Numerical Simulation of a Cross Flow Hydrokinetic...
Transcript of Numerical Simulation of a Cross Flow Hydrokinetic...
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Numerical Simulation of a Cross Flow Marine Hydrokinetic Turbine
Taylor Hall
University of WashingtonNorthwest National Marine Renewable Energy Center
MSME Thesis Presentation3/13/2012
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Tidal Energy
Tidal energy resource realized
Renewable Clean Predictable Many similarities to wind energy
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Axial Flow Turbines Cross Flow Turbines
Turbine Classifications
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Turbine Design Concepts
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Cross Flow Turbine Advantages High energy density typically found in
narrow constricted channels Packing critical to efficiency and
economic feasibility Cross flow turbines can be stacked,
efficiently utilizing limited space Vertical axis: works in any direction of
flow
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Motivation and Goals Recently realized advantages have ignited interest in cross flow hydrokinetic turbines (CFHT)
Significant gaps in understanding and modeling capabilities Benefits of numerical models
Turbine performance for a variety of parameters Influence of turbine surroundings: stacking, mooring, supports Environmental impacts Larger scale turbine performance
Goals: Gain a better understanding of the CFHT flow dynamics Develop a numerical methodology for CFHT Ultimate goal of developing a computational tool to aid in turbine design and array installation process
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Hydrodynamics of a Cross Flow Turbine
Many differences from axial flow turbines Unsteady and largely three-dimensional Interference between shed vortices and blades Can reach very high angles of attack Rapidly changing angles of attack Dynamic stall behavior
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Hydrodynamics of a Cross Flow Turbine
Tip Speed Ratio:
Relative Velocity:
Tangential Velocity:
Free Stream Velocity:
Power available in the flow:
Azimuthal Position:
Source: Antheaume
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Hydrodynamics of a Cross Flow TurbineAngle of Attack:
Relative Reynolds Number:
Torque:
Power:
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Angle of Attack Relative Reynolds Number
Hydrodynamics of a Cross Flow Turbine
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Micropower generation project as benchmark study:
Adam Niblick and UW Mech. Eng. Capstone Design Team
Source: Adam Niblick
Helical Cross Flow Turbine
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Experiment/Simulation Parameters
Re 28,000
AspectRatio 1.4
SolidityRatio
0.075 for 1blade0.3 for 4blades
CFDSoftwareFluentv12.0 Reynolds‐AverageNavier‐Stokes RANS equations
Turbine and Channel Flow Numerical Modeling
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Reynolds Average Navier Stokes (RANS) Equations
ShearStressTransport‐kω turbulenceclosuremodel Defaultturbulencemodelcoefficients Low‐Reynoldsnumbermodeling
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Channel Domain and Boundary Conditions
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Blockage Ratio: Matched to ExperimentsBlockageratio
0.12
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Simulation Cases Static Turbine
—1 blade—4 blades
Rotating Turbine—1 blade—4 blades
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Labeling of Helical Blade Position
“ θ=45⁰ ”Top
Bottom
Top
Bottom
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Static Turbine: Single Blade
Particle brake applies constant torque to hold turbine in stationary position: λ=0
Torque cell measurements available from experiments
Repeated at several azimuthal locations
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Static Turbine: Single Blade
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α=15⁰
α=5⁰ α=60⁰
α=205⁰
Flow fields for angles of attack (α)
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Modeling in Near Wall RegionWall Functions Near Wall Approach
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Modeling in Near Wall RegionWall Functions
30< y+ < 300
0.15
Total Elements = 185,000
Near Wall Approach y+ < 1
0.0001
Total Elements = 4.0 million
Near Wall: 20x computation time, 20-25% reduction in error
First Length
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Static Turbine: Single Blade with near‐wall modeling approach
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Static Turbine: 4 Blades
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Static Torque: 4 Bladed Turbine
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Superposition of Single Blades vs. 4 Bladed Turbine
VS.
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CFD:
Experiments:
Superposition of Single Blades vs. 4 Bladed Turbine
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Single Blade vs. 1 blade from 4 bladed turbine
VS.
VS.
VS.
VS.
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Single Blade vs. 1 blade from 4 bladed turbine
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Wake Interactions
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Simulation Cases Static Turbine
—1 blade—4 blades
Rotating Turbine—1 blade—4 blades
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Set RPM of rotating domain
Time step =1.2 degree rotation
At each time step:• Non-conformal boundary • Determine interfaces• Calculate flux
Sliding Mesh Technique for Rotating Turbine
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Rotating Turbine: Single Blade
CFD—λ=3.2—λ=3.6 —λ=1.6
Experiment—λ=3.2—λ=3.6 (no load)
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Dynamic Torque: Single Blade
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Rotating Single Bladed Turbine:CFD vs. Experiment
Dynamic Torque for a Single-Bladed Turbine at λ=3.2
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Oscillating Rotational Velocity
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System Dynamics
• CFD models the Hydrodynamic Torque
• Experiments measure the Particle Brake Torque
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Torque Calculations
0
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Experiment Single Blade, 2
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Model Validation
λ=3.2
Differences Attributed To:
• Constant vs. varying tip speed ratio
• System Frictional Torque λ=3.6
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Possible Comparison Improvements
—Run simulations at several different tip speed ratios : create a composite result
—Run experiments with a variable load to keep a constant rotation speed
Four‐ bladed turbine• Hydrodynamic torque undergoes much smaller fluctuations• Much higher moment of inertia• Leads to much smaller oscillations in the rotational velocity
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Increased Reynolds Number Simulation
• Decreased viscosity to achieve higher Re
• Required finer mesh
• Increase in turbine efficiency from 21 to 42%
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Rotating Turbine: 4 Blades
CFD—λ=1.3, 1.6, 2.0
Experiments—λ=1.3 to 2.1
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Rotating 4 Bladed Turbine
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1 Bladed Turbine vs. 4 Bladed Turbine:Effect of Solidity for λ=1.6
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1 Bladed Turbine vs. 4 Bladed Turbine:Effect of Solidity
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4 Bladed Rotating Turbine: CFD vs. Experiments
λ
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Summary and ConclusionsStatic Turbine Analysis
—Methodology can accurately model the starting torque of the turbine
—Limitations associated with predictions of separated flow in RANS simulations
Rotating Turbine Analysis—Direct comparisons between the model and experiments were
challenging for a 1‐bladed turbine with high levels of experimental angular acceleration
—Limitations modeling dynamic stall—Simulations for 4 blades show great qualitative agreement—Promising results for using the methodology for future turbine
performance predictions
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AcknowledgementsProfessor AlisedaProfessor MalteProfessor RileyAdam Niblick and the Capstone Design TeamNorthwest National Marine Renewable Energy CenterDepartment of EnergyFriends and Family