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編號(hào) 畢業(yè)設(shè)計(jì) 論文 外文翻譯 原文 學(xué) 院 國防生學(xué)院 專 業(yè) 機(jī)械設(shè)計(jì)制造及其自動(dòng)化 學(xué)生姓名 李卓霖 學(xué) 號(hào) 1000110106 指導(dǎo)教師單位 桂林電子科技大學(xué) 姓 名 曹泰山 職 稱 講師 2014 年 3 月 09 日 0 Solid Modeling and Finite Element Analysis of an Overhead Crane Bridge C Alkin C E Imrak H Kocabas Abstract The design of an overhead crane bridge with a double box girder has been investigated and a case study of a crane with 35 ton capacity and 13 m span length has been conducted In the initial phase of the case study conventional design calculations proposed by F E M Rules and DIN standards were performed to verify the stress and deflection levels The crane design was modeled using both solids and surfaces Finite element meshes with 4 node tetrahedral and 4 node quadrilateral shell elements were generated from the solid and shell models respectively After a comparison of the finite element analyses the conventional calculations and performance of the existing crane the analysis with quadratic shell elements was found to give the most realistic results As a result of this study a design optimization method for an overhead crane is proposed Keywords overhead crane finite element method solid modeling box girder Notation b distance between two side plates bk width of lower plate FAA static load due to the trolley FY load due to the working load h0 height of the girder end h2 height of the side plates LA distance between trolley wheels LK span of crane girder LP distance between two adjacent supports q weight of one meter platform qK weight of one meter maintenance platform qP uniformly distributed mass units of bridge t1 thickness of the upper and lower plates t2 thickness of the side plates x2 distance between center of gravity and the midpoint of the left side plate x4 distance between center of gravity and the midpoint of the rail y1 distance between neutral axis and the midpoint of the rail y3 distance between center of gravity and the midpoint of the top plate y5 distance between neutral axis and the midpoint of the top plate WX1 moment of resistance on x axis 1 WY1 moment of resistance on y axis amplifying coefficientC dynamic coefficient 1 Introduction Cranes are the best way of providing a heavy lifting facility covering virtually the whole area of a building An overhead crane is the most important materials handling system for heavy goods The primary task of the overhead crane is to handle and transfer heavy payloads from one position to another Thus they are used in areas such as automobile plants and shipyards 1 2 Their design features vary widely according to their major operational specifications such as type of motion of the crane structure weight and type of the load location of the crane geometric features and environmental conditions Since the crane design procedures are highly standardized with these components most effort and time are spent on interpreting and implementing the available design standards 3 There are many published studies on structural and component stresses safety under static loading and dynamic behavior of cranes 5 16 Solid modeling of bridge structures and finite element analysis to find the displacements and stress values has been investigated by Demirsoy 17 Solid modeling techniques applied for road bridge structures and an analysis of these structures using the finite element method are provided in 18 In this study stress and displacements were found using FEM90 software Solid modeling of a crane bridge the loading at different points on the bridge and then application of the finite element method have been studied by Celiktas 19 She presented the results of finite element methods for an overhead crane DIN Taschenbuch and F E M Federation Europ enne de la Manutention Rules offer design methods and empirical approaches and equations that are based on previous design experience and widely accepted design procedures DIN Taschenbuch 44 and 185 are a collection of standards related to crane design DIN norms generally state standard values of design parameters F E M Rules are mainly an accepted collection of rules to guide crane designers It includes criteria for deciding on the external loads to select crane components 3 20 In this study the calculations apply the F E M rules and DIN standards which are used for box girder crane bridges The calculation of the box girder uses the CESAN Inc standard bridge tables Then a solid model of the crane bridge is generated with the same dimensions as in the calculation results Then static analysis is performed using the Finite Element Method Before starting the solution the 2 boundary conditions are applied as in practice 2 Overhead cranes with a double box girder Overhead travelling cranes with a double box girder not only hoist loads but also carry them horizontally A double beam overhead crane is built of a trolley travelling on bridges and bridges travelling on rails The trolley hoists or lowers the loads and carries