1D AND 3D TOOLS TO DESIGN SUPERCRITICAL CO 2 RADIAL COMPRESSORS: A COMPARISON

Transcription

1 1D AND 3D TOOLS TO DESIGN SUPERCRITICAL CO 2 RADIAL COMPRESSORS: A COMPARISON B. Monje *, D. Sánchez *, M. Savill, P. Pilidis and T. Sánchez * * Thermal Power Group (GMTS) School of Engineering, University of Seville Camino de los descubrimientos s/n 41092, Sevilla, Spain Department of Power and Propulsion School of Engineering, Cranfield University Cranfield MK430AL United Kingdom

2 CONTENTS 1. INTRODUCTION 2. THE ONE-DIMENSIONAL MODEL 3. VALIDATION 4. CASE STUDY 5. FURTHER DISCUSSION 6. APPLICATIONS OF NEW GUIDELINES 7. SUMMARY AND CONCLUSIONS

3 CONTENTS 1. INTRODUCTION 2. THE ONE-DIMENSIONAL MODEL 3. VALIDATION 4. CASE STUDY 5. FURTHER DISCUSSION 6. APPLICATIONS OF NEW GUIDELINES 7. SUMMARY AND CONCLUSIONS

4 AR 1D AND 3D TOOLS TO DESIGN SUPERCRITICAL CO 2 RADIAL COMPRESSORS: A COMPARISON 1. INTRO Review of past work The Thermal Power Group at the University of Seville and the Department of Power & Propulsion at Cranfield University have researched the performance of S-CO 2 diffusers. B. Monje et al., Comparing the pressure rise of air and supercritical carbon dioxide in conical diffusers, Paper GT , Turbo Expo 2012, Copenhagen. A. López et al., Effect of turbulence intensity and flow distortion on the performance of conical diffusers operating on supercritical carbon dioxide, Paper GT , Turbo Expo 2013, San Antonio. B. Monje et al., Aerodynamic analysis of conical diffusers operating with air and supercritical carbon dioxide, International Journal of Heat and Fluid Flow, In press (2013). Cp for B th = 3% ; M th = 0.2 ; Re th = ; Tu th = 1% ; l th / th = 10 ; Z th = 0.3 L Air Dth 2θ Dout = 10º 0.74 (1) (2) 3 2 = 9º 2 = 8º S-CO 2 + K, C p = F(AR, L/D th, Re, M, B th, T u, l tu /δ, α dist, α swirl, Z, γ) 2 = 7º 2 = 6º 2 = 5º 2 = 4º B th = 3 % ; M th = 0.2 ; Re th = L/D

5 1. INTRO Review of past work The Thermal Power Group at the University of Seville and the Department of Power & Propulsion at Cranfield University have researched the performance of S-CO 2 diffusers. Outcome: understanding S-CO 2 turbomachinery design gained by exploring the design space, as done by other researchers in the past (for air). F.X. Dolan, P.W. Runstadler Jr., Pressure recovery performance of conical diffusers at high subsonic Mach numbers, NASA CR 2299, David Japikse, Turbomachinery diffusers design technology. Concepts ETI, Inc., Norwich, VT.

6 1. INTRO This work The Thermal Power Group at the University of Seville and the Department of Power & Propulsion at Cranfield University have researched the performance of S-CO 2 diffusers. Outcome: understanding S-CO 2 turbomachinery design gained by exploring the design space, as done by other researchers in the past (for air). The work presented today aims to 1. Assess the suitability of a particular 1D model to design efficient S-CO 2 compressors. 2. Use 3D-CFD analysis to determine if local flow phenomena are likely to be overlooked by a 1D tool: condensation, shock waves, choke

7 1. INTRO This work STEP 1 Diffusers: Air vs. S-CO2 2D CFD (ANSYS Fluent ) STEP 2 STEP 3 STEP 4 (Radial) Compressor: Air vs. S-CO2 0) TBD: Is the standard design practice valid for S-CO 2? Experimental validation of diffusers Matlab 1D Experimental validation of compressors Impeller + Diffuser ANSYS Fluent 3D Draft design VS. 3D design (not optimized) 1) Validation and/or comparison Design guidelines/correlations still valid? 2) If not, how do they change? 2.1) How far from expected efficiency? 2.2) New design guidelines (hopefully) developed

