倾卸车提升机构设计优化外文翻译、中英文翻译、外文文献翻译

倾卸车提升机构设计优化外文翻译、中英文翻译、外文文献翻译,倾卸,提升,机构,设计,优化,外文,翻译,中英文,文献 Mine design and optimization of lifting mechanism of dumping truck Li-Ronghao1,a,Yang-Jue2,b and Peng-Lilong3,c 1,2,3School of Mechanical Engineering,University of Science and Technology Beijing Beijing,China ,, keywords:Mining equipments,Lifting mechanism,Ground protection,Matlab.Abstract.Lifting mechanism is one of the most important work system.Its design quality directly influences the using performance of mining dump truck.The dissertation takes large dump truck as research object,with the knowledge of the mechanism dynamics for the top rear lifting mechanism of dump truck for innovative design,using the optimization function of MATLAB make the lifting mechanism optimal,to articulated point lifting mechanism the reasonable optimally lay out,and improves the lifting organization performance fundamentally.1.Introduction The old design of lifting mechanism of dump truck,when building a mathematical model,on the hypothesis premise of the total mass in the the goods in carriage and center of mass position invariance.The stress of the lifting mechanism will increase because of packing case forward center of mass during lifting uninstall,this point is rarely considered,but it has a great influence on.Common carriage and bucket type car unloading is presented in this paper mathematical model of center of mass in the process of change,it lays the foundation for lift unloading process of lifting mechanism design.Large dump trucks for vehicle,Schematic Fig 1.1:Fig 1.1 Large dump truck vehicle figure Fig 1.2 Three-dimensional containerstowage way 1.1 The basic parameters of the selected Structure is mining shovel car of the train,the goods rest Angle of choice for 30/30-45,stow cargo car adopts 1/2 stowage method,the specific shape as shown in figure 1.2 the pink area.1.2 Mathematical model of bucket type hopper car process Establish a car as the origin of coordinates,hinge pin point O level to the left for the X axis is left hand,right Angle coordinate system As shown in figure 1.3.It can be easily to find the lifting process at any time in the car innage quality and center of mass position.In the process of dumping,carriage of goods by full quality decrease to 0,increasing from 0 to the maximum lift Angle demotion Anglem.Between the car demotion Angle and the quality of innage is nonlinear relationship,can be segmented analysis.Interface of goodsDZ1 in the process of lifting,andZZ32,ZZ43,ZZ54,ZZ65 the edge of the intersection D for a floating point,when the point D to pointZ6,namely all unload goods.Carriage when the initial position coordinates of each point)i(),y,x(ZZiZii6100=,with crate on both sides of the side plate plane intersection)j(),y,x(Wwjwjj6100=,both ends of container vertex coordinates,),),(k,y(xHHkHkk2100=Carriage barycentric coordinates G(gx,gy),Carriage weight W,Carriage width L.Advanced Materials Research Vols.760-762(2013)pp 1274-1277Online available since 2013/Sep/18 at (2013)Trans Tech Publications,Switzerlanddoi:10.4028/ rights reserved.No part of contents of this paper may be reproduced or transmitted in any form or by any means without the written permission of TTP,.(ID:140.116.207.56,National Cheng Kung University,Tainan,Taiwan-14/04/14,17:10:31)Fig 1.3 Lift unloading process 2 The lifting mechanism design 2.1 Mechanical model of lifting mechanism Lifting process,assuming the plane parallel to the horizontal plane on the frame,wheel in the ground level completely,oil cylinder force around the same in the process of lifting.Under ground contact A connected to the frame,on the ground are connected to the crate contact B,point O for crate and frame on the coordinate system of ground contact.point C is point B for rotating lifting Angle,point M is crate has not lifting the centroid position,the point G is not lifting the centroid position of