Theory of turbo machinery / Turbomaskinernas teori Chapter 4 · Turbomaskinernas teori Chapter 4....
Transcript of Theory of turbo machinery / Turbomaskinernas teori Chapter 4 · Turbomaskinernas teori Chapter 4....
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Theory of turbo machinery / Turbomaskinernas teori
Chapter 4
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow turbines
FIG. 4.1. Large low pressure steam turbine (Siemens)
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow turbines
FIG. 4.2. Turbine module of a modern turbofan jet engine (RR)
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.3. Turbine stage velocity diagrams.
Note direction of 2
1
2
3
Nozzle row
Rotor row
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
Assumptions:
• Hub to tip ratio high (close to 1)
• Negligible radial velocities
• No changes in circumferential direction (wakes and nonuniform outlet velocity distribution neglected)
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
1 1 1 2 2 2 3 3 3x x xA c A c A c
Continuity equation for uniform steady flow:
1 2 3x x x xc c c c
Assuming constant axial velocity
1 1 2 2 3 3A A A
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Design parameters
Flow coefficient
Stage loading coefficient
or
Δ 02
Or using Euler:
Δ
Δ 0 Δ
(4.2)
change of tangential velocity in rotor!
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Stage reaction
Stage reaction =
31
32
hhhhR
Static enthalpy drop across rotor
Static enthalpy drop across stage
dpdhTds Second law,assuming isotropic process and ignoring density changes dpdh
31
32
ppppR
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
01 03 2 3Δ y yW W m h h U c c 01 02h h
Please note:
No work done in nozzle row:
With
And using above equations:
Work done on rotor by unit mass of fluid
32
23
22
23
22
320302 22 ccUcccchhhh xx
22
222
0cch
chh x
320301 ccUhhmWW
Angle defined in opposite direction at 2
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
Combining above equations:
Rewriting this in terms of relative velocity
U
Relative stagnation enthalpy, , does not change across rotor
with 2 3x x xw w c and 2 2 2x yw w w
2 22 3 2 3 2 0h h w w
0,relh
3232
33
22
wwccwUcwUc
022
23
22
23
22
32
xx ccwwhh
2c
2w
(4.6 approximately)
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.4. Mollier diagram for a turbine stage.
Nozzle row (1 to 2):
• Static pressure:
• Stagnation enthalpy:
• Stagnation pressure:(isentropic: )
1 2p p
01 02h h
01 02p p
Subscript ‘s’ denotes isentropic change and ‘ss’ denotes both rows isentropic
01 02p p
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
2 3p p
FIG. 4.4. Mollier diagram for a turbine stage.
Rotor row (2 to 3):
• Static pressure:
• Stagnation enthapy:
• Stagnation pressure:02 03h h
02 03p p
However:
• Relative Stagnation enthapy, 2
02, 02 2 03,2rel relh h w h
32 pp
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Repeating Stage
FIG. 4.5. General arrangement of a 6-stage repeating turbine.
Multi-stage turbines: Stages often similar to each other
•
•
•
However, channel must be widened
.constcx
.constr
31
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Repeating Stage
0301
21
31
21
31
32 11hhhh
hhhh
hhhhR
Reaction: Relative enthalpy drop across rotor = 1- relative enthalpy drop across stator
Same velocities in and out => 030131 hhhh
2tantan0
21
22
22
21
22
020121
xccchhhh
03012 hhU Stage loading
2tantan1 1
22
22 R (4.12)
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Repeating Stage
1212 tantantantan
Uc
Uc x
2 eq 4.13 a + eq 4.12:
(4.13 a)
2
tantan1 12 R
1tan12 R (4.14)
the reaction becomes
with
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: number of stages
From the definition of stage loading:
The number of stages may be expressed as22
0301
UW
Uhh
2UmWnstage
– Higher mass flow– Higher stage loading– Higher blade velocity
All lead to reduced number of stages
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Stage losses and efficiency
01 03
01 03
Actual work outputIdeal work output when operating to same back pressurett
ss
h hh h
Turbine stage total to total efficiency:
01 03 1 3
01 03 1 3tt
ss ss
h h h hh h h h
For a repeating stage, no changes in are made in velocities from inlet to outlet: . Further assuming the efficiency becomes:
1 3 1 3 and c c 3 3ssc c
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Stage losses and efficiency
2 2 3 32 22 3
and 2 2
s sN R
h h h hc w
Defining enthalpy loss coefficients for the nozzle and rotor respectively:
12 2
01 03 3 2
01 03, 1 3
12 2 2
01 03 3 2 1
01 3, 1 3
12
12
R Ntt
ss
R Nts
ss
h h w ch h h h
h h w c ch h h h
Neglecting rotor temperature drop, the stage efficiencies may be expressed as:
(4.18 c)
(4.19 c)
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Soderberg
22 1 22 cos tan tan 0.8T
id
Y s bY
Soderberg’s correlation:• Large set of data compiled
• Design assuming Zweifel’s criteria for optimum space – axial chord ratio
• Result: Turbine blade losses are a function of
Deflection
Blade aspect ratio
Blade thickness-chord ratio
Reynolds number
H b
maxt l
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Soderberg
1 2
3H b
max 0.15 0.3t l
52 2 2 2Re defined at exit throat 2 cos cos 10h h hc D D D sH s H
• Deflection
• Blade aspect ratio:
• Blade thickness-chord ratio
maxt
l
b
s
is height of blade (radial direction)H
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
1 2
For turbines:
• Deflection, , is large, but
• Deviation, , is small2 2 '
2 2 '
1 2' '
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Soderberg
FIG. 3.25. Soderberg’s correlation of turbine blade loss coefficientwith fluid deflection (adapted from Horlock, 1960).
