Numerical Model Calibration forSimulating Coal Pillars, Gob and Overburden Respnse
An Automated Method to Calibrate Industrial Robot Kinematic
Abstract —This paper describes our new method and updatedsystem for industrial robot kinematic parameters calibration. The system consists of an IRB 120 industrial robot, a laser tool attached to the robot’s end-effector, a rotatable position sensitive detector (PSD), and a PC based controller. In the process of calibration, the surface of the PSD can be rotated around a fixed center, and the center points of PSD surface keep in a same 3D spherical surface. In the each position, the laser beams with small angles are aimed at the surface of the PSD and the laser spots are automatically located to the center of rotatable PSD. The calibration algorithm with different optimization objective functions have been adopt to identify the robot parameters. The simulation results verify the effectiveness of both the sensitivity analysis and the developed system.I. I NTRODUCTIONt is common issue that industrial robots are highly repeatable but not accurate. Accuracy has not been deemed necessary insome simple industrial application. However, for moreThis work was supported in part by the National Natural Science Foundation of China under grants 61175082, Jiangsu prospective joint research project under grants BY2013046, Jiangsu Science & Technology Pillar Program under grants BE2011192 and and Lianyungang joint research project under grants CXY1310, A beforehand research project under grants 9140A03030713BQ02033, the Jiangsu key laboratory of image and video understanding for social safety (Nanjing university of science and technology) under grant No.30920130122006.Yong Liu, Dingbing Shi and Jixiang Ding are with the of Computer Science and Technology, Nanjing University of Science and Technology, Nanjing, China (corresponding author to e-mail: liuy1602@).advanced applications, such as robotic surgery, accuracy playsa significant role. Consequently, a simple, fast, and accurate robot kinematic model with real parameters identified through a calibration process is needed. Physical errors, such as machining tolerances, assembly errors and elastic deformations, cause the geometric properties of a manipulator to be different from their ideal values. Calibration of the geometrical parameters of a manipulator is important to ensure the accuracy of robot positioning.To improve robot accuracy several calibration techniques have been used, including open and closed-loop methods. Open-loop methods [1][2] require an external metrology system to measure the end-effector pose, such as theodolites. Obtaining open-loop measurements is generally very costly and time consuming, and must be performed regularly for very high precision systems and replies on the operator’s skill. In contrast, closed-loop methods only need joint angle sensing, and the robot becomes self-calibrating.These closed-loop [3]-[9] methods impose some constraints on the end effector, and the joint readings alone are used to calibrate the robot using kinematic closed-loop equations. Marco A. Meggiolaro first proposed a method called Single Endpoint Contact (SEC) calibration, the robot endpoint is constrained to a single contact point. However, it is almost impossible to exactly fit point constraint Newman et al. [10] and Chen et al. [11] proposed a calibration method using laser line tracking. This approach relies upon constraining the point on the end-effector moving along a stationary laser beam. However, it is difficult to exactly and automatically fit the line constraint.A new method called “virtual closed kinematic chain”An Automated Method to Calibrate Industrial Robot Kinematic Parameters Using Spherical Surface Constraint ApproachYong Liu, Senior Member, IEEE , Dingbing Shi and Jixiang DingIThe 4th Annual IEEE International Conference onCyber Technology in Automation, Control and Intelligent SystemsJune 4-7, 2014, Hong Kong, China(ViCKi) [12] is proposed. Unlike previous closed-loop methods, this approach does not require any physical constraints. In the proposed method, a laser pointer tool, attached to the robot’s end effector, aims at a constant but unknown location on a fixed object, effectively creating a virtual 7 DOFs closed kinematic chain.An industrial robot joint offset calibration method called the virtual line-based single-point constraint approach[13] is proposed, this proposed method relies mainly upon a laser pointer attached on the end-effector and single position-sensitive detector (PSD) arbitrarily located on the workcell. The automated calibration procedure involves aiming the laser lines loaded by the robot towards the center of the PSD surface from various robot positions and orientations. However, in order to keep laser lines intersect at a same point in high accuracy, the laser lines should approximately perpendicular aiming towards the center of the PSD surface. So the working area of robot is narrowed, in this paper a rotatable PSD is adopted to solve this problem.This paper is structured as follows: the calibration system is presented in Section II. The methodology of kinematic parameter calibration is described in Section III. The simulation and experimental results are demonstrated in Section IV. Finally, we conclude the work.II.C ALIBRATION S YSTEMThe structure of this industrial-robot calibration system, is shown in Fig.2 and the actual, physical system is shown in Fig.1. The figures show the main components of the robot calibration system, which consists of an industrial robot, a designed end-effector fixture, a rotatable PSD and an industrial computer. A focusable laser pointer with its adapter is fixed and rigidly attached on the end-effector of the robot. The laser beam is adjusted to align its orientation toward the X-axis of the end-effector frame. The robot loads the laser to shoot a beam onto the surface of the PSD.The rotatable PSD is shown in Fig.3. The surface of the PSD can rotate around a fixed point, which keeps that the center point of PSD always in a same 3D spherical surface. In the process of calibration, the laser lines should approximately perpendicular (or small angle with the vertical of PSD surface) aiming towards the center of the PSD surface. The rotatable PSD not only expands the working area of robot but also improves the accuracy of positioning.Fig.1 The developed industrial robot calibration systemFig.2The designed structure of industrial robot calibration systemPSD surfaceLEDRotationmechanismIRB 120LaserRotatablePSDA/D interfaceCameraPSDFig.3 The developed industrial robot calibration systemThe position of beam point can be checked by PSD sensor and be acquired to the computer by AD board. The errors, between target position and actual current position of the laser spot on the surface of the PSD, are used to guide the robot to move to the desired position precisely.The computer communicates with the ABB robot via sockets based on TCP/IP protocol and can send orders to control the robot according to joint-level instructions or Cartesian instructions. The PC-based controller can obtain the current robot position information (task space and joint space) from the robot controller and send the control command to the robot controller as well as update the target position in real-time.III. CALIBRATION METHODOLOGYA ǃ Kinematic Error ModelThe Denavit-Hartenberg (J. Denavit, R.S. Hartenberg 1955) convention is widely used for defining frames of reference for describing the forward kinematics. A model of the IRB120 robot according to D-H conventions is given in Table 1.»»»»¼º««««¬ª 1000cossin 0)sin(sin )cos(cos )cos()sin()cos(sin )sin(cos )sin()cos(1i i i i i i i i i i i i i i i i i i i d a a T D D T D T D T T T D T D T T (1) wherei i T 1represents the homogeneous transformation fromi-1th frame to ith frame, i i i i d a T D ,,,are generally named as link length, link twist, link offset, and joint angle ,respectively.Table 1 D-H parameters for ABB IRB 120 RobotAxis ș d a Į 1 2 3 4 5 6ș1 ș2 ș3 ș4 ș5 ș6d 1 0 0 d 4 0 d 60 a 2 a 3 0 0 0Į1 0 Į3 Į4 Į5 0Combining the six coordinate frames, nominal forward kinematics of the IRB120 become,76655443322110T T T T T T T T (2)B ǃCalibration MethodologyThe calibration method relies mainly upon a laser pointer attached on the end-effector of a robot and a rotatable PSD. The surface of the PSD can rotate around a fixed point, which keeps that the center point of PSD always in a same 3D spherical surface. As shown in Fig.4, the calibration procedure is first fixing the PSD at an appropriate angle and aiming a laser beam from the laser pointer at the same point from various positions and orientations by using hybrid visual/PSD servoing. Then changing the pose of the PSD driven by the motor, and aiming laser beams at the same point by the method above. The same point is the center point of the PSD and the coordinates of the point in the robot base frame are unknown. Suppose M*N Sets of robot joint angles are recorded during the localization. There are M groups joint angles and N joint angles in each group, that means N laser beams intersecting at a same point and M point locating at a same spherical surface. Substituting the recorded joint angle into the forward kinematics (Equation (2)), the homogeneous transformations of end-effector fame with regard to the robot base frame are given by»»»»¼º««««¬ª1000333222111z y x p z y x p z y x p z y x (3)A laser tool, a focusable laser pointer with its adapter, is rigidly attached on the end-effector of the robot. The laser line is adjusted to roughly align its orientation toward the x-axis in the end-effector frame. Once the laser pointer and the adapter is fixed, the laser line in the end-effector frame is given byEl E l E l P z z N y y M x x (4)where l l l z y x ,,is the position of one point of the laser line in the end-effector fame and E E E P N M ,, is the unit vector of the laser line orientation in the end-effector fame.Suppose N sets of joint angle in each group are recorded after calibration. From Equation (4) N laser lines are obtained. Each two laser lines have one intersection, so there areOLQH 1Fig.4 The process of calibration)1(21N N intersections from N lines. And the mean point of the total intersections can be achieved.G G G z y x ,, denotes thesum of error from )1(2/1 N N intersections to the mean point in the x, y, z directions, respectively. So M mean points ),,(l l l l z y x P , M l ,,2,1 are constrained by one spherical. Spherical surface can be fitted by any four of M mean points.0111114444333322221111 z y x s z y x s z y x s z y x s z y x s ˄5˅where 222z y x s ,222i i i i z y x s 4,3,2,1 i , where i i i z y x ,, 4,3,2,1 i is the position of any four of M (M>4)mean points. k Q ,K k ,,2,1 denote the center of the sphere , there are )3)(2)(1(24/1 M M M M K centers of sphere from M mean points. ),,(z y x Q denotes mean point of K centers of the sphere. The coordinate errors of the points between k Q andQ are denoted as V V V zy x ,,in the x, y, z directions, respectively. The kinematic parameters are identified by minimizing the total sum of the coordinate errors. There are two kinds of optimization objective functions.The first kind is just using the error of centers of the sphere as the optimization objective function.V V V G z y x Min arg * ˄6˅The second kind combines the error of enters of the sphereand error of intersections.G G G V V V G z y x z y x Min arg * (7)C ǃProcedureCombined with fig.4, the procedure is summarized inthese steps. Step 1: Change the pose of PSD driven by a motor. The center of PSD surface is always in a same spherical surface. Step 2: Guide by the visual servo, the robot is controlled to move and the spot of the laser pointer attached at the end-effector is located on the PSD active area at one pose.Step 3: When the laser beam from the laser pointer shoots onto the surface of PSD, the controller is switched to the PSD guided servo for precision localization. That is, the position of beam point can be checked by PSD sensor and be acquiredto the computer by AD board. The errors, between targetposition and actual current position of the laser spot on the surface of the PSD, are used to guide the robot to move to thedesired position precisely. Thus the first line is obtained.Step 4: Repeat step 2 and step 3. The same action is repeated. The difference is that robot changes to another pose.Then we obtain another line. Each two lines have oneintersection point (or common perpendicular center), then calculate the average point of these intersection points. Step 5˖Repeat step 1 and step 4. The same action isrepeated. The difference is that PSD changes to another pose. In each pose, one average intersection point will get and all these points constrain at a same spherical surface. Step 6: Computing the parameters of the each fouraverage intersection points. Step 7: Substituting the parameters into Equation (6) then the kinematic parameters are identified. IV. EXPERIMENTAL RESULTS AND DISCUSSION Simulation of the calibration experiment was performed using very accurate joint readings. A robot was created in Simulink with a known set of parameters as the factory design. The laser pointer was fixed on the end-effector toward theX-axis of the end-effector frame, as in the experimentaldesign. A virtual rotatable PSD was built as a feedback toexactly locate the laser beam on the center of the PSD surface.The two different kinds of optimization objectivefunctions have been used to calibrate the robot. The result ofcalibration with perfect data is shown in Table II. Column 2shows the actual offset parameters used by the simulation.Column 3 shows the initial parameters for the LMA. Column2 shows the solution of the optimization using equation (6)and the result shows that using this optimization objectivefunction to calculate the error of robot parameters cannot besuccessful. Table 2 presents partial data of the final i ntersections of laser lines when the iterative of optimization stop. From the data of table 2, all the mean intersections are ata same spherical surface, but the intersections of laser lines ineach group don’t converge to one point. The result ofcalibration in column 2 of table 2 are incorrect, therefore,using equation (6) as optimization objective function cannotsolve this problem.Table 2 THE INTERSECTIONS OF LASER LINESThe intersections of laser linesThe mean intersections1) (752.708364 24.902123 111.511853)(779.470923 25.810713 75.258997)(765.517424 26.268866 95.033415)(765.89890425.66056793.934755)2˅(672.186026 23.160547 28.616782)(679.762640 22.260981 115.164029)(675.853295 23.677631 121.726975)(675.93398723.033053121.835929)3˅(740.859442 78.891738 63.776401)(669.888290 57.713157 179.267000)(762.359559 86.000925 22.433060)(724.36909774.20194088.492154)4) (733.581663 -27.370943 76.484291)(693.585793 -18.586751 143.306996)(713.166918 -24.626421 108.771789)(713.444791-23.528038109.521025)5˅(759.964842 21.024512 106.959947) (767.362034 21.435361 97.150865) 21.329374 101.556788)6˅(681.295289 19.475693 93.688693)(662.287993 19.061408 133.901320)(668.959645 19.654634 116.374301)(670.84764219.397245114.654771)7˅(670.895036 23.604863 93.584571)(657.062795 24.068211 125.342953)(669.502523 22.466880 96.303557)(665.82011823.379985105.077027) Another improved optimization objective function(equation (7)) has been used to solve this problem, which the error of intersections of laser lines have been added into the function. Column 5 shows that the solution using equation (7) as optimization objective functions was perfect. Fig.5 shows that the sphere centers are discretely distributed in the 3D-space at beginning and all these centers converge to one point at last. In theory the result verified the effectiveness ofthe proposed method.Fig.5 The distribution of sphere centersTable 3 CALIBRATION RESULTS (PRECISE DATA) parametersInitialvalueActualerrorFirstoptimizationfunctionsecondoptimizationfunction 1a0 0 0 01D-90e0 0.05 02T0 0 -0.0480e02d0 0.05 -0.1996 0.04912a270 -0DŽ1 0.0342 -0.1105 2D0 0 0 0.00313T0 0 -0.0494e0.00123d0 -0.05 -0.1996 -0.05013a70 -0.04 0.0995 -0.04003D-90e-0.3e0.4165e-0.3010 4T0 0 -0.0499e0.00034d302 0.04 -0.0973 0.03994a0 0 -0.0010 0.0041 4D90e-0DŽ06e0.2099e-0.06245T0 0 -0.0500e0.00035d0 0.04 0.1982 0.04305a0 0 -0.0073 0.00325D-90e0 -0.2612e-0.0018 6T0 0 0.05 0.0039 6d72 0 -0.4910 -0.00146a0 0 0 0.00036D0 0 0.0001 0.0009V.C ONCLUSIONRobot calibration plays a significant role in improving the robot accuracy of the current complicated manufacturingprocesses. Robot kinematic parameters have a much larger influence on robot positioning accuracy. To address this issue, a Spherical Surface constraint approach and well-developed kinematic parameters calibration system for industrial robots were presented in this paper. Simulation results verify the feasibility of the proposed method and demonstrate the developed system can fit the need of kinematic parameters calibration for the industrial robot user. The further simulations and experiments will be conducted on the real robot to verify the proposed method and the developed system.R EFERENCES[1] M. R. Driels, L. W. Swayze, and L. S. Potter, “Full-pose calibration of arobot manipulator using a coordinate measuring machine,” Int. J. Adv.Manuf. Technol., vol. 8, no. l, pp. 34–41, 1993.