Springer Proceedings in Energy

Suneet SinghVenkatasailanathan Ramadesigan   Editors

Advances in Energy Research, Vol. 2Selected Papers from ICAER 2017

Springer Proceedings in Energy

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Suneet Singh • Venkatasailanathan RamadesiganEditors

Advances in EnergyResearch, Vol. 2Selected Papers from ICAER 2017

123

EditorsSuneet SinghDepartment of Energy Scienceand EngineeringIndian Institute of Technology BombayMumbai, Maharashtra, India

Venkatasailanathan RamadesiganDepartment of Energy Scienceand EngineeringIndian Institute of Technology BombayMumbai, Maharashtra, India

ISSN 2352-2534 ISSN 2352-2542 (electronic)Springer Proceedings in EnergyISBN 978-981-15-2661-9 ISBN 978-981-15-2662-6 (eBook)https://doi.org/10.1007/978-981-15-2662-6

© Springer Nature Singapore Pte Ltd. 2020This work is subject to copyright. All rights are reserved by the Publisher, whether the whole or partof the material is concerned, specifically the rights of translation, reprinting, reuse of illustrations,recitation, broadcasting, reproduction on microfilms or in any other physical way, and transmissionor information storage and retrieval, electronic adaptation, computer software, or by similar or dissimilarmethodology now known or hereafter developed.The use of general descriptive names, registered names, trademarks, service marks, etc. in thispublication does not imply, even in the absence of a specific statement, that such names are exempt fromthe relevant protective laws and regulations and therefore free for general use.The publisher, the authors and the editors are safe to assume that the advice and information in thisbook are believed to be true and accurate at the date of publication. Neither the publisher nor theauthors or the editors give a warranty, expressed or implied, with respect to the material containedherein or for any errors or omissions that may have been made. The publisher remains neutral with regardto jurisdictional claims in published maps and institutional affiliations.

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Preface

This proceedings contains selected papers presented in the 6th InternationalConference on Advances in Energy Research (ICAER 2017), which was held at IITBombay, Mumbai, India, from 12 to 14 December 2017. The biennial conferencehas been organised since 2007, for providing a common platform for theresearchers in the field of energy and allied domains. The conference was inau-gurated by the honourable Union Minister of Petroleum and Natural Gas and SkillDevelopment and Entrepreneurship, Shri. Dharmendra Pradhan, and was presidedover by Prof. Devang Khakkar, Director, IIT Bombay. The Department of EnergyScience and Engineering (DESE) has been organising the biennial conference,which serves as an excellent forum to present new findings, exchange novel ideas,discuss new developments and finally reflect on the challenges that lie ahead in linewith the vision of the department “To develop sustainable energy systems, solutionsand workforce for the future”. DESE has developed several novel education pro-grammes focussing on the application of science and engineering to problems inenergy.

Various aspects of energy research, including but not limited to renewableenergy, energy storage, energy efficiency and modelling, energy policy and con-ventional energy, are covered in this conference. This conference throws light onvarious recent accomplishments by researchers worldwide in the areas of solarthermal, thermal storage, solar PV with new materials, novel batteries, biofuel-based transportation and rural energy needs, to name a few. More than 420 sub-missions were received, and a rigorous peer review process was followed foracceptance of the papers. About 150 papers were accepted for oral presentation, andaround 110 papers were accepted in the poster category in the conference based onthe reviews received. This proceedings is divided into two volumes. Volume 1contains papers from topics related to solar photovoltaics, energy storage andconversion and energy efficiency and management. Volume 2 contains papers fromtopics related to renewable energy other than solar photovoltaics; IC engines,biofuels and other conventional energy; and power electronics and microgrids.

v

We would like to take this opportunity to thank all the invited speakers, dele-gates, sponsors, the members of the organising and advisory committee and mostimportantly the students and the staff of DESE for their dedicated efforts inorganising this conference. These papers represent the most recent research on thesubject. The editors would like to thank all the authors and the anonymous refereesfor paying attention to the quality of the publications. We express our gratitude forthe financial support and sponsorship from government agencies and industries—ONGC, SERB-DST, EESL, NCPRE-IITB, IMASE-IITB, Pine Instruments,BioLogic, Cummins, HHV and NPCIL. The awards were sponsored by the RoyalSociety of Chemistry (RSC) and Springer. The publication of the issue will surelyamplify the conference outcome and generate a much larger discussion and sci-entific progress. The contents of this proceedings reveal the breadth of currentactivities in different themes related to energy. We hope they form a useful startingpoint for beginners as well as practitioners in this discipline.

Mumbai, IndiaDecember 2017

Suneet SinghVenkatasailanathan Ramadesigan

(Organising Secretaries, ICAER 2017)

vi Preface

Contents

1 Mathematical Modeling of Heat Losses from Cylindrical CavityReceiver in Solar Parabolic Dish . . . . . . . . . . . . . . . . . . . . . . . . . . . 1R. Sinha and N. P. Gulhane

2 Performance Evaluation of Latent Heat Storage Filledwith Paraffin Wax for Solar Thermal Applications . . . . . . . . . . . . . 13D. Gudeta, S. R. Jena, P. Mahanta and P. S. Robi

3 Performance Analysis of Spiral and Conical Receiversfor the Paraboloidal Dish Collector Using CFD . . . . . . . . . . . . . . . 23Rashmi R. Joshi, Sandeep S. Joshi, Nilesh S. Wakchaureand Akshay C. Suryawanshi

4 Performance Analysis of Phase Change Material Storage Systemfor Solar Thermal Applications . . . . . . . . . . . . . . . . . . . . . . . . . . . . 35Sneha Murali, R. P. Saini and Ambuj Punia

5 Exergy and Energy Analysis of a Packed Bed Thermal EnergyStorage System with Different Heat Transfer Fluids . . . . . . . . . . . . 49Ambuj Punia, R. P. Saini and Sneha Murali

6 Performance Analysis of Parabolic Trough Solar Collectorwith ‘U’-Tube and Helical Coil Receivers . . . . . . . . . . . . . . . . . . . . 59Mohd. Mubashshir Naved, Sandeep S. Joshi and Nikhil A. Bhave

7 Performance Evaluation of an Improved Dual PurposeSolar Collector . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 67P. P. Krishnaraj and P. Arun

8 Experimental Investigation on Farmer-Friendly Hybrid Dryerfor Indoor Drying of Mushroom . . . . . . . . . . . . . . . . . . . . . . . . . . . 81K. Sharma, S. Kothari, N. L. Panwar, N. Rathore and K. Samar

vii

9 Wind Speed Forecasting Using New Adaptive RegressiveSmoothing Models . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 93Parikshit G. Jamdade, Prasad A. Godse, Prathamesh P. Kulkarni,Sujay R. Deole, Sudesh S. Kolekar and Shrinivas G. Jamdade

