Heat transfer characteristics of rectangular heat exchanger with circular fin roughness

Heat transfer characteristics of rectangular heat exchanger with circular fin roughness | Research Square window.SnipcartSettings = { analytics: { enabled: false } }; (function() { var accessVector = localStorage.getItem('access_vector') || ''; window.dataLayer = window.dataLayer || []; if (accessVector) { window.dataLayer.push({ user: { profile: { profileInfo: { snid: accessVector } } } }); } })(); (function(w,d,s,l,i){w[l]=w[l]||[];w[l].push({'gtm.start':new Date().getTime(),event:'gtm.js'});var f=d.getElementsByTagName(s)[0],j=d.createElement(s),dl=l!='dataLayer'?'&l='+l:'';j.async=true;j.src='https://www.googletagmanager.com/gtm.js?id='+i+dl;f.parentNode.insertBefore(j,f);})(window,document,'script','dataLayer','GTM-K279D39R'); Browse Preprints In Review Journals COVID-19 Preprints AJE Video Bytes Research Tools Research Promotion AJE Professional Editing AJE Rubriq About Preprint Platform In Review Editorial Policies Our Team Advisory Board Help Center Sign In Submit a Preprint Cite Share Download PDF Research Article Heat transfer characteristics of rectangular heat exchanger with circular fin roughness Tarun Prakash Prajapati, Abhishek Kumar Gupta, Ankur Gangwar, and 2 more This is a preprint; it has not been peer reviewed by a journal. https://doi.org/ 10.21203/rs.3.rs-3927115/v1 This work is licensed under a CC BY 4.0 License Status: Posted Version 1 posted You are reading this latest preprint version Abstract The methodology of the circular fin heat exchanger has been analysis by the help of ANSYS fluent workbench and the Ansys fluent also known as computational fluid dynamics (CFD), which used to design the single heat exchanger rectangular channel with parameters. The single rectangular channel is a 605 mm long with height H = 66 mm and width is 30 mm. Under a constant heat flux of I = 1000 w/m2, a heat exchanger fin tube bank being tested. The results of this investigation lead to the following conclusions: Nusselt number improves with changes in Reynolds number when pitch distance between the circular fins used. Heat transfer grows as well as friction factor reduces with increasing Reynolds number values (Re = 2000–8000). At pitch spacing P/l = 9 mm, P 1 = 21 mm, l = 20 mm, as well as Reynolds number Re = 8000, the number of the heat transfer rate rose 5.28 times. Renewable Resources Computational Physics Theoretical Physics Energy Engineering Fan shaped circular fin Heat transfer rate friction factor coefficient and Thermal hydraulic performance Figures Figure 1 Figure 2 Figure 3 Figure 4 Figure 5 Figure 6 Figure 7 1.0 Introduction The usage of heat exchangers is common in numerous industrial operations. Mini heat exchangers are one example of effective heat transport equipment that has been developed in response to rising energy consumption and the efficient operation of thermal transportation networks. The thermodynamic efficiency of heat exchangers has been improved using many passive approaches. According to the research that has been published, turbulence promoters/VGs considerably improve a heat exchanger tube's thermal performance. L. Syam Sundaret al.[ 1 ] He observes Experimental estimates are made of the tumultuous convective energy transfer and the frictional properties of ferromagnetic Fe 3O 4 nanofluid [ 12 , 13 , 14 ] moving through a horizontal, circular tube that has been uniformly heated, with as well as with wrapped tape inserts. Halit Bas et al.[ 2 ] uses Experimental research is done on the flow of heat and friction transfer behavior in a tube with twisted tape swirl spinner installed. The tube wall is put before the twisted tapes. In the Reynolds number range of 5132 to 24,989, the impacts of the ratios of twist (y/D = 2, 2.5, 3, 3.5, and 4) and clearances rates (c/D = 0.0178 or 0.0357) are examined. N. Piriyarungrod et al. [ 3 ] investigations have been done on how inserted curved twisted tapes affect temperature transfer rate, friction factor, and other thermal performance factors [ 11 ]. Suvanjan Bhattacharyya et al. [ 4 ] uses laminar water flow over a cylindrical duct with integral diagonal ribs and outfitted with center-cleared twisted tape, laboratory findings on the amount of friction and Nusselt number have been reported. Smith Eiamsa-ard et al. [ 5 ] explains the objective of the current research is to improve the cooling qualities in an exchange tube by investigating (i) numerous twisted tapes arranged in various configurations and (ii) TiO2 nanoparticles as the working fluid at various concentrations. Mayank Uniya et al. [ 6 ] explained Highly efficient lightweight and small devices for heat transfer are in high demand as a result of recent technological advancements. Finned surfaces, which improve the rate of heat transmission, are frequently employed to meet this demand. Suvanjan Bhattacharyya et al. [ 7 ] observes laminar flow across a channel that is square fitted with diagonal cut wavy tape, the numerical coefficient of friction and Nusselt number statistics have been presented. As swirl flow movers in the square channel, fixed angles of 45° asymmetrical cut wavy fabric were used. Suvanjan Bhattacharyya et al. [ 8 ] explained numerical analysis was used to explore the effects of center-trimmed twisted tapes (CTTT) on the transfer of heat rate, friction factor, and thermal enhancement efficiency. Inside the circular duct, the center-trimmed twisted tapes served as swirl flow generators. Though the optimum performance is obtained at TR = 1.0 & 3.0, an enhanced parameter is seen for all TR in the Reynolds number ranges below 800 and above Re 4000.Suvanjan Bhattacharyya et al. [ 9 ] explained numerical analysis of the heat transmission properties in a tube with an inserted swirl generator made of twisted tape is carried out. Agung Tri Wijayanta et al. explained [ 10 ] using the findings of the experiment for a similar shape, benchmarking was carried out. The heat transmission and pressure drop properties of the improved