外文翻译--蚁群优化冲压激光组合机床的最佳工艺设计方法
机械专业外文文献翻译
翻译部分英文原文High-speed machining and demand for the development ofHigh-speed machining is contemporary advanced manufacturing technology an important component of the high-efficiency, High-precision and high surface quality, and other features. This article presents the technical definition of the current state of development of China's application fields and the demand situation.High-speed machining is oriented to the 21st century a new high-tech, high-efficiency, High-precision and high surface quality as a basic feature, in the automobile industry, aerospace, Die Manufacturing and instrumentation industries gained increasingly widespread application, and has made significant technical and economic benefits. contemporary advanced manufacturing technology an important component part.HSC is to achieve high efficiency of the core technology manufacturers, intensive processes and equipment packaged so that it has a high production efficiency. It can be said that the high-speed machining is an increase in the quantity of equipment significantly improve processing efficiency essential to the technology. High-speed machining is the major advantages : improve production efficiency, improve accuracy and reduce the processing of cutting resistance.The high-speed machining of meaning, at present there is no uniform understanding, there are generally several points as follows : high cutting speed. usually faster than that of their normal cutting 5 -10 times; machine tool spindle speed high, generally spindle speed in -20000r/min above 10,000 for high-speed cutting; Feed at high velocity, usually 15 -50m/min up to 90m/min; For different cutting materials and the wiring used the tool material, high-speed cutting the meaning is not necessarily the same; Cutting process, bladed through frequency (Tooth Passing Frequency) closer to the "machine-tool - Workpiece "system the dominant natural frequency (Dominant Natural Frequency), can be considered to be high-speed cutting. Visibility high-speed machining is a comprehensive concept.1992. Germany, the Darmstadt University of Technology, Professor H. Schulz in the 52th on the increase of high-speed cutting for the concept and the scope, as shown in Figure 1. Think different cutting targets, shown in the figure of the transition area (Transition), to be what is commonly called the high-speed cutting, This is also the time of metal cutting process related to the technical staff are looking forward to, or is expected to achieve the cutting speed.High-speed machining of machine tools, knives and cutting process, and other aspects specific requirements. Several were from the following aspects : high-speed machining technology development status and trends.At this stage, in order to achieve high-speed machining, general wiring with high flexibility of high-speed CNC machine tools, machining centers, By using a dedicated high-speed milling, drilling. These equipment in common is : We must also have high-speed and high-speed spindle system feeding system, Cutting can be achieved in high-speed process. High-speed cutting with the traditional cutting the biggest difference is that "Machine-tool-workpiece" the dynamic characteristics of cutting performance is stronger influence. In the system, the machine spindle stiffness, grip or form, a long knife set, spindle Broach, torque tool set, Performance high-speed impact are important factors.In the high-speed cutting, material removal rate (Metal Removal Rate, MRR), unit time that the material was removed volume, usually based on the "machine-tool-workpiece" whether Processing System "chatter." Therefore, in order to satisfy the high-speed machining needs, we must first improve the static and dynamic stiffness of machine spindle is particularly the stiffness characteristics. HSC reason at this stage to be successful, a very crucial factor is the dynamic characteristics of the master and processing capability.In order to better describe the machine spindle stiffness characteristics of the project presented new dimensionless parameter - DN value, used for the evaluation of the machine tool spindle structure on the high-speed machining of adaptability. DN value of the so-called "axis diameter per minute speed with the product." The newly developed spindle machining center DN values have been great over one million. To reduce the weight bearing, but also with an array of steel products than to the much more light ceramic ball bearings; Bearing Lubrication most impressive manner mixed with oil lubrication methods. In the field of high-speed machining. have air bearings and the development of magnetic bearings and magnetic bearings and air bearings combined constitute the magnetic gas / air mixing spindle.Feed the machine sector, high-speed machining used in the feed drive is usually larger lead, multiple high-speed