10 Thermal Performance Analysis of a Heat Pump-BasedPhotovoltaic/Thermal System . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 103S. Vaishak and Purnanand V. Bhale

11 Overall Performance of N Partially Covered PhotovoltaicThermal-Compound Parabolic Concentrator (PVT-CPC)Collector with Different Concentration Ratio . . . . . . . . . . . . . . . . . 113Rohit Tripathi, Abhishek Tiwari and G. N. Tiwari

12 Thermo-Hydraulic Performance of Solar Air HeaterRoughened with V-Shaped Ribs Combined with V-ShapedPerforated Baffles . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 123Vijay Singh Bisht, Anil Kumar Patil and Anirudh Gupta

13 Highly Efficient Solar Steam Generation Using CarbonCloth System . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 133M. W. Higgins, A. R. Shakeelur Rahman and Neetu Jha

14 Floating Absorber Integrated with Compound ParabolicConcentrator for Effective Solar Water Desalination . . . . . . . . . . . 141Chandan and Bala Pesala

15 Study of Performance of Solar Flat Plate CollectorUsing Al2O3/Water Nanofluids . . . . . . . . . . . . . . . . . . . . . . . . . . . . 149Pankaj Raj, Geleta Fekadu and Sudhakar Subudhi

16 Thermo-Hydraulic Performance of Solar Air Heater DuctProvided with Conical Protrusion Rib Roughnesses . . . . . . . . . . . . 159Tabish Alam, Ashok Kumar and Nagesh B. Balam

17 Flocculation–Solar Distillation—an Integrated Energy-EfficientTechnology for Desalination of Seawater . . . . . . . . . . . . . . . . . . . . 169Devlina Das and Nilanjana Mitra

18 Macro-Encapsulation of PCM Integrated with Double-PassSolar Air Heater System . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 181Arun K. Raj, M. Srinivas and S. Jayaraj

19 Studies on Biomass Torrefaction for Energy Densificationof the Fuel . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 195Pradeep Kumar Budde and Jay Pandey

20 Experimental and Theoretical Investigation of Different Coatingon the Performance of the Parabolic Trough Collector . . . . . . . . . . 205K. H. Motwani and J. R. Patel

viii Contents

21 Optically Enhanced Solar Selective and Thermally StableAbsorber Coating for Concentrated Solar ThermalApplication . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 217S. R. Atchuta, B. Mallikarjun and S. Sakthivel

22 Liquid Desiccant Dehumidification Using Solar RegeneratedSystem . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 229Geleta Fekadu and Sudhakar Subudhi

23 Wind Flow Simulation Over a Hilly Terrain for Wind EnergyHarvesting . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 239Ganesh Kumar, Ajay Gairola and Raghvendra Pratap Singh

24 Theoretical Modeling of Phase Change Material-Based SpaceHeating Using Solar Energy . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 251Ashwath Vaidhyanathan and N. D. Banker

25 Investigations on Improving the Efficiency of Solar Air HeaterUsing Extended Surfaces . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 261S. Babu, S. Senthilvel, F. Paul Gregory and T. Gopi

26 Productivity Enhancement of Passive Type Solar Still UsingCopper and Aluminum Based Absorber Plate with Al2O3

NanoFluid in Water Basin . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 273Amrit Kumar Thakur and V. P. Chandramohan

27 Design and Performance Investigation of Wind Turbine Bladefor Solar Updraft Tower Under Low Wind Speeds . . . . . . . . . . . . 283Ramakrishna Balijepalli, V. P. Chandramohan and K. Kirankumar

28 Numerical Analysis of Heat Transfer Enhancement in ArtificiallyRoughened Solar Air Heater . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 297Vishakha Chopade and Sharad D. Patil

29 Design and Weight Minimization of Small Wind TurbineBlade for Operation in Low-Wind Areas . . . . . . . . . . . . . . . . . . . . 311Aarti More and Anindita Roy

30 Thermohydraulic Performance of Packed Bed SolarAir Heater . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 323Parag Jyoti Bezbaruah, Doljit Borah, Rupam Patowaryand Debendra Chandra Baruah

31 Numerical Investigation on Triangular Fin-Based SolarAir Heater . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 341Parag Jyoti Bezbaruah, Aabir Das, Rajat Subhra Dasand Bikash Kumar Sarkar

Contents ix

32 Comparative Performance Assessment of a Solar Hybrid Dryerwith Traditional Drying Techniques . . . . . . . . . . . . . . . . . . . . . . . . 351Bhaskar Ranjan Tamuli and Pradyumna Kumar Choudhury

33 Numerical Study of Blade Profiles of Vertical Axis Wind Turbine(VAWT) with Bidirectional Wind Flow in Highway Roads . . . . . . 361C. ArunPrakash, P. PonsuganthIlangovan, Nitin Joyand R. Subramanian

34 CCS Combined with Geothermal Energy Generation—HybridGeothermal Energy Concept . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 369Nandlal Gupta and Manvendra Vashistha

35 Effect of Preheating and Fuel Injection Pressure on PerformanceParameters of Diesel Engine Running with Biodiesel . . . . . . . . . . . 379Menelik Walle Mekonen, Niranjan Sahoo and Santosh Kumar Hotta

36 Experimental Investigation on Range of Fuel Premixing Ratiofor Stable Engine Operation of Dual Fuel Engine Using PortInjection of Gasoline/Methanol and Direct Injection of Diesel . . . . 393Mohit Raj Saxena and Rakesh Kumar Maurya

37 Used Temple Oil, a Source for Biodiesel Production . . . . . . . . . . . . 405Sharanabasappa Saddu, Sangshetty B. Kivade and P. Ramana

38 An Experimental Study on Late PCCI Technique for ReducingNOx and Smoke Under Optimum Operating Conditionson DI Diesel Engine . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 413S. Parodwad Onkar and M. Sutaria Bharatkumar

39 An Assessment of Properties of Briquettes Producedfrom Blends of Cascabela Thevetia Seed Shell,Maize Corn Cob and Black Liquor . . . . . . . . . . . . . . . . . . . . . . . . 425Santhosh Ujjinappa and L. K. Sreepathi

40 Experimental Investigation of In-situ Biodiesel Productionfrom Castor Seeds (Ricinus communis) Using Combinationof Microwave and Ultrasound Intensification . . . . . . . . . . . . . . . . . 435Kartikkumar Thakkar, Keyur Shah, Pravin Kodgireand Surendra Singh Kachhwaha

41 Investigations on the Effects of Diethyl Ether as Fuel Additivein Diesel Engine Fueled with Tamarind Seed Methyl Ester . . . . . . 447V. Dhana Raju, P. S. Kishore and R. Subbarao

