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人人文库网 > 图纸下载 > 毕业设计 > 3吨叉车的液压系统设计【cad高清图纸和说明书打包】

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3吨叉车的液压系统设计【cad高清图纸和说明书打包】

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3吨叉车的液压系统设计【cad高清图纸和说明书打包】.zip

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内容简介：: Mechanical Engineering EnglishLesson 1 Modern Manufacturing EngineeringAWhat Is Manufacturing Maybe youve never thought about it before, but it is all around you. It affects every part of your life. What is it? In this case, “it” is manufacturing. Actually “manufacturing” is not all around you. But manufactured products are. Look around you right now. Name some things you see that were manufactured. Chairs, notebooks, blue jeans, books, floor tile, chalkboards, light bulbs, pencils, eyeglassesnearlyeverything around you was manufactured.The manufacturing industry is important to our society. Its essential to our economy. An economy is a system for producing and distributing products and services. Many people work in manufacturing. They help produce products. And they buy products with the money they earn. The more products people buy, the more products are manufactured. And this allows more people to work. Manufacturing is also important to the economy in another way. A piece of material is worth more after its been changed into a useful product. Thats added value. Value is increased by the manufacturing process.B. Modern Manufacturing A manufacturing industry needs three basic types of resources: Material resources, Human resources, Capital resources. The elements of industry are seven key steps for organizing production: Research and Development, Production Tooling, Production Planning and Control, Quality Control, Personnel Management, Manufacturing, Marketing. R&D is the planning of new products, processes, or materials and the improvement of old skill. R&D is such a large, important part of the industrial world and requires many people with different talents. Production Tooling is the element of industry concerned with these tools. The PT obtains the tools, machines, and equipment needed to make a product. The most important parts of Production Planning and Control are routing, scheduling, dispatching, and plan layout. The machinery and equipment must be arranged so that production can take place smoothly, without wasted time and effort. Quality Control can be defined as those activities which prevent defective articles. In this way management tries to insure that a product will be acceptable to the buyer. Marketing is the process of getting products from those who make them to those who use them and it helps to deliver the right kinds of goods to us, in the right form and amount, at the time and price.Lesson 2 Mechanical Engineering Design Mechanical engineering design is a major segment of engineering, it deals with the conception, design, development, refinement, and application of machines and mechanical apparatus of all kinds. For many students, mechanical engineering design is one of their first professional engineering courses. Professional engineering is concerned with obtaining solutions to practical problems, and the engineers are able to devise better solutions to practical problems. The most problems in mechanical engineering design do not have a single right answer. Hence, modern mechanical engineers are able to produce distinctly better solutions to meet todays needs. The engineer must use the best available scientific understanding together with empirical information, good judgment. When considering a complete machine, the engineer invariably finds that the requirements and constraints of the various components are interrelated. The modern engineer has become increasingly concerned with the broader considerations of safety, ecology, and overall “quality of life.”Good designs require trying new ideas and being willing to take a certain amount of risk, knowing that if the new idea does not work the existing method can be reinstated. Thus a designer must have patience, since there is no assurance of success for the time and effort expanded. Creating a completely new design generally requires that many old and well-established methods be thrust aside. This is not easy since many people cling to familiar ideas, techniques and