tube were examined using attack angles of 30, 50, and 70°. [ 5 ]. J.H. Lee et al. (2007) worked on active and passive roughness [28] inserts in environment domain. This paper observed study of indoor and outdoor of buildings with CFD simulation at given parameters of design model. [ 6 ] A.D. Radford and J.S. Gero (1980) worked for improving the technology of agriculture based. In this paper found many problems of stability and sensitivity solved by design model. v [ 7 ] V. Machairas et al. (2014) presented a review on design model and method is used for calculating strength of structural buildings and also identify the characteristics of design model. [ 8 ] J. Xu et al. 2015 [ 8 ] purposed a passive building design. The paper observed net zero energy buildings by help of non sorting algorithm software. The study is based on heating and cooling process of building by experimental setup. [ 9 ] K. Negendahl et al. [ 9 ] observed performance of building with dynamics model. The simulation of building is enhanced by use of programming language and BPS (building performance simulation) to make good conclusion of combined tool model. [ 10 ] Y. Huang et al. 2016 [ 10 ] studied on the performance of design building within enveloped area and results changed with elevation of building. The building is comfortable by indoor environment of low energy consumption. This paper is based on green building design model. 2.0 Methodology The physical modelling of the single heat exchanger with circular fins shape has been designed is shown Figs. 1 (i, ii, iii, and iv). The physical modelling of the heat exchanger contains single Rectangular channel. The single rectangular channel is a 605 mm long with height H = 66 mm and width is 30 mm which is propagated in Fig. 1 . The starting of the parameter is taken as total length of the tube L = 605 mm and then entrance length L 1 = 80 mm and exit of the heat energy from L 3 = 25 mm is applied to the fin tube heat exchanger. The thickness of the arc is 4 with gap g = 3 mm to increase the rectangular channel strength. The pitch space given between the circular fin in horizontal axis is P = 60 mm, 70 mm, 80 mm, 90 mm, and 100 mm and second pitch space P 1 = 19 mm, 21 mm, and 24 mm between the circular and arc fins in vertical axis. The pitch space is also explained as a relative roughness pitch, with the length of the fin's length (l/Dh) being equal to 0.24 and the pitch space (p) being on each unit hydraulic diameter (Dh). The heat exchanger's perforated inserts are used to regulate the effect of temperature and move fluid from the heated part to the cool section. Figure 1 (i, ii, iii, and iv) shows how the heat exchanger with a fin tube bank is designed. After the heat exchanger's fin tube bank has been completely shaped, it is tested with a uniform heat flux of I = 1000 w/m2. Relative hydraulic pitch ratio P/l = 6, 7, 8, 9, and 10. Reynolds number (Re = 2000, 3500, 5000, 6500, and 8000). 2.1 Grid independence test of the meshing used This section represents the accuracy of the meshing which is applied in the meshing of the design domain. A second aspect of meshing that clarifies the tube's perfect meshing has emerged as the grid independence test. A method for determining the right meshing involves using the grid independence test. The grid independence test (0.002m size), which must be conducted to obtain correct results without any meshing error as shown in Fig. 2 , becomes known when the results do not change when the grain size meshing has become varied. 3.0 Results and Discussion 3.1 Validation of Heat transfer rate of Smooth Rectangular heat exchanger channel and Dittus-Boelter Correlations This section is essential part of the investigated numerical with or without use of circular fin in the rectangular channel so Fig. 3 provides an explanation concerning the way of Smooth tube and the Dittus-Boelter equation compare. Dittus-Boelter represents a theoretical equation of thermal transfer factor that expresses the influence of the Reynolds number, which is the number on fluid flowing through a heat exchanger channel. These comparison results are varied from 8% − 2% with Reynolds numbers Re = 2000, 3500, 5000, 6500, and 8000. Dittus-Boelter correlation: Nu = 0.023× Re 0.8 ×Pr 0.4 (1) 3.2 Effects of circular fin on rectangular heat exchanger rectangular 3.2.1 Results and Effects of Colburn J-Factor on Finned Heat Exchanger Rectangular Channel The results and effects of the circular fin heat exchanger rectangular vortex generator are calculated by the Colburn j-factor which is shown in the Figs. 4 . The Colburn j-factor is corresponding to the Reynolds number because j-factor equation is dimensionless similar to the Reynolds number when hydrodynamic applied in the heat exchanger. All the factors of the circular fin those are affected by Colburn j-factor. On the other hand, it is possible to state that the Colburn j-factor and the heat transfer coefficient are associated directly, mass transfer coefficient and friction factors. The Fig. 4 shows the minimum JF = 0.013at p/l = 6 and maximum JF = 0.021at p/e = 9 with fixed variations Re = 8000, d = 8 mm and l = 20 mm. The purpose behind the circular fin coarseness is to optimise the heat exchanger's capacity for heat transmission and prevent heat loss to the surroundings. The Fig. 5 presents the behaviour of the heat transfer rate to the environment from heat exchanger rectangular generator when circular fin with arc is inserted in the heat exchanger. The fin has variations in diameter and length to increase the performance of the heat exchanger and we obtained maximum heat transfer of 3.9, 5.2, 4.9 and 4.2 times as compared to smooth rectangular channel at d = 6 mm, 8 mm, 10 mm and 12 mm respectively at Re = 8000 and p/l = 9. In the figure we found the maximum Nusselt number as heat dissipation to environment of the complete design model. In Fig. 6 , the maximum velocity is observed 15.46 m/s in the circular fin rectangular channel when diameter d = 8 mm applied to circular fin and at Reynolds number Re = 8000. 