42 Effect of Nitromethane–n-Butanol–Diesel Blends on DieselEngine Emissions . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 457Naveen Kumar Sain, Ashish Nayyar, Chandan Kumar,K. B. Rana and B. Tripathi

x Contents

43 Experimental Study on CI Engine Performance for OptimumBlending Ratio of Blended Kusum Biodiesel . . . . . . . . . . . . . . . . . . 467A. G. Poshetti and M. S. Tandale

44 Preparation and Characterization of Biodiesel Extractedfrom Acidic Oil: A by-Product of Soybean Oil RefiningProcess . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 479Abhijeet P. Shah, Pankaj S. Ghatage and Rahul S. Khanase

45 Thermodynamic Analysis of Diesel Engine Primed TrigenerationConfigurations . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 489S. D. Bagade, M. N. Shelar and S. R. Mahajan

46 Investigations on Performance of CI Engine with Waste Palm OilBiodiesel-Diesel Blends Using Response Surface Methodology . . . . 505Jagannath Hirkude and Vivek Belokar

47 Design and Optimization of Air–Biogas Mixing Devicefor Dual Fuel Diesel Engines . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 515Akash Chandrabhan Chandekar and Biplab Kumar Debnath

48 Energy Response Function of Stilbene and BC501 NeutronDetection System . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 529Annesha Karmakar, S. Prasad and A. Kelkar

49 Surface Remodelling of Zeolite 4A Bodies for CO2 Capture:A Case Study . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 541Debashis Panda, Sanjay Kumar Singh and E. Anil Kumar

50 Experimental Investigation on the Feasibility of SugarcaneBagasse for Gasification . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 551Joel George, P. Arun and C. Muraleedharan

51 Quasi-Dimensional Thermodynamic Simulation Studyof Downsizing on a Four-Cylinder Turbocharged Engine . . . . . . . . 563Prajit Ravi, V. Devanandh, Sunil Kumar Pandey, K. Senthilnathan,Krishnan Sadagopan and Brijesh P. Patel

52 Numerical Simulation of Coal Char Gasification with CO2

in a Drop Tube Furnace . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 577Hrusikesh Barik, Manaswita Bose, Tao Xu, Mahmud Kibriaand Sankar Bhattacharya

53 Experimental Analysis of Performance and Emissionsof Nanofluid Dosed Pure Neem Biodiesel (PNB)—EucalyptusOil (EO)-Water (W)-Surfactant (S) Emulsion Fuelon Diesel Engine . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 587V. W. Khond, V. M. Kriplani, S. D. Butaley, Amol Pitaleand Pramod Walke

Contents xi

54 A Study on Conversion of Glycerol into Solketal Using RiceHusk-Derived Catalyst . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 599Jaspreet Kaur, Poonam Gera, M. K. Jha and Anil Kumar Sarma

55 Mathematical Model of Design and Performance Evaluationof a 210 MW CFB Boiler for Indian Lignite . . . . . . . . . . . . . . . . . . 607S. Naga Kishore, T. Venkateswara Rao and M. L. S. Deva Kumar

56 Experience of Self-powered Neutron Detectors at TAPS-3&4 . . . . . 623Manish Raj, Rajarshi Das, A. S. Pradhan, P. N. Prasadand A. K. Balasubramanian

57 Study of Kinetics and Reactivity Parameters of Indian Coaland Biomass Blends . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 633Ankit Kumar, Manjula Das Ghatak, Sujan Sahaand Prakash D. Chavan

58 Impact of Coal Quality on Post-combustion, Amine-Based CO2

Capture in Indian Coal Power Plants . . . . . . . . . . . . . . . . . . . . . . . 643Pranav C. Phadke, Anand B. Rao and Munish K. Chandel

59 3D Kinetic Model for Simulation in Real Time for Full-ScopeSimulator . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 655Suresh Kandpal, M. P. S. Fernando, A. S. Pradhan, P. N. Prasadand A. K. Balasubrahmanian

60 Flux Mapping System for Large PHWRs with Boilingat the Coolant Exit . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 669Abhishek Chakraborty, M. P. S. Fernando, A. S. Pradhan,P. N. Prasad and A. K. Balasubrahmaniam

61 CFD Simulation on the Effect of Hydrogen Mass Fractionand Initial Temperature in a CI Engine Under Hydrogen-DieselDual Fuel Mode . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 679S. Sirajuddin and R. Manimaran

62 Multi-objective Optimization of Performance and EmissionsCharacteristics of CI Engine Using Cottonseed Oilas an Alternative Fuel . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 689Milind A. Pelagade, Madhavi S. Harne and Ramakant Shrivastava

63 Effect of Compression Ratio on the Performance and EmissionCharacteristics of a Raw Biogas Fueled Spark IgnitionEngine . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 701Santosh Kumar Hotta, Niranjan Sahoo, K. Mohanty, P. Mahantaand A. J. Chaudhari

xii Contents

64 Evaluating the Sensitivity of Biomass Feedstocks to Producer GasComposition Using Stoichiometric Equilibrium Model . . . . . . . . . . 715P. Pradhan, S. M. Mahajani and A. Arora

65 Estimation and Characterization of Tar from an Open-TopDowndraft Gasifier . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 725Priyanka Tripathi, Sadhan Mahapatra and S. Dasappa

66 CO2 Capture Using Crude Glycerol-Derived Deep EutecticSolvents . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 735R. Alok, S. S. Dawn, N. Priscilla, R. Priyanka and A. Joshua

67 NOx Reduction with Coherence of Particulate Matterfor Single-Cylinder Diesel Engine Using Proportional EGRTechnique . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 745Chetan V. Bhusare and Kiran V. Chandan

68 Two-Step Modeling for Growth of Microorganisms in StirredTank Photobioreactor . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 753Raj Kumar Saini, Pramod P. Wangikar and Manaswita Bose

69 RBFN-Based MPPT Technique for PV System with High VoltageGain Four-Phase Interleaved Boost Converter . . . . . . . . . . . . . . . . 763K. Jyotheeswara Reddy and N. Sudhakar

70 Analysis and Comparative Study of Various Charging MethodsImplemented for Solid-State Marx Generator . . . . . . . . . . . . . . . . . 773Neelam S. Pinjari, S. Bindu and Ruchi D. Singh

71 Reliability Modeling of Multiphase DC–DC Boost Converter . . . . . 787D. Umarani and R. Seyezhai

72 A Novel ANN-SMC-Based Maximum Power Point Trackingfor Efficient DC Stage Conversion of a Solar PV Power Plant . . . . 803Bijit Kumar Dey, Nirabhra Mandal and Ankur Bhattacharjee

73 Coordinated Control of DC Electric Springs for Reductionof Main Grid Dependability . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 815S. Hari Charan Cherukuri, B. Saravanan and K. S. Swarup

74 A PI with Fuzzy-Based Multifunctional DSTATCOM OperatingUnder Stiff Source . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 825Sampath Kumar Pappula and Sushama Malaji

