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VF-0.850空气压缩机的设计（整体设计编程及1-2级缸设计）【11张图纸】【优秀】

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摘要

　　　压缩机是用来提高气体压力和输送气体的机械。从能量转换的方式来看，压缩机是属于将原动机的动力能转变为气体压力的工作机。本设计为中压活塞式空气压缩机设计。活塞式压缩机与其他类型的压缩机相比，其优点是：压力范围最广、效率高、适应性强，即排气量范围较广，且不受压力高低的影响。活塞式压缩机应用较广泛，例如在吹瓶机、核电站、仪表等方面，特别是在中小制冷范围内成为应用最广，生产批量最大的一种机型。

　　　本次整个设计的内容包括压缩机的总体、气缸及基本部件的设计。主要通过热力计算和动力计算来确定压缩机的总体结构方案设计，和各种零部件的设计。同时，在本次的设计过程中，开发了一个计算机软件来完成热力计算和动力计算，借助AutoCAD绘图软件绘图。

关键词：活塞式压缩机；计算机编程；热力计算；动力计算；主要零部件设计

摘要III

AbstractIV

目录V

1 绪论1

1.1本课题的研究内容和意义1

1.2国内外的发展概况1

1.3本课题应达到的要求2

2总体设计方案3

2.1设计参数及依据3

2.1.1 设计参数3

2.1.2 设计活塞压缩机应符合以下基本原则3

2.2 主要结构参数的选择3

2.2.1 转速n3

2.2.2 行程S3

2.2.3 活塞平均速度4

2.3 结构方案的选择4

2.3.1 气缸排列的型式及其选择4

2.3.2 运动机构的结构及选择5

2.4 中间冷却器5

3 热力计算7

3.1 概述7

3.2 热力计算原始数据13

3.3 初步确定各级名义压力15

3.4 计算各级排气温度17

3.5 确定各级的排气系数19

3.5.1 容积系数19

3.5.2 压力系数21

3.5.3 温度系数21

3.5.4 气密系数21

3.5.5 排气系数22

3.6 确定各级干气系数22

3.7确定各级抽气系数22

3.8 确定各级气缸行程容积22

3.9 确定各级气缸直径24

3.10 圆整后各级名义压力及温度26

3.10.1 确定圆整后各级实际行程容积26

3.10.2 求各级压力修正系数、27

3.10.3 修正后各级名义压力及压力比29

3.10.4 修正后各级排气温度30

3.11 计算活塞力31

3.11.1 计算气缸内实际吸排气压力31

3.11.2 计算各列的活塞力32

3.12 计算轴功率，选取电机35

3.12.1 计算各级指示功率35

3.12.2 整个机器总指示功率36

3.12.3 轴功率36

3.12.4 选择电机36

4 动力计算37

4.1 概述37

4.2 初始数据37

4.3 作各级气缸设计示功图37

4.4 作往复惯性力图44

4.5 计算各级往复摩擦力47

4.6 作综合活塞力曲线图47

4.7 作切向力图52

4.8 确定飞轮距56

5 主要零部件设计58

5.1 一、二级气缸设计58

5.1.1 气缸结构型式58

5.1.2 气缸结构设计58

5.2 一、二级活塞组件61

5.2.1 活塞61

5.2.2 活塞环与活塞环的润滑62

5.3 一、二级气阀65

5.3.1 气阀的基本要求65

5.3.2 气阀主要参数的确定65

结论与展望71

6.1 结论71

6.2 不足之处及未来展望71

致谢72

参考文献73

附录74

2总体设计方案

2.1设计参数及依据

2.1.1 设计参数

　　　排气量：0.85m3/min

　　　压缩介质：空气

　　　进气压力：大气压

　　　公称排气压力：5 MPa(表压力)

