1 Turbomachinery Class 12. 2 Axial vs. Radial Machines Need to determine what type of turbine is...
-
Upload
ethan-little -
Category
Documents
-
view
228 -
download
8
Transcript of 1 Turbomachinery Class 12. 2 Axial vs. Radial Machines Need to determine what type of turbine is...
1
Turbomachinery
Class 12
2
Axial vs. Radial Machines
Need to determine what type of turbine is most efficient for application - function of Ns for both compressors and turbine
3
2 23/ 4 3/ 4
1 /0
0201
01
/ /
1
s
ideal
p
N m N mN
h pc T
p
Need to determine what type of turbine is most efficient for application - function of Ns for both compressors and turbine
4
Radial Radial OutflowOutflow Turbine Turbine
Ljungstrom Steam Turbine: Dixon - steam turbine design - No stator blades counter-rotating blades - radial outflow - large amount of work per stage - rugged
5
Radial Outflow Turbines
• Ljungstrom Turbine arrangement
Compatible with expanding steam, more area with same blade height as density drops
Vaneless - Counter rotating
Old Configuration recently re-invented for gas turbines
– axial counter-rotating
6
Counter-Rotating Turbines
• Counter Rotation High Stage Work
Compare: – Conventional Axial Stage, 50% Reaction & 90 Gas Turning
vs. – Counter Rotating, Vaneless Stages with 90 Gas Turning
Cx1 = Cx2, U1 = U2 = Cx/U= 0.6
Repeating Stages
Counter Rotation U changes direction
7
Radial Flow Turbine Analysis
• Remember from Class:
2
2tan 1
RE
2
22tan 1
RE
2
2tan 2
RE
2
22tan 2
RE
0
1
2
1
2
3
8
Radial Flow Turbine Analysis
• In this problem, for the axial stage
=0.6, R=0.5, and 1212
- Iteration:
Guess 1
From Calculate E.
From Calculate 2
Iterate until turning (12 is correct
• For the counter-rotating stage…..match turning
2
2tan 1
RE
2
2tan 2
RE
9
Radial Flow Turbine Analysis Conventional vs Counter-Rotating
Counter Rotating
Cx/U 0.600 0.600Beta 1 25.097 15.482Alpha 1 64.903 62.774Turning 90.000 90.000Beta 2 -64.903 -74.518Alpha 2 -25.097 -62.774Reaction 0.500 1.000E -1.562 -2.332
2nd StageCx/U -0.600Alpha 3 -62.774Beta 1 -15.482Error 0.000
Convergence 2.135 3.610
Conventional
Counter-rotating: high stage work (E)
10
Radial Flow Turbine Analysis - Conventional Design
50% Reaction, 90 Deg Turning
-1.5
-1.0
-0.5
0.0
0.5
1.0
1.5
-1.0 -0.5 0.0 0.5 1.0 1.5 2.0 2.5 3.0 3.5 4.0
C1 U
W1
W2
C2
50% Reaction, 90 Deg Turning
-1.5
-1.0
-0.5
0.0
0.5
1.0
1.5
-1.0 -0.5 0.0 0.5 1.0 1.5 2.0 2.5 3.0 3.5 4.0
C1 U
W1
W2
C2
11
Radial Flow Turbine Analysis - Counter-Rotating Design
01 2 90
Vaneless, Counter Rotating, 90 Deg Turning
W1
C1 U
W2U
U'
W3
C2
Vaneless, Counter Rotating, 90 Deg Turning
W1
C1 U
W2U
U'
W3
C2
12
Radial Inflow [90Radial Inflow [9000 IFR] Turbines IFR] Turbines
Kinematic view Thermodynamic view
Exit part of rotor (exducer) is curved to remove most of tangential component of velocity
Advantage of IFR turbine: efficiency equal to axial turbine, greater amount of work per stage, ease of manufacture, ruggedness
13
Radial Flow Turbines
• Radial Inflow Turbine with Scroll
14
Radial Flow Turbines
• Radial Inflow Turbine Stator/Rotor
15
Radial Flow Turbines
• Radial Inflow Turbine Stator/Rotor [No shroud]
16
Radial Flow Turbines• Radial Inflow Turbine Scroll
Scroll or distributor - streamwise decreasing cross flow area - provide nearly uniform properties at exit
17
Radial Flow Turbines• Radial Inflow Turbine Scroll - Stator
18
Radial Flow Turbines• Radial Inflow Turbine Impeller
Note - direction of rotation - rotor rearward curvature
19
Radial Flow Turbine Design• Nominal Stator / Rotor Design:
Station 1 – Inlet to StatorStation 2 – Exit of Stator, Inlet to Rotor
[Radially inward]Station 3 – Exit of Rotor [Absolute velocity is axial]Station 4 - Exit of Diffuser
• Rotor inlet relative velocity is radially inward
- For Zero Incidence at Rotor Inlet, W2=Cr2 and C2=U2
• Rotor exit absolute flow is axial
- For Axial Flow at Rotor Exit, C3=Cx3 and C3=0
C2
Cm2=Cr2=W2
U2
Cm3=C3=Cx3
U3
W3
20
Radial Flow Turbine Design- 900 IFR
• For adiabatic irreversible [friction] processes in rotating components
• From the Alternate Euler Equation:
• and
2 2 2 2 2 22 3 2 3 2 3
0 2Rotor
U U W W C Ch
gJ
2 2 22 2 2C W U 2 2 2
3 3 3W C U
2 3
2 22
2 32 2 2orel orel orel
U UUI h h h
21
Radial Flow Turbine Design
• substituting:
• Thus from Alternate Euler’s Equation :
gJ
UUWUCUWCh Rotor 2
23
22
23
22
22
23
23
22
0
22
0 01 03 02 03Rotor
Uh h h h h
gJ
22
Radial Flow Turbine Design• Example: Dixon 8.1
• The rotor of an IFR turbine, designed to operate at nominal condition, – Diameter is 23.76 cm and rotates at 38,140 rev/min.