attitudes. A design engineer should constantly search for ways to improve an existing product and must decide what old, proven concepts should be used and what new, untried ideas should be incorporated.New designs generally have “bugs” or unforeseen problems which must be worked out before the superior characteristics of the new design can be enjoyed. Thus there is a chance for a superior product, but only at higher risk. It should be emphasized that, if a design does not warrant radical new methods, such methods should not be applied merely for the sake of change.During the beginning stages of design, creativity should be allowed to flourish without a great number of constraints. Even though many impractical ideas may arise, it is usually easy to eliminate them in the early stages of design before firm details are required by manufacturing. In this way, innovative ideas are not inhibited. Quite often, more than one design is developed, up to the point where they can be compared against each other. It is entirely possible that the design which is ultimately accepted will use ideas existing in one of the rejected designs that did not show as much overall promise.Another important point which should be recognized is that a design engineer must be able to communicate ideas to other people if they are to be incorporated. Communicating the design to others is the final, vital step in the design process. Undoubtedly many great designs, inventions, and creative works have been lost to mankind simply because the originators were unable or unwilling to explain their accomplishments to others. Presentation is a selling job. The engineer, when presenting a new solution to administrative, management, or supervisory persons, is attempting to sell or to prove to them that this solution is a better one. Unless this can be done successfully, the time and effort spent on obtaining the solution have been largely wasted. 英文文献翻译学生姓名：学院：专业及班级：学号：指导教师： 2011年 4月 25 日机械工程英语第1课现代制造工程 A.什么是制造业也许你从来没有想过这个问题之前，但它是你周围的一切。它影响着你生活的一部分。是什么呢？在这种情况下，“它”是制造业。其实“制造”是不是你周围的一切。而是人为制造的产品。现在看看你周围。名称有些事情你看到这些制造。椅子，笔记本电脑，蓝色牛仔裤，书籍，地板砖，黑板，灯泡，铅笔，眼镜，近周围的一切你是制造。制造业是香港的重要的社会。这对于我们的经济。一个经济体是生产和销售的产品和服务体系。许多人工作在制造业。他们帮助生产的产品。他们用这些钱购买他们赚的产品。人们购买的产品越多，越产品的生产。这让更多的人来工作。制造业也是重要的另一种方式的经济。甲片的材料后，更是值得它被改变成一个有用的产品。这就是附加值。价值是增加了生产过程。二现代制造一个制造业的资源需要三个基本类型：物质资源，人力资源，资本资源。工业的七个关键要素是组织生产步骤：研究，开发，生产模具，生产计划与控制，质量控制，人事管理，制造，营销。研发新产品，工艺或材料，旧技术的改进计划。 RD是这么大，工业世界的重要组成部分，需要与不同的人才很多人。生产工具是工业元素与这些工具有关。在PT获得的工具，机器和设备需要做出的产品。生产计划与控制最重要的部分是路由，调度，调度，并规划布局。机械及设备，必须使生产安排，可以进行顺利，没有浪费时间和精力。质量控制可以被定义为那些活动，防止缺陷的文章。在尝试这种方式管理，以确保产品将可以接受的买家。营销是让那些谁使他们对那些谁使用它们，有助于提供各种货物的权利给我们，在正确的方式和数额，时间及价格，产品的过程。第2课机械工程设计机械工程设计是工程的主要部分，它涉及的概念，设计，开发，改进和应用机器及各种机械设备。对于许多学生，机械工程设计是他们的第一个专业的工程课程之一。专业工程关注的是获得解决实际问题，工程师们能够设计出更好的解决实际问题。在机械工程设计中的大多数问题没有唯一正确的答案。因此，现代机械工程师能够产生显着更好的解决方案，以满足今天的需要。工程师必须使用现有的最佳科学信息的理解以及经验，良好的判断力。当考虑一个完整的机器，工程师都认为，要求和约束是相互关联的各个组成部分。现代工程师已越来越多地安全，生态，更广泛的考虑和整体有关“生活质量”。好的设计需要尝试新的想法并愿意采取了一定的风险，因为他们知道如果新的观点并不工作中存在的方法可以恢复。因此，设计者必须要有耐心，因为没有时间和扩大的努力取得成功的保证。创建一个全新的设计，通常需要许多旧的和行之有效的方法，将重点放在一边。这并不容易，因为许多人抱着熟悉的想法，技巧和态度。设计工程师必须不断寻找方法来改进现有产品，必须决定哪些旧的，成熟的概念，应使用什么新的，未经试验的想法应该被纳入。新的设计通常有“错误”或之前，必须制定新设计出来的优良特性，可享有不可预见的问题。因此，有一个优越的产品的机会，但只有在较高的风险。应该强调的是，如果设计不保证激进的新方法，这种方法不能申请的改变而而已。在设计的开始阶段，创意应该允许繁荣没有大量的约束。尽管许多不切实际的想法可能发生时，通常很容易消除在设计的早期阶段，他们之前是由公司生产所需的细节。通过这种方式，创新的思想不是抑制。很多时候，一个以上的设计，开发，到那里他们可以相互比较点。这是完全可能的是，最终设计将接受使用心得在被拒绝的设计，没有太多的整体表现为一个现有的承诺。另一项重要的一点，应该承认的是，设计工程师必须能够与其他人交流意见，如果他们要纳入。传达给其他人设计的最后，在设计过程中的重要一步。毫无疑问，许多伟大的设计，发明和创新工程已失去了人类仅仅是因为创始人是无法或不愿解释他们的成就给其他人。演讲是一个销售的工作。这位工程师，当提出一个新的解决方案，行政，管理或监督人，正试图出售或向他们证明这个解决方案是一个更好的。除非这是可以做到成功，获得的时间和精力花在解决方案已经在很大程度上浪费了。湖南农业大学全日制普通本科生毕业设计 3吨叉车液压系统设计3 TON FORKLIFT TRUCK HYDRAULIC SYSTEM DESIGN学生姓名：学号：年级专业及班级：指导老师及职称：学院：工学院湖南长沙提交日期：2013年5月湖南农业大学全日制普通本科生毕业设计诚信声明本人郑重声明：所呈交的本科毕业设计是本人在指导老师的指导下，进行研究工作所取得的成果，成果不存在知识产权争议。除文中已经注明引用的内容外，本论文不含任何其他个人或集体已经发表或撰写过的作品成果。对本文的研究做出重要贡献的个人和集体在文中均作了明确的说明并表示了谢意。本人完全意识到本声明的法律结果由本人承担。毕业设计作者签名：年月日目录摘要.1关键词.11前言.21.1课题背景21.2叉车发展概况42 液压元件62.1液压阀块简介62.2集成块的设计步骤83.1液压系统设计概述93.2液压系统设计113.2.1原理图113.2.2起升油缸最大工作压力及流量123.2.3求液压系统最大压力133.2.4液压泵站及液压泵的规格及选用133.2.5油泵功率及电机选择143.2.6选择换向阀153.2.7管道设计与管件的选择193.2.8液压油选取213.2.9滤油器及油箱选取213.2.10压力损失的计算223.2.11节流阀的设计234 液压站结构设计254.1液压站的结构型式254.2液压泵的安装方式254.3液压油箱的设计274.3.1液压油箱有效容积的确定274.3.2液压油箱的结构设计274.4液压泵结构设计的注意事项285 倾斜机构设计计算285.1倾斜机构设计概述295.2倾斜机构设计295.2.1倾斜油缸受力分析及负荷计算305.2.2计算倾斜油缸缸径和活塞杆直径305.2.3计算油缸行程305.2.4计算油缸作用时间315.2.5稳定性校核31 5.2.6油缸壁厚的计算325.2.7活塞杆强度计算335.2.8缸体螺纹连接计算335.2.9 缸底厚度及缸底的焊缝强度计算33结论34参考文献3513 3 吨叉车的液压系统设计吨叉车的液压系统设计摘要：随着工业的发展，叉车的使用越来越普遍。