75 A Novel Three-Phase Five-Level Inverter Controland Its Performance Analysis for a Grid-ConnectedSolar PV Power System . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 839Nirabhra Mandal, Bijit Kumar Dey, Abhishek Pauland Ankur Bhattacharjee

Contents xiii

76 Enhancement of Machine Performance by DeployingSuperconductors with Numerical Analysis and UpdatedCharacteristics—A Novel Approach . . . . . . . . . . . . . . . . . . . . . . . . 851Sasidharan Srinivasan, Sethuraman Sivakumarand Krishna Kumar Rathinam

77 Analysis of Three-Phase Quasi-Switched Boost Inverter Topologyfor Renewable Energy Applications . . . . . . . . . . . . . . . . . . . . . . . . 863P. Sriramalakshmi, A. Arvindh, S. R. Sanjay Kumar,M. Prasanth and V. T. Sreedevi

78 Unbalanced Voltage Mitigation with Reactive Power Controlof Grid-Tied Solar PV System . . . . . . . . . . . . . . . . . . . . . . . . . . . . 877Swathy Pillai, Sushil Thale and Akshay Purohit

Author Index . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 893

xiv Contents

About the Editors

Suneet Singh is a faculty at the Department of Energy Science and Engineering,Indian Institute of Technology Bombay (IITB), India. He received his MTech andPhD in Nuclear Engineering from the IIT Kanpur and the University of Illinois atUrbana-Champaign, USA respectively. He completed his postdoctoral research atIdaho National Lab, USA. He has received the Bhaskara Advanced Solar Energy(BASE) Fellowship 2014 from the Indo-US Science & Technology Forum(IUSSTF). His research interests include stability analysis of nuclear reactors,advanced numerical methods for fluid flows and neutron diffusion, analyticalsolution of multilayer heat conduction problems, and solar thermal heat transfer.

Venkatasailanathan Ramadesigan is a faculty at the Department of EnergyScience and Engineering, Indian Institute of Technology Bombay (IITB), India.He received his MS in Chemical Engineering from the University of SouthCarolina, USA, and PhD in Energy, Environmental, and Chemical Engineeringfrom Washington University in Saint Louis, USA. His research interests includemodelling and simulation of chemical and electrochemical processes, electro-chemical large/grid-scale energy storage systems, system integration, nonlinearparameter estimation, and system-level optimization and control, as well asnumerical and applied mathematics.

xv

Chapter 1Mathematical Modeling of Heat Lossesfrom Cylindrical Cavity Receiverin Solar Parabolic Dish

R. Sinha and N. P. Gulhane

Abstract The recent experimental investigations on model receiver with constantheat flux boundary condition have shown that the temperature profile along the cavitywalls is non-uniform and seen to vary with cavity inclination. This paper presentsa mathematical analysis of heat losses from cylindrical cavity receiver applied toconstant heat flux boundary conditions. In addition, the empirical correlations forthe radiationNusselt number and total heat loss Nusselt numbers, with its influencingparameters like Grashof number (Gr), cavity inclination angle (θ), temperature ratio(Ta/Tw), and conductance parameter (γ ), are proposed. The mathematical analysisand empirical correlations are based on experimental results in previous publisheddata. In mathematical analysis, the heat loss by natural convection is observed tobe more sensitive to the cavity inclination angle in comparison with heat loss byradiation and conduction. The heat loss by radiation and conduction are not constantas initially estimated; they increase with increase in cavity inclination. It led us toconclude that it may not be accurate to predict convection heat loss using previouslydeveloped correlations based on the isothermalwall condition. Secondly, even thoughthe variation in heat loss by radiation and conduction with cavity inclination is small,it needs to be considered for accurate design of solar parabolic dish receiver system.

Keywords Cavity receiver · Receiver inclination · Boundary condition · Nusseltnumber correlation

R. Sinha (B) · N. P. GulhaneDepartment of Mechanical Engineering, VJTI, Mumbai, Indiae-mail: ramolasinha@somaiya.edu

R. SinhaK. J. Somaiya College of Engineering, Mumbai, India

© Springer Nature Singapore Pte Ltd. 2020S. Singh and V. Ramadesigan (eds.), Advances in Energy Research, Vol. 2,Springer Proceedings in Energy,https://doi.org/10.1007/978-981-15-2662-6_1

1

2 R. Sinha and N. P. Gulhane

Units and Symbol

Nomenclature

A Area (m2)d Cavity diameter (m)D Aperture diameter (m)g Gravitational acceleration (m/s2)h Heat transfer coefficient (W/m2-K)K Conductivity (W/m °C)L Length of cavity (m)P Power (W)q Heat flux (W/m2)T Temperature (K)θ Angle of inclination of the receiver (°)β Thermal expansion coefficient (1/°C)γ Conductance parametersε Cavity cover emissivityθ Angle of inclination of the receiver (º)υ Kinematic viscosity (m/s2)σ Stefan–Boltzmann constant (W/m2 K4)

Subscripts

a Ambientap Aperturecond Conductionconv Convectionf FilmIn Inputins Insulationrad Radiationt Thicknessw Wall

Abbreviations

AR Aspect ratioOR Opening ratioGr Grashof numberNu Nusselt number

1 Mathematical Modeling of Heat Losses from Cylindrical … 3

1.1 Introduction

The concentrating solar technology is most important as it can be used for processindustry as well as for generating power. The parabolic dish receiver assembly isone such useful system. It usually consists of a reflector in the form of a dish withdownward-facing receiver at the focus of the dish. Generally, a cavity receiver isused since it can maximize the solar radiation absorption of the concentrated solarflux and minimize heat losses [1]. The heat losses in solar parabolic dish systeminclude convective and radiative losses through the cavity opening and conductionthrough the solid structure and through the insulation used behind the cavity surfacesto reduce conduction. The heat loss due to conduction is smaller and can be calcu-lated by analytical method. The heat loss by radiation is dependent on the cavity walltemperature, the shape factors and emissivity/absorptivity of the receiver walls, whileconduction is dependent on the receiver temperature and the material used for insula-tion. The heat loss by radiation and conduction are observed to be independent of thecavity inclination [2, 3]. The heat loss by convection depends on the air temperaturewithin the cavity, the cavity inclination and the external wind velocity, and complexto estimate [4, 5]. A detailed review on the convection heat loss for different shapesof cavity, normally used in different types of engineering systems, is also availablein the literature [6]. A Nusselt number correlation was also proposed, relating cavityinclination and aperture size for a cylindrical cavity receiver [7]. On the basis ofexperimental result, another correlation of Nusselt number variation with Grashofnumber and the surface temperature of cylindrical cavitywere also developed [8]. TheAustralian National University (ANU) conducted number of experiments to studythe convection heat loss of a cylindrical cavity with isothermal surface boundary [9–11]. Subsequent experiments had confirmed the same conclusion [12]. As a result ofextensive investigation, a series of Nusselt number correlations were obtained fromexperimental results. A brief review on the natural convection in cavity receiver isavailable in the literature [6, 12–16]. The heat transfer coefficient for a rectangularcavity was also investigated by many researchers experimentally [17, 18]. Recentinvestigation result on electrically heated cylindrical cavity models tested the effectof constant heat flux and cavity inclination on the convective losses and concludedthat the heat losses are also dependent on the surface boundary conditions [19]. Inorder to better understand the mechanism of heat loss under constant heat flux, manyresearchers have studied both experimentally and numerically. Moreover, the litera-ture survey shows that most of those investigations on the heat loss of cavity werelimited to the isothermal and/or adiabatic surfaces’ boundary conditions. Abbasi-Shavazi conducted the experimental investigations on model receiver to study theconvection heat loss from a cylindrical cavity receiver, applied to a range of constantheat flux boundary condition [20]. However in the constant heat flux boundary con-dition, the temperature distribution along the cavity walls was non-uniform and wasa function of cavity inclination. The heat loss by natural convection was observed tobe more sensitive to the cavity inclination as compared to radiation and conductionheat losses.