ball screw and ball array of small-diameter silicon nitride (Si3N4) ceramic ball, to reduce its centrifugal and gyroscopic torque; By using hollow-cooling technology to reduce operating at high speed ball screw as temperature generated by the friction between the lead screw and thermal deformation.In recent years, the use of linear motor-driven high-speed system of up to'' Such feed system has removed the motor from workstations to Slide in the middle of all mechanical transmission links, Implementation of Machine Tool Feed System of zero transmission. Because no linear motor rotating components, from the role of centrifugal force, can greatly increase the feed rate. Linear Motor Another major advantage of the trip is unrestricted. The linear motor is a very time for a continuous machine shop in possession of the bed. Resurfacing of the very meeting where avery early stage movement can go, but the whole system of up to the stiffness without any influence. By using high-speed screw, or linear motor can greatly enhance machine system of up to the rapid response. The maximum acceleration linear motors up to 2-10G (G for the acceleration of gravity), the largest feed rate of up to 60 -200m/min or higher.2002 world-renowned Shanghai Pudong maglev train project of maglev track steel processing, Using the Shenyang Machine Tool Group Holdings Limited McNair friendship company production plants into extra-long high-speed system for large-scale processing centers achieve . The machine feeding system for the linear guide and rack gear drive, the largest table feed rate of 60 m / min, Quick trip of 100 m / min, 2 g acceleration, maximum speed spindle 20000 r / min, the main motor power 80 kW. X-axis distance of up to 30 m, 25 m cutting long maglev track steel error is less than 0.15 mm. Maglev trains for the smooth completion of the project provided a strong guarantee for technologyIn addition, the campaign machine performance will also directly affect the processing efficiency and accuracy of processing. Mold and the free surface of high-speed machining, the main wiring with small cut deep into methods for processing. Machine requirements in the feed rate conditions, should have high-precision positioning functions andhigh-precision interpolation function, especially high-precision arc interpolation. Arc processing is to adopt legislation or thread milling cutter mold or machining parts, the essential processing methods. Cutting Tools Tool Material developmenthigh-speed cutting and technological development of the history, tool material is continuous progress of history. The representation ofhigh-speed cutting tool material is cubic boron nitride (CBN). Face Milling Cutter use of CBN, its cutting speed can be as high as 5000 m / min, mainly for the gray cast iron machining. Polycrystalline diamond (PCD) has been described as a tool of the 21st century tool, It is particularly applicable to the cutting aluminum alloy containing silica material, which is light weight metal materials, high strength, widely used in the automobile, motorcycle engine, electronic devices shell, the base, and so on. At present, the use of polycrystalline diamond cutter Face Milling alloy, 5000m/min the cutting speed has reached a practical level. In addition ceramic tool also applies to gray iron of high-speed machining; Tool Coating : CBN and diamond cutter, despite good high-speed performance, but the cost is relatively high. Using the coating technology to make cutting tool is the low price, with excellent mechanical properties, which can effectively reduce the cost. Now high-speed processing of milling cutter, with most of the wiring between the Ti-A1-N composite technology for the way of multi-processing, If present in the non-ferrous metal or alloy material dry cutting, DLC (Diamond Like Carbon) coating on thecutter was of great concern. It is expected that the market outlook is very significant;Tool clamping system : Tool clamping system to support high-speed cutting is an important technology, Currently the most widely used is a two-faced tool clamping system. Has been formally invested as a commodity market at the same clamping tool system are : HSK, KM, Bigplus. NC5, AHO systems. In the high-speed machining, tool and fixture rotary performance of the balance not only affects the precision machining and tool life. it will also affect the life of machine tools. So, the choice of tool system, it should be a balanced selection of good products.Process ParametersCutting speed of high-speed processing of conventional shear velocity of about 10 times. For every tooth cutter feed rate remained basically unchanged, to guarantee parts machining precision, surface quality and durability of the tool, Feed volume will also be a corresponding increase about 10 times, reaching 60 m / min, Some even as high as 120 m / min. Therefore, high-speed