叉车的使用不仅可实现装卸搬运作业的机械化，减轻劳动强度，节约大量劳力，提高劳动生产力，而且能够缩短装卸、搬运、堆码的作业时间，加速汽车和铁路车辆的周转，提高仓库容积的利用率，减少货物破损，提高作业的安全程度。本课题主要是介绍叉车液压系统设计。本章以叉车工作装置液压系统设计为例，介绍叉车工作装置液压系统的设计方法及步骤，包括叉车工作装置液压系统主要参数的确定、原理图的拟定、液压元件的选择以及液压系统性能验算等。关键词：叉车；电液控制；液压元件3 Ton Forklift Truck Hydraulic System DesignAbstract：With he development of industry, forklift is used more and more widely. The use of forklift trucks can be realized not only the mechanization of loading and unloading operations, reduce labor intensity, save a lot of labor, improve labor productivity, and can shorten the operating time of loading and unloading, handling, stacking, and accelerate the turnover of the automotive and railway vehicles, improve the utilization of warehouse volumerate and reduce the damaged goods, improve the degree of job security. The main subject is to introduce the forklift hydraulic system design. This chapter, for example, describes the forklift hydraulic system design methods and procedures, including the forklift hydraulic system to determine the parameters forklift hydraulic system design, the formulation of the schematic, select hydraulic components and hydraulic system performance checkingKey words: Forklift; Electro-hydraulic control; Hydraulic components1 前言1.1 课题背景叉车最先出现在上世纪 20 年代，由工作装置完成垂直方向作业，由车轮行驶系2统完成水平方向作业，是室内搬运的首选工具。目前欧美发达国家和日本的电动叉车的产量已经占有了国际上 80%以上的市场。目前，科技先进的国家已经广泛采用负荷传感，变量系统，并利用先导控制技术实现了液压系统的高效节能和远程控制等。但传统叉车的液压系统仍采用定量泵，使得整机流量大、压力高，引起了系统油温过高，液压元件泄露，所以可靠性差。与此同时其制动节能，转向动力提高等方面也都已经不能满足要求，所以叉车行业也正面临着改革与创新。我国的机械制造行业起步较晚，原有的基础比较薄弱，与工业先进国家相比，差距不小。国内生产叉车的技术更是比国外落后很多，如何提高叉车技术是我们大家共同努力的目标。为此，本文主要进行叉车的设计计算，重点在于液压系统设计计算，已经完成了油箱、动力元件、控制元件、执行元件以及各种液压元器件的选型和设计、校核等，将液压系统各部分组成按流程逐步设计后，以此为依据，设计了液压系统布置图。本设计还将论述设计方案的合理性，以合力叉车为原型集中研究现今国内叉车技术发展的实际情况，学习叉车总体设计结合所学汽车、机械和液压知识，将其融会贯通，力求设计能够达到技术上的创新同时又能兼顾经济性1。1.2 叉车发展概况随着社会化生产的发展与进步，劳动力与机械的专业分工也越来越细，各种专业设备的配套与衔接，使得整个物流系统运作井然有序，效率得到成倍提高。而叉车作为装卸搬运车辆的一种，因为具有能量转换效率高、噪声小、无废气排放、控制方便等优点而成为室内搬运的首选工具。为了作业方便，通常工作装置放在叉车的前方，其主要工作属具是货叉，叉车由此得名。叉车主要用于成件货物的装卸，实现了装卸作业的机械化。现阶段电动叉车在车体、门架、液压系统以及底盘技术方面与传统叉车相比均取得了一定成就。车体一般 5mm 以上钢板制成，无大梁车体强度高，可承受重载此外流线型设计也将叉车的护顶架，车身，配重及其各种装饰融为一体。宽视野的两节或三节型门架，起升高度在 2-6m。目前门架下降还采用负载势能回收的原理，实现门架下降的无级调速。将势能转化为电能对蓄电池充电，从而达到节能的目的。新型液压系统采用了负荷传感、变量系统、先导控制技术等实现了液压系统的高效节能和远程控制，系统油温显著降低，整机性能先进，操作舒适，安全可靠。由单独电机驱动的油泵又能为门架工作系统的提升和倾斜机构提供液压动力。同时在工作装置回路上增设了单向阀，作用是当油泵侧压力比工作油缸侧压力低的情况下换向时油液不会倒流。目前国外品牌叉车还采用液压脉冲控制技术，可自动平衡电机速度与3用油量，电源利用率高，无电压峰值，噪声低，液压元件磨损低，大大提高了整车的可靠性，节能性和使用寿命。随着电子技术渐渐融入机械制造技术，电动叉车要求能够实现高效、节能、环保、安全及智能化。各种新方案的推出让电动叉车在性能、结构方面取得了长足进步，配置也变得更优化3。1.3 叉车的液压系统叉车液压系统是叉车的重要组成部分，其工作装置、助力转向系统甚至行走传动系统等都需要由液压系统驱动完成。因此，叉车液压系统的质量优劣直接影响着叉车的性能。某型号叉车工作装置的液压系统原理图如图 1 所示，该液压系统有起升液压缸4、倾斜液压缸 9 和属具液压缸 10 三个执行元件，由定量泵 6 供油，多路换向阀（属具滑阀 1、起升液压缸滑阀 7、倾斜液压缸滑阀 8）控制各执行元件的动作，单向节流阀 3 调节起升和属具动作速度，从而驱动工作装置完成相应的工作任务。1-属具滑阀 2-分配阀 3-单向节流阀 4-起升液压缸 5-安全阀 6-液压泵 7-起升液压缸滑阀 8-倾斜液压缸滑阀 9-倾斜液压缸 10-属具液压缸图 1 工作装置液压系统Fig 1 Implement hydraulic system 由于叉车原动机（内燃机和电动机）的转速高，扭矩小，而叉车的行驶速度较低，驱动轮的扭矩较大，因此在原动机和驱动轮之间必须有起减速增矩作用的传动装置，当叉车在不同载荷和不同作业条件下工作时，传动装置必须要保证叉车具有良好的牵引性能。对于内燃叉车，由于内燃机不能反转，叉车要想倒退行驶，必须依靠传动装4置来实现。叉车的传动装置有机械式、液力式、液压式和电动机械式几种。机械式传动只能具有有限数目的传动比，因此只能实现有级变速。液力传动效率较机械式低，液压传动能够使传动系大大简化，取消机械式和液力式传动中的传动轴和差速器。某型号叉车行走驱动液压系统的原理图如图 2 所示，该液压系统由变量主液压泵1 供油，执行元件为液压马达 7，主液压泵的吸油和供油路与液压马达的排油和进油路相连，形成闭式回路。双向安全阀 5 保证液压回路双向工作的安全，梭阀 6 和换油溢流阀 8 使低压的热油排回油箱，辅助液压泵 2 把油箱中经过冷却的液压油补充到系统中，起到补充系统泄漏和换油的作用，溢流阀 4 限定补油压力，单向阀 3 保证补油到低压油路中。1- 主泵 2-辅助液压泵 3-补换油溢流阀 4-单向阀 5-双向安全阀 6-梭阀 7-液压马达 8-换油溢流图 2 行走驱动液压系统Fig 2 Travel drive hydraulic system 叉车作业时转向频繁，转弯半径小，有时需要原地转向。叉车空载时，转向桥负荷约占车重的 60%。为了减轻驾驶员的劳动强度，现在起重量 2 吨以上的叉车多采用助力转向液压助力转向或全液压转向。液压助力转向操作轻便，动作迅速，有利于提高叉车的作业效率，油液还可以缓冲地面对转向的冲击。某叉车液压助力转向系统原理图如图 3 所示，该转向液压系统和叉车工作装置液压系统属各自独立的液压系统，分别由单独的液压泵供油。系统中流量调节阀 2 可保证转向助力器稳定供油，并使系统流量限制在发动机怠速运转时液压泵流量的 1.5 倍。随动阀 3 与普通的三位四通换向阀基本相同，只不过该阀的阀体与转向液压缸缸筒连接为一体，随液压缸缸筒的动作而动作。叉车直线行驶时，方向盘处于中间位置，随动阀 3 的阀芯也处于中间位置，转向液压缸 4 不动作，叉车直线行驶。当叉车转弯时，驾驶员转动方向盘，联动机构带动随动阀 4 的阀芯动作，使转向液压缸的两腔分别与液压泵或油箱连通，液压缸动作，驱动转向轮旋转，叉车转向，直到液压缸缸筒的移动距离与阀芯的移动距离相同时，阀芯复位，转向停止。51-液压泵 2-调速阀 3-随动阀 4-转向液压缸 5-滤油器6-单向阀 7-安全阀 8-油箱图 3 叉车助力转向液压系统Fig 3 Forklift hydraulic power steering system 叉车液压系统的设计要能够保证叉车正常安全地完成工作任务，对液压系统的工作要求包括：（1）超载保护，多路换向阀壳体无裂纹、渗漏；工作性能应良好可靠；安全阀动作灵敏，在超载 25%时应能全开，调整螺栓的螺帽应齐全坚固。操作手柄定位准确、可靠，不得因震动而变位。叉车在装卸运输作业时不允许货物的重量大于叉车本身的重量。