7 Papers_merged

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Mechanical Engineering 6th & 7th May, 2022 ALUMINIUM 201 Element Type : Solid 20 node186 Material Properties: Youngs Modulus (EX) : 71000 N/mm2 Poissons Ratio (PRXY) : 0.33 Density Yield Strength : 0.000002800 kg/mm3 : 435 N/mm2 Solution Solution – Solve – Current LS – ok General Post Processor Displacement Vector Sum Von Misses Stress ISBN: 978-93-5620-351-8 138 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Mechanical Engineering 6th & 7th May, 2022 Strain Results MG ZK60 AL201 Displacement (mm) 0.0563 0.03539 Von-Mises stress (N/mm2) 5.824 5.938 0.187e-3 Strain 0.119e-3 Yield stress 382 435 STATIC ANALYSIS OF MODIFIED MODEL WITH SLOTSMAGNESIUM ALLOY (ZK60) Imported Model from CATIA ISBN: 978-93-5620-351-8 139 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Mechanical Engineering 6th & 7th May, 2022 Element Type : Solid 20 node186 Material Properties: Youngs Modulus (EX) : 45000 N/mm2 Poissons Ratio (PRXY) : 0.35 Density : 0.0000017 kg/mm3 Yield Strength : 382 N/mm2 Loads Meshed Model Pressure – 0.0572 N/mm2 Solution Solution – Solve – Current LS – ok General Post Processor Displacement Vector Sum ISBN: 978-93-5620-351-8 140 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Mechanical Engineering 6th & 7th May, 2022 Von Misses Stress Strain ALUMINIUM 201 Element Type : Solid 20 node186 Material Properties: Youngs Modulus (EX) : 71000 N/mm2 Poissons Ratio (PRXY) : 0.33 Density Yield Strength : 0.000002800 kg/mm3 : 435 N/mm2 Solution 141 ISBN: 978-93-5620-351-8 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Mechanical Engineering 6th & 7th May, 2022 Solution – Solve – Current LS – ok General Post Processor Displacement Vector Sum Von Misses Stress Strain Results Displacement (mm) MG ZK60 AL201 Von-Mises stress (N/mm2) 0.00923 0.00584 3.255 3.2859 Strain 0.996e-4 0.634e-4 Yield stress 382 435 5.0 CONCLUSION We used ansys workbench software to do structural analysis on various-shaped spoke wheels under conditions of maximum rpm stress. Stress levels are being taken into account in order to provide the ISBN: 978-93-5620-351-8 142 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Mechanical Engineering 6th & 7th May, 2022 best possible outcomes. This slotted shaped spoke wheel can withstand these loads since the stress values are below the yield stress. Under the stress value, it's not performing as expected. In terms of findings, we've seen stress values for MG ZK 60 and AL 201 alloys for the original model of the slotted alloy wheel.By comparison with other alloy wheels, MG ZK 60 has superior life for slotted wheels due to lowerstress and displacement values than AL 201 alloy, which is a little on the high side. Accordingly, improved performance may be expected for MG ZK60 slotted alloy. 6.0 REFERENCES 1. Saran Theja , Shankar G, Vamsi Krishna , Design Analysis of Two Wheeler Lighter Weight Alloy Wheel, Indian Journal of Engineering, Volume 6, Number 15, November 2013 [2] V. K. K. Upadhyayula, A. G. Parvatker, A. Baroth, and K. Shanmugam, “Lightweighting and electrification strategies for improving environmental performance of passenger cars in India by 2030: a critical perspective based on life cycle assessment,” Journal of Cleaner Production, vol. 209, pp. 1604–1613, 2019. [3] C. Xianhua, G. Yuxiao, and P. Fusheng, “Research progress in magnesium alloys as functional materials,” Rare Metal Materials and Engineering, vol. 45, no. 9, pp. 2269–2274, 2016. [4] H. J. Jiang, C. Y. Liu, B. Zhang et al., “Simultaneously improving mechanical properties and damping capacity of AlMg-Si alloy through friction stir processing,” Materials Characterization, vol. 131, pp. 425–430, 2017. [5] M. M. Avedesian and H. Baker, “ASM specialty handbook,” in Magnesium and Magnesium Alloys, ASM international, Geauga County, Ohio, 1999. [6] Y. Li and H. Cheng, “Research status and prospect of damping magnesium alloys,” Electrical Engineering Materials, vol. 10, no. 5, 2016. [7] Y. Ding and D. Ju, “Finite element analysis of residual stress in the diffusion zone of Mg/Al alloys,” Advances in Materials Science and Eng ISBN: 978-93-5620-351-8 143 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Mechanical Engineering 6th & 7th May, 2022 THERMAL ANALYSIS OF HEAT PIPES WITH THERMAL STORAGE DURING A COOLING CYCLE Y. Narsa Reddy1, N. Chandrakanth2, Rentu Philiopose3 1Assistant Professor, Department of Mechanical Engineering, Nalla Narasimha Reddy Education Society’s Group of Institutions, Hyderabad, Telangana India. 2 Assistant Professor, Department of Mechanical Engineering, MCEME, Hyderabad, Telangana India. 