　　　排气温度：25℃

2.1.2 设计活塞压缩机应符合以下基本原则

　　　a.满足用户提出的排气量、排气压力，及有关使用条件的要求。

　　　b. 使用寿命要足够长，即压缩机需要大修时间间隔的长，使用可靠性要足够高，及压缩机被迫停车的次数短。

　　　c.有较高的运转经济性。

　　　d.有良好的动力平衡性。

　　　e.维护检修方便。

　　　f.尽可能采用新结构、新技术、新材料。

　　　g.制造工艺性良好。

　　　h.机器的尺寸小、重量轻。

2.2 主要结构参数的选择

　　　所谓结构参数是指能反映机器结构面貌和工作性能的特征数据，如转速n，活塞平均速度Cm、行程S等。选择这些参数时，必须符合压缩机三化（系列化、通用化、标准化）标准。

2.2.1 转速n

　　　由排气量公式可知，排气量随转速的提高而增大。对于已使用的机器，适当提高转速，可使生产能力增大；对于新设计的机器，转速取得高，可使机器尺寸小、重量轻。转速越高，相同功率的电机越小，并有可能与压缩机直联，占地面积小，总的经济性好。因此，近年来，压缩机转速趋于提高。但是，转速提高也带来许多不利因素。当转速增加时，往复惯性力与转速的平方成正比的增加。若最大惯性力大于最大活塞力，则运动机构的设计将以空车运行时的最大惯性力为依据，运动件的利用程度差。因此，设计时应选取恰当的转速，使最大惯性力不超过最大活塞力；对于平衡得不够好的压缩机，高转速会使不平衡的惯性力和力矩增加，使机器和基础的振动加剧；转速高使易损件寿命低。如活塞环、填料函、十字头，连杆大小头轴瓦以及主轴瓦等的磨损均速转速增高而加快。特别是阀片的工作寿命大致与转速成反比，为使阀片有相当的寿命，转速也不宜过高；此外，转速增高，气流在气阀中的速度增大，阻力损耗增加，使压缩机效率降低。

　　　近代压缩机的转速，通常在下列范围：微型和小型：1000~3000rpm；中型：500~1000rpm；大型：250~500rpm。

2.2.2 行程S

　　　在选定行程时，需考虑下列因素：

　　　（1）排气量的大小排气量大，则行程应取得长一些，反之，应短些；

　　　（2）对于立式、V型、W型、扇型等结构形式，活塞行程可以取得小些，这样机器就不太高，方便使用和维修；

　　　（3）气缸的结构主要考虑Ⅰ级缸径与行程要保持一定的比例。若行程太小，则吸、排气接管在气缸上的布置将发生困难（特别是径向布置气阀的情况）。

　　　在保证运转可靠、零部件寿命较长的前提下，趋向于采用高转速、短行程。

2.2.3 活塞平均速度

　　　活塞平均速度是衡量压缩机是否先进的重要参数之一，它与转速、行程直接相关。其值的大小直接影响运动件的磨损、气阀的工作状况和气流的阻力损失等。活塞平均速度、转速n和行程S的关系如下：