在叉车试验项目中，有一项是允许叉车以 110%的起重量载荷进行联合操作，即一边起升载荷一边向前运行，以检验叉车各部件的协调性和动作的可能性，此时发动机的功率、转速应达到额定的参数，液压系统应能够承压、无渗油。对超载起升保护的性能检验是以 125%的起重量载荷进行起升动作。此时，液压系统中应设置相应的超载保护装置，例如多路换向阀中安全阀。超载时，虽然多路换向阀阀杆动作，但货叉和 125%起重量载荷不得离开地面或离开地面不超过 300mm，即叉车应呈现出起升速度下降或起升动作失灵。（2）最大下降速度控制，为了提高装卸效率，如果叉车起升速度增大，满载下降速度也增大，下降速度过大是危险的，因此叉车液压系统中应设置下降限速阀，既要控制货叉的下降速度不超过限定的速度值，又要防止起升液压缸的高压橡胶软管突然爆破时，起升在一定高度的载荷不会和货叉一起突然落下，损伤货物或伤人。（3）液压系统管路接头牢靠、无渗漏，与其它机件不磨碰，橡胶软管不得有老化、变质、腐蚀等现象。（4）液压系统中的传动部件在额定载荷、额定速度范围内不应出现爬行、停滞和明显的冲动现象。6（5）其它为节省叉车携带电动机，减少叉车附属设备，从而减小液压系统的整体尺寸，叉车工作装置液压系统可以由叉车发动机直接驱动液压泵来提供油源。为适应叉车有可能工作在具有粉尘和沙粒的厂房环境中，应考虑为液压系统设置合适的过滤器，液压油的工作温度应限定在合适的范围内，叉车的工作环境温度一般为-1045C。1.3.1 本设计要求及技术参数（1）起升装置液压系统技术参数本设计实例所设计的叉车主要用于工厂中作业，要求能够提升 5000kg 的重物，最大垂直提升高度为 2m，叉车杆和导轨的重量约为 200kg，在任意载荷下，叉车杆最大上升（下降）速度不超过 0.2m/s，要求叉车杆上升（下降）速度可调，以实现叉车杆的缓慢移动，并且具有良好的位置控制功能。要求对叉车杆具有锁紧功能，无论在多大载荷作用下，或者甚至在液压油源无法供油，油源到液压缸之间的液压管路出现故障等情况下，要求叉车杆能够被锁紧在最后设定的位置。叉车杆在上升过程中，当液压系统出现故障时，要求安全保护装置能够使负载安全下降。本设计实例所设计叉车工作装置中叉车杆起升装置示意图如图 4 所示，由起升液压缸驱动货叉沿支架上下运动，从而提升和放下货物4。图 4 起升装置Fig 4 Lifting device2 液压元件2.1 液压阀块简介油路块的结构油路块是一块较厚的液压元件安装板，用螺钉将板式液压元件安装在油路板的正面或者各个侧面（保持底面或某一个面为安装固定面），在正面对应的孔与液压阀的各孔相通，各孔间按照液压系统原理图的通路要求，在油路板内部钻纵、7横孔道，在孔口开有螺纹，安装管接头用以接管。为避免孔道过长、过多而不便于加工，在一块油路板上安装元件的数量一般不超过 10-12 个。油路板边长不宜大于400mm。油路板内部孔道数量较多且又互相交叉时，为了便于设计和制造，减少工艺孔，可将油路板的厚度分为三层，第一层为泄露油和控制油孔的通道（L层），其孔径较小；第二层为压力油孔通道（P层）；第三层为回油孔通道（O层）。如果元件数量并不多，尽可能将压力油孔通道和回油孔通道布置在同一层内，以减小油路板的厚度。把液压元件分别固定在几块集成块上，再把各集成块按设计规律装配成一个液压集成回路，这种方式与油路板比较，标准化、系列化程度高，互换性能好，维修、拆装方便，元件更换容易；集成块可进行专业化生产，其质量好、性能可靠而且设计生产周期短。使用近年来在液压油路板和集成块基础上发展起来的新型液压元件叠加阀组成回路也有其独特的优点，它不需要另外的连接件，由叠加阀直接叠加而成。其结构更为紧凑，体积更小，重量更轻，无管件连接，从而消除了因油管、接头引起的泄漏、振动和噪声。本次设计采用系统由集成块组成，由于本液压系统的压力比较大，所以调压阀选择DB/DBW型直动溢流阀，而换向阀等以及其他的阀采用广州机床研究所的GE系列阀。2.2 集成块的设计步骤（1）制作液压元件样板。根据产品样本，对照实物绘制液压元件顶视图轮廓尺寸，虚线绘出液压元件底面各油口位置的尺寸，按照轮廓线剪下来，便是液压元件样板。若产品样本与实物有出入，则以实物为准。若产品样本中的液压元件配有底板，则样板可按底板提供的尺寸来制作。若没有底板，则要注意，有的样本提供的是元件的俯视图，做样板时应把产品样本中的图翻成 180。（2）决定通道的孔径。集成块上的公用通道，即压力油孔P回油孔T泄露孔L及四个安装孔。压力油孔由液压泵流量决定，回油孔一般不小于压力油孔。直接与液压元件连接的液压油孔由选定的液压元件规格确定。孔与孔之间的连接孔用螺塞在集成块表面堵死。与液压油管连接的液压油孔可采用米制细牙螺纹或英制管螺纹。（3）集成块上液压元件的布置。把制做好的液压元件样板放在集成块各视图上进行布局，有的液压元件需要连接板，则样板应以连接板为准。电磁阀应布置在集成块的前后面上，要避免电磁阀两端的电磁铁与其它部分进行相碰。液压元件的布置应以在集成块上加工的孔最少为好。孔道相通的液压元件尽可能布置在同一水平面，或在直径d的范围内，否则要钻垂直中间油孔，不通孔之间的最小壁厚h必须进行强8度校核。液压元件在水平面上的孔道若与公共孔道相通，则应尽可能地布置在同一垂直位置或在直径d范围内，否则要钻中间孔道，集成块前后与左右连接的孔道应互相垂直，不然也要钻中间孔道。设计专用集成块时，要注意其高度应比装在其上的液压元件的最大横向尺寸大 2mm，以避免上下集成块上的液压元件相碰，影响集成块紧固。（4）集成块上液压元件布置程序。电磁换向阀布置在集成块的前面和后面，先布置垂直位置后布置水平位置，要避免电磁换向阀的固定螺孔与阀口通道集成块固定螺孔相通。液压元件泄露孔可考虑与回油孔合并。水平位置孔道可分三层进行布置。根据水平孔道布置的需要，液压元件可以上下左右移动一段距离。溢流阀的先导部分可伸出集成块外，有的元件如单向阀，可以横向布置。（5）集成块零件图的绘制。集成块的六个面都是加工面，其中有三个面要装液压元件，一个侧面引出管道。块内孔道纵横交错，层次多，需要由多个视图和 2-3 个剖视图才能表达清楚。孔系的位置精度要求较高，因此尺寸公差及表面粗糙度应标注清楚，技术要求也应予说明。集成块的视图比较复杂，视图应尽可能少用虚线表达。为了便于检查和装配集成块，应把单向集成回路图和集成块上液压元件布置图绘在旁边。而且应将各孔道编上号，列表说明各个孔的尺寸深度以及与哪些孔相交等情况。图5 油路块Fig 5 Manifold3 液压系统设计计算93.1 液压系统设计概述液压系统除油箱及其管路外，由工作转向油泵和电机作为动力元件，多路换向阀，限速阀等作为控制元件，油缸作为执行元件。液压系统执行元件主要可分三部分：9（1）为了升降货物配有起升油缸。（2）转向油缸和全液压转向器。（3）为使装货的框架能前后倾斜，以利于搬运和行走方便使用倾斜油缸。油泵输出的压力油分别进入到工作装置和转向操纵机构，通过前后倾手柄使多路换向阀的滑阀移动以改变液压油的流动方向，从而控制升降油缸与门架倾斜油缸，实现起重货架和门架的前后倾斜。另一个油路是油液经转向油泵与电机到全液压转向器控制转向油缸；最后油液将再度重返油箱如此不断循环，液压系统是叉车工作过程中的重要环节。一套合理的液压系统方案要求能够实现主机要求的各项功能，并且操纵方便，工作可靠，动作平稳，调整维修方便。完善的液压系统设计主要包括以下部分的设计：（1）选执行元件：液压缸。（2）选液压油：普通矿物液压油。（3）确定换向回路：三位六通手动换向阀控制。（4）调速方式：定量泵变转速调速，同时使用换向阀阀口实现微调。（5）液压泵类型：系统压力小于 21Mpa，选用齿轮泵或叶片泵；大于 21Mpa选柱塞泵。（6）确定回路方式：选开式回路，即执行元件的排油直接回油箱，油液径沉淀、冷却后再进入液压泵的进口。（7）调压方式：溢流阀做安全阀，限制系统最高压力；执行元件不工作时液压泵在小功率下工作采用卸荷回路。对垂直变负载(起升缸升降)采用限速阀，以保证重物平稳下落。3.2 液压系统设计前文已经对液压系统设计进行了概述，为了更进一步学习和研究，本节将直观讲述液压原理图、工作线路图、零部件图等相关图示并进行相关计算。主要任务包括：负载分析；系统参数分析（包括泵和电机参数的选取和设计计算）；元件选择；以及验算液压系统性能，（压力损失验算）等。3.2.1 原理图液压系统设计说明：（1）油箱：选择开式油箱。（2）液压泵：工作油泵采用齿轮泵，型号分别为CB-F18C-FL。10（3）工作电机：Z4-112-4。（4）起升油缸：选择单作用柱塞式液压缸。（5）倾斜油缸：选择双作用活塞式液压缸。（6）液压控制阀：选用多路换向阀ZFS-L10C-YT-O。（7）流量控制：设计单向限速阀。（8）液压辅件设计：过滤器设计，空气滤清器设计，各种仪表选择密封件的选型等，液压油及压力损失计算。液压系统回路的工作线路主要分两路进行，详见框图：图 6 液压系统回路的工作线路Figure 6 Circuit of hydraulic system lines为了说明液压系统回路，下面插图表示加深对液压系统的认识，（液压系统原图、液压系统工作线路图）11图 7 液压系统示意简图Figure 7 Hydraulic system of schematic diagram3.2.2 起升油缸最大工作压力及流量压力为 100/2；流量为 25.8L/min3.2.3 求液压系统最大压力换向阀要求最大压力 100/2，参照同类同规格产品，P1选 100/2。3.2.4 液压泵站及液压泵的规格及选用液压泵站是液压系统的重要组成部分，它向液压系统提供一定的压力和流量的工作介质。在液压泵站上安装必须的液压阀可以直接控制液压执行元件工作，本课题布置采用非上置卧式，即油泵及电机单独安装在专用平台上，即采用机座带底脚、端盖上无凸缘结构，电动机水平放置，安装处可加弹性防振垫。（1）液压泵的最大工作压力据公式 + (1)pP1P1P12图 8 液压系统工作线路图Figure 8 Hydraulic system wiring diagram即+=110.12/2 (2)pP1P1P式中：为进回油路中总压力损失，其包括局部损失和沿程压力损失。1P（2）液压泵流量 (3)maxpQKQ式中：K为系统漏损系数，常取 1.1；为同时动作的各液压执行器的最大泵工maxQ作流量，可由同时动作的各液压执行器最大流量相加。 (4)maxmax=25.8 / minQQL (5)1.1 25.8 / min28.4 / minpQLL（3）选油泵。工作油泵采用CB系列齿轮泵，型号为CB-F18C-FL。其参数如下：流量为=30.6L/min；额定转速为 1800r/min；额定压力为 12.5Mpa；驱动功率为maxQ11.2kw；质量为 8.2kg；容积效率大于 90%。转向油泵采用CB-6：流量为 8.7L/min；驱动功率为 0.31kw，额定压力为 2.5Mpa；额定转速 1450r/min。3.2.5 油泵功率及电机选择（1）油泵的驱动功率： (6)61.2pnvPQPw式中：为泵的实际最大工作压力，其值为 140Mpa；为泵的额定流量，其值为pPnQ510cm3/s；为泵的机械效率，取 0.8。因此，v (7)6614 10510 1089258.9361.2 0.8Pwkw（2）选择油泵电机据油泵额定转速及所需驱动功率，选择Z4-112-4，其参数如下：额定功率为5.5kw；额定电压为 160v；额定电流为 42.7A；转速(最高)3000/4000r/min；效率为83.5%；飞轮矩为 0.8；质量为 60kg。选用的油泵电机采用 5min工作制，故折算成后功率，故该电机油泵符合工作需要。155.59.55Pkw133.2.63.2.6 选择换向阀选择换向阀查液压控制传动手册表 17.6-1，选择关于ZFS-C型多路换向阀性能参数，选择图 9 ZFS-C型多路换向阀性能参数Figure 9 ZFS-C Multi directional control valve performance parameters 主要参数：工作压力为 14Mpa；最大流量为 30L/min；概算质量为 10.5kg；公称直径为 10mm。ZFS型多路换向阀时手动控制换向阀的组合阀，由 2-5 个三位六通手动换向阀、溢流阀、单向阀组成。根据用途的不同，阀在中间位置时，主油路有中间全封闭式、压力口封闭式及中间位置时压力油路短路卸荷等。主要用于多个工作机构的集中控制。换向阀图示如下：图 10 换向阀示意图Figure 10 Valve schematic完成快进工进快退停止等自动循环，工作台采用平导轨，主要参数见下表。表 1 自动循环参数Table 1 Automatic cycle parameters行程(mm)速度(m/min)液压缸负载力（N）工作台重量（N）工作台及夹具重量（N）快进工进快进工进快退启动时间(s)静摩擦系数 fs动摩擦系数 ft48009008001504070.2570.70.250.1514（1）初选液压缸的工作压力表 2 工作压力Table 2 Operating pressure工况计算公式液压缸的负载N启动F启=F静F密F启=425/0.9=472.2加速F加=F动F贯F密F加=（25528.882）/0.9=315.42快进F快=F动F密F快=255/0.9=283.3工进F工=F切F动F密F工=（4800255）/0.9=5616.7快退F快=F动F密F快=255/0.9=283.3由以上分析计算可知，该铣床在最大负载约为 5616.7N是的液压系统宜取压力P=2MP。（2）确定液压缸的内径D和活塞竿直径d由液压缸工作负载表可以看出，最大负载为工几年阶段的负载F=5616.7N，考虑两边的差动比为 2，则工作腔的有效工作面积和活塞直径分别为： (8)62/5616.7(2 10 )0.00281AF Pm (9)44 0.002810.0598ADm活塞直径为： (10)20.707 0.05980.0423dD根据行业标准，选取标准直径：63Dmm45dmm根据缸径和活塞竿内径，计算出液压缸实际有效工作面积，无竿腔面积 A1和有竿腔面积 A2分别为 (11)2421/ 43.14 0.063431.17 10ADm (12)22422()/ 43.14 (0.0630.045)415.27 10ADdm则液压缸的实际计算工作压力为： (13)24/4 5616.7/(0.063 )1.802PFDMpa则实际选取的工作压力P=2MP满足要求。按最低工作速度验算液压缸的最小稳定速度。若验算后不能获得最小的稳定速度是，还需要响应家大液压缸的直径，直至满足稳定速度为止。 (14)2/(50/ 250) 100.02 10q vm15由于，所以能满足最小稳定速度的要求。/Aq v计算液压缸各运动阶段的压力，流量和功率。根据上述所确定的液压缸的内径D和活塞竿直径 d，以及差动快进时的压力损失 P=0.5MP，工进时的背压力 P=0.8MP，快退是P=0.5MP，则可以计算出液压缸各工作阶段的压力、流量和功率。如下表：表 3 压力、流量和功率参数Table 3 Pressure, flow and power parameters工况负载F（N）回油腔压力P2105(Pa)进油腔压力P1105(MPa)输入流量q(L/min)输出流量p(kw)计算公式快进启动472.22.97212/()PFAPAA快进加速315.411.7856.785变化值变化值12()qAA v快快进恒速283.311.5836.58314.310.1571Pp q工进5616.7821.940.780.02851122()/pFA pA；1 1qAv1Pp q快退启动472.23.11122()/pFA pA快退加速315.4512.272变化值变化值2qA v快快退恒速283.3512.06210.6890.2151Pp q根据上表可以用坐标法绘制出“液压工况图” ，此图可以直观看出液压缸各运动阶段的主要参数变化情况。（3）确定液系统方案和拟订液压系统原理图1）由于该机床是固定式机械，却不存在外负载对系统作功的工况，并由其工况图可知，这台铣床液压系统的功率小，滑台运动速度不是很高，工作负载变化小。则该液压系统以采用节流式开式循环为宜。现才用进油路节流调速回路。从工况图很清楚地看到，在这个液压系统的工作循环内，液压缸要求油源提供低压大油量和高压小流量的油液。快进加快退的时间和工进的时间分别为 (15)3111315060190602.97 10007 1000lltsvv (16) 22260409.60.25 1000ltsv因此从提高系统效率和节省能量的角度来看，采用单个定量液压泵作为油源显然是不合适的，而宜采用大，小两个液压泵并联供油的油源方案162）选择基本回路。由于不存在负载对系统作功的工况，也不存在负载制动的过程，故不需要设置平衡及制动回路。但必须具有快速运动，换向，速度换节以及调压，卸荷等回路。系统中采用节流调速回路以后，不论采用何中油源形式都必须有单独的油路直接通向液压缸两腔，以实现快速远东。在本系统中，快进，快退换向回路采用所示形式。由工况图中的可知，当滑台从快进转为工进时，输入液压缸的流量由降至，滑台的速度变化交大，可选用行程阀来控制速度的换接，以减小液压冲击。当滑台由工进转为快退时，回路中通过的流量很大进油路中通过，回油路中通过。为了保证换向平稳其见，宜采用换向时间可调的电液式换接回路。由于这一回路换要实现液压缸的差动连接，所以换向阀必须是五通的。3）选择调压和卸荷回路油源中有逆流阀，调定系统工作压力，因此调压 3 问题在油源中解决，无须另外在设置调压回路。而且，系统采用进油节流调速，故溢流阀常开，即使滑台被卡住，系统的压力也不会超过溢流阀的调定值，所以又起安全作用。双液压泵自动两级供油的油源中设有卸荷阀，当滑台工进和停止时，低压，大流量液压泵都可以经此阀卸荷。由于工进在整个工作循环周期中占了绝大部分时间，切高压，小流量液压泵的功率较小，故可以认为卸荷问题已基本解决，就不需要在设置卸荷回路。（4）选择液压元件图 11 液压缸结构示意图Figure 11 Hydraulic cylinder diagram1-防尘圈，2-前端盖密封“O”型圈，3-缸体，4-活塞，5-孔用密封，6-后缸盖，7-活塞杆密封“O”型圈1）确定液压泵的压力液压缸在整个工作循环中的最大工作压力为 2.193MP，如取进油路上的压力损失为，为使继电器能可靠的工作，取其调整压力高出系统最大工作压力，则小流量液压17泵的最大工作压力为 (17)=2.940.82.994ppMpa泵额 (18) =3.75ppMpa小 (19)=1.5ppMpa大2）计算液压泵的流量两个液压泵的向液压缸提供的最大的流量为 14.31L/min，取泄漏系数为KL=1.1，则两个液压泵的实际流量为 (20)1.1 14.3115.751 / minpqL3）选择液压泵的型号由于溢流阀的最小稳定流量为 3L/min，而工进时输入液压缸的流量为0.78L/min，由小流量液压泵单独供油，所以小液压泵的流量规格最少应为3.78L/min。根据以上压力和流量的数值查阅产品样本，最后确定选取小泵排量为6ml/r，大泵排量为 12ml/r的YB型双联叶片泵。当液压泵的转速为n=960r/min时，若取液压泵的容积效率为 0.95，该液压泵的实际输出流量为 (21)(6 12) 940 0.95 10005.47 10.9416.41 / minpqL表 4 液压元件的型号及规格Table 4 Hydraulic component models and specifications序号元件名称估计通过流量（L/min）额定流量(L/min)额定压力(MPa)额定压降(MPa)型号和规格1双联叶片泵5.47+10.9417.5YB1，YB22三位五通电磁阀3680160.535DYF3Y-E19B3行程阀3263160.34调速阀0.780.07-50165单向阀3663160.2AXQF-E10Bqmax=100L/min6液控顺序阀1663160.3XF3-E10B7背压阀0.786316YF3-E10B8溢流阀56316YF3-E10B9滤油器1863160.02XU-J63X8010压力表开关16KF3-E3B3 测点11单向阀3663160.2AF3-EA3B18qmax=80L/min12压力继电器14PF-B8L8 通径表 5 电磁铁动作顺序表Table 5 Magnet order form注：“”表示电磁铁通电吸合，其他表示断电脱开发信YV1YV2YV3YV4aYV4bYV5起动人工按钮上料人工工作夹紧人工按钮定位缸下降xk5磨架进给xk9 xk5 xk3主刃磨削xk1磨架后退凸轮计数松开xk2回转xk8工作台锁紧xk6磨架进给xk3 xk5 xk9圆刃磨削xk1磨架后退凸轮计数松开xk2回转xk8工作台锁紧xk7定位缸上升凸轮计数 xk2工件松开人工按钮下料人工3.2.7 管道设计与管件的选择1液压管件是用来连接泵、阀、缸等液压元件构成液压油传输回路，实现液压能的传递。