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274 iitb 274 corrected

  1. 1. Studies on Suitability of Heat Exchanger to Solar Receivers for Solar Thermal Power Applications D.R.RAJENDRAN & R.PACHAIYAPPAN Asst. Professor/ Mechanical Engg, Adhiparasakthi Engineering College, Melmaruvathur - 603 319. Tamilnadu.
  2. 2. INTRODUCTION Thermal power generation from concentrated Solar Power (CSP) is based on the solar collector technologies. The important technologies are Point focusing (dish or concentrated) type, line focusing (trough and Fresnel) type
  3. 3.  The point focusing or parabolic concentrators need the receiver with internal cavity absorber and heat transfer system design with limited length and diameter.  To improve heat transfer area and convective heat transfer  To enhance overall heat transfer co efficient by Nano fluid  The line focusing collectors are not limited by its receiver length with respect to the trough type.  To increase the heat transfer area with different configuration by porous discs.  To improve Nusselt number by turbulence and drag coefficient for better heat transfer rate.
  4. 4. METHODOLOGY • Literature review for existing models • Design and fabrication of Shell and Helical tube Heat exchanger • Model and Analyze of porous disc line receiver with CFD • Simulate the system with different design configurations, working fluids and materials • Find the parameters for maximum efficiency
  5. 5. LITERATURE REVIEW Sl. No . Journal Name 1 Energy (ELSEVIER) 2 Author(s) Marthew Neber , Hohyun Lee Modification / Material, Tools used Observations in Experiment Results Silicon carbide cylindrical receiver over coiled heat exchanger L/D =2 Temperature achieved is 1270 k and effectiveness 0.82 International Fuqiang Wang Journal of Yong Shuai. Heat and Mass Transfer (ELSEVIER) Porous Media Receiver Influence of Heat flux Radiation Concentrated direction features of the focal flux affects the radiation flux distribution of cavity receiver. 3 Solar Energy Ramon Ferreiro Gareia, A.Coronal Internal cavity Structure, Porosity heat transfer surface for closed loop and open loop cycle. 4 Solar Energy A.Carotenuto , Multi cavity Volumetric F.Renle solar Receiver Emittance and .absorptance properties are improved, The Cavity Energy balance for a control minimize volume of air and wall. convective, radiative Thermal performance is find out. losses and improve the radiation absorption
  6. 6. LITERATURE REVIEW CONTD…. Sl. No . Journal Name Author (s) Modification / material, Tools used 5 Renewable Energy Y.L.He , Z.O. Cheng. parabolic The domed quartz window is concentrator used to maintain high pressure with hexagonal inside the pressure vessel. entrance, domed quartz window. The 3-d structure volumetric air receiver are capable of absorbing high solar flux operating at temperature range of 800 to 10000c Pressure of 1,5 Mpa 6 Solar Energy X.Daguenet_ Friek A.Toutant G.Olalde The 2-stage Straight Fins are increase the absorber with heat exchange area divided modules with SiC channels with straight Fins Increase the heat Transfer coefficient and better mean temperature is obtained Janna Martirek , Refractory material with insulation. 7 8 Solar Energy Applied M.J.Montes, Tube Receiver thermal A.Roviraeval engineering Observations in Experiment Results ɳoverall =40 % Predicted efficiency (ɳth) =32% Calculating the energy emitted by For small scale level up to 1MW the inner surface of the receiver Absorbing cavity configuration solar power . with 3-5 large tube in semi cirle is better in thermal performance. Maintain Uniform Heat Transfer throughout the receiver. More uniform temperature are achieved at the outlet of the all circuits reducing heating up of central surface.