QQ截图20131114212143.gif

VF-0.850空气压缩机的设计（整体设计编程及1-2级缸设计）.gif

内容简介：: 无锡太湖学院毕业设计（论文）开题报告题目： VF-0.8/50空气压缩机设计（整体设计编程，一、二级气缸设计）信机系机械工程及自动化专业学号： 0923183 学生姓名：陆暤冉指导教师：俞萍（职称：高级工程师）（职称：） 2012年11月20日课题来源“VF-0.8/50空气压缩机（整体设计编程、一、二级气缸设计）”的课题来源于企业；结合所学知识，老师拟定题目；综合大学里所学的知识，将理论与实践相互结合。科学依据（包括课题的科学意义；国内外研究概况、水平和发展趋势；应用前景等）1、化工、冶金、化肥、食品、医疗等众多企业的生产过程需要用到气体压缩机，而活塞式空气压缩机由于有较高的压缩比，在高压气体生产与输送中尚不能被其它设备所替代，是许多工程项目中的关键设备。2、由于计算机的飞速发展与普遍应用，在活塞式压缩机设计中，设计人员可以使用计算机编程来实现热力计算和动力计算，可以使得设计过程变得迅捷、方便、高效且计算结果精确。3、活塞式压缩机上所用的密封活塞环通常用自润滑材料聚四氟乙烯制成，由于活塞环长期运行在剧烈的摩擦环境下，活塞环极易磨损，导致压缩机不能正常工作。为了减少高分子材料的摩擦磨损，传统气体压缩机活塞环需要用油润滑，以减少活塞环与气缸壁的摩擦磨损，提高活塞环的使用寿命。4、 VF-0.8/50空气压缩机一级活塞环采用金属制造，有油润滑。二活塞环采用自润滑聚合物复合材料制造，为微油润滑，所生产的压缩气体洁净无污染，既节省了大量的润滑油，又可简化生产工艺流程，降低能耗，减少环境污染，是当前活塞式压缩机的发展方向。5、目前压缩机制造业已经发展成为机械制造工业的一个重要组成部分。研究内容1、活塞式空气压缩机的工作原理以及工作形成；2、热力计算和动力计算的计算机编程实现；3、一、二级气缸的主要零部件设计；4、一、二级气缸主要零部件图纸的绘制。拟采取的研究方法、技术路线、实验方案及可行性分析（1）研究方法通过阅读有关资料，文献，收集筛选，整理课题研究所需的有关数据，理论依据，综合运用所学理论知识研究论文课题。（2）技术路线根据已知的压缩机参数并选取适当的系数，然后通过建立的数学模型来编程计算出热力学参数和动力学参数，最后根据热力学参数和动力学参数来确定一、二级气缸的结构参数。（3）可行性分析通过对论文课题的学习研究，达到巩固，扩大，深化已学理论知识，提高思考分析解决实际问题等综合素质的目的。研究计划及预期成果1、对VF-.08/50空气压缩机整体结构进行分析，对传动结构进行筛选，初步选择达到设计要求的结构方案；2、对压缩机的热力部分进行编程计算；3、对压缩机的动力部分进行编程计算；4、对一、二级气缸主要零部件设计；5、对无油压缩机的主要零部件进行强度校核，提高机构稳定性，稳定性。特色或创新之处在VF-0.8/50空气压缩机的设计及计算的过程中，同时设计了一个活塞式压缩机的热力计算和动力计算软件，该软件能方便高效的完成一个热力计算和动力计算，并且计算结果精确，有利于进一步的压缩机的结构设计。已具备的条件和尚需解决的问题（1）已具备的条件拥有机械设计手册等参考资料及文献；到企业进行参观，对空气压缩机进行直观的了解与认识，对所学的机械基础知识有较好的掌握；掌握C#编程语言并熟悉面向对象编程的方法；能熟练运用Visual Studio编程软件；能熟练运用CAD制图软件，提高作图效率。（2）尚需解决的问题对于VF-0.8/50空气压缩机的工作原理不是非常清楚和熟悉，缺乏设计经验。指导教师意见指导教师签名：年月日教研室（学科组、研究所）意见教研室主任签名：年月日系意见主管领导签名：年月日编号无锡太湖学院毕业设计（论文）题目： VF-0.8/50空气压缩机设计（整体设计编程，一、二级气缸设计）信机系机械工程及自动化专业学号：学生姓名：指导教师：（职称：高级工程师）（职称：）2013年5月25日I无锡太湖学院本科毕业设计（论文）诚信承诺书本人郑重声明：所呈交的毕业设计（论文） VF-0.8/50空气压缩机的设计（整体设计编程，一、二级缸设计）是本人在导师的指导下独立进行研究所取得的成果，其内容除了在毕业设计（论文）中特别加以标注引用，表示致谢的内容外，本毕业设计（论文）不包含任何其他个人、集体已发表或撰写的成果作品。班级：机械94 学号： 0923183 作者姓名： 2013 年 5 月 25 日摘要压缩机是用来提高气体压力和输送气体的机械。从能量转换的方式来看，压缩机是属于将原动机的动力能转变为气体压力的工作机。本设计为中压活塞式空气压缩机设计。活塞式压缩机与其他类型的压缩机相比，其优点是：压力范围最广、效率高、适应性强，即排气量范围较广，且不受压力高低的影响。活塞式压缩机应用较广泛，例如在吹瓶机、核电站、仪表等方面，特别是在中小制冷范围内成为应用最广，生产批量最大的一种机型。本次整个设计的内容包括压缩机的总体、气缸及基本部件的设计。主要通过热力计算和动力计算来确定压缩机的总体结构方案设计，和各种零部件的设计。同时，在本次的设计过程中，开发了一个计算机软件来完成热力计算和动力计算，借助AutoCAD绘图软件绘图。