液压能是以压力和流量的形式传输的。因此液压管道首先应具备承受压力的能力，即必须选用适当材料和壁厚，同时还应保证恰当的流速，即应选用合理的通径。钢管多用于吸回油管路一般选用硬管，即管路尽可能短，过流面积尽可能大以减少吸油阻力。中高压系统多采用无缝钢管；压力在 8-31.5Mpa时采用 20 号冷拔无缝钢管，管路中较长部分一般选软管即胶管（或塑料管）。管道设计注意问题：管道设计压力流量和回油管道流速进行限制、排列走向要一致、尽量水平或垂直布置。油管弯曲处应圆滑，不应由凹痕或压扁现象，短长轴比大于 0.75，尽可能选用高19压软管，有抑制机械振动和噪声的作用。（1）硬管的选用1）压油管油管内径： (23)24Qdv得 (24)304.6114.53dmm式中：d为油管内径；Q为通过油管的流量，取Q=30L/min；v为液压油在油管内允许流速。查液压液压系统元件设计手册第 864 页，据油口公称直径尺寸：取d=15mm，外径为 22mm相应的管接头螺纹为M22 1.5。2）油管内流速 (25)2244 301.69/ min3.14 0.15QVmd满足要求。3）油管壁厚 (26)168 6.30.662 2 800Pdcmcm式中：为液压系统最大工作压力，取值为 140kg/；d为油缸内径；为许用P2cm 拉伸应力单位/，对于钢管=，取=6000/。查液压控制传动gk2cm nbbgk2cm手册，在 P17.5 压力时，安全系数 n=4；故=6000/6=1000kg/，故选用油壁管厚 2cm=mm=1.05mm (27)1000215140考虑到与阀等件的联结，取=3mm。则钢管外径=15+2 3=21mm，选用钢管为20 3。4）回油管选取：为保证统一性，与压油管选用相同。（2）软管的选择（胶管）中高压系统选用钢丝编织型和钢丝缠绕型胶管，查液压控制传动手册第 79920页表 12-5：选用胶管B-140，内径为 13mm，外径：20.5-23.1mm，工作压力为140Mpa，最小曲率半径为 140mm。（3）管接头：详见附录-液压系统图中标示。（4）螺纹连接：采用 60 圆锥管螺纹：适用于机器的油管及水管等的连接，内外螺纹配合无间隙。（5）密封件设计与选择。倾斜油缸的密封为例：选用了O型密封圈、V型密封圈。查液压控制传动手册第 825 页表 13-1，由于系统压力小于 25Mpa，故选用O型氟化乙丙烯封装的密封圈。V型密封圈由支承环、密封环、压环三部分成套使用。3.2.8 液压油选取查液压控制传动手册第 12 页，表 1-3 由于温度和压力较高，选用 46 号普通液压油。46 号(HL)普通油：40时运动粘度/10/s 数值范围为 41.450.6；粘度26m指数不小于 90；闪点不低于 170；凝点不高于-10；无机械杂质；氧化稳定性不小于 1000；最重要的是其具有良好的防锈性和氧化安定性，其空气释放能力，抗泡性，分水性和对橡胶密封材料的适应性也较好。故选用此种油液满足要求。3.2.9 滤油器及油箱选取过滤器的功用是清除液压系统工作介质中固体的污染物，使工作介质保持清洁，延长元器件的使用寿命，保证液压元件性能可靠，液压系统故障的 75%左右是由介质的污染所造成的，因此过滤器对液压系统来说是不可缺少的重要辅件。（1）过滤器主要性能参数是指：过滤精度是指油液通过过滤器时能穿过滤芯的球形污染物的最大直径；过滤能力（通油能力）；纳垢容量，允许压降等。（2）过滤器设计时应注意：1)据使用目的选择种类，据安装位置选安装形式2)过滤器应有足够的通油能力，且压力损失要小。（通油能力大于实际通过流量的两倍）。3)过滤精度应满足液压系统或元件所要求的清洁度要求。4)滤芯使用的滤材应满足所用工作介质要求，且有足够的强度。5)过滤器的强度及压力损失要求在合适范围内。6)滤芯的更换和清洗要方便。7)据系统要求考虑选择合适的滤芯保护附件。8)结构尽量简单紧凑，安装形式合理，价格低廉。滤油器：常用网式，线隙式，纸芯式，烧结式等网式滤油器，应用广泛且结构简单，通油能力大，压力损失小，清洗方便，主要用于泵的吸油管路上保护油，故选用21网式滤油器。选型号（WU型网式过滤器）。图 12 WU 型网式过滤器Figure 12 WU mesh filter (3)油箱的设计：本课题选开式油箱，设计问题：油箱的容量及液面、隔板高度；滤油器、箱底坡度选择；是否采用加强筋增加刚性以便承载液压泵或其他液压件；密封装置的选取，是否用热交换器及其安装位置的布置等。具体要求如下：1）油箱一般用 2.5-4mm钢板焊成，尺寸高大的油箱要加焊角铁和肋板以增加刚度。叉车要在油箱上放置电动机，液压泵等其他液压件，故其厚度要增加。2）油箱应有足够容量，以满足散热要求，同时注意到：在系统工作时油面必须保持足够高度，以防液压泵吸空；系统停止时由于油液全返回油箱，不至于造成油液溢出油箱，通常油箱容量可按照液压泵 2-6min的流量估计，油箱液面高度要小于80%，并用油位计观察。油箱有效容积应为泵每分钟流量的 2-3 以上，设泵每分钟流量为，则油箱的有效容量为V=30.6 2.8=85.8L。3）油箱底设计一定坡度以方便放油，箱底与地面有一定距离，（离安装底面150mm 以上以便散热和搬移），最低处应装放油阀。4）泵吸油管上安装网式滤油器，滤油器与箱底间的距离不应小于 20mm。且其和系统回油管应该插入最低油面以防卷入空气和回油冲溅产生气泡，管口和箱底，箱壁距离要大于管径的三倍。此外管口须斜插成 45，并面向箱壁，泄油管不宜插入油中。回油管隔开，以增加油液循环距离，使油液可以有充分时间沉淀污物，排出气泡和和冷却。隔板高度取油面高度的 1/4。为防止油液被污染，箱盖各盖板、管口都要加密封装置，注油口要装滤油网通气孔要装空气滤清器。5）安装热交换器时，还要考虑安装位置，还可以装油温计测油温。6）箱壁要涂防锈涂料油箱设计如下图所示：22图 13 油箱装配图Figure 13 Fuel tank Assembly3.2.10 压力损失的计算管道中的压力损失是指：粘性液体在管道内流动时，都要受到与流动方向相反的流体阻力，消耗的能量将以压力降的形式反映出来，故产生压力损失（或水头损失）。表现为局部压力损失与沿程压力损失之和。又因为柱塞上升时，柱塞与密封环之间的相对滑动也产生摩擦阻力损失： (28)112121.25 10.9=1.0968644444l kl kl kPddd摩擦式中：为起升油缸柱塞直径，单位cm；为密封环与柱塞接触器长度；为密封填ldk料单位工作表面上摩擦力，常取=1kg/。k2cm（1）沿程压力损失 (29)22dLP式中：为沿程阻力系数；为圆管的沿程长度，取管总长 3m；为圆管内径 15mm；Ld为管内平均流速，取 3m/s。行走机械为紊流且光滑，则沿程阻力系数采用公式：=0.04； (30)25. 03164. 0eR查机械设计手册中（液压工程手册单行本）第 644 页表 23.10-2 可知，矿物质液压油的密度范围为 850960kg/m3，据机械设计课程设计手册第二页表 1-5 选取液压油密度为 920kg/m3。由以上公式得：=3.312kg/ P2cm23（2）局部压力损失= = (31)P22式中：总的局部阻力系数，考虑起升油缸工作，则有单向阀，溢流阀，换向阀，起升缸的节流阀等均存在局部压力损失。查5表 8-7-阀类元件局部损失估算：=11+10.5+14+11=6.5kg/ (32)P2cm为确保精确在进行公式验算，查12表 23.2-79，其中：局部阻力取=1.5；弯头处取=0.29 弯头较多，设计弯头 20 个；入口阻力系数=0.5；出口阻力系数=2；所以=1.5 4+1.5+0.5+0.29 20=13.8 (33)=5.72kg/。P2cm=3.31+5.72+1.09=10.12kg/ (34)1P2cm（3）液压系统调节压力为 100+3.31+5.72+1.09=110.12kg/，故选用 140kg/2cm满足要求。2cm3.2.11 节流阀的设计节流阀应该满足一下性能要求：流量调节范围大，流量-压差变化平滑；内漏量小，对外的泄漏口也应小；压力损失小；调节力矩小；动作灵敏；流量稳定性。叉车设计时采用MK单向节流阀。（1）节流阀的结构。如下图所示。主阀座孔主阀芯调节阀接起升油缸孔孔图 14 节流阀Fig 14 Throttle valve （2）节流阀能通过的流量最大起升速度V=0.30.4m/s，即为 1824m/min，根据起升速度的范围计算：空载下降时，初定v=24m/minQ=74.7L/min (35)vD 24243 . 642满载下降时，初定v=18m/min24=56.1L/min vDQ24183 . 642（3）压力当空载后缸下降时，/=11.37/ (36)24DNP9 . 03 . 648 .3182gk2cmgk2cm前缸下降时 P=6.5/cm2；当满载下降（后缸下降）时，假定 P=42.4/cm2，前缸下gkgk降时，假定 P=41.4/cm2。gk（4）节流孔两端的压力差1）空载下降，孔A=11.37-10.12=1.25/cm2，后缸空载下降时压力gk=11.37/cm2。gk2）满载下降，孔B=42.4-10.12=32.28/cm2，后缸满载下降时压力gk=42.4/cm2。gk（5）节流口通流面积，本节流阀采用薄壁小孔查机械设计手册中（液压工程手册单行本）查得： (37)0.885QcfP 式中：c为流量系数，取值为 0.7；f为节流孔通流面积；为节流孔前后压差（即P损失）。利用此公式反求通流面积：Q=74.7L/min (38)vD 24243 . 642Q=56.1L/min (39)vD 24183 . 6421）空载下降，fA=108.26mm2 (40)25. 17 . 0885. 