4 R. Sinha and N. P. Gulhane

The cavity inclination has a less effect on the radiation and conduction heat losses.Also, these losses were not constant as initially estimated. It led us to conclude thatit may not be sufficiently accurate to predict convection heat loss using previouslydeveloped correlations based on isothermal boundary wall condition. Secondly, eventhough the variation in radiation and conduction heat losses with cavity inclinationis small, it needs to be considered for accurate design of cavity receiver.

However, to the author’s best knowledge, very few empirical correlations areavailable in the literature to estimate heat loss from cavity receiver subjected toconstant heat flux boundary condition. This paper presents a mathematical analysisof heat loss through solar cavity receiver, subjected to a range of constant heatflux boundary conditions. The empirical correlations of the total heat loss Nusseltnumbers and radiation heat loss Nusselt are proposed, incorporating the effectingparameters like Grashof number (Gr), inclination angle of the receiver (θ ), cavityemissivity (ε), area ratio (Ta/Tw), temperature ratio, conductance parameters (γ ), andambient temperature. The model is developed from experimental results in previouspublished data [20]. The empirical correlation can be used to estimate total heatloss and radiation heat loss from a cavity receiver, subjected to constant heat fluxboundary condition.

1.2 Analysis of Heat Loss Based on Constant Input Power

In recent experimental investigation, the heat loss frommodel cavity receiver purpose,a laboratory-scale cylindrical cavity models, was investigated. The model receivergeometric aspect ratios (cavity length to diameter) of 1 and 2 and aperture open-ing ratios (aperture diameter to cavity diameter) of 0.5 and 1 were considered. Aconstant heat flux was applied to model receiver and non-uniform temperature wasobserved inside cavity receiver [20]. During the experiment, the total power inputwasmaintained constant (equal to the power loss from cavity receiver). The system wasoperated at steady state; under steady state, the power delivered to the heating cableis lost by conduction, convection, and radiation to the surroundings, as representedin Eq. 1.1,

Pin = Pcond + Pconv + Prad (1.1)

The input power (Pin) set at the value by using power controller, and the convective(Pconv) loss must be indirectly estimated from the value of total input power (Pin),conduction power loss (Pcond), and radiation power loss (Prad). Power input Pin canbe expressed as where V is the voltage in Volt and I is current in Ampere.

Pin = V I (1.2)

To analyze the nature of heat loss from cavity receiver, heat loss by convection andradiation at different inclinationwas taken fromexperimental result. Figure 1.1 shows

1 Mathematical Modeling of Heat Losses from Cylindrical … 5

y = -0.0032x2 + 0.7719x + 32.464R² = 0.997

y = 92.385e-0.014x

R² = 0.9923

y = 0.2271x + 27.997R² = 0.9775

0

10

20

30

40

50

60

70

80

90

100

0 20 40 60 80 100

Prad

Pconv

Pcond

Poly. (Prad)

Expon. (Pconv)

Linear (Pcond)

Heat

Los

s (W

)

Inclina on angle (θ)

Fig. 1.1 Variations of heat losses with cavity inclination (θ) at constant heat flux q = 3195 w/m2

(P = 150 W) [20]

the variations of conduction, radiation, and convection power losses with inclinationunder constant input power (150 W) and aspect ratio 2 (AR = L/d) as measured inthe experiment [20]. Convection and radiation power loss is taken from experimentaldata for constant heat input 150 W, and conduction heat loss has been estimated bysubtraction heat loss by convection and radiation from heat input as in Eq. (1.1).The convection and radiation data is best fitted with second degree of polynomialand regression factor more than 0.98. However, the heat loss by conduction varieslinearly with the cavity inclination.

As shown in Fig. 1.1, the heat losses by radiation and conduction increases slightlywith the increase of cavity inclination, while the heat loss by natural convectiondecreases greatly with increase in cavity inclination. This observation reveals thatthe natural heat loss by natural convection is more sensitive to the cavity inclinationangle in comparison with the heat loss by radiation and conduction. This can alsobe observed from mathematical equation that for convection at zero inclination (θ =0) heat loss is maximum, and it decreases greatly with inclination with the order ofsecond degree of polynomial. The rate of radiation heat loss is higher as comparedto conduction heat loss, but with increase in inclination (θ), rate of radiation heatloss decreases. This variation in heat transfer is similar to the previous experimentalresults [19].

1.3 The Development of Nusselt Number Correlation

The main influencing parameters to estimate heat losses through cavity receiver suchas Grashof number (Gr) opening ratio Aap/Aw, angle of inclination (θ ), cavity walltemperature (Tw), material thickness (t), conductivity (k), and emissivity (ε) playsmajor role.

6 R. Sinha and N. P. Gulhane

From the power balance inside a cavity receiver (Eq. 1.1), we have

Pin = Pcond + Pconv + Prad

where (Pconv) is the power loss by natural convection from cavity, (Pcond) is the powerloss by conduction which is loss from the heated cavity surface to the surroundingthrough insulation and (Prad) is the power loss by radiation from the heated cavitysurface to the ambient air, and (Pin) is the total input power and can be expressed asEq. 1.1. A model receiver was examined experimentally to estimate the heat lossesfrom a model solar cavity receiver. For this purpose, laboratory-scale cylindricalcavity models with geometric aspect ratios (cavity length to diameter) of 1 and 2and aperture opening ratios (aperture diameter to cavity diameter) of 0.5 and 1 wereconsidered. Receiver was subjected to constant heat flux boundary condition, andnon-uniform temperature was observed inside cavity receiver [20].