关键词：活塞式压缩机；计算机编程；热力计算；动力计算；主要零部件设计AbstractThe compressor is used to increase the gas pressure and gas transportation machinery. Judging from the energy conversion, the compressor is working machine, which can transform the prime mover into gas pressure. This design is for the medium-pressure piston air compressor. Compared with other types of compressors, advantages of piston compressor are: pressure range is the most extensive, high efficiency, adaptability. That means a wider range of displacement and pressure level will not affect it. The piston compressor is used widely, such as blowing machine, nuclear power plants, instrument, particularly in small and medium-sized refrigeration. It is also the largest production volume of a model.The entire design includes the design of the compressor overall, the cylinder and the basic member. The compressor overall structure of the program and various parts of the design is mainly determined by thermodynamic calculation and dynamic calculation.In the design process, I develop a computer software to complete the thermodynamic calculation and dynamic calculation, drawing with AutoCAD drawing software.Key words: piston compressor; computer programming; heating calculation; dynamic calculation; structural design目录摘要IIIAbstractIV目录V1 绪论11.1本课题的研究内容和意义11.2国内外的发展概况11.3本课题应达到的要求22总体设计方案32.1设计参数及依据32.1.1 设计参数32.1.2 设计活塞压缩机应符合以下基本原则32.2 主要结构参数的选择32.2.1 转速n32.2.2 行程S32.2.3 活塞平均速度42.3 结构方案的选择42.3.1 气缸排列的型式及其选择42.3.2 运动机构的结构及选择52.4 中间冷却器53 热力计算73.1 概述73.2 热力计算原始数据133.3 初步确定各级名义压力153.4 计算各级排气温度173.5 确定各级的排气系数193.5.1 容积系数193.5.2 压力系数213.5.3 温度系数213.5.4 气密系数213.5.5 排气系数223.6 确定各级干气系数223.7确定各级抽气系数223.8 确定各级气缸行程容积223.9 确定各级气缸直径243.10 圆整后各级名义压力及温度263.10.1 确定圆整后各级实际行程容积263.10.2 求各级压力修正系数、273.10.3 修正后各级名义压力及压力比293.10.4 修正后各级排气温度303.11 计算活塞力313.11.1 计算气缸内实际吸排气压力313.11.2 计算各列的活塞力323.12 计算轴功率，选取电机353.12.1 计算各级指示功率353.12.2 整个机器总指示功率363.12.3 轴功率363.12.4 选择电机364 动力计算374.1 概述374.2 初始数据374.3 作各级气缸设计示功图374.4 作往复惯性力图444.5 计算各级往复摩擦力474.6 作综合活塞力曲线图474.7 作切向力图524.8 确定飞轮距565 主要零部件设计585.1 一、二级气缸设计585.1.1 气缸结构型式585.1.2 气缸结构设计585.2 一、二级活塞组件615.2.1 活塞615.2.2 活塞环与活塞环的润滑625.3 一、二级气阀655.3.1 气阀的基本要求655.3.2 气阀主要参数的确定65结论与展望716.1 结论716.2 不足之处及未来展望71致谢72参考文献73附录74151VF-0.8/50空气压缩机的设计（整体设计编程，一、二级缸设计）1 绪论1.1本课题的研究内容和意义随着现代工业的发展，压缩机的使用已十分普遍，所占的地位相当重要。