3 Sr Piping Engineer, PT. Citra Kusuma Perdana, Jakarta, Indonesia Abstract— A mathematical model has been developed to of heat pipes with thermal storage during a cooling cycle, which indirectly influences Heat transfer within heat pipes, predict the thermal behavior of heat pipes with thermal Thermal resistance of the wall of the heat pipes, Thermal storage during a cooling cycle. A heat transfer model based resistance of air fins, heat transfer rate and efficiency. upon the various mechanisms of conduction, convection, and heat of fusion of the melted ice is presented. The thermal Horbaniuc et al. [1] developed a mathematical model for heat behavior of heat pipes has also been studied experimentally pipes in thermal storage. Finned heat pipes were used to and analyzed under different conditions. Comparisons were transfer heat from fluids from solar collectors to a phase made against the experimental data for validation of the change material in a storage tank, and another set of finned predictive model. The model fairly predicted experimental heat pipes was used to transfer latent heat from the storage data obtained at various inlet conditions. tank to a cold fluid stream, charging, discharging, or both simultaneously. Various studies have been presented Keywords— Heat transfer; Conduction; Convection; Fusion; discussing traditional “ice-on-coil” and “melt-water” in storage tanks. Thermal storage; Numerical modelling. Lee and Jones [2] developed a stand-alone analytical model of the charging and discharging of thermal energy storage I. INTRODUCTION with “ice-on-coil” in a storage tank. The study focused on the formation of ice with evaporator coils inside the tank, and Heat pipes are tubes containing a refrigerant, and discharge through water circuit that is cooled by direct contact positioned either at an angle or vertically, depending on their with the stored ice. construction. The refrigerant in the lower end of the heat pipes Zhu and Zhang [3] analyzed the charging and discharging of evaporates from the incoming heat and moves upward in the an “ice-on-coil” thermal storage tank and simulated the pipes to a colder region, where it condenses and returns to the freezing and thawing of water around the coils. Their work lower half. If the upper (condenser) section of these heat pipes identified various stages of ice thawing from the warm brine is placed in an ice container, and the evaporator is placed in an in the coils. Experimental results were compared to simulated airstream flow, the heat of fusion is transferred until all the ice data. has melted. Since the refrigerant in the heat pipes requires Stewart et al. [4,5] also provided methods of modeling the only a temperature differential between both sections to charging of ice with harvester-type icemakers, and circulate, the advantages of such a thermal storage system discharging of tanks with water. The models were become apparent where space and power usage are limited. incorporated into the ICEPAK software and they were By eliminating the use of brine and circulating pumps to transport heat between the container and the air stream, heat evaluated with empirical experimentation. Furthermore, losses are significantly reduced. Heat pipes also require less maintenance, and a lesser amount of tubing to transfer heat Stewart et al. [4, 5] modeled the melting of the ice stored in compared to other heat transport/recovery systems. rectangular tanks with multiple ice openings, using the II. LITERATURE SURVEY ICEPAK software, incorporating three-dimensional time- In the literature survey we have observed that researchers have made extensive study in evaluating the thermal behavior explicit algorithms by resolution of the Navier–Stokes equations. charging of ice with harvester-type icemakers and discharging of tanks with water. The models were incorporated into the ISBN: 978-93-5620-351-8 144 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Me6cthha&nic7atlhEMngaiyn,ee2r0in2g2 Yanadori [6] acquired experimental data on the discharge and, C1 = 0.24 for R-22 of heat in melt water. He introduced water flow to a tank filled with crushed ice particles. Theoretically, since the contact Similarly, the condenser section thermal resistance is surface between the water and the ice particles is greater, there should be a greater heat exchange. Heat transfer was measured 1 1 (5) for a tank with rectangular, particles, and ice. Another study ℎ������������������������.������������������������������.������������������ ℎ������������������������.������������������������.������������������������������������ paper on the melting process of traditional thermal storage ������ = =������������������������ tanks using heat pipes was presented by Tady and Sami [7], where detailed experimental work was presented and analyzed. Thermal resistance of the wall of the heat pipes Other recent studies have also been reported on the subject, namely, The heat pipes wall represents a thermal resistance that can be Murphy and Reay [8] and Liu et al. [9]. This research has calculated as a function of the length and the total number of been undertaken to enhance our understanding of the subject and to develop a heat transfer model to the thermal heat pipes: ln (������������������.