The radiative and total Nusselt number empirical correlations have been devel-oped, relating the influencing parameters like Grashof number (Gr), cavity inclina-tion angle (θ ), cavity emissivity (ε), temperature ratio (Ta/Tw), area opening ratio(Aw/Aap), and conductance parameter (γ ). To develop the empirical correlations ofNusselt number versus the inclination, the total heat flux q is maintained constantand is taken at the power input (Pin) during the experiment. The Grashof number forthis calculation is defined as [20].

Gr = gβqd4/kaϑ2a (1.3)

The parameters like g is the gravitational acceleration, β is the coefficient ofthermal expansion of air, q is the total heat flux at power input, andϑa is the kinematicviscosity of air. Fluid properties are taken corresponding to film temperature. Wherefilm temperature, Tf = (Tw + Ta)/2 [20].

As opening ratio Aap/Aw is same in experiment and emissivity (ε) is 0.86–0.88,average value 0.87 was taken for all the data, so the variable parameter is Grashofnumber (Gr), angle of tilt (θ ), temperature ratio (Ta/Tw), and conduction resistanceparameters (γ ). The ambient temperature ((Ta) is taken as 298 K. The ratio of effec-tive thermal resistance of the solid to the thermal resistance of the fluid is taken asconduction resistance parameters (γ ) and is given by

(γ ) = [(tw/kw) + (tins/kins)]/(d/ka) (1.4)

1 Mathematical Modeling of Heat Losses from Cylindrical … 7

1.3.1 Development of Total Heat Loss Nusselt NumberCorrelation from Experimental Result

The empirical correlations for the total heat loss have been developed, relating theinfluencing parameters like Grashof number (Gr), inclination angle of the receiver(θ ), cavity emissivity (ε), temperature ratio (Ta/Tw), area opening ratio (Aap/Aw),and conductance (γ ).

For the development of the total Nusselt number correlation, the total Nusseltnumber is given by

Nutotal = Pind/Awka(Tw − Ta) (1.5)

The total Nusselt number (Nutotal) is function of Grashof number (Gr), inclinationof the receiver (θ ), cavity emissivity (ε), temperature ratio (Ta/Tw), area openingratio (Aw/Asp), and conductance parameter (γ ). The empirical correlations for totalNusselt number relating the four influencing parameters, i.e., Grashof number (Gr),angle of tilt (θ ), temperature ratio (Ta/Tw), and conductance resistance parameters(γ ) are expressed as:

Nutotal = atGrbt(1 + cos θ)ct(Aap/Aw)dt(1 + ε)et[1 − (Ta/Tw)4

]ft[1/(1 + γ )

]gt

(1.6)

Nutotal = 108.185184Gr−0.8764(1 + cos θ)0.1202[1 − (Ta/Tw)4

]−43.43247[1/(1 + γ )

]2.157

(1.7)

The total Nusselt number (Nutotal) is calculated at different inclination and thecorresponding wall temperature from Eq. 1.7 and cavity inclination (θ ). The actualtotal heat loss (Ploss) is calculated from Eq. 1.8 at calculated total Nusselt number(Nutotal), where Tw is the mean cavity surface temperature, and Aw is the total heattransfer area of the cavity wall. The variation of total heat transfer coefficient (htotal)at different inclination is estimated from Eq. (1.9) at estimated power loss (Ploss)from Eq. 1.8. The ambient temperature is taken as 298 K.

Nutotal = Plossd/Awka(Tw − Ta) (1.8)

Ploss = htotal Aw(TW − Ta) (1.9)

The change in total Nusselt number with cavity inclination is given in Fig. 1.2.

8 R. Sinha and N. P. Gulhane

y = 0.0017x2 - 0.2757x + 26.814R² = 0.9864

0

5

10

15

20

25

30

0 20 40 60 80 100

Series1

Poly.(Series1)

Fig. 1.2 Variation of total Nusselt number (Nutotal) with cavity inclination (θ)

1.3.2 Development of Radiation Heat Loss Nusselt NumberCorrelation from Experimental Result

The empirical correlations for the radiation have been developed, with the relatingparameters like Grashof number (Gr), inclination angle of the receiver (θ ), emis-sivity of cavity (ε), ratio of temperature (Ta/Tw), area opening ratio (Aap/Aw), andconductance parameters (γ ). The ambient temperature is taken as 298 K.

The radiation heat loss is small as compared to convection heat loss as given inEq. 1.10.

Prad = εaσ Aap(T 4w − T 4

a

)(1.10)

εa = 1/[1 − (1 − εw)(1 − Aap/Aw)

](1.11)

The heat loss by radiation is also an important factor that affects the performanceof a cavity receiver. The heat loss by radiation Nusselt number is given by Eq. 1.12(Wu et al. 2013). Where εa is the effective emissivity of cavity, σ is the Stefan–Boltzmann constant, and Aap is the area of opening. Effective emissivity is calculatedusing Eq. 1.11.

Nur = Pradd/[Awka(Tw − Ta)] (1.12)

By substituting Prad from Eq. (1.10) into Eq. (1.12), we have

Nurad = [εwσ Aap

(T 4w − T 4

a

)d]/[{1 − (1 − εw)(1 − Aap/Aw)

}Awka(Tw − Ta)

]

(1.13)

1 Mathematical Modeling of Heat Losses from Cylindrical … 9

y = -0.0044x2 + 0.9312x + 90.917R² = 0.9838

0

20

40

60

80

100

120

140

160

0 20 40 60 80 100

Series1

Poly. (Series1)

Cavity Incilna on (θ)

Fig. 1.3 Variation of radiation Nusselt number (Nurad) with cavity inclination (θ)

Nusselt number can be expressed with the relation given in Eq. 1.14.

Nurad = aGrbr(1 + cos θ)cr(Aap/Aw)dr(1 + ε)er[1 − (Ta/Tw)4

]fr[1/(1 + γ )

]gr

(1.14)

With Grashof number from Eq. 1.3, emissivity 0.87, conductance ration (γ ) fromEq. 1.4 and Nusselt number from Eq. 1.13, Nusselt number radiation correlation isfound to be

Nurad = 10−11aGr1.912495(1 + cos θ)−0.20818[1 − (Ta/Tw)4

]81.49707[1/(1 + γ )

]−0.28799

(1.15)

The change in radiationNusselt numberwith cavity inclination is given in Fig. 1.3.

1.4 Results and Conclusions

This paper presents a mathematical analysis of cylindrical cavity receiver heat lossunder constant heat flux cavity wall boundary conditions.

• To analyze the nature of heat loss from cavity receiver, convection and radiationheat loss at different cavity orientations has been taken from experimental result[20]. Figure 1.1 shows the variations of conduction, radiation, and convectionpower losses with inclination under constant input power (150W) and aspect ratio2 (AR = L/d) as measured in the experiment. Convection and radiation heat lossis taken from experimental data for constant power input 150 W, and conductionheat loss has been estimated by subtraction heat loss by convection and radiationfrom power input.