them on the bridge structure The bridges carry the loads on a rail As a result three perpendicular movements are performed The system is depicted in Fig 1 where the payload of the mass is attached to the bridge with wire ropes 21 22 The double box girders are subjected to vertical and horizontal loads by the weight of the crane the working hook load and the dynamic loads With a double box girder construction the trolley runs above or between the girders The acceptable construction requirements and values for a box girder bridge structure are shown in Fig 2 Fig 1 Overall view of an overhead crane Fig 2 Construction requirements for a box girder bridge 3 3 Application of FEM to an overhead crane Among numerical techniques the finite element method is widely used due to the availability of many user friendly commercial softwares The finite element method can analyse any geometry and solves both stresses and displacements 23 FEM approximates the solution of the entire domain under study as an assemblage of discrete finite elements interconnected at nodal points on the element boundaries The approximate solution is formulated over each element matrix and thereafter assembled to obtain the stiffness matrix and displacement and force vectors of the entire domain In this study finite element modeling is carried out by means of the Cosmos Works and MSC commercial package Patran and 4 node tetrahedral elements and 4 node quadrilateral shell elements have been used for modeling the overhead crane bridge The four node tetrahedral element is the simplest three dimensional element used in the analysis of solid mechanics problems such as bracket stress analysis This element has four nodes with each node having three translational and three rotational degrees of freedom on the x y and z axes A shell element may be defined which allows in the plane or curved surface of the element and posses both length It width and may only be used in 3 D simulations The four node shell element is obtained by assembling the bending element to the appropriate degrees of freedom This is sufficient as long as the shell element deflection is within the predefined ratio 4 of shell thickness otherwise the system works as a large deflection A typical four node tetrahedral element and four node quadratic shell element and their coordinate systems are illustrated in Fig 3 24 The four node tetrahedral element chosen has six degrees of freedom at each node translation in the nodal x y and z directions and rotations about the nodal x y and z directions For the four node quadratic shell element used to model the overhead crane girder r and s denote the natural coordinates and is the thickness of the element This system does not have any horizontal force The axial displacements and rotations of the first and last faces are equal to zero In addition the transverse displacement is zero at the first and last face nodes The external forces acting on the system are the mass of the main girder of the crane distributed load and the forces acting on the wheels of the trolley along the crane active load The forces acting on the trolley wheels are caused by the mass of the trolley an the lifting load which will be moved on the crane 4 node tetrahedral element 5 4 node quadratic shell element Fig 3 Elements used to model an overhead crane girder 4 Solid and finite element modeling of an overhead crane bridge The finite element method is a numerical procedure that can be applied to obtain solutions to a variety of problems in engineering Steady transient linear or nonlinear problems in stress analysis heat transfer fluid flow and electrome chanism problems may be analysed with finite element methods The basic steps in the finite element method are defined as follows preprocessing phase solution phase and post processing phase Real crane data was gathered from CESAN Inc a Turkish company involved in mass production of overhead cranes First the crane bridge is modeled as a surface Bridge geometry is suitable for this and long and thin parts should also be modeled as a surface Later a mesh is created In this study a quadratic element type is used Solid modeling is generated for the calculated crane bridge and the solid model is shown in Fig 4 20 Solid model of a crane bridge Wireframe view of a crane bridge 6 Fig 4 Models of an overhead crane bridge 5 Numerical example of an overhead crane A 35 ton capacity overhead crane of overall length 13 m and total weight 22 5 tons was selected as a study object The configuration of the overhead crane is shown in Fig 1 The overhead crane consists of two girders two saddles to connect them and a trolley moving in the longitudinal direction of the overhead crane and wheels The driving unit is installed in one of the two girders The overhead crane is supported by two rails and the runway girders installed in building In order to calculate the stress in the structure the rules of F E M 1 001 are applied The design values used in the bridge analysis from the F E M