3.3 Thermo-hydraulic performance of circular fin rectangular channel Figure 7 explains the heat exchange appliance tube's thermal hydraulic effectiveness in relation to Reynolds numbers between 2000 and 8000. The hydraulic efficiency is at its peak when = 3.47 when circular fin inserted with diameter d = 8 mm, length of the fin l = 20 mm and at Re = 8000, and Pitch space P 1 = 21 mm in vertical direction, and relative roughness pitch P/l = 9. 4.0 Conclusion The study of the transfer of heat & fluid flow via ducts using different inserts was the focus for an extensive amount in investigations in numerical study during the last few decades. In the current research, changes in the Reynolds number Re = 2000, 3500, 5000, 6500, and 8000, fluctuations in the pitch space within the inserts P = 60 mm, 70 mm, 80 mm, 90 mm, and 100 mm, and change in the measurement diameters of the circular fin, d = 6 mm, 8 mm, 10 mm, and 12 mm, were all studied numerically. With these modifications, the friction inside the heat exchanger is reduced while the rate of heat transmission throughout the heat exchanger to the outside environment is increased. As a consequence of the results, it becomes evident that the k-standard model may produce results for the study of heat conveyance and flow processes in rectangular heat exchangers having a suitable degree of engineering precision. As the Reynolds number Re = 2000–8000 rises, the heat transmission improves and the friction factor diminishes. At a fluctuation in Reynolds number Re = 2000–8000, a shift in the varied hardness raises the numbers of Nusselt as well as frictional factors in the range of 1.99-5.28and 2.33-3.55times of Plain tube, respectively. With changes in the Reynolds number and Pitch spacing between the round fins, the Nusselt number rises. The minimum Colburn j-factor JR = 0.0091 at Re = 8000, l = 10 mm and P/l = 6 and maximum JR = 0.029030547 at Re = 2000, l = 20 mm and P/l = 9 mm. With a circle-shaped fin size of 8 mm, the greatest Nusselt number has been achieved at pitch space P/l = 9 mm, P1 = 21 mm, l = 20 mm, when Reynolds number Re = 8000. At Re = 8000 and l = 10 mm, the simplest friction factor was obtained at P/l = 6 mm, d = 6 mm, and P1 = 24 mm. Best hydraulic energy efficiency was attained at Re = 8000, d = 8 mm, P/l = 9 mm, P1 = 21 mm, and l = 20 mm with a value of = 3.47. References Sundar, L. S., Kumar, N. R., Naik, M. T., & Sharma, K. V. (2012). Effect of full length twisted tape inserts on heat transfer and friction factor enhancement with Fe3O4 magnetic nanofluid inside a plain tube: An experimental study. International Journal of Heat and Mass Transfer, 55(11–12), 2761–2768. Bas, H., &Ozceyhan, V. (2012). Heat transfer enhancement in a tube with twisted tape inserts placed separately from the tube wall. Experimental Thermal and Fluid Science, 41, 51–58. Piriyarungrod, N., Eiamsa-Ard, S., Thianpong, C., Pimsarn, M., &Nanan, K. J. C. E. (2015). Heat transfer enhancement by tapered twisted tape inserts. Chemical Engineering and Processing: Process Intensification, 96, 62–71. Bhattacharyya, S., Saha, S., &Saha, S. K. (2013). Laminar flow heat transfer enhancement in a circular tube having integral transverse rib roughness and fitted with centre-cleared twisted-tape. Experimental Thermal and Fluid Science, 44, 727–735. Eiamsa-ard, S., &Kiatkittipong, K. (2014). Heat transfer enhancement by multiple twisted tape inserts and TiO2/water nanofluid. Applied Thermal Engineering, 70(1), 896–924. Uniyal, M., & Joshi, K. (2015). Numerical and Experimental Investigation Plane Fin with the Help of Passive Augmentation Method. IOSR Journal of Mechanical and Civil Engineering (IOSR-JMCE), 12(6), 48–53. Bhattacharyya, S., Chattopadhyay, H., &Benim, A. C. (2016). Heat transfer enhancement of laminar flow of ethylene glycol through a square channel fitted with angular cut wavy strip. Procedia Engineering, 157, 19–28. Bhattacharyya, S., Chattopadhyay, H., &Bandyopadhyay, S. (2016). Numerical study on heat transfer enhancement through a circular duct fitted with centre-trimmed twisted tape. International Journal of heat and Technology, 34(3), 401–406. Bhattacharyya, S., Chattopadhyay, H., &Haldar, A. (2018). Design of twisted tape turbulator at different entrance angle for heat transfer enhancement in a solar heater. Beni-Suef University Journal of Basic and Applied Sciences, 7(1), 118–126. Wijayanta, A. T., Aziz, M., Kariya, K., &Miyara, A. (2018). Numerical study of heat transfer enhancement of internal flow using double-sided delta-winglet tape insert. Energies, 11(11), 3170. Singh, H., Kishore, C., Kumar, K. N., Patil, P. P., & Avikal, S. (2021). Numerical analysis of thermal-hydraulic performance of fully developed turbulent flow in heat exchanger tube with Half Moon inserts. Materials Today: Proceedings, 46, 11182–11189. Singh, A. K., Singh, D. B., Mallick, A., Sharma, S. K., Kumar, N., & Dwivedi, V. K. (2019). Performance analysis of specially designed single basin passive solar distillers incorporated with novel solar desalting stills: a review. Solar Energy, 185, 146–164. Singh, A. K., Singh, D. B., Dwivedi, V. K., Tiwari, G. N., & Gupta, A. (2020). Water purification using solar still with/without nano-fluid: a review. Materials Today: Proceedings, 21, 1700–1706. Singh, A. K., Singh, D. B., Dwivedi, V. K., Kumar, N., & Yadav, J. K. (2018, October). A review of performance enhancement in solar desalination systems with the application of nanofluids. In 2018 International Conference on Advances in Computing, Communication Control and Networking (ICACCCN) (pp. 814–819). IEEE. Additional Declarations The authors declare no competing interests. Cite Share Download PDF Status: Posted Version 1 posted You are reading this latest preprint version Research Square lets you share your work early, gain feedback from the community, and start making changes to your manuscript prior to peer review in a journal. As a division of Research Square Company, we’re committed to making research communication faster, fairer, and more useful. We do this by developing innovative software and high quality services for the global research community. 