lecture 17 shaft loading.pdf
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shaft loadingTRANSCRIPT
Shaft LoadingShaft Loading
Lecture 17Lecture 17
Engineering 473Engineering 473Machine DesignMachine Design
Shaft Design IssuesShaft Design Issues
Shafts are one of the most commonly Shafts are one of the most commonly encountered machine components.encountered machine components.
MaterialMaterial
C
IC
e
RKS
q
SS
yt
ut
EnvironmentEnvironmentTemperature
CorrosionMagnetic
LoadsLoadsStationaryRotating
Press FitsKeywaysSplines
Bearings
InterfacesInterfaces
AssemblyAssembly
StiffnessStiffnessTolerancesTolerances
Mott, Fig. 5-1
ShaftShaft: Rotating machine elementthat transmits power.
Parallel Shaft Gear BoxParallel Shaft Gear Box
Shaft design spans most topics taught in a Machine Design Course.
Mott, Fig. 15-7
Design Detail Needed to Design Detail Needed to Specify a ShaftSpecify a Shaft
Mott, Fig. 15-5
Significant detail is required to completely specify the geometry needed to fabricate a shaft.
Common Shaft Common Shaft Loading MechanismsLoading Mechanisms
Spur GearsSpur Gears Unbalanced MassUnbalanced Mass
Helical GearsHelical GearsSpiral Bevel GearsSpiral Bevel Gears Belt DrivesBelt Drives
Chain DrivesChain Drives
Spur Gear LoadsSpur Gear Loads
tanφWW2
DTW
nP63,000T
tr
t
⋅=
=
⋅=
[ ][ ]
[ ][ ]
angle pressureφindiameter pitch Dlbin ueshaft torqTrpm speed rotationaln
hppower dtransmitteP
≡≡
⋅≡≡≡
Mott, Fig. 12-3
Helical Gear LoadsHelical Gear Loads
Mott Fig’s 10-3 & 10-4(a)
Helical Gear LoadsHelical Gear Loads(Continued)(Continued)
Mott Fig’s 10-4(a)
force AxialWforce RadialW
force dTransmitteWforce normalResultant W
angleHelix ψangle pressure Transverseφ
angle pressure Normalφ
x
r
t
n
t
n
≡≡≡≡
≡≡≡
cosψtanφtanφ tn ⋅=
Helical Gear LoadsHelical Gear Loads(Continued)(Continued)
Mott Fig 10-4
Helical Gear LoadsHelical Gear Loads(Continued)(Continued)
ψtanWW
ψ /cosφtan WW
2DTW
nP63,000T
tx
ntr
t
⋅=
⋅=
=
⋅=
Mott Fig 10-4
Chain Drive LoadsChain Drive Loads
Mott Fig 12-4
θ
Belt Drive LoadsBelt Drive Loads
Mott, Fig. 12-5
Net Driving ForceNet Driving Force
2DTF
FFF
n
21n
=
−=
21b FFF +=Total Bending ForceTotal Bending Force
Belt Drive LoadsBelt Drive Loads(Bending Force)(Bending Force)
Net Driving ForceNet Driving Force
2DTF
FFF
n
21n
=
−=
21b FFF +=Total Bending ForceTotal Bending Force
3.0FF
5.0FF
2
1
2
1
=
=
Tension RatioTension Ratio
(V-belts)
(Flat-belts)nB
nB
22
22
22
22
21
21
n
B
F 0.2FF 5.1F
2.0F3FF3FC
5.1F5FF5FC
FFFF
FFC
==
=−+=
=−+=
−+==
(V-belts)
(Flat-belts)
(V-belts)(Flat-belts)
Stationary LoadsStationary Loads
1F
1F
1F
1F
2F
2F
2F
2F
Bending Stresses Due to Bending Stresses Due to Stationary LoadsStationary Loads
3
2
32b
32b
33
23
22
32b
MM-θ tan
0Iθsin rM
Iθ cos rM
θσ
Iθ cosr M
Iθsin r Mσ
IcM
IcMσ
=
=/
/+/
/=∂∂
−=
−=
2M
3M
θ
3
2
θsin r cθ cosr cIII
3
2
3322
==
==
2c3c Eq. 1
Eq. 2
Bending Stresses Due to Bending Stresses Due to Stationary LoadsStationary Loads
2M
3M
θ
3
22c
3c
MMθ cos
MMθsin
θ cosθsin
MM
MM
θtan
2, Eq. with Combining
MMM
3
2
3
2
23
22
=
−=
=−
=
+=
3
2
32b
MM-θtan
Iθ cosr M
Iθsin r Mσ
=
−= Eq. 1
Eq. 3
Eq. 4Eq. 2
Bending Stresses Due to Bending Stresses Due to Stationary LoadsStationary Loads