8 CONTENTS 1. INTRODUCTION 2. THE ONE-DIMENSIONAL MODEL 3. VALIDATION 4. CASE STUDY 5. FURTHER DISCUSSION 6. APPLICATIONS OF NEW GUIDELINES 7. SUMMARY AND CONCLUSIONS

9 2. THE ONE-DIMENSIONAL MODEL 1D Mean streamline code based on Conservation Laws and Empirical Correlations: Mass conservation Energy conservation Deviation m = ρ i v m,i A i 1 B i 2 nd principle Δs 0 0 (Stationary elements) 0,i = 0,i 1 0,i + w i 2 P 0,i = P 0,i 1 P 0,i 1 P i 1 ω (Impeller) f c = ρ 03 T 03 / ρ 02 T 02 P 03 P 02 Pressure losses P 03 = P 02 f c P 02 P 2 ω u 2 i 2 (Aungier s proposal) (Used in this work) 2 = 0,i 1 + w i 1 2 u 2 i (Stationary elements) (Rotating elements) Work input coefficients (secondary) Inducer Disk friction Contraction Incidence Leakage Diffusion from inlet to throat Choking at the throat Recirculation H Impeller Friction Aerodynamic loading Mixing processes Clearance gap flow Local shock waves on suction surfaces u 2 2 = I B + I DF + I L + I R 1 Impeller: slip factor, σ (Wiesner) Volute Friction Meridional losses Tangential losses VOLUTE Diffuser throat VANELESS SPACE Impeller throat INDUCER 2 IMPELLER 6 5 DIFFUSER 4 3 Splitter blade Full blade Diffuser Incidence Choking at the throat Friction Aerodynamic loading Mixing processes Diffuser: deviation angle, δ(howell) Compressor inlet Impeller inlet Impeller exit Diffuser inlet Diffuser exit Volute

10 CONTENTS 1. INTRODUCTION 2. THE ONE-DIMENSIONAL MODEL 3. VALIDATION 4. CASE STUDY 5. FURTHER DISCUSSION 6. APPLICATIONS OF NEW GUIDELINES 7. SUMMARY AND CONCLUSIONS

11 3. VALIDATION Validation for S-CO 2 : Centrifugal compressor at SANDIA N.L. N (rpm) T 01 (K) P 01 (bar) m (kg/s) Exp. P 3 (bar) P 05 (bar) T 05 (K) Mod. Dev. (%) Exp. Mod. Dev. (%) Exp. Mod Dev. (%) S.A. Wrigth et al., Operation and Analysis of a Supercritical CO2 Brayton Cycle, Report SAND , R.B. Vilim, A One-Dimensional Compressor Model for Super- Critical Carbon Dioxide Applications, Proceedings of ICAPP 10, Paper

12 CONTENTS 1. INTRODUCTION 2. THE ONE-DIMENSIONAL MODEL 3. VALIDATION 4. CASE STUDY 5. FURTHER DISCUSSION 6. APPLICATIONS OF NEW GUIDELINES 7. SUMMARY AND CONCLUSIONS

13 4. CASE STUDY 10 MW S-CO2 power cycle for a CSP application Compressor inlet: 85 bar & ~ 40 ºC Mass flow rate: kg/s Pressure ratio: 3:1 Design inputs: M 2s, Z FB, β 3 Optimization of η tt in the ranges Z FB =[18,30], β 3 =[30,45] and M 2s =[0.6,0.75] Design results: Z FB =24, β 3 =37.8º and M 2s =0.676 Common design inputs Inlet total temperature: 40 ºC Inlet total pressure: 85 bar Static pressure at impeller outlet: bar Number of full/splitter blades: 24/24 Splitter-full blade length ratio: 0.5 Blade thickness: constant, 1 mm Hub/Shroud inlet radius: 25/44.6 mm Impeller exit radius: 94.8 mm Impeller exit blade height: 5.1 mm Hub/Shroud blade angle at inlet: 49.9/64.71º Blade angle at impeller exit: 37.79º

