International Engineering Research Journal Optimization of Temperature and heat transfer rate for cashew roasting Shridhar M. Jadhav, Dr.Kisor P. Kolhe Mechanical Department,ICOER, Pune university, Pune Maharashtra,India Mechanical Department, ICOER,Pune university, Pune Maharashtra,India Abstract The bubbling of crude cashew seed is broadly in little scale cashew nut handling factories with the assistance of minimal one heater. The child evaporator usually utilized for steaming of crude seeds was assessed. The weight vessel is one of a substantial number of plant parts for which stretch investigations must be performed. A weight vessel hones sorts of stresses which are essential anxieties and optional burdens. significant anxieties are a result of worry inside weight vessel and optional burdens are a direct result of warm load. Warm stacking is impressive in a weight vessel which handles hot liquid. Scientifically, prompted stresses are figured utilizing weight vessel hypothesis or ASME codes. The outcomes are then contrasted and expository outcomes. This work shows utilization of business FEA apparatus over investigative approach. Utilization of FEA devices is not extremely acknowledged in weight vessel enterprises. FEA of this sort of load requires coupled field examination. In the work ANSYS is utilized to perform coupled field investigation. cashew seeds are bubbled in vessel. The infant heater coupled ordinarily utilized for a steaming of crude seeds was assess. In this paper investigative and ansys results are looked at which is vital for the reason of assembling. Keywords:Pressure Vessel, FEA Analysis, Cashew Nut, temperature 1. Introduction On the planet, India possesses a first position adding to around 43 for each penny of the cashew nut. Maharashtra has 164300 ha of territory under cashew development with normal generation of 1,978000 tons of cashew nuts and achieving profitability of 1500 kg/ha.a a few procedures worried in cashew nut handling are cleaning, drying, bubbling or steaming, shelling and injuring, drying of parts, peeling, reviewing, and bundling. Bubbling strategy includes utilization of warmth to the nut, which discharge the nutshell liquid and makes the shell flimsy which encourages the extraction of the portion when tearing the shell open..[4] A weight vessel is a shut potused to hold gasses or fluid at a weight impressively not quite the same as the encompassing weight. These round and hollow vessels are generally utilized as compartments to store liquids in different ventures. The liquid might be at conspicuous temperatures and in a hurried state. One of the huge uses of weight vessel is steaming the crude cashewbefore shelling. Because of steaming the shell of cashew nut turns out to be delicate and shelling process requires less endeavors.. Extraordinary concern must be taken while outlining weight vessels. This paper shows the plan strategy for weight vessel utilized for steaming the cashew nuts. From content it creates the impression that conservatively outline of weight vessel is built up out utilizing ASME codes. Weight vessels are for the most part subjected to mechanical loadings henceforth; essential burdens are continually centering of the creator. Henceforth this paper shows the plan and FE examination of weight vessel.[5] 2. Formulation of Design 2.1 Classification of pressure Vessel The two important factors for the classification of Pressurevesselare: According to thickness I. Thin cylinder when t/d < 0.1 ii. Thick cylinder- when t/d > 0.1 According to end construction I. Closed ended ii. Open ended There are two ways in which vessels are designed I. Design by Rule ii. Design by Analysis Design by rule is used to analyze basic shell thickness, thermo-mechanical stresses and keeping stresses below allowable values FE analysis is carried out to validate the design that is made by design by rule method. lastly the results obtained from these methods are compared.[16] 2.2 Material SA-108 Grade B is a grade of carbon steel plannedprincipally for use of boilers and pressure vessels which are calculated for use in raised temperature examine. All material properties are specifiedin the table 2. 1