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Also discoverable on Platform About Our Team In Review Editorial Policies Advisory Board Help Center Resources Author Services Accessibility API Access RSS feed Manage Cookie Preferences © Research Square 2026 | ISSN 2693-5015 (online) Privacy Policy Terms of Service Do Not Sell My Personal Information {"props":{"pageProps":{"initialData":{"identity":"rs-3927115","acceptedTermsAndConditions":true,"allowDirectSubmit":true,"archivedVersions":[],"articleType":"Research Article","associatedPublications":[],"authors":[{"id":270942389,"identity":"d5af4bec-e3b9-4936-9669-335406e26e88","order_by":0,"name":"Tarun Prakash Prajapati","email":"","orcid":"","institution":"Graphic Era (Deemed to be University), Dehradun, Uttarakhand 248002, India","correspondingAuthor":false,"prefix":"","firstName":"Tarun","middleName":"Prakash","lastName":"Prajapati","suffix":""},{"id":270942647,"identity":"c95aea1d-6a32-4436-a4de-8986723d5134","order_by":1,"name":"Abhishek Kumar 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channel.\u003c/p\u003e\n\u003cp\u003e(iii, and iv) Geometry of finned heat exchanger rectangular channel.\u003c/p\u003e","description":"","filename":"1.png","url":"https://assets-eu.researchsquare.com/files/rs-3927115/v1/a899d3b4c31bcee1b1abf6ed.png"},{"id":50709347,"identity":"e41d8c83-8a1a-46d8-bb3e-25265534069f","added_by":"auto","created_at":"2024-02-06 07:06:43","extension":"png","order_by":2,"title":"Figure 2","display":"","copyAsset":false,"role":"figure","size":294145,"visible":true,"origin":"","legend":"\u003cp\u003eMesh generation of design model.\u003c/p\u003e","description":"","filename":"2.png","url":"https://assets-eu.researchsquare.com/files/rs-3927115/v1/17ae50a849602b7bcb7032aa.png"},{"id":50708846,"identity":"76c80791-e1a6-4c21-a33b-da2595bbe211","added_by":"auto","created_at":"2024-02-06 06:58:43","extension":"png","order_by":3,"title":"Figure 3","display":"","copyAsset":false,"role":"figure","size":52318,"visible":true,"origin":"","legend":"\u003cp\u003eValidation between dittus-boelter corelation and smooth channel.\u003c/p\u003e","description":"","filename":"3.png","url":"https://assets-eu.researchsquare.com/files/rs-3927115/v1/3d5c5ca1d8787c5b3e9bca77.png"},{"id":50708849,"identity":"4f5224d6-0c65-4fec-bd01-804d9d8d1af0","added_by":"auto","created_at":"2024-02-06 06:58:43","extension":"png","order_by":4,"title":"Figure 4","display":"","copyAsset":false,"role":"figure","size":115600,"visible":true,"origin":"","legend":"\u003cp\u003ehas details about the colburn j-factor results at the diameter d = 8 mm of fin with length l = 20 mm.\u003c/p\u003e","description":"","filename":"4.png","url":"https://assets-eu.researchsquare.com/files/rs-3927115/v1/da60fa720d69f9a77c3a6fff.png"},{"id":50709346,"identity":"ea646c19-0d57-4869-8cc7-3827d85a9507","added_by":"auto","created_at":"2024-02-06 07:06:43","extension":"png","order_by":5,"title":"Figure 5","display":"","copyAsset":false,"role":"figure","size":102820,"visible":true,"origin":"","legend":"\u003cp\u003eexplains the increment in the heat transfer rate with Reynolds number at l = 20 mm and P/l = 9.\u003c/p\u003e","description":"","filename":"5.png","url":"https://assets-eu.researchsquare.com/files/rs-3927115/v1/0674c98830ebc158dcc6daea.png"},{"id":50708850,"identity":"b95fbe26-fbfc-47f3-9779-e91c14c9af14","added_by":"auto","created_at":"2024-02-06 06:58:43","extension":"png","order_by":6,"title":"Figure 6","display":"","copyAsset":false,"role":"figure","size":754972,"visible":true,"origin":"","legend":"\u003cp\u003eVelocity contour at l = 20 mm and d = 8 mm.\u003c/p\u003e","description":"","filename":"6.png","url":"https://assets-eu.researchsquare.com/files/rs-3927115/v1/10e7bbf38af981082d1f29d0.png"},{"id":50709348,"identity":"97599601-dfad-407b-8e69-52d6a1c54eed","added_by":"auto","created_at":"2024-02-06 07:06:43","extension":"png","order_by":7,"title":"Figure 7","display":"","copyAsset":false,"role":"figure","size":67176,"visible":true,"origin":"","legend":"\u003cp\u003eThermal hydraulic performance parameter (THPP) of rectangular heat exchanger using circular fin roughness.\u003c/p\u003e","description":"","filename":"7.png","url":"https://assets-eu.researchsquare.com/files/rs-3927115/v1/eae5baca74f0be679b1aacb4.png"},{"id":50709350,"identity":"a1242392-35bf-47de-8141-66c179b920ce","added_by":"auto","created_at":"2024-02-06 07:06:50","extension":"pdf","order_by":0,"title":"","display":"","copyAsset":false,"role":"manuscript-pdf","size":1703382,"visible":true,"origin":"","legend":"","description":"","filename":"manuscript.pdf","url":"https://assets-eu.researchsquare.com/files/rs-3927115/v1/c89e0d82-f0ba-4864-967f-cd23906821d1.pdf"}],"financialInterests":"The authors declare no competing interests.","formattedTitle":"\u003cp\u003e\u003cstrong\u003eHeat transfer characteristics of rectangular heat exchanger with circular fin roughness\u003c/strong\u003e\u003c/p\u003e","fulltext":[{"header":"1.0 Introduction","content":"\u003cp\u003eThe usage of heat exchangers is common in numerous industrial operations. Mini heat exchangers are one example of effective heat transport equipment that has been developed in response to rising energy consumption and the efficient operation of thermal transportation networks. The thermodynamic efficiency of heat exchangers has been improved using many passive approaches. According to the research that has been published, turbulence promoters/VGs considerably improve a heat exchanger tube's thermal performance. L. Syam Sundaret al.[\u003cspan citationid=\"CR1\" class=\"CitationRef\"\u003e1\u003c/span\u003e] He observes Experimental estimates are made of the tumultuous convective energy transfer and the frictional properties of ferromagnetic Fe 3O\u003csub\u003e4\u003c/sub\u003e nanofluid [\u003cspan citationid=\"CR12\" class=\"CitationRef\"\u003e12\u003c/span\u003e, \u003cspan citationid=\"CR13\" class=\"CitationRef\"\u003e13\u003c/span\u003e, \u003cspan citationid=\"CR14\" class=\"CitationRef\"\u003e14\u003c/span\u003e] moving through a horizontal, circular tube that has been uniformly heated, with as well as with wrapped tape inserts. Halit Bas et al.