goods,and N is the barycentric position of the container the lifting Angle.Point A,B,M,G coordinates are(ax,ay),(bx,by),(mx,my),(gx,gy).Fig 2.1 Lifting coordinates 2.2 The size of the lifting mechanism design In order to guarantee the vehicle structure is compact,simple process,low failure rate,make the geometry size of each components in the lifting mechanism and institutions in the initial state position occupied a very small space,does not appear in the process of exercise intervention into consideration at the same time,so as to guarantee the mechanism motion coordination.First of all,according to the cargo rest Angle of lifting mechanism of selecting maximum demotion Angle.Through the above parameters,the installation of the lifting oil cylinder can be determined the length of AB and largest demotion Angle.)y(y)x(xABbaba+=there is a formulaAOBcosOBOAOBOAAB+=222 obtain a result AOB Lifting is determined to the greatest extent:AOCcosOBOAOBOAAC+=222 (1)The lifting cylinder stroke:ABACL=The first level of cylinder bore Advanced Materials Research Vols.760-7621275222112)yy()xx(yxyxp)xgmxgmK(dbabaabbamg+=(2)And the roundness result shall be according to the provisions of the state standard,after work back calculation of hydraulic pressure.Determination of lifting the first class I cylinder inner diameter:When lifting the first level will be stretched out,crate corner.Point B to point C,Point M to point N 22212)yy()xx(yxyxp)xgmxgmK(dcacaaccangi+=(3)This can be determined,when lifting the first class the first level will be out of the lift cylinder bore size.Fig2.2 The lifting cylinder 3.The ground contact location optimization Elongation before and after the optimization with the lifting Angle contrast figure(solid line is optimized,the dotted line in order to optimize the former)Lifting force before and after the optimization with the lifting Angle contrast figure(solid line is optimized,the dotted line in order to optimize the former)Fig 3.1 Lifting cylinder contrast figure Fig 3.2 Lifting force contrast figure Lifting hydraulic cylinder with the lifting Angle variation before and after optimization Fig 3.3 Before the optimization Fig 3.4 After the optimization(1)After optimization,the lifting cylinder elongation curve and offset a lifting force curve,the maximum lifting thrust and lift elongation reduced 3.6%and 4%respectively,lifting performance is greatly improved.1276Optoelectronics Engineering and Information Technologies in Industry(2)After optimization,the initial position is 875 kn lifting force,reduced by 6%than before optimization,lifting oil pressure 19.4 MPa,reduced by 4.3%than before optimization,Obviously,the optimized for hydraulic lifting mechanism at the initial position is low,gradually with the increase of turn Angle increases,the turning Angle is about 30 degrees when maximum,maximum oil pressure is higher than the initial value,and in the process of the dump,oil pressure curve flat,oil pressure fluctuation coefficient is small,accord with the requirement of hydraulic characteristic curve(3)After optimization,the initial position of lifting force,the lift is better than the before optimization and lifting hydraulic,even during the second half of the lifting process has reached levels before optimization.Optimization design based on MATLAB parameter coordinates,it can map out the lifting installation location after optimized design,as shown below:Fig 3.4 The optimized lifting location map Summary Based on studies of lifting system on the basis of both domestic and overseas,according to the bucket type car dumping process mathematical model of the mining machinery parts of innovative design of lifting mechanism of tipper,and MATLAB optimization theory is applied to the mining equipments in the design of the lifting mechanism,a mathematic model of the mine lifting mechanism of dump truck,lifting capacity and the lift as the