Table 1: Properties of SA108 Modulus of Elasticity Yield Strength Allowable Stress Coeff. of thermal Expansion 210*10 3 N/mm2 240 N/mm2 160 N/mm2 10 6 K 1 2.3 Input Design Data The application chosen for the study is pressure vessel whose approximate dimensions are given in Table 1. Pressure vessel is considered with hemispherical head. Table 2 various parameter of pressure vessel Parameters SI Units Inner Diameter (D) 263 mm Length of the Vessel 410 mm 210x103 Modulus of Elasticity (E) N/mm2 Yield Strength (σ yield) 240 N/mm2 Allowable Stress (S) 160 N/mm2 Coeff. of thermal expansion (α) 10 6 K 1 OpertingTemperature (T) 110 C Environmental temperature (T) 30 C Operating Pressure (P) 1N/mm 2 Factor of Safety (FOS) 1.5 Minimum Shell Thickness Min. Hemispherical head thickness 2.4 Operating conditions Characteristic operating conditions are given in the table 3. Table 3: Operating Condition of pressure vessel OperatingTemprature 110 C Environmental temperature 30 C Operating Pressure 1MPa Factor of Safety 1.5 2.5 Preparation of CAD Drawing Pro-E 5.o software is used to generate the CAD drawing. The 3D model is generated and after that Cad drawing is placed. 3. Analytical Calculations All input specifications are converted to SI unit. The variety of parameters has been calculated using the standard formulae available in the literature. 3.1 Design of Shell Thickness: Minimum shell thickness is calculated using Eq. t = P i + CA η P i 2σ t D i t = 4 mm 5 mm 4 mm Fig.1. CAD drawing 3.2 Design of Hemispherical Head Thickness: Minimum head thickness is calculated using Eq. t = P i + CA η 0.2 P i 2σ t t = 3.5 mm D i It is recommended to use same thickness for shell as well as head i.e 5mm due to several reasons when thickness difference is very small.[17] 3.3 Circumferential Stress of Cylindrical Shell: After computationofleast amount thickness for shell and head, stresses are back calculated and checked the design for safety. Safe thickness assumed is 5 mm. σ l =P i D i /2t = 26.6 MPa<allowable limit 3.4 Longitudinal Stress of Cylindrical Shell: Succeeding to calculating minimum thickness for shell and head, stresses are back calculated and checked the design for safety. Safe thickness assumed is 5 mm. 2
σ l =P i D i /4t = 13.3 MPa<allowable limit 3.5 Thermal Stress Calculation For Simple Temperature Profile Thermal stress = EαT Thermal stress = 16MPa 3.6 Heat required to raise the temperature of water Q= m C p (T 2 - T 1 ) =6720 KJ 3.7 Heat transfer rate Q= mc p (T 2 - T 1 )/t = 5.6 KW 3.8 Amount of steam generated m = q/h = 0.002698 kg/s = 7.4 kg/hr 4. Result And Discussion 4.1 Axi-Symmetric Approach for analysis Fig. 3Thermal stresses model 4.2 Analysis of Shell Shell is the segment of pressure vessel without heads. SOLID187 element is a higher order 3-D, 10-node element. SOLID187 hasquadraticdisplacementbehavio ur and is well suited to modeling unbalanced meshes (such as those shaped from various CAD/CAM systems). Axi-symmetry advance simplifies the model and also reduces the computational time. This advance can be used if the geometry is revolved about a particular axis.axi-symmetry is used about Y-axis. One needs to create a model and mesh with PLANE elements of ANSYS. In all suitcasesaxi-symmetryadvance is used in this paper to represent shell, head and complete model for structural, thermal and coupled field analysis.[12] Fig.4static structural model Fig2 :Meshed Model for Complete Pressure Vessel The element is defined by 10 nodes having three degrees of liberty at each node: translations in the nodal x, y, and z directions. The element has agility, hyperelasticity, creep, pressure stiffening, large deflection, and large strain capabilities. It also has mixed formulation capability for simulating deformations of nearly incompressible elastoplastic materials, and fully incompressible hyperelastic materials.[13] next are the details of the meshed model using plane elements: 1) Number of elements = 96315 2) Number of nodes = 47903 3) Element type = solid 4.3 Structural Analysis of Shell : Structural analysis is carried outby means of PLANE42 element.foraxi-symmetric shell cross-section is model 3