[\u003cspan citationid=\"CR2\" class=\"CitationRef\"\u003e2\u003c/span\u003e] uses Experimental research is done on the flow of heat and friction transfer behavior in a tube with twisted tape swirl spinner installed. The tube wall is put before the twisted tapes. In the Reynolds number range of 5132 to 24,989, the impacts of the ratios of twist (y/D\u0026thinsp;=\u0026thinsp;2, 2.5, 3, 3.5, and 4) and clearances rates (c/D\u0026thinsp;=\u0026thinsp;0.0178 or 0.0357) are examined. N. Piriyarungrod et al. [\u003cspan citationid=\"CR3\" class=\"CitationRef\"\u003e3\u003c/span\u003e] investigations have been done on how inserted curved twisted tapes affect temperature transfer rate, friction factor, and other thermal performance factors [\u003cspan citationid=\"CR11\" class=\"CitationRef\"\u003e11\u003c/span\u003e]. Suvanjan Bhattacharyya et al. [\u003cspan citationid=\"CR4\" class=\"CitationRef\"\u003e4\u003c/span\u003e] uses laminar water flow over a cylindrical duct with integral diagonal ribs and outfitted with center-cleared twisted tape, laboratory findings on the amount of friction and Nusselt number have been reported. Smith Eiamsa-ard et al. [\u003cspan citationid=\"CR5\" class=\"CitationRef\"\u003e5\u003c/span\u003e] explains the objective of the current research is to improve the cooling qualities in an exchange tube by investigating (i) numerous twisted tapes arranged in various configurations and (ii) TiO2 nanoparticles as the working fluid at various concentrations. Mayank Uniya et al. [\u003cspan citationid=\"CR6\" class=\"CitationRef\"\u003e6\u003c/span\u003e] explained Highly efficient lightweight and small devices for heat transfer are in high demand as a result of recent technological advancements. Finned surfaces, which improve the rate of heat transmission, are frequently employed to meet this demand. Suvanjan Bhattacharyya et al. [\u003cspan citationid=\"CR7\" class=\"CitationRef\"\u003e7\u003c/span\u003e] observes laminar flow across a channel that is square fitted with diagonal cut wavy tape, the numerical coefficient of friction and Nusselt number statistics have been presented. As swirl flow movers in the square channel, fixed angles of 45\u0026deg; asymmetrical cut wavy fabric were used. Suvanjan Bhattacharyya et al. [\u003cspan citationid=\"CR8\" class=\"CitationRef\"\u003e8\u003c/span\u003e] explained numerical analysis was used to explore the effects of center-trimmed twisted tapes (CTTT) on the transfer of heat rate, friction factor, and thermal enhancement efficiency. Inside the circular duct, the center-trimmed twisted tapes served as swirl flow generators. Though the optimum performance is obtained at TR\u0026thinsp;=\u0026thinsp;1.0 \u0026amp; 3.0, an enhanced parameter is seen for all TR in the Reynolds number ranges below 800 and above Re 4000.Suvanjan Bhattacharyya et al. [\u003cspan citationid=\"CR9\" class=\"CitationRef\"\u003e9\u003c/span\u003e] explained numerical analysis of the heat transmission properties in a tube with an inserted swirl generator made of twisted tape is carried out. Agung Tri Wijayanta et al. explained [\u003cspan citationid=\"CR10\" class=\"CitationRef\"\u003e10\u003c/span\u003e] using the findings of the experiment for a similar shape, benchmarking was carried out. The heat transmission and pressure drop properties of the improved tube were examined using attack angles of 30, 50, and 70\u0026deg;. [\u003cspan citationid=\"CR5\" class=\"CitationRef\"\u003e5\u003c/span\u003e]. J.H. Lee et al. (2007) worked on active and passive roughness [28] inserts in environment domain. This paper observed study of indoor and outdoor of buildings with CFD simulation at given parameters of design model. [\u003cspan citationid=\"CR6\" class=\"CitationRef\"\u003e6\u003c/span\u003e] A.D. Radford and J.S. Gero (1980) worked for improving the technology of agriculture based. In this paper found many problems of stability and sensitivity solved by design model. v [\u003cspan citationid=\"CR7\" class=\"CitationRef\"\u003e7\u003c/span\u003e] V. Machairas et al. (2014) presented a review on design model and method is used for calculating strength of structural buildings and also identify the characteristics of design model. [\u003cspan citationid=\"CR8\" class=\"CitationRef\"\u003e8\u003c/span\u003e] J. Xu et al. 2015 [\u003cspan citationid=\"CR8\" class=\"CitationRef\"\u003e8\u003c/span\u003e] purposed a passive building design. The paper observed net zero energy buildings by help of non sorting algorithm software. The study is based on heating and cooling process of building by experimental setup. [\u003cspan citationid=\"CR9\" class=\"CitationRef\"\u003e9\u003c/span\u003e] K. Negendahl et al. [\u003cspan citationid=\"CR9\" class=\"CitationRef\"\u003e9\u003c/span\u003e] observed performance of building with dynamics model. The simulation of building is enhanced by use of programming language and BPS (building performance simulation) to make good conclusion of combined tool model. [\u003cspan citationid=\"CR10\" class=\"CitationRef\"\u003e10\u003c/span\u003e] Y. Huang et al. 2016 [\u003cspan citationid=\"CR10\" class=\"CitationRef\"\u003e10\u003c/span\u003e] studied on the performance of design building within enveloped area and results changed with elevation of building. The building is comfortable by indoor environment of low energy consumption. This paper is based on green building design model.\u003c/p\u003e "},{"header":"2.0 Methodology","content":"\u003cp\u003eThe physical modelling of the single heat exchanger with circular fins shape has been designed is shown Figs.