07 .742）满载下降，fB=15.94mm2 (41)28.327 . 0885. 01 .56（6）节流的直径查新编液压工程手册设计手册，表中节流阀的通径及流量表1）空载下降，A口直径dA=9.2mm10mm。 Af426.108425(42)2）满载下降，B口直径dB=3.5mm4mm。 (43)Bf494.154（7）确定弹簧刚度1）空载下降，此时调节阀由于左右压力差的作用，把主阀芯压住。只通过A口回流，但主阀芯不动，即弹簧的压紧力与油压差对阀作用的力平衡。2）满载下降，起升油缸油压增高，调节阀左右压力差也随之升高，主阀开始克服弹簧力向左移动，关闭主阀座上的下孔，仅由小孔B回油，孔C直径为 12mm。因此，弹簧位移为 12mm.参照同类产品选择弹簧刚度K=8kg/cm2。4 4 液压站结构设计15液压站是由液压油箱，液压泵装置及液压控制装置三大部分组成。液压油箱装有空气滤清器，滤油器，液面指示器和清洗孔等。液压站装置包括不同类型的液压泵，驱动电机及其它们之间的联轴器等，液压控制装置是指组成液压系统的各阀类元件及其联接体。4.1 液压站的结构型式机床液压站的结构型式有分散式和集中式两种类型，下面进行介绍：（1）分散式。这种型式将机床液压系统的供油装置、控制调节装置分散在机床的各处。例如，利用机床或底座作为液压油箱存放液压油。把控制调节装置放在便于操作的地方。这种结构的优点是结构紧凑，泄漏油回收，节省占地面积，但安装维修方便。同时供油装置的振动、液压油的发热都将对机床的工作精度产生不良影响，故较少采用，一般非标设备不推荐使用。（2）集中式。这种型式将机床液压系统的供油装置、控制调节装置独立于机床之外，单独设置一个液压站。这种结构的优点是安装维修方便，液压装置的振动、发热都与机床隔开；缺点是液压站增加了占地面积。本次设计采用集中式。4.2 液压泵的安装方式液压站装置包括不同类型的液压泵、驱动电动机及其联轴器等。其安装方式为卧式和立式两种。（1）卧式安装。液压泵及管道都安装在液压油箱外面，安装维修方便，散热条件好，但有时电动机与液压泵的同轴度不易保证。（2）立式安装。将液压泵和与之相联接的油管放在液压油箱内，这种结构型式紧凑、美观，同时电动机与液压泵的同轴度能保证，吸油条件好，漏油可直接回液压26油箱，并节省占地面积。但安装维修不方便，散热条件不好。考虑到空间，占地面积等方面的要求，本设计中采用立式联接。4.3 液压油箱的设计液压油箱的作用是贮存液压油、充分供给液压系统一定温度范围的清洁油液，并对回油进行冷却，分离出所含的杂质和气泡。4.3.1 液压油箱有效容积的确定液压油箱在不同的工作条件下，影响散热的条件很多，通常按压力范围来考虑。本设计中油箱为叉车用，所以油箱不能过大，应为 300-500L。液压油箱的外形尺寸设计。液压油箱的有效面积确定后，需设计液压油箱的外形尺寸，一般设计尺寸比为 1:1:1-1:2:3。但有时为了提高冷却效率，在安装位置不受限制时，可将液压油箱的容量予以增大，本设计中的油箱根据液压泵与电动机的联接方式的需要以及安装其它液压元件需要，选择长为 1.0m，宽为 0.8m，高为 0.6m。4.3.2 液压油箱的结构设计一般采用抗腐蚀性钢材制作，且须考量油箱内表面防腐处理，并顾及与介质之相容性、处理后之可加工性及制造之经济性，条件允许时采用不锈钢制作是最理想的选择。油箱必须有足够的容积，一方面须满足散热的要求，另一方面在液压系统停止工作时应能容纳系统中的所有工作介质，工作时又能保持适当的液位。为了便于随时检查和观察箱内液体液位的情况，应该在油箱壁板的侧面安装液面指示器，指示最高、最低油位。液面指示器一般选用带有温度计的液面指示器。油箱顶板需要装设空气滤清器，对进入油箱的空气进行过滤，防止大气中的杂质污染液压油。空气滤清器的过滤能力一般为油泵流量的两倍，其过滤精度应与液压系统中最细的滤油器的精度相同。油箱内部应刷浅色的耐油油漆。以防止锈蚀。4.4 液压泵结构设计的注意事项（1）液压装置中各部件、元件的布置要均匀、便于装配、调整、维修和使用，并且要适当地注意外观的整齐和美观。（2）考虑液压油箱的大小与刚度，液压泵与电动机装在液压油箱的盖子上或装在液压油箱之外。（3）在阀类元件的布置中，行程阀的安放位置必须靠近运动部件。手动换向阀的位置必须靠近操作部位。换向阀之间应留有一定的轴向距离，以便进行手动调整或装拆电磁铁。压力表及其开关应布置在便于观察和调整的地方。（4）压泵与机床相联的管道一般都先集中接到机床的中间接头上，然后再分别通向不同部件的各个执行机构中去，这样做有利于搬运、装拆和维修。27（5）硬管应贴地或沿着机床外形壁面敷设。相互平行的管道应保持一定的间隔，并用管夹固定。随工作部件运动的管道可采用软管、伸缩管或弹性管。软管安装时应避免发生扭转，影响使用寿命。液压站设计如下图：图 19 液压站俯视图Figures 19 Top view of hydraulic station5 倾斜机构设计计算5.1 倾斜机构设计概述门架倾斜机构是利用倾斜油缸的伸缩运动，使门架绕下部铰点前倾或后倾，达到货叉从水平位置向前或后倾斜一个角度，在可移式叉车和侧面式叉车上门架需沿导轨移动。门架倾角是指无载的叉车在坚实平坦的地面上，门架相对其垂直位置向前或向后倾斜的最大角度。门架前倾角a作用是为便于叉取和卸放货物。后倾角的作用是当叉车带载行驶时，防止货物从货叉上滑落，增加叉车行使的纵向稳定性。门架前倾角一般不小于叉车在水平地面上叉卸卸货物时的最小前倾角与仓库地面的正常坡度角之和。增加门架后倾角,有利于提高叉车的纵向稳定性，但后角加大往往受到叉车结的限制，门架倾角还与轮胎的类型有关。叉车叉货时，后轮负荷大,前轮负荷小,前后轮胎变形量不同，将使门架的前倾角减小。叉车满载行驶时，前轮负28荷大，后轮负荷小，将使门架的实际后倾角减小。为此，对于充气轮胎的叉车,门架的前后倾角都应适当加大。倾斜油缸为双作用活塞式油缸，正确的调整活塞杆的长度，可以保证门架的前后倾角符合工作要求，且倾斜油缸的同侧油缸腔连通，保证两个倾斜油缸协同动作。门架倾斜机构的计算主要是确定倾斜油缸的最大拉力和行程，计算倾斜油缸的的相关尺寸参数，计算缸壁、缸底厚度，并对活塞杆强度、稳定性进行计算与校核。工况一般为 1t的货物上升至最高位置，（且达到amax）。倾斜油缸工作工况如图所示：图 20 倾斜油缸工作工况示意图Figure 20 Tilt cylinder condition schematic diagram倾斜机构的设计要求：（1）设计倾斜油缸，受力分析计算活塞尺寸参数及行程，油缸作用时间。（2）强度与稳定性校核，油缸壁与缸体，缸底厚度计算，螺纹连接计算等。5.2 倾斜机构设计工况：1t的货物上升至最高位置，（且达到）超载系数 1.1。已知参数：门max架前后倾角为；门架离地间隙 100mm；门架离铰点 160mm。6 /12oo（1）倾斜油缸布置在门架两侧，分别与车架及外门架铰接。（2）倾斜油缸型式及数目：双作用活塞杆式，2 个。（3）倾斜油缸行程及长度：作图法求解。5.2.15.2.1 倾斜油缸受力分析及负荷计算参数数值：Q=12501.1=1375kg；G1为货叉滑架重量 160kg；G2为起升油缸等重29量 100kg；G3为外门架重 120kg；G4为柱塞重 15kg；门架升至最大高度时，货物重心至门架铰点之距为(3000-100-160+500)=3240mm，考虑倾角可知：L=3240/0.9=3600mm；门架升至最大高度时，货叉滑架重心至门架铰点之距为L1=3288mm；门架升至最大高度时，起升油缸及内门架起重链等重心高，L2=2220mm；门架升至最大高度时，外门架重心高，L3=1000mm；门架升至最大高度时，柱塞重心高，L4=455mm；货物重心与门架中心线之距l=500+150=650mm；货叉滑架与门架中心线之距l1=440-270=170mm。求倾斜油缸的轴拉力 rlGrlGrlGrlLGrlLQTsinsin3sin)cossin()cossin(44322211kgrrrrr3866sin15455sin1000120sin2220160)cos170sin3288(160)cos650sin3600(1375结构上采用两只油缸，则单只油缸承受轴拉力=T/2=1933kg5.2.2 计算倾斜油缸缸径和活塞杆直径（1）采用双作用油缸，当油进入有杆腔时，活塞杆受力=1933 (44)单T2Tgk式中：P为液压系统压力，由起升油缸选用 100/；为油缸机械效率，用耐油gk2cm橡胶密封，取=0.95；D 为缸内径。选择活塞杆往复运动速度比=1.15 (45)222dDD则=7.6 (46)2D15. 015. 12d2d所以=P（7.6-） (47)单T42d2d=3.9mm (48)2dPT6 . 64单95. 0806 . 619334230结合=7.6=29.8mm2推出：D=5.46mm，d=1.97mm。查参考文献9可知：2D2dD=40，50，63，d=18，22，25 等。故最终选择D为 63mm，d为 22mm按速比 1.15 系列，选D=6.3mm，d=2.2mm。验算：，则符合要求。22=(7.6)250719334TPddkgkg较5.2.3 计算油缸行程在确定倾斜油缸与门架的连接点，与车架的连接点和门架的前后倾角的条件下，可用作图法求得倾斜油缸活塞的行程，拉力和行程确定之后，可设计倾斜油缸，考虑液压系统。BDFEo40024080AACCr=398mmaaaCA图 22 倾斜油缸行程分析Figure 22 Tilt cylinder stroke analysis为了计算方便，引入C和C（作为A和A旋转一定角度后的另一种状态）求行程 H。