machining is usually preclude the use of high-speed, feed and depth of cut small cutting parameters. Due to the high-speed machining cutting cushion tend to be small, the formation of very thin chip light, Cutting put the heat away quickly; If the wiring using a new thermal stability better tool materials and coatings, Using the dry cutting process for high-speed machining is the ideal technology program. High-speed machining field of applicationFlexible efficient production lineTo adapt to the needs of new models, auto body panel molds andresin-prevention block the forming die. must shorten the production cycle and reduce the cost of production and, therefore, we must make great efforts to promote the production of high-speed die in the process. SAIC affiliated with the company that : Compared to the past, finishing, further precision; the same time, the surface roughness must be met, the bending of precision, this should be subject to appropriate intensive manual processing. Due to the extremely high cutting speed, and the last finishing processes, the processing cycle should be greatly reduced. To play for machining centers and boring and milling machining center category represented by the high-speed machining technology and automatic tool change function of distinctions Potential to improve processing efficiency, the processing of complex parts used to be concentrated as much as possible the wiring process, that is a fixture in achieving multiple processes centralized processing and dilute the traditional cars, milling, boring, Thread processing different cutting the limits of technology, equipment and give full play to the high-speed cutting tool function, NC is currently raising machine efficiency and speed up product development in an effective way. Therefore, the proposed multi-purpose tool of the new requirements call for a tool to complete different partsof the machining processes, ATC reduce the number of ATC to save time, to reduce the quantity and tool inventory, and management to reduce production costs. More commonly used in a multifunctional Tool, milling, boring and milling, drilling milling, drilling-milling thread-range tool. At the same time, mass production line, against the use of technology requires the development of special tools, tool or a smart composite tool, improve processing efficiency and accuracy and reduced investment. In the high-speed cutting conditions, and some special tools can be part of the processing time to the original 1 / 10 below, results are quite remarkable. HSC has a lot of advantages such as : a large number of materials required resection of the workpiece with ultrafine, thin structure of the workpiece, Traditionally, the need to spend very long hours for processing mobile workpiece and the design of rapid change, short product life cycle of the workpiece, able to demonstrate high-speed cutting brought advantages.中文译文高速切削加工的发展及需求高速切削加工是当代先进制造技术的重要组成部分，拥有高效率、高精度及高表面质量等特征。
用蚁群算法求解Job-Shop问题的机器分解方法
ｆｒｓ ｌｉｇＪｂＳ ｏ ｃ ｅ ｕｉｇＰ ｏ ｌｍ．Ａ ｅ ｓａｅｔａ ｓｔ ｎｐｏ ａ ｉｔ ｕｅａ ｄａｍｅｈ ｄ ｏ ｉｉｇｔｅ ａ ｔ ｔｒ ｏ ｏｖｎ ｏ ｈ ｐ Ｓ ｈ ｄ ｌ ｒｂｅ ｎ ｎｗ ｔｔ ｒｎ ｉｏ ｒｂ ｂｌｙ ｒｌ ｎ ｔｏ ｆｇｖｎ ｈ ｎ ａｔ ｉ ｉ ｓ
ｏｈ ｒｍａ ｈ ｎ ｓｃ ｎ ｔ ｃｓｔ ｅ ｓ ｈ ｄ ｌ ｇ ｒ ｓ ｌ ｔ ｉ ｔ ．Ｔ ｉ ｔ ｏ ｍｐ ｏ ｅ ｅ ｅ ｃｅ ｃ ｆ ｔｃ ｌｎ ｇ ｒ ｈ ｔ ｅ ｃ ｉ ｅ ｏ ｓ ｕ ｔ ｃ ｅ ｕ ｉ ｅ ｕ ｔ ｈ ｓ ｉ ｒ ｈ ｎ ｍｅ ｈ ｓｍｅ ｈ ｄ ｉ ｒ ｖ ｓｔ ｆ ｉｎ ｙ ｏ ｏｏ ｙ ａ ｏ ｔ ｍ ｈ ｉ ｎ ａ ｌ ｉ
摘要 ： 针对生产调度中 Ｊｂ Ｓｏ 问题 ， ｏ — ｈｐ 蚁群算法在求解 Ｊｂ Ｓｏ ｏ — ｈｐ问题时有计算量大的缺点 ， 为了提高求解效率 ， 机器分 将 解方法引入蚁群算法。机器分解方法在每次迭代中蚂蚁仅在子图中构造部分解 ， 并与上次迭代 中其他机器上 的顺 序共同构 成本次解 ， 提高了蚁 群算法求解 Ｊ Ｓｏ 问题的效 率。并且在算法 中提 出了一 种新的状态转 移规 则和设计 了蚂 蚁起点位 ｏ ｈｐ ｂ—
基于深度学习的数控加工设备工艺参数优化方法研究
基于深度学习的数控加工设备工艺参数优化方法研究摘要：本文旨在探索深度学习技术在数控加工设备工艺参数优化中的应用。
传统数控加工方法工艺参数选择存在不确定性，影响生产效率。
我们提出一种基于深度学习的工艺参数优化方法，结合卷积神经网络（CNN）和递归神经网络（RNN）。
该方法自动学习和识别工艺参数模式，提高加工效率和质量。
实验结果表明，该方法在不同加工任务下显著优化了加工过程。
本研究为数控加工设备的工艺参数优化提供了新途径，推动智能制造的发展。
关键词：深度学习，数控加工设备，工艺参数优化，卷积神经网络，递归神经网络一、引言数控加工设备在现代制造业中扮演着关键角色，但传统工艺参数选择方法受制于人工经验和试错方法，面临生产效率低下、资源浪费和质量不稳定等挑战。
这些问题的根本原因在于工艺参数的多样性和复杂性，难以通过传统手段精确控制。
为应对这一问题，本研究旨在探讨如何利用深度学习技术来优化数控加工设备的工艺参数。
我们的研究目的在于开发一种基于深度学习的方法，使其能够自动学习和识别工艺参数模式，从而实现高效的参数优化。
通过这一研究，我们的目标是提高生产效率、资源利用率和产品质量，促进智能制造的发展。
深度学习的应用将为制造业带来新的机遇，为工艺参数的自动化优化打开新的可能性，对提升竞争力、降低成本和推动技术创新具有深远的意义。
二、深度学习技术及其应用2.1 深度学习基础深度学习，作为一种机器学习技术，其核心在于构建多层神经网络，模拟人脑神经元的工作方式。
通过大规模数据集的训练，深度学习能够自动学习特征，并实现高级模式的识别和预测。
其中，卷积神经网络（CNN）和递归神经网络（RNN）等结构在深度学习中扮演关键角色。
CNN被广泛用于图像识别和处理领域，而RNN在处理序列数据，如自然语言处理中具有显著优势。
2.2 深度学习在制造业中的应用深度学习技术的应用在制造业中展现了广阔前景。
在数控加工设备领域，深度学习为工艺参数的优化提供了一种全新的方法。
机床大讲堂第175讲——机床床身结构综合优化设计技术（下）
机床大讲堂第175讲——机床床身结构综合优化设计技术（下）《制造技术与机床》杂志1951年创刊，属中文核心期刊，中国科技论文统计用刊和《中国学术期刊文摘》摘录用期刊。
[ 本文共3911字，预计阅读时间10分钟 ]机床床身结构综合优化设计技术（下）2 算例分析2.1 研究对象本案例以上海机床厂某型号的数控外圆(端面)磨床床身为研究对象，该型号床身结构如图2a所示。
机床床身由HT250铸造而成，前床身上有V-平型导轨。
床身筋板结构如图2b所示，其前床身内部分布有6块横隔板，后床身有3块横隔板和3块纵隔板组成了井字筋结构，床身外部框架厚度为25 mm，内部筋板厚度为25 mm。
床身底面由10块垫铁支撑，垫铁位置如图3黑色点所示，前床身平导轨下方部分均匀分布4个垫铁，V轨下方在角点上有两个垫铁，后床身的垫铁则分布于四个角点位置。
工况取工作台处于左中右三个位置时这三种工况处理。
