goals of the workshop and targets for sco2 power cycle integration with thermal … ·...
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Goals of the workshop and targets for sCO2 power cycle integration with thermal energy storage
Dr. Rajgopal Vijaykumar, Technology Manager
USDOE sCO2 Workshop 2019
October 31, 2019
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Focus: sCO2 Power Block Integrated with TES
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Example Power Block: RCBC
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• Make Utility Operators Comfortable with sCO2 Power Block Integration with TES
• TES is a Critical Feature that Decouples Energy Collection from Discharge to Grid, but no Operational Experience
• Need to Gain Experience by Operating at Temperatures of Today’s Plants
• Overcome Operator O&M Concerns by developing an Integrated Power Block and Robust Control Strategy
Commercialization Pathway for sCO2 Power Cycle
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• While Working on 700°C, in order to gain experience:
• Target TIT down to 550°C - 620°C (Piping not high-nickel alloy)
• Materials for Piping, tanks, ready, available and not very costly
• For turbomachinery, easier casing, impeller and seal design and fabrication
• Focus on integrated operation of turbomachinery/heat exchangers and TES for ≥1,000 hours; utility operators comfort
• Interaction of Materials, Temperature and SubComponentDesign still to be resolved
sCO2 Integration with Power Plants: Materials Issues
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Compressor
Pre-Cooler
HT Recuperator
Seals Expander
PHX
Piping Tank
Comfort Zone for Fabrication and Testing
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• Current generation plants use Nitrates as TES
• 60-40 NaNO3/KNO3; not an eutectic
• Liquidus = 222°C
• Temperature Limit ~600°C
• Low Vapor Pressure
• Reasonable Specific Heat (1.545 kJ/kg°C) and Density (>1,700 kg/m3)
• GEN3: Chloride Salt and Solid Particles for 700°C
Thermal Energy Storage Fluid
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• Similar for Parabolic Trough and Power Tower
• General Dimensions 120’(D) X 40’(H)
• getting bigger (Noor 153’ X 46’) ~18,000 m3; 2,700 MWt
• Limits on H & D Set by Soil Bearing Load (for H) and by 1.5” thickness for Steel Plates, no Heat Treat (for D)
• Bruce counts 82 Tanks built so far
• 290°C Carbon Steel Cold Tank and 565°C Stainless Steel Hot Tank Operating Temperatures
TES Tank Design for Nitrate Salt
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• Specific Requirement for CSP: Molten Salt->sCO2
• Approach Temperatures of 15-20°C Indicated
• For ~250 MWT, Shell and Tube Heat Exchangers can be quite expensive
• MicroChannel Heat Exchangers Have Not been Developed to Even Facility Scale
• Differences Between Molten Salt and sCO2 Channels for Pressure, Thermal Conductivity.
Primary Heat Exchanger
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Major Issue for sCO2 Power Block Integration with TES
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T-S Cycle Plot for Turbine Inlet temperature = 550 C
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Major Issue for sCO2 Power Block Integration with TES
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P-h Cycle Plot for Turbine Inlet temperature = 550 C
150°C
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Major Issue for sCO2 Power Block Integration with TES
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Mismatch between ΔT for TES and Optimized ΔT for sCO2 Cycle
565°C
290°C
550°C
400°CsCO2
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• Dagget, CA • Denver, CO
Ambient Air Temperatures at Representative CSP Sites
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-10
0
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20
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0 2000 4000 6000 8000 10000
Tem
per
atu
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°C)
Hour of the Year -20
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0 1728 3456 5184 6912 8640
Am
bie
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tem
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ratu
re, °C
Hour of the Year
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• Ambient Temperature + PreCooler Design Sets Compressor Inlet Temperatures
• Large Swings in Ambient temperature, both, on a Daily basis and Seasonal Basis
• Traditional A-Frame Air Coolers: Can they Can Maintain Compressor Inlet Temperature in the 35-40°C?
• MicroChannel ACHEs have not Been Designed
• Reduced PreCooler approach Temperatures and ΔP Needed for Maximum Cycle Efficiency.
Operating sCO2 Cycles with Air Coolers
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• Steady State Cycle Efficiency Decreases with Increasing Ambient Air Temperature
• Compressor Head Flow Curve and impact on wide range Performance
Ambient Air Temperatures at Representative CSP Sites
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0.38
0.385
0.39
0.395
0.4
0.405
0.41
0.415
0.42
0.425
0.43
20 25 30 35 40 45 50
Cyc
le E
ffic
ien
cy
Ambient Temperature, °C
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• Realized that Cost Competitive sCO2 cycles will need to be at higher Turbine Inlet Temperatures
• Lower capital costs due to simplicity and smaller size; addressed by Nate in a following presentation
• Lower (or zero) use of water, due to compatibility with dry cooling
• 4X more compact design or footprint (permitting more operational flexibility, rapid startup and shutdown)
sCO2 Cycles Need to be Competitive with Steam
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System Temperature (oC) Conversion Efficiency Capital Cost ($/kWe)
Super-critical Steam 540 – 620 ~40-45% 1,200
Super-critical CO2 550 - 649 ~41-46% <900
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sCO2 Cycles Need to be Competitive with Steam
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Dostal V., Driscoll M. J., P. Hejzlar and N. E. Todreas, A Supercritical Carbon Dioxide Cycle for Next Generation Nuclear Reactors, MIT-ANP-TR-100, March (2004).