（1）求BA在COA中，=408mmOA2240080 OA OA在C OA中C OA=arcsin=COA=C OA =11.3 80OAA OD=95-C OA=83.7在AOE中, =sinA OD-240=405.54-240=165.54mm166mmaAOA同理： =510-cosA OD=465.2mm465mmBaOADE=493mmBA22465166 （2）求rOA B=90-A OD+arcsin=76.97（90-A OD=arcsin）BABaAOEr= sin=397.5 mm 398 mmOA（3）求 BA31= BA2 2 .BaaAA OD=96-COC-C 0A=72.7 =A F-240=OAsinA OD-240=149.5mm150mm aA =510-=389mmBa DF2 2.FAOA=416.9mm417mmBA BA2 2 .BaaA综上可得：活塞杆行程为：493mm-417mm=76mm5.2.4 计算油缸作用时间油泵流量的选择一般据起升油缸的要求来决定，至于能否满足倾斜油缸的工作需要，要按门架前倾最大角度时启用的时间来校核，时间一般规定在（1.5-2s）内，据门架由垂直位置到前倾位置所需时间为 (49)2323107.66.310440.6125.86060vvsDstsQv式中：s门架前倾最大角度时活塞行程，作图法求得s=76mm=7.6cm；Q为油泵的额定流量（L/min）暂取为起升油缸的流量Q=25.8L/min；为油泵的容积效率，取值为v0.9；P 为实际倾斜油缸活塞推出的压力。 (50)24DTp推kgT8.5295398sin45515sin1000100sin2220100398cos170sin3288160398cos650sin36001375推所以：=/2=2647.92648kg (51)推单T推Tgkkg/5 .8995. 03 . 6426482P2cm以起升油缸公称压力 100Mpa，即 89.5100140（Mpa）是满足要求的。当 P=89.5kg/时，实际流量为：23.1L/min；对应的实际油缸作用时间t=0.68s2cm综上：油缸作用时间不在（1.5-2s）内，所以为了弥补这一弊端在油缸的各进油管路中装有回油节流阀以减慢油缸的动作速度。325.2.55.2.5 稳定性校核根据力矩平衡，列出下式： (52)0cossin1144332211lGQlLGLGLGLGQL上述方程各项除 cos得tan= 4433221111LGLGLGLGQLlGQl0158. 045515100012022201003288160360013751701606501375 =8.98(向后倾斜)由参考文献11，压杆稳定性校核计算步骤如下：1）根据压杆支承情况及相关尺寸求出压杆的柔度（长细比）2）根据压杆材料求出和213）由值确定压杆类型，并选用适当的公式求出临界力或临界应力4）按压杆稳定条件计算。上式所求结果含负号表示此时油缸后倾=8.98时才开始进入受压工况，在门架后倾最大角=12活塞杆受压最厉害。活塞杆受压最大时计算油缸的长细比：（采用两端铰支=1，据Q235 钢的E=200Gpa，=200Mpa）p=100 (53) 1200102003据经验公式Q235 钢的 a=304，b=1.12，=62 (54)2bas12. 1235304再据公式= (55)iAI=16.89 (56)223 . 66 . 747 .411l式中：焊缝外径 7.6cm；满足，即62100。故，此时油缸的活塞杆属于短杆，不存在失稳计21算与校核，稳定性计算略去。335.2.6 油缸壁厚的计算=cm=0.66cm=6.6mm (57) 2DPy80023 . 6168式中：PY为液压系统最大工作压力的 1.2 倍，其值为 140 1.2=168kg/cm2；D为油缸内径 6.3cm；s为缸体材料的许用应力，20 号无缝钢 sb=4000kg/cm2安全系数，n=5，故s=4000/5=800kg/cm2；选用油缸壁厚=(76-63)/2=6.5mm，故壁厚强度满足。综合以上，设计的倾斜油缸缸体的零件图为：图 23 倾斜油缸缸体零件图Fig 23 Tilt cylinder cylinder parts diagram5.2.7 活塞杆强度计算由于活塞杆受压时不存在稳定性计算，则活塞杆计算主要为拉、压强度破坏。= (58) 2max4杆dT (59) max4 Td杆式中：Tmax为取受压时最大压力，T推 =2648kg；s= s/b =6000/3=2000kg/cm2，45号钢 s=6000kg/cm2，n取 3。d=1.29cm (60) 200026484则选用d=2.2cm强度足够。5.2.8 缸体螺纹连接计算螺纹处拉应力=294.2kg/cm2 (61)(4221DdKP)3 . 62 . 7(785. 0193345. 12234 (62)210333310.12 1.45 1933 8109.4/0.2 ()0.2 (7.26.3 )K KPdkg cmdD式中：K为螺纹预紧力系数，通常取K=1.25-2.5，暂取 1.45；P为拉力，其值1933kg；D为缸内径 6.3mm；为螺纹内径=7.188mm；为螺纹直径 8mm；为螺纹1d0d1K内摩擦系数，取值为 0.12。故合成应力为=350kg/cm2 (63)n223224 .10932 .294则，螺纹处强度足够。n 5.2.9 缸底厚度及缸底的焊缝强度计算（1）缸底厚度=0.84cm=8.4mm (64) PD 25 . 010001405 . 45 . 02式中：缸底内径；P为液压系统最大压力 140kg/cm2；s为许用拉力 sb/n，因为D20 号钢的 sb=4000，n取 4，故有s=1000kg/cm2；结构上要求缸底厚度要超过 7mm才可，故满足要求。（2）缸体和缸底焊缝强度计算焊缝应力： (65)2222222468418/()(7.66.8 ) 0.744Pkg cmDd式中：P为油缸推力，其值为 2648；为焊接效率；为焊缝外径，其值为kg1D7.6cm；焊缝内径，其值为 6.8cm；2d最终设计出的倾斜油缸装配图示：图 24 倾斜油缸装配图Fig 24 Tilt cylinder assembly6 结论35在本次毕业设计中，碰到了许多自己开始毕业设计前所没想到的或是以前不太熟悉的知识点，如零件设计时相关数据的计算、查证、绘制零件图、零件图的标注等，基本上是把自己这大学四年来所学的课程来了一次大综合，是对我们在大学期间所学的专业知识进行系统的检验。可以说通过本次设计我熟悉和学到了很多专业知识，尤其在机械制图方面，通过对所设计的零部件的表达，使我的制图能力更上一个台阶，但是这还远远不够，我知道这离我们所要达到的目标还有大段的距离，所谓学无止境，知识是永远也学不完的，在以后的工作实践中要对自己严格要求，本着谦虚谨慎和积极进取的态度主动发现自己的不足之处，并对其加以弥补。本次设计是一次理论与实际相结合的过程，由于经验不足，参考了现有的设计资料，但其中仍存在一些问题。设计中也许有某些细节没有考虑到，使设计不是很准确。在设计过程中，通过自己认真思考和老师的指导，理论联系实际，解决了不少实际问题，这不仅培养了解决问题的能力，而且在设计过程中增加了同学和老师的感情，提高了我的沟通能力和表达能力。参考文献1 濮良贵，纪名刚.机械设计M.北京：高等教育出版社，2004.02：151452 陶元芳.叉车构造与设计.机械工业出版社.2001：22673 范祖荛. 现代机械设备设计手册.机械工业出版社.2008：34544 陈慕忱.装卸搬运车辆. 人民交通出版社.2007：1371985 胡宗武.非标准机械设备设计手册.机械工业出版社.2008：56756 王耀斌，简晓春主编. 物流装卸机械. 北京: 人民交通出版社. 2003：781097 陈慕忱主编. 装卸搬运车辆. 北京: 人民交通出版社. 1986：12388 刘娜，陈慕忱主编. CPD1 型电动叉车设计计算书（液压系统）. 武汉. 1980：251209 陈启松主编. 液压传动与控制手册. 上海: 上海科技出版社. 2006. 12：598210 许福玲，陈尧明主编. 液压与气压传动（第二版）. 北京: 机械工业出版社. 2006：15616711 刘鸿文主编. 材料力学第四版. 北京: 高等教育出版社. 2004：209012 吴克坚，于晓红，钱瑞明主编. 机械设计. 北京: 高等教育出版社. 2003：337813 吴宗泽，罗圣国主编. 机械设计课程设计手册. 北京: 高等教育出版社. 2004：1724514 刘毅整理编著. CPD1.5 型叉车课题毕业设计指导书. 南京: 东南大学收藏. 1985：266715 周恩涛主编. 液压系统元器件选型手册. 北京: 机械工业出版社. 2007：27763616 张利平主编. 液压气动技术实用问答. 北京: 化学工业出版社. 2007：457917 机械设计编委会. 机械设计手册（液压单行本）. 北京: 机械工业出版社. 2007: 237918 雷天觉主编.新编液压工程手册（下）. 北京：北京理工大学出版社,2005：209020 周明衡，常绕功主编. 管路附件设计选用手册. 北京: 化学工业出版社. 2004：567521 Horberry T, LarssonTJ, Johnston I, Lambert J, Forklift safety. traffic engineering and intellirent transport systems: a case study. APPLIED ERGONMICS.35(2004):57-9822 Sangivanni-Vincentelli A. Electroic-system design in the automobile industry. IEEE MICRO. 23(2003):8-18致谢本论文是在杨文敏老师的悉心指导和热情关怀下完成的，使我对叉车的液压系统有了很深层次的了解，对我的大学毕业受益匪浅。通过本次毕业设计，我又系统地学习、总结了四年来的知识，许多原来只是感性认识的东西也变的理性化了，同时也体验了作为一名工程技术人员的艰辛。非常感谢杨老师在设计中对我的悉心引导、支持与帮助，您的严谨治学态度和崇高的敬业精神，将使我受益非浅。在大学学习和生活的四年中，得到了众多老师的教导以及很多同学的帮助，使我在大学中学到了丰富的基础知识和专业知识，为本次设计以及今后的工作生活打下了坚实的基础。在此，对以及工学院的各位领导和老师表示衷心感谢并致以崇高的敬意；对本次设计的指导老师表示最诚挚的谢意！精品文档精品文档精品资料精品文档- 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