2.2 设计过程2.2.1 机床床身垫铁位置优化设计如图2a所示床身结构图，依据床身材料设定其有限元模型的弹性模量、泊松比和密度;基于整机载荷传递图确定载荷边界条件，分解出床身承受的载荷位置和大小，根据工作台位置将其分为左、中、右3个工况对其有限元模型施加载荷约束。
依据机床床身实际安装位置，确定垫铁位置优化设计区域，如图3所示垫铁设计区域，几何尺寸与原模型尺寸相同。
建立原结构的无筋板框架结构模型，然后采用壳单元划分有限元网格，四角垫铁位置约束Y方向移动自由度及X、Y、Z方向转动自由度，其余垫铁位置约束Y方向移动自由度，并根据实际载荷工况对模型施加载荷约束。
根据式(1)建立优化模型，采用多岛遗传算法对图3的设计模型进行优化设计，得到如图4所示优化后垫铁位置。
2.2.2 筋板布局优化垫铁位置确定之后，要对床身的筋板布局进行优化设计。
如图5所示黑色部分为导轨部分是非设计区域，灰色部分为筋板分布的设计区域，外形几何尺寸与原模型几何尺寸相同。
机械设计制造及其自动化 外文翻译 外文文献 英文文献 液压支架的最优化设计
英文原文中文译文液压支架的最优化设计摘要：本文介绍了从两组不同参数的采矿工程所使用的液压支架（如图1）中选优的流程。
这种流程建立在一定的数学模型之上。
第一步，寻找四连杆机构的最理想的结构参数以便确保支架的理想的运动轨迹有最小的横向位移。
第二步，计算出四连杆有最理想的参数时的最大误差，以便得出最理想的、最满意的液压支架。
图1 液压支架关键词：四连杆机构；优化设计；精确设计；模糊设计；误差1.前言：设计者的目的时寻找机械系统的最优设计。
导致的结果是一个系统所选择的参数是最优的。
一个数学函数伴随着一个合适的系统的数学模型的出现而出现。
当然这数学函数建立在这种类型的系统上。
有了这种数学函数模型，加上一台好的计算机的支持，一定能找出系统最优的参数。
Harl描述的液压支架是斯洛文尼亚的Velenje矿场的采煤设备的一个组成部分，它用来支护采煤工作面的巷道。
它由两组四连杆机构组成，如图2所示.四连杆机构AEDB控制绞结点C 的运动轨迹，四连杆机构FEDG 通过液压泵来驱动液压支架。
图2中，支架的运动，确切的说，支架上绞结点C 点竖向的双纽线的运动轨迹要求横向位移最小。
如果不是这种情况，液压支架将不能很好的工作，因为支架工作在运动的地层上。
实验室测试了一液压支架的原型。
支架表现出大的双纽线位移，这种双纽线位移的方式回见少支架的承受能力。
因此，重新设计很有必要。
如果允许的话，这会减少支架的承受能力。
因此，重新设计很有必要。
如果允许的话，这种设计还可以在最少的成本上下文章。
它能决定去怎样寻找最主要的图2 两四连杆机构四连杆机构数学模型AEDB 的最有问题的参数421,,a a a 。
否则的话这将有必要在最小的机构AEDB 改变这种设计方案。
上面所罗列出的所有问题的解决方案将告诉我们关于最理想的液压支架的答案。
真正的答案将是不同的，因为系统有各种不同的参数的误差，那就是为什么在数学模型的帮助下，参数421,,a a a 允许的最大的误差将被计算出来。
冲压模具的排样优化系统
状，如矩形或凸多边形，然后嵌套。
Dagli 和Tatoglu [ 5 ]提出了一个启发式的方法，是用毛坯的形状来决定不同优先级规则的配置。
Nee [ 6,7 ]和Nee 和Foong [ 8 ]已经开发了一个实验方案，其中包括算法和评价函数。
该算法被设计用来执行对成对聚类的全面搜索，将它的形状增量旋转180°，直到所有可能的方面进行配对。
该算法包括例程来执行坐标旋转、平移变换，同时检测任何重叠的形状。
Ismail 和Hon [ 9 ]提出了一种基于边缘数组形式的边缘信息提取算法，这种算法是用识别形状可能发展的方向来获得更好的配对方案。
Lin 和 Hsu [ 10 ]引入了优化布局方法来获得的双行排样，并用AutoLisp 排样图显示在屏幕上。
Tang 和Rajesham [ 11 ]提出了一种算法，排样模型被近似为一个有充分大量角构成的多边形。
该算法是在微元流动方向考虑的，特别是与弯曲模式。
Singh 和Sekhon [ 12 ]提出的一种基于计算机的测量矩阵的方法。
Cheok 和Foong [ 13 ]开发系统IAPDie 系统，它被旋转的一部分是通过一系列的选择角度，且将其每个角相同的部分向前推进。
Choiet 等其他工作者[ 14 ]开发了一套基于AutoCAD 的冲裁不规则形状钣金产品的系统。
产品利用率参照以倾斜2°角间隔变化的增量来计算。
似乎所有的算法开发都预计将提高毛坯排样自动化的能力，但却很少有人关注如何建立一个实用的排样。
这不仅是一个合理的算法优化的系统需要考虑的，也是实践制造的要求。
基于以上事实，本文首先介绍了排样优化的基本原则，然后提出了一般结构实际排样系统。
最后，对一些关键技术，如毛坯形状补偿算法、排样参数的计算和调整排样方案进行了详细介绍。
2.排样的基本原则优化一个排样可以简单地描述为一个需要冲孔或冲裁过程的外轮廓零件，但如果冲裁件需要移动或弯曲边缘，这意味着的外部轮廓的展开部分总是包含了自由切削区。
基于智能算法的机械参数优化设计
基于智能算法的机械参数优化设计引言：随着科技的不断发展，智能算法在各个领域的应用也变得越来越广泛。
在机械设计领域，传统的人工参数优化设计方法已经不能满足日益复杂和多样化的需求。
因此，基于智能算法的机械参数优化设计成为了一种有效的解决方案。
本文将介绍智能算法在机械参数优化设计中的应用，并讨论其优势和挑战。
一、智能算法在机械参数优化设计中的应用1.1 遗传算法遗传算法是一种模拟自然界生物进化过程的优化算法。
它通过模拟生物的遗传操作（选择、交叉和变异）来搜索最优解。
在机械参数优化设计中，遗传算法可以用于寻找最佳的参数组合，以实现特定的设计目标。
例如，在机械结构优化设计中，通过遗传算法可以找到最优的结构参数，使得结构的强度和刚度达到最佳平衡。
1.2 粒子群算法粒子群算法是一种模拟鸟群觅食过程的优化算法。
在粒子群算法中，每个粒子代表一个候选解，粒子通过学习其他粒子的经验来不断更新自己的位置。
在机械参数优化设计中，粒子群算法可以用于搜索参数空间中的最优解。
例如，在机械传动系统的优化设计中，通过粒子群算法可以找到最佳的传动比例，以达到最佳的运动效果和能量利用率。
1.3 蚁群算法蚁群算法是一种模拟蚂蚁觅食行为的优化算法。
在蚁群算法中，蚂蚁通过释放信息素来通信并引导其他蚂蚁选择路径。
在机械参数优化设计中，蚁群算法可以用于寻找最优的参数组合。
例如，在机械加工过程的优化设计中，通过蚁群算法可以找到最佳的切削参数，以提高工件加工质量和生产效率。
二、智能算法在机械参数优化设计中的优势2.1 高效性智能算法在机械参数优化设计中具有高效的特点。
与传统的人工参数优化设计方法相比，智能算法可以通过并行计算和全局搜索策略快速找到最优解。
这大大缩短了设计时间，提高了设计效率。
2.2 自适应性智能算法在机械参数优化设计中具有自适应的特点。
在设计过程中，智能算法可以不断学习和自我调整，以适应不同的设计需求和约束条件。
这使得智能算法在复杂和多样化的设计问题中表现出色。
外文翻译
一个实用的冲压模具排样优化系统的开发Z. Zhao ，Y. Peng中国上海交通大学摘要：排样是冲压模具设计中的一个重要工序。
板料冲压的主要成本之一是材料成本，因此节省材料的本质是最大限度的减少废料，这不仅体现在板料冲压过程中，而且也体现在整个生产过程中。
本文旨讨论通过使用AutoCAD的ObjectARX开发工具，为冲压模具设计开发一个实用的排样优化系统。
这个排样优化系统的基本原理还是被首次描述，并且也提出了此系统的一般结构。
该系统不仅是一个排样算法的计算问题，还要一个要充分考虑制造要求和用户操作的问题。
最后，以一个毛坯形状补偿法去解决补偿曲面的自交问题，这种方法是对传统的“一步转换”法的一种改良，它可以协调排样过程中的效率与精度问题。
关键词：排样；优化；冲压模具。
1.引言冲压工艺是制造业中发展最早的工业技术之一。
冲压工艺一直在不断的发展，冲压产品也是随处可见。
排样是冲压模具设计中最重要的工序之一，它可以被定义为冲压毛坯在板料和条料总面积中所占的最大比例。
排样的目的是提高材料利用率和减少废品的数量，以满足冲压工艺要求。
板料冲压的主要成本之一是材料成本，因此节省材料的本质是最大限度的减少废料，这不仅体现在板料冲压过程中，而且也体现在整个生产过程中。
此外，排样的结果是条料设计和冲压模具设计如模板设计的基础。
在过去，排样完全是靠手工操作的，它高度依赖于设计师的经验和技术。
当然，这种方法经历了一个长时间的经验积累，它解决了许多工艺设计中的实际问题，这是从书本和手册中所得不到的。
为了提高设计工作者的设计质量和缩短设计周期，开发一款计算机辅助设计软件是很有必要也是很实用的。
基于这种需求，本文主要是讨论用AutoCAD的ObjectARX开发工具为冲压模具开发一个实用的排样优化系统。
为板材提供了三种方案，被描述为数学建模过程的排样算法，已经被很多工人推荐使用，并且被证实在提高材料的最大利用率方面具有很大的潜力。
改进蚁群算法在YKK系列中型高压电机优化设计中的应用
电力技术
改进蚁群算法在 YKK 系列中型高压电机 优化设计中的应用
贾荣生 （杭州新恒力电机制造有限公司 , 杭州 310024）
摘 要：在工业领域当中，则主打高效电机，通过对电机进行优化设计以有效提升其工作效率、降低工作能耗。在此基础之上，本文将通过对 蚁群算法进行改进，并简要分析改进蚁群算法在 YKK 系列中型高压电机优化设计中的应用。 关键词：蚁群算法；高压电机；优化设计；应用 DOI:10.16640/ki.37-1222/t.2017.13.149
蚂蚁的转移概率。在这一公式当中城市 i 与 j 在 t 时刻信息搜索下 的信息素强度用 表示，作为两个参数 α 和 β 的值分别大于零，而 城市 i 与 j 的距离倒数则用 表示，其也被看做是启发信息之一。下一 步蚂蚁将选择的城市则用 allowed k = {1,2,3,⋅ ⋅ ⋅, n − 1} 进行表示，在经过一 定时间之后，信息将不断更新，以往信息将慢慢消失，此时使用 1 − ρ 代表信息消失的程度，蚂蚁最后将经过 n 个时刻完成一次循环。通过 运用公式：
1 蚁群算法及其改进
蚂蚁算法即蚁群算法，简单来说就是一种在图中进行优化路径找寻 的机率型算法。如果假设在图中共有 n 个城市，在转移概率的影响之 下每一只蚂蚁将随机从城市 i 向相邻城市 j 进行转移，则可以用公式表示
因子用 Ri 表示，其会根据具体的违背程度进行不断变化 [2]。 （3）信息素矩阵的构建。当蚂蚁从原来的第 i 行变量进行第 j 行 变量期望度选择时，同样可以使用矩阵的形式表示信息素 ，并且信 息素 和变量矩阵相互对应。 （4）启发式信息。在每一条路径当中，信息量受到的重视程度 均通过 α 值的具体大小进行判断，如果 α 值非常大，则搜索会在短时 间内出现深陷局部最小点的情况，因此本文将 α 值设定为 1，即可有 效避免这一问题的发生。而启发式信息受到的重视程度则通过 β 值的 大小进行判断，β 值越大则越能代表启发式信息受重视。 （5）构建解。通过利用相关公式完成随机概率的计算，此时， 蚂蚁能够从其尚未访问和搜索过的变量当中进行下一变量的选择，并 按照此步骤逐渐选择每一个优化变量，在利用接口将选择的优化变量 转化为设计变量之后，将其放入至主程序当中，从而通过电磁核算的 方式精确、科学地完成评估优化设计电机方案的工作。 （6）信息素的更新与检验。在进行信息素矩阵更新的过程当中 可以通过使用公式： 以及
液压专业毕业设计外文翻译(有译文、外文文献)值得收藏哦!