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• Higher Turbine Inlet Temperature (Equivalent to Higher HTF Temperature)
Means to Higher Power Cycle Efficiency
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0.43
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0.46
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0.48
0.49
0.5
500 550 600 650 700 750 800
Po
wer
Cyc
le E
ffic
ien
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HTF Inlet Temperature into PHX
UA=2000 UA=3000
Power Cycle Efficiency as a Function of HTF inlet Temperature, for Varying Recuperator UA; Compressor
Inlet Temperature = 40°C; Turbine Efficiency = 91%; Main Compressor, Recompressor Efficiency = 85%
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• Higher recuperation is Probably not as effective
Means to Higher Power Cycle Efficiency
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0.42
0.43
0.44
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0.47
0.48
10000 15000 20000 25000 30000 35000 40000
Effi
cien
cy
UA (kW/K)
T_HTF=574 T_HTF=600 T_HTF=625 T_HTF=650
Power Cycle Efficiency as a Function of Recuperator UA, for a range of HTF temperatures Compressor
Inlet Temperature = 40°C; Expander Efficiency = 91%; Compressor(s) Efficiency = 85%
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• Turbine Efficiency has a Significant Impact
Means to Higher Power Cycle Efficiency
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Power Cycle Efficiency as a Function of Expander Efficiency, for Varying HTF Temperature;
Compressor Inlet Temperature = 40°C; Main Compressor, Recompressor Efficiency = 85%;
UA = 3,000 kW/K
0.41
0.42
0.43
0.44
0.45
0.46
0.47
0.84 0.85 0.86 0.87 0.88 0.89 0.9 0.91 0.92
Cyc
le E
ffic
ien
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Turbine Efficiency
T_HTF = 574 T_HTF = 600 T_HTF = 620
Current SOA
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• Compressor efficiencies somewhat Less So
Means to Higher Power Cycle Efficiency
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Power Cycle Efficiency as a Function of Compressor Efficiency, for HTF Temperature of
574°C; Compressor Inlet Temperature = 40°C; Expander Efficiency = 91%; UA = 3,000
kW/K
0.43
0.435
0.44
0.445
0.77 0.78 0.79 0.8 0.81 0.82 0.83 0.84 0.85
Cyc
le E
ffic
ien
cy
Compressor Efficiency
MC Efficiency RC Efficiency
Current SOA
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• Higher Expander Efficiency requires Careful Turbomachinery Packaging and Reduced Expander Leakage
• Compressor and Expander development at a stage that Single Shaft/Single Casing Designs can Be Considered
• Packaging and reduction of seal count easier at 550 C than 700 C; give vendors breathing room
• Robust Control Strategy
Integrated Turbomachinery
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• Determine the scope of the Conceptual Research Effort
• Size of the Power Block
• Size of TES
• Ultimate Heat Sink Definition: Air Cooling Only or Cold Storage to Allow a Broader testing Program
• Turbomachinery Enhancements Considering the Narrowed Scope of Turbine Inlet Temperature (550-620°C)
• Heating the TES Fluid: FiredGas Heater or Pumped Thermal or Electrical?
• If a broader TIT (550-620 C) considered, methods for heating sCO2
Goals of the Workshop (1)
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• Turbomachinery Panel
• Breakout Panel Discussion discuss Steps beyond the current vendor efforts and STEP program
• Expander and Compressor Design Improvements
• Packaging Turbomachinery
• Dry Gas Seals and Bearing Subcomponents
• Power Block Size and testing hours in the Facility for Utility Operator Comfort
• O&M Reduction
• “Autonomous” Control Systems (?)
Goals of the Workshop (2)
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• Heat Exchanger Panel
• Panel discussions with Vendors in the morning
• Heat Exchanger Breakout
• Recuperators
• Primary heat exchanger design unknowns
• Air Cooler design unknown
• For Wide Range Testing Program of Compressor-PrecoolerIntegration, look at Cold Storage?
Goals of the Workshop (3)
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• Thermal Energy Storage
• Presentation on CSP experience with TES
• Facilities
• Experience in Existing Facilities Design and Operation
• Breakout Session on TES
• Nitrate Salt or ?
• Integration with sCO2 cycle a big Question mark
• How to heat the TES? Fired Heater or Grid-Heated?
Goals for this Workshop (4)
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Questions?Rajgopal Vijaykumar
[email protected] Manager, CSP, SETO