14 4. CASE STUDY 10 MW S-CO2 power cycle for a CSP application Compressor inlet: 85 bar & ~ 40 ºC Mass flow rate: kg/s Pressure ratio: 3:1 Design inputs: M 2s, Z FB, β 3 Optimization of η tt in the ranges Z FB =[18,30], β 3 =[30,45] and M 2s =[0.6,0.75] Design results: Z FB =24, β 3 =37.8º and M 2s =0.676 Computation model: Single Reference Frame (SRF) Moving walls. Common design inputs Boundary conditions: Mass flow inlet, static pressure outlet and shaft speed Highly turbulent flow (Re ~ ) boundary layer refinement Given the limitation in the computational capacity, the realizable k-ε model is used No refinement in the near wall region

15 4. CASE STUDY Results (impeller) Parameter 1D CFD/1D 1D CFD/1D 1D CFD/1D 1D CFD/1D m (kg/s) 43.6 B.C B.C B.C B.C. N (rpm) B.C B.C B.C B.C. P 01 /P 04 (bar) 85.0/ / / / / / / /1.03 T 01 /T 04 (K) 333.1/408.9 B.C./ /408.4 B.C./ /335.8 B.C./ /345.9 B.C./1.02 P 1 /P 4 (bar) 82.4/ /B.C 82.3/ /B.C. 84.0/ /B.C. 83.5/ /B.C. T 1 /T 4 (K) 330.7/ / / / / / / /1.01 v 1 /v 4 (m/s) 48.9/ / / / / / / /1.12 ρ 1 /ρ 4 (kg/m 3 ) 207.8/ / / / / / / /0.89

16 4. CASE STUDY Results (impeller) Differences between 5-10 % in P&T - Underestimation at inlet & overestimation at outlet Higher discrepancies for velocities (inaccurate blockage factor?) Inlet pressure overpredicted by CFD suggests that losses are underestimated, which can be explained by: - Computation capacity Refined grids + UDRGM simultaneously? - Realizable k-ε instead of k-ω SST inaccurate friction loses - No gap in the impeller model but - from 1D: friction + tip losses = % of overall impeller losses - Condensation likely to take place UDRGM needs to be improved to model two-phase flow. Results for high speed (~86 %) confirm the existence of a saturated wet CO 2 vapour region at the throat of the impeller.

17 CONTENTS 1. INTRODUCTION 2. THE ONE-DIMENSIONAL MODEL 3. VALIDATION 4. CASE STUDY 5. FURTHER DISCUSSION 6. APPLICATIONS OF NEW GUIDELINES 7. SUMMARY AND CONCLUSIONS

18 5. FURTHER DISCUSSION A very recent contribution by MIT: Nikola Baltadjiev MSc Thesis, 2012 Influence of real-gas effects on compressor performance (mean streamline code) Gap: analysis of condensation under non-equilibrium conditions Metastable gas region added

19 5. FURTHER DISCUSSION A very recent contribution by MIT: Nikola Baltadjiev MSc Thesis, 2012 Influence of real-gas effects on compressor performance (mean streamline code) Gap: analysis of condensation under non-equilibrium conditions The work confirms the observations by Pecnik et al. (TU Delft): saturation conditions are met around the leading edge of the impeller

20 5. FURTHER DISCUSSION A very recent contribution by MIT: Nikola Baltadjiev MSc Thesis, 2012 Influence of real-gas effects on compressor performance (mean streamline code) Gap: analysis of condensation under non-equilibrium conditions The work confirms the observations by Pecnik et al. (TU Delft): saturation conditions are met around the leading edge of the impeller Proposal: a parameter is suggested to evaluate whether non-equilibrium condensation will take place: If t n time for nucleation to take place = < 1 Condensation occurs t r residence time in saturation region

21 5. FURTHER DISCUSSION A very recent contribution by MIT: Nikola Baltadjiev MSc Thesis, 2012 Influence of real-gas effects on compressor performance (mean streamline code) Gap: analysis of condensation under non-equilibrium conditions The work confirms the observations by Pecnik et al. (TU Delft): saturation conditions are met around the leading edge of the impeller Proposal: a parameter is suggested to evaluate whether non-equilibrium condensation will take place: If t n time for nucleation to take place = < 1 Condensation occurs t r residence time in saturation region It is not conclusive with regard to whether or not condensation will actually take place in a S-CO 2 compressor with close to critical inlet conditions most likely it will (?)