外文原文：The Analysis of Cavitation Problems in the Axial Piston Pumpshu WangEaton Corporation,14615 Lone Oak Road,Eden Prairie, MN 55344This paper discusses and analyzes the control volume of a piston bore constrained by the valve plate in axial piston pumps. The vacuum within the piston bore caused by the rise volume needs to be compensated by the flow; otherwise, the low pressure may cause the cavitations and aerations. In the research, the valve plate geometry can be optimized by some analytical limitations to prevent the piston pressure below the vapor pressure. The limitations provide the design guide of the timings and overlap areas between valve plate ports and barrel kidneys to consider the cavitations and aerations. _DOI: 10.1115/1.4002058_Keywords: cavitation , optimization, valve plate, pressure undershoots1 IntroductionIn hydrostatic machines, cavitations mean that cavities or bubbles form in the hydraulic liquid at the low pressure and collapse at the high pressure region, which causes noise, vibration, and less efficiency.Cavitations are undesirable in the pump since the shock waves formed by collapsed may be strong enough to damage components. The hydraulic fluid will vaporize when its pressure becomes too low or when the temperature is too high. In practice, a number of approaches are mostly used to deal with the problems: (1) raise the liquid level in the tank, (2) pressurize the tank, (3) booster the inlet pressure of the pump, (4) lower the pumping fluid temperature, and (5) design deliberately the pump itself.Many research efforts have been made on cavitation phenomena in hydraulic machine designs. The cavitation is classified into two types in piston pumps: trapping phenomenon related one (which can be preventedby the proper design of the valve plate) and the one observed on the layers after the contraction or enlargement of flow passages (caused by rotating group designs) in Ref. (1). The relationship between the cavitation and the measured cylinder pressure is addressed in this study. Edge and Darling (2) reported an experimental study of the cylinder pressure within an axial piston pump. The inclusion of fluid momentum effects and cavitations within the cylinder bore are predicted at both high speed and high load conditions. Another study in Ref. (3) provides an overview of hydraulic fluid impacting on the inlet condition and cavitation potential. It indicates that physical properties (such as vapor pressure, viscosity, density, and bulk modulus) are vital to properly evaluate the effects on lubrication and cavitation. A homogeneous cavitation model based on the thermodynamic properties of the liquid and steam is used to understand the basic physical phenomena of mass flow reduction and wave motion influences in the hydraulic tools and injection systems (4). Dular et al. (5, 6) developed an expert system for monitoring and control of cavitations in hydraulic machines and investigated the possibility of cavitation erosion by using the computational fluid dynamics (CFD) tools. The erosion effects of cavitations have been measured and validated by a simple single hydrofoil configuration in a cavitation tunnel. It is assumed that the severe erosion is often due to the repeated collapse of the traveling vortex generated by a leading edge cavity in Ref. (7). Then, the cavitation erosion intensity may be scaled by a simple set of flow parameters: the upstream velocity, the Strouhal number, the cavity length, and the pressure. A new cavitation erosion device, called vortex cavitation generator, is introduced to comparatively study various erosion situations (8).More previous research has been concentrated on the valve plate designs, piston, and pump pressure dynamics that can be associated with cavitations in axial piston pumps. The control volume approach and instantaneous flows (leakage) are profoundly studied in Ref. [9]. Berta et al. [10] used the finite volume concept to develop a mathematical model in which the effects of port plate relief grooves have been modeled andthe gaseous cavitation is considered in a simplified manner. An improved model is proposed in Ref. [11] and validated by experimental results. The model may analyze the cylinder pressure and flow ripples influenced by port plate and relief groove design. Manring compared principal advantages of various valve plate slots (i.e., the slots with constant, linearly varying, and quadratic varying areas) in axial piston pumps [12]. Four different numerical models are focused on the characteristics of hydraulic fluid, and cavitations are taken into account in different ways to assist the reduction in flow oscillations [13].The experiences of piston pump developments show that the optimization of the cavitations/aerations shall include the following issues: occurring cavitation and air release, pump acoustics caused by the induced noises, maximal amplitudes of pressure fluctuations, rotational torque progression, etc. However, the aim of this study is to modify the valve plate design to prevent cavitation erosions caused by collapsing steam or air bubbles on the walls of axial pump components. In contrastto literature studies, the research focuses on the development of analytical relationship between the valve plate geometrics and cavitations. The optimization method is applied to analyze the pressure undershoots compared with the saturated vapor pressure within the piston bore.The appropriate design of instantaneous flow areas between the valveplate and barrel kidney can be decided consequently.2 The Axial Piston Pump and Valve PlateThe typical schematic of the design of the axis piston pump is shown in Fig. 1. The shaft offset e is designed in this case to generate stroking containment moments for reducing cost purposes.The variation between the pivot center of the slipper and swash rotating center is shown as a. The swash angle αis the variable that determines the amount of fluid pumped per shaft revolution. In Fig. 1, the n th piston-slipper assembly is located at the angle ofθ. The displacement of the n thnpiston-slipper assembly along the x-axis can be written asx n= R tan（α）sin（θ）+ a sec（α）+ e tan(α) (1)nwhere R is the pitch radius of the rotating group.Then, the instantaneous velocity of the n th piston isx˙n = R 2sec ()αsin （n θ）α+ R tan （α）cos （n θ）ω+ R 2sec ()αsin （α）α + e 2sec ()αα (2)where the shaft rotating speed of the pump is ω=d n θ / dt .The valve plate is the most significant device to constraint flow inpiston pumps. The geometry of intake/discharge ports on the valve plateand its instantaneous relative positions with respect to barrel kidneys areusually referred to the valve plate timing. The ports of the valve plateoverlap with each barrel kidneys to construct a flow area or passage,which confines the fluid dynamics of the pump. In Fig. 2, the timingangles of the discharge and intake ports on the valve plate are listed as(,)T i d δ and (,)B i d δ. The opening angle of the barrel kidney is referred to asϕ. In some designs, there exists a simultaneous overlap between thebarrel kidney and intake/discharge slots at the locations of the top deadcenter (TDC) or bottom dead center (BDC) on the valve plate on whichthe overlap area appears together referred to as “cross -porting” in thepump design engineering. The cross-porting communicates the dischargeand intake ports, which may usually lower the volumetric efficiency. Thetrapped-volume design is compared with the design of the cross-porting,and it can achieve better efficiency 14]. However, the cross-porting isFig. 1 The typical axis piston pumpcommonly used to benefit the noise issue and pump stability in practice.3 The Control Volume of a Piston BoreIn the piston pump, the fluid within one piston is embraced by the piston bore, cylinder barrel, slipper, valve plate, and swash plate shown in Fig. 3. There exist some types of slip flow by virtue of relativeFig. 