������������������⁄������������������.������������������) performance of heat pipes for thermal storage in air ln (���2���������������������������.������������������������������������⁄������������������������������������������.������������������) conditioning applications. ������ =tube−evap (6) ������ =tube−cond 2������������������������������������������������������ (7) Eqs. (6) and (7) are similar since the condenser and evaporator of the heat pipe share the same geometry. III. METHODOLOGY Thermal resistance of air fins Theoretical analysis: Since air fins exist only on the evaporator side, the heat 2.1. Calculation of thermal resistances To calculate the heat transfer for the heat pipe thermal storage transfer coefficient is [11] system, the thermal resistances are considered as shown in Fig. 1 ℎ = ������������������������������������������������ (8) ������������������ ���������������2������⁄������3��� And the thermal resistance between the air and the fins of the evaporator is ������������������������ = 1 (9) ℎ������������������������������������������������.������ Fig. 1. The thermal resistance of the heat pipes system. where Afins and η are the fin surface area and efficiency. Pr represents and Prandtl number. ������������������������������������ = ������������������������ + ������������������������������,������������������������ + ������������������������������ + ������������������������������ + ������������������������������,������������������������ + Tardy [10] in his thesis developed the following expressions ������������ (1) The thermal resistances outlined in Eq. (1) represent axial for calculating the water thermal resistances Rw1, Rw2, Rw3 resistances from the water resulting from the melting of ice to and Rw5 for surface areas S1, S2, S3 and S5 using conduction, the airflow. Please refer to the nomenclature section for an convection and fusion as well as radiation heat transfer explanation of the thermal resistances. Fig. 2a shows the axial mechanisms: heat transfer flow as well as the storage tank and the airflow ������ = ln (������������������.������������������+������⁄������������������.������������������) (10) (11) duct. ������,1 2������������������������������������������������������������������������������������������ (12) 2.1.1. Heat transfer within heat pipes ������������,2 = 1 + ������������,1 ������������������������������������������������2������2 The heat transfer taking place within the heat pipes can be 1 ������������,3 = ������������������������������������������3������3 + ������������,1 described by the basic formulas for Nusselt film boiling and condensation. Operating temperature T is the average and temperature between T and T, the extreme temperatures of the ������������,5 = 1 (13) ℎ������.5������������������������.������������������������������������ heat pipe. The convective heat transfer coefficient for boiling can be calculated as proposed by LeBlanc [11]: Interested readers in the development of the aforementioned expressions are advised to consult Tardy [10] for further ℎ������������������������ = ������2(���������3��� ������������(������������−������������������)���������������������.���������������������������������������������(���ℎ���(���������������4���−+���0������.���4������������������������������()������4−������������������������������)))1/4 (2) details. The water temperature T5, where the heat pipe Where C2= 0.68 for R-22 condenser placed is The thermal resistance of the evaporator section is 1 1 (3) ℎ������������������������������������������������������.������������������ ℎ������������������������.������������������������.������������������������������������ ������ = =������������������������ Similarly, LeBlanc [11] proposed the following equation for (14) (15) heat transfer coefficient during film condensation The average water temperature is calculated as follows: ℎ������������������������ = ������1(������������������(���������������������������−���������������.���������������)���������������(���������������������������������������������������ℎ���−������������������2���)������3��� )1/4 (4) ������������ = ������5+������������������������ 2 ISBN: 978-93-5620-351-8 145 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Me6cthha&nic7atlhEMngaiyn,ee2r0in2g2 Once the ice is melted T5 and will be used to calculate the water resistance Rw,5 and (16), (17) where T2 and T4 are the evaporator and condenser wall Fig. 2a. Experimental setup showing the storage tank and the heat pipes. temperatures, respectively. These two temperatures are used to calculate heat transfer coefficients at the evaporator and condenser hevap and hcond, respectively. 