Supercritical Carbon Dioxide in Microchannel Devices for Advanced Thermal Systems Brian M. Fronk School of Mechanical, Industrial and Manufacturing Engineering Oregon State University, Corvallis, OR, USA March 30 th, 2017 Presented at Oklahoma State University
Outline 1. My Background 2. Supercritical CO 2 Solar Thermal Receivers 3. Experimental Microchannel sco 2 Heat Transfer 2
My Background 3
Oregon State University is Oregon s Land Grant university with the mission to educate the students of the state; it is a public research university with eleven colleges and the state s primary research engineering program. 196 faculty in five engineering schools $55.0M research funding in 2016 10% growth in enrollment (annual average) The College of Engineering, by the numbers: 7,120 undergraduate students 1,304 graduate students 4
School of Mechanical, Industrial and Manufacturing Engineering (MIME) By The Numbers 54 1,900+ 340+ 2x-3x Research Faculty Undergraduate Students in 4 Majors Graduate Students in 4 Majors Growth in Total Enrollment over the past 10 years 5
Research Interests System Scale Concentrated Solar Thermal Waste Heat Recovery/CCHP Solar Thermal Heating Building Energy Systems (HVAC&R) Thermal Management Devices Phenomena Scale Multiphase Heat and Mass Transfer Supercritical Heat Transfer Renewable Conversion Energy Efficiency Energy Storage 6
Concentrated Solar Power (CSP) http://www.desertsun.com/story/tech/science/energy/2015/01/22/abengoa-big-plans-solar-towers-desert/22186683/ 7
Next Gen Solar Thermal Current central receivers operate at 30 100 W cm -2 Receiver cost estimated $100-$200/kW t Future receiver improvements: Smaller and simpler design Increase thermal transfer efficiency Increase receiver exit temperature Decrease cost per kw t Leverage sco 2 Brayton Cycles Conboy T, Wright S, Pasch J, Fleming D, Rochau G, Fuller R. Performance Characteristics of an Operating Supercritical CO2 Brayton Cycle. ASME. J. Eng. Gas Turbines Power. 2012;134(11):111703-111703-12. doi:10.1115/1.4007199 8
Microchannel Receiver Concept Demonstrated 90% thermal efficiency at 2 x 2 cm scale L Estrange T, Truong E, Rymal C, et al. High Flux Microscale Solar Thermal Receiver for Supercritical Carbon Dioxide Cycles. ASME 2015 13th International Conference on Nanochannels, Microchannels, and Minichannels:V001T03A009. doi:10.1115/icnmm2015-48233. 9
Research Question Can micropin devices be scaled to megawatt capacities? 10
Numbering Up Concept Zada K. R., Hyder M. B., Drost M. K., Fronk B. M. Numbering-Up of Microscale Devices for Megawatt-Scale Supercritical Carbon Dioxide Concentrating Solar Power Receivers. ASME. J. Sol. Energy Eng. 2016;138(6):061007-061007-9. doi:10.1115/1.4034516 11
Unit-Cell Level 12
Thermal Model [9] 13
Thermal Model Q Q 3 sco 2 Q h A ( T T ) sco sco s W sco 2 2 2 16
Thermal Network Model 18
Module Level Multi-Unit Cell Module 19
Module Level 20
Flow Distribution Model 21
Module Level Results Fluid Inlet Temperature 550 C Incident flux 140 W cm -2 System Pressure 250 bar Ambient Temperature 20 C Wind Speed 2 m s -1 22
Module Level Results Fluid Inlet Temperature 550 C Fluid Outlet Temperature 720 C System Pressure 250 bar Number of Unit Cells per Module 6 Mass flow rate Varying 23
Receiver Model 250 Modules = 250 MW thermal input Zada K. R., Hyder M. B., Drost M. K., Fronk B. M. Numbering-Up of Microscale Devices for Megawatt-Scale Supercritical Carbon Dioxide Concentrating Solar Power Receivers. ASME. J. Sol. Energy Eng. 2016;138(6):061007-061007-9. doi:10.1115/1.4034516 24