2 Timing of the valve platemotions and clearances between thos e components. Within the control volume of each piston bore, the instantaneous mass is calculated asM= n V(3)nwhere ρ and n V are the instantaneous density and volumesuch that themass time rate of change can be given asFig. 3 The control volume of the piston boren n n dM dV d V dt dt dtρρ=+ (4) where d n V is the varying of the volume.Based on the conservation equation, the mass rate in the control volume isn n dM q dtρ= (5)where n q is the instantaneous flow rate in and out of one piston. From the definition of the bulk modulus,n dP d dt dtρρβ= (6) where Pn is the instantaneous pressure within the piston bore. Substituting Eqs. (5) and (6) into Eq. (4) yields(?)n n n n n ndP q dV d V w d βθθ=- (7) where the shaft speed of the pump is n d dtθω=. The instantaneous volume of one piston bore can be calculated by using Eq. (1) asn V = 0V + P A [R tan （α）sin （n θ）+ a sec （α） + e tan(α) ] (8)where P A is the piston sectional area and 0V is the volume of eachpiston, which has zero displacement along the x-axis (when n θ=0, π).The volume rate of change can be calculated at the certain swash angle, i.e., α =0, such thattan cos n p n ndV A R d αθθ=（）（） (9) in which it is noted that the piston bore volume increases or decreaseswith respect to the rotating angle of n θ.Substituting Eqs. (8) and (9) into Eq. (7) yields0[tan()cos()] [tan sin sec tan() ]n P n n n p n q A R dP d V A R a e βαθωθαθαα-=-++（）（）（）(10)4 Optimal DesignsTo find the extrema of pressure overshoots and undershoots in the control volume of piston bores, the optimization method can be used in Eq. (10). In a nonlinear function, reaching global maxima and minima is usually the goal of optimization. If the function is continuous on a closed interval, global maxima and minima exist. Furthermore, the global maximum (or minimum) either must be a local maximum (or minimum) in the interior of the domain or must lie on the boundary of the domain. So, the method of finding a global maximum (or minimum) is to detect all the local maxima (or minima) in the interior, evaluate the maxima (or minima) points on the boundary, and select the biggest (or smallest) one. Local maximum or local minimum can be searched by using the first derivative test that the potential extrema of a function f( · ), with derivative ()f ', can solve the equation at the critical points of ()f '=0 [15].The pressure of control volumes in the piston bore may be found as either a minimum or maximum value as dP/ dt=0. Thus, letting the left side of Eq. (10) be equal to zero yieldstan()cos()0n p n q A R ωαθ-= (11)In a piston bore, the quantity of n q offsets the volume varying and thendecreases the overshoots and undershoots of the piston pressure. In this study, the most interesting are undershoots of the pressure, which may fall below the vapor pressure or gas desorption pressure to cause cavitations. The term oftan()cos()p n A R ωαθ in Eq. (11) has the positive value in the range of intake ports (22ππθ-≤≤), shown in Fig. 2, which means that the piston volume arises. Therefore, the piston needs the sufficient flow in; otherwise, the pressure may drop.In the piston, the flow of n q may get through in a few scenariosshown in Fig. 3: (I) the clearance between the valve plate and cylinder barrel, (II) the clearance between the cylinder bore and piston, (III) the clearance between the piston and slipper, (IV) the clearance between the slipper and swash plate, and (V) the overlapping area between the barrel kidney and valve plate ports. As pumps operate stably, the flows in the as laminar flows, which can be calculated as [16]312IV k k Ln i I k h q p L ωμ==∑ (12)where k h is the height of the clearance, k L is the passage length,scenarios I –IV mostly have low Reynolds numbers and can be regarded k ω is the width of the clearance (note that in the scenario II, k ω =2π· r, in which r is the piston radius), and p is the pressure drop defined in the intake ports as p =c p -n p (13)where c p is the case pressure of the pump. The fluid films through theabove clearances were extensively investigated in previous research. The effects of the main related dimensions of pump and the operating conditions on the film are numerically clarified inRefs. [17,18]. The dynamic behavior of slipper pads and the clearance between the slipper and swash plate can be referred to Refs. [19,20]. Manring et al. [21,22] investigated the flow rate and load carrying capacity of the slipper bearing in theoretical and experimental methods under different deformation conditions. A simulation tool calledCASPAR is used to estimate the nonisothermal gap flow between the cylinder barrel and the valve plate by Huang and Ivantysynova [23]. The simulation program also considers the surface deformations to predict gap heights, frictions, etc., between the piston and barrel andbetween the swash plate and slipper. All these clearance geometrics in Eq.(12) are nonlinear and operation based, which is a complicated issue. In this study, the experimental measurements of the gap flows are preferred. If it is not possible, the worst cases of the geometrics or tolerances with empirical adjustments may be used to consider the cavitation issue, i.e., minimum gap flows.For scenario V, the flow is mostly in high velocity and can be described by using the turbulent orifice equation as((Tn d i d d q c A c A θθ= (14)where Pi and Pd are the intake and discharge pressure of the pump and ()i A θ and ()d A θ are the instantaneous overlap area between barrel kidneys and inlet/discharge ports of the valve plate individually.The areas are nonlinear functions of the rotating angle, which is defined by the geometrics of the barrel kidney, valve plate ports,silencing grooves, decompression holes, and so forth. Combining Eqs.(11) –(14), the area can be obtained as3()K IV A θ==(15)where ()A θ is the total overlap area of ()A θ=()()i d A A θλθ+, and λ is defined as=In the piston bore, the pressure varies from low tohigh while passing over the intake and discharge ports of the valve plates. It is possible that the instantaneous pressure achieves extremely low values during the intake area( 22ππθ-≤≤ shown in Fig. 2) that may be located below the vapor pressure vp p , i.e., n vp p p ≤;then cavitations canhappen. To prevent the phenomena, the total overlap area of ()A θ mightbe designed to be satisfied with30()K IV A θ=≥(16)where 0()A θ is the minimum area of 0()A θ=0()()i d A A θλθ+ and 0λis a constant that is0λ=gaseous form. The vapor pressure of any substance increases nonlinearly with temperature according to the Clausius –Clapeyron relation. With the incremental increase in temperature, the vapor pressure becomes sufficient to overcome particle attraction and make the liquid form bubbles inside the substance. For pure components, the vapor pressure can be determined by the temperature using the Antoine equation as /()10A B C T --, where T is the temperature, and A, B, and C are constants[24].As a piston traverse the intake port, the pressure varies dependent on the cosine function in Eq. (10). It is noted that there are some typical positions of the piston with respect to the intake port, the beginning and ending of overlap, i.e., TDC and BDC (/2,/2θππ=- ) and the zero displacement position (θ =0). The two situations will be discussed as follows:(1) When /2,/2θππ=-, it is not always necessary to maintain the overlap area of 0()A θ because slip flows may provide filling up for the vacuum. From Eq. (16), letting 0()A θ=0,the timing angles at the TDC and BDC may be designed as31cos ()tan()122IV c vpk k i I P k p p h A r L ωϕδωαμ--≤+∑ (17) in which the open angle of the barrel kidney is . There is nocross-porting flow with the timing in the intake port.