and DIN standards are given in Table 1 Table 1 Bridge property values First the maximum and minimum stresses and then the shear stress are calculated using the F E M rules Using the finite element method for the considered girder we obtain the stress valnes We obtain the static loads due to the dead weight the loads due to the working load multiplied by the dynamic coefficient and the two most Handling Capacity 35 ton Trolley Weight 3 ton Bridge Length 13 m Distance between wheels of trolley 2m Trolley Velocity 20 m min Crane Velocity 15 m min Hoisting Velocit 2 7 m min Total duration of use U4 Load spectrum class Q3 Appliance group A5 Loading type H main load Dynamic coefficient 1 15 Amplifying coefficient 1 11 7 unfavourable horizontal effects excluding the buffer forces The maximum stress consists of the stress on the bridge dead weights the stress on the trolley dead weight the stress from the hoisting load stress from the inertia forces and the stress of the trolley contraction The minimum stress includes the stress on the bridge dead weights and the stress on the trolley dead weight The maximum and minimum stresses for the given values according to the F E M rules 20 are written in standard form as and The value of the dynamic coefficient is applied to the loading arising from the working load The value of the amplifying coefficient depends the group classification of the application and the weight of one meter maintenance platform is zero in this work 25 It is assumed that the total load 372780 N is effected on the midpoint of the rail and each girder shares this total load equally This load is applied via the contact points of the two trolley wheels in this system Therefore the value of the acting force on each point is 93195 N Applying the total load in the system the value of the maximum stress according to Eq 1 is 143 90 N mm2 to two decimal places and the value of the minimum stress according to Eq 2 is 47 33 N mm2 to two decimal places According to Fig 5 the permissible stress in shear consists of the shear stresses of the wheel forces and is defined as 20 8 The value of the maximum shear stress is 24 82 N mm2 to two decimal places from Eq 5 Substituting Eq 1 3 the equivalent stress is given by The value of the equivalent stress is 150 18 N mm2 to two decimal places Fig 5 Inertia and moment of resistance in a box girder 6 Results from a girder model with a four node tetrahedral element To model the overhead crane girder with a four node tethrahedral element Cosmosworks software was used for finite element analysis using the girder solid model generated by means of SolidWorks 2003 Young s Modulus E is 2 1 105 N mm2 and the Poisson Ratio is 0 3 for finite element analysis The value of the maximum stress of the side plate is 12 07 N mm2 to two decimal places and the value of the maximum stress of the bottom plate is 15 08N mm2 to two decimal places from Fig 6 20 The displacement of the modelled overhead crane girder was obtained from CosmosWorks and is illustrated in Fig 7 The value of maximum displacement of the girder is about 2 2 mm 9 Fig 6 Stress values of an overhead crane girder with a four node tetrahedral element Fig 7 Displacements of an overhead crane girder with a four node tetrahedral element 7 Results from a girder model with a four node quadratic shell element To model the overhead crane girder with a four node quadratic shell element MSC Patran software was used for the finite element analysis Young s Modulus E is 2 1 10 N mm2 and the Poisson Ratio St is 0 3 for finite element analysis The value of the maximum stress of the side plate is 35 40 N mm2 to two decimal places 10 and the value of the maximum stress of the bottom plate is 49 30 N mm2 to two decimal places from Fig 8 20 The displacement of the modelled overhead crane girder was obtained from MSC Patran and is illustrated in Fig 9 The value of maximum displacement of the girder is about 3 89 mm The value of the maximum stress according to Eq 1 is calculated as 143 90 N mm2 to two decimal places The safety factor should be considered between 2 and 3 for overhead crane girder design The maximum stress value of the side plate is between 24 14 and 36 21 N mm2 to two decimal places and the maximum stress value of the bottom plate is between 30 16 and 45 24 N mm2 to two decimal places for a four node tetrahedral element taking into account the safety factor The maximum stress value of the side plate is between 70 8 and 106 2 N mm2 to two decimal places and the maximum stress value of the bottom plate is between 98 6 and 147 9 N mm2 to two decimal places for a four node quadratic shell element taking into account the safety factor The permissible displacement of the girder is 13 mm according to F E M rules The maximum displacement obtained from the finite element model with a four node tetrahedral element is between 4 40 and 6 60 mm taking into account the safety factor The maximum displacement obtained from the finite element model with a four node quadratic