[2] M. Vincze, J. P. Prenninger, and H. Gander,“A laser tracking system tomeasure position and orientation of robot end effectors under motion,”Int. J. Robot. Res., vol.13, pp. 305–314, 1994.[3] D. W. Osborn and W. S. Newman, “A new method for kinematicparameter calibration via laser line,” in Proc. IEEE Int. Conf. Robot.Autom, 1993, vol. 2, pp. 160–165.[4] M. Ikits and J. M. Hollerbach, “Kinematic calibration using a planeconstraint,” in Proc. IEEE Int. Conf. Robot. Autom., 1997, pp.3191–3196.[5] H. Zhuang, S. H. Motaghedi, and Z. S. Roth,“Robot calibration withplanar constraints,” in Proc. IEEE Int. Conf. Robot. Autom., Detroit, MI,1999, pp. 805–810.[6] D. J. Bennet and J. M. Hollerbach, “Autonomous calibration, ofsingleloop closed kinematic chains, formed by manipulators with passive endpoint constraints,” IEEE Trans. Robot. Autom., vol. 7, no. 5, pp.597–606, Oct. 1991.[7] M. A. Meggiolaro, G. Scriffignano, and S. Dubowsky, “Manipulatorcalibration using a single endpoint contact constraint,” presented at the 26th Biennial Mech. Robot. Conf. 2000 ASME Design Eng. Tech. Conf., Baltimore,MD, Sep. 2000.[8] L. J. Everett and C. Y. Lin, “Kinematic calibration of manipulators withclosed loop actuated joints,” in Proc. IEEE Int. Conf. Robot. Autom., Philadelphia, PA, 1988, pp. 792–797.[9] L. Giugovaz and J. M. Hollerbach,“Closed loop kinematic calibration ofthe Sarcos Dexterous Arm,” in Proc. IEEE/RSJ Intl. Conf. Intell. Robots Syst. Sep. 12–16, 1994, pp. 329–334.[10] W. S. Newman and D.W.Osborn,“A new method for kinematicparameter calibration via laser line,” in Proc. IEEE Int. Conf. Robot.Autom., 1993, vol. 2, pp. 160–165.[11] H. Chen, T. Fuhlbrigge, S. Choi, et al. “Practical Industrial Robot ZeroOffset Calibration,” IEEE Conference on Automation Science and Engineering, 23-26 Aug. 2008.[12] C. S. Gatla, R. Lumia, J. Wood, and G. Starr, “Calibration of industrialrobots by magnifying errors on a distant plane,” presented at the IEEE Int.Conf. Intell. Robots Syst., San Diego, CA, Oct. 29–2 Nov. 2007.[13] Yong Liu, Ning Xi and George Zhang,” An automated Method toCalibrate Industrial Robot Joint Offset Using Virtual Line-based Single-point Constraint Approach” in IEEE/RSJ International Conference on Intelligent robots and Systems, pp.715-720, October, 2009。
六棱柱模块化可展开天线形面精度分析
第29卷第12期2021年12月Vol.29No.12Dec.2021光学精密工程Optics and Precision Engineering六棱柱模块化可展开天线形面精度分析田大可1,范小东1,金路2*,刘荣强3,张珂1(1.沈阳建筑大学机械工程学院,辽宁沈阳110168;2.沈阳建筑大学土木工程学院,辽宁沈阳110168;3.哈尔滨工业大学机器人技术与系统国家重点实验室,黑龙江哈尔滨150001)摘要:针对空间可展开天线大型化、模块化、高精度化发展趋势,提出一种六棱柱模块化空间可展开天线支撑结构形面精度分析模型。
阐述了六棱柱模块化空间可展开天线的结构组成,分析了六棱柱模块化结构的拓扑规律。
基于等包络圆思想及机器人学基本理论,提出了点面法和两点法2种包络圆数学建模方法,并由此建立了等包络圆交点数学模型及肋单元夹角数学模型,进而构建了用于六棱柱模块化可展开天线支撑结构形面精度分析的数学模型。
最后,采用数值仿真与试验验证相结合的方式对建立的模型进行了验证。
仿真及试验结果表明:包络圆能紧密地贴合在球面上,与球面吻合良好;数值仿真模型状态下,六棱柱模块间实现了准确连接;试验中特征点的绝对误差主要分布在5~10mm,相对误差主要集中在0.05%~0.1%,肋单元夹角绝对误差多分布在0.05°~0.1°之间,表明测量值和理论值间偏差较小、吻合较好。
所提出的形面精度分析模型能够求解出所有模块连接点的空间坐标,为超多模块可展开天线形面精度的分析及研究提供了理论基础。
关键词:可展开天线;模块化;形面精度;数值仿真;工业摄影测量;大口径;坐标变换中图分类号:V443.4文献标识码:A doi:10.37188/OPE.20212912.2855Surface accuracy analysis for hexagonal prism modulardeployable antennaTIAN Da-ke1,FAN Xiao-dong1,JIN Lu2*,LIU Rong-qiang3,ZHANG Ke1(1.School of Mechanical Engineering,Shenyang Jianzhu University,Shenyang110168,China;2.School of Civil Engineering,Shenyang Jianzhu University,Shenyang110168,China;3.State Key Laboratory of Robotics and System,Harbin Institute of Technology,Harbin150001,China)*Corresponding author,E-mail:jinlu@Abstract:A surface accuracy analysis model for the support structure of a hexagonal prism modular de⁃ployable antenna is proposed because of the large-scale,modular,and high-precision development trend of deployable antennas.The structural composition of the hexagonal modular deployable antenna is elaborat⁃ed,and the topological rules of the hexagonal modular structure are analyzed.Based on the idea of equal 文章编号1004-924X(2021)12-2855-13收稿日期:2021-05-17;修订日期:2021-07-01.基金项目:国家自然科学基金重点项目(No.51835002);中国博士后科学基金面上项目(No.2019M661126);辽宁省教育厅科学研究面上项目(No.LJKZ0563);辽宁省“兴辽英才计划”青年拔尖人才项目(No.XLYC1807188)第29卷光学精密工程envelope circles and the basic theory of robotics,two mathematical modeling methods of envelope circle,point-surface method and two-point method,are proposed,from which the mathematical model of the in⁃tersection point of the equal envelope circle and the mathematical model of the included angle of rib unit are established;the mathematical model for accuracy analysis of the shape surface of the support structure of a modular deployable antenna with a hexagonal prism is built.Finally,the model is verified using a combina⁃tion of numerical simulations and experimental verifications.The simulation and experimental results show that the enveloping circle can closely fit on the spherical surface,and it is in good agreement with the spher⁃ical surface.In the numerical simulation model,the modules of the hexagonal prism are connected accu⁃rately.In the experiment,the absolute error of feature points is mainly distributed in5to10mm,the rela⁃tive error is mainly concentrated in the range of0.05%to0.1%,and the absolute error of the rib unit an⁃gle is mostly distributed in the range of0.05°to0.1°.The deviation between the measured and the theoret⁃ical values is small,and the values are in good agreement.The proposed model can solve the spatial coor⁃dinates of all module connection points,which provides a theoretical basis for the analysis and research of the shape accuracy of multi-module deployable antennas.Key words:deployable antennas;modularization;surface accuracy;numerical simulation;photogram⁃metry;large aperture;coordinate transformation1引言空间可展开天线是航天器无线通信系统中不可或缺的重要装备[1-3],同时也是国际宇航界研究的前沿与热点,广泛应用于星际探测、卫星导航、移动通信、电子侦察和射电天文等领域[4-6]。
直流电磁铁磁场和牵引力的数值模拟
2005年2月农业机械学报第36卷第2期直流电磁铁磁场和牵引力的数值模拟*付文智 李明哲 邓玉山 【摘要】 从工程应用的观点出发,阐述有限元法在电磁场数值分析中的应用。
首先建立直流螺管式电磁铁的数学模型,并用有限元法对电磁铁进行了求解。
得到电磁场的等磁位线、磁通密度等参数的分布规律及动铁芯的吸力与行程的关系。
与实际测试的吸力基本吻合,相对误差为5.8%。
为电磁铁的设计和安装过程中控制牵引力提供了理论依据,即控制了工作气隙D c ,也就等于控制了牵引力F c 。
关键词:电磁铁 数学模型 有限元法 电磁场中图分类号:TM153+.3;O242.82文献标识码:ANumer ical Simulation for Electromagnetic Field and ItsTr action Used in Multipoint Forming MachineFu Wenzhi Li Mingzhe Deng Yushan(J ilin University )Abstr actApplication of finite element method for numerical simulation of electromagnetic field was stated in this paper in view of engineering application.At first,mathematical model for DC spiratr on type electromagnet was constructed and its mathematical model for electromagnet was solved with finite element method .Distribution of electr omagnetic intensity ,flux density isodynamic lines in electromagnet field and relation of electromagnetic traction and its displacement wer e obtained.Theoretical results tallies with its test and its relation errors is 5.8%.It is a theoretical groundwork that electromagnetic traction is controlled in designed and fixed electr omagnet,i.e.controlling working air gap D c is controlling electromagnetic traction F c .Key words Electr omagnet,Mathematical model,Finite element method,Electromagneticfield收稿日期:20030602*国家自然科学基金资助项目(项目编号:50275063)和“十五”国家科技攻关计划资助项目(项目编号:2001BA 203B 11)付文智 吉林大学辊锻工艺研究所 副教授,130025 长春市李明哲 吉林大学辊锻工艺研究所 教授 博士生导师邓玉山 吉林大学辊锻工艺研究所 工程师 引言有限元分析技术在多点成形领域中的应用对其发展和完善起到重要的推动作用。
管外翅片强化传热途径与研究进展
技术综述收稿日期:2004 04 16作者简介:徐百平(1969 ),男,吉林公主岭人,博士,从事高分子材料加工动力学模拟仿真、化工过程强化传热与节能以及传热过程的热力学效能评价方面的工作。
文章编号:1000 7466(2004)05 0041 04管外翅片强化传热途径与研究进展徐百平1,2,朱冬生2,黄晓峰1,顾雏军1(1 华南理工大学,广东广州 510640; 2.广东科龙电器股份有限公司博士后工作站,广东佛山 528303)摘要:介绍了管翅式换热器管外翅片强化传热的措施及其最新研究进展,总结了不同翅片形式强化传热的机理及翅片参数对传热与流阻的影响规律。
提出了翅片尺度的新概念,并指出了今后的研究方向。
关 键 词:换热器;翅片;强化传热中图分类号:TQ 051 501 文献标识码:AThe measurements and study advances for the heat transfer enhancement of outer fins of tubeXU Bai pi ng 1,2,ZHU Dong sheng 2,HUANG Xiao feng 1,GU Chu jun 1(1 College of Industrial Eq uipment and Control Eng ,SouthChina University of Technology,Guangzhou 510640,Chi na;2 Guangdong Kelon Electrical Holding Co Ltd ,Foshan 528303,China)Abstract :The measurements and up to datestudy advances for the heat transfer enhancement of ou ter fins in tube fin heatexchangers are reviewed,the mechanism of heat transfer enhancement and effectof fin parameters on heat transfer and flow resistance are sum marized Meanwhile,the novel concept of fin scale is proposed and further research direction is g i venKey words :heat ex changer;fin;heat transfer enhancement 管翅式换热器是空调中最常用的换热器结构形式,冷、热流体间壁错流换热,管内走冷媒,管外为空气。
Calibration procedures for a computational model of ductile fracture
Calibration procedures for a computational model of ductile fracture Z.Xue a,1,M.G.Pontin b,2,F.W.Zok b ,J.W.Hutchinson a,*aSchool of Engineering and Applied Sciences,Harvard University,Cambridge,MA,United States b Materials Department,University of California,Santa Barbara,CA,United Statesa r t i c l e i n f o Article history:Received 18August 2009Received in revised form 22October 2009Accepted 29October 2009Available online 1November 2009Keywords:Ductile fracture Computational fracture Shear fracture Damage parametersa b s t r a c tA recent extension of the Gurson constitutive model of damage and failure of ductile struc-tural alloys accounts for localization and crack formation under shearing as well as tension.When properly calibrated against a basic set of experiments,this model has the potential topredict the emergence and propagation of cracks over a wide range of stress states.Thispaper addresses procedures for calibrating the damage parameters of the extended consti-tutive model.The procedures are demonstrated for DH36steel using data from three tests:(i)tension of a round bar,(ii)mode I cracking in a compact tension specimen,and (iii)shearlocalization and mode II cracking in a shear-off specimen.The computational model is thenused to study the emergence of the cup-cone fracture mode in the neck of a round tensilebar.Ductility of a notched round bar provides additional validation.Ó2009Elsevier Ltd.All rights reserved.1.IntroductionProgress in computational fracture mechanics has paralleled advances in constitutive models that incorporate damage mechanisms.For many ductile structural alloys the mechanism governing failure is void nucleation,growth and coalescence.The grand challenge for these alloys is the development of a computational capability for predicting localization,crack for-mation and crack propagation under all states of stress.Capturing both tensile (mode I)and shear (mode II)fractures has been particularly challenging.When properly calibrated for a specific structural alloy,the Gurson model [1]and some of its close relatives,such as the Rousselier model [2],have shown considerable promise for characterizing mode I crack growth[3–8].In addition,the models have been used to simulate transitions from mode I crack growth to mixed mode shear crack-ing in the cup-cone fracture process of round tensile bars [9,10]and in three-dimensional through-cracks in thin plates [11].Such transition problems are generally more challenging because the constitutive models have not been developed to explic-itly address damage under shear dominated conditions.A recent extension of the Gurson model [12]specifically incorporates damage in shear,adding the flexibility to address shear ruptures as well as tension dominated failures.This extension will be employed here in conjunction with a suite of three tests (round bar tension,mode I compact tension,and mode II shear-off)to calibrate the constitutive parameters for the structural steel,DH36.For verification,the calibrated model is then used to study the failure details of several other problems.To put the overall objectives of this work into some perspective,it is noted that three parameters are required to calibrate the extended Gurson model:the initial void volume fraction,f 0,a shear damage coefficient,k x (defined below)and the finite element size,D .To accurately characterize localization and fracture,D must be on the order of the spacing between the voids 0013-7944/$-see front matter Ó2009Elsevier Ltd.All rights reserved.doi:10.1016/j.engfracmech.2009.10.007*Corresponding author.E-mail address:hutchinson@ (J.W.Hutchinson).1Present address:Schlumberger Reservoir Completions,Rosharon,TX,United States.2Present address:Ceradyne,Costa Mesa,CA,United States.Engineering Fracture Mechanics 77(2010)492–509Contents lists available at ScienceDirectEngineering Fracture Mechanicsj o u r n a l h o m e p a g e :w w w.elsevier.c om /loc ate/engfracmechthat dominate the fracture process,typically from tens to hundreds-of microns.With mesh requirements this fine,it is only possible to predict the onset and propagation of cracks in relatively small components or in larger structures where the loca-tion of the failure can be anticipated in advance.In contrast,it would not be feasible to employ a fracture model of this type to analyze fractures in large structures where the failure locations cannot be anticipated.Under such circumstances,because the finite element size for a large structure is necessarily orders of magnitude greater than void spacing and often larger than plate thickness,coarser criteria based on a critical effective plastic strain or a through-thickness cohesive zone must be em-ployed.These criteria must also be calibrated for each material,but against tests that make no attempt to resolve the fine scale fracture processes relevant for the present class of models.The two classes of fracture models complement each other.In principle,computations based on a fine scale model could be used to calibrate a coarse scale model.2.The extended Gurson modelThe Gurson model is an isotropic formulation that employs the mean stress,r m =r kk /3,and the effective stress,r e ffiffiffiffiffiffiffi3J 2p ¼ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi3s ij s ij =2p ,where s ij ¼r ij À13r kk d ijis the stress deviator.The extended model [12]employs,in addition,the third stress invariantJ 3¼det ðs Þ¼13s ij s ik s jk ¼ðr I Àr m Þðr II Àr m Þðr III Àr m Þð1Þwhere the expression on the right is couched in terms of principal stresses,assumed to be ordered asr I P r II P r III .Thenon-dimensional metric x ðr Þ¼1À27J 3r 3e 2ð2Þlies in the range,06x 61,with x ¼0for all axisymmetric stress states,r I P r II ¼r III or r I ¼r II P r III ;ð3Þand x ¼1for all states comprised of a pure shear stress plus a hydrostatic contribution,r I ¼s þr m ;r II ¼r m ;r III ¼Às þr m ðs >0Þð4ÞThe original Gurson model was formulated and calibrated based on the mechanics of void growth under axisymmetric stress states.The extension [12]does not alter the model for these states.The extension modifies the predictions for states with non-zero x ðr Þ.In particular,a contribution to damage growth under pure shear stress states is accounted for in the extension whereas the original Gurson model predicts no change in damage for states having r m ¼0.NomenclatureA 0;Across-sectional area of neck:initial,current Dcharacteristic element size D P ij plastic strain rate EYoung’s modulus f 0;f ;f c ;f fvoid volume fraction:initial,current,onset of coalescence,failure Hplate thickness J 3stress invariant k xshear damage coefficient Nstrain hardening exponent q 1;q 2;q 3fitting parameters in Gurson model Rpunch radius s ijstress deviator d punch displacemente fductility—true strain in neck at failure e P M ;r Mintrinsic true plastic strain and stress in tension (damage-free)e peak