and meshed with PLANE42 elements. Pressure is applied inner surface and solved for stress in shell.the stresses in shell due to pressure load for greatest stress is 1 N/mm 2. 4.4Analysis of Pressure Vessel Analysis of pressure vessel is also accepted out like way the shell analysis is carried out. Following elements with axi-symmetry option are used for various analysis of pressure vessel. Structural Analysis: Solid 187 Thermal Analysis: Solid 187 Thermal Stress Anlysis: Solid 187 Coupled Field Analysis: Solid 187 subsequent various analysis are carried out on shell of pressure vessel to contrast analysis process for pressure vessel analysis. Pure Structural Analysis Pure Thermal Analysis for Temperature Distribution Pure Thermal Analysis for Stress Coupled Field Analysis Various stress outcome are below allowable limits of shell as per the guidelines of ASME. Results of FE analysis are within 15% error limit when compared to analytical results. Error in FE and analytical results occurs because of various reasons such as assumptions in analytical formulation, approximation in FE formulations, choice of element in FE analysis, etc. Hence, similar procedure can be used for analysis of pressure vessel along with heads.[14] Complete pressure vessel is modeled and analyzed in ANSYS using axi-symmetric analysis and results of various analyses are presented. a variety of stress values obtained are lesser than allowable limits of material and hence pressure vessel is safe and this design can be used to manufacture the pressure vessel. The analysis has been done in ANSYS for the pressure vessel taking different instances into consideration. Table 4: Comparison of results (of shell analysis) Analytical ANSYS Percentage Shell (Mpa) (Mpa) Error Thermal 16 17.59 3 % Pressure 26 27 5 % Combined Thermal & NA 34.28 NA Pressure Additional inspection in complete pressure vessel analysis is that junction of shell and head is subjected to high stresses whereas shell and head independently indicates lower values of pressure. This is typically because of sudden change in geometry. Hence, it important to select appropriate head type for given pressure vessel. Conclusions: In design of pressure vessels FEA tool can be successfully used. Typically it helps the designer to understand thermo - mechanical activities of pressure vessel. Overall conclusions based on present study are as below: Pressure vessel is intended and analyzed for the given thermo-mechanical loads. Maximum stress induced due to pressure alone in the shell is calculated using ASME formula and compared with the analysis values and the maximum percentage error is 15%. Safe operating conditions for the vessel are verified within framework of FEA advanced techniques. REFERENCES 1. Hongjun Li, Xun Huang, Peng Yang, Hui Yang (2017), A new pressure vessel design by analysis method avoiding stress Elsevier 2. UnheonChoi,DaejunChang(2015), ChoongheeJo, Estimation of the design pressure of a prismatic LNG storage vessel Elsevier. 3. Kolhe K.P and Datta C.K, Parametric study of submerged arc welding on mild steel Indian welding journal 2004, 37 (3/4) Pp.33-42. 4. Kolhe K.P. Development and testing of tree climbing and harvesting device for mango and coconut trees. Indian coconut journal, published by Ministry of Agriculture, CDB board Kochi Kerla 2009, LII (3) Pp. 15-19. 5. Shinde A.A., Chavan A.J and Kolhe K.P Testing and Performance evaluation of tractor Mounted Hydraulic for Mango Harvesting International journal of Agricultural Engineering, 2010,3(2) Pp. 275-278. 6. Ashish A. Wankhede, Kishor P. Kolhe 2015 Experimental Application of Heat Pipes in Hydraulic Oil Cool International Journal of Engineering Research & Technology Vol. 4 - Issue 03 Pp 7. MullaNiyamat, K.Bicha, DESIGN AND STRESS ANALYSIS OF PRESSURE VESSEL BY USING ANSYS, July, 2015 8. Sunil Kumar D1, Suhas B2 (2016) Design and Evaluation of Pressure Vessel as 9. per ASME Section VIII Division 2,IJRISET. 10. Bandarupalli Praneeth¹, T.B.S.Rao, 2012, Finite Element Analysis of Pressure Vessel andpiping Design International Journal of Engineering Trends and Technology- Volume3Issue5 4
11. Jurandir Primo, PE, ASME Pressure Vessels Basic Calculations 12. Ove T Gudmestad (2013), A Comparison Study of Pressure Vessel Design Using Different Standards Conference Paper 13. Shyam R. Gupta,(2014) A Review Paper on Pressure Vessel Design and Analysis IJERT 14. Shyam R.(2014), A Review Paper on Pressure Vessel Design and Analysis, IJERT 15. MayankNirbhay, 2014 Implementation of ASME Codes to Design APressure Vessel and To explore the Influence ofvarious Design Parameters researchgate. 16. V.B. Bhandari, Design of machine elements 17. R.S.Khurmi&J.K.Gupta Machine Design 5