Numerical simulation for functional painting of ship hull ...
Transcript of Numerical simulation for functional painting of ship hull ...
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摩擦抵抗低減効果を持つ 機能性船底塗料の数値解析
Numerical simulation for functional painting of ship hull with friction drag
reduction effect
応用流体力学グループ
高木 洋平
Research group of applied hydrodynamics
Y. Takagi
RIAM研究集会「壁乱流における大規模構造の統計法則と動力学に果たす役割」
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Turbulent drag reduction
• Applications in wall turbulence
Riblet Micro bubble
Stenzel et al., Prog. Org. Coat. (2011)
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Turbulent drag reduction
M. O. Kramer, J. American Soc. Naval Eng. (1960)
Compliant surface Requirement for ship hull: • Easy-to-use • Durability • Low cost
Painting is usually used for anti-fouling.
Functional painting with drag reduction effect
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Commercial painting
• LF-Sea (Nippon Paint)
– Hydrogel formation
– DR ~ 10%
– Biomimetic
– Water trapping effect
Water trapped layer
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Drag reduction effect with hydrogel
Result of towing tank test
山盛, TECHNO-COSMOS, 2005 山盛&島田, TECHNO-COSMOS, 2009
Water trapped layer
Proposed drag reduction mechanism
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Painting condition in sea water
Self-polishing type Hydration type
• Green • Stress relaxation
after shipping
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Structures around hydrogel painting
Proposed mechanism for drag reduction 1. Slip velocity due to water trapping 2. Stress relaxation due to compliant gel polymer 3. Surface deformation and roughness 4. Water penetration into hydrated and gel layers
(porous-like structure)
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1. Slip velocity due to water trapping: numerical modeling in plane channel flow
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Direct Numerical Simulation
(DNS) of turbulent channel flow
¶ui
¶t+
¶(uiu j )
¶x j
= -1
r
¶p
¶xi
+1
Re
¶2ui
¶x j
2
¶ui
¶xi
= 0
Navier-Stokes equation:
Continuity equation:
Property Symbol Value
Grid number
Re number
Nx×Ny×Nz
ReC (Ret)
128×151×128
4200 (180)
Numerical scheme
• 2nd-order Finite Difference Method
• Crank Nicholson for viscous term
• 3rd-order Runge-Kuttta
• Poisson eq. in Fourier space was
solved by TDMA.
Governing equations
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Slip velocity condition
us = lx
¶u
¶y,ws = lz
¶w
¶y
lx ,lz = fx f zl0
Local slip velocity
where
Property Value
Reference slip length (l0+)
Slip wave length:
x-direction (lx+)
z-direction (lz+)
0.36
275, 368, 550, 735, 1100
50, 100, 183, 367
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Validation of simulation code
Case Slip length DR
(Min & Kim[1])
DR
(Present)
Streamwise slip lx+ = 0.36, lz
+ = 0 5% 5.5%
Spanwise slip lx+ = 0, lz
+ = 0.36 -3% -3.6%
Isotropic slip lx+ = lz
+ = 0.36 -1% -0.6%
Drag reduction ratio (DR) under uniform slip velocity condition
[1] T. Min and J. Kim, Phys. Fluids, 16(7), L55 (2004).
Drag reduction ratio
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Validation of simulation code
Mean velocity profiles under uniform slip velocity condition
Drag decrease/increase
mechanism (Min&Kim, 2004)
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Streak structure
Streamwise velocity fluctuation at y+ ~ 5.8
u’ > 0: high speed streak
u’ < 0: low speed streak
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Scale of streak structures
Two-point correlations at y+ ~ 5.8
In the streamwise direction In the spanwise direction
Negative correlation is related with the scale of high/low streaks.
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Scale of streak structures
xS+ ~ 500
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Dependency of local slip velocity
Optimum local slip condition was not specified uniquely.
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Suppression of energy dissipation
One-dimensional energy spectra at y+ ~ 5.8
The spanwise intensity of streak structure decreased by local slip.
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Vortex interaction
Two-point correlation of vorticity Velocity fluctuation (streak structure)
Peaks by local slip
No significant change
Vortex interaction was seen in the
horizontal plane.
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Summary of topic 1
• A turbulent channel flow simulation with local
slip velocity was carried out.
• The slip wavelength compared with the size of
streak structure was effective for drag reduction.
• The spanwise energy dissipation related with
the streak scale was selectively suppressed.
• The vortex interaction was seen in the
streamwise and spanwise directions. However,
it did not lead to drag increase.