T ;r peak T true strain and stress at maximum nominal stress r ij ;r e ;r m true stress,effective stress,mean stress r I P r II P r III true principal stressesx measure of shearing relative to axisymmetric stressingZ.Xue et al./Engineering Fracture Mechanics 77(2010)492–509493The yield surface of the extended Gurson model is the same as the original.Including the fitting parameters,q 1,q 2and q 3,introduced by Tvergaard [13],it is given in terms of the effective and mean stress measures byF ðr e ;r m ;f Þ¼r e r M 2þ2q 1f cos h 3q 2r m r M Àð1þq 3f 2Þð5ÞThe current state is characterized by f ,the ‘‘apparent”void volume fraction,and r M ,the current effective stress governing flow of the damage-free matrix material.All quantities not labeled with the subscript M represent overall quantities asso-ciated with the bulk material.Normality implies that the plastic strain rate,D Pij ,is given byD Pij ¼1h P ij P kl _r kl ð6Þwhere P ij ¼@F r ij ¼3s ij r M þfq 1q 2r M sin h 3q 2r m r M d ij ð7ÞIn finite strain formulations,_rij is identified with the Jaumann rate of stress.The hardening modulus,h ,is identified in the Appendix A .If r m ¼0,P kk ¼0and the rate of plastic volume change vanishes,i.e.,D Pkk ¼0;this feature persists in the exten-sion.In the absence of nucleation,the extension of the Gurson model posits_f ¼ð1Àf ÞD p kk þk x f x ðr Þs ij D p ij r e ð8ÞThe first contribution is that incorporated in the original model while the second is the crux of the extension.As previ-ously noted,the modification leaves the constitutive relation unaltered for axisymmetric stress states.In a state of pureshear,however,(8)gives _f ¼k x f _cP =ffiffiffi3p ,where _c P is the plastic shear strain rate and k x is the shear damage coefficient,the sole new parameter in the extended model.The inclusion of the second term in (8)rests on the notion that the volume of voids undergoing shear may not increase,but void deformation and reorientation contribute to softening and constitute an effective increase in damage [14–16].In addition,the second term can model damage generated by the nucleation in shear of tiny secondary voids in void sheets linking larger voids.Thus,in the extension,f is no longer directly tied to the plastic volume change.Instead,it must be regarded either as an effective void volume fraction or simply as a damage param-eter,as it is for example when the Gurson model is applied to materials with distinctly non-spherical voids.Further discus-sion and illustrations of the extension are given in [12],where the emphasis is on its role in shear localization.The remaining equations specifying the entire description of the model are listed in the Appendix A .Included is the specification of the widely used technique [13]that accelerates damage from f ¼f c to f ¼f f ,at which point the material element is deleted.De-tails of the numerical algorithm used to implement the constitutive model in the finite element code ABAQUS Explicit [16]are also presented in the Appendix A .3.Outline of the calibration protocolThe elastic–plastic inputs into the extended Gurson Model are the Young’s modulus,E ,the Poisson’s ratio,m ,and the intrinsic stress–strain response of the damage-free material (f 0¼0).The two damage-related input parameters are theinitial Fig.1.Optical micrograph of polished and etched cross-section through DH36steel plate,showing a microstructure of ferrite (light)and pearlite (dark).494Z.Xue et al./Engineering Fracture Mechanics 77(2010)492–509effective void volume fraction,f0,and the shear damage coefficient,k x.Additionally,because the constitutive model contains no material length scale,the size of thefinite element mesh,D,is calibrated through crack growth predictions,employing well-established procedures[4,7].This paper addresses the general task of calibrating the three fracture-related parameters:f0,k x and D.The procedures are demonstrated through experiments and analyses of DH36steel(Fig.1):a high strength alloy commonly used in ship con-struction.Following extensive prior work on calibration procedures for the standard Gurson model(e.g.,[4,7]),the present study employs data from a mode I fracture test and a round bar tensile test to identify intrinsic uniaxial stress–strain behav-ior,f0and D.Additionally,a shear-off test is added to the suite of tests to determine the shear damage coefficient,k x.The paper is organized following closely the steps in the calibration protocol:Section4:Determination of the intrinsic stress–strain response of the undamaged material from round bar tensile tests and establishing that f0,k x and D have little influence on the plastic response until neck development is quite advanced.Section5:Determination of f0and D from compact tension mode I fracture tests and establishing that k x has little influ-ence on crack growth prediction when the crack is planar.Section6:Determination of k x using data from shear-off tests and the previously determined f0and D.Section7:Discussion of the applicability of the calibrated constitutive model to the cup-cone failure mode as one illus-tration and the ductility of notched round bars as another.Possible variations in the identification protocol for other materials are also discussed.The three calibration tests were conducted under quasi-static loading,while all simulations were carried out using the dynamic code ABAQUS Explicit.In order to minimize inertial effects and efficiently simulate the quasi-static tests in the ex-plicit code,a preliminary series of calculations with differentfixed applied loading rates was performed for each test con-figuration.At some loading rate,as the rates decrease,the simulations converge to a quasi-static limit.That loading ratewas then employed in all subsequent calculations.Material strain rate dependence is ignored in the presentcomputations.Fig.2.Tensile specimen geometry andfinite element mesh.Z.Xue et al./Engineering Fracture Mechanics77(2010)492–5094954.Intrinsic plastic response of the undamaged materialThe plastic response of the undamaged material (f 0¼0)was obtained from quasi-static uniaxial tensile tests on round bars coupled with elastic–plastic finite element computations.The test geometry and finite element mesh are shown in Fig.2.The nominal axial strain e N was measured using a non-contacting laser extensometer over a central 12.7mm length within the gauge section.Prior to necking,the true (logarithmic)strain is given by e T ¼ln ð1þe N Þand the true stress by r T ¼r N ð1þe N Þ,where r N is the nominal stress (load/initial area).To ascertain the true response in the post-necking regime,computations were performed using an assumed form of the stress–strain relation (detailed below)and matching the pre-dicted nominal stress–strain curves with those obtained experimentally.To accurately capture strain localization,a finite strain formulation of elasto-plastic theory was employed in the finite element model.Four-node axisymmetric elements 0 0.1 0.2 0.3 0.4 0.5900800700600500400300200100N=0.200.1850.16Experimental True strain, εT0 0.1 0.2 0.3 0.47006005004003002001000N=0.200.1850.16Experimental Nominal strain, εNεσT peak T peak ,()of the true tensile stress–strain curve beyond the onset of necking and (b)the corresponding element analysis.Error bars represent the full range of experimental measurements from six tests.extensometer over a 12.7mm gauge length near the specimen center.The nominal strain,defined as consistently employed in both the experiments and the finite element calculations.The 496Z.Xue et al./Engineering Fracture Mechanics 77(2010)492–509with reduced Gaussian integration (CAX4R in ABAQUS/Explicit [16])were used.The model was based on an axisymmetric mesh comprised of square section elements with size,D =50l m,providing more than 30elements across the gauge radius.The element size was selected to be consistent with the value emerging from the calibration of the mode I fracture data,pre-sented in the next section.Nevertheless,since the selected element size is already very much smaller than the macroscopic specimen dimensions and hence the strains are adequately resolved,further reductions in element size would have essen-tially no effect on the intrinsic (damage-free)stress–strain response.Additional computations were performed to demon-strate that f 0and k x do not affect the identification of the true stress–strain curve even up to strains approaching that for rupture.The average true stress–strain curve from five tensile tests is plotted in Fig.3a.This curve was subsequently used to char-acterize the stress–strain response for stresses below that corresponding to the load maximum,denoted r peakT.To extrapolate beyond r peak T ,a true stress–strain curve of the form r T ¼r peak T ðe T =e peak TÞN was assumed.A preliminary estimate of the strain hardening exponent N was obtained by a least squares fit of the small strain data.A series of finite element computations was then performed to ascertain the full nominal tensile stress–strain curve,using a range of values of N ,guided by the pre-ceding curve fitting.As shown in Fig.3b,the results for N ¼0:185(and f 0¼0)accurately replicate the experimental mea-surements up to the onset of rupture (at a nominal strain of e N ¼0:32).In summary,the true stress–strain curve used tocharacterize the damage-free material (f 0¼0)is given by the experimental curve below r peakT and the power law extrapo-lation at stresses above r peak T .For e N <0:3,void growth has almost no effect on the tensile behavior of DH36.This result is demonstrated in Fig.4by comparing the experimental data with finite element computations based on a hardening exponent N ¼0:185and several representative initial void volume fractions (including the Mises limit,wherein f 0¼0).Other than f 0,k x and D ,the basic parameters characterizing the constitutive model that are used in all simulations in this paper are:E ¼210MPa ;m ¼0:3;N ¼0:185;q 1¼1:5;q 2¼1;q 3¼2:25;f c ¼0:15and f f ¼0:25ð9ÞThe comparisons show that the effects of void growth,manifested in a divergence in the stress–strain response from that of a Mises material,are important only very near the point of final rupture for the DH36tensile specimen.Their effect is to accelerate the softening of the material such that the load drops more rapidly than that predicted for the damage-free mate-rial.Further details of the failure process in the neck,including formation of a cup-cone fracture surface,are presented in Section 7.5.Determination of f 0and D from compact tension testCompact tension tests were performed on specimens with the geometry shown in Fig.5a.Crack mouth opening displace-ment was measured using a non-contacting extensometer and a pair of fiducial tapes mounted on the specimen edge,sep-arated by a distance of 14mm.Optical images of the broad sample surface were periodically recorded.The experimental 0 0.1 0.2 0.3 0.47006005004003002001000f o = 0.0010.0020.003Experimental Nominal strain, εNf o =0(Mises)k ω = 0fraction f o on the computed nominal tensile stress–strain response.Over the pertinent range of experimental measurements up to the onset of fracture.Z.Xue et al./Engineering Fracture Mechanics 77(2010)492–509497measurements and observations are summarized in Figs.6and 7.Significant nonlinearity due to plasticity is evident in both the load–displacement response and in the optical images at displacements above 0.5mm.Following an initial rising por-tion,the load–displacement curve reaches a maximum,at a displacement of about 3–4mm.This point corresponds to the emergence of a crack on the external surface of the sample (Fig.7d–f ).Further growth both at the surface and in the interior occurs under decreasing load.The corresponding finite element model is shown in Fig.5b.In the present analysis,deformations are restricted to be symmetric with respect to the mid-plane such that a symmetry boundary condition is applied to the mid-plane.Conse-quently,the region meshed is only one half of the full specimen.Eight-node brick elements with reduced Gaussian integra-tion (C3D8R in ABAQUS/Explicit [16])were used.Iterations on element size and meshing details were made prior to arriving at the mesh used to carry out the final analysis.The smallest elements at the mid-plane in the vicinity of the crack tip have dimensions 30Â30Â50l m with 50l m in the through-thickness direction.Near the surface of the specimen and near the tip the element dimensions are 30Â30Â80l m.Approximately 100elements extend from the mid-plane to the surface in the vicinity of the crack tip.The 30l m in-plane mesh at the tip allows accurate resolution of the initial tip notch.Further away from the notch tip in the region of crack propagation,the in-plane dimensions of the mesh are approximately 50Â50l m.Relatively small differences in results were found from a series of computations with different meshes with ele-ment dimensions in the range from 30l m to 50l m.The mesh in Fig.5b is regarded as having a nominal (characteristic)size D =50l m.In order to improve computational efficiency,only the material in the region of crack propagation,whichstartsFig.5.(a)Compact tension test geometry employed in the experimental study and (b)corresponding finite element model.Specimen thickness is 12.5mm.Crack mouth opening displacements were measured using a non-contacting extensometer and a pair of fiducial tapes mounted on the specimen edge,separated by a distance of 14mm.The same definition was used in the subsequent finite element calculations.498Z.Xue et al./Engineering Fracture Mechanics 77(2010)492–509Z.Xue et al./Engineering Fracture Mechanics77(2010)492–509499from the notch tip to the left edge of the specimen and has width of7mm,was modeled using the extended Gurson model. Outside this region,the specimen was modeled using von Mises plasticity(i.e.,f0¼0and k x¼0).Load–displacement predictions for four values of f0(including f0¼0)and k x¼2are compared with the experimental results in Fig.6.Over the range plotted,the load of the damage-free specimen increases monotonically with displacementbecause there is no damage-induced softening or crack growth.In contrast,the prediction for f 0¼0:001follows the exper-imental curve closely for displacements as large as 5mm.Furthermore,it predicts that cracking initiates at the center of the notch front,at a displacement of about 1mm.Thereafter,the crack grows deeper into the specimen and spreads laterally from the center (Fig.7).Upon reaching the free surface,at a displacement of 3.6mm,the load reaches a maximum and a load fall-off ensues.These results agree well with the experimental measurements.The predictions for the two larger values of f 0clearly over-predict the effect of damage and cracking at displacements below 5mm.They are particularly deficient in predicting the displacement at the load maximum.At displacements above 5mm,the experimental data fall below the numerical predictions for all three values of f 0.This discrepancy arises for two reasons.The symmetry imposed in the simulation precludes the transition to slant fractures that usually develop as the crack advances and the crack in the test is likely to have departed from the imposed symmetry.In addition,element deletion was used to mimic the crack propagation such that the element is deleted when f ¼f f .As the crack advances,it encounters larger elements in the mesh and these dissipate more energy prior to failure than the cali-brated elements with D =50l m.It is indeed observed from Fig.8for the case of the crack month opening displacement reaching 8mm that some of the deleted elements are much larger than D =50l m.It remains for the future to verify that predictions based on the present choices of f 0and D can replicate the present experimental results for larger displacements using a computational model with no symmetry restrictions,as well as a uniform mesh with the same calibrated element size throughout the region of crack propagation.Unfortunately,this would result in a significant increase in computational size that would not be feasible for the calibration procedure.3Although the results in Fig.6b were computed with k x ¼2,the shear damage coefficient has essentially no effect on these predictions.To illustrate this,results for f 0¼0:001computed with k x =2,2.5and 3are plotted in Fig.6a.The response under-goes