Flywheel Problem
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Transcript of Flywheel Problem
Flywheel Problem
The Second Tutorial
Finding acceleration and velocity
xex
yey
r
r = xex+yey = rer
er=cosθex+sinθey
ereθ
x
y
z
v = d/dt(rer)
a=d/dt(d/dt(rer))
Finding acceleration and velocity
v= r*(-sinθ*(dθ/dt) ex+cos θ*(dθ/dt)ey ) (1)
v=d/dt(rer)=r*d/dt (cosθex+sinθey)
Now recall that:
• eθ= (cosθex - sin θey)
• ω=(dθ/dt)
Substitution into (1) gives the form:
v=ωr eθ
Now a=dv/dt= d/dt(ωr eθ ) = ωr*d/dt(eθ)
(2)
v=ωr eθ
This becomes: a=- ω2r er
Kinetic Energy
K=(1/2)I*ω2 where I = ∫r2dm I= ∫ ρ r2dV = ∫∫∫ρ r2 dtdrdθ = (2πρtR4)/4
dθ=2πrdr ∫dt=t, thickness
Substitution gives:
K=(1/4) πρtR4ω2
Material consideration
Yield- At high speeds centrifugal forces cause tensile strength Material needs to be designed resistant to these
stresses Young’s modulus and Possion’s ratio must be
accounted for in design
Stress-Strain relations
• Assuming plane stress t<<R
• Use Strain-Displacement relationships given:ur=u(r), uz, uθ=rωt
εrr=d/dθ(ur), εθθ=(1/r)d/dθ(uθ) + ur/r, εzz=d/dz (uz)
εθr= (1/2)(d/dz(uθ) +r-1d/dθ(uz)-uθ/r)εθz=(1/2)(d/dz(uθ)+r-1d/dθ(uz))εrz=(1/2)(d/dr(uz)+d/dz(ur))
Stress-Strain relationsSimplifying we find that:
εθr= (1/2)(d/dz(uθ) +r-1d/dθ(uz)-uθ/r) = 0εθz=(1/2)(d/dz(uθ)+r-1d/dθ(uz)) = 0εrz=(1/2)(d/dr(uz)+d/dz(ur)) = 0
εrr=d/dθ(ur), εθθ=ur/r, εzz=d/dz (uz)
Stress-Strain relations
σθz = σrz = σrθ = 0
Using the governing Stress-Strain relation:
σij= (E/(1+ν) [εij + (v/(1-2v))(Σ εkk)δij]
σzz=(E/(1-v2))(εrr+vεθθ) = 0 (from assumption)
σθθ=(E/(1-v2))(vεrr+εθθ)
σrr=(E/(1-v2))(εrr+vεθθ)
Equation of Motion for ur
Since looking for ur use the following Equation of Motion:
d/dr(σrr)+r-1d/dθ(σrθ)+d/dz(σrz)+(1/r)(σrr- σθθ)=ρd2/dt2(ur)
(ignores body force ρbr)
Using the stresses derived earlier we can simplify to the following:
d/dr(σrr)+(1/r)(σrr- σθθ)=ρd2/dt2(ur)= -ρω2r
d2/dr2(ur)+(1/r)(d/dr(ur))- (ur)/r2= -[ρω2r(1-v2)]/E (3)
Equation of Motion for ur
d2/dr2(ur)+(1/r)(d/dr(ur))- (ur)/r2= -[ρω2r(1-v2)]/E (3)
This equation will solve for ur. But first re-write using reverse chain rule:
d/dr[(1/r)(d/dr(urr))]= -[ρω2r(1-v2)]/E
Integrating yields the solution:
ur=Ar+Br-1-[((1-v2)/8E)ρω2r3
Stress field Using the stress-strain and the strain-
displacement relations derived earlier
σrr=(E/(1-v2))(εrr+vεθθ) σθθ=(E/(1-v2))(vεrr+εθθ)
εrr=d/dθ(ur), εθθ=ur/r, εzz=d/dz (uz)
Plug into new equation for ur setting boundary conditions:
σr(R)=0 (no mass rotating and pulling on outside)ur(0)=0 no displacement in the r direction at center
Stress field After solving for “A” and “B” substitute to obtain final Stresses
σrr=ρω2(3+v)/8[(R2)(1-(r/R)2)]σθθ=(R2 ρω2(3+v)/8 )[1-(r/R)2((1+3v)/(v+3))]
When r=0 you get the maximum stress
σrr=σθθ=(R2 ρω2(3+v))/8
Product bound
Plug in max stresses to mises yield condition toobtain:
σ(mises)= σ(max)
σ(max)<σ(yield)
ωR< 2(2σ(yield)/(ρ(3+v))).5