压缩机是输送气体介质并提高其压力能的机械装置，它在国民经济各部门中特别在化工、石油、矿山、冶金、机械、农田灌溉以及国防工业中已成为必不可少的关键设备。其重要的应用场合有：(1) 化工工艺过程上的应用在化工生产中，为了保证某些合成工艺能在高压条件下进行，往往通过压缩机把气体预先加压到所需的压力。例如高压聚乙烯的聚合反应要求把乙烯加压到2000kgf/cm2以上；合成氨的反应要求把合成气加到320kgf/cm2;石油裂解如氢要求把氢气加压到150kgf/cm2以上等。(2) 动力工程上的应用在动力、机械以及国防工业上常采用压缩空气作为驱动装置的动力气源，例如常见的风动机械，要求空气的压力为8kgf/cm2；用于控制仪表及自动化装置上的气源压力6kgf/cm2；国防工业中某些武器的发射、潜水艇的沉浮、鱼雷的发射驱动等需要采用压缩机。(3) 气体输送在石油、化工生产中，为了输送原料气，常用压缩机增压。例如从油田输出天然气，煤气厂输出煤气都要求事先加以增压。压缩机种类有很多，有往复式压缩机、回转式压缩机、透平式压缩机、喷射式压缩机等。其中在往复式压缩机中最典型的是活塞式压缩机。活塞式压缩机是依靠气缸内活塞的往复运动来压缩气体。活塞压缩机由于具有耗能低、适应性强和灵活性大等优点，应用比较普遍。所以活塞压缩机的设计及研究对国民经济的发展具有十分重要的意义。由于计算机的飞速发展与普遍应用，在活塞式压缩机设计中，可以使用计算机编程来实现热力计算和动力计算。通过利用计算机编程，可以使得热力计算和动力计算变得迅捷、方便、精确。同时借助AutoCad的二次开发，可以很方便的生成气缸的示功图、综合活塞力图、切向力图和总切向力图。本次设计中编程语言采用C#。C#是一款面向对象的编程语言，是微软公司在2000年7月推出.NET Framework的第1版时提供的一种全新语言，它从C和C+语言演化而来，并吸取了以往的教训，考虑了其他语言的许多优点，并解决了它们的问题12。本次设计使用Visual Studio 2010开发工具进行所有的C#编程。1.2国内外的发展概况近年来，国民经济不断的发展，行业集中度提高了许多，大企业进一步集中供货。气体压缩机的产业布局，正在逐步合理的向新局面发展。由于战略性的经济重组的不断推进，很多不合格的企业退出，杰出的企业找准发展方向，加强主要业务的发展，不断做大做好，达到强强联合，承担起国家重大技术装备项目。在相关政策方面，为应对全球性金融危机对我国经济的影响，早在09年年初，国家已经制定了一系列的刺激经济方案，重点调整振兴包括石化、冶金等气体压缩机的下游产业在内的十大产业。由于这些措施，使得气体压缩机产业得到了积极的发展，同时也使得压缩机行业经济在2009年的下半年逐渐变好。在开拓国际市场方面，压缩机行业应积极而谨慎地探索自己的国际化道路。近年来，压缩机行业的国际化步伐放缓，特别是在2009年，压缩机的出口形势不容乐观，这主要表现于国内压缩机行业技术发展水平与国外压缩机技术发展水平存在一定的差距，真正意义上的具有国际竞争力的大型国际企业集团还没有形成。但是在将来，压缩机的需求在我国压缩机市场中将进一步提高。2013年，是压缩机行业发展的新起点，预计行业未来呈现出新的发展态势。首先是结构调整将有重大突破。目前在我国的压缩机行业中，企业规模小而且分散，产业集中度低；生产力布局不合理现象依然存在；企业节能减排的任务重；科技创新能力不强；资源控制力不强，保障体系建设滞后等。正因为压缩机行业中存在这些矛盾，所以，特别的要在压缩机行业中特别的调整好压缩机产业结构，不断升级产业，并且解决压缩机行业的重大问题，不影响其发展。第二，行业内要大力推动共性技术研究开发，掌握核心技术、关键技术的自主知识产权。当前，压缩机行业共性技术的科研经费投入不足，研究开发力量薄弱。2013年，各企业应加大在我国重点培育自主知识产权的技术装备研发力量。可以循序渐进地加强建设国家工程技术研究中心、国家重点实验室、行业科研院所等共性技术研究开发平台，重点对原创性技术、战略性关键技术、及共性技术的研究开发，并且培养一支既精通基础技术又熟悉行业技术的高科技人才队伍，努力使其掌握关键技术、核心技术和重要产品的自主知识产权。第三，进入加快发展制造服务业阶段。当前，压缩机行业存在一些不利于产业发展的缺陷，如缺少高端技术，企业规模偏小等。面临这些问题和激烈的市场竞争，压缩机企业极需提高自身的核心竞争力，转变增长方式。在制造过程中，并且在市场调研，销售，产品报废回收过程中，力争为客户提供方便，高品质的优异服务，这点对一个压缩机企业的发展有着重要意义，因为通过这些可以实现可持续发展。现代服务业主要投入的大部分是人力资本和知识资本，这些解决了压缩机企业发展、升级问题，并且提升了市场竞争力。我国往复压缩机设计与制造技术水平跟国外水平相比，主要差距是在研究基础理论上的差距，开发产品的技术能力相对较低，落后国外的工艺装备和实验手段，产品技术起点不高。