Receiver Model Results Zada K. R., Hyder M. B., Drost M. K., Fronk B. M. Numbering-Up of Microscale Devices for Megawatt-Scale Supercritical Carbon Dioxide Concentrating Solar Power Receivers. ASME. J. Sol. Energy Eng. 2016;138(6):061007-061007-9. doi:10.1115/1.4034516 25
Modular Receiver Concept 26
Conclusions Pathway to megawatt scale demonstrated Modular concept advantageous Tailored receiver design Manufacturability Physical test article designs generated Pin-level CFD (Dr. S. Apte OSU) Manufacturing (Dr. B. Paul OSU) Materials/Solid Mechanics (Dr. R. Maholtra OSU) Reciever Structural Analysis (Dr. D. Borello - OSU) 27
Ongoing Work 28
Supercritical CO 2 T critical (ᵒC/ᵒF) 31.0 / 87.9 P critical (kpa/psi) 7377.3 / 1072 Applied Science, 2011, https://www.youtube.com/watch?v=-gctkten5y4 29
Supercritical CO 2 Heat Transfer 30
How to Exploit? Supercritical Brayton HVAC&R (cooling) Thermal Management? Fronk B. M., Rattner A. S. High-Flux Thermal Management With Supercritical Fluids. ASME. J. Heat Transfer. 2016;138(12):124501-124501-4. doi:10.1115/1.4034053. 31
Convective Heat Transfer Thermophysical Property Variation Buoyancy Effects Bulk Flow Acceleration Flow Profile Changes Heat Transfer Affected 32
Convective Heat Transfer D H = 10.9 mm Pidiparti et al., 2015 Stratification of low-density fluid Pidaparti S, Jarahbashi D, Anderson M, Ranjan D. Unusual Heat Transfer Characteristics of Supercritical Carbon Dioxide. 2015. ASME International Mechanical Engineering Congress and Exposition, Volume 8A: Heat Transfer and Thermal Engineering:V08AT10A040. doi:10.1115/imece2015-51225. 33
Research Objectives 1. Experimentally investigate heat transfer for single-wall applied heat flux in small diameter channels 2. Evaluate applicability of convective heat transfer correlations 3. Create a publically available database 4. Use data to verify DES models (Dr. A. Rattner PSU) 34
Experimental Facility 35
Experimental Facility 36
Test Section Design Test Section Heat Length (mm) 20 Development Length (-) 40D Hydraulic Diameter (mm) 0.75 Number of Channels (-) 5 Aspect Ratio (-) 1:1 37
Measurement Technique 38
Measurement Technique 39
Test Section Fabrication D h (mm) 0.75 AR (-) 1:1 Type Channel D h (mm) 0.75 AR (-) 2:1 Type Channel D h (mm) 0.75 AR (-) N/A Type Staggered Pin 40
Test Section Fabrication 41
Test Section Fabrication D h (mm) 0.75 AR (-) 1:1 Type Channel D h (mm) 0.75 AR (-) 2:1 Type Channel D h (mm) 0.75 AR (-) N/A Type Staggered Pin 42
Test Section Fabrication 43
Experimental Matrix D h (mm) 0.75 AR (-) 1:1 Type Channel Reduced Pressure (-) 1.03 1.1 Mass Flux (kg m -2 s -1 ) 500 500 1000 Heat Flux (W cm -2 ) 20 40 Inlet Temperature ( C) 20 100 20 100 44
Heat Transfer Results 45
Heat Transfer Results 46
Heat Transfer Results T pc 35.4 C 32.4 C 47
Single-Phase Correlations Dittus and Boelter, 1930 Wu and Little, 1984 Adams et al., 1998 48
Importance of Buoyancy? 50
Conclusions 1. Functioning supercritical facility (up to 18 Mpa & 200 C) 2. High heat transfer coefficients measured Poor correlation predictive capability (under prediction) Geometry and boundary conditions 3. Buoyancy effects potentially play a role in heat transfer 51
Ongoing Work 1. Investigation of different geometry and orientation 2. 2 nd Generation experiment Lower uncertainty Higher heat fluxes 3. Develop new test article, local HTC 52
Acknowledgments TEST Lab Students SunShot Collaborators Dr. M. K. Drost (OSU) Dr. S. Apte (OSU) Dr. B. Paul (OSU) Dr. H. Wang (OSU) Dr. R. Maholtra (OSU) Dr. V. Narayanan (UC- Davis) Dr. O. Dogan (NETL) Dr. A. Rattner 53
Questions? 54