(2) When θ =0, the function of cos θ has the maximum value, which can provide another limitation of the overlap area to prevent the low pressure undershoots suchthat 30(0)K IVA =≥ (18)where 0(0)A is the minimum overlap area of 0(0)(0)i A A =.To prevent the low piston pressure building bubbles, the vaporpressure is considered as the lower limitation for the pressure settings in Eq. (16). The overall of overlap areas then can be derived to have adesign limitation. The limitation is determined by the leakage conditions, vapor pressure, rotating speed, etc. It indicates that the higher the pumping speed, the more severe cavitation may happen, and then the designs need more overlap area to let flow in the piston bore. On the other side, the low vapor pressure of the hydraulic fluid is preferred to reduce the opportunities to reach the cavitation conditions. As a result, only the vapor pressure of the pure fluid is considered in Eqs. (16)–(18). In fact, air release starts in the higher pressure than the pure cavitation process mainly in turbulent shear layers, which occur in scenario V.Therefore, the vapor pressure might be adjusted to design the overlap area by Eq. (16) if there exists substantial trapped and dissolved air in the fluid.The laminar leakages through the clearances aforementioned are a tradeoff in the design. It is demonstrated that the more leakage from the pump case to piston may relieve cavitation problems.However, the more leakage may degrade the pump efficiency in the discharge ports. In some design cases, the maximum timing angles can be determined by Eq. (17)to not have both simultaneous overlapping and highly low pressure at the TDC and BDC.While the piston rotates to have the zero displacement, the minimum overlap area can be determined by Eq. 18 , which may assist the piston not to have the large pressure undershoots during flow intake.6 ConclusionsThe valve plate design is a critical issue in addressing the cavitation or aeration phenomena in the piston pump. This study uses the control volume method to analyze the flow, pressure, and leakages within one piston bore related to the valve plate timings. If the overlap area developed by barrel kidneys and valve plate ports is not properly designed, no sufficient flow replenishes the rise volume by the rotating movement. Therefore, the piston pressure may drop below the saturated vapor pressure of the liquid and air ingress to form the vapor bubbles. To control the damaging cavitations, the optimization approach is used to detect the lowest pressure constricted by valve plate timings. The analytical limitation of the overlap area needs to be satisfied to remain the pressure to not have large undershoots so that the system can be largely enhanced on cavitation/aeration issues.In this study, the dynamics of the piston control volume is developed by using several assumptions such as constant discharge coefficients and laminar leakages. The discharge coefficient is practically nonlinear based on the geometrics, flow number, etc. Leakage clearances of the control volume may not keep the constant height and width as well in practice due to vibrations and dynamical ripples. All these issues are complicated and very empirical and need further consideration in the future. Theresults presented in this paper can be more accurate in estimating the cavitations with these extensive studies.Nomenclature0(),()A A θθ= the total overlap area between valve plate ports and barrel kidneys 2()mmAp = piston section area 2()mmA, B, C= constantsA= offset between the piston-slipper joint and surface of the swash plate 2()mmd C = orifice discharge coefficiente= offset between the swash plate pivot and the shaft centerline of the pump 2()mmk h = the height of the clearance 2()mmk L = the passage length of the clearance 2()mmM= mass of the fluid within a single piston (kg)N= number of pistonsn = piston and slipper counter,p p = fluid pressure and pressure drop (bar)Pc= the case pressure of the pump (bar)Pd= pump discharge pressure (bar)Pi = pump intake pressure (bar)Pn = fluid pressure within the nth piston bore (bar)Pvp = the vapor pressure of the hydraulic fluid(bar)qn, qLn, qTn = the instantaneous flow rate of each piston(l/min)R = piston pitch radius 2()mmr = piston radius (mm)t =time (s)V = volume 3()mmwk = the width of the clearance (mm)x ,x ˙= piston displacement and velocity along the shaft axis (m, m/s) x y z --=Cartesian coordinates with an origin on the shaft centerline x y z '''--= Cartesian coordinates with an origin on swash plate pivot ,αα=swash plate angle and velocity (rad, rad/s)β= fluid bulk modulus (bar)δδ= timing angle of valve plates at the BDC and TDC (rad),B Tϕ= the open angle of the barrel kidney(rad)ρ= fluid density(kg/m3),θω= angular position and velocity of the rotating kit (rad, rad/s)μ=absolute viscosity(Cp),λλ= coefficients related to the pressure drop外文中文翻译：在轴向柱塞泵气蚀问题的分析本论文讨论和分析了一个柱塞孔与配流盘限制在轴向柱塞泵的控制量设计。
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毕业设计(论文)外文资料翻译系部：机械工程系专业：机械工程及自动化姓名：学号：外文出处Optimal Process Planning for a CombinedPunch-and-Laser Cutting Machine UsingAnt Colony Optimization附件： 1.外文资料翻译译文；2.外文原文。
注：请将该封面与附件装订成册。
附件1：外文资料翻译译文蚁群优化—冲压激光组合机床的最佳工艺设计方法摘要一部既能进行冲压又能进行激光切割操作的机器就是所谓的冲压激光组合机床。
这种类型的机床在市场上已经有二十年了。
尽管工序设计软件已经用于这类组合机床的设计，但是从我们搜索的结果来看，这类组合机床最优的工序设计还没有被直接研究出来。
本文提到的冲压激光组合机床的问题可通过整合知识，定量分析和数字优化等方法来解决。
这些方法又带来了下面的问题：（Ⅰ）每一个功能应该有什么样的操作，（Ⅱ）什么是最佳操作序列（工具路径）以实现最大生产效率。
蚁群优化（蚁群优化）算法被用来寻找最佳的刀具轨迹。
而且有关其灵敏度的控制参数也得到了分析。
通过研制，这种方法可以大大地提高冲压激光组合机床的工作效率。
这种方法也很容易自动化和整合生成G-代码子程序，而且与此相关的课题也在进行着研究。
关键词组合机床冲压激光组合机床金属板工序设计最优化蚁群优化1 引言现代计算机数字控制（数控）转塔式机床作为被高度广泛应用的工作机，有着快速精确地生产金属薄板和塑料部件的能力。
然而，这种转塔式机床的变化只能限定材料是通过冲压操作从工件上去除的。
当工件有很大一部分面积要去除时，或者当工件需要被分成许多独立的工件时，再或者要制造相当长或者大的直径零配件时，这只能通过一系列重复的冲压操作才能完成材料的去除。
这样的重复的去除材料的操作有效地增加冲床的多功能性。
但是，这些操作，有时，导致了不想要的结果，比如形成不清晰的轮廓，不能进行高度精确的生产，粗糙的边以及相关操作的缓慢等（克拉克和卡波恩，1980年）。
而且，当要切出的形状不是普遍的冲压工具的形状，那必须制造专用工具，但制造专用工具的成本通常都很高。
结果，许多切断或剪切操作都要通过其他机床的跟进操作来进行额外的工件处理。
这样多种机械操作的结果影响的不仅是生产效率还有生产质量和成本。
上述所讲的原因给了所谓的冲压激光组合机床（克拉克和卡波恩，1980年）或者叫复式机床（Katayama,1989年和a.b.xie等人，2001年）或者组合式冲压和激光切割机（Klingel和Doettling 2000年）。
在这篇文章里，这种机器被叫做冲压激光组合机床。
在1980年，第一台冲压激光组合机床被发明了（克拉克和罗兰，1980年），后来，人们又申请了一系列的有关克服其振动干扰的问题的专利（Bredow 1982年,Katayama 1989年,Klingel和Doettling 1990年,Ulrish 2000年），使之渐渐成熟起来。
随着如各种各样的专利中所描述的机床详细结构的变化，冲压激光组合机床，大体上就是将冲压工具和激光切割机整合到一台机器上了。
现在有些机床可以允许将冲压系统分离出激光切割系统，并且用一些常用的冲压系统配上激光系统翻新改进成的组合机床将很稳定（Ulrish 2000年）。
冲压激光组合机床的优点是多方面的。
这样的机床能提高传统冲压设备的性能以加工不规则形状的大工件。
它代表了机床的一个大的进展，能够提供一种单一的、高速的、高精度的冲压切割机床，其轨迹都是由一个终端自动控制器所控制的，而且工件之间的运动都是通过一个机械装置完成的，以消除操作时引起的工件之间的不必要的滑动。
在过去的二十多年里，工业的发展带动了冲压激光组合机床的发展。
生产这种机床的公司包括明尼苏达州的Dalsin工业公司，北卡罗来纳州的LVD公司，康涅狄格州的通用制造公司，这些都在美国，还有德国的TRUMPF集团，美国加里福里亚州的Amada America公司和芬兰国际公司。
图1显示的就是Amada America公司拥有的组合机床。
鉴于冲压激光组合机床的性能，这种机床的工艺设计就变得更加复杂。
然而，至今还没有发现有关直接研究这种冲压激光组合机床的工艺设计的文章，并且也没有发现这种组合机床的最优工艺设计。
这与工业上机床的发展速度是不能相配合的。
不过最近发现了两个相关的研究，这些研究是关于激光冲压机床的柔性制造单元的工艺设计（高希，等人，1993年）和车间优化工序的模拟方法（安多，等人，1996年）。
同时，以工艺设计为主题的研究有着悠久的历史和卓越的成果。
最近的一个具有总结性意义的研究是由李等人完成的。
图1 Amada Apelio 冲压激光组合机床这篇文章将侧重于冲压激光组合机床的工艺设计问题，是为了提高机床的效率和从布局到加工的加工程序的完全自动化。
这篇文章还将给出冲压激光组合机床的最优的工艺设计。
2 冲压激光组合机床的工艺设计问题对于冲压激光组合机床的工艺设计，每批工件都有两个重要的决定性方面，例如：执行什么功能，是冲压还是切割？执行什么样最优的操作可以确保整体最大的机械效率？让我们以图2所示的工件为例，一块1000×1120mm的金属板，两种类型的组成部分被展示出来了。
第一个组成部分是带有中心孔和四个小孔以及倒圆角的方形，第二个组成部分是顶部带有小孔的半圆形与长方形的组合图形。
对于组合机床，有四种不同的操作特征。
例如，23个ø50mm的小孔，4个ø180mm的大孔，四个第一部分的部件以及七个第二部分的部件。
而对于自动规划设计，什么特征是用来冲压的还有什么是用来切割的？如果第一个问题得到解决，那将要用什么最好的操作来得到最大的机械效率？本文讲的是在第一个问题的启发下得到的一个定量的方法，那就是蚁群优化，它将是第二个问题的答案。
再用它来测试如图2所示的或者更为复杂的金属薄板工件。
整合了计算机辅助设备（CAN）和G代码子程序的方法也将被讨论。
在讨论之前提到的方法时，有一些需要我们考虑的注意点：操作序列（进程）将得到优化，以提高冲压激光组合机床的机械效率。
可能提高的效率将转化为机器成本，劳动力成本的降低以及生产力的提高等等。
图2 冲压激光组合机床的工件组成部分（单位：mm）事实上很多组合机床只有一个冲压头或者一个激光切割器。
本文所要研究的是，如果要用这个方法将机床扩展成多刀头的话，应该不是太难的。
冲压激光组合机床应该设计成数控型的，以便最优的操作程序能够被输出而生成G代码。