only very slight softening with increasing k x but remains well within the range of the experimental data.The weak dependence on k x is consistent with the fact that mode I cracking occurs over the range of load–displacement data used for thefitting.Fig.7.Images of broad face of compact tension specimen with increasing crack mouth opening displacements.Arrows in the right column indicate the emerging near-surface crack.3More than ten days were required for each calculation based on the current mesh using a personal computer with memory requirements up to 1GB.The trade-off between efficiency and accuracy suggests that the present calibration strategy is a reasonable compromise.500Z.Xue et al./Engineering Fracture Mechanics 77(2010)492–509In summary,based on the agreement between prediction and experiment for displacements below5mm,the choicesf0¼0:001with D%50l m are made for DH36.6.Determination of k x from a shear-off testThefixture in Fig.9was designed to create a controlled test in which shear localization gives way to mode II fracture[17].The corresponding load–displacement curve is used to infer the shear damage coefficient,k x.In the test,a plate specimen(3mm thick)is clamped between two thick steel platens,each with a through-hole of diameter19.2mm.Cylindrical steelplungers,19.05mm in diameter,are inserted into each of the two holes,leaving a narrow(0.075mm)radial gap between theplunger surface and the hole.An additional pair of plungers with slightly reduced diameter(to accommodate Teflon bear-ings)is then inserted into the holes.The four plungers and the test specimen are then clamped together with a single boltpassing through open holes in each of three of the plungers and the test specimen and a threaded hole in the last plunger,asshown in Fig.9.With one side of the assembly placed on a stiff supporting base,the plunger on the opposite side is loadaxially in compression.The movement of the plungers induces shear deformation within a narrow cylindrical ring in thespecimen.Failure starts as shear localizations near the upper and lower surfaces of the plate which subsequently developinto mode II cracks as the deformation progresses into the plate.The experimental measurements are summarized in Fig.10.The coordinate axes are the nominal applied shear stress, s P=ð2p RHÞ(R being the plunger radius and H the plate thickness)and the normalized displacement,d=H.The resulting curves exhibit features reminiscent of those obtained in tension tests.That is,the initial linear region gives way to plasticityat a shear stress of r O=2%240MPa(r O being the tensile yield stress,obtained from Fig.3).Following a period of strain hard-ening,the load reaches a peak,at a displacement of d=H%0.3–0.4,and subsequently diminishes with increasing displace-ment.Scanning electron micrographs of a cross-section through a test specimen that had been interrupted followingloading to a displacement d=H%0.5are presented in Fig.11.They reveal a diffuse damage zone within the region of intenseshear as well as well-defined shear cracks emanating from the specimen surface in the vicinity of the plunger periphery.A detail of thefinite element mesh is depicted in the inset of Fig.9a.Based on the prior calibrations,computations ofshear-off employ an initial void fraction f0¼0:001and element size D=50l m in the region of shear localizationandFig.8.Evolution of plastic strain and crack growth fromfinite element calculations of the compact tension test.Z.Xue et al./Engineering Fracture Mechanics77(2010)492–509501。
基于陀螺和星敏感器的卫星姿态确定算法_边志强
( 3)
2
陀螺的测量模型
陀螺模型中考虑陀螺的随机漂移 d 、 常值漂移 b
T gi 2
上式中, 按照四元数相乘的定义, 很容易得到下式 ^ 1 bo 1 ^ bo $ q ª Xbo X ª $ qbo = 2 2
和测量噪声 ng , 有 E{ ngi ( t) n ( S ) } = Rg D ( t- S) ( i= x , y , z ) , Rg 为 测量噪声 均方差阵 , D ( t) 是方差 强 度。模型如下
[1 - 2]
Xg = X+ d + b + ng
( 1)
U [1 0
0 0] , 所以有
T
其中 , Xg 为陀螺角速度在本体系上坐标 , X 为 卫星相对惯性空间的角速度在本体系上的坐标。 陀螺随机漂移通常被描述为一阶马尔 柯夫过 程
[ 8]
1 $ qbo ª $ Xbo = 1 $ Xbo + $( | $ qbo | | $ Xbo | ) 2 2 1 Abo ( $ qbo ) = - 2 $q 3 2 $q 2 2 $q 3 1 2 $q 1 - 2 $q 2 2 $q 1 1 ( 5)
- 0 1 5I 3@ 3 - DS 03@ 3
- 0 1 5I 3@ 3 03@ 3 03@ 3
9@ 9
相同, 测量精度为 v( 3R ) , 则可以得到 Rk = v2 I3@ 3 。ຫໍສະໝຸດ 6姿态确定算法过程
1) 在没有测量值时, 进行预报计算[ 2- 3, 6, 9] 在 k - 1 时刻 , 即使在没有星敏感器的测量输出
= I 3@ 3 - 2[ $q @ ]
将式( 4) 、 ( 5) 代入式( 3) 中, 忽略 ( 5) 中的二阶小 量, 有 $Û q0 = 0 $Û q = $q @ ^ Xbo + 1 $Xbo 2 =- [^ Xbo @ ] $q + 1 $Xbo 2 根 据 Xbo = X - Abo ( qbo ) Xoi , ^ Xbo = X ^ ^ Abo ( qbo ) Xoi , 真实姿态角速度 X 和陀螺测量角速度 X 之差为: $X= X- ^ ^ X= - $b- $d - ng , 则有 $Xbo = Xbo - ^ Xbo = $X+ 2[ $q @ ] Abo ( qbo ) Xoi 。 结合以上各式 , 可得关于 $q 的线性状态方程 $Û q=- [^ X @ ] $q - 1 $b - 1 $d - 1 ng 2 2 2 $Û q0 = 0 ( 7) ( 6)
双吸式叶轮内流三维数值模拟及性能预测
第22卷第1期2006年1月农业工程学报T r ansactions of the CSA E V ol.22 N o.1Jan. 2006双吸式叶轮内流三维数值模拟及性能预测赵斌娟1,袁寿其2,李 红2,谈明高2(1.江苏大学能源与动力工程学院,镇江212013; 2.江苏大学流体工程技术中心,镇江212013)摘 要:以时均化的N -S 方程和考虑旋转与曲率影响的修正的k-湍流模型为基础,在贴体坐标系中运用SIM P LEC 算法,对双吸式离心叶轮内流进行三维湍流数值模拟。
计算得到叶轮内的速度、压力场分布,预估了扬程、水力效率并与试验值进行对比。
计算结果表明,在双吸式叶轮中,从叶轮进口到出口压力逐渐增加;在叶片区域,处于前盖板和对称面之间的中间截面上,叶片工作面附近的压力明显大于背面附近的压力,且从对称面到前盖板各中间截面上的压力梯度显著增加;流动关于对称面对称,在对称面上不存在轴向速度;设计工况下叶轮出口断面上压力分布明显比其它工况均匀,因此水力效率最高。
关键词:双吸式叶轮;三维湍流模拟;性能预测中图分类号:T H311 文献标识码:A 文章编号:1002-6819(2006)01-0093-04赵斌娟,袁寿其,李 红,等.双吸式叶轮内流三维数值模拟及性能预测[J ].农业工程学报,2006,22(1):93-96.Zhao Binjuan,Yuan Sho uqi,Li Ho ng ,et al.3D numerical simulat ion and per for mance pr edict ion of do uble-suctio nimpeller [J ].T r ansactions of t he CSA E ,2006,22(1):93-96.(in Chinese with English abst ract )收稿日期:2005-03-17 修订日期:2005-05-24基金项目:江苏省自然科学基金项目(BK2004406)作者简介:赵斌娟(1977-),女,江苏镇江人,博士生,研究方向为流体机械内部流动数值模拟及测试技术。
自适应蒙特卡洛法评定全站仪测距不确定度
自适应蒙特卡洛法评定全站仪测距不确定度仇跃鑫1,2,朱进1,2,王瑛辉1,2*(1.浙江省计量科学研究院,浙江杭州 310018;2.浙江省数字精密测量技术研究重点实验室,浙江杭州310018)摘要:全站仪测距精度的校准需要在标准基线场上进行,由于野外环境不可控和气象条件波动剧烈,因此判断全站仪的测量结果的可靠程度具有重要意义。
为了解决全站仪测距不确定度评定模型的非线性和输入量强相关等问题,本文首先采用了自适应蒙特卡洛法进行不确定度评定,然后与GUM的不确定度评定结果进行对比,当测距距离为1 176 m时,自适应蒙特卡洛法评定的不确定度结果为2.2 mm,GUM为2.6 mm,结果显示两种不确定度评定方法的测量结果均在合理预期之内,且自适应蒙特卡洛法评定的不确定度置信区间更窄。
自适应蒙特卡洛法结合了大量数据样本和自适应优化仿真次数的优势,不仅对全站仪测距过程中的各项误差源引入的不确定度分量评估更为全面,而且在保证了全站仪测距不确定度评定结果准确的同时,相比于蒙特卡洛法节约了70%的样本数量。
关键词:计量学;自适应蒙特卡洛法;全站仪;测量不确定度中图分类号:TB921;TH711 文献标志码:A 文章编号:1674-5795(2023)05-0104-08Evaluation of uncertainty of distance measurement by total station usingadaptive Monte Carlo methodQIU Yuexin1,2, ZHU Jin1,2, WANG Yinghui1,2*(1.Zhejiang Institute of Metrology, Hangzhou 310018, China;2.Key Laboratory of Digital Precision Measurement Technology of Zhejiang Province, Hangzhou 310018, China)Abstract: The calibration of total station distance measurement accuracy needs to be carried out on a standard baseline field, and it is of great significance to judge the reliability of the measurement results of the total station due to the uncontrollable field environment and the drastic fluctuation of meteorological conditions. In order to solve the problems of nonlinearity and strong correlation of inputs of the total station distance measurement uncertainty evaluation model, this paper firstly adopts the adaptive Monte Carlo method to evaluate the uncertainty, and then compares the uncertainty evaluation results with those of the GUM. When the ranging distance is 1 176 m, the un⁃certainty evaluation results of the adaptive Monte Carlo method is 2.2 mm, and the GUM is 2.6 mm. The results show that the measurement results of both uncertainty assessment methods are within reasonable expectations, and the uncertainty confidence interval of the adaptive Monte Carlo method is narrower. The adaptive Monte Carlo method combines the advantages of a large number of data samples and adaptive optimization of the simulation doi:10.11823/j.issn.1674-5795.2023.05.15收稿日期:2023-04-01;修回日期:2023-05-12基金项目:2022年度浙江省科技厅“尖兵”“领雁”研发攻关计划项目(2022C01139)引用格式:仇跃鑫,朱进,王瑛辉.自适应蒙特卡洛法评定全站仪测距不确定度[J].计测技术,2023,43(5):104-111.Citation:QIU Y X,ZHU J,WANG Y H.Evaluation of uncertainty of distance measurement by total station using adaptive Monte Carlo method[J].Metrology & Measurement Technology,2023,43(5):104-111.times, which not only provides a more comprehensive assessment of the uncertainty components introduced by vari⁃ous error sources in the process of total station distance measurement, but also saves 70% of samples compared with the Monte Carlo method, while guaranteeing the accuracy of the uncertainty assessment results of the total station distance measurement.Key words: metrology; adaptive Monte Carlo method; total station; measurement uncertainty0 引言全站仪被广泛应用于精密测量、机械制造和大地测量领域,本质是由一个经纬仪和一个电子测距仪共同组成,这二者的精度直接决定了全站仪的精度。
胜利稠油渗流机理研究与应用
胜利稠油渗流机理研究与应用X刘冬青,王善堂,白艳丽,邹 斌,于田田(中国石化胜利油田分公司采油工艺研究院,山东东营 257000) 摘 要:稠油渗流机理的研究对稠油开采工艺优化具有非常重要的指导意义,本文主要从稠油流变特性、地下渗流特征、相渗曲线三个方面开展了胜利油田稠油渗流机理的研究。
温度对稠油的流变性具有决定性影响,当其高于一定值时,稠油均可转变成牛顿流体。
不同稠油流型转变温度差异很大。
稠油在地下渗流时存在初始压力梯度,初始压力梯度不但与稠油本身的性质有关,而且与油藏孔隙度及渗透率有关,降低初始压力梯度,显著改善热采开发效果。
相渗曲线是两相渗流时渗流规律的体现,开展了油-热水、油-蒸汽相渗曲线的研究及加入化学剂后对相渗曲线的影响,并且建立了相渗曲线的数学方程。
通过稠油渗流机理的研究,为稠油的开采工艺优化提供了理论基础。
关键词:胜利稠油;流变性;渗流特征;相渗曲线;热采 中图分类号:T E345 文献标识码:A 文章编号:1006—7981(2012)02—0003—04 稠油粘度高,渗流阻力大,导致开发难度大。
稠油渗流特征普遍不符合达西定律,因此在稠油的开采过程中,若能建立相应的稠油渗流数学模型,就能更加准确地描述采油全过程中采油系统的动态特性,实现系统参数的优化,建立合理工作制度、增产降耗、提高开发水平。
1 稠油流变特性研究1.1 原理及方法利用旋转粘温流变仪对原油的屈服应力和流变性进行测定。
其工作原理是:样品的粘度正比于剪切应力,也就是在确定的转速或剪切速率下的流动阻力。
流变曲线的测定方法是在一定的温度下,采用不同的剪切速率,测定流体剪切应力与剪切速率的关系曲线。
其公式为:L =S /C式中:L -流体的粘度,Pa s ;S -剪切应力,Pa ;C -剪切速率,s -1。
[9] 郭永存,卢德唐,曾清红,等.有启动压力梯度渗流的数学模型[J ].中国科学技术大学学报,2005,35(4):492~498.[10] 韩大匡.油藏数值模拟基础[M ].北京:石油工业出版社,2003.[11] 吕成远,王健,孙志刚.低渗透砂岩油藏渗流启动压力梯度试验研究[J ].石油勘探与开发,2002,29(2):86~89.Study on Numer ical Simulation of the NonlinearFlow in Low Per meability Reser voir CH AN G T ielong ZH AN G Yun(Research Institute of Petroleum Exploration&Production,SINOPEC,Beijing 100083,China)Abstr act:Low permeability reservoirs exists start -up pressure gradient.And Darcy law has been unable to accurately describe the reservoir fluid flow.The mathematical characterization of the start-up pr essure gradient method was proposed in this paper in Low per meability reservoir s,and nonlinear flow model and the cor responding mathematical model and numerical model was built.T hen nonlinear flow numerical simulation software based on the existing numer ical simulation software has been developed.At last it was applied to a small oil field model.Calculations show that the initial simulation results are consistent with the actual data and verify the cor rectness of the method.Key words:Low permeability r eser voir;Nonlinear flow;Start -up pressure gradient;Reser voir numerical simulation3 2012年第2期 内蒙古石油化工*收稿日期作者简介刘冬青(—),男,中石化胜利油田分公司采油工艺研究院工程师,年获得长江大学油气田开发工程硕士学位,主要从事稠油热采开发实验和工艺技术研究。
秦岭终南山特长隧道竖井衬砌的数值计算
文章编号:0451-0712(2007)12-0214-04 中图分类号:U 453.4 文献标识码:B 秦岭终南山特长隧道竖井衬砌的数值计算史彦文,韩常领,董 溥(中交第一公路勘察设计研究院 西安市 710075)摘 要:选取建设规模居世界第一的秦岭终南山隧道1号通风竖井为研究对象,根据设计提供的支护参数,采用M IDA S/G T S 真实模拟了竖井施工的全过程。
通过对竖井初期支护、竖井二次衬砌的受力状态分析,评价了衬砌结构的安全性。
结果表明:对于竖井二次衬砌,在距离送风道交接口边缘约5m 区域内,是高应力聚集区,是需要设计中重点加强的关键部位,普通素混凝土不能保证结构的安全,需要采取增配钢筋进行补强。
竖井二次衬砌的其余地段和送风道排风道二次衬砌,设计时可以作为安全储备,仅需要按照构造要求进行设计。
关键词:隧道工程;竖井;数值计算;二次衬砌1 竖井设计概况秦岭终南山公路隧道是世界上最长的双洞公路隧道,隧道全长18.02km 。
隧道位于包(头)北(海)线和银(川)武(汉)线的共线段上,按照上下行双洞双车道标准设计,设计车速80km /h,隧道净宽10.50m ,净高5.0m 。
隧道通风采用竖井分段纵向式通风方案,共设3座竖井,是世界口径最大、深度最深的竖井通风工程。
竖井最大埋深661m,最大直径为11.5m ,通风竖井通过送风道、排风道以及隔风板等实现通风换气。
隧道竖井与通风洞室的交叉口段的结构见图1所示。
单位:cm图1 竖井通风洞室结构示意 秦岭终南山隧道竖井的工程规模巨大,通风洞室彼此交错,空间跨度大,受力复杂,各洞室的施工彼此干扰大。
面对如此复杂的竖井,本行业还没有成熟的规定、规范,国内也无工程实例,目前国内尚无对这部分结构的数值模拟计算,在国外这方面的分析计算也不多见。
为此,本文以终南山隧道1号竖井为分析对象,重点对1号竖井与各洞室交叉口处的衬砌受力状态进行分析,重现施工过程中衬砌的真实受力状况,以此对各设计参数进行复核。
DD2004-01 1∶250000区域水文地质调查技术要求
DD2004-01 1∶250000区域水文地质调查技术要求DD 2004—011∶250000区域水文地质调查技术要求Technical Requirement of 1∶250000 Regional Hydrogeologic Survey1 主题内容与适用范畴1.1 本《技术要求》规定了1∶250000区域水文地质调查的性质、目的、任务以及调查内容、技术方法、工作程度与精度、资料整理、图件编制、报告编写与提交成果的要求及方法。
1.2 本《技术要求》是区域水文地质调查工作程序、设计编写、调查实施、成果编制、质量监控、成果提交、验收与评审的要紧依据。
1.3 本《技术要求》适用于1∶250000区域水文地质调查。
开展其它比例尺的区域水文地质调查也可参照。
2 引用标准GB 5749—85 生活饮用水水质标准GB/T 13727—92 天然矿泉水地质勘探规范GB 10202—88 海岸带综合地质勘查规范GB/T 14158—93 区域水文地质工程地质环境地质综合勘查规范(1∶50000)GB/T 14175—93 水文地质术语GB/T 14497—93 地下水资源治理模型文件要求GB/T 14848—93 地下水质量标准GB 15218—94 地下水资源分类分级标准GB 50027—2001 供水水文地质勘察规范DZ 44—86 城镇及工矿供水水文地质勘察规范DZ 55—87 都市环境水文地质工作规范DZ/T 0124—94 水文地质钻孔数据文件格式DZ/T 0128—94 地下水资源数据文件格式DZ/T 0133—94 地下水动态监测规程DZ/T 0148—94 水文地质钻探规程DZ/T 0151—95 区域地质调查遥感技术规定(1∶50000)DZ/T 0181—97 水文测井工作规范3 术语与定义3.1 区域水文地质调查regional hydrogeologic survey为调查区域地下水类型、埋藏、分布、形成条件、物理及化学性质、运动规律,区域地下水资源及其开发利用与爱护、区域环境地质咨询题所进行的综合性水文地质工作。
线性与非线性强度的坝坡稳定分析_荆富荣
系数一般还是一致的, 这是因为下游的水位一致, 且 上游水位的变化主要对上游坝坡产生作用, 对于下 游坝坡土料的性质影响不大。
线性强度计算的稳定安全系数明显小于非线性 强度计算结果, 这种趋势应该说是对的。土石坝新 规范条文说明中, 黄委会设计院所作的比较分析也 是如此。对该坝, 非线性强度计算的安全系数比线 性强度计算的安全系数大 2% ~ 20% 。
表 3 计算安全系数
工况 位置
方法
线性强度的 安全系数
非线性强度 的安全系数
(
FsN
FsL) / FsL
FsL
FsN
/%
竣 工
上游坡 瑞典法 毕肖普法
1. 858 2. 002
1. 893 2. 068
1. 9 3. 3
期 下游坡 瑞典法
1. 792
1. 831
2. 2
毕肖普法 1. 822
1. 910
c 土体粘聚力;
土体内摩擦角。
毕肖普简化法公式为:
Wi t an + cb
Fs =
mi
( 3)
Wi s in i
其中,
mi=
cos i +
sin i tan Fs
( 4)
式中: b 土条宽度。
计算所用程序为河海大学岩土工程研究所研制
的 SLP 土坡稳定分析程序。它可以作总应力法计算,
也可以作有效应力法计算; 可以用于各种复杂的土层
Numerical simulation of wind s influence on water quality of reservoir with net tank fish culture
LI Rong hui1, CAI De suo2
数学de一些英文名称
Applied Partial Differential Equations Computer Graphics Computer Aided Geometric Design Selections from System Modeling Biology Mathematics Mathematical Finance Multimedia Techniques Applied Geometry Principle of Computer Network Dynamical Systems The Theory of Interest Actuarial Mathematics Coding Theory Numerical Analysis(Computing Method) Nonlinear Programming Combinatorial Optimization Optimal Control Theory Fractal Geometry Functions of Several Complex Variables Theory of Integral Equations and Its Applications Elementary Number Theory Stochastic Processes Applied software of Mathematics and Practice Introduction to Actuarial Science Advanced course on Mathematical Physics Mathematics of Demography Financial Economics Combinational Analysis Life Insurance Fourier Analysis Introduction to Insurance Introduction to Insurance and Actuarial Science Nonlife Actuarial Mathematics Complex Analysis Introduction to Control Theory Life Actuarial Mathematics Data Structures Statistics Digital Signal Processing Linear Programming Basic Information Theory Element of Database System
中英文力学对准