2M
3M
θ
3
22c
3c
Iθ cosr M
Iθsin r Mσ 32
b −= Eq. 1
MMθ cos
MMθsin
MMM
3
2
23
22
=
−=
+= Eq. 3
Eq�s 4
Combining Eq�3 1,3, and 4
IrMM
σ
IrM
IrMσ
Iθ cosr M
Iθsin r Mσ
23
22
b
23
22
b
32b
⋅+−=
−−=
−=
Bending Stresses Due to Bending Stresses Due to Stationary LoadsStationary Loads
IrMM
σ23
22
maxb,
⋅+=
IrMM
σ23
22
minb,
⋅+−=
Mott, Fig. 5-3(e)
Torsional Torsional Stresses Due to Stresses Due to Stationary LoadsStationary Loads
2M
3M
3
2
1M
JrMτ 1=
r
time
τ
The torsional stress at a point will be constant under steady state conditions.
Axial Stresses Due to Axial Stresses Due to Stationary LoadsStationary Loads
Helical, worm, and spiral gears will generate axial loads in the shaft. Under steady state conditions, the axial stress from these loads will be constant.
AWσ x
x =
Mott Fig 10-4
Unbalanced Mass LoadsUnbalanced Mass Loads
Bending stresses in a shaft due to in-balance loads are complicated by whether the rotational speed is lower or higher than the critical speeds of the shaft. In practice, the in-balance loads are minimized by balancing the shaft and attached components as a system. Rotordynamics theory is required if the magnitudes of the stresses at a particular operating speed is required.
Synchronous WhirlSynchronous Whirl(Due to Unbalanced Mass)(Due to Unbalanced Mass)
Thomson, Fig. 3.4-2
( )( ) ( )222
2
scωmωk
φ-ωtcosmeωx+−
=( )
( ) ( )222
2
scωmωk
φ-ωtsinmeωy+−
=
( ) ( )222
22s
2s
cωmωk
meωyxOS+−
=+= 2mωkcωφtan
−=
φe
m=unbalanced mass
AssignmentAssignment(Problem 1)(Problem 1)
The shaft rotating at 550 rpm carries a spur gear B having 96 teeth and a diametral pitch of 6. The teeth are of the 20o, full-depth, involute form. The gear receives 30 hp from a pinion directly above it.
Compute the torque delivered to the shaft and the tangential and radial forces exerted on the shaft by the gear.
Mott, Fig. 12-20
AssignmentAssignment(Problem 2)(Problem 2)
Mott, Fig. 12-21
The shaft rotating at 200 rpm carries a 20-in-diameter flat-belt pulley at A that receives 10 hp from below.
Compute the torque delivered by the pulley to the shaft and the force exerted on the shaft by the pulley.
AssignmentAssignment(Problem 3)(Problem 3)
The shaft is rotating at 650 rpm and receives 7.5 hp through a flexible coupling. The power is delivered to an adjacent shaft through a single helical gear B having a normal pressure angle of 20o and a helix angle of 15o.
(a) draw free-body diagrams for the shaft in both the vertical and horizontal planes, (b) find the magnitude of the forces shown, (c) draw the shearing force and bending moment diagrams for the shaft in both planes.
DB=4.141 in
Mott, Fig. 12-29
AssignmentAssignment(Problem 4)(Problem 4)
The shaft rotating at 480 rpm carries a 10-in-diameter chain sprocket at C that receives 11 hp from a mating sprocket below and to the left as shown.
Compute the torque delivered to the shaft by the sprocket and the total force exerted on the shaft by the sprocket. Resolve the force into its horizontal and vertical components, and show the net forces acting on the shaft at C in the vertical and horizontal directions.
Mott, Fig. 12-22