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7/30/2019 AERO ENGINES NOTES
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3.2 Compressor
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3.2 Compressor
Role of the compressorAccording to thermal
cycle analysis,
compressor is aimportant componentwhich increases gaspressure and so that thecycle can outputmechanical work.
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1. Compressor structures and types
1.1 Often seen types
Centrifugal
Axial
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3.2 Compressor (Contd)
Centrifugal Shaft is coupled
directly to
turbine.
Impeller can be
single or double
sided.
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Centrifugal compressor
Rotating guidevane:Air goes
in axially. It can
be made in one
piece withimpeller.
Impeller: Radial
blades increase
air speed and
pressure.
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Centrifugal compressor
Diffuser:Reduces speedand getspressure rise.
Air outletcasing: Turnsair to adaptcombustion
chamber.
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Characteristic
Structure simple and reliable Single stage pressure ratio highmay>12
Performance stable
Efficiency lower Frontal area bigger
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Centrifugal compressor (Cont'd)
Uses Small power
Cruise missiles
UAVs or small airplanes
Helicopters
Often compressor is combined with
axial and centrifugal (last stage)
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1. Compressor structures and types
Axial compressors
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Axial compressor (Contd)
Single spool Consists in one rotor and one stator.
The rotor may includes blades, disks drum
and shaft. They are assembled togetherand sit on 2 bearings.
Stator has guide vanes and casing.
Axial compressor has pressure ratio lower
than centrifugal, normally 1.15~1.35. Thatwhy multiple stage axial compressor.
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Axial compressor (Contd)
Two spool compressors
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Axial compressor (Contd)
Twin spool compressors The same axe, but different shafts.
Front one is low pressure (LP)
compressor, it rotates with LP Turbine;Rear one is high pressure (HP)
compressor coupled with HP turbine.
Two rotors have no mechanicalconnection, and they have their own
rotational speed.
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1. Compressor structures and types
1.2 Compressor rotorsResistances
High speed rotation (thousands
~ hundreds k rpm)
Bending moment, torque,
centrifugal forces, vibrations. Require light and enough
strength and stiffness
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1.2 Compressor rotors (Cont'd)
Structure Disks+shaft. One shaft and many disks
where blades are installed. Centrifugal
forces of blades and disks are borne by
the disks and bending stiffness dependson the shaft.
No more used because of
bending stiffness too weak.
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1.2 Compressor rotors (Cont'd)
Strurcture Drum and drum+disks.
Blades are attached
circumferentially or axiallyin drum or disk. Forces
are transferred through
the drum and disks. The
drum insures the bending
stiffness.
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Rolls Royce structure
Meridian plane
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Drum
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Drum+discks
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1. Compressor structures and types
1.3 Blades Important parts
in axial
compressor,composed by
airfoil and
attachment.
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1.3 Blades
Blades suffer centrifugal,aerodynamic and vibrating forces.
Attachment is also important.
Swallow tail (easy fabrication)
Pivot (No bending stress)
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1.3 Blades (Cont'd)
Blades may be broken due to fatigue,especially vibrating fatigue.
To reduce vibration amplitude, long
blades are often made with a mid-spansupport called snubber or clapper.
centrifugal force
efficiency
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1.3 Blades (Cont'd)
At the end of compressor, temperaturecan reach 500 ~600C, even higher.
Materials used are normally titanium,
aluminum alloys, steels and composites.
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1. Compressor structures and types
1.4 Compressor stator is the part which does not rotate
and consists of vanes and casings.
bears axial forces, torques,vibration and rotors forcestransferred by bearings.
is part of air passage, bears
pressure and thermal stresscaused by temperature.
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1.4 Compressor stators (Cont'd)
Types of casing Half-half
Good stiffness
Assembly no need disassemble therotor
Heavier
Entire
Must disassemble rotor (blades),normally used in few stagescompressor.
Lighter
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1. Compressor structures and types
1.5 Anti-icing and axial force redistribution Water droplets may become ice. They may
reduce air passage and break blades when
detached.
Anti-icing methods
Heating (electricity,
hot air)
Hydrophobiccoating
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1.5 Anti-icing and axial force redistribution
Bearing Ball (Axial and radial forces)
Roller (Journal bearing, Radial force only)
Compressor axial force (>total thrust) istoo big for balls.
Coupling with turbine
Creating rooms (Not in air passage)
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1.5 Anti-icing and axial force redistribution
High pressure (push)
Low pressure (pull)
Rooms have one side: rotor; another side: stator.
They are sealed.
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3.2 Compressor
2. Basic equations 2.1 Energy equation
Fixed system
(Ignoring heat)
*
1
*
2
2
1
2
2
12 2 hh
vv
hhWu
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1.1 Energy equation (Cont'd)
Mobile system(Ignoring heat exchange)
Compressor
ublade circumferential velocity
wRelative velocity
22
2
1
2
212
2
1
2
2 wwhhuu
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1.1 Energy equation (Cont'd)
In case of axial compressor (u notsignificant change), so
i.e.
Gas relative total enthalpy unchanged
form inlet to outlet.
*
2
*
1 ww hh
22
2
22
2
11 whwh
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2. Basic equations (Cont'd)
2.2 Bernoulli equation Fixed system
WfLosses
Polytropic work:
fu
Wvvdp
W
2
2
1
2
22
1
)(1
12
2
1TTR
n
ndp
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2.2 Bernoulli equation (Cont'd)
Polytropic work (Compressor)
Isentropic work
11
1
1
21
n
n
nCp
pRT
n
nW
11
1
1
21
ppRTWiC
2 2 B lli i (C 'd)
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2.2 Bernoulli equation (Cont'd)
Work added by compressor blades usedto accomplish generic compression,
increase air kinetic energy and
overcome flow losses.