一般力学类:分析力学 analytical mechanics拉格朗日乘子 Lagrange multiplier拉格朗日[量] Lagrangian拉格朗日括号 Lagrange bracket循环坐标 cyclic coordinate循环积分 cyclic integral哈密顿[量] Hamiltonian哈密顿函数 Hamiltonian function正则方程 canonical equation正则摄动 canonical perturbation正则变换 canonical transformation正则变量 canonical variable哈密顿原理 Hamilton principle作用量积分 action integral哈密顿-雅可比方程 Hamilton-Jacobi equation作用--角度变量 action-angle variables阿佩尔方程 Appell equation劳斯方程 Routh equation拉格朗日函数 Lagrangian function诺特定理 Noether theorem泊松括号 poisson bracket边界积分法 boundary integral method并矢 dyad运动稳定性 stability of motion轨道稳定性 orbital stability李雅普诺夫函数 Lyapunov function渐近稳定性 asymptotic stability结构稳定性 structural stability久期不稳定性 secular instability弗洛凯定理 Floquet theorem倾覆力矩 capsizing moment自由振动 free vibration固有振动 natural vibration暂态 transient state环境振动 ambient vibration反共振 anti-resonance衰减 attenuation库仑阻尼 Coulomb damping同相分量 in-phase component非同相分量 out-of -phase component超调量 overshoot 参量[激励]振动 parametric vibration模糊振动 fuzzy vibration临界转速 critical speed of rotation阻尼器 damper半峰宽度 half-peak width集总参量系统 lumped parameter system 相平面法 phase plane method相轨迹 phase trajectory等倾线法 isocline method跳跃现象 jump phenomenon负阻尼 negative damping达芬方程 Duffing equation希尔方程 Hill equationKBM方法 KBM method, Krylov-Bogoliu- bov-Mitropol'skii method马蒂厄方程 Mathieu equation平均法 averaging method组合音调 combination tone解谐 detuning耗散函数 dissipative function硬激励 hard excitation硬弹簧 hard spring, hardening spring谐波平衡法harmonic balance method久期项 secular term自激振动 self-excited vibration分界线 separatrix亚谐波 subharmonic软弹簧 soft spring ,softening spring软激励 soft excitation邓克利公式 Dunkerley formula瑞利定理 Rayleigh theorem分布参量系统 distributed parameter system优势频率 dominant frequency模态分析 modal analysis固有模态natural mode of vibration同步 synchronization超谐波 ultraharmonic范德波尔方程 van der pol equation频谱 frequency spectrum基频 fundamental frequencyWKB方法 WKB methodWKB方法Wentzel-Kramers-Brillouin method缓冲器 buffer风激振动 aeolian vibration嗡鸣 buzz倒谱cepstrum颤动 chatter蛇行 hunting阻抗匹配 impedance matching机械导纳 mechanical admittance机械效率 mechanical efficiency机械阻抗 mechanical impedance随机振动 stochastic vibration, random vibration隔振 vibration isolation减振 vibration reduction应力过冲 stress overshoot喘振surge摆振shimmy起伏运动 phugoid motion起伏振荡 phugoid oscillation驰振 galloping陀螺动力学 gyrodynamics陀螺摆 gyropendulum陀螺平台 gyroplatform陀螺力矩 gyroscoopic torque陀螺稳定器 gyrostabilizer陀螺体 gyrostat惯性导航 inertial guidance 姿态角 attitude angle方位角 azimuthal angle舒勒周期 Schuler period机器人动力学 robot dynamics多体系统 multibody system多刚体系统 multi-rigid-body system机动性 maneuverability凯恩方法Kane method转子[系统]动力学 rotor dynamics转子[一支承一基础]系统 rotor-support- foundation system静平衡 static balancing动平衡 dynamic balancing静不平衡 static unbalance动不平衡 dynamic unbalance现场平衡 field balancing不平衡 unbalance不平衡量 unbalance互耦力 cross force挠性转子 flexible rotor分频进动 fractional frequency precession半频进动half frequency precession油膜振荡 oil whip转子临界转速 rotor critical speed自动定心 self-alignment亚临界转速 subcritical speed涡动 whirl固体力学类:弹性力学 elasticity弹性理论 theory of elasticity均匀应力状态 homogeneous state of stress 应力不变量 stress invariant应变不变量 strain invariant应变椭球 strain ellipsoid均匀应变状态 homogeneous state of strain应变协调方程 equation of strain compatibility拉梅常量 Lame constants各向同性弹性 isotropic elasticity旋转圆盘 rotating circular disk 楔wedge开尔文问题 Kelvin problem布西内斯克问题 Boussinesq problem艾里应力函数 Airy stress function克罗索夫--穆斯赫利什维利法 Kolosoff- Muskhelishvili method基尔霍夫假设 Kirchhoff hypothesis板 Plate矩形板 Rectangular plate圆板 Circular plate环板 Annular plate波纹板 Corrugated plate加劲板 Stiffened plate,reinforcedPlate中厚板 Plate of moderate thickness弯[曲]应力函数 Stress function of bending 壳Shell扁壳 Shallow shell旋转壳 Revolutionary shell球壳 Spherical shell[圆]柱壳 Cylindrical shell锥壳Conical shell环壳 Toroidal shell封闭壳 Closed shell波纹壳 Corrugated shell扭[转]应力函数 Stress function of torsion 翘曲函数 Warping function半逆解法 semi-inverse method瑞利--里茨法 Rayleigh-Ritz method松弛法 Relaxation method莱维法 Levy method松弛 Relaxation量纲分析 Dimensional analysis自相似[性] self-similarity影响面 Influence surface接触应力 Contact stress赫兹理论 Hertz theory协调接触 Conforming contact滑动接触 Sliding contact滚动接触 Rolling contact压入 Indentation各向异性弹性 Anisotropic elasticity颗粒材料 Granular material散体力学 Mechanics of granular media热弹性 Thermoelasticity超弹性 Hyperelasticity粘弹性 Viscoelasticity对应原理 Correspondence principle褶皱Wrinkle塑性全量理论 Total theory of plasticity滑动 Sliding微滑Microslip粗糙度 Roughness非线性弹性 Nonlinear elasticity大挠度 Large deflection突弹跳变 snap-through有限变形 Finite deformation 格林应变 Green strain阿尔曼西应变 Almansi strain弹性动力学 Dynamic elasticity运动方程 Equation of motion准静态的Quasi-static气动弹性 Aeroelasticity水弹性 Hydroelasticity颤振Flutter弹性波Elastic wave简单波Simple wave柱面波 Cylindrical wave水平剪切波 Horizontal shear wave竖直剪切波Vertical shear wave体波 body wave无旋波 Irrotational wave畸变波 Distortion wave膨胀波 Dilatation wave瑞利波 Rayleigh wave等容波 Equivoluminal wave勒夫波Love wave界面波 Interfacial wave边缘效应 edge effect塑性力学 Plasticity可成形性 Formability金属成形 Metal forming耐撞性 Crashworthiness结构抗撞毁性 Structural crashworthiness 拉拔Drawing破坏机构 Collapse mechanism回弹 Springback挤压 Extrusion冲压 Stamping穿透Perforation层裂Spalling塑性理论 Theory of plasticity安定[性]理论 Shake-down theory运动安定定理 kinematic shake-down theorem静力安定定理 Static shake-down theorem 率相关理论 rate dependent theorem载荷因子load factor加载准则 Loading criterion加载函数 Loading function加载面 Loading surface塑性加载 Plastic loading塑性加载波 Plastic loading wave简单加载 Simple loading比例加载 Proportional loading卸载 Unloading卸载波 Unloading wave冲击载荷 Impulsive load阶跃载荷step load脉冲载荷 pulse load极限载荷 limit load中性变载 nentral loading拉抻失稳 instability in tension加速度波 acceleration wave本构方程 constitutive equation完全解 complete solution名义应力 nominal stress过应力 over-stress真应力 true stress等效应力 equivalent stress流动应力 flow stress应力间断 stress discontinuity应力空间 stress space主应力空间 principal stress space静水应力状态hydrostatic state of stress对数应变 logarithmic strain工程应变 engineering strain等效应变 equivalent strain应变局部化 strain localization应变率 strain rate应变率敏感性 strain rate sensitivity应变空间 strain space有限应变 finite strain塑性应变增量 plastic strain increment 累积塑性应变 accumulated plastic strain 永久变形 permanent deformation内变量 internal variable应变软化 strain-softening理想刚塑性材料 rigid-perfectly plastic Material刚塑性材料 rigid-plastic material理想塑性材料 perfectl plastic material 材料稳定性stability of material应变偏张量deviatoric tensor of strain应力偏张量deviatori tensor of stress 应变球张量spherical tensor of strain应力球张量spherical tensor of stress路径相关性 path-dependency线性强化 linear strain-hardening应变强化 strain-hardening随动强化 kinematic hardening各向同性强化 isotropic hardening强化模量 strain-hardening modulus幂强化 power hardening塑性极限弯矩 plastic limit bending Moment塑性极限扭矩 plastic limit torque弹塑性弯曲 elastic-plastic bending弹塑性交界面 elastic-plastic interface弹塑性扭转 elastic-plastic torsion粘塑性 Viscoplasticity非弹性 Inelasticity理想弹塑性材料 elastic-perfectly plastic Material极限分析 limit analysis极限设计 limit design极限面limit surface上限定理 upper bound theorem上屈服点upper yield point下限定理 lower bound theorem下屈服点 lower yield point界限定理 bound theorem初始屈服面initial yield surface后继屈服面 subsequent yield surface屈服面[的]外凸性 convexity of yield surface截面形状因子 shape factor of cross-section 沙堆比拟 sand heap analogy屈服Yield屈服条件 yield condition屈服准则 yield criterion屈服函数 yield function屈服面 yield surface塑性势 plastic potential能量吸收装置 energy absorbing device能量耗散率 energy absorbing device塑性动力学 dynamic plasticity塑性动力屈曲 dynamic plastic buckling塑性动力响应 dynamic plastic response塑性波 plastic wave运动容许场 kinematically admissible Field静力容许场 statically admissibleField流动法则 flow rule速度间断 velocity discontinuity滑移线 slip-lines滑移线场 slip-lines field移行塑性铰 travelling plastic hinge塑性增量理论 incremental theory ofPlasticity米泽斯屈服准则 Mises yield criterion普朗特--罗伊斯关系 prandtl- Reuss relation特雷斯卡屈服准则 Tresca yield criterion洛德应力参数 Lode stress parameter莱维--米泽斯关系 Levy-Mises relation亨基应力方程 Hencky stress equation赫艾--韦斯特加德应力空间Haigh-Westergaard stress space洛德应变参数 Lode strain parameter德鲁克公设 Drucker postulate盖林格速度方程Geiringer velocity Equation结构力学 structural mechanics结构分析 structural analysis结构动力学 structural dynamics拱 Arch三铰拱 three-hinged arch抛物线拱 parabolic arch圆拱 circular arch穹顶Dome空间结构 space structure空间桁架 space truss雪载[荷] snow load风载[荷] wind load土压力 earth pressure地震载荷 earthquake loading弹簧支座 spring support支座位移 support displacement支座沉降 support settlement超静定次数 degree of indeterminacy机动分析 kinematic analysis 结点法 method of joints截面法 method of sections结点力 joint forces共轭位移 conjugate displacement影响线 influence line三弯矩方程 three-moment equation单位虚力 unit virtual force刚度系数 stiffness coefficient柔度系数 flexibility coefficient力矩分配 moment distribution力矩分配法moment distribution method力矩再分配 moment redistribution分配系数 distribution factor矩阵位移法matri displacement method单元刚度矩阵 element stiffness matrix单元应变矩阵 element strain matrix总体坐标 global coordinates贝蒂定理 Betti theorem高斯--若尔当消去法 Gauss-Jordan elimination Method屈曲模态 buckling mode复合材料力学 mechanics of composites 复合材料composite material纤维复合材料 fibrous composite单向复合材料 unidirectional composite泡沫复合材料foamed composite颗粒复合材料 particulate composite层板Laminate夹层板 sandwich panel正交层板 cross-ply laminate斜交层板 angle-ply laminate层片Ply多胞固体 cellular solid膨胀 Expansion压实Debulk劣化 Degradation脱层 Delamination脱粘 Debond纤维应力 fiber stress层应力 ply stress层应变ply strain层间应力 interlaminar stress比强度 specific strength强度折减系数 strength reduction factor强度应力比 strength -stress ratio横向剪切模量 transverse shear modulus 横观各向同性 transverse isotropy正交各向异 Orthotropy剪滞分析 shear lag analysis短纤维 chopped fiber长纤维 continuous fiber纤维方向 fiber direction纤维断裂 fiber break纤维拔脱 fiber pull-out纤维增强 fiber reinforcement致密化 Densification最小重量设计 optimum weight design网格分析法 netting analysis混合律 rule of mixture失效准则 failure criterion蔡--吴失效准则 Tsai-W u failure criterion 达格代尔模型 Dugdale model断裂力学 fracture mechanics概率断裂力学 probabilistic fracture Mechanics格里菲思理论 Griffith theory线弹性断裂力学 linear elastic fracturemechanics, LEFM弹塑性断裂力学 elastic-plastic fracture mecha-nics, EPFM断裂 Fracture脆性断裂 brittle fracture解理断裂 cleavage fracture蠕变断裂 creep fracture延性断裂 ductile fracture晶间断裂 inter-granular fracture准解理断裂 quasi-cleavage fracture穿晶断裂 trans-granular fracture裂纹Crack裂缝Flaw缺陷Defect割缝Slit微裂纹Microcrack折裂Kink椭圆裂纹 elliptical crack深埋裂纹 embedded crack[钱]币状裂纹 penny-shape crack预制裂纹 Precrack 短裂纹 short crack表面裂纹 surface crack裂纹钝化 crack blunting裂纹分叉 crack branching裂纹闭合 crack closure裂纹前缘 crack front裂纹嘴 crack mouth裂纹张开角crack opening angle,COA裂纹张开位移 crack opening displacement, COD裂纹阻力 crack resistance裂纹面 crack surface裂纹尖端 crack tip裂尖张角 crack tip opening angle,CTOA裂尖张开位移 crack tip openingdisplacement, CTOD裂尖奇异场crack tip singularity Field裂纹扩展速率 crack growth rate稳定裂纹扩展 stable crack growth定常裂纹扩展 steady crack growth亚临界裂纹扩展 subcritical crack growth 裂纹[扩展]减速 crack retardation止裂crack arrest止裂韧度 arrest toughness断裂类型 fracture mode滑开型 sliding mode张开型 opening mode撕开型 tearing mode复合型 mixed mode撕裂 Tearing撕裂模量 tearing modulus断裂准则 fracture criterionJ积分 J-integralJ阻力曲线 J-resistance curve断裂韧度 fracture toughness应力强度因子 stress intensity factorHRR场 Hutchinson-Rice-Rosengren Field守恒积分 conservation integral有效应力张量 effective stress tensor应变能密度strain energy density能量释放率 energy release rate内聚区 cohesive zone塑性区 plastic zone张拉区 stretched zone热影响区heat affected zone, HAZ延脆转变温度 brittle-ductile transitiontemperature剪切带shear band剪切唇shear lip无损检测 non-destructive inspection双边缺口试件double edge notchedspecimen, DEN specimen单边缺口试件 single edge notchedspecimen, SEN specimen三点弯曲试件 three point bendingspecimen, TPB specimen中心裂纹拉伸试件 center cracked tension specimen, CCT specimen中心裂纹板试件 center cracked panelspecimen, CCP specimen紧凑拉伸试件 compact tension specimen, CT specimen大范围屈服large scale yielding小范围攻屈服 small scale yielding韦布尔分布 Weibull distribution帕里斯公式 paris formula空穴化 Cavitation应力腐蚀 stress corrosion概率风险判定 probabilistic riskassessment, PRA损伤力学 damage mechanics损伤Damage连续介质损伤力学 continuum damage mechanics细观损伤力学 microscopic damage mechanics累积损伤 accumulated damage脆性损伤 brittle damage延性损伤 ductile damage宏观损伤 macroscopic damage细观损伤 microscopic damage微观损伤 microscopic damage损伤准则 damage criterion损伤演化方程 damage evolution equation 损伤软化 damage softening损伤强化 damage strengthening 损伤张量 damage tensor损伤阈值 damage threshold损伤变量 damage variable损伤矢量 damage vector损伤区 damage zone疲劳Fatigue低周疲劳 low cycle fatigue应力疲劳 stress fatigue随机疲劳 random fatigue蠕变疲劳 creep fatigue腐蚀疲劳 corrosion fatigue疲劳损伤 fatigue damage疲劳失效 fatigue failure疲劳断裂 fatigue fracture疲劳裂纹 fatigue crack疲劳寿命 fatigue life疲劳破坏 fatigue rupture疲劳强度 fatigue strength疲劳辉纹 fatigue striations疲劳阈值 fatigue threshold交变载荷 alternating load交变应力 alternating stress应力幅值 stress amplitude应变疲劳 strain fatigue应力循环 stress cycle应力比 stress ratio安全寿命 safe life过载效应 overloading effect循环硬化 cyclic hardening循环软化 cyclic softening环境效应 environmental effect裂纹片crack gage裂纹扩展 crack growth, crack Propagation裂纹萌生 crack initiation循环比 cycle ratio实验应力分析 experimental stressAnalysis工作[应变]片 active[strain] gage基底材料 backing material应力计stress gage零[点]飘移zero shift, zero drift应变测量 strain measurement应变计strain gage应变指示器 strain indicator应变花 strain rosette应变灵敏度 strain sensitivity机械式应变仪 mechanical strain gage 直角应变花 rectangular rosette引伸仪 Extensometer应变遥测 telemetering of strain横向灵敏系数 transverse gage factor 横向灵敏度 transverse sensitivity焊接式应变计 weldable strain gage 平衡电桥 balanced bridge粘贴式应变计 bonded strain gage粘贴箔式应变计bonded foiled gage粘贴丝式应变计 bonded wire gage 桥路平衡 bridge balancing电容应变计 capacitance strain gage 补偿片 compensation technique补偿技术 compensation technique基准电桥 reference bridge电阻应变计 resistance strain gage温度自补偿应变计 self-temperature compensating gage半导体应变计 semiconductor strain Gage集流器slip ring应变放大镜 strain amplifier疲劳寿命计 fatigue life gage电感应变计 inductance [strain] gage 光[测]力学 Photomechanics光弹性 Photoelasticity光塑性 Photoplasticity杨氏条纹 Young fringe双折射效应 birefrigent effect等位移线 contour of equalDisplacement暗条纹 dark fringe条纹倍增 fringe multiplication干涉条纹 interference fringe等差线 Isochromatic等倾线 Isoclinic等和线 isopachic应力光学定律 stress- optic law主应力迹线 Isostatic亮条纹 light fringe 光程差optical path difference热光弹性 photo-thermo -elasticity光弹性贴片法 photoelastic coating Method光弹性夹片法 photoelastic sandwich Method动态光弹性 dynamic photo-elasticity空间滤波 spatial filtering空间频率 spatial frequency起偏镜 Polarizer反射式光弹性仪 reflection polariscope残余双折射效应 residual birefringent Effect应变条纹值 strain fringe value应变光学灵敏度 strain-optic sensitivity 应力冻结效应 stress freezing effect应力条纹值 stress fringe value应力光图 stress-optic pattern暂时双折射效应 temporary birefringent Effect脉冲全息法 pulsed holography透射式光弹性仪 transmission polariscope 实时全息干涉法 real-time holographicinterfero - metry网格法 grid method全息光弹性法 holo-photoelasticity全息图Hologram全息照相 Holograph全息干涉法 holographic interferometry 全息云纹法 holographic moire technique 全息术 Holography全场分析法 whole-field analysis散斑干涉法 speckle interferometry散斑Speckle错位散斑干涉法 speckle-shearinginterferometry, shearography散斑图Specklegram白光散斑法white-light speckle method云纹干涉法 moire interferometry[叠栅]云纹 moire fringe[叠栅]云纹法 moire method云纹图 moire pattern离面云纹法 off-plane moire method参考栅 reference grating试件栅 specimen grating分析栅 analyzer grating面内云纹法 in-plane moire method脆性涂层法 brittle-coating method条带法 strip coating method坐标变换 transformation ofCoordinates计算结构力学 computational structuralmecha-nics加权残量法weighted residual method有限差分法 finite difference method有限[单]元法 finite element method配点法 point collocation里茨法 Ritz method广义变分原理 generalized variational Principle最小二乘法 least square method胡[海昌]一鹫津原理 Hu-Washizu principle 赫林格-赖斯纳原理 Hellinger-Reissner Principle修正变分原理 modified variational Principle约束变分原理 constrained variational Principle混合法 mixed method杂交法 hybrid method边界解法boundary solution method有限条法 finite strip method半解析法 semi-analytical method协调元 conforming element非协调元 non-conforming element混合元 mixed element杂交元 hybrid element边界元 boundary element强迫边界条件 forced boundary condition 自然边界条件 natural boundary condition 离散化 Discretization离散系统 discrete system连续问题 continuous problem广义位移 generalized displacement广义载荷 generalized load广义应变 generalized strain广义应力 generalized stress界面变量 interface variable 节点 node, nodal point[单]元 Element角节点 corner node边节点 mid-side node内节点 internal node无节点变量 nodeless variable杆元 bar element桁架杆元 truss element梁元 beam element二维元 two-dimensional element一维元 one-dimensional element三维元 three-dimensional element轴对称元 axisymmetric element板元 plate element壳元 shell element厚板元 thick plate element三角形元 triangular element四边形元 quadrilateral element四面体元 tetrahedral element曲线元 curved element二次元 quadratic element线性元 linear element三次元 cubic element四次元 quartic element等参[数]元 isoparametric element超参数元 super-parametric element亚参数元 sub-parametric element节点数可变元 variable-number-node element拉格朗日元 Lagrange element拉格朗日族 Lagrange family巧凑边点元 serendipity element巧凑边点族 serendipity family无限元 infinite element单元分析 element analysis单元特性 element characteristics刚度矩阵 stiffness matrix几何矩阵 geometric matrix等效节点力 equivalent nodal force节点位移 nodal displacement节点载荷 nodal load位移矢量 displacement vector载荷矢量 load vector质量矩阵 mass matrix集总质量矩阵 lumped mass matrix相容质量矩阵 consistent mass matrix阻尼矩阵 damping matrix瑞利阻尼 Rayleigh damping刚度矩阵的组集 assembly of stiffnessMatrices载荷矢量的组集 consistent mass matrix质量矩阵的组集 assembly of mass matrices 单元的组集 assembly of elements局部坐标系 local coordinate system局部坐标 local coordinate面积坐标 area coordinates体积坐标 volume coordinates曲线坐标 curvilinear coordinates静凝聚 static condensation合同变换 contragradient transformation形状函数 shape function试探函数 trial function检验函数test function权函数 weight function样条函数 spline function代用函数 substitute function降阶积分 reduced integration零能模式 zero-energy modeP收敛 p-convergenceH收敛 h-convergence掺混插值 blended interpolation等参数映射 isoparametric mapping双线性插值 bilinear interpolation小块检验 patch test非协调模式 incompatible mode 节点号 node number单元号 element number带宽 band width带状矩阵 banded matrix变带状矩阵 profile matrix带宽最小化minimization of band width波前法 frontal method子空间迭代法 subspace iteration method 行列式搜索法determinant search method逐步法 step-by-step method纽马克法Newmark威尔逊法 Wilson拟牛顿法 quasi-Newton method牛顿-拉弗森法 Newton-Raphson method 增量法 incremental method初应变 initial strain初应力 initial stress切线刚度矩阵 tangent stiffness matrix割线刚度矩阵 secant stiffness matrix模态叠加法mode superposition method平衡迭代 equilibrium iteration子结构 Substructure子结构法 substructure technique超单元 super-element网格生成 mesh generation结构分析程序 structural analysis program 前处理 pre-processing后处理 post-processing网格细化 mesh refinement应力光顺 stress smoothing组合结构 composite structure流体动力学类:流体动力学 fluid dynamics连续介质力学 mechanics of continuous media介质medium流体质点 fluid particle无粘性流体 nonviscous fluid, inviscid fluid连续介质假设 continuous medium hypothesis流体运动学 fluid kinematics水静力学 hydrostatics 液体静力学 hydrostatics支配方程 governing equation伯努利方程 Bernoulli equation伯努利定理 Bernonlli theorem毕奥-萨伐尔定律 Biot-Savart law欧拉方程Euler equation亥姆霍兹定理 Helmholtz theorem开尔文定理 Kelvin theorem涡片 vortex sheet库塔-茹可夫斯基条件 Kutta-Zhoukowskicondition布拉休斯解 Blasius solution达朗贝尔佯廖 d'Alembert paradox 雷诺数 Reynolds number施特鲁哈尔数 Strouhal number随体导数 material derivative不可压缩流体 incompressible fluid 质量守恒 conservation of mass动量守恒 conservation of momentum 能量守恒 conservation of energy动量方程 momentum equation能量方程 energy equation控制体积 control volume液体静压 hydrostatic pressure涡量拟能 enstrophy压差 differential pressure流[动] flow流线stream line流面 stream surface流管stream tube迹线path, path line流场 