另外，技术含量高和特殊要求的产品在国内压缩机市场上供不应求。1.3本课题应达到的要求1、根据设计参数，利用计算机编程进行压缩机的热、动力计算（主要包括缸径的确定，电动机功率计算及选型，压缩机中的作用力的分析，飞轮距的确定）；2、对压缩机主要零件进行强度校核；3、根据计算结果，确定压缩机结构尺寸，绘制主要零部件图及一、二级气缸组装图；4、查阅相关资料，完成毕业设计说明书一份，不少于30页。2总体设计方案2.1设计参数及依据2.1.1 设计参数排气量：0.85m3/min压缩介质：空气进气压力：大气压公称排气压力：5 MPa(表压力)排气温度：252.1.2 设计活塞压缩机应符合以下基本原则a.满足用户提出的排气量、排气压力，及有关使用条件的要求。b. 使用寿命要足够长，即压缩机需要大修时间间隔的长，使用可靠性要足够高，及压缩机被迫停车的次数短。c.有较高的运转经济性。d.有良好的动力平衡性。e.维护检修方便。f.尽可能采用新结构、新技术、新材料。g.制造工艺性良好。h.机器的尺寸小、重量轻。2.2 主要结构参数的选择所谓结构参数是指能反映机器结构面貌和工作性能的特征数据，如转速n，活塞平均速度Cm、行程S等。选择这些参数时，必须符合压缩机三化（系列化、通用化、标准化）标准。2.2.1 转速n由排气量公式可知，排气量随转速的提高而增大。对于已使用的机器，适当提高转速，可使生产能力增大；对于新设计的机器，转速取得高，可使机器尺寸小、重量轻。转速越高，相同功率的电机越小，并有可能与压缩机直联，占地面积小，总的经济性好。因此，近年来，压缩机转速趋于提高。但是，转速提高也带来许多不利因素。当转速增加时，往复惯性力与转速的平方成正比的增加。若最大惯性力大于最大活塞力，则运动机构的设计将以空车运行时的最大惯性力为依据，运动件的利用程度差。因此，设计时应选取恰当的转速，使最大惯性力不超过最大活塞力；对于平衡得不够好的压缩机，高转速会使不平衡的惯性力和力矩增加，使机器和基础的振动加剧；转速高使易损件寿命低。如活塞环、填料函、十字头，连杆大小头轴瓦以及主轴瓦等的磨损均速转速增高而加快。特别是阀片的工作寿命大致与转速成反比，为使阀片有相当的寿命，转速也不宜过高；此外，转速增高，气流在气阀中的速度增大，阻力损耗增加，使压缩机效率降低。近代压缩机的转速，通常在下列范围：微型和小型：10003000rpm；中型：5001000rpm；大型：250500rpm。2.2.2 行程S在选定行程时，需考虑下列因素：（1）排气量的大小排气量大，则行程应取得长一些，反之，应短些；（2）对于立式、V型、W型、扇型等结构形式，活塞行程可以取得小些，这样机器就不太高，方便使用和维修；（3）气缸的结构主要考虑级缸径与行程要保持一定的比例。若行程太小，则吸、排气接管在气缸上的布置将发生困难（特别是径向布置气阀的情况）。在保证运转可靠、零部件寿命较长的前提下，趋向于采用高转速、短行程。2.2.3 活塞平均速度活塞平均速度是衡量压缩机是否先进的重要参数之一，它与转速、行程直接相关。其值的大小直接影响运动件的磨损、气阀的工作状况和气流的阻力损失等。活塞平均速度、转速n和行程S的关系如下：（2.1）式中活塞平均速度，m/s；压缩机转速，rpm；活塞行程，m。为顾及易损件的寿命及运转的经济性，对于大、中型工艺用压缩机，一般可取3.54.5m/s；对于大批生产的动力用固定式空压机，为获得较高的效率，可取34m/s；对于移动式压缩机，为尽量减小尺寸和重量，可取45m/s；对于微、小型压缩机，为了让结构紧凑些，可以选取较小的行程，尽管转速较高，但是活塞平均速度较低，约2m/s左右。对于无油润滑的迷宫式压缩机，要求，以减少泄露；而用聚四氟乙烯或石墨环等自润滑材料活塞环及填料的压缩机，；乙炔压缩机具有爆炸的危险性，为安全计，取。在往复活塞式压缩机设计中，由于一定的参数和使用条件的限制下，第一步应考虑选择适当的活塞平均速度，因为（1）活塞平均速度的高低，对运动机件中的摩擦和磨损有直接的影响。对气缸内的工作过程也有影响。（2）本次设计的压缩机二、三级采用微油自润滑材料的半无油润滑，活塞速度过高，功率的消耗及排气温度将会过高。严重地影响压缩机运转的经济性和使用的可靠性。故VF-0.8/50空气压缩机行程定为90mm，转速定为750rpm。根据式（2.1），活塞平均速度为：2.3 结构方案的选择活塞式压缩机的结构特点主要体现在气缸排列的型式，即指气缸中心线的排列位置和运动机构的结构这两个方面。2.3.1 气缸排列的型式及其选择根据气缸排列的型式不同，有立式压缩机、卧式压缩机、对称平衡型压缩、对置型压缩机及角度式压缩机。角度式压缩机，气缸中心线具有一定的角度，但不等于零度和180。按气缸中心线的位置不同，又可以分为W型、V型、L型和扇型。角式压缩机的特点是同一曲拐上装有几个连杆，与每个连杆相应的气缸中心线间具有一定的夹角，角式压缩机优点有：（1）各列一阶往复惯性力的合力，可用装在曲轴上的平衡重达到大部分或完全平衡，动力平衡好，机器可取较高的转速，可达5002200rpm。（2）气缸彼此错开一定角度，有利于安排气阀及配置中间冷却器，结构紧凑。