外文文献翻译--基于80t起重机回转系统的动态模拟实验研究【中文2250字】 【PDF+中文WORD】

外文文献翻译--基于80t起重机回转系统的动态模拟实验研究【中文2250字】 【PDF+中文WORD】,中文2250字,PDF+中文WORD,外文文献翻译,基于80t起重机回转系统的动态模拟实验研究【中文2250字】,【PDF+中文WORD】,外文,文献,翻译,基于,80,起重机,回转,系统,动态,模拟 基于80t起重机回转系统的动态模拟实验研究 CHEN Jinshi , LIU Xinhui , Zhang Cui , DONG Quan , ZHAO Feng 摘要：本文模型研究80t汽车起重机回转系统的动态特性。分析的组成及液压系统的工作原理，建立回转系统基于AMESim模型，然后测试模型。仿真分析结果表明，影响动态的因素 系统的特点，提出了改进措施。结果表明，采用旁路电路使冲击压力降低百分之18系统运行；此外，改变系统的控制策略和安装单向节流提高制动稳定性明显。 关键词：汽车起重机 回转液压系统 动态仿真 压力冲击 1简介 最近，港口，地铁，高速公路等因国家投资迅速扩大，和发电站，冶炼设备，桥梁工程和高层建筑逐年增加，起重机行业进入快速发展期。回转系统是一个汽车起重机的重要组成部分。然而，回转机构的转动惯量和摩擦阻力大扭矩之间的机制，导致大液压系统工作时，回转系统启动的影响或停止使旋转稳定性差。因此，对回转系统的动态性能非常重要。传统的依靠经验和类比不满足要求高性能的液压系统。本文建立了基于AMESim模型模拟回转系统，研究通过仿真分析和动态稳定性实验测试。 2回转系统的组成和原理 80t汽车起重机回转系统属于开放泵控制马达回路。图1显示系统由主电路和控制电路组成。对压力补偿阀4使用组合方向控制阀5的主电路，消除了外部负载对系统的影响，使流进电机10是开放成正比阀5。阀9具有缓冲和填充油的功能。泵18提供了一个稳定的控制压力3MPa控制回路，整个控制回路电子优先阀门控制电路。蓄电池12可以消除补油压力瞬时脉动 [1-2]。图1 图1。汽车起重机回转液压系统 回转系统的工作原理如下： 1）旋转时，主控制阀13不发电上，回转机构锁紧，和旋转电机10不工作。 2）当阀13通电，系统控制电路连接到压力油。第一，油经制动控制阀15，打开制动11，回转刹车解除。然后，如果回油控制阀Y5，Y6是同时通电换向控制阀6没有电，回转系统是一个自调整状态。如果换向阀Y3是5通阀连接到左，而阀Y6通连接回油阀8，电机10的主回路连接，然后实现旋转平台旋转。如果阀Y4、Y5有权限的同时，将旋转平台逆转。 3）当操作装置需要停止转动时，这阀5处于中间状态，阀8关闭，并电机10的电源被切断。同时制动控制阀15失去权限，制动开始。回转机构的惯性力被缓冲器填充阀制动，最后装置停止。 3建立回转系统的AMESIM模型 根据组成及工作原理80t汽车起重机回转系统，建立仿真基于AMESim模型如图2所示。该模型由液压，信号，控制，机械和动力总成。在建模的过程中，一些液压元件是等价的，并简化了一定模型。更换液压控制阀和制动的电气控制模型，忽略了控制油路和通过组合电磁阀替代方向控制阀该模型的主要参数见表1。 泵容量 48 电机容量 28 电机轴等效转动惯量 0.0012 压力安全阀 23 缓冲补油阀压力 18 发动机转速 850~2200 方向控制阀的额定流量 120 额定流量的回油阀 120 制动力矩 250 减速器传动比 105.7 4仿真和实验结果分析 起重机的回转过程中，转动惯量和对回转机构的摩擦阻力矩的变化随着重配置，举重，繁荣角度和臂长，同时，转换静态和动态、变速转动时将也带来了他们[ 3-4 ]效果显著。据在实际条件下，模拟模型4.75t的重量，条件无负载，5m回转半径旋转控制手柄推快，分析该方向控制阀的进口压力。仿真结果显示在图3和实验结果如图4所示。比较图4发现 仿真和实验的趋势是一致的。两旋转任务周期期间，系统稳定压力和启动压力冲击6.2mpa。因此，模型的建立是正确的。 汽车起重机回转液压系统的AMESim模型 图为方向控制阀的入口压力的仿真结果 图为方向控制阀的入口压力的实验结果 通过分析，增加液压系统阻尼比可以降低启动压力的影响，回转机构[ 5 ]具有大惯性。各种速度控制回路比较，旁通回路具有增加系统阻尼比[ 6 ]特别的效果。当原系统旋转，方向控制阀和相应的回油阀通电构成回油回路，形成循环回路如果另一个回油阀打开。相同的参数设置下的系统，原来的系统回路和旁通回路有不同的结果。图5显示的结果两个循环马达进口压力。表示输入相同的信号方向控制阀，与原系统相比，该系统的循环开始滞后，该旁路回路压力降低2.5MPa，0.46s。 原系统的压力和循环的仿真结果环 当回转机构停止转动，这实验结果示于图6。该图显示了起重机，猛地一震，需要趋于10S稳定，整个系统的稳定性很差。这是因为方向控制阀在卸荷位置时间和制动关闭过早，然后两端该电机没有压力脉动和液压系统无法消耗掉平台的动能。 图为制动控制压力和电机的压力端口的实验结果 基于上述分析结果，优化回转系统参数下的仿真模型，提出了改进，如图7所示，修改原有系统的控制策略，增加了旁路回路和延迟刹车，控制信号外，安装了单向节流阀回油口 该制动器。测试系统的改进，其结果示于图8。如图所示，改进后的系统比原系统的冲击压力下2MPa和刹车关闭延迟时停止旋转。液压系统吸收平台的动能，因此整个系统的运动稳定。 改进后的系统的实验结果 5总结 （1）建立了基于AMESim的80t汽车起重机回转系统的仿真模型，并通过实验测试模型。然后，模拟和分析在启动和停止条件的回转系统的动态特性。 （2）旁路回路可以减小回转系统的惯性阻力矩和摩擦力矩大的启动压力的影响。它可有效的提高启动回转系统的稳定性。 （3）增加时间控制信号和安装单向节流阀液压制动回路可以保证制动延迟时停止旋转。因此，对回转机构的动能可以由液压系统充分吸收，和回转制动系统的稳定性可以得到改善。根据仿真分析结果，提高实车回转系统和测试系统。结果表明，回转系统的工作稳定性明显增强。 参考文献 [1] IMAGINE SA: Hydraulic Component Design Library version 8.0A [S], June 2008. [2] IMAGINE SA: AMESim version 8.0A [S], June 2008. [3] GAO Shunde, ZHANG Minghui, WANG Xin, LI Xihong. Simulation research of slewing hydraulic system on large crawler cranes [J]. Construction Machinery, 2007(7): 47-51. [4] ZHANG Minghui. Simulation research of slewing hydraulic system on large crawler crane [D].Dalin University of Technology, 2006. [5] YUE Liming. Dynamic analysis and design of hydraulic circuit for rotating mechanism in hydraulic crane [J]. Construction Machinery and Equipment, 1991(10):27-30. [6] HUANG Xiaojiang,BI Long. Dynamic Characteristics Simulation of Throttling Speed Control Circuit on Hydraulic System [J]. Machine Tool & Hydraulics, 2006(12):214-218. Dynamic Simulation and Experimental Study of Slewing System on 80T Crane CHEN Jinshi1,LIU Xinhui1,2,Zhang Cui1,DONG Quan3,ZHAO Feng1(1.College of Mechanical Science and Engineering,Jilin University,Changchun,130025 2.State Key