2.1.4. Calculation of heat transfer rate and system efficiency The heat transfer rate includes the latent heat received from the melting ice and the sensible heat transferred from the water at temperature Tw: (18) Sensible heat transfer absorbed by the water is where (19) Fig. 2b. Closeup showing the two sections of the heat pipes. is the mass flow rate of the melting ice. To study the ice-water interface various thermocouples type The total heat transfer rate is T were placed in the water reservoir, where the heat pipe condenser was immersed. The accuracy of the thermocouples (20) was of ±0.5% full scale. The accuracy of air mass flow The ice melt mass flow rate can be calculated from the latent measurement was ±3% of the nominal flow. The working heat and the fusion latent heat transfer as fluid in the heat pipes was R-22. The uncertainty analysis conducted for the experimental data used in this study (21) revealed an accuracy of ±4% of full scale. Readers interested in detailed uncertainty analysis are advised to consult Tardy Therefore, the total heat transfer rate is [10] for further details. (22) Data collection was carried out using the LabView The system efficiency is defined as the rate of heat transferred acquisition system. This enabled us to record local properties divided by maximum heat transfer. The maximum heat with a single scan. All tests were performed under steady state transfer rate is attained when the outside evaporator conditions. The channels were scanned every second and temperature is equal to the outside condenser temperature stored every 10 s. Tests started with ice in the reservoir at −1°C. All recorded measurements were obtained according to (23) the ARI and ASHRAE [10] Standards. Experiments will carry out with accuracy in order to keep the error minimum and determine the results appropriately. By Discussion and analysis: using input parameters such as welding current, voltage, gas The aforementioned system of equations has been flow rate, and filler rods we perform the experiment and will note down the output values during the procedure of the numerically solved and samples of the predicted results are experiment. plotted in Figs. 3–5, and compared with the experimental data for a cooling cycle at different inlet conditions. In general, it is quite clear from these figures that the experimental data were underpredicted for the first 30 min. This was attributed to the fact that the heat flux diminishes faster than the rate of heat transfer predicted by the model especially as the ice reaches the tank walls. However, after 2 h the heat transfer rate stabilized at 0 and 38 kW for up to 10 h. At this point the heat ISBN: 978-93-5620-351-8 146 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Me6cthha&nic7atlhEMngaiyn,ee2r0in2g2 transfer rate diminished for the next 5 h until the cooling cycle ends. Fig. 3. Heat rate transferred to the storage tank versus time for ϕin = Fig. 5. Total of heat rate transferred to the storage tank versus time 75%, Tair_in ≈ 24 °C for ϕin = 75%, Tair_in ≈ 24 °C Fig. 4. Heat rate transferred to the storage tank versus time for ϕin = Numerical prediction was in general very representative 75%, Tair_in ≈ 24 °C and depicts the heat exchange rate between the condenser of heat pipes immersed in the reservoir and ice. Initially, the heat exchange was very high between the heat pipes and the ice for about 1 h and 12 min, then the heat exchange diminished as the ice melts. The numerical model’s prediction showed that the ice was fully melted after 12 h and 48 min after the cooling cycle started. Furthermore, the model predicted that the heat transfer with air was reduced to 100 W at 16 h and 12 min. This was in fair agreement with the experimental data. The heat transfer rate absorbed from the air flow and transferred to ice in the reservoir has been plotted as a function of cooling cycle time and compared to the model’s prediction in Figs. 4 and 5. These figures showed that the model fairly predicted the heat transfer rate under various inlet conditions. Furthermore, Fig. 3 also showed that in general the model prediction of the system thermal characteristics, temperatures and heat transfer rates was satisfactory, during the cooling cycle. The data presented hereby suggest that heat transfer rates at certain time intervals are equal to the heat flux at the surface. As the heat flux remained relatively constant during the cooling cycle, heat transfer was relatively linear over the cooling cycle period for the last 10 h of the experiment. The predicted results showed similar behaviour. As shown in the figures beyond this point heat transfer diminished until the end of the cooling cycle. Since the heat flux was relatively constant during the experiment it can be concluded that heat transfer rates had temporal linear dependence during the cooling cycle. IV. CONCLUSION During the course of this study, the heat transfer characteristics of heat pipes in the storage process have been modeled, presented, and analyzed. An experimental setup has ISBN: 978-93-5620-351-8 147 Department of Mechanical Engineering, NNRG.