objective function to optimize design,considered the boundary constraints,the lifting cylinder maximum pendulum Angle,installation length constraints,not to interfere in constraints such as constraint conditions,realize the optimal design of lifting mechanism References 1 Wei Xiang,Sai Cheong Fok,Georg Thimm.Agent-based Composable Simulation for Virtual Prototyping of Fluid Power System.Computers in Industry.2004,54(3):237251.2 Peter Beater，Martin Otter.Multi-Domain simulation:Mechanics and Hydraulics of an Excavator.Proceedings of the 3rd International Modelica Conference，2003 3 Kong Xiaowu，Qiu Minxiu,Wei Jianhua.A Atudy of the Influences of Pipe on Valve Control Hydraulics System.Proceedings of the 15th Internation Conference on Fluid Power Transmission and Control(ICFP2001),2001.4 Michael Decken,Hubertus Murrenhoff.Simulation of Fluid Power Components Using DSHplus and ADAMS.2001 ASME International Mechanical Engineering Congress and Exposition.2001.5 Nong Zhang,Wade Smith,Jeku Jeyakumaran.Hydraulically interconnected vehicle suspension:background and modeling J.Vehicle System Dynamics:2010,(1):17-40.Funded project number:Z101103055010004.Beijing science and technology committee Advanced Materials Research Vols.760-7621277Optoelectronics Engineering and Information Technologies in Industry 10.4028/ Mine Design and Optimization of Lifting Mechanism of Dumping Truck 10.4028/ 5 外文资料翻译 倾卸车提升机构设计优化 起重机构是最重要的工作体系之一。 其设计质量直接影响矿山自卸车的使用性能。 本论文以大型自卸车为研究对象，借助于自卸车顶部后提升机构的创新设计机理动力学知识，利用MATLAB的优化功能，提升机构优化，铰接点提升机构合理最优化 布置，从根本上提高提升组织绩效 关键词：采矿设备，起重机构，地面保护，Matlab。 1.介绍 自卸车提升机构的旧设计，建立数学模型时，对货物总体质量和质量中心位置不变性的假设前提。提升机构的应力将因包装箱向前而增加 提升卸载时的质心，这一点很少考虑，但对本文的影响较大。本文提出了在本文中的质量中心数学模型在变化过程中的载体和铲斗式车辆卸载，为 升降机卸载过程提升机构设计。大型自卸车用于车辆，结构是挖掘铲车的列车，30 / 30 - 45的货物的休息角，stow货车采用1 / 2的积载法，摘要桶式料斗式料斗车的数学模型建立了一辆车作为坐标的原点，铰链销点O水平在左边的X轴是左手。在汽车的质量和质量中心的任何时间都可以很容易地找到提升过程。在倾倒过程中,货物运输全面质量降低为0,从0增加到最大升力角降级角α。汽车降级角β和剩余货物的质量是非线性关系,可以分段分析。 2 提升机构设计 2.1 提升机构的机械模型提升过程中，假设平面平行于框架上的水平面，车轮在地面完全完整，油缸在提升过程中大致相同。 接地触点A连接到框架上，在地面上连接到板条接触点B，将点O连接到地面接触坐标系上的箱体和框架。 点C为点B，用于旋转提升角β，点M为箱体未提升重心位置，点G不提升货物的重心位置，而N为集装箱重心位置的提升角度θ。 点A，B，M，G坐标是（a x，a y），（b x，b y），（m x，m y），（g x，g y）。 2.2 起重机构设计尺寸为保证车辆结构紧凑，过程简单，故障率低，使起重机构各部件的几何尺寸和初始状态下的机构占用非常小的空间， 同时不考虑运动干预的过程，以保证机构运动协调。 首先，根据货物的仰角提升机构选择最大降级角度。θ 通过上述参数，提升油缸的安装可以确定AB的长度和最大的降级角度θ 这里是一个公式 起重是最大程度上决定的. 升降缸行程： 第一级气缸孔 圆度结果应按照国家标准的规定，倒车后计算液压。   确定提升第一级I缸内径： 当提升第一级时将被拉伸出来，将角点θ。点B到点C，点M指向N点 这可以确定，当提升第一级时，第一级将脱离提升缸内径。 3 地面接触位置优化 拉伸前后优化提升角度对比图（实线优化，虚线以优化前者）提升力前后优化提升角度对比图（实线优化，虚线为了优化前者） （1）优化后，提升缸伸长曲线偏移提升力曲线，最大提升推力和升力伸长分别降低了3.6％和4％，提升性能大大提高。 （2）优化后，初始位置为875 kn提升力，比优化前降低6％，提升油压19.4 MPa，比优化前降低4.3％，显然，初始位置液压提升机构优化低，逐渐随着转角的增加而增加，转角大约在30度时最大值，最大油压高于初始值，而在过渡过程中，油压曲线平坦，油压波动系数小符合液压特性曲线要求 （3）优化后，提升力的初始位置，升力优于前优化提升液压，即使在下半年提升过程中达到优化前的水平。基于MATLAB参数坐标的优化设计，优化设计后可绘出起重安装位置，如下图所示： 总结 根据国内外起重系统研究，根据挖掘机铲斗式倾倒过程数学模型挖掘机提升机构创新设计，MATLAB优化理论应用于采矿设备 提升机构的设计，自卸车矿山提升机构的数学模型，起重能力和电梯作为优化设计的目标函数，考虑了边界约束，提升缸最大摆角度，安装长度限制，不 干扰约束条件等约束条件，实现提升机构的优化设计 参考文献 [1] Wei Xiang, Sai Cheong Fok, Georg Thimm. Agent-based Composable Simulation for Virtual Prototyping of Fluid Power System. Computers in Industry. 2004, 54(3):237~251. [2] Peter Beater，Martin Otter. Multi-Domain simulation: Mechanics and Hydraulics of an Excavator. Proceedings of the 3rd International Modelica Conference，2003 [3] Kong Xiaowu，Qiu Minxiu, Wei Jianhua. A Atudy of the Influences of Pipe on Valve Control Hydraulics System. Proceedings of the 15th Internation Conference on Fluid Power Transmission and Control (ICFP2001), 2001. [4] Michael Decken, Hubertus Murrenhoff. Simulation of Fluid Power Components Using DSHplus and ADAMS. 2001 ASME International Mechanical Engineering Congress and Exposition. 2001. [5] Nong Zhang, Wade Smith, Jeku Jeyakumaran. Hydraulically interconnected vehicle suspension: background and modeling [J]. Vehicle System Dynamics: 2010, (1): 17-40. Funded project number: Z101103055010004.Beijing science and technology committee 第 5 页 共 5 页