10 R. Sinha and N. P. Gulhane

• This can be observed from mathematical analysis result that the heat loss byconvection is maximum at zero inclination and decreases greatly with cavity incli-nation in the order of second degree of polynomial (Fig. 1.1). The conduction heatloss increases linearly with the inclination. The radiation heat losses increases inthe order of second degree of polynomial, and the heat loss by radiation decreaseswith increase in cavity inclination. The rate of heat loss by natural convection ismore sensitive to the cavity tilt angle as compared to heat loss by radiation andconduction. The heat losses by radiation and conduction are not constant as ini-tially estimated; they increase with increase in cavity inclination. This variation isvery similar to the previous experimental results [19].

• The empirical correlations for radiation and total heat loss Nusselt numbers relat-ing influencing parameters, the Grashof number (Gr), cavity inclination angle(θ), temperature ratio (Ta/Tw), and conductance parameter (γ ) are proposed onthe basis of experimental results of cavity temperature profile in model receiverobtained at 200 W power input [20]. The total Nusselt number (Nutotal) is highestat the 0◦ and slightly decreases with increase in inclination and minimum at 90°as shown in Fig. 1.2. This result is similar to heat loss from actual helical coil typecavity receiver, where maximum heat loss was observed at 0◦ and minimum at 90°[12]. The radiation Nusselt number (Nurad) is minimum at 0◦ and increases withinclination as shown in Fig. 1.3.

• Experimental investigation is necessary tomodel heat losses from cavity receivers.Initially, solar cavity receivers used for high-temperature applications were gen-erally modeled as plain walls with uniform temperature boundary conditions,where radiation and conduction were independent of inclination and observedto be constant.

• It led us to conclude that it may not be sufficiently accurate to predict convectionheat loss using previously developed correlations based on isothermal boundarywall condition. Secondly, even though the variation in heat loss by radiation andconduction with cavity inclination is small, it needs to be considered for accuratedesign of solar parabolic dish receiver system.

• A very few experiments are carried out on actual helical coil type cavity receiver,where temperature is observed to be non-uniform.More experimental investigationis required for accurate heat loss prediction from cavity receiver as it is mostimportant parameter to decide efficiency and cost-effectiveness of concentratedsolar power parabolic dish receiver system.

Acknowledgements A mathematical modeling and Nusselt number of heat loss correlation formcavity receiver are proposed on the basis of literature survey and the research work done in the pastas well as in recent years. The authors gratefully acknowledge the contribution of all the researchersand professors working in this area for giving valuable insight into the topic and guided me in rightdirection. The author acknowledges the contribution of K.J. Somaiya management for sponsoringPh. D research. The authors gratefully acknowledge the contribution of the VJTI, Mumbai ResearchFund and for giving the opportunity to explore research scope in this area.

1 Mathematical Modeling of Heat Losses from Cylindrical … 11

References

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2. W.B. Stine, C.G. McDonald, Cavity receiver heat loss measurements, in Proceedings of ASMESolar Energy Division Conference. Denver, Colorado (1988)

3. U. Leibfried, J. Ortjohann, Convective heat loss from upward and downward-facing cavity solarreceivers: measurements and calculations. ASME J. Sol. Energy Eng. 117(2), 75–84 (1995)

4. A.M. Clausing, Convective losses from cavity solar-receivers—comparisons between ana-lytical predictions and experimental results. ASME J. Sol. Energy Eng. 105(1), 29–33(1983)

5. W.B. Stine, C.G. McDonald, Cavity receiver convective heat loss, in Proceedings of theinternational solar energy society (ISES) solar world conference (Kobe, Japan, 1989)

6. S.Y. Wu, L. Xiao, Y. Cao, Y.R. Li, Convection heat loss from cavity receiver in parabolic dishsolar thermal power system: a review. Sol. Energy 84(8), 1342–1355 (2010)

7. A.A. Koenig, M. Marvin, Convection heat loss sensitivity in open cavity solar receivers. FinalReport, DOE Contract No: EG77-C-04-3985, Department of Energy, USA (1981)

8. D.L. Siebers, J.S. Kraabel, Estimating convective energy losses from solar central receivers.Sandia National Laboratories Report, SAND 84-8717 (1984)

9. T. Taumoefolau, K. Lovegrove, An experimental study of natural convection heat loss from asolar concentrator cavity receiver at varying orientation, in Proceedings of 40th Conference ofthe Australia and New Zealand Solar Energy Society (ANZSES) (Newcastle, Australia, 2002)

10. T. Taumoefolau, S. Paitoonsurikarn, G. Hughes, K. Lovegrove, Experimental investigation ofnatural convection heat loss from a model solar concentrator cavity receiver. ASME J. Sol.Energy Eng. 126(2), 801–807 (2004)

11. S. Paitoonsurikarn, K. Lovegrove, A new correlation for predicting the free convection lossfrom solar dish concentrating receivers, inProceedings of 44th ANZSESConference (Australia,2006), pp. 1–9

12. M. Prakash, S.B. Kedare, J.K. Nayak, Investigations on heat losses from a solar cavity receiver.Sol. Energy 83, 157–170 (2009)

13. M. Prakash, S.B. Kedare, J.K. Nayak, Numerical study of natural convection loss from opencavities. Int. J. Therm. Sci. 51(1), 23–30 (2012)

14. J.O. Juárez, J.F. Hinojosa, J.P. Xamán, M.P. Tello, Numerical study of natural convection inan open cavity considering temperature-dependent fluid properties. Int. J. Therm. Sci. 50,2184–2197 (2011)

15. M. Prakash, Numerical study of natural convection heat loss from cylindrical solar cavityreceivers, Hindawi Publishing Corporation, ISRN Renewable Energy Volume 2014, Article ID104686, 7 pages (2014)

16. J. Samanes, J. García-Barberena, F. Zaversky, Modeling solar cavity receivers: a review andcomparison of natural convection heat loss correlations. Energy Procardia. 69, 543–552 (2015)

17. W. Chakroun, M.M. Elsayed, S.F. Al-Fahed, Experimental measurements of heat transfercoefficient in a partially/fully open tilted cavity. ASME J. Sol. Energy Eng. 119(4), 298–303(1997)

18. W. Chakroun, Effect of boundary wall conditions on heat transfer for fully opened tilted cavity.ASME J. Heat Transf. 126(6), 915–923 (2004)

19. S.-Y. Wu, J.-Y. Guan, L. Xiao, Z.-G. Shen, L.-H. Xu, Experimental investigation on heat lossof a fully open cylindrical cavity with different boundary conditions. Exp. Thermal Fluid Sci.45, 92–101 (2013)

20. E. Abbasi-Shavazi, G.O. Hughes, J.D. Pye, Investigation of heat loss from solar cavity receiver.Energy Procedia. 69, 269–278 (2015)

Chapter 2Performance Evaluation of Latent HeatStorage Filled with Paraffin Waxfor Solar Thermal Applications

D. Gudeta, S. R. Jena, P. Mahanta and P. S. Robi

Abstract Owing to the non-uniform availability of solar radiation, designing of alatent heat storage found necessary so as to bridge the supply and demand gap. Inthe current investigation, the charging and discharging characteristics of a 10 MJcapacity, paraffin wax-based latent heat storage are analyzed numerically. Valida-tions with experimental results showed reasonably good agreement following whichparametric studies are conducted and detailed discussion on results are presented.

