Shafts
round
Axle
rotates
Transmits power motion
spring columb
linkage
Beam
Design for strength and or Rigidity
Find critical Area
enangEs tJdE9stnYng
I.EE
Deflection can be an issue
Any time you have a change In dimensions like this (as depicted below) …then you will have a stress
consentration at that point. The sharper the curve the higher the stress consentration.
8
Ehoulder
Fillet
Start of Swanbom lecture
_f
d
_RERt
lle Ba___
serotonin
tffftttt
constant
carriestorque
stPn takenplane
In
Ty52000ps
rotors
MCMANN
Sut 93700ps
Simmons
4 193 4 Fema
3
Fita
4
fg.fm i3 KfsgiyTm
Static Analysis to find unknown forces Applied to the shaft
Maxis 70lb 4in F 1in
F 280lb
O
EMA 7016 9in 280lb 24in RB 34in
Fy RA 70lb 28016117916 0
0
RB 179lb
RA
31lb
calculating the Fully corrected Endurance limit
Se Se Ka Kb Kc Kd ke Kf
Ka surfacefactor
Kpisize factor
cold drawn
ka 27193.7
0265
0.8107
Kc loadingfactor
Don't use we used DEinstead
Kd Tempfactor
Room temp
Kd 1
For delin
0.10
0.879
0.87911
Kp
For d 0.75in
ky 0.879 0.755010 0.9065
Ke reliability Factor
95 reliability
Ke 0.868
computing se
ÉÉdg 93.7Ksi 0.8107 0.879 1 0.868
Se 28.98Ksi
For d 0.75in
Se 0.5 93.7Ksi 08107 0.9605 1 0.868
Se 29 8851451
Finding the Fatigue stress concentrationFactors
For torsion
For d 0.75in
Kts 1.75
iommr.org
gplyfpy
becausethereis no T toright
For BendingMoment
1515
Ford 0.75
kt 2.2
if.is scz n i.ais
3
For d 0.75
Kf 1 0.752.2 1 1.9
Drawing a shear and moment diagram to find bending moments
70lb
17916
28016
3116
101lb
31lb
179lb
1790in b
ftp.gtsgsgimategentssshehtchfncinding
Pñ nib ma
m
because itsFully reversed
00
Findingbendingmoments and torques that cause midrange and alternating stresses
Mm O
Ma 1790in lb
Tm 280in lb
Ta 0
Computing Factor of safety againstfatigue For infinite life using ASME
4 193 4 fj
a
3
Fgta 4
fg.fm i3 kfsgyTm
For d 1
i
ns 4
91
198
n 0.803
For d 0.75
in nco inss
4
9
n 0.364
sit failure
98 1
1.68388ps b