shell element is between 7 78 and 11 67 mm taking into account the safety factor 11 Fig 8 Stress values of an overhead crane girder with a quadratic shell element Fig 9 Displacements of an overhead crane girder with a four node quadratic shell element 8 Conclusion In this study unlike the other studies carried out previously shell elements in 12 finite element modeling of an overhead box girder have been examined In order to show the use of shell elements one illustrative overhead crane bridge example is given The maximum stress value is 143 90 N mm2 and 45 24 N mm2 for a four node tetrahedral element and 147 9 N mm2 for a four node quadratic shell element using both calculations according to the F E M Rules and finite element analysis The value of the equivalent stress is 150 18 N mm2 to two decimal places Taking into account the safety factor the stress value varies between 97 145 5N mm2 which is obtained from MSC Patran The ratio of length to thickness of the element used in modelling the overhead crane box girder is higher than 20 Therefore in order to show the accuracy of the analysis of the overhead crane bridges a four node quadratic shell element is used instead of the four node tetrahedral element for finite element analysis Acknowledgment It is pleasure to acknowledge much stimulating correspondence with Dr Haydar Livatyali and gratefully to acknowledge the support of CESAN Inc which provided the design data Machine tool numerical control reforms 1 CNC systems and the development trend of history 1946 birth of the world s first electronic computer which shows that human beings created to enhance and replace some of the mental work tools It and human agriculture industrial society in the creation of those who merely increase compared to manual tools from a qualitative leap for mankind s entry into the information society laid the foundation Six years later in 1952 computer technology applied to the machine in the United States was born first CNC machine tools Since then the traditional machine produced a qualitative change Nearly half a century since the CNC system has experienced two phases and six generations of development 1 1 Numerical Control NC phase 1952 to 1970 13 Early computer s computational speed low and the prevailing scientific computing and data processing is not affected but can not meet the requirements of real time control machine People have to use digital logic circuit tied into a single machine as a dedicated computer numerical control system known as the hardware connection NC HARD WIRED NC called the Numerical Control NC With the development of components of this phase after three generations that is in 1952 the first generation tube 1959 of the second generation transistor 1965 of the third generation small scale integrated circuits 1 2 Computer Numerical Control CNC phase 1970 to present To 1970 GM has been a small computer and mass produced So it transplant system as the core component of NC have entered a Computer Numerical Control CNC stage in front of the computer should be universal word omitted To 1971 the United States INTEL company in the world will be the first time the two most core computer components computing and controller a large scale integrated circuit technology integration in a chip called the microprocessor MICROPROCESSOR also known as the central processing unit CPU 1974 microprocessor to be used in CNC system This is because the function of the computer is too small to control a machine tool capacity affluent the time has been used to control more than one machine called Group Control as a reasonable economic use of the microprocessor Minicomputer reliability and then not ideal Early microprocessor speed and functionality while still not high enough but can be adopted to solve the multi processor architecture As microprocessor core is a general computer components it is still known as the CNC By 1990 PC machines personal computers domestic habits that computer performance has been developed to a high stage as a CNC system to meet the requirements of the core components NC system based on PC has now entered the stage In short CNC has also experienced a stage three generations That is in 1970 s fourth generation small computer 1974 of the fifth generation microprocessors and the sixth generation 1990 Based on the PC called PC BASED abroad Also pointed out that although the foreign computer has been renamed NC CNC but China still customary said Numerical Control NC Therefore we stress the day to day NC in essence is that computer numerically controlled 14 1 3 the trend of future development of NC 1 3 1continue to open the sixth generation of PC based development Based on the PC with the open low cost high reliability rich in resources such as hardware and software features and more CNC system manufacturers will embark on this path At least it used PC as a front end machine to deal with the human machine interface programming networking and communications problems the former NC Some systems