flow field流态 flow regime流动参量 flow parameter流量 flow rate, flow discharge涡旋 vortex涡量 vorticity涡丝 vortex filament涡线 vortex line涡面 vortex surface涡层 vortex layer涡环 vortex ring涡对 vortex pair涡管 vortex tube涡街 vortex street卡门涡街 Karman vortex street马蹄涡 horseshoe vortex对流涡胞 convective cell卷筒涡胞 roll cell涡 eddy涡粘性 eddy viscosity环流 circulation环量 circulation速度环量 velocity circulation 偶极子 doublet, dipole驻点 stagnation point总压[力] total pressure总压头 total head静压头 static head总焓 total enthalpy能量输运 energy transport速度剖面 velocity profile库埃特流 Couette flow单相流 single phase flow单组份流 single-component flow均匀流 uniform flow非均匀流 nonuniform flow二维流 two-dimensional flow三维流 three-dimensional flow准定常流 quasi-steady flow非定常流unsteady flow, non-steady flow 暂态流transient flow周期流 periodic flow振荡流 oscillatory flow分层流 stratified flow无旋流 irrotational flow有旋流 rotational flow轴对称流 axisymmetric flow不可压缩性 incompressibility不可压缩流[动] incompressible flow 浮体 floating body定倾中心metacenter阻力 drag, resistance减阻 drag reduction表面力 surface force表面张力 surface tension毛细[管]作用 capillarity来流 incoming flow自由流 free stream自由流线 free stream line外流 external flow进口 entrance, inlet出口exit, outlet扰动 disturbance, perturbation分布 distribution传播 propagation色散 dispersion弥散 dispersion附加质量added mass ,associated mass收缩 contraction镜象法 image method无量纲参数 dimensionless parameter几何相似 geometric similarity运动相似 kinematic similarity动力相似[性] dynamic similarity平面流 plane flow势 potential势流 potential flow速度势 velocity potential复势 complex potential复速度 complex velocity流函数 stream function源source汇sink速度[水]头 velocity head拐角流 corner flow空泡流cavity flow超空泡 supercavity超空泡流 supercavity flow空气动力学 aerodynamics低速空气动力学 low-speed aerodynamics 高速空气动力学 high-speed aerodynamics 气动热力学 aerothermodynamics亚声速流[动] subsonic flow跨声速流[动] transonic flow超声速流[动] supersonic flow锥形流 conical flow楔流wedge flow叶栅流 cascade flow非平衡流[动] non-equilibrium flow细长体 slender body细长度 slenderness钝头体 bluff body钝体 blunt body翼型 airfoil翼弦 chord薄翼理论 thin-airfoil theory构型 configuration后缘 trailing edge迎角 angle of attack失速stall脱体激波detached shock wave 波阻wave drag诱导阻力 induced drag诱导速度 induced velocity临界雷诺数critical Reynolds number前缘涡 leading edge vortex附着涡 bound vortex约束涡 confined vortex气动中心 aerodynamic center气动力 aerodynamic force气动噪声 aerodynamic noise气动加热 aerodynamic heating离解 dissociation地面效应 ground effect气体动力学 gas dynamics稀疏波 rarefaction wave热状态方程thermal equation of state喷管Nozzle普朗特-迈耶流 Prandtl-Meyer flow瑞利流 Rayleigh flow可压缩流[动] compressible flow可压缩流体 compressible fluid绝热流 adiabatic flow非绝热流 diabatic flow未扰动流 undisturbed flow等熵流 isentropic flow匀熵流 homoentropic flow兰金-于戈尼奥条件 Rankine-Hugoniot condition状态方程 equation of state量热状态方程 caloric equation of state完全气体 perfect gas拉瓦尔喷管 Laval nozzle马赫角 Mach angle马赫锥 Mach cone马赫线Mach line马赫数Mach number马赫波Mach wave当地马赫数 local Mach number冲击波 shock wave激波 shock wave正激波normal shock wave斜激波oblique shock wave头波 bow wave附体激波 attached shock wave激波阵面 shock front激波层 shock layer压缩波 compression wave反射 reflection折射 refraction散射scattering衍射 diffraction绕射 diffraction出口压力 exit pressure超压[强] over pressure反压 back pressure爆炸 explosion爆轰 detonation缓燃 deflagration水动力学 hydrodynamics液体动力学 hydrodynamics泰勒不稳定性 Taylor instability 盖斯特纳波 Gerstner wave斯托克斯波 Stokes wave瑞利数 Rayleigh number自由面 free surface波速 wave speed, wave velocity 波高 wave height波列wave train波群 wave group波能wave energy表面波 surface wave表面张力波 capillary wave规则波 regular wave不规则波 irregular wave浅水波 shallow water wave深水波deep water wave重力波 gravity wave椭圆余弦波 cnoidal wave潮波tidal wave涌波surge wave破碎波 breaking wave船波ship wave非线性波 nonlinear wave孤立子 soliton水动[力]噪声 hydrodynamic noise 水击 water hammer空化 cavitation空化数 cavitation number 空蚀 cavitation damage超空化流 supercavitating flow水翼 hydrofoil水力学 hydraulics洪水波 flood wave涟漪ripple消能 energy dissipation海洋水动力学 marine hydrodynamics谢齐公式 Chezy formula欧拉数 Euler number弗劳德数 Froude number水力半径 hydraulic radius水力坡度 hvdraulic slope高度水头 elevating head水头损失 head loss水位 water level水跃 hydraulic jump含水层 aquifer排水 drainage排放量 discharge壅水曲线back water curve压[强水]头 pressure head过水断面 flow cross-section明槽流open channel flow孔流 orifice flow无压流 free surface flow有压流 pressure flow缓流 subcritical flow急流 supercritical flow渐变流gradually varied flow急变流 rapidly varied flow临界流 critical flow异重流density current, gravity flow堰流weir flow掺气流 aerated flow含沙流 sediment-laden stream降水曲线 dropdown curve沉积物 sediment, deposit沉[降堆]积 sedimentation, deposition沉降速度 settling velocity流动稳定性 flow stability不稳定性 instability奥尔-索末菲方程 Orr-Sommerfeld equation 涡量方程 vorticity equation泊肃叶流 Poiseuille flow奥辛流 Oseen flow剪切流 shear flow粘性流[动] viscous flow层流 laminar flow分离流 separated flow二次流 secondary flow近场流near field flow远场流 far field flow滞止流 stagnation flow尾流 wake [flow]回流 back flow反流 reverse flow射流 jet自由射流 free jet管流pipe flow, tube flow内流 internal flow拟序结构 coherent structure 猝发过程 bursting process表观粘度 apparent viscosity 运动粘性 kinematic viscosity 动力粘性 dynamic viscosity 泊 poise厘泊 centipoise厘沱 centistoke剪切层 shear layer次层 sublayer流动分离 flow separation层流分离 laminar separation 湍流分离 turbulent separation 分离点 separation point附着点 attachment point再附 reattachment再层流化 relaminarization起动涡starting vortex驻涡 standing vortex涡旋破碎 vortex breakdown 涡旋脱落 vortex shedding压[力]降 pressure drop压差阻力 pressure drag压力能 pressure energy型阻 profile drag滑移速度 slip velocity无滑移条件 non-slip condition 壁剪应力 skin friction, frictional drag壁剪切速度 friction velocity磨擦损失 friction loss磨擦因子 friction factor耗散 dissipation滞后lag相似性解 similar solution局域相似 local similarity气体润滑 gas lubrication液体动力润滑 hydrodynamic lubrication 浆体 slurry泰勒数 Taylor number纳维-斯托克斯方程 Navier-Stokes equation 牛顿流体 Newtonian fluid边界层理论boundary later theory边界层方程boundary layer equation边界层 boundary layer附面层 boundary layer层流边界层laminar boundary layer湍流边界层turbulent boundary layer温度边界层thermal boundary layer边界层转捩boundary layer transition边界层分离boundary layer separation边界层厚度boundary layer thickness位移厚度 displacement thickness动量厚度 momentum thickness能量厚度 energy thickness焓厚度 enthalpy thickness注入 injection吸出suction泰勒涡 Taylor vortex速度亏损律 velocity defect law形状因子 shape factor测速法 anemometry粘度测定法 visco[si] metry流动显示 flow visualization油烟显示 oil smoke visualization孔板流量计 orifice meter频率响应 frequency response油膜显示oil film visualization阴影法 shadow method纹影法 schlieren method烟丝法smoke wire method丝线法 tuft method。
小型五轴数控机床的刀库设计及其优化
小型五轴数控机床的刀库设计及其优化摘要:目前科技发展迅猛,在这发展过程中工业化是的生产方式也更加多样化了,智能化的生产方式逐渐取代了手工作坊式的生产模式,在加工工件过程中,由于工艺的复杂性,一把刀具并不能满足加工工件的需求,这就需要多把刀具分工来完成,自动换刀装置的出现能够很好的的为加工工件提升效率。
现如今我国大多数的工厂还是以手工换刀的方式存在,主要原因在于现在市场上直接购买的自动换刀装置都是按普遍性设计,价格高且普遍性不强。
本文主要针对的是小型五轴机床作为对象,研究并设计基于机床的刀库设计及其优化,使其刀库结构简单、小巧、成本低廉,提高加工效率,为进一步研发小型五轴机床低成本刀库打下基础。
我们通过搜集有关的文献,发现我国的自动换刀装置相较于国外来说发展起步晚,现在的大型数控机床主要还是来源国外工业发达的国家,国内生产机床的的企业在国际市场中目前缺乏有效的竞争力,市场上对于小型机床的自动换刀装置没有投入多大这一方面的研究,而小型五轴机床能够很好的的为高校提供教学之用,推进我国五轴数控的发展。
在制造业这一领域,加工中心与五轴机床的区别在于多了能够存取刀具的刀库,在加工工件的时候能够极大的提高换刀效率。
在进行研究自动换刀装置中的设计,着重点在于刀库的设计,他的作用在于对刀具的存放,能使工件加工的效率大大提高,本文研究的内容如下所示:(1)对小型五轴数控机床的技术进行分析,并对国内外的刀库研究现状进行综述,通过机床的参数要求,完成刀库的总体方案设计。
(2)结合上述机床有关参数及技术设计要求,本文完成小型五轴数控机床刀库的结构设计,并在Pro/E中完成建模和装配。
(3)运用powermill软件进行模拟加工,建立机床仿真模块,对刀库进行仿真加工,生成相应的刀具路径。
(4)对PM-post后置处理模块的设置方法和流程进行研究,根据刀位文件来生成机床能识别的NC程序。
关键词:加工中心;刀库;后置处理;数控加工仿真III小型五轴数控机床的刀库设计及其优化Design and optimization of tool magazine for small five axis NCmachine toolAbstract:At present,science and technology are developing rapidly,In this development process,the industrial production mode is also more diversified.The intelligent production mode gradually replaces the manual workshop production mode.In the process of processing the workpiece,because of the complexity of the process,one tool can not meet the needs of processing the workpiece,which requires more tools to complete the division of labor.The emergence of automatic tool change device can be a good way to process the workpiece Improve efficiency.At present,most of the factories in our country still use the way of manual tool change.The main reason is that the automatic tool change device purchased directly in the market is designed according to the universality,and the price is high and the universality is not strong.This paper mainly aims at the small five axis machine tool as the object,studies and designs the design and optimization of the tool magazine based on the machine tool,which makes the structure of the tool magazine simple,compact,low cost, improves the processing efficiency,and lays the foundation for further research and development of the low-cost tool magazine of the small five axis machine tool.Through the collection of relevant literature,we found that the development of automatic tool change device in China started late compared with that in foreign countries. Now the large-scale CNC machine tools mainly come from foreign countries with developed industries.The domestic enterprises producing machine tools are lack of effective competition in the international market,and the market has not invested much in the research of automatic tool change device of small-scale machine tools Research,and small five axis machine tools can provide a good teaching for colleges and universities,promote the development of five axis CNC in China.In the field of manufacturing industry,the difference between machining center and five axis machine tool is that there are more tool libraries thatIVcan access tools,which can greatly improve the efficiency of tool change when machining workpiece.In the study of the design of the automatic tool change device,the focus is on the design of the tool magazine.Its function is to store the tools,which can greatly improve the efficiency of workpiece processing.The content of this paper is as follows: Firstly,This paper analyzes the technology of small five axis numerical control machine tool,summarizes the research status of tool magazine at home and abroad,and completes the overall design of tool magazine through the parameter requirements of the machine tool.Secondly,Combined with the above machine parameters and technical design requirements,this paper completed the structure design of small five axis CNC machine tool magazine,and completed the modeling and assembly in Pro/E.Thirdly,Using PowerMILL software to simulate machining,the simulation module of machine tool is established,and the tool library is simulated to generate the corresponding tool path.Fourthly,This paper studies the setting method and flow of PM post post processing module,and generates NC program which can be recognized by machine tool according to cutter position file.Key words:Machining Center;tool magazine;post processing;numerical control machining simulatV小型五轴数控机床的刀库设计及其优化目录摘要 (III)Abstract (IV)1绪论 (1)1.1课题研究背景 (1)1.2国内外自动换刀装置研究 (2)1.3课题研究价值和意义 (3)1.3.1加工中心刀库 (3)1.3.2刀库问题及处理方法 (5)1.3.3刀库故障及修理方法 (5)1.4主要研究内容 (5)1.4.1研究目标 (6)1.4.2研究内容 (6)1.5本章小结 (6)2刀库方案设计 (7)2.1五轴数控机床简单介绍 (7)2.1.1五轴联动数控机床结构特点 (7)2.1.2五轴联动数控机床类型 (8)2.2刀库型式、特点、方案 (8)2.2.1刀库的型式 (8)2.2.2刀库的特点 (8)2.2.3刀库的方案 (9)2.3主要部件选型 (10)2.3.1油水分离器 (10)2.3.2空气压缩机 (10)2.3.3电磁换向阀 (11)2.3.4自动换刀主轴 (12)VI2.4用Creo软件进行刀库建模 (15)2.4.1Creo软件 (15)2.4.2基于Creo软件的刀库设计 (15)2.4.3刀座卡簧夹紧力计算 (16)2.4.4Creo软件使用步骤 (16)2.5本章小结 (17)3加工工艺分析及其数控编程 (18)3.1Powermill软件介绍 (18)3.1.1多轴数控加工概述 (18)3.1.2powermill简介 (18)3.2基于powermill的五轴数控机床仿真 (19)3.3刀库的仿真加工 (20)3.3.1powermill加工编程步骤 (20)3.3.2加工工艺分析 (21)3.4本章小结 (23)4后置文件处理应用 (24)4.1后置处理的方法 (24)4.1.1后置处理程序 (24)4.1.2powermill后置处理方法 (24)4.1.3后置处理程序工作流程 (26)4.2PM-post软件 (27)4.2.1PM-post后处理 (27)4.2.2PM-post软件介绍 (28)4.2.3PM-post后处理步骤 (28)4.3本章小结 (29)结论与展望 (30)5.1结论 (30)5.2展望 (30)VII小型五轴数控机床的刀库设计及其优化参考文献 (31)致谢 (32)附录 (33)VIII1绪论1.1课题研究背景随着科技的高速发展,我国的制造业也迎来了新一轮的春天,机床产业是我国国民经济发展的基础,也是高科技领域中的重要组成成分。
涡轮叶栅叶型损失的数值模拟方法
第12卷 第2期航空动力学报Vol.12No.2 1997年4月Journal of Aerospace Power Apr. 1997涡轮叶栅叶型损失的数值模拟方法北京航空航天大学 于 清**哈尔滨工业大学 杨 弘【摘要】 给出了一个计算亚、跨音涡轮叶栅叶型损失的数值计算方法。
主流采用时间推进有限体积法求解积分型欧拉方程,并采用了局部网格修正技术;附面层采用全隐格式求解有限差分方程;在叶栅出口与远后方均匀流之间进行了叶片尾迹与主流的掺混损失计算。
算例表明本文的数值方法可准确地预测涡轮叶栅的叶型损失。
主题词: 叶型损失 数值模拟 涡轮 叶栅流动 分类号: V231.3 V211.191 前 言 要正确预测叶栅的气动性能关键在于对流道内部各种损失的合理确定。
工程设计中广泛应用的损失计算方法仍然是建立在大量实验数据基础上的经验计算公式[1,2],所有的经验公式都只反映部分叶栅几何参数和气动参数同损失的变化关系。
大量的数值计算及实验表明,叶片型面设计对叶栅流道内的损失有很大影响,局部型面的变化有可能引起叶片表面气流分离的发生。
因此,损失经验计算公式的适用性就受到了很大的限制。
本文数值模拟求解叶型损失的方法分为三步:(1)主流区无粘流场的计算,求得叶片表面的压力分布和速度分布;(2)叶片表面附面层的计算,确定附面层的特征参数以及叶栅出口附面层的速度形分布;(3)栅后的气流掺混计算。
主流流场的求解是关键,合理的叶片表面压力分布,是附面层求解的前提,而附面层的计算结果又是掺混计算的出发点。
2 计算方法2.1 主流场的求解 基本方程是建立在任意回转面的正交曲线坐标系下,不考虑气体的粘性,其中 =const,为子午面,0≤ ≤2 ,n=co nst,为旋成流面,l是与上述旋成流面正交的旋成面。
根据流面假设,对于任意气流参数均有: / n=0,W n=0。
这样就将流动控制方程简化为二维,在绝热、无质量力的假设条件下,微分型的连续方程、运动方程和能量方程可由矩阵表示为:Q1( Z/ t)+Q2( Z/ l)+Q3( Z/r )+Y=0(1) Z为变量向量,Q1,Q2,Q3,Y为系数及常量矩阵[3]。
Computer simulation model for determining damage t
专利名称:Computer simulation model for determiningdamage to the human central nervoussystem发明人:Fraser C. Henderson,Kingsley Joel Berry申请号:US10682376申请日:20031009公开号:US06980922B2公开日:20051227专利内容由知识产权出版社提供专利附图:摘要:A computerized model simulates the human spinal cord and makes it possible to draw inferences about the probability of future injury or the likelihood that specificinjuries occurred in the past. The spinal cord is modeled by a plurality of two-dimensional graphs formed of a large number of finite elements. The two-dimensional graphs are stacked in positions corresponding to the measured positions of the spinal cord at various vertebral levels of a patient. The stacked graphs yield a three-dimensional model, which may be compared with similar data taken from other patients. The model may include the simulation of stress, applied to all or part of the spinal cord, resulting in a perturbed three-dimensional model which may again be compared with similar data taken from patients having known injuries. The invention can therefore be used, among other things, to verify claims of spinal injury as a result of vehicular or sporting accidents.申请人:Fraser C. Henderson,Kingsley Joel Berry地址:Upper Marlboro MD US,Flint MI US国籍:US,US代理人:William H. Eilberg更多信息请下载全文后查看。
Geometric Modeling
Geometric ModelingGeometric modeling is a crucial aspect of computer graphics, engineering, and design. It involves creating digital representations of objects and environments using mathematical and computational techniques. Geometric modeling plays a significant role in various industries, including architecture, manufacturing, animation, and virtual reality. This technology enables designers and engineers to visualize and analyze complex structures, simulate real-world scenarios, and create realistic visualizations. However, like any other technology, geometric modeling also presents its own set of challenges and limitations. One of the primary challenges in geometric modeling is the complexity of representing real-world objects and environments accurately. While simple geometric shapes can be easily defined using mathematical equations, complex objects with irregular shapes and intricate details require advanced modeling techniques. Capturing theintricate details of natural objects, such as trees, rocks, and human faces, poses a significant challenge for geometric modelers. Achieving a high level of realism and accuracy in these representations often requires sophisticated algorithms and extensive computational resources. Another challenge in geometric modeling is the balance between accuracy and computational efficiency. As the complexity of geometric models increases, the computational resources required to manipulate and render these models also escalate. High-resolution models with intricate details demand substantial memory and processing power, making real-time interactions and simulations challenging. Finding the right balance between geometric accuracy and computational efficiency is a constant struggle for designers and engineers working in this field. Moreover, geometric modeling also faces challenges related to data interoperability and standardization. In many industries, geometric models need to be shared and utilized across different software applications and platforms. However, the lack of standardized file formats and data structures often leads to compatibility issues and data loss during the transfer process. This hinders seamless collaboration and integration of geometric models across various design and engineering tools. Furthermore, geometric modeling in virtual reality and augmented reality applications presents unique challenges. In these immersive environments, geometric models need to be rendered in real-time toprovide users with a seamless and interactive experience. Achieving high frame rates and low latency while maintaining visual quality is a demanding task for geometric modelers working in the virtual and augmented reality space. Despite these challenges, advancements in geometric modeling technology continue to push the boundaries of what is possible in computer graphics and design. Innovations in computational geometry, rendering algorithms, and virtualization techniques are enabling the creation of highly detailed and realistic geometric models. Additionally, the integration of artificial intelligence and machine learning is opening up new possibilities for automating the process of geometric modeling and enhancing the realism of digital representations. From an emotional perspective, the challenges and limitations in geometric modeling can be both frustrating and motivating for professionals in the field. The frustration arises from the constant struggle to achieve a balance between accuracy and efficiency, as well as the difficulties in ensuring seamless interoperability and data exchange. However, these challenges also serve as a source of motivation, driving researchers and practitioners to innovate and develop new solutions that push the boundaries of geometric modeling. In conclusion, geometric modeling is a complex and dynamic field that plays a crucial role in various industries. While it presents its own set of challenges and limitations, the continuous advancements in technology and the dedication of professionals in the field continue to drive innovation and progress. As the demands for realistic digital representations and immersive experiences grow, the importance of overcoming these challenges in geometric modeling becomes increasingly significant.。