（3）若干列的连杆连接在同一曲拐上，曲轴的曲拐数减少，轴向长度可缩短，主轴颈有可能采用滚动轴承。由于本设计排气量和排气压力比较小，选择角度式中的V型压缩机，使其具有较好的平衡性，同一曲拐上相邻的汽缸中心线夹角做成90，如图2.1。图2.1 V型压缩机结构图2.3.2 运动机构的结构及选择活塞式压缩机的运动机构有：无十字头和带十字头两种。本设计为无十字头。选择无十字头的理由是：结构简单、紧凑，机械高度较低，相应的机械重量较轻，一般不需要专门的润滑机构。同时本次选择的是v型结构，无十字头适用于小功率范围内使用。 2.4 中间冷却器冷却器对上一级排出气体的冷却效果的好坏直接影响到机器的性能，所以冷却器的设计也是本系列压缩机设计的一个重要部分。根据已有的科研成果和实践经验先选型，风冷中冷器采用铝制板翅式中冷器，一级中冷器和二级中冷器组合在一起，结构紧凑，再由兼作风扇作用的飞轮对中间冷却器进行强制冷却。试验证明该中间冷却器起到了很好的冷却效果。空气由一级进气阀吸入级差式气缸底部的一级气缸，压缩后,一级压缩空气经一级排气阀排出，经一级中间冷却器冷却后，气体温度由140左右降到25左右经二级进气阀进入级差式气缸的上部二级气缸压缩，二级压缩空气经二级排气阀排出，再经二级中间冷却器冷却后，气体温度由150左右降到25左右，经三级进气阀进入级差式气缸的上部三级气缸压缩后进入储气罐。见图2.2 。图2.2 中间冷却器1.一级冷却 2.二级冷却3 热力计算3.1 概述压缩机的热力计算，是根据气体的压力，容积和温度之间存在一定的关系，结合压缩机的具体特性和使用要求而进行的，其目的是要求得最有利的热力参数(各级的吸排气温度，压力，所耗动力）和适宜的主要结构尺寸（活塞行程，气缸直径等）。本次计算利用计算机编程辅助，采用基于对象和面向过程的方法编程。基于对象就是将压缩机的属性、结构、零部件（如气缸、活塞等）数据抽象出来，将数据集中起来，便于直观的操作。面向过程就是按热力计算的步骤流程来计算，通过向接口输入参数触发对象的一个计算过程（见图3.1）。活塞式压缩机热力计算的过程如图3.2所示。图3.1 软件总构架图3.2 热力计算流程图图3.3 StageHeads数组图3.4 LineHeads数组图利用C#语言可以简单的将压缩机的属性、零部件表示出来。见如下代码：public class CPistonCompressorprivate ulong StructureType; /结构类型private ulong NumberOfCylinders; /气缸数目public CCylinder cylinders;/气缸private ulong Stage; /压缩级数private ulong Line;/气缸列数public StageHeadNode StageHeads; /气缸级结点public LineHeadNode LineHeads; /气缸列列结点public CPower AxlePower;/轴功率public CPower IndicatedPower; /各级指示功率public CPower SumIndicatedPower; /总指示功率public CCoefficient MachineEfficientcy;/机械效率public CPower MotorPower; /电机功率public CCoefficient Multiple; /电机功率是轴功率的多少倍public CForce ReciprocateFriction;/各级往复运动摩擦力private CPressure SuctionPressure; /进气压力private CPressure DischargePressure;/输气压力private CTemperature SuctionTemperature;/进气温度private CTemperature DischargeTemperature;/输气温度public MixGas WorkingMedium;/工质public CCoefficient RelativeHumidity;/气体相对湿度public double ReciprocatingPartsMass;/往复运动件的质量public ReciprocatingInertialForce I;/往复惯性力private Link link; /连杆private Crank crankpin; /曲柄public CCoefficient RatioOfCrankRadiusToLengthOfConnectingRod; /径长比private String label; /压缩机标注private CVolume ExhaustVolume; /排气量private CLength Stroke; /行程private CCoefficient OverallPressureRatio; /总压力比private CCoefficient AveragePressureRatio; /平均压力比private CRevolution Revolution;/压缩机转速在活塞式压缩机类CPistonCompressor中，除了表示了其应有的属性，零部件外，还添加两个数组：StageHeads和LineHeads。