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2. Stress relaxation due to compliant gel polymer: Nonlinear response of hydrogel to shear stress
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Response to high wall shear stress
• Gel: nonlinear stress response
¶ui
¶y
No-slip
Slip
Simplified nonlinear-response
0
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Threshold of slip condition
Nonlinear stress response Calculated range of velocity gradient
on wall (no-slip case)
¶u
¶y~ 8,
¶w
¶y~ 1
Label Type Threshold
Case 1 only x-slip
0 ~ 20 Case 2 only z-slip
Case 3 isotropic (xz-slip)
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Dependency of drag reduction
Total slip effect was given by the summation of each contribution.
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Summary of topic 2
• A three-dimensional simulation considering shear stress
response in hydrogel was carried out.
• Although the stress response was isotropic, significant
drag reduction effect was achieved.
• Isotropic hydrogel painting might be useful for wall
turbulence with the change of streamwise direction.
In oblique flow Super hydrophobic flow
Ou&Rothstein,2005
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3. Surface deformation and roughness: wavy channel flow simulation
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Numerical condition
Wave shape of the wall :
Streamwise wavy channel Spanwise wavy channel Case 1
Case1 Case2 Case3
Wave type streamwise spanwise
Wave length(λ) [m] 2.0 1.33 0.1
Amplitude(a) [m]
Grid Number(x, y, z) 148,95,128 128,95,148 129,97,241
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5600ν
δ2 mu
eR
um: mean velocity
δ : channel-half width
ν : kinematic viscosity
Cyclic
Wall
DNS of a turbulent channel flow by using OpenFOAM®
[1] J. Kim et al., J. Fluid Mech., 177, pp. 133-166 (1987).
No turbulence model
Label Grid number Method
Kim et al. (1987)[1]
192×129×160
Fourier-spectral
Coarse 64×64×64
Middle 96×96×96 FVM with OF
Fine 128×128×128
Code validation
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Code validation
Middle and Fine resolution
showed good agreements.
OpenFOAM is available for
DNS on a turbulent channel flow.
Mean velocity profiles
Coarse Middle Fine
Averaged y+ 0.60 0.51 0.49
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Drag reduction ratio (DR)
flat
wavyflat
dx
dP
dx
dP
dx
dP
DR
: mean pressure gradient in a flat channel
flatdx
dP
: mean pressure gradient in a wavy channel
wavydx
dP
Drag increase Drag reduction
Case 1
DR = -20.4 %
Case 2
DR = -9.4 %
Case 3
DR = +9.3 %
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a
The peak of RMS value profile
Most random flow region
z direction
wave tip
y δ
Two peaks above and below wave tip
Discussion ― Case1 : streamwise wavy channel
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Fluctuation is conserved in the wall wave
Vortex ?
Median diameter of eddies Case1 Case 2 Case 3 Flat channel
Median diameter [m] 0.184 0.272 0.09 0.240
Spanwise wave spacing[m] 1.333 0.1 ―
DR [%] -20.4 -9.4 +9.3 0
z (spanwise direction )
z (spanwise direction )
Advance the dissipation Drag reduction
Unit vortex in one wave Some vortices in one wave
Case 2 Case 3
collision
Case2 and Case 3 : spanwise wavy channel
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• Drag reduction effect was shown when collision of vortices was
suppressed by wall shape. • Dissipation was advanced by collision of several vortices in one
wave .
Case1 Case2 Case 3
Wave type Streamwise Spanwise
Wave length(λ) 2.0 1.33 0.1
Median diameter 0.184 0.272 0.09
DR [%] -20.4 -9.4 9.3
Soft matter, Hydrogel, has advantage for drag reduction on ships bottom surface
Summary of topic 3
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4. Water penetration into hydrated and gel layers (porous-like structure): channel flow with porous wall
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1) K. Suga et al., Int. J. Heat Fluid Flow, 32, 586-595 (2011)
2) S. Hahn et al., J. Fluids Mech. vol. 450, pp. 259- 285(2002)
3) W. P. Breugem et al., J. Fluids Mech. vol. 562, pp. 35-72 (2006)
Approaches for fluid flow through porous structure
Boundary condition approach2)
Decrease of skin friction due to slip velocity
Increase of turbulent drag
?