Laboratory of Automobile Dynamics Simulation,Jilin University,Changchun,130025,China 3.Xuzhou Heavy Machinery Co.,Ltd.Xuzhou,221002,China)C AbstractThis paper models and studies the dynamic characteristics of slewing system of 80T truck crane.Analyzing the composition and working principle of the hydraulic system,and building the model of slewing system based on AMESim,then testing the model.And the simulation analysis results indicate the factors which affect the dynamic characteristics of the system and propose the measures to improve them.The results show that adopting the bypass circuit makes the shock pressure reduced 18 percent when the system operates;besides,changing the system s control strategy and installing one-way throttle enhance the stability of braking obviously.Keywords:truck crane slewing system dynamic simulation pressure shock I.INTRODUCTION Recently,as the country investment of ports,subway,highways and so on expanding rapidly,and power station,smelting equipment,bridge engineering and high-rise building increasing year by year,the crane industry has entered a rapid development period.Slewing system is an important part of truck crane.However,the slewing mechanism s moment of inertia and frictional resisting torque between mechanisms is large,which result in great impact on hydraulic system when the slewing system starts or stops and make the rotary stability badly.Therefore,analyzing the dynamic performance of slewing system is very important.Analyzing and designing the dynamic characteristics of hydraulic systems,the traditional methods of relying on experience and analogy haven t satisfied the requirements of high-performance systems.This paper builds the simulation model of slewing system based on AMESim,and studies the dynamic stability through simulation analysis and experimental testing.II.COMPOSITION AND PRINCIPLE OF SLEWING SYSTEM The slewing system of 80T truck crane belongs to open loop of pump-controlled motor.Fig.1 shows the system is composed of the main circuit and control circuit.The combination using of the pressure compensation valve 4 and the direction control valve 5 of the primary circuit eliminates the impact of external load on the system,so that the flow into the motor 10 is directly proportional to the opening of the valve 5.The valve 9 has buffer and filling oil functions.Pump 18 provides a stable control pressure 3Mpa to the control loop and the whole control loop is electronic priority valve control circuit.The accumulator 12 can eliminate pressure pulsation and fill oil transiently 1-2.1.pump 2.safety valve 3.shuttle valve 4.pressure compensation valve 5.direction control valve 6.reversing control valve 7.oil return control valve 8.oil return valve 9.oil fill valve 10.rotary motor 11.brake 12.accumulator 13.rotary main control valve 14.priority relief valve 15.brake control valve pression release valve 17.relief valve 18.pilot control pump 19.tank Figure 1.Hydraulic slewing system of truck crane Slewing system works as follows:1)When the rotary main-control valve 13 does not power up,the slewing mechanism is locked,and the rotary motor 10 does not work.2)When the valve 13 is electrified,the system control circuit connects to pressure oil.First,the oil through the brake control valve 15 and open the brake 11,the slewing brake is relieved.Then,if the oil return control valve Y5,Y6 was electrified simultaneously and the reversing control valve 6 did not power up,the slewing system is in a self-regulating state.If the reversing control valve Y3 was electrified and the