  7. 7. LITERATURE REVIEW CONTD…. Sl. No . 9 Journal Name Applied Energy Author (s) Modification / material, Tools used Observations in Experiment Results Uniform heat flux is applied over the entire surface of the receiver which increases the overall heat transfer co efficient and Nu with pressure drop. K.Ravikumar K.S.Reddy Porous disc receiver with Various geometry Heat transfer rate in terms of Nu convective heat transfer co-efficient increased by porous medium 10 International R.Kandasamy journal of L.Muhaimin thermal ev.al sciences Cu-nanofluid over a porous wedge Unsteady Hiemeuz flow of Improve receiver performance Cu-nanofluid in the presence and absorption of thermal startification , due to solar energy radiation; Lie group transformation. International Fengwu Bai 11 Journal of Thermal Sciences silicon carbide ceramic foam The air flow resistance increases obviously with increasing air outlet temperature One dimensional analysis of flow and heat transfer process of ceramic foams suggest that there exists an input solar energy flux limit for the unpressurized system, which will lead to limit the power capacity and the outlet air temperature enhancement.
  8. 8. Pictures of Experimental Work Shell and helical tube heat exchanger with Ag-H2O Nano HTF
  9. 9. Optimization of parameters using Taguchi analysis Range of parameters Sl.No. Parameters Parameters Range 1. 2. 3. Tube side flow rate Shell side flow rate Volume Fraction 1-2 lit/min 1-2 lit/min 0.1-0.3 % Orthogonal array Sl. No. 1 2 3 4 5 6 7 8 9 Tube Side Flow Rate, lpm 1.0 1.0 1.0 1.5 1.5 1.5 2.0 2.0 2.0 Shell Side Flow Rate, lpm 1.0 1.5 2.0 1.0 1.5 2.0 1.0 1.5 2.0 Volume Fraction, % 0.1 0.2 0.3 0.2 0.3 0.1 0.3 0.1 0.2
  10. 10. RESULTS AND DISCUSSIONS Scat t er plot of Over all Heat t r ansf er coef f icient f or var ious f luid medium Ov e r a ll He a t Tr a n s f e r Co e f f ic ie n t ( Uo ) 1500 Variable Water Ag-water nanofluid 1250 1000 750 500 1.0 1.2 1.4 1.6 Mass Flow Rat e (mh) 1.8 2.0
  11. 11. RESULTS AND DISCUSSIONS Scat t erp lo t o f Overall h eat t ran sf er co ef f icien t vs mass f lo w rat e o f co ld f lu id Ov er all Heat T r ansf er Coef f icient ( Uo) 1400 Variable Mass flow rate of hot fluid= 1 lpm Mass flow rate of hot fluid= 1.5 lpm Mass flow rate of hot fluid= 2 lpm 1300 1200 1100 1000 900 800 700 1.0 1.2 1.4 1.6 1.8 Mass f low r at e of cold f luid ( mc) 2.0
  12. 12. RESULTS AND DISCUSSIONS Scat t er plot over all heat t r ansf er vs mass f low r at e of hot f lu id Ov e r a ll He a t Tr a n sf e r Co e f f icie n t ( Uo ) 1400 Variable Volume Fraction = 0.1 % Volume Fraction = 0.2 % Volume Fraction = 0.3 % 1300 1200 1100 1000 900 800 700 1.0 1.2 1.4 1.6 1.8 Mass Flow Rat e of Hot Fluid ( mh) 2.0
  13. 13. Porous Disc ReceiverSimulation
  14. 14. HEAT TRANSFER AND FLUID FLOW ANALYSIS OF RECEIVER The following boundary conditions are applied in the receiver model: Inlet Boundary Conditions.  The flow is having uniform velocity at atmospheric temperature at the receiver inlet.  U = u , T = T = 300K at L = 0, 0 ≤ r ≤ d /2, -90° ≤ θ ≤ 90° in f in i  Wall boundary conditions:  No – slip condition exist at inside the pipe wall u = 0 at r = di/2, -90° ≤ θ ≤ 90°, 0 ≤ L ≤ 2.  A uniform heat flux is applied of the receiver is subjected to The top half periphery of the receiver is subjected to q"ut = Ig at r = do/2, 0≤ θ ≤ 90°; 0 ≤ L ≤ 2
  15. 15. Heat Transfer And Fluid Flow Analysis  The bottom half periphery of the receiver is subjected to • q"ub = CR x Ib at r = do/2, -90°≤ θ ≤ 0; 0 ≤ L ≤ 2 • Where CR = Ap/Ar, Ig = 800 W/m², Ib = 600 W/m². • Zero pressure gradient condition is employed across the outlet boundary.  The following porous medium parameters are considered for the analysis: • • Porosity Permeability : φ = 0.37; : Kp = 2.9 x 10-10; • Form Coefficient : F = 0.24;