\u0026nbsp;\u003cspan refid=\"Fig2\" class=\"InternalRef\"\u003e1\u003c/span\u003e (i, ii, iii, and iv). The physical modelling of the heat exchanger contains single Rectangular channel. The single rectangular channel is a 605 mm long with height H\u0026thinsp;=\u0026thinsp;66 mm and width is 30 mm which is propagated in Fig.\u0026nbsp;\u003cspan refid=\"Fig2\" class=\"InternalRef\"\u003e1\u003c/span\u003e. The starting of the parameter is taken as total length of the tube L\u0026thinsp;=\u0026thinsp;605 mm and then entrance length L\u003csub\u003e1\u003c/sub\u003e\u0026thinsp;=\u0026thinsp;80 mm and exit of the heat energy from L\u003csub\u003e3\u003c/sub\u003e\u0026thinsp;=\u0026thinsp;25 mm is applied to the fin tube heat exchanger. The thickness of the arc is 4 with gap g\u0026thinsp;=\u0026thinsp;3 mm to increase the rectangular channel strength. The pitch space given between the circular fin in horizontal axis is P\u0026thinsp;=\u0026thinsp;60 mm, 70 mm, 80 mm, 90 mm, and 100 mm and second pitch space P\u003csub\u003e1\u003c/sub\u003e\u0026thinsp;=\u0026thinsp;19 mm, 21 mm, and 24 mm between the circular and arc fins in vertical axis. The pitch space is also explained as a relative roughness pitch, with the length of the fin's length (l/Dh) being equal to 0.24 and the pitch space (p) being on each unit hydraulic diameter (Dh). The heat exchanger's perforated inserts are used to regulate the effect of temperature and move fluid from the heated part to the cool section. Figure\u0026nbsp;\u003cspan refid=\"Fig2\" class=\"InternalRef\"\u003e1\u003c/span\u003e (i, ii, iii, and iv) shows how the heat exchanger with a fin tube bank is designed. After the heat exchanger's fin tube bank has been completely shaped, it is tested with a uniform heat flux of I\u0026thinsp;=\u0026thinsp;1000 w/m2. Relative hydraulic pitch ratio P/l\u0026thinsp;=\u0026thinsp;6, 7, 8, 9, and 10. Reynolds number (Re\u0026thinsp;=\u0026thinsp;2000, 3500, 5000, 6500, and 8000).\u003c/p\u003e\u003cp\u003e \u003cb\u003e2.1 Grid independence test of the meshing used\u003c/b\u003e \u003c/p\u003e \u003cp\u003eThis section represents the accuracy of the meshing which is applied in the meshing of the design domain. A second aspect of meshing that clarifies the tube's perfect meshing has emerged as the grid independence test. A method for determining the right meshing involves using the grid independence test. The grid independence test (0.002m size), which must be conducted to obtain correct results without any meshing error as shown in Fig.\u0026nbsp;\u003cspan refid=\"Fig3\" class=\"InternalRef\"\u003e2\u003c/span\u003e, becomes known when the results do not change when the grain size meshing has become varied.\u003c/p\u003e "},{"header":"3.0 Results and Discussion","content":"\u003cp\u003e \u003cb\u003e3.1 Validation of Heat transfer rate of Smooth Rectangular heat exchanger channel and Dittus-Boelter Correlations\u003c/b\u003e \u003c/p\u003e \u003cp\u003eThis section is essential part of the investigated numerical with or without use of circular fin in the rectangular channel so Fig.\u0026nbsp;\u003cspan refid=\"Fig4\" class=\"InternalRef\"\u003e3\u003c/span\u003e provides an explanation concerning the way of Smooth tube and the Dittus-Boelter equation compare. Dittus-Boelter represents a theoretical equation of thermal transfer factor that expresses the influence of the Reynolds number, which is the number on fluid flowing through a heat exchanger channel. These comparison results are varied from 8% \u0026minus;\u0026thinsp;2% with Reynolds numbers Re\u0026thinsp;=\u0026thinsp;2000, 3500, 5000, 6500, and 8000. Dittus-Boelter correlation: Nu\u0026thinsp;=\u0026thinsp;0.023\u0026times; Re\u003csup\u003e0.8\u003c/sup\u003e\u0026times;Pr\u003csup\u003e0.4\u003c/sup\u003e (1)\u003c/p\u003e\u003cp\u003e \u003cb\u003e3.2 Effects of circular fin on rectangular heat exchanger rectangular\u003c/b\u003e \u003c/p\u003e \u003cp\u003e \u003cb\u003e3.2.1 Results and Effects of Colburn J-Factor on Finned Heat Exchanger Rectangular Channel\u003c/b\u003e \u003c/p\u003e\u003cp\u003eThe results and effects of the circular fin heat exchanger rectangular vortex generator are calculated by the Colburn j-factor which is shown in the Figs.\u0026nbsp;\u003cspan refid=\"Fig5\" class=\"InternalRef\"\u003e4\u003c/span\u003e. The Colburn j-factor is corresponding to the Reynolds number because j-factor equation is dimensionless similar to the Reynolds number when hydrodynamic applied in the heat exchanger. All the factors of the circular fin those are affected by Colburn j-factor. On the other hand, it is possible to state that the Colburn j-factor and the heat transfer coefficient are associated directly, mass transfer coefficient and friction factors. The Fig.\u0026nbsp;\u003cspan refid=\"Fig5\" class=\"InternalRef\"\u003e4\u003c/span\u003e shows the minimum JF\u0026thinsp;=\u0026thinsp;0.013at p/l\u0026thinsp;=\u0026thinsp;6 and maximum JF\u0026thinsp;=\u0026thinsp;0.021at p/e\u0026thinsp;=\u0026thinsp;9 with fixed variations Re\u0026thinsp;=\u0026thinsp;8000, d\u0026thinsp;=\u0026thinsp;8 mm and l\u0026thinsp;=\u0026thinsp;20 mm. The purpose behind the circular fin coarseness is to optimise the heat exchanger's capacity for heat transmission and prevent heat loss to the surroundings. The Fig.\u0026nbsp;\u003cspan refid=\"Fig6\" class=\"InternalRef\"\u003e5\u003c/span\u003e presents the behaviour of the heat transfer rate to the environment from heat exchanger rectangular generator when circular fin with arc is inserted in the heat exchanger. The fin has variations in diameter and length to increase the performance of the heat exchanger and we obtained maximum heat transfer of 3.9, 5.2, 4.9 and 4.2 times as compared to smooth rectangular channel at d\u0026thinsp;=\u0026thinsp;6 mm, 8 mm, 10 mm and 12 mm respectively at Re\u0026thinsp;=\u0026thinsp;8000 and p/l\u0026thinsp;=\u0026thinsp;9. In the figure we found the maximum Nusselt number as heat dissipation to environment of the complete design model. In Fig.\u0026nbsp;\u003cspan refid=\"Fig7\" class=\"InternalRef\"\u003e6\u003c/span\u003e, the maximum velocity is observed 15.46 m/s in the circular fin rectangular channel when diameter d\u0026thinsp;=\u0026thinsp;8 mm applied to circular fin and at Reynolds number Re\u0026thinsp;=\u0026thinsp;8000.