valve 5 connected to the left,while the 2011 Third International Conference on Measuring Technology and Mechatronics Automation978-0-7695-4296-6/11$26.00 2011 IEEEDOI 10.1109/ICMTMA.2011.2821129valve Y6 was electrified and connected to the oil return valve 8,the main loop of the motor 10 is connected,and then realizing the rotary platform turning.If the valve Y4 and Y5 had power simultaneously,the rotary platform will turn reversed.3)When the operating device needs to stop turning,the valve 5 is in the middle state and the valve 8 is closed,and the power of the motor 10 is cut off.Meanwhile the brake control valve 15 loses of power and the brake starts to work.The inertia force of the slewing mechanism is absorbed by the buffer-fill valve and the brake,and the device stops finally.III.THE ESTABLISH OF SLEWING SYSTEM AMESIM MODEL According to the composition and working principle of 80T truck crane slewing system,establish the simulation model based on AMESim shown in Fig.2.The model consists of Hydraulic,Signal,Control,Mechanical and Powertrain.In the modeling process,some hydraulic components were equivalent,and the model was simplified necessarily.Such as replace the hydraulic control valves and the brake by electricity control model,neglect the control oil circuit and replace the direction control valve by a combination solenoid valve.The main parameters of the model are shown in table 1.Figure 2.AMESim model of truck crane slewing system TABLE I.MAIN PARAMETERS OF THE SLEWING SYSTEM MODEL pump capacity/(mlr-1)motor capacity/(mlr-1)equivalent moment of inertia of motor shaft/(kgm2)pressure of relief valve/MPa pressure of buffer fill valve/MPa rotational speed of engine/?r?min-1?rated flow of direction control valve/(L/min)rated flow of oil return valve/(L/min)torque of brake/Nm reducer transmission ratio teeth number of gear/module of gear/mm teeth number of tooth ring/module of tooth ring/mm 48 28 0.0012 23 18 850?2200 120 120 250 105.7 14/12 149/12 IV.SIMULATION AND EXPERIMENT RESULTS ANALYSIS During the crane slewing process,moment of inertia and frictional resistance torque of the slewing mechanism change along with the weight configuration,lifting weights,boom angle and boom length,meanwhile,transforming between static and dynamic and the speed changing when turning will also bring about significant effect to them 3-4.According to the actual conditions,simulate the model under the conditions of the weight 4.75t,no load,rotation radius of 5m and rotary controlling handle pushed quickly,and analyze the inlet pressure of the direction control valve.The simulation result is shown in Fig.3 and the experiment result is shown in Fig.4.Comparing Fig.3 and Fig.4 find that the simulation and the experimental trends are consistent.During the two rotating duty circle,the stable system pressure are 6.2Mpa and starting pressure shock are 10.8Mpa.Therefore,the model establish is correct.?Figure 3.Simulation result of inlet pressure of direction control valve Figure 4.Experimental result of inlet pressure of direction control valve 1130Through analysis,increasing the damping ratio of hydraulic system can reduce the starting pressure impact of the slewing mechanism which has large inertia 5.Comparison of various speed control loop,bypass loop has particular effect on increasing system damping ratio 6.When the original system rotates,the direction control valve and the corresponding oil return valve electrified constitutes a return oil circuit,which forms the bypass loop if another oil return valve is open.Under the same