DESIGN AND ANALYSIS OF EOT CRANE HOOK FOR

DESIGN AND ANALYSIS OF EOT CRANE HOOK FOR VARIOUSCROSS SECTIONS1Sarvesh A. Mehendale1, Prof. Santosh. R. Wankhade2P.G student, Y.T.I.T., Bhivpuri, 2Associate Prof., Y.T.I.T., Bhivpuri.AbstractCrane hooks are one of the importantcomponents which are used to transfermaterials having heavy loads, mainly inindustries.Cranehooksareliablecomponents subjected to failure due to stressin accumulation of heavy loads. Failure of acrane hook mainly depends on three majorfactors i.e. dimension, material, overload.The design parameters for crane hook arearea of cross section, material and radius ofcrane hook. In this project the design of EOTcrane hook has been carried out. Thedimensions of the hook have been determinedfor a load capacity between 9 to 12.5 Tonesfor Trapezoidal, Rectangular and d on the basis of design criteria i.e.keeping area same for all cross-sections. Afterthe analytical i.e. theoretical calculations,ANSYS 15 is used to calculate thedeformation, stress and strain for all threecross-sections for different loads. The stressesobtained by theoretical method and bysoftware are in good agreement. The modelprepared is used for further studied withdifferent loads and also for differentmaterials.Index Terms: Lifted load, Eye diameter ofhook, Direct stress, Bending stress,Equivalent stress, Deformation, Strain.I. INTRODUCTIONCranes are industrial machines that aremainly used for materials movements inconstruction sites, production halls, assemblylines, storage areas, power stations and similarplaces. Their design features vary widelyaccordingtotheirmajor operationalspecifications such as: type of motion of thecrane structure, weight and type of the load,location of the crane, geometric features,operating regimes and environmental conditions.A hook is a tool consisting of a length ofmaterial that contains a portion that is curved orindented, so that this portion can be used to holdanother object. In a number of uses, one end ofthe hook is pointed, so that this end can pierceanother material, which is then held by thecurved or indented portion.In the industries crane hooks are one of theimportant components. They are used to transferthe materials having heavy loads. Crane hooksare liable components subjected to failure due tostress in accumulation of heavy loads. Area ofcross section, material and radius of crane hookare the design parameters for crane hook. Failureof a crane hook mainly depends on three majorfactors i.e. dimension, material, overload.The design of EOT crane hook has been carriedout. The dimensions of the hook have beendetermined for different load capacities. Variousdimensions for cross sections of various shapesfor crane hook have been found. After the systemwas designed, the stress and deflection arecalculated at critical points using ANSYS andoptimized.II. DESIGN AND CALCULATIONA. DESIGN OF HOOKThe hook is to be designed having loadcarrying capacity of 125kN. Hook is made upof high tensile steel. Three different crosssections i.e. trapezoidal, rectangular andISSN (PRINT): 2393-8374, (ONLINE): 2394-0697, VOLUME-3, ISSUE-12, 201653

INTERNATIONAL JOURNAL OF CURRENT ENGINEERING AND SCIENTIFIC RESEARCH (IJCESR)circular are considered. By keeping area samefor all cross sections as a design criteria, directstress, bending stress, shear stress are found.Stresses induced in hook (at section A-A & B-B)B. CALCULATION FOR TRAPEZOIDALCROSS SECTIONA) Distance of neutral axis from axis of curvature(PSG 6.3)(I) 107.98 mmB) Distance of CG from axis of curvature.(PSG6.3)Fig. No.1 Standard Trapezoidal HookEye diameter of hook, C 131mm andDimensions corresponding to C are G 70mm,G1 M68.Table No.1 Notation for trapezoidal c/s areaNotation onPSG 9.11Dimension(mm)Notation onPSG 6.3NomenclatureH 0.93C121.83HHeight fortrapezoidal c/s.M 0.6C78.6biInner width oftrapezoidal c/s.2z 2(0.12C)31.44boOuter width oftrapezoidal c/s.C/265.5riInner radiusfor trapezoidalc/s.H C/2187.33roOuter radiusfor trapezoidalc/s.R , R 117.71mmCross section area,, a 6703.08 mm2(II)(III)Total stress induced at A-AFor innermost layer: - Total stress,Where, direct stress 18.648N/mm2 bending stress (IV) 146.312 N/mm2(PSG 6.2)(V)Hence 164.96 N/mm2, taking FOS 3. 494.88 N/mm2Selecting material 40cr1 (PSG 1.13) Yield stress 600 N/mm (PSG 1.13)Hence, design stress [ ] (VI)N/mm2[ ] / 2. FOS 100 N/mm2/ FOS 200ISSN (PRINT): 2393-8374, (ONLINE): 2394-0697, VOLUME-3, ISSUE-12, 201654