  16. 16. Meshed Receiver With Different Orientations Meshed Receiver with Full Porous Disc Meshed Receiver with Top half porous disc Meshed Receiver with Bottom half Porous disc Meshed Receiver with Alternate Half Porous disc
  17. 17. Results And Discussions For Porous Disc Receiver
  18. 18. Results And Discussions For Porous Disc Receiver
  19. 19. Results And Discussions For Porous Disc Receiver
  20. 20. CONCLUSION    The study found that the use of Nano fluid (Ag +water ) instead of water as a heat transfer fluid increases the overall heat transfer coefficient . Increasing the shell side flow rate(water) and helical tube (Nano fluid) side flow rate to 2 lpm and 1.5 lpm respectively increased the overall heat transfer coefficient to 1383.905 w/m2k The volume fraction of the Nano material in the mixture is 0.1% for maximum heat transfer coefficient.
  21. 21.  In the numerical investigation of silicon carbide (SiC) porous disc line receiver found that, the maximum heat transfer was in top half and then, in alternate of top and bottom half discs, which are increasing the heat transfer area, thermal conductivity and turbulence.  The study also explored that the Nusselt number for porous disc receiver is higher than that the tubular receiver for all the Reynolds number in this study.  The increase of the Nusselt number increases the overall heat transfer coefficient.
  22. 22. REFERENCE      Qi Li, Gilles Flamant, Xigang Yuan, Pierre Neveu, Lingai Luo,(2011) compact heat exchangers :A review and future applications for a new generation of high temperature solar receivers, International Journal of Renewable and Sustainable Energy Reviews, 15, pp. 4855-4875. Matthew Neber, Hohyun Lee, (2012) Design of a high temperature cavity receiver for residential scale concentrated solar power, International Journal of Energy, 47, pp. 481-487. Kandasamy.R, Muhaimin.I, Azme B.Khamis, Rozaini bin Roslan(2013) Unsteady hiemenz flow of Cu- nanofluid over a porous wedge in the presence of thermal stratification due to solar energy radiation: Lie group transformation, International Journal of Thermal sciences, 65, pp. 196-205. Buongiorno, (2006) Convective transport in Nano fluid, International Journal of Heat Transfer, 128, pp. 240-250. Ravi Kumar. K, Reddy.K.S, (2009) Thermal analysis of solar parabolic trough with porous disc receiver, International Journal of Solar Energy, 86, pp. 18041812.
  23. 23. REFERENCE Cont….      Daguenet-Frick.X, Toutant. A, Bataille.F, Olalde.G, (2013) Numerical investigation of a ceramic high-tempe rature pressurized-air solar receiver, International Journal of Solar Energy, 90, pp. 164-178. Janna Martinek, Alan W.Weimer, (2013) Design considerations for a multiple tube solar reactor, International Journal of Solar Energy, 90, pp. 68-83. Fuqiang Wang, Yong Shuai , Heping Tan , Chunliang Yu (2013) Thermal performance analysis of porous media receiver with concentrated solar irradiation, International Journal of Heat and mass Transfer, 62, pp. 247-254. He.Y.L, Cheng. Z.D, Cui. F.Q, Li. Z.Y, Li. D,(2012) Numerical investigations on a pressurized volumetric receiver: Solar concentrating and collecting modelling, International Journal of Renewable Energy, 44, pp. 368-379. Carotenuto A, Reale F, Ruocco G, Nocera U and Bonomo F (1993) Thermal behaviour of a multi-cavity volumetric solar receiver: Design and Tests result, Solar energy, 50, pp.113-121.
  24. 24. PLEASE….any