• Experimental research • Observation of
sweep/ejection near wall1)
• Numerical research
Continuum approach3)
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Case 5%D 10%D 20%D Flat
―
Total channel width
149,(129+16),129 149,(129+20),129 149,(129+20),129 129,129,129
)(2 pf f4
f2
5600)(2
Re
pfmm
u
Non-uniform grid 5.0
miny
f
p
: Width of fluid region : Porous wall thickness
Numerical conditions
Porous region
Fluid region
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DNS of turbulent channel flow
Spatial discretization scheme Finite Volume Method Time advancement Implicit Euler method ( 1 st) Poisson equation PISO algorithm
Continuity equation
Momentum equation
0 u
Suu
)1(' 2 pDt
D
Governing equations Numerical scheme
OpenFOAM®
mmm uuuSK
c
K
f2
Darcy-Forchheimer equation
Porous model : Porosity 0.80
K : Permeability 0.02 [mm2]
cf : Forcheheimer
coefficient 0.17
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Drag reduction ratio
FIK identity[1]
Viscous term and Turbulent term
Case DR [%]
5%D 6.55 +9.6 9
10%D 7.16 +1.3 18
20%D 7.56 -4.3 37
Flat 7.25
[1 ]Fukagata, K., Iwamoto, K. and Kasagi, N., Phys. Fluids, 14 (2002), pp.73-76
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Turbulent statistics
Mean velocity profiles Turbulence intensity
Slip velocity occurred over porous walls.
Turbulent intensity became stronger.
pδ
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Turbulent structure – Streak structure
Flat Smooth Channel 5%D (DR=+9.6%) Longer streaky structure
10%D (DR=+1.3%) 20%D (DR=-4.3%)
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Effect of wall thickness
The mechanism of vortex generation
Porous wall
Unstable
Flat wall
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Effect of wall thickness
The mechanism of vortex generation and decaying
Thick Porous wall (Drag increasing)
Unstable
Thin porous wall (Drag reducing)
Weak source flow
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Joint Probability Density Function (JPDF)
The mechanism of vortex generation and decaying
Thick Porous wall 20%D (Drag increasing) Thin porous wall 5%D (Drag reducing)
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Summary of topic 4
• The direct numerical simulation on a channel with porous walls which had varying wall thickness were carried out.
• The drag reduction was achieved over the thinnest porous wall,
and in that case, turbulent intensity became weaker. • The turbulent structures suggested that the relationship between
the intensity of sweep (or ejection) and the thickness of porous wall was an important factor for drag reduction.
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5. Experimental evaluation of drag reduction: Taylor-Couette flow
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ri : radius of inner cylinder [m]
ro : radius of outer cylinder [m]
L: height [m]
ω: angular velocity [m]
d: gap between the cylinders [m]
ν: kinetic viscosity [m2/s]
ρ: density [kg/m3]
T: toque of inner cylinder [Nm]
dreR i
Nondimensionalized
torque: L
TG
2
= 48 mm
= 64 mm
= 128 mm
ri
ro
L
mmh
mmr
mmr
o
i
128
64
48
Motor
Torque Meter
Acrylic
outer cylinder
Stainless
inner cylinder
Camera
ω
Rotating cylinder facility
Reynolds number:
Experimental setup
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Re = 4.4×104
dreR i
mmh
mmr
mmr
o
i
128
64
48
Motor
Torque Meter
Acrylic
outer cylinder
Stainless
inner cylinder
Camera
ω
Rotating cylinder facility
Reynolds number:
Flow pattern
Wavy vortexes
Re = 8.8×103
Steady vortexes
Re = 4.2×103
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oi rrratioradius /:
547.1
4/7
2/3
425.1
4/7
2/3
10Re10Re)1(
23.0
10Re104Re)1(
45.1
for
for
G =
Wendt’s empirical relations
F. Wendt, Ingenieur-Archiv. 4, 577 (1933).
109
108
107
106 103 104 105
Re
G
Validity of measurement
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4.4×104 < Re < 8.1×104
Range of Re
Smooth Cured Hydrogel
Test cylinders
Cured
Hydrogel
Thick
380 μm
380 μm
Thin
240 μm
240 μm
Thickness of coating
Thickness of primer
1st layer : 140 μm
2nd layer : 80 μm
Total : 220 μm
Experimental conditions
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Torque G of hydrogel coating was smaller than that of Cured coating.
109
108 104 105
G
Re
L
TG
2
Nondimensionalized torque
dreR i
Reynolds number
Drag reduction effect
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109
108 104 105
G
Re
L
TG
2
Nondimensionalized torque
dreR i
Reynolds number
Drag reduction effect
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105
Thick
Thin
Re
DR
104
0
5
10
15
20
25
30
35
40
100
Cured
HydrogelCured
G
GGDR
Drag Reduction Ratio
Drag reduction effect of thin hydrogel was larger than thick one.
Relation with DR and Re
DR ~ 7%