. 3) Multiple speeds can be obtained; where as regular clutches are of ON – OFF type Where only one speed is available.

4) Infinitely variable speed available over a given range.

5) Ease of operation; the speed changes are gradual , with any shock.

6) Singular control :- Entire range of speeds is covered by a single knob control .

7) Low cost.

8) Compact size.

CHAPTER 6

APPLICATIONS

1) Speed drives for machine tools spindles :-Machine tool spindle are required to be driven at various speeds depending upon the size of work and material to be cut in such cases the gear less variable speed reducer can be used along with all geared head stock to give an infinitely variable speed condition.

2) By combination the duplex friction drive and a three stage all gear head stock a Still wide range of speed can be obtained for the main spindle of lathe.

3) Feed drives for machine tool slides. Machine tool slides can be moved at different

Speeds to impart feeding motion to the cutting tool.

4)Variable speed drive for conveyors in assembly line and automatic assembly

Plants.

5) Variable speed drive in automatic transfer lines and place robotic devices.

CHAPTER 7

CONCLUSION

The ball traction drive has been completed successful. It was associated with

a lot of excitement right from beginning. Many problems were faced during

design and in manufacturing. But all of them were successfully overcome,

with help of our project guide and various persons from different industries.

We got a great deal of experience during designing and

manufacturing of our project. Also we got a lot of practical experience.

While working on this project Especially discussion with our project guide

various persons form different industries. Workers and our friends,

regarding. Our project proved to be successful. they helped us to a great deal

in understanding the problem and way to tackle them.

This project was great experience, which will surely help us in

future career.

CHATER- 8

COST ESTIMATION

** LIST OF MATERIALS :-

S . N

DESCRIPTION QTY MATERIAL

1 LP-CONE –SHAFT

01 EN24

2 OP-CONE-SHAFT

01 EN24

3 LH- BRG-HOUSING

01 EN9

4 RH-BRG-HOUSING

01 EN9

5 LH-CASING PLATE

01 EN9

6 RH-CASING-PLATE

01 EN9

7 TOP-CASING-PLATE

01 EN9

8 BALL-HOLDER 04 EN99 CARRIER NUT 01 EN910 CARRIER 01 EN911 DIAL 01 EN912 DIAL BARREL 01 EN9

13 BRG 6205-ZZ 02 STD14 BRG 6204-ZZ 02 STD15 GM 01 PB16 KEY 6x3x60 01 STD17 BOLTS M8x30 06 STD18 BELT (6x500) 01 STD19 MOTOR 01 STD20 PULLEY 01 STD21 BALL 01 STD

** RAW MATERIAL COSTThe total raw material cost as per the individual material and their corresponding rates per kg is as follows. Total raw material cost = RS 3200 /-

** MACHINING COSTOPERATION RATE RS /HR TOTAL TIME

HRSTOTAL COST RS /-

LATHE 60 32 1920MILLING 55 14 720DRILLING 40 3.6 144TAPPING RS 3 / -per hole 16 48

TOTAL 2880 TOTAL MACHINING COST = RS 2880 /-**MISCELLAEOUS COSTS OPERATION COST (RS) Sawing 160Gas cutting 80Bench work 40 TOTAL 280COST OF PURCHASED PARTS:-

SR NO.

DESCRIPTION QTY COST

1. VEE BELT 01 75

2. BOLTS -- 353. ELECTRIC MOTOR 01 10504. BALL 02 7005. ELECTRONIC SPEED

VARIATORThe cost of purchase parts = Rs 1910/-

TOTAL COST

TOTAL COST = Raw material Cost + Machine Cost + Miscellaneous Cost + cost of Purchased Parts + Overheads = Rs. 8300/-

Hence the total cost of machine = Rs. 8300 / -

CHAPTER 9

BIBLIOGRAPHY

1. MACHINE DESIGN PRACTICE

- R.S KHURMI

2. PSG DESIGN DATA HANDBOOK.

3. SOME MECHANICAL CHARACTERS OF

AGAVE FIBRES

- NUTMAN

4. THEORY OF MACHINE

- R.S. KUURMI & J.K. GUPTA

5. PRODUCTION ENGINEERING

- P. C. SHARMA.