22 5. FURTHER DISCUSSION With respect to the gap Parameter 1D No Gap + No BL Gap + No BL No Gap + BL Gap + BL m (kg/s) B.C. B.C. B.C. B.C. N (rpm) B.C. B.C. B.C. B.C. P 01 /P 04 (bar) 75.00/ / / / / T 01 /T 04 (K) / B.C./ B.C./ B.C./ B.C./ P 1 /P 4 (bar) 73.07/ /B.C /B.C /B.C /B.C. T 1 /T 4 (K) / / / / /336.1 v 1 /v 4 (m/s) 61.28/ / / / /163.8 ρ 1 /ρ 4 (kg/m 3 ) 221.6/ / / / /278.8 Slip factor, σ Total pressure loss coefficient, Σπ

23 CONTENTS 1. INTRODUCTION 2. THE ONE-DIMENSIONAL MODEL 3. VALIDATION 4. CASE STUDY 5. FURTHER DISCUSSION 6. APPLICATIONS OF NEW GUIDELINES 7. SUMMARY AND CONCLUSIONS

24 Mach ( ) 1D AND 3D TOOLS TO DESIGN SUPERCRITICAL CO 2 RADIAL COMPRESSORS: A COMPARISON 6. APPLICATIONS OF NEW GUIDELINES Novel contributions to the design methodology Upper-bounded absolute/relative Mach number M 1 /M 1 Avoiding condensation Upper bound of pressure ratio Avoiding acceleration Condensation Maximum β beta (45º) 1,min Absolute Mach number at throat Relative Mach number at throat Maximum Mach established M th,shroud DESIGN Minimum β beta (25º) 1,max M th,shroud Design Condensation radius (m) c 1 β 1 w 1 c 1 β 1 w 1 c 1 β 1 w 1 u 1 u 1 u 1

25 Mach ( ) 1D AND 3D TOOLS TO DESIGN SUPERCRITICAL CO 2 RADIAL COMPRESSORS: A COMPARISON 6. APPLICATIONS OF NEW GUIDELINES Novel contributions to the design methodology Upper-bounded absolute/relative Mach number M 1 /M 1 Avoiding condensation Upper bound of pressure ratio Avoiding acceleration Condensation Maximum β beta (45º) 1,min Absolute Mach number at throat Relative Mach number at throat Maximum Mach established M th,shroud DESIGN Minimum β beta (25º) 1,max M th,shroud Design Condensation radius (m) N s = N Q H 3/4 D s = D H1/4 Q

26 Mach ( ) 1D AND 3D TOOLS TO DESIGN SUPERCRITICAL CO 2 RADIAL COMPRESSORS: A COMPARISON 6. APPLICATIONS OF NEW GUIDELINES Novel contributions to the design methodology Upper-bounded absolute/relative Mach number M 1 /M 1 Avoiding condensation Upper bound of pressure ratio Avoiding acceleration Condensation Maximum β beta (45º) 1,min Absolute Mach number at throat Relative Mach number at throat Maximum Mach established DESIGN Minimum β beta (25º) 1,max M th,shroud Design Condensation M th,shroud radius (m) Need to increase the number of blades due to high aerodynamic loading Need to add splitter blades due to high aerodynamic loading

27 CONTENTS 1. INTRODUCTION 2. THE ONE-DIMENSIONAL MODEL 3. VALIDATION 4. CASE STUDY 5. FURTHER DISCUSSION 6. APPLICATION OF NEW GUIDELINES 7. SUMMARY AND CONCLUSIONS

28 7. SUMMARY AND CONCLUSIONS The analysis of air vs. S-CO2 conical diffusers shows substantial differences between both fluids A 1D tool for centrifugal compressor design is implemented and used to produce a reference S-CO2 compressor validation to the extent possible 1D vs 3D differences are large enough to suggest that standard design rules might not be applicable if efficiencies comparable to contemporary air compressors are sought. Some complements to ANSYS Fluent are necessary in order to properly simulate two phase flow (likely to happen in supercritical CO2 turbomachinery) when pushing the supercritical features to the limit.

29 1D AND 3D TOOLS TO DESIGN SUPERCRITICAL CO 2 RADIAL COMPRESSORS: A COMPARISON Thank you Q&A David Sánchez ds@us.es B. Monje *, D. Sánchez *, M. Savill, P. Pilidis and T. Sánchez * * Thermal Power Group (GMTS) School of Engineering, University of Seville Camino de los descubrimientos s/n 41092, Sevilla, Spain Department of Power and Propulsion School of Engineering, Cranfield University Cranfield MK430AL United Kingdom