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All figures taken from Design of Machinery, 3 rd ed. Robert Norton 2003 MENG 372 Chapter 9 Gears.

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Presentation on theme: "All figures taken from Design of Machinery, 3 rd ed. Robert Norton 2003 MENG 372 Chapter 9 Gears."— Presentation transcript:

1 All figures taken from Design of Machinery, 3 rd ed. Robert Norton 2003 MENG 372 Chapter 9 Gears

2 Rolling Cylinders Gear analysis is based on rolling cylinders External gears rotate in opposite directions Internal gears rotate in same direction

3 Gear Types Internal and external gears Two gears together are called a gearset

4 Fundamental Law of Gearing The angular velocity ratio between 2 meshing gears remains constant throughout the mesh Angular velocity ratio (m V ) Torque ratio (m T ) is mechanical advantage (m A ) Input Output

5 Involute Tooth Shape Shape of the gear tooth is the involute curve. Shape you get by unwrapping a string from around a circle Allows the fundamental law of gearing to be followed even if center distance is not maintained

6 Meshing Action

7 Contact Geometry Pressure angle (  ): angle between force and motion

8 Fundamental Law of Gearing The common normal of the tooth profiles, at all contact points within the mesh, must always pass through a fixed point on the line of centers, called the pitch point

9 Change in Center Distance With the involute tooth form, the fundamental law of gearing is followed, even if the center distance changes Pressure angle increases

10 Backlash Backlash – the clearance between mating teeth measured at the pitch circle Whenever torque changes sign, teeth will move from one side of contact to another Can cause an error in position Backlash increases with increase in center distance Can have anti-backlash gears (two gears, back to back)

11 Gear Tooth Nomenclature Circular Pitch, p c =  d/N Diametral Pitch (in 1/inch), p d =N/d=  /p c Module (in mm), m=d/N

12 Interference and Undercutting Interference – If there are too few pinion teeth, then the gear cannot turn Undercutting – part of the pinion tooth is removed in the manufacturing process For no undercutting  (deg) Min # teeth

13 Gear Types Spur Gears Helical Gears (open or crossed) Herringbone Gears Worm Gears Rack and Pinion Bevel Gears

14 Spur Gears Straight teeth Noisy since all of the tooth contacts at one time Low Cost High efficiency (98- 99%)

15 Helical Gears Slanted teeth to smooth contact Axis can be parallel or crossed Has a thrust force Efficiency of 96-98% for parallel and 50-90% for crossed

16 Crossed Helical Gears

17 Herringbone Gears Eliminate the thrust force 95% efficient Very expensive

18 Rack and Pinion Generates linear motion Teeth are straight (one way to cut a involute form)

19 Worm gear has one or two teeth High gear ratio Impossible to back drive 40-85% efficient Worm Gears

20 Bevel Gears Based on rolling cones Need to share a common tip

21 Other Gear Types Noncircular gears – give a different velocity ratio at different angles Synchronous belts and sprockets – like pulleys (98% efficient)

22 Simple Gear Trains Maximum gear ratio of 1:10 based on size constraints Gear ratios cancel each other out Useful for changing direction Could change direction with belt

23 Compound Gear Trains More than 1 gear on a shaft Allows for larger gear train ratios

24 Compound Train Design If N 2 =N 4 and N 3 =N 5 Reduction ratio 2 stages Will be used to determine the no. of stages given a reduction ratio

25 Compound Train Design Design train with gear ratio of 180:1 Two stages have ratio too large Three stages has ratio At 14 teeth actual ratio is OK for power transmission; not for phasing Pinion Teeth* ratioGear teeth

26 Compound Train Design: Exact RR Factor desired ratio: 180=2 2 x3 2 x5 Want to keep each ratio about the same (i.e. 6x6x5) 14x6=84 14x5=70 Total ratio We could have used: 180=2x90=2x2x45=2x2x5x9=4x5x9 or 4.5x6x(20/3) etc.

27 Manual Transmission

28 Manual Synchromesh Transmission Based on reverted compound gears

29 Reverted Compound Train Input and output shafts are aligned For reverted gear trains: R 2 +R 3 =R 4 +R 5 D 2 +D 3 =D 4 +D 5 N 2 +N 3 =N 4 +N 5 Gear ratio is Commercial three stage reverted compound train

30 Design a reverted compound gear train for a gear ratio of 18:1 18=3x6 N 3 =6N 2, N 5 =3N 4 N 2 +N 3 =N 4 +N 5 =constant N 2 +6N 2 =N 4 +3N 4 =C 7N 2 =4N 4 =C  Take C=28, then N 2 =4, N 4 =7  This is too small for a gear! Choose C=28x4=112 (say) N 2 =16, N 3 =96, N 4 =28, N 5 =84

31 Planetary or Epicyclic Gears Conventional gearset has one DOF If you remove the ground at gear 3, it has two DOF It is difficult to access  3

32 Planetary Gearset with Fixed Ring Planetary Gearset with Fixed Arm

33 Planetary Gearset with Ring Gear Output Two inputs (sun and arm) and one output (ring) all on concentric shafts

34 Different Epicyclic Configurations Gear plots are about axis of rotation/symmetry Axis of symmetry Sun (external) Ring (internal) bearing teeth

35 Compound Epicycloidal Gear Train Which picture is this?

36 Tabular Method For Velocity Analysis Basic equation:  gear =  arm +  gear/arm Gear ratios apply to the relative angular velocities Gear#  gear =  arm  gear/arm Gear ratio

37 Example Given: Sun gear N 2 =40 teeth Planet gear N 3 =20 teeth Ring gear N 4 =80 teeth w arm =200 rpm clockwise w sun =100 rpm clockwise Required: Ring gear velocity w ring

38 Gear#  gear =  arm +  gear/arm N 2 =40, N 3 =20, N 4 =80 w arm = -200 rpm (clockwise) w sun = -100 rpm (clockwise) Tabular Method For Velocity Analysis Sign convention: Clockwise is negative (-) Anti-clockwise is positive(+) Gear ratio w 4 = rpm

39 Tabular Method For Velocity Analysis N 2 =40, N 3 =20, N 4 =30, N 5 =90  arm =-100,  sun =200 Gear#  gear =  arm  gear/arm Gear ratio Gear#  gear =  arm +  gear/arm Gear ratio # # # #

40 Equation Method For Velocity Analysis N 2 =40, N 3 =20, N 4 =30, N 5 =90  arm =-100rpm,  sun =200


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