INTERNATIONAL JOURNAL OF CURRENT ENGINEERING AND SCIENTIFIC RESEARCH (IJCESR)Checking for direct shear stress at B-B18.648N/mm2 100 N/mm2 (safe)(VII)C. CALCULATION FOR RECTANGULARC/SFor same cross section by keeping area is sameand assuming h/b 1.5Cross section area, a 6703.08 b * h b *(1.5b) 1.5 b2Hence, b 67mm and h 101mm(VIII)Fig. No. 3 Standard Circular HookA) Distance of neutral axis from axis ofcurvature (PSG 6.3) [ ro ri ] 2 / 4 106.95mm(XIII)ro ri h C/2 h 65.5 101 166.5mm(IX)B) Distance of CG from axis of curvature (PSG6.3)(XIV)R ri d/2 112mmTable No. 2 Different Stresses (MPa) forTrapezoidal, Rectangular and CircularsSection A-A at curvatureFig. No. 2 Standard Rectangular HookA) Distance of neutral axis from axis ofcurvature (PSG 6.3) h / ln (ro / ri ) 108.25mm(X)B) Distance of CG from axis of curvature (PSG6.3)(XI)R ri h/2 116mmD. CALCULATION OF CIRCULAR C/SCross section area, a 6703.08 π/4 * d2hence, d 93mmro ri d 65.5 93 158.5mm(XII)18.648N/mm2 18.648N/mm2 18.648N/mm2146.312N/mm2182.174N/mm2 216.725N/mm2164.96N/mm2200.822N/mm2 280.373N/mm2Section B-B at curvature18.648N/mm2 18.648N/mm2 18.648N/mm2Table No. 2 gives the values of direct stress,bending stress and shear stress for all crosssections. However above calculations are onlyfor 125 kN load. By following same designprocedure respective values for all stresses isbeen calculated for remaining loads i.e. 110 kN,90 kN.III. SIMULATIONFinite element analysis is done in following foursteps namely, 1. Geometry 2. Meshing 3.Boundary Condition & 4.Solver. Geometry i.e.ISSN (PRINT): 2393-8374, (ONLINE): 2394-0697, VOLUME-3, ISSUE-12, 201655

INTERNATIONAL JOURNAL OF CURRENT ENGINEERING AND SCIENTIFIC RESEARCH (IJCESR)solid modeling is done using solid works. Fig.No. 4 shows the solid model of hook.(A)(B)(C)Fig. No. 7 ANSYS Result for 90kN and circularcross section (A) Total deformation (B)Equivalent Stress (C) Equivalent StrainFig. No. 4 3D model of HookThis solid model is then imported in ANSYS15.0 for further analysis. Meshing of the hook isdone in ANSYS mesher keeping proximity andcurvature option on. Fine mesh is done for goodquality mesh. Meshing of the hook of differentcross sections is shown in Fig. No. 5.(A )(B)(C)Fig. No. 5 Meshing of hook (A) Trapezoidal c/s(B) Rectangular c/s (C) Circular c/sAfter meshing, boundary condition i.e. load of90 kN, 110 kN and 125kN is applied to generatereal time condition. Application of boundarycondition is shown in Fig. No. 6(A)(B)(C)Fig. No. 8 ANSYS Result for 110kN and circularcross section (A) Total deformation (B)Equivalent Stress (C) Equivalent Strain(A)(B)(C)Fig. No. 9 ANSYS Result for 125kN and circularcross section (A) Total deformation (B)Equivalent Stress (C) Equivalent StrainFig. No. 10 ANSYS Result for 90kN andrectangular cross section (A) Total deformation(B) Equivalent Stress (C) Equivalent StrainFig. No.6 Application of Boundary Condition.In solver, all the data is processed to givesolution for different combinations of crosssections and loads.Fig. No. 11 ANSYS Result for 110kN andrectangular cross section (A) Total deformation(B) Equivalent Stress (C) Equivalent StrainISSN (PRINT): 2393-8374, (ONLINE): 2394-0697, VOLUME-3, ISSUE-12, 201656