\u003c/p\u003e \u003cp\u003e \u003cb\u003e3.3 Thermo-hydraulic performance of circular fin rectangular channel\u003c/b\u003e \u003c/p\u003e \u003cp\u003eFigure \u003cspan refid=\"Fig8\" class=\"InternalRef\"\u003e7\u003c/span\u003e explains the heat exchange appliance tube's thermal hydraulic effectiveness in relation to Reynolds numbers between 2000 and 8000. The hydraulic efficiency is at its peak when =\u0026thinsp;3.47 when circular fin inserted with diameter d\u0026thinsp;=\u0026thinsp;8 mm, length of the fin l\u0026thinsp;=\u0026thinsp;20 mm and at Re\u0026thinsp;=\u0026thinsp;8000, and Pitch space P\u003csub\u003e1\u003c/sub\u003e\u0026thinsp;=\u0026thinsp;21 mm in vertical direction, and relative roughness pitch P/l\u0026thinsp;=\u0026thinsp;9.\u003c/p\u003e"},{"header":"4.0 Conclusion","content":"\u003cp\u003eThe study of the transfer of heat \u0026amp; fluid flow via ducts using different inserts was the focus for an extensive amount in investigations in numerical study during the last few decades. In the current research, changes in the Reynolds number Re\u0026thinsp;=\u0026thinsp;2000, 3500, 5000, 6500, and 8000, fluctuations in the pitch space within the inserts P\u0026thinsp;=\u0026thinsp;60 mm, 70 mm, 80 mm, 90 mm, and 100 mm, and change in the measurement diameters of the circular fin, d\u0026thinsp;=\u0026thinsp;6 mm, 8 mm, 10 mm, and 12 mm, were all studied numerically. With these modifications, the friction inside the heat exchanger is reduced while the rate of heat transmission throughout the heat exchanger to the outside environment is increased.\u003c/p\u003e \u003cp\u003eAs a consequence of the results, it becomes evident that the k-standard model may produce results for the study of heat conveyance and flow processes in rectangular heat exchangers having a suitable degree of engineering precision. As the Reynolds number Re\u0026thinsp;=\u0026thinsp;2000\u0026ndash;8000 rises, the heat transmission improves and the friction factor diminishes. At a fluctuation in Reynolds number Re\u0026thinsp;=\u0026thinsp;2000\u0026ndash;8000, a shift in the varied hardness raises the numbers of Nusselt as well as frictional factors in the range of 1.99-5.28and 2.33-3.55times of Plain tube, respectively. With changes in the Reynolds number and Pitch spacing between the round fins, the Nusselt number rises. The minimum Colburn j-factor JR\u0026thinsp;=\u0026thinsp;0.0091 at Re\u0026thinsp;=\u0026thinsp;8000, l\u0026thinsp;=\u0026thinsp;10 mm and P/l\u0026thinsp;=\u0026thinsp;6 and maximum JR\u0026thinsp;=\u0026thinsp;0.029030547 at Re\u0026thinsp;=\u0026thinsp;2000, l\u0026thinsp;=\u0026thinsp;20 mm and P/l\u0026thinsp;=\u0026thinsp;9 mm. With a circle-shaped fin size of 8 mm, the greatest Nusselt number has been achieved at pitch space P/l\u0026thinsp;=\u0026thinsp;9 mm, P1\u0026thinsp;=\u0026thinsp;21 mm, l\u0026thinsp;=\u0026thinsp;20 mm, when Reynolds number Re\u0026thinsp;=\u0026thinsp;8000. At Re\u0026thinsp;=\u0026thinsp;8000 and l\u0026thinsp;=\u0026thinsp;10 mm, the simplest friction factor was obtained at P/l\u0026thinsp;=\u0026thinsp;6 mm, d\u0026thinsp;=\u0026thinsp;6 mm, and P1\u0026thinsp;=\u0026thinsp;24 mm. Best hydraulic energy efficiency was attained at Re\u0026thinsp;=\u0026thinsp;8000, d\u0026thinsp;=\u0026thinsp;8 mm, P/l\u0026thinsp;=\u0026thinsp;9 mm, P1\u0026thinsp;=\u0026thinsp;21 mm, and l\u0026thinsp;=\u0026thinsp;20 mm with a value of =\u0026thinsp;3.47.\u003c/p\u003e"},{"header":"References","content":"\u003col\u003e\u003cli\u003e\u003cspan\u003eSundar, L. S., Kumar, N. R., Naik, M. T., \u0026amp; Sharma, K. V. (2012). Effect of full length twisted tape inserts on heat transfer and friction factor enhancement with Fe3O4 magnetic nanofluid inside a plain tube: An experimental study. International Journal of Heat and Mass Transfer, 55(11\u0026ndash;12), 2761\u0026ndash;2768.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eBas, H., \u0026amp;Ozceyhan, V. (2012). Heat transfer enhancement in a tube with twisted tape inserts placed separately from the tube wall. Experimental Thermal and Fluid Science, 41, 51\u0026ndash;58.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003ePiriyarungrod, N., Eiamsa-Ard, S., Thianpong, C., Pimsarn, M., \u0026amp;Nanan, K. J. C. E. (2015). Heat transfer enhancement by tapered twisted tape inserts. Chemical Engineering and Processing: Process Intensification, 96, 62\u0026ndash;71.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eBhattacharyya, S., Saha, S., \u0026amp;Saha, S. K. (2013). Laminar flow heat transfer enhancement in a circular tube having integral transverse rib roughness and fitted with centre-cleared twisted-tape. Experimental Thermal and Fluid Science, 44, 727\u0026ndash;735.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eEiamsa-ard, S., \u0026amp;Kiatkittipong, K. (2014). Heat transfer enhancement by multiple twisted tape inserts and TiO2/water nanofluid. Applied Thermal Engineering, 70(1), 896\u0026ndash;924.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eUniyal, M., \u0026amp; Joshi, K. (2015). Numerical and Experimental Investigation Plane Fin with the Help of Passive Augmentation Method. IOSR Journal of Mechanical and Civil Engineering (IOSR-JMCE), 12(6), 48\u0026ndash;53.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eBhattacharyya, S., Chattopadhyay, H., \u0026amp;Benim, A. C. (2016). Heat transfer enhancement of laminar flow of ethylene glycol through a square channel fitted with angular cut wavy strip. Procedia Engineering, 157, 19\u0026ndash;28.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eBhattacharyya, S., Chattopadhyay, H., \u0026amp;Bandyopadhyay, S. (2016). Numerical study on heat transfer enhancement through a circular duct fitted with centre-trimmed twisted tape. International Journal of heat and Technology, 34(3), 401\u0026ndash;406.