parameter settings of the system,the original system loop and the bypass loop have different simulation result.Fig.5 shows the results of motor inlet pressure of both loops.And the Fig.represents that input the same signal to direction control valve,comparing with the original system loop,the system pressure of the bypass loop reduces 2.5Mpa and has 0.46s hysteresis at the beginning.Figure 5.Simulation results of system pressure of the original and bypass loop When the slewing mechanism stops turning,the experimental results are shown in Fig.6.The figure presents that the crane shakes fiercely and needs 10s to tend stably and the whole system s stability is very poor.This is because the direction control valve is in the unloading position at this time and the brake shuts down prematurely,then both ends of the motor have not pressure fluctuation and the hydraulic system can t consume the platform s kinetic energy.Figure 6.Experimental results of brake control pressure and both ports of motor s pressure Figure 7.Improvements of the system Based on the above analysis results,optimize the parameters of the slewing system under the simulation model and put forward the improvements as shown in Fig.7,which modifies the original system s control strategy,adds the bypass loop and delays the control signal of the brake,besides,installs one-way throttle valve to the oil return port of the brake.Test the improved system,and the results are shown in Fig.8.As shown in the figure,the shock pressure of improved system is 2Mpa lower than the original system and the brake shuts down delay when rotation stops.The hydraulic system absorbs the kinetic energy of the platform,so the whole system motion stably.Figure 8.Experimental results of the improved system V.CONCLUSION (1)Establish the simulation model of the 80T truck crane slewing system based on AMESim,and test the model through experiments.Then,simulate and analyze the dynamic characteristics of the slewing system under the starting and stopping conditions.(2)Bypass loop can reduce the starting pressure impact of the slewing system which has large moment of inertia and frictional resistance torque.It can improve the starting stability of the slewing system effectively.1131(3)Increasing the time control signal and install the one-way throttle valve to the hydraulic brake loop can ensure braking delay when rotation stops.Therefore,the kinetic energy of the slewing mechanism can be absorbed by hydraulic system sufficiently,and the brake stability of the slewing system can be improved.According to the simulation and analysis results,improve the real vehicle slewing system and test the system.And the results show that the working stability of the slewing system is enhanced evidently.ACKNOWLEDGE This work is partly supported by the National 863 Project(2007AA04Z208).REFERENCES 1 IMAGINE SA:Hydraulic Component Design Library version 8.0A S,June 2008.2 IMAGINE SA:AMESim version 8.0A S,June 2008.3 GAO Shunde,ZHANG Minghui,WANG Xin,LI Xihong.Simulation research of slewing hydraulic system on large crawler cranes J.Construction Machinery,2007(7):47-51.4 ZHANG Minghui.Simulation research of slewing hydraulic system on large crawler crane D.Dalin University of Technology,2006.5 YUE Liming.Dynamic analysis and design of hydraulic circuit for rotating mechanism in hydraulic crane J.Construction Machinery and Equipment,1991(10):27-30.6 HUANG Xiaojiang,BI Long.Dynamic Characteristics Simulation of Throttling Speed Control Circuit on Hydraulic System J.Machine Tool&Hydraulics,2006(12):214-218.1132