1. Presentation on Machine drawing &design
Prepared By :-
Neeraj
(Mech Engg. Deptt. Gpes Meham)

2. INTRODUCTION
Machine design may be defined as the creation of new and better machines.
Existing machine are also made to improve.
TYPES OF MACHINE DESIGN:
New design
Development design
Adapative design

3. NECESSITY OF MACHINE DESIGN
To create new and better machines
For faster production
For automation of industries
For innovation of new products
To convert existing design into new design

4. SCREW THREAD A screw thread is formed by cutting helical grooves on a cylinderical surface

5. Design of Shaft
A shaft is a rotating member usually of circular cross-section (solid or hollow), which transmits power and rotational motion.
Machine elements such as gears, pulleys (sheaves), flywheels, clutches, and sprockets are mounted on the shaft and are used to transmit power from the driving device (motor or engine) through a machine.

6. COMBINED BENDING AND TORSION LOADS ON SHAFT: SHAFT CARRYING GEARS.
From power and rpm find the torque (T), which gives rise to shear stress.
From Torque (T) and diameter (d), find Ft = 2T/d. From Ft and pressure angles of gears you can find Fr and Fa.
Fr and Ft are orthogonal to each other and are both transverse forces to the shaft axis, which will give rise to normal bending stress in the shaft. When shaft rotates, bending stress changes from tensile to compressive and then compressive to tensile, ie, completely reversing state of stress.
Fa will give rise to normal axial stress in the shaft.

7. Power, toque & speed For linear motion: Power = F.v (force x velocity)
For rotational motion
Power P = Torque x angular velocity
= T (in-lb).w (rad/sec) in-lb/sec
= T.(2 p n/60) in-lb/sec [n=rpm]
= T.(2 p n/(60*12*550)) HP [HP=550 ft-lb/sec]
= T.n/63,025 HP
or, T= 63,025HP/n (in-lb), where n = rpm
Similarly, T= 9,550,000kW/n (N-mm), where n = rpm

8. Shear (t) and bending (s) stresses on the outer surface of a shaft, for a torque (T) and bending moment (M)
For solid circular section:
For hollow circular section:

9. Loads on shaft due to pulleys
Pulley torque (T) = Difference in belt tensions in the tight (t1) and slack (t2) sides of a pulley times the radius (r), ie
T = (t1-t2)xr
Left pulley torque
T1 = ( )x380=1,710,000 N-mm
Right pulley has exactly equal and opposite torque:
T2 = ( )x380=1,710,000 N-mm
FV2
Bending forces in vertical (Fv) and horizontal (FH) directions:
At the left pulley: FV1=900N; FH1= = 9900N
At the right pulley: FV2= =9900N; FH2=0

10. PRINCIPAL NORMAL STRESSES AND MAX DISTORTION ENERGY FAILURE CRITERION FOR NON-ROTATING SHAFTS
The stress at a point on the shaft is normal stress (s) in X direction and shear stress (t) in XY plane.
From Mohr Circle:
Max Distortion Energy theory:
Putting values of S1 & S2 and simplifying:
This is the design equation for non rotating shaft

11. DESIGN OF ROTATING SHAFTS AND FATIGUE CONSIDERATION
The most frequently encountered stress situation for a rotating shaft is to have completely reversed bending and steady torsional stress. In other situations, a shaft may have a reversed torsional stress along with reversed bending stress.
The most generalized situation the rotating shaft may have both steady and cyclic components of bending stress (sav,sr) and torsional stress (tav,tr).
From Soderberg’s fatigue criterion, the equivalent static bending and torsional stresses are:
Using these equivalent static stresses in our static design equation, the equation for rotating shaft is:

12. Bearing mounting considerations and stress concentration

13. Various types of keys for transmitting torque

14. Other common types of keys

15. Cams
Cams are used to convert rotary motion to oscillatory motion (almost always) or oscillatory motion to rotary motion (rarely)
For high speed applications – example, internal combustion engines

16. Cam types
Plate cam
Wedge cam
Barrel cam
Face cam  y

17. Followers
Knife-edge
Flat-face
Roller
Sperical-face

18. 3. Motion of the follower
As the cam rotates the follower moves upward and downward.
The upward movement of follower is called rise (Outstroke)
The downward movement is called fall (Returnstroke).
When the follower is not moving upward and downward even when the cam rotates, it is called dwell.

19. 3.1 Types of follower motion
Uniform motion ( constant velocity)
Simple harmonic motion
Uniform acceleration and retardation motion
Cycloidal motion

20. a) Uniform motion (constant velocity)

21. a) Uniform motion (constant velocity)
Displacement diagram
Since the follower moves with uniform velocity during its rise and fall, the slope of the displacement curve must be constant as shown in fig

22. b) Simple Harmonic motion

23. b) Simple harmonic motion
Since the follower moves with a simple harmonic motion, therefore velocity diagram consists of a sine curve and the acceleration diagram consists of a cosine curve.

24. c) Uniform acceleration and retardation
Since the acceleration and retardation are uniform, therefore the velocity varies directly with time.

25. d) Cycloidal motion

26. CAM Profile

27. Gears
A body of circular shape having uniform small width and teeth of uniform formation on its outer circumferential surface

28. Type of Gears
Spurs
Helical
Bevel
And Worm Gears

29. Spur Gears
Are used in transmitting torque between parallel shafts

30. Helical Gears
Are used in transmitting torques between parallel or non parallel shafts, they are not as noisy as spur gears

31. Fig. 13.2

32. Bevel Gears
Are used to transmit rotary motion between intersecting shafts
Teeth are formed on conical surfaces, the teeth could be straight or spiral.

33. Worm Gears
Are used for transmitting motion between non parallel and non transmitting shafts, Depending on the number of teeth engaged called single or double. Worm gear mostly used when speed ratio is quiet high, 3 or more

34. Nomenclature Smaller Gear is Pinion and Larger one is the gear
In most application the pinion is the driver, This reduces speed but it increases torque.

35. Internal Spur Gear System

36. pitch circle, theoretical circle upon which all calculation is based
p, Circular pitch, p the distance from one teeth to the next, along the pitch circle. p=πd/N
m, module=d/N pitch circle/number of teeth
p= πm
P, Diametral Pitch P=N/d
pP= π

37. Angle Φ has the values of 20 or 25 degrees. Angle 14
Angle Φ has the values of 20 or 25 degrees. Angle 14.5 have been also used.
Gear profile is constructed from the base circle. Then additional clearance are given.

38. Standard Gear Teeth Item 20o full depth 20o Stub 25o full depth
Addendum a
1/P
0.8/P
Dedendum
1.25/P
Clearance f
0.25/P
0.2/P
Working depth
2/P
1.6/P
Whole depth
2.25/P
1.8/P
Tooth thickness
1.571/P
Face width
9/P<b<13/P

39. THANK YOU