INTERNATIONAL JOURNAL OF CURRENT ENGINEERING AND SCIENTIFIC RESEARCH (IJCESR)Fig. No. 12 ANSYS Result for 125 kN andrectangular cross section (A) Total deformation(B) Equivalent Stress (C) Equivalent StrainFig. No. 13 ANSYS Result for 90 kN andtrapezoidal cross section (A) Total deformation(B) Equivalent Stress (C) Equivalent StrainTable No. 4 Stress in MPaTrapezoida Rectangl 52265.44KN125143.82304301.64KNTable No. 5 StrainTrapezoidaLoadsRectangleCircularl90 KN 0.00052944 0.0010944 0.0011171110 KN 0.0006471 0.0013376 0.0013654125 KN 0.00073534 0.00152 0.0015516V. CONCLUSION By using curved beam concept cranehooks are successfully designed for threedifferent cross sections.Fig. No. 14 ANSYS Result for 110 kN andtrapezoidal cross section (A) Total deformation(B) Equivalent Stress (C) Equivalent StrainFig. No. 15 ANSYS Result for 125 kN andtrapezoidal cross section (A) Total deformation(B) Equivalent Stress (C) Equivalent StrainIV. RESULT AND DISCUSSIONTable No. 3 Total Deformation in mmTrapezoida Rectangl CirculaLoadsler900.517180.55896 0.56792KN1100.63210.68318 0.69413KN1250.71830.77634 0.78878KN The model was prepared using CREOsoftware and analysis has been carriedout using ANSYS 15. All sections are safe in all loadingconditions. Sample calculation is shown below for aload of 125KNTable No. 6 Stress in MPa at section A-A(sample calculation)Trapezo Rectang Circularidal c/sular c/sc/sAnalytical 64 The circular section has more stressinduced than other two cross section. The trapezoidal cross section gives betterresults in comparison with other twocross sections as because stressesinduced are less in trapezoidal crosssection.ISSN (PRINT): 2393-8374, (ONLINE): 2394-0697, VOLUME-3, ISSUE-12, 201657

INTERNATIONAL JOURNAL OF CURRENT ENGINEERING AND SCIENTIFIC RESEARCH (IJCESR) The stresses obtained in theoretical andanalytical methods are in goodagreement. The model prepared is usedfor further studied with different loadsand also for different materials.REFERENCESBooks[1] M.P. Alexandrov, Material HandlingEquipment. Moscow: Mir Publishers, 1981.[2] N. Rudenko, Material Handling Equipment.Moscow: Peace publication, 1964.Journal papers[2] A Gopichand , R.S. Lakshmi,Dec2013,”Optimization of design parameters forcrane hook using taguchimethod”IJIRSET, issn2319-8753[3] Patel Ravin, Patel Bhakti, 2015, “Design andanalysis of crane hook with different materials,IJACT, ISSN 2319-7900.[4] Jayeshchopda, S.H. Mankar, May 2015,”Design analysis and optimization of electricoverhead travelling crane hook”, IJMTER, ISSN2349-9745[5] Tushar Hire, V.N bartaria, 4/2014,”Optimum stress analysis of crane hook with helpof finite element: IJEET.[6] Rashmi U.,” 3/2011”Stress Analysis of cranehook and validation by photo elasticity”SciRP.org[7] Chetan N. Benkar, Dr. N. A. Wankhade,May-2014 “FINITE ELEMENT STRESSANALYSIS OF CRANE HOOK WITHDIFFERENTCROSSSECTIONS”International Journal For TechnologicalResearch In Engineering Volume 1, Issue 9,ISSN : 2347 – 4718Data book[8] Design data book of engineers, January2010”PSG college of technology”, Coimbatore.ISSN (PRINT): 2393-8374, (ONLINE): 2394-0697, VOLUME-3, ISSUE-12, 201658

[2] A Gopichand , R.S. Lakshmi,Dec 2013,”Optimization of design parameters for crane hook using taguchimethod”IJIRSET, issn 2319-8753 [3] Patel Ravin, Patel Bhakti, 2015, “Design and analysis of crane hook with different materials, IJACT, ISSN 2319-7900. [4] Jayeshchopda, S.H. Mankar