– At the design point the absolute flow angle at the rotor entry is 72 deg.
– The rotor mean exit diameter is ½ the rotor diameter
– The relative velocity at the rotor exit is twice the relative velocity at the inlet.
23
Radial Flow Turbine Design• Example: Dixon 8.1
2
3 2
3 2
02
22
2 2 2
2 2 2
23.76
38,140
/ 2 12.88
2
72
38,140 0.2376 / 60 474.560cot 154.17
/ sin 498.9
mean
Given
D cm
N rpm
D D cm
W W
rotor inlet design point flow angle
NDU mps
W U mps
C U mps
24
Radial Flow Turbine Design• Example: Dixon 8.1
2 22 2 2 2 23 3 3
2 2 2 2 22 3 2
2 2 2 2 23 2 2
2 2 2 22 3
2 2 2 2 2 22 3 2 3 2 3 2 2
0
2 154.17 0.5 474.5 38,786 /
1 0.25 168,863 /
3 71,305 /
210,115 /
225,142 /2
C W U m s
U U U m s
W W W m s
C C m s
Examing relative sources of specific work
U U W W C CW h m s
W
2 2 20 2
0.375( ) 0.158( ) 0.476( ) [% ]
225,142 /
U W C of total
Also
W h U m s
25
Radial Flow Turbine Design• Example: Baskharone p. 434-8
• 0=inlet 1=stator exit 2=rotor inlet 3=rotor exit
• Stator / nozzle exit Mach number M1=0.999
00 0
4.16 / s 71,600 1.33
8.84 1205 0.038stator
m kg N rpm
p bar T K
1 1 1 1
01 00 00
010 1 1
01 1
1156.71
0.999 1034.4 628.35 590.6
[ ] 73.0cos
pc R
M T a C
p p p
m T RFP f M
p A
26
Radial Flow Turbine Design• Example: Baskharone p. 434-8 cont’d
• In constant area interstage duct, apply free-vortex condition to flow from stator exit to rotor inlet
1 1 1
1 1 1
cos 172.6
sin 564.8r
u
C C mps
C C mps
2 1 1 2
2 1 1 2
2
22 02 2
2 2
2
( / ) 184.8
( / ) 605.1
632.69
/ 2 1032
627.62
1.008
r r
u u
p
C C r r mps
C C r r mps
C mps
T T C c K
a RT mps
M
27
Radial Flow Turbine Design
• Mollier Diagram for Radial Flow Turbine (Dixon):
s
1/2 C2spouting
28
Radial Flow Turbine Design
• Spouting Velocity [from hydraulic turbine practice]:
Spouting Velocity, C0: the velocity which has an associated kinetic energy equal to the isentropic enthalpy drop from the turbine inlet stagnation pressure P01 to the final exhaust pressure.
• By taking the exhaust pressure as the isentropic exit static pressure, and assuming no diffuser, then
• For an ideal radial turbine with KE recovery, this leads to
or
20
01 03
1;
2 ss
Ch h ss refers to ideal work at same back pressure
gJ
Jg
C
gJ
Uh Rotor
20
22
0 2
1 707.0
0
2 C
U
29
01 03
01 3
2 202 03 2 3 2 3
01 3 02 03 03 3 3 3 3 3
0
20 3 3 3 3 3
1
2
1( ) ( )
2
tsts ss
ss ss s s ss
Rotorts
Rotor s s ss
h hactual W
ideal m h h h
W h h h h C C
h h h h h h W h h h h
h
h C h h h h
Radial Flow Turbine Design
• Nominal Design Point Efficiency:
Efficiency is centrifugal devices is often represented by total-to-static conditions: ts = total-static
s
22U
30
Radial Flow Turbine Design
• The enthalpy losses for the stator (nozzle) and rotor can be expressed as a fraction, , of the exit kinetic energy:
• For a constant pressure process, ds = dh/T so that:
23 3 3
1for rotor
2s rh h w
2 33 3 2
2
1for nozzle
2s ss n
Th h c
T
33 3 2 2
2
( )s ss s
Th h h h
T
ss
31
Radial Flow Turbine Design
• Substituting into the efficiency definition:
• For the Nominal Design Point velocity triangles, we see that:
0
2 2 2 33 3 2
2
11 ( )
2
Rotorts
r n
h
TC W C
T
2 2 2
3 3 3
3 3 3
csec
csec
cot
C U
W U
C U
32
Radial Flow Turbine Design
• Substituting, we get for the efficiency:
• The temperature ratio, T3/T2, generally only has a very minor effect on the value of ts so that it can be neglected.