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Numerical Model Calibration for Simulating Coal Pillars, Gob andOverburden Response Essie Esterhuizen , Senior Service FellowChris Mark , Principal Reserach Engineer, Mining Engineer Michael M. Murphy , Research Engineer, Mining EngineerGround Control BranchNIOSH, Offce of Mine Safety and Health ResearchPittsburgh, PAABSTRACTThe design of underground coal mines requires a clear understanding of the overburden response, the loading of pillars, the loading of the gob, the pillar failure process, and the ultimate load carried by partly or fully yielding pillars. Very few high-quality stress measurements of yielding pillars and gob loading have been made in full extraction mining. Well-calibrated numerical models can assist in providing a better understanding of the load and failure processes, provided the coal, the overburden, and the gob are all modeled with suffcient realism. A program of numerical model calibration and validation was carried out using FLAC3D.1 1 Mention of any company name or product does not constitute endorsement by the National Institute for Occupational Safety and Health.The models were calibrated against observed and measured performance of coal pillars and the overburden in operating mines to provide a basic set of input parameters that can be used to provide a realistic frst estimate of expected ground response and pillar loading. Input parameters for modeling coal pillar response were based on data from triaxial testing on coal samples, combined with both matching the depth of failure in the coal ribs to observations as well as matching the peak pillar resistance to an empirical equation. The models were calibrated against strong roof and foor case histories in which the pillar strength is governed by failure and yielding of the coal within the pillar and the surrounding strata only had a limited impact on pillar strength. Input parameters for the overburden were determined from a large database of laboratory tests and model calibration against maximum subsidence and subsidence curvature. Further overburden calibration was carried out by matching stresses in the mining horizon to feld measurements. Three examples of the application of the calibrated dataset and modeling methodology to feld measurements are presented. The results show that a reasonable estimate of the in-seam stress distribution and overburden response can be obtained for both strong and weak overburden scenarios at various depths of cover.INTRODUCTIONThe planning and design of coal mine excavations requires reliable estimates of the expected strength and loading of the mine structures to achieve global stability. Empirical methods arewidely used to estimate the strength and loading of coal pillars and have been incorporated into pillar design procedures, such as Analysis of Longwall Pillar Stability (ALPS) (Mark, 1987) and Analysis of Retreat Mining Pillar Stability (ARMPS) (Mark and Chase, 1997), that are widely used in the United States. Numerical models are fnding increasing application as a tool for underground mine design because of their versatility and the ever increasing computational power available to mine designers. A prerequisite for the application of numerical models is the calibration of the models against observed rock mass response (Hoek et al., 1990; Skiles and Stricklin, 2009). The calibration process may include comparison of model results to measured stress and deformation and modifying the input parameters in a systematic manner to achieve a satisfactory agreement between the model results and measurements. Once models have been calibrated, they can be applied to evaluating similar mining layouts in similar geological conditions.Models that correctly simulate the basic mechanics of rock failure and deformation are required to improve the prediction of the larger scale rock mass response to mining excavations. However, knowing the likely deformations and extent of rock fracturing does not fully predict the actual mining conditions. Empirical relationships need to be established between model outputs and the serviceability of the proposed mining excavations. Such relationships need to include both model outputs and signifcant geological structures that impact excavation stability. For example, Wang and Heasley (2005) describe a system that allows composite hazard maps to be developed in which various geological data and numerical model outputs can be combined into a single index.During the planning stages of a mine or a new section of a mine, data on local geological structures and variations of the bedded sequence can be limited. Planning is typically based on the "expected "average conditions. Modifcations to the mining plan are made if hazardous conditions are exposed during development. Numerical models can provide additional insight into the expected "response of the "average rock mass, but the reliability of the prediction is not better than the available geotechnical data. When developing a numerical model, one of the frst challenges is to identify appropriate input parameters for modeling therock mass. The large-scale strength of the rock mass needs to be known as well as the initial loading conditions. Establishing appropriate values for rock mass strength can be a challenge because laboratory-determined test results do not necessarily represent the properties of the large-scale rock mass. Methods of relating laboratory tests to the large-scale rock mass strength have been developed (Hoek and Brown, 1997) and can be used as a frst estimate. However, these relationships are more appropriate for a relatively homogeneous, jointed rock mass, rather than the strongly bedded and highly variable rock layering that is found in coal mine strata. The initial stress conditions in coal strata can also be more complex than in more homogeneous rock masses. In the eastern and midwestern United States, the in situ horizontal stress appears to be caused by current-day tectonic loading, (Zoback and Zoback, 1989; Dolinar, 2003; Mark and Gadde, 2008), resulting in horizontal stress that is greater in stiffer rock strata. The resulting variation in horizontal stress should be included in numerical models. Further issues exist when attempting to model the gob response. Little is known about the extent of caved rock above the mining horizon and the properties of the fully caved and partially caved material. Nevertheless, numerical models have found wide acceptance in coal mine design, in spite of the diffculties and challenges associated with model development and calibration.This paper addresses the need for a basic set of model parameters to provide a frst estimate of the expected rock mass response in U.S. coal mines. The models were calibrated against published case histories of in situ monitoring of the rock mass response to coal mining as well as laboratory testing of coal, intact rock, and gob materials. This paper does not, however, provide relationships between model outputs and excavation serviceability indices.The modeling software used in this paper is FLAC3D (Anon., 2007). The model parameters will be useful as initial estimates when using other modeling techniques, but each technique should be calibrated independently.PILLAR STRENGTH MODELINGThe strength of pillars is affected by the properties of the coal within the pillars, the contact between the coal and the surrounding rock mass, and the response of the surrounding rock mass to the pillar stress. Therefore, the pillar-roof-foor system should be considered as a unit when assessing pillar strength.Strength of the CoalThe scale dependence of rock strength, particularly coal, has received much attention in rock engineering literature (Hoek and Brown, 1980; Bieniawski, 1968). Coal is one of the few rock materials that has been extensively tested at various scales and the results indicate that its strength reduces as the sample size increases. For modeling purposes, the coal strength as well as the residual strength and the rate of strength decay need to be known.The Hoek-Brown constitutive model that is available in FLAC3D was used to model the coal strength. The peak strength is assumed to follow the Hoek-Brown rock mass strength criterion (Hoek et al., 2002) and yield is modeled based on strain softening and non-associated plastic fow rules. The Hoek-Brown criterion describes a non-linear relationship between confnement and stress, and can be written as follows, in its general form:mσ 3 aσ1=σ 3 +σ ( + s)σ (1)where I1and I3are the effective principal stresses; Icis the strength of the intact rock; and m, s, and a are empirically derived parameters. The parameters can be determined by laboratory testing of small samples of rock. However, obtaining the parameters for the large-scale rock mass cannot be practically done by direct testing. Methods for estimating these parameters from rock mass classifcation data and small-scale laboratory tests have been proposed (Hoek and Brown, 1997).To obtain a set of realistic coal strength parameters for the Hoek-Brown criterion, the strength of laboratory-scale coal samples was frst considered. Unpublished triaxial test data available to the authors, supplemented by published data (Atkinson and Ko, 1977; Morsy and Peng, 2001; Newman and Hoelle, 1993), were used to determine an initial set of parameters describing laboratory coal strength. There was a considerable scatter in the results, and each data set was assessed individually. The s-parameter was set to 1.0, which represents intact rock material, and the a-parameter was set at either 0.50 or 0.65, depending on which value provided the best ft. The resulting m-parameter for the intact coal (m,) was determined for each data set. The resulting m,-values ranged between a low of 5.0 and a high value of 17.6, and the uniaxial compressive strength (UCS) of the coal varied between 16 MPa and .0 MPa (2,321 and 5,802 psi).The next step was to modify the m-and s-parameters so that they would be representative of a large-scale (1-m (3.3-ft) edge) coal sample. The literature contains several approaches to estimate this value, since it is impractical to determine it by direct testing. For example, Gadde et al. (2007) estimated the large-scale m-parameter for coal through rock classifcation considerations. Barron and Yang (1992) showed that the coal type and rank result in an m-parameter variation and proposed that the large-scale m-parameter can be estimated from the coal rank number. Medhurst and Brown (1988) conducted triaxial strength tests on laboratory samples with diameters of 61 mm (2.. in) up to 300 mm (12 in) and extrapolated the results to large-scale coal. They" assumed that the 61-mm (2.. in) samples represent "intact coaland the larger samples were considered to represent increasingly fractured coal as the number of cleats and faws in the samples increased. The results of the study showed that the m-value decreases with sample size. For medium rank, mid-brightness coal samples, they found that setting the a-parameter to 0.65 gives the best ft to the test results and the following relationship can be used to estimate the in situ m-value for large-scale coal:m = 0.15m (2) ,Using the above relationship the m -parameter for U.S. coal can be calculated. Based on the review of triaxial tests on U.S. coal "samples, the m ,-parameter for "average U.S. coal was calculated to be 9.8, which is the average of the laboratory derived values. The m -parameter for the large-scale coal can then be calculated to be 1..7, using Equation 2. This value of the m -parameter was used in all the pillar models described in this paper.Further parameters that are required for modeling large-scale coal are the s -parameter of the large-scale coal, the residual m -and s -parameters, and the rate of strain softening from the peak to the residual strength. These parameters have not been determined in the laboratory due to practical problems with preparing, handling, and crushing such large blocks of material. An alternative approach may be to use rock classifcation methods to estimate the s -parameter and the residual values of m and s. However, rock classifcation methods are poorly suited to classifying coal material. In addition, the relationships between classifcation values and the Hoek-Brown parameters are not necessarily valid for coal materials. Therefore, the fnal estimates of the unknown parameters were obtained through numerical model calibration against empirically derived pillar strength equations, observed failure of coal in pillar ribs, and measurements of stress distributions in coal pillars.Numerical Model Testing to Obtain Unknown Parameters The unknown strength parameters of the coal were determined by creating numerical models of coal pillars and subjecting them to increasing loads while monitoring their stress-strain response. The pillar response was compared to empirical strength equations and to feld monitoring data and the unknown parameters were varied until satisfactory agreement was obtained between model response and observed pillar performance. At all times, the reasonableness of the inputs was considered against measured values.Numerical models were created in which a portion of the roof strata, the coal pillar, and the foor strata were simulated. Pillars with width-to-height ratios of 3, ., 6, 8 and 10 were modeled. Interface elements were used to model the contacts between the coal and the surrounding rocks. The surrounding rocks were elastic having a Young's modulus of 20 GPa (2,901 ksi) and Poisson's ratio of 0.25. Figure 1 shows a pillar model with the coal, roof, and foor strata included, only a quarter of a full pillar was modeled because of symmetry.Coal pillarFigure 1. Example of a three dimensional model of a coal pillar and the surrounding roof and foor strata.The model pillars were loaded by gradual compression in the vertical direction. The rate of compression was controlled so that the unbalanced forces in the model remained within pre-defned limits. As the stress in the model increased, failure and deformation of the coal was allowed to occur based on the defned strength properties and assumed unknown parameters. The model pillars were tested up to their peak strength and were allowed to yield to a residual value. Some of the wider pillars displayed strain hardening characteristics and the tests were typically stopped when the model deformation became excessive.Bieniawski's (1992) empirical pillar strength equation was used for comparing the peak strength of the numerical models to actual pillar strength. The comparisons were carried out for pillars with width-to-height ratios of 