In case of isentropic
fnCC Wvv
WW
2
2
1
2
2
2
2
1
2
2 vvWW iCC
2 2 B lli ti (C t'd)
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2.2 Bernoulli equation (Cont'd)
Due to losses, more work needed
)( iCnCf WWW
2 2 B lli ti (C t'd)
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2.2 Bernoulli equation (Cont'd)
Polytropic work (Turbine)
Isentropic work
n
nnT
p
p
TRn
ndpW
1
2
1
1
'2
1
11
1
'
' 1
2
1
1'
'
'
111
p
p
TRWiT
2 2 B lli ti (C t'd)
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2.2 Bernoulli equation (Cont'd)
Gas expansion work and kineticenergy change generate shaft
work and overcome losses.
Isentropic expansion
fTnT WWvv
W 2
22
21
TiT Wvv
W
2
2
2
2
1
2 2 B lli ti (C t'd)
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2.2 Bernoulli equation (Cont'd)
Work lost in turbine due to losses
More work needed in compressor
)( nTiTf WWW
)( iCnCf WWW
2 2 B lli ti (C t'd)
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2.2 Bernoulli equation (Cont'd)
)( nTiTf WWW )( iCnCf WWW
2 2 B lli ti (C t'd)
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2.2 Bernoulli equation (Cont'd)
Rotational coordinate system
For axial compressor
Relation of velocities and pressures in
inlet and outlet.
fWwwdpuu
222
1
2
22
1
2
1
2
2
02
2
1
2
22
1
fW
wwdp
2 2 B lli ti (C t'd)
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2.2 Bernoulli equation (Cont'd)
In case of isentropicFor compressor,p, w.
For turbine,p, w.
02
2
1
2
22
1
wwdp
3 2 C (C t'd)
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3.2 Compressor (Cont'd)
2. Basic equations 2.3 Efficiency and losses
Due to viscosity, gas flowing in
turbomachines will produce manykinds of losses and they can classed
into 2 :
(1) Airfoil losses
(1) Airfoil losses (Cont'd)
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(1) Airfoil losses (Cont'd)
Boundary layer lossFriction (a) Separation loss (b)
(1) Airfoil losses (Cont'd)
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(1) Airfoil losses (Cont'd)
Tail trace vortexes (c) Shockwave loss (d)
2 3 Efficiency and losses (Cont'd)
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2.3 Efficiency and losses (Cont'd)
(2) Circumferential losses (secondary flow)
Tip and hub circumferential boundary layers
Tip clearance leaking and passage
vortexes
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(2) Circumferential losses (Contd)
2 3 Efficiency and losses (Cont'd)
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2.3 Efficiency and losses (Cont d)
These losses are presentedW
f inBernoulli equation. But, usually,
efficiency is used to evaluate
performance.
Bernoulli equation can be used for
whole compressor:
)(2
*1*2
2
1
2
2 TTcWvvWW pfnCC
2 3 Efficiency and losses (Cont'd)
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2.3 Efficiency and losses (Cont d)
Isentropic
11
)(2
1
*
1
*
2*
1
*
1
*
2
2
1
2
2
p
pRT
TTcvv
WW ipiCCi
2 3 Efficiency and losses (Cont'd)
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2.3 Efficiency and losses (Cont d)
Compressor efficiency (definition for certain
pressure ratio)
Real work
In general, 0.9 for a single stage, 0.83 forwhole compressor.
*
1
*
2
*
1
*
2*
)Real( TT
TT
W
W i
C
CiC
*1
**
1 /1
1CCC RTW
2 3 Efficiency and losses (Cont'd)
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2.3 Efficiency and losses (Cont d)
The same, for turbine
3-25
)(
2
*
4
*
3
2
4
2
3 TTcWvv
WW pfnTT
2 3 Efficiency and losses (Cont'd)
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2.3 Efficiency and losses (Cont d)
Isentropic
(3-26)
'
' 1
*
4
*3
*
3
'
'
'
*
4
*
3
2
4
2
3
11
1
)(2
p
p
TR
TTcvv
WW ipiTTi
2 3 Efficiency and losses (Cont'd)
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2.3 Efficiency and losses (Cont d)
Turbine efficiency
Real work
0.88 for a stage, 0.92 for whole turbine.
*
4
*
3
*
4
*
3* )(
iTi
TT
TT
TT
W
GenericW
*
1*
*
3'
'
'
'
1
11 T
T
T RTW
2 Basic equations (Cont'd)
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2. Basic equations (Cont d)
2.4. Equation of moment of
momentum
Take an isolated element
from 1-1 to 2-2. After dt, it
moves to 1'-1' to 2'-2'.Between 2-2 and 2'-2',
moment of momentum:
dm2v2ur2 and between 1-1and1'-1', dm1v1ur1 .
2 4 Equation of moment of momentum (Cont'd)
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2.4. Equation of moment of momentum (Cont d)
Because of continuity, dm1=dm2=qmdtIn period dt, Momentum change:
dm2v2ur2- dm1v1ur1 = qmdt(v2ur2-v1ur1)
Based on law of moment ofmomentum: Change is equal to sum of
moments, so the Moment:
)()(
11221122 rvrvq
dt
rvrvdtqM uum
uum
2 4 Equation of moment of momentum (Cont'd)
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2.4. Equation of moment of momentum (Cont d)
Specific work (Euler equation)
If equal radius in inlet and outlet
(3-31)
11221122
1122
)(
)(
uvuvrvrv
dtq
dtrvrvq
dtq
MdW
uuuu
m
uum
m
u
uuuu vuvvuW )( 12