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Soderberg
Corrections for
• Reynolds number
• Blade aspect ratio
Nozzles:
Rotors:
Tip clearance losses and disc friction not included
5Re 10
1 45* *10
Recor
* *1 1 0.993 0.021cor b H
* *1 1 0.975 0.075cor b H
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theoryDesign considerations
• Rotor angular velocity (stresses, grid phasing)
• Weight (aircraft)
• Outside diameter (aircraft)
• Efficiency (almost always)
• ………
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theoryConsider a case with given
• Blade speed
• Specific work (or stage loading)
• Axial velocity (or flow coefficent)
U
xc
The only remaining parameter to define is since
• Triangles may be constructed
• Loss coefficients determined from Soderberg
• Efficiencies computed from loss coefficients
2c
32 ccUW
23 cUWc
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
Variation of efficiency with c 2/U (Reaction) for several values of stage loadingfactor W/U2 (adapted from Shapiro et al. 1957).
2
ΔStage loading factor: WU
flow coefficient: xcU
Aspect ratio: Hb
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theoryStage reaction, R
• Alternative description to
• Several definitions available
• Here:
2yc U
2 3 1 3R h h h h
E.g: R = 0.5
2 3 1 3
2 3 1 2
0.5 h h h hh h h h
R = 0.5
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
2 3 01 03R h h h h
For a repeating stage, 1 3c c
Using and Euler 2 22 3 2 3 2 0h h w w
2 23 2
2 32 y y
w wRU c c
3 2 3 2 3 2
2 3 22 y y
w w w w w wRUU c c
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
tany xw c
Relative tangential velocity
3 23 2tan tan
2 2xw w cR
U U
Or using 2 2y yc w U
3 23 2
3 2
2 21 tan tan2 2
y
x
w U ww wRU U
cU
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.6. Velocity diagram and Mollier diagram for a zero reactionturbine stage.
3 2 3 2tan tan 0 if 2
xcRU
Zero reaction stage
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.8. Velocity diagram and Mollier diagram for a 50% reactionturbine stage.
3 2 3 21 tan tan 0.5 if 2 2
xcRU
50% reaction stage
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.7. Velocity diagram for 100% reaction turbine stage.
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.9. Influence of reaction on total-to-static efficiency with fixed values of stage loading factor.
FIG. 4.4
22
Δ12
yCWRU U
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.6. Mollier diagram for an impulse turbine stage.
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Smith charts
FIG. 4.14. Design point total-to-total efficiency and deflection angle contours for a turbine stage of 50 percent reaction.
Alternative representation for specified reaction
Based on measurements at Rolls-Royce
2
( , ) where
Δ is the stage loading and
is the flow coefficientx
f
WUcU
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.11. Design point total-to-total efficiency and rotor flow deflection angle for a zero reaction turbine stage.
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Centrifugal stresses
FIG. 4.15. Centrifugal forces acting on rotor blade element.
2d Ω dcF r m
d dm A r
2cd dF Ω dc r rA
With constant cross section this may be integrated
22Ω d 1
2t
h
r tipc hr
t
U rr rr
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.16. Effect of tapering on centrifugal stress at blade root (adapted from Emmert 1950).
Tapering: Reduction of cross sectional area in radial direction, in order to reduce stresses
Pure fluid dynamics would recomend the opposit
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.17. Maximum allowable stress for various alloys (1000 hr rupture life) (adapted from Freeman 1955).
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: 2-D theory
FIG. 4.18. Properties of Inconel 713 Cast (adapted from Balje 1981).
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Cooling
Turbine blade cooling.
Why is the efficiency of the gas turbine comparable to that of a Rankine cycle?
(given that we do have to pay a considerable amount of energy to the compressor, whereas compression of water in the Rankine cycle is cheap)
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Cooling
The evolution of allowable gas temperature at the entry to the gas turbine and the contribution of superalloy development, film cooling technology, thermal barrier coatings and (in the future) ceramic matrix composite (CMC) air foils and perhaps novel cooling concepts
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Department of Energy Sciences / Division of Thermal Power Eng. / JK
Axial-flow Turbines: Cooling
FIG. 4.20. Turbine thermal efficiency vs inlet gas temperature (adaptedfrom le Grivès 1986).