2
2 2 23 32 3 3
2 2
1
11 csec ( csec cot )
2
ts
n r
T r
T r
33
Radial Flow Turbine Design
• In addition, the values of r3 and 3are taken to apply at the mean exit radius of the rotor, i.e. r3 = ½ (r3h+ r3t), so that:
2
32 2 22 3 3
2
1
11 csec ( csec cot )
2
ts
avgn r avg avg
r
r
Read Dixon Example 8.2, page 254
34
From Centrifugal Compressor Notes
• Slip: flow does not leave impeller at metal angle [even for inviscid flow]
• If absolute flow enters impeller with no swirl, =0.• If impeller has swirl (wheel speed) , relative to the impeller the
flow has an angular velocity - called the relative eddy [from Helmholtz theorem].
• Effect of superimposing relative eddy and through flow at exit is one basis for concept of slip.
Relative eddy Relative eddy with throughflow
35
• Static pressure gradient across passage causes streamline to shift flow towards suction surface
• In reality, the incidence to the rotor varies over the pitch of the rotor as:
due to – Potential and wake interaction with the vane.– Relative eddy effect seen at exit of compressor– Effect produces a LE slip factor
This variation over the pitch leads to an - optimal incidence and - optimal number of blades
where the efficiency of the rotor is a maximum.
Radial Flow Turbine Design
2 2 , rCf
U
P=pressureS=suction
36
• Rotor Inlet Velocity Triangle (with incidence):
– Average relative velocity W and avg. relative incidence 2
• If we define an incidence factor, [like slip factor in compressors]:
Radial Flow Turbine Design
2
2
U
CU
U2
W2CR2=CM2
C2
CU2
37
Radial Flow Turbine Design
• From the work of Stanitz regarding slip factors:
• Then from the rotor inlet velocity triangles, the inlet flow angle to the rotor is:
0.63 21 1 where Z=Number of Rotor Blades
Z Z
2 22
2 2
2tan where = M
M
U C
Z C U
38
Radial Flow Turbine Design
• Criteria for the Optimal Number of Blades:
2
2
min
min
2
1 12
2
1
2
0;
r
T T T T T T
From particle physics analogy
dWF ma f r f r W
dtp W p
W r and Wr r
WGets r implying that
W at given r is not constant across passage p s
W W r
At r r if W U r and W r U U
min
min 2
2
2 2 tan
T
T
T
Z
UZ
W
Jamieson model
39
Radial Flow Turbine Design
• Criteria for the Optimal Number of Blades:
Optimum blade number balances loading & friction
• Rohlick model uses (quantities at the inlet to rotor):
• Jamieson model
min2
2 min
2
min 2
2
0.03 57 12
UC Z
U Z
Z
min 22 tanZ
40
Radial Flow Turbine Design
• Other Correlations for Optimal Number of Blades (Rohlick results similar to Jamieson):
from Dixon
41
This is to clarify some of the confusing notation in Dixon regarding blade count
• Stanitz correlation
– uses blade number and flow coefficient to calculate the relative radial turbine exit flow angle.
• Other correlations – uses semi-empirical expressions for calculating the optimum
[minimum] blade count Z for an optimum efficiency design, where
– For such a design the exit flow will be radial [in the absolute frame], therefore 2=0 and the correlations are in terms of the corresponding absolute frame air angles [2], e.g.
22
2
2 2tan
M
U
ZC Z
2 2 2tanrU C
42
This is to clarify some of the confusing notation in Dixon regarding blade count
• Jamieson
• Rohlik
min 22 tanZ
2
min 20.03 57 12Z
43
Radial Flow Turbine Design
• Specific Speed relates impeller shape & velocity diagram
• Rohlick shows:
where
4/3
2/1
H
NQN s
3/ 4 3/ 2 1/ 2 3/ 23/ 2
3 3 32/
3 3 2 3
is
ii
h C D hUN
C U D Dh
/0 sin exit
0 0in exit
ideal work, P to P
ideal work, P to Pi
i
h
h
44
Efficiency [ts] of 900 IFR Turbine with Ns [Rohlick analysis]
3 2
3
2 2
3 2
3 2
2
/ 2.0
0
. .
/ 0.7
/ 0.4
,
av
U
opt
shroud
hub
Constraints of analsis
W W
C
i e zero incidence
r r
r r
For each value of shaded
area governed by geometric
scale limits as above
45
Efficiency [ts] of 900 IFR Turbine with Ns [Rohlick analysis]
Dixon Fig. 8.14
Ns units: Nondimensional=radians
46
Radial Flow Turbine Design• Rohlik Model shows Distribution of Losses
Clearance: pressure diff. effects between rotor and shroud
Windage: friction effects between rotor and shroud
47
Radial Flow Turbine Design• Flow Path Shape is Related to Specific Speed
Maximum efficiency designs