Proceedings of RTIME-2K22 5th National Conference on Recent Trends & Innovations in Me6cthha&nic7atlhEMngaiyn,ee2r0in2g2 been constructed and various tests of the thermal storage International Mechanical Engineering Congress and cooling cycle have been carried out under different inlet Exposition IMECE 2005, IMECEC2005-82793, November 5– conditions. In general, the presented numerical model fairly 11, 2005, Orlando, FL. predicted the heat transfer characteristics and interactions between the ice and heat pipes as well as airflow and [8] E.D. Murphy, D. Reay compared well with the experimental data. A PCM/heat pipe cooling system for air conditioning in building: review of options and report on field tests V. FUTURE WORK Building Services Engineering Research and Technology, 27 Till now in the project stage-1 we have decided the project (1) (2006), pp. 27-39 and researched many literatures based on our experiments and just planned our project. [9] Z.l. Liu, Z.Y. Wang, C.F. Ma Now, in project stage-2 the work will be continues as per our An experimental study on heat transfer characteristics of heat frame work. pipes heat exchanger with latent heat storage. Part 1: charging only and discharging only modes REFERENCES Energy Conversion and Management, 47 (7–8) (2006), pp. 944-966 Article PDF (365KB) [1] B. Horbaniuc, G. Dumitrascu, A. Popescu Mathematical models for the study of solidification within a [10] F. Tardy, Passive Air Conditioner using Heat Pipes longitudinally finned heat pipe latent heat thermal storage during Thermal storage, M.Sc Thesis, University of Quebec, system Montreal, Canada, 2005. Energy Conversion and Management, 40 (1999), pp. 1765- 1774 Article PDF (157KB) [11] W. LeBlanc, Numerical and Experimental study of Non-azeotropic Behaviour in a Heat Pipe, M.Sc Thesis, University of Moncton, Moncton, NB, 1991. [2] A.H. Lee, J.W. Jones Modeling of an ice-on-coil thermal energy storage system Energy Conversion and Management, 37 (10) (1996), pp. 1493-1507 Article PDF (918KB) [3] Y. Zhu, Y. Zhang, Modeling of internal melt ice-on- coil tank, Building Simulation’99, September 1999, Kyoto, Japan. [4] W.E. Stewart Jr., G.D. Gute, C. Saunders, L.A. Stickler Icepak-Modeling the ice-filling and ice-melting processes of thermal energy storage tanks ASHRAE Transactions, 101 (1) (1995) [5] W.E. Stewart Jr., G.D. Gute, J. Chandrasekharan, C.K. Saunders Modeling of the melting process of ice stores in rectangular thermal energy storage tanks with multiple openings ASHRAE Transactions, 100 (1995) [6] M. Yanadori Fundamental study of the melting process of crushed ice in a heat storage container Scripta Technica (1999) [7] F. Tady, S.M. Sami, A study of the use of heat pipes in thermal storage cooling, in: Proceedings of ASME ISBN: 978-93-5620-351-8 148 Department of Mechanical Engineering, NNRG.