附件2：外文原文（复印件）Optimal process planning for a combined punch-and-laser cuttingmachine using ant colony optimizationA machine that performs both punching and laser-cutting operations is referred as combined punch-and-laser machine. Such a machine has been in the market for about two decades. Although process-planning tools have been used on such a combined machine, the optimization of process planning dedicated to combined machines, based on our literature search results, has never been directly studied. This work addresses the process-planning problem for the combined punchand-laser machine by integrating knowledge, quantitative analysis, and numerical optimization approaches. The proposed methodology helps making decisions on following issues: (i) which type of operation should be applied to each feature,and (ii) what is the optimal operation sequence (tool path) to achieve the maximum manufacturing efficiency. The ant colony optimization (ACO) algorithms are employed in searching the optimal tool path. Sensitivities of control parameters of ACO are also analysed. Through applications, the proposed method can significantly improve the operation efficiency for the combined punch-and-laser machine. The method can also be easily automated and integrated with the nesting and G-code generation processes. Some issues and possible future research topics have also been discussed.Keywords: Combination machine; Combined punch-and-laser machine; Sheet metal; Process planning; Optimization; Ant colony optimization1. IntroductionModern computer numeric controlled (CNC) turret punches represent highly versatile machine tools capable of producing sheet metal and plastic components quickly and accurately. However, the versatility of such turret punches is limited in that material can be removed from the work piece only by a punching type operation. When large areas of the work piece are to be removed, or when the work piece is to be subdivided into a number of separable work pieces, or when relatively long or large diameter parts are to be made, this can be accomplished only by a series of slightly overlapping punching typemetal removal operations. Such overlapping material removal operations can be effectively used to increase the versatility of a punch, however, those operations, at times, lead to undesired consequences, such as formation of burred edges, inability to produce highly accurate, smooth side edges, relative slowness of operation, etc. (Clark and Carbone 1980). Moreover, when the cut-out shape is not one of the common punch tool shapes, special tools have to be made and the costs of making such tools are normally high. As a result, many cutting or shearing type operations are performed by other machine tools in a subsequent operation that requires additional work piece handling. This multimachinery requirement influences not only the manufacturing efficiency, but also the manufacturing quality and cost. The above stated reasons motivated the development of a so-called combined punch-and-laser cutting machine (Clark and Carbone 1980), or compound machine (Katayama 1989a, b, Xie et al. 2001), or combination punch press and laser cutting machine (Klingel and Doettling 1990, Ulrish 2000). In this work, this machine will be referred as combined punch-and-laser machine. The combined punch-and-laser machine was first invented in 1980 (Clark and Carbone 1980), and then gradually matured by overcoming its vibration interference problem through a number of patents (Bredow 1982, Katayama 1989a, b, Klingel and Doettling 1990, Ulrish 2000). With variations on detailed machine structure as described in various patents, a combined punch-and-laser machine, in principle, integrates a punch tool with a laser beam cutter into one machine. The current version of the machine allows the separation of the punching system from the laser system, and a standard punch tool can be readily retrofitted with a laser system to therefore become a combined machine (Ulrish 2000).The advantages of the combined punch-and-laser machine are manifold. Such a machine increases the ability of conventional punching equipment to provide large and/or irregularly shaped parts in the work piece. It represents a major advance in the art of machine tools to provide a single machine tool capable of high speed, high accuracy punching, cutting, and surface marking wherein all functions are controllable from a central automatic control and wherein work piece movement is accomplished by a single mechanism so as to eliminate the necessity of work piece handling between operations.In the past 20 years, the industry embraced the combined punch-and-laser machine. Companies that supply such machines include, for example, Dalsin Industries, Inc. in Minnesota, LVD Corporation in North Carolina, GE Capital Manufacturing in Connecticut, all USA, TRUMPF Group, Germany, Amada America, Inc. in California, USA, and Finn-Power International, Inc. Figure 1 shows an example of such a machine by Amada America.Given the capability of combined punch-and-laser machines, the process planning of the machine becomes more complex. However, no study has been found in literature directly on process planning for combined punch-and-laser machines. Neither was found the optimization of process planning dedicated to combined punch-and-laser machines. This is incommensurate with the development of the machine in industry. Two related studies are found on the process planning for a flexible manufacturing cell that includes a punch and a laser (Ghosh et al. 1993), and a simulation method to optimize the work sequence in a job shop (Endo et al. 1996).While, process planning as a topic in general has a long history with many fruitful results. A recent work with a good review is done by Li et al. (2004).Figure 1. Amada Apelio combined punch-and-laser machine (Amada American, Inc. )This work will focus on the process-planning problem for the combinedpunch-and-laser machine in order to improve the efficiency of the machine and fully automate the process from layout nesting to machining. This work will be the first on optimal process planning for combined punch-and-laser machines.2. Process planning problem for a combined punch-and-laser machineFor the process planning of a combined punch-and-laser machine, one has to make two important decisions for each batch of work pieces, i.e.Which feature is to be punched or cut?What is the optimal sequence of operation to ensure the overall maximum machine efficiency?Let us use the work piece shown in figure 2 as an example. On a sheet metal of1000_1120 mm, two types of components are laid out. The first component has a square shape with round corners, a central hole, and four small holes. The second component is a combination of a semicircle and a rectangle, with a small hole. For the combined machine, there are four different operation features, i.e. 23 small holes of F50, four large holes of F180, four contours for the first component, and 7 contours for the second component. For automatic process planning, which feature is to be punched and which is to be cut? If the first question were answered, what would be the optimal operation sequence that yields the maximum machine efficiency? This work will develop a quantitative method guided by heuristics to address the first question, and then apply the ACO algorithms to answer the second question. The methods are then tested with the problem shown in figure 2 and a more complex sheet metal work piece. Integration of the proposed methods with Computer-Aided Nesting (CAN) and G-Code generation tools will also be discussed. Before discussing the proposed methodology, some assumptions are given first to confine us to an appropriate scope of study:Operation sequence (process) will be optimized to improve the machine efficiency of the combined punch-and-laser machine. The increase of machine efficiency is expected to translate into reduced machine cost, abour cost and increased throughput, etc.Figure 2. Batch of work pieces to be machined in the combined punch-and-laser machine (unit:mm).Given the fact that most combined machines have only one punch head and one laser cutter, this study will focus on this type of machine. Extension of the proposed method to machines with multiple heads shouldnot be difficult.Combined punch-and-laser machine is assumed to be CNC so that theoptimal operation sequence can be output to generate G-codes.。