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eBhattacharyya, S., Chattopadhyay, H., \u0026amp;Haldar, A. (2018). Design of twisted tape turbulator at different entrance angle for heat transfer enhancement in a solar heater. Beni-Suef University Journal of Basic and Applied Sciences, 7(1), 118\u0026ndash;126.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eWijayanta, A. T., Aziz, M., Kariya, K., \u0026amp;Miyara, A. (2018). Numerical study of heat transfer enhancement of internal flow using double-sided delta-winglet tape insert. Energies, 11(11), 3170.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eSingh, H., Kishore, C., Kumar, K. N., Patil, P. P., \u0026amp; Avikal, S. (2021). Numerical analysis of thermal-hydraulic performance of fully developed turbulent flow in heat exchanger tube with Half Moon inserts. Materials Today: Proceedings, 46, 11182\u0026ndash;11189.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eSingh, A. K., Singh, D. B., Mallick, A., Sharma, S. K., Kumar, N., \u0026amp; Dwivedi, V. K. (2019). Performance analysis of specially designed single basin passive solar distillers incorporated with novel solar desalting stills: a review. Solar Energy, 185, 146\u0026ndash;164.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eSingh, A. K., Singh, D. B., Dwivedi, V. K., Tiwari, G. N., \u0026amp; Gupta, A. (2020). Water purification using solar still with/without nano-fluid: a review. Materials Today: Proceedings, 21, 1700\u0026ndash;1706.\u003c/span\u003e\u003c/li\u003e \u003cli\u003e\u003cspan\u003eSingh, A. K., Singh, D. B., Dwivedi, V. K., Kumar, N., \u0026amp; Yadav, J. K. (2018, October). A review of performance enhancement in solar desalination systems with the application of nanofluids. In 2018 International Conference on Advances in Computing, Communication Control and Networking (ICACCCN) (pp. 814\u0026ndash;819). IEEE.\u003c/span\u003e\u003c/li\u003e\u003c/ol\u003e"}],"fulltextSource":"","fullText":"","funders":[{"identity":"6e1db1fb-781d-4ec2-9e62-29e9e286f472","identifier":"10.13039/501100018973","name":"Lovely Professional University","awardNumber":"Paper ID 100","order_by":0}],"hasAdminPriorityOnWorkflow":false,"hasManuscriptDocX":true,"hasOptedInToPreprint":true,"hasPassedJournalQc":"","hasAnyPriority":true,"hideJournal":true,"highlight":"","institution":"1st International Conference on Sustainable Energy Sources, Technologies and Systems (ICSESTS-2023) held on August 2-3, 2023, organized by Division of Research and Development, Lovely Professional University, Punjab.","isAcceptedByJournal":false,"isAuthorSuppliedPdf":false,"isDeskRejected":"","isHiddenFromSearch":false,"isInQc":false,"isInWorkflow":false,"isPdf":false,"isPdfUpToDate":true,"isWithdrawnOrRetracted":false,"journal":{"display":true,"email":"[email protected]","identity":"researchsquare","isNatureJournal":false,"hasQc":true,"allowDirectSubmit":true,"externalIdentity":"","sideBox":"","snPcode":"","submissionUrl":"/submission","title":"Research Square","twitterHandle":"researchsquare","acdcEnabled":true,"dfaEnabled":false,"editorialSystem":"","reportingPortfolio":"","inReviewEnabled":false,"inReviewRevisionsEnabled":true},"keywords":"Fan shaped circular fin, Heat transfer rate, friction factor coefficient and Thermal hydraulic performance","lastPublishedDoi":"10.21203/rs.3.rs-3927115/v1","lastPublishedDoiUrl":"https://doi.org/10.21203/rs.3.rs-3927115/v1","license":{"name":"CC BY 4.0","url":"https://creativecommons.org/licenses/by/4.0/"},"manuscriptAbstract":"\u003cp\u003eThe methodology of the circular fin heat exchanger has been analysis by the help of ANSYS fluent workbench and the Ansys fluent also known as computational fluid dynamics (CFD), which used to design the single heat exchanger rectangular channel with parameters. The single rectangular channel is a 605 mm long with height H = 66 mm and width is 30 mm. Under a constant heat flux of I = 1000 w/m2, a heat exchanger fin tube bank being tested. The results of this investigation lead to the following conclusions: Nusselt number improves with changes in Reynolds number when pitch distance between the circular fins used. Heat transfer grows as well as friction factor reduces with increasing Reynolds number values (Re = 2000–8000). At pitch spacing P/l = 9 mm, P 1 = 21 mm, l = 20 mm, as well as Reynolds number Re = 8000, the number of the heat transfer rate rose 5.28 times.\u003c/p\u003e","manuscriptTitle":"Heat transfer characteristics of rectangular heat exchanger with circular fin roughness","msid":"","msnumber":"","nonDraftVersions":[{"code":1,"date":"2024-02-06 06:58:38","doi":"10.21203/rs.3.rs-3927115/v1","editorialEvents":[{"type":"communityComments","content":0}],"status":"published","journal":{"display":true,"email":"[email protected]","identity":"researchsquare","isNatureJournal":false,"hasQc":true,"allowDirectSubmit":true,"externalIdentity":"","sideBox":"","snPcode":"","submissionUrl":"/submission","title":"Research Square","twitterHandle":"researchsquare","acdcEnabled":true,"dfaEnabled":false,"editorialSystem":"","reportingPortfolio":"","inReviewEnabled":false,"inReviewRevisionsEnabled":true}}],"origin":"","ownerIdentity":"8e76550a-a922-415c-899f-84d813783e12","owner":[],"postedDate":"February 6th, 2024","published":true,"recentEditorialEvents":[],"rejectedJournal":[],"revision":"","amendment":"","status":"posted","subjectAreas":[{"id":28556618,"name":"Renewable Resources"},{"id":28556619,"name":"Computational Physics"},{"id":28556620,"name":"Theoretical Physics"},{"id":28556621,"name":"Energy Engineering"}],"tags":[],"updatedAt":"2024-02-06T06:58:38+00:00","versionOfRecord":[],"versionCreatedAt":"2024-02-06 06:58:38","video":"","vorDoi":"","vorDoiUrl":"","workflowStages":[]},"version":"v1","identity":"rs-3927115","journalConfig":"researchsquare"},"__N_SSP":true},"page":"/article/[identity]/[[...version]]","query":{"redirect":"/article/rs-3927115","identity":"rs-3927115","version":["v1"]},"buildId":"qtupq5eGEP_6zYnWcrvyt","isFallback":false,"isExperimentalCompile":false,"dynamicIds":[84888],"gssp":true,"scriptLoader":[]}