Keywords Charging and discharging · Latent heat storage · Paraffin wax · Meltfraction

2.1 Introduction

Due to fluctuation in solar heat flux owing to adverse weather conditions, storage ofsolar thermal energy is necessary and it provides ameans to utilize the thermal energyfor nocturnal use. Directions of research involving latent heat thermal energy storage(LHS) have become manifold ascribed to its many practically relevant applicationswhich include building heating, providing hot water for domestic needs, refrigerationapplications, drying equipment and waste heat recovery. It has innumerous advan-tages comparable to sensible energy storage (SES) device in terms of effectivenessand storage capacity. Study by Sharma et al. [1] revealed that energy storing capacityof LHS is 14 times higher than SES. There are various types of storage media forLHS out of which, paraffin wax is cheap and easily available.

Agarwal and Sarviya [2] investigated a shell and tube type latent heat storage(LHS) for solar drying application using paraffin wax as the storage medium. In

D. Gudeta · S. R. Jena · P. Mahanta · P. S. Robi (B)Department of Mechanical Engineering, Indian Institute of Technology, Guwahati 781039, Indiae-mail: psr@iitg.ernet.in

D. Gudetae-mail: dawitphd@gmail.com

P. Mahantae-mail: pinak@iitg.ernet.in

© Springer Nature Singapore Pte Ltd. 2020S. Singh and V. Ramadesigan (eds.), Advances in Energy Research, Vol. 2,Springer Proceedings in Energy,https://doi.org/10.1007/978-981-15-2662-6_2

13

14 D. Gudeta et al.

their study, the effect of flow rate and temperature of heat transfer fluid (HTF) duringcharging and discharging process were also analyzed. Kabeel et al. [3] conductedan experimental study and evaluated the energy yield and performance of a solardesalination system by comparing a conventional system with an improved LHS-based system. The result indicated that the LHS-based system showed an improvedperformance in terms of daily freshwater yield.Melting and solidification in a doublepipe heat exchanger were investigated by Jesumathy et al. [4] using paraffin wax asthemeans of storage. They reported that charging is dominated by natural convectionand discharging is dominated by conduction. Performance of a finned solar air heateris experimentally studied by Kabeel et al. [5]. The effects of variation in mass flowrate on daily and instantaneous efficiencyweremeasured. The result revealed that theefficiency increased by 10.8–13.6%. Hu et al. [6] performed a wide investigation onPCMs for investigating the thermal management of electronic devices and empha-sized on using the modularized thermal storage unit as an improvement over currentPCM-based heat sinks for cooling applications in high duty electronic equipment.

Korti and Tlemsani [7] researched a latent heat-based energy storage system withvarious types of paraffin and the effect of inlet temperature and flow rate of HTFwere studied. It was also noted that addition of engine oil to paraffin improved thecharging and discharging process by 42.4 and 66%, respectively. Experimental inves-tigations have been performed by Sobolciak et al. [8] for various compositions oflinear low-density polyethylene, paraffin wax and expanded graphite using both con-ventional and non-conventional methods. From the testing, it is found that thermalconductivity was improved by adding extended graphite. Melting process of indus-trial grade paraffin wax-based energy storage was studied by Saraswat et al. [9] bothexperimentally and numerically (using OpenFOAM). They highlighted about usingthe copper pipes along with the PCM to enhance heat dissipation rate. Salunkhe andKrishna [10] reviewed the recent works on latent heat storage materials (LHSMs)and their thermophysical properties. Further, they discussed in detail the various fac-tors affecting the life of a LHSM. Experimental studies involving paraffin wax-basedlatent heat storage with an application in forced convection solar dryer was reportedby Rabha andMuthukumar [11] and the exergy and energy efficiencies were reportedas 18.3–20.5% and 43.6–49.8%, respectively. Wahid et al. [12] provided a compre-hensive review of literatures based on the various features of the PCMs, their latestdevelopments and future directions with an application towards the building archi-tecture. Naghavi et al. [13] analyzed a solar water heating system by implementing anevacuated tube heat pipe solar collector along with latent heat storage (LHS). Resultsindicated that the system efficiency in the summer was found to be 38–42% and itshowed a fluctuation of about 8% in the rainy season. Németh et al. [14] preparedmicrocapsules containing paraffin wax and studied the various process parameters.Khan et al. [15] performed parametric investigation in a shell and tube-based thermalenergy storage to study the performance of LHS. It was observed that increase ininlet temperature increases the efficiency of the storage. Comparison study betweena naturally cooled and a storage-based latent heat cooled PV solar panels conductedby Tana et al. [16] was found that the panel temperature of the latent heat cooled shellreduced by 15 °C in comparison with a naturally cooled PV panel. It is observed from

2 Performance Evaluation of Latent Heat … 15

the above literatures that most of the studies were either numerical or experimental.However, studies including both methods were a few.

The objective of the present study is to perform the numerical analysis of a latentheat storage system (LHS) and, subsequently, to compare the results with the exper-imental model of 10 MJ capacities using paraffin wax as PCM. Various perfor-mance parameters have been analyzed during the charging/discharging process andare reported in terms of energy stored/released, variation of melt fraction, etc.

2.2 Numerical Details

2.2.1 Modelling and Assumptions

The three-dimensional sectional view of a shell and tube heat exchanger is pre-sented with paraffin wax as the phase change material (PCM) and water as the heattransfer fluid (HTF). The tube radial-thickness and tube internal diameter are main-tained as 4 mm and 14 mm, respectively, whereas the shell length and diameter aremaintained as 1000 mm and 300 mm, respectively. The data related to the thermo-physical properties of paraffinwax are taken fromNiyas et al. [15] and arementionedas follows. The properties of PCM, namely, thermal conductivity (k), specific heatcapacity (Cp), density (ρ), dynamic viscosity (μ) and latent heat of fusion (L) aremaintained as 0.25 W m−1 K−1, 2000 J kg−1 K−1, 780 kg m−3, 0.0041 kg m−1

s−1 and 168 kJ kg−1, respectively. The melting temperature and the melting rangeare maintained at 315.15 K and 3 K, respectively. While simulating the model, thefollowing assumptions were considered (Fig. 2.1).

Fig. 2.1 Flow domain