Pitchwise distributions of ensemble average velocites · 2003. 4. 18. · FEM for Turbomachinery...
Transcript of Pitchwise distributions of ensemble average velocites · 2003. 4. 18. · FEM for Turbomachinery...
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
Corsini and Rispoli Inoue and Kuroumaru free vortex rotor (1984)
Navier-Stokes prediction obtained with XENIOS finiteelement code (1991) - grid 59 × 21 × 31
tip clearance t = 1.8% lc tip clearance t = 1.2% lc
Pitchwise distributions of ensemble average velocites
Trailing vortextrailing vortex
Va/Uc
Vp/Uc
Vr/Uc
PS SS
passage vortex
wake
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
Corsini and Rispoli Inoue and Kuroumaru free vortex rotor (1984)
Navier-Stokes prediction obtained with XENIOS finiteelement code (1991) - grid 59 × 21 × 31
tip clearance t = 1.8% lc tip clearance t = 1.2% lc
Pitchwise distributions of ensemble average velocites
Leakage vortex
PS SS
Vp/Uc
Va/Uc
Vr/Uc
wake
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
Corsini and Rispoli Storer and Cumpsty linear cascade (1991)
Navier-Stokes prediction obtained with XENIOS finiteelement code - grid 59 × 21 × 31
Navier-Stokes prediction obtained with Dawes finite volume code(1987) - grid 61 × 25 × 33
tip clearance t = 1.8% lc tip clearance t = 4% lc
Blade surface static pressure distribution (Cp) - pressure side
0.5
0.4
0.3
te le
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
Corsini and Rispoli Storer and Cumpsty linear cascade (1991)
Navier-Stokes prediction obtained with XENIOS finiteelement code - grid 59 × 21 × 31
Navier-Stokes prediction obtained with Dawes finite volume code(1987) - grid 61 × 25 × 33
tip clearance t = 1.8% lc tip clearance t = 4% lc
Blade surface static pressure distribution (Cp) - suction side
-0.6
te le
leakage flow influence
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
Corsini and Rispoli Storer and Cumpsty linear cascade (1991)
Navier-Stokes prediction obtained with XENIOS finiteelement code - grid 59 × 21 × 31
Navier-Stokes prediction obtained with Dawes finite volume code(1987) - grid 61 × 25 × 33
tip clearance t = 1.8% lc tip clearance t = 2% lc
Chordwise distribution of averaged tip leakage flow velocity
Leakage velocity
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
Corsini and Rispoli Storer and Cumpsty linear cascade (1991)
Navier-Stokes prediction obtained with XENIOS finiteelement code - grid 59 × 21 × 31
Navier-Stokes prediction obtained with Dawes finite volume code(1987) - grid 61 × 25 × 33
tip clearance t = 1.8% lc tip clearance t = 2% lc
prediction measurement
Blade surface static pressure distribution (Cp) - pressure side
0.5
0.4 0.3
0
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
CFD ORIENTED AXIAL FAN DESIGN IMPROVEMENT (1)
• CFD INTER-BLADE FLOW PHYSICS PREDICTION
• Blade lift synthesized by use of “cone couple” model
separate optimization of blade pressure and suction sides
extend the validity of 2D cascade concept
blade tip
Velocity field close to the blade suction side
fraction of chord lenght
Rpredicted streamtracesmodeled streamtraces
Velocity field close to the blade pressure side
fraction of chord lenght
blade tip modeled streamtraces
predicted streamtraces
R
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
CFD ORIENTED AXIAL FAN DESIGN IMPROVEMENT (2)
• on the basis of computed pitch-averaged flow
force factor is evaluated ( ) ll ct
optimum lc * is defined (Howell, 1942) ⇒ optimum solidity values ( )tl *
lc * ( ) ll ct ( )tl *
SS cone 0.893 1.004 1.124
PS cone 0.591 0.859 1.453
• optimized axial fan rotor geometry with FORWARD SWEPT blades
midspan
hub
casing
**sssssspspsps TLTL ll =>=
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
SWEPT AXIAL FAN ROTOR
• NON FREE VORTEX DESIGN
• CIRCULAR ARC CAMBERED
PLATE
Unswept bladedrotor
Swept bladed rotor
blade number 12 12hub-to-casing diameter ratio 0.676 0.676tip clearance (percent span) 2 % 2 %flow coefficient Φ 0.50 0.50Ideal total head risecoefficient Ψ
0.70 0.70
hub mid tip hub mid tipblade solidity l / t 1.53 1.24 1.05 1.79 1.23 1.13forward sweep angle, deg 0 0 0 30 30 30stagger angle, deg 47.9 42.2 38.3 56.3 43.1 37.4camber angle, deg 27.4 23.1 19.9 35.4 25.4 20.3
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
SWEPT AXIAL FAN ROTOR FLOW SURVEY (1)
Pitchwise-averaged flow data for FSW and USW rotors(circles: FSW; squares: USW)
ϕ3a
RR
a) b)
ϕ1a
ψth,FSW
ψth,USW
ψ3
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
SWEPT AXIAL FAN ROTOR FLOW SURVEY (2)
[deg]
[deg]
R
R
FSW
USW
SSPS
ST
W
C
SSPS
ST
W
C
0.60.3
0.2
0.6
0.2
0.3
0.25
Axial flow coefficient behind the rotor
Uc
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
SWEPT AXIAL FAN ROTOR FLOW SURVEY (3)
Fig. 5: Local ideal total head rise coefficientbehind the rotor
0.55
0.8
1.25
[deg]
R
FSW
SSPS
ST
W
C
1.2
0.55
0.8
[deg]
R
USW
SSPS
ST
W
C
Uc
Ideal total head rise coefficientbehind the rotor
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
SWEPT AXIAL FAN ROTOR FLOW SURVEY (4)
[deg]
R
USW
SS
PS
ST
W
C
Uc
[deg]
R
FSW
SS
PS
ST
W
C
Uc
0.08
-0.08
0.06
0.0
0.05
-0.05
radial flow coefficientbehind the rotor
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
SWEPT AXIAL FAN ROTOR LOADING
R
DF
Diffusion factor profile along the span(circles: FSW; squares: USW)
inpinout w/www)R(DF σ∆ 21 +−=
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
SWEPT AXIAL FAN ROTOR LOSS BEHAVIOR
[deg]
[deg]
R
R
FSW
USW
SS
PS
SS
PS
0.1
0.6
0.1
0.6
0.7
Loss coefficient distributionat 98% blade chord
Uc
R
∆ω
Loss improvement factor
∆ω(R) = RUSWFSW |ωω −
ω = 2inout0in0 V5.0pp ρ−
FEM for Turbomachinery Flows
Alessandro Corsini, BUTE - 28 November 2000
SWEPT AXIAL FAN ROTOR FLOW SURVEY (5)
streamlines on blade suction side streamlines on blade pressure side
8% pitch from blade pressure side