3.0 to 8.0. Beyond a width-to-height ratio of 8.0 the empirical data are sparse. The large-scale coal strengthused in the Bieniawski equation was set at 6.2 MPa (899 psi) being representative of the typical coal strength in U.S. coal mines, after Mark and Chase (1997).Field monitoring data in the form of stress measurements in pillars adjacent to longwall panels were used to verify that the extent of coal failure and the stress gradient at the edge of the pillars were acceptable. The calibration of the models against coal rib failure was carried out by comparing the model results to a series of pillar stress measurements from feld study sites in the U.S. (Iannacchione, 1990a; Campoli et al., 1990; Koehler et al., 1996; Oram, 1996), shown in Figure 2. Vertical stress values in excess of 80 MPa (11,603 psi) were measured within the coal ribs at some of the sites. The depth of coal yield can be seen to extend about 5 m into the pillar where these peak stress values were measured. The fgure also shows a collection of stress profles determined by the numerical models, after fnal calibration of the coal properties. It can be seen that the peak stress in the model profles follow a similar path as the measured results. For a peak stress of about 80 MPa (11,603 psi), the model shows the peak located at about 5 m (16 ft) into the pillar, which falls within the range of feld results. It was concluded that the pillar models were satisfactory and were producing realistic peak strength values at the edges of pillars and depths of failure into the coal ribs.Sensitivity studies of the effect of the interface properties showed, similar to the experience of other researchers (Gale, 1999; Iannacchione, 1990b; Lu et al., 2008), that the interface properties can have a signifcant effect on the strength of a pillar. However, if a similar stress gradient is desired at the edge of the pillar, as measured in underground trials, a friction angle of about 25° is required, with a nominal interface cohesion value of 0.1 MPa (1..5 psi). The friction angle of 25° is lower than the internal friction angle of most coal types and seems to be a reasonable value to represent a typical coal-rock interface.After conducting many combinations of inputs, and always evaluating the assumptions for reasonableness and the outcomesagainst empirical results, the following set of input parameters was found to be satisfactory for modeling coal pillars based on the requirements of matching the Bieniawski strength equation and achieving similar depths of failure and stress gradients as observed in the feld: UCS (lab scale) = 20 MPa (2,901 psi) Young's modulus = 3 GPa (.35 ksi) Poisson's ratio = 0.25 m -value = 1..7 s -value = 0.07 m -residual = 1.0 s -residual= 0.001 Interface friction angle = 25°Interface cohesion= 0.1 MPa (1..5 psi)Interface tensile strength = 0.0Interface normal stiffness = 100.0 GPa/m (1.,50. ksi/m) Interface shear stiffness= 50 GPa/m (7,252 ksi/m)The strength decrease of the coal from the peak to a residual value was allowed to take place over a plastic strain value of 0.0. for element sizes in the range of 0.30 to 0.33 m (1 to 1.1 ft). This value is affected by the element size used in the models, and needs to be adjusted if models are created using a signifcantly different element size. The FLAC3D software also has a dilation parameter that is used in the implementation of the Hoek-Brown criterion. This parameter was set to zero, mainly because non-zero values appeared to cause large geometric distortions of the yielding elements which were considered to be excessive. It is recognized that the fnal set of inputs is not unique, and it is possible that a different combination of input values can equally satisfy the empirical data.100 :e a s :r e " s t r e s s :Q a )0 12345678990 80 7060 50 40 30 20 10 0Distance into coal rib m)Figure 2. Stress at the edge of coal pillars subject to increasedloading. Solid lines indicate model results of the stress profle at the edge of a W:H = 16 pillar at various loading stages. Symbols indicate feld measurements at the edges of four longwall chain pillars.Resulting Model Pillar Strength and Stress-Strain Response Figure 3 shows the resulting stress-strain curves obtained from the pillar models. 50.0 45.0 40.035.0S t r e s s :Q a )30.0 25.0 20.0 15.0 10.0 5.0 0.00% 1% 2% 3% 4% 5% 6% 7% 8% 9% 10%StrainFigure 3. Stress-strain curves obtained from calibrated numerical models of pillars with width-to-height ratios of 3.0 to 10.0.It can be seen that when the width-to-height ratio is 6.0 and below, the pillars exhibit a clear peak strength followed by strain softening behavior as the pillars continue to be compressed. However, for the width-to-height ratios of 8.0 and 10.0 the pillars do not display strain softening behavior, but become strain hardening. This type of behavior has been observed in laboratory tests on coal samples (Das, 1986) and is predicted by some pillar strength theories (Wilson, 1972; Salamon and Wagner, 1985).The peak pillar resistance produced by the numerical models is compared to the Bieniawski pillar strength equation up to a width-to-height ratio of 8.0 in Figure .. The results show that satisfactory agreement has been achieved between the model results and the empirical equation, which was the target of the model calibration exercise.0 5 10 15 20 25 30 "e a - p i l l a r 't r e g t h "a 02 4 6 81012Width-to-height ratioFigure 4. Pillar strength results obtained by numerical modelsafter calibrating the models to the empirical pillar strength equation of Bieniawski (1989). The Effect of Weak Surrounding RocksThe above results were all obtained using models of coal that is contained between elastic roof and foor strata. The elastic material was not allowed to fail in the models. A number of analyses were carried out to evaluate the impact of weak and moderate strength roof and foor rocks on pillar strength, which showed that the peak pillar strength will be reduced if bedding slip occurs in the roof or foor. Other issues also arose, such as punching of the pillar core into the surrounding strata and pillar weakening if the roof collapses between the pillars. These phenomena have been observed in the feld and can be analyzed using foundation engineering principles or numerical models (Chugh and Pytel, 1992; Gadde, 2009). Pillar design issues related to weak roof and foor strata fall beyond the scope of this paper. The results shown here assume that the pillar strength is governed by failure and yielding of the coal within the pillar and the surrounding strata have only a limited impact on the strength.GOB RESPONSE MODELINGWhen modeling full extraction mining, such as longwall or pillar extraction, it is necessary to realistically simulate the gob (caved rock) in the mined out areas. The characteristics of the gob are diffcult to measure in the feld because of the large displacements that occur and fragmented nature of the caved rocks. Attempts have been made to locate load cells within the gob and measurements have been made in the foor strata below the gob (Iannacchione, 1990b). Laboratory tests on rock fragments have also provided valuable insight into the compaction behavior of fragmented gob materials (Pappas and Mark, 1993). Gob CharacteristicsThe gob is usually subdivided into two zones: a lower, fully caved zone and an upper fractured zone (Peng and Chiang, 198.). The fully caved zone can be expected to extend vertically to about 2 to 3 times the mining height and behaves as a granulated material with a relatively high void ratio. The rock in the fractured zone has a relatively low void ratio but the overall strength is reducedowing to the presence of fracturing associated with the passage ofthe longwall panel face stress abutment.Laboratory tests on coal measure shale and sandstone fragments showed that the stress-strain response of confned gob material follows an exponential hardening curve (Pappas and Mark, 1993). The tests were carried out on rock fragments that resembled a fully caved gob, having void ratios in the region of 30% to .0%. It was found that the stronger sandstone gob material had a stiffer response than the weaker shale material, as one would expect. A hyperbolic equation after Salamon (1990) was found to adequately represent the gob stress-strain behavior, which can be expressed as follows:a ×εσ=b −(3)where a and b are empirically derived parameters and E is the vertical strain. The b -parameter is related to the void ratio and the a -parameter is the gob stress when the strain is equal to b12. For shale gob, the laboratory tests (Pappas and Mark, 1993) showed that a = 7.65 MPa (1,110 psi) and b = 0...2, and for sandstone gob, a = 13.03 MPa (1,890 psi) and b = 0..27. Modeling Gob as a Strain Hardening MaterialGob modeling can follow two approaches. In the frst approach, the intent may be to study roof fracturing, caving and gob development in response to mining. In this approach, it is necessary to explicitly model the gob formation process so that variations in geology and loading conditions can be studied. A second approach may be modeling of the effect of the gob on the surrounding coal mine entries and pillars. In the second situation, the gob is implicitly modeled; that is, the effect of the gob is modeled accurately so that the load redistribution to the surrounding rock and coal is correct and the large-scale overburden defection and subsidence is correct. This paper addresses the second scenario, in which rock fracture and gob development is not explicitly modeled, but the effect of the gob needs to be included in a model.When using the FLAC3D software, it is possible to simulate the effects of the fully-caved gob as a strain-hardening, granulated "material using "double-yield elements. These elements can model the compaction of granulated materials under increased loading using a cap-plasticity criterion and have been successfully used to model gob compaction and response (Esterhuizen and Barczak, 2006). Alternatively, when a large-scale model is set up, equivalent gob elements can be created by simply following the gob response curve without attempting to simulate the complex material behavior that forms the response curve (Board and Damjanac, 2003; Esterhuizen and Mark, 2009).All the model calibrations presented in this paper were done using equivalent gob elements that follow the hyperbolic stress-strain curves (Equation 3). The gob response to various depths of cover, mining geometries and overburden types was investigated.OVERBURDEN RESPONSE MODELINGThe defection and potential subsidence or collapse of the overburden has a signifcant impact on the load redistribution around coal mine panels. When full extraction mining is carried out, the overburden will settle onto the gob and stress will be regenerated in the mined area. The amount of stress regeneration depends on the gob stiffness as well as the stiffness of the overburden. Subsidence is also directly affected by the overburden properties and the panel width-to-depth ratio. Strong overburden strata can form a stable arch over a mined panel, which can result in signifcantly higher stress in the unmined coal while reducing the gob stress and magnitude of subsidence. The overburden stiffness also determines how stresses will be distributed over the unmined coal. Stiff overburden can be expected to transfer stress over a greater lateral distance than softer strata. When modeling the overburden, the characteristics of the overburden materials must be captured as accurately as possible to reproduce the observed response. The accuracy of the overburden models can be verifed against feld measurements of subsidence and of stress magnitudes in the coal surrounding mined panels. Modeling Bedded StrataThe bedded overburden rocks were modeled using the strain softening, ubiquitous joint elements available in the FLAC3D software. These elements consist of a strain softening Coulomb material that represents the rock matrix and planes of weakness representing the bedding. The orientation and strength of the planes of weakness can be defned separately from the matrix properties and can also exhibit strain softening behavior. These elements allow a reasonable approximation of the characteristics of bedded strata to be made.For the purpose of model calibration, a suite of rock strengths and bedding types was created, which could be combined to model any rock type, from a strong limestone with no bedding weaknesses to a low strength shale or claystone with smooth bedding planes. The initial properties of the strata were based on extensive databases of rock properties available at NIOSH as well as published data (Zipf, 2007; Rusnak and Mark, 2000). The approach was to simulate the rock matrix without any bedding "effects or "rock mass effects. The matrix strength of the in-situ rocks was determined from the laboratory scale strength using the relationship suggested by Hoek and Brown (1980):50 0.18σ =σ 50 ()(.)dwhere I 50 is the laboratory sample diameter in mm and d is the feld-scale sample diameter in mm. Assuming the laboratory sample size is nominally 50 mm (2 in), the strength of a 1,000 mm (. in) sample will be 0.58 times the laboratory sample size. Initial StressThe initial stresses in the models were defned to closely match the current understanding of stress in the coal measures in the United States. The pre-mining vertical stress is gravity driven andis determined by the depth of the overburden. The horizontal stress is also depth dependent, but there is a tectonic component that is caused by the movement of the North American plate (Zoback and Zoback, 1989; Dolinar, 2003; Mark and Gadde, 2008). According to current understanding, the tectonic component of the horizontal stress is higher in stiff strata than in softer strata (Dolinar, 2003). In the numerical models, the pre-mining horizontal stress is calculated in each layer of rock, depending on its modulus of elasticity. The following equations are used, after Mark and Gadde (2008), to calculate the maximum and minimum horizontal stress components in MPa units:σ h 1 = 1.2σ v + 2.6 + 0.003E(5)σ h 2 = 1.2σ v + 0.0015E(6)where E is the elastic modulus of the rock and I(vis the vertical overburden stress.OVERBURDEN AND GOB MODEL CALIBRATION Calibration of the models was carried out by simulating total extraction mining of panels at various depths of cover and with various excavation spans. The model results were compared to predicted and measured subsidence profles and empirically determined stress distributions from published case studies from around the United States. Correct modeling of the subsidence profle helps to confrm that the large-scale stiffness and deformation properties of the overburden and gob are reasonable. During the calibration stage, many combinations of rock strength properties and geometric scenarios were tested. Ultimately it was found that a single set of overburden material properties and gob properties could be used to obtain satisfactory agreement between model results and feld observations for modeling the large-scale rock mass response and pillar response around full extraction panels. Overburden PropertiesThe rock strength, deformation properties, and bedding strength properties suggested for modeling large-scale coal measure rocks in the United States are presented in Table 1. These properties can be used for panel scale models, where a single element can include both intact rock and weak bedding planes. Element sizes in the overburden models typically varied between 5 and 10 m (16 and 33 ft). Figure 5 shows a typical large-scale model that was used in the calibration exercises; the models always extended up to the ground surface and rock layering was modeled down to approximately 5-m (16-ft) bed thicknesses. Model element thickness varied between about 5 and 10 m (16 and 33 ft) in the proximity of the coal seam and was sometimes larger when modeling thick beds near the ground surface.The uniaxial compressive strength shown in Table 1 is the laboratory-scale strength, which was reduced by the 0.58 factor from Equation . to simulate the large-scale strength in the models. Strength reduction owing to strain softening was achieved by reducing the rock cohesion only; the friction component of the。