前者是一个数组，存储着单链表的头结点，作用是将气缸按级次关联起来（见图3.3）。后者是存储双链表的头结点的数组，这些双链表表示出了各列上气缸的关系（见图3.4），每一条双链表上的结点都是按气缸级次从低到高的排列的有序结点。之所以需要这两个链表头结点数组，是因为，在计算的时候，有时需要按级次遍历气缸，有时需要按列来遍历每个气缸，通过链表的使用，能很方便的做到。在热力计算中，主要通过设置一些参数来计算气缸的吸排气压力、吸排气温度，行程容积，缸径，气体力等。按参数作用，将参数分为性能参数，结构参数以及设计系数，气缸类的属性表示，部分代码如下：public class CCylinderpublic ulong type; /气缸类型private ulong stage; /压缩级别private ulong line; /所在的列public MixGas MixGas;/气体public DesignCoefficient DesignCoe; /设计系数/名义的性能参数 Nominal Performance Parameterpublic NominalPerformanceParameter NPPara;/修正的性能参数 Corrective Performance Parameterpublic CorrectivePerformanceParameter CPPara;/实际的性能参数 Real Performance Parameterpublic ActualPerformanceParameter RPPara;/计算的结构参数 Calculating Constructional Parameterpublic CalculatingConstructionalParameter CCPara;/实际的结构参数 Real Constructional Parameterpublic ActualConstructionalParameter RCPara;public CPiston piston; /活塞public Ergogram AxisErgogram; /轴侧示功图public Ergogram CapErgogram; /盖侧示功图public Ergogram AxisErgogramExpansion;/轴侧施工图展开图public Ergogram CapErgogramExpansion; /盖侧示功图展开图public CForce SumPistonForce; /综合活塞力在热力计算中，吸排气压力、吸排气温度及缸径等需要在修正、圆整等操作，所以将性能参数分为名义性能参数、修正性能参数及实际性能参数，将结构参数分为计算结构参数和实际结构参数。由于这些参数有公共部分，所以将公共参数放到基类当中，再通过继承来表示，部分代码如下：public partial class PerformanceParameter/*基类，性能参数*/public CPressure DischargePressure; /排气压力public CPressure SuctionPressure; /吸气压力public CTemperature DischargeTemperature;/排气温度public CTemperature SuctionTemperature;/吸气温度public CCoefficient PressureRatio;/压力比public class NominalPerformanceParameter/*子类，气缸名义性能参数*/ : PerformanceParameterpublic class CorrectivePerformanceParameter /*子类，气缸修正性能参数*/ : PerformanceParameterpublic CCoefficient Bx; /修正系数xpublic CCoefficient Bx_plus_1; /修正系数x+1public class ActualPerformanceParameter/*子类，气缸实际性能参数*/ : PerformanceParameter/ 排气相对压力损失 Discharge Relative Pressure Losspublic CCoefficient DRelativePressureLoss;/ 吸气相对压力损失 Suction Relative Pressure Losspublic CCoefficient SRelativePressureLoss;public class ConstructionalParameter/*基类，气缸结构参数*/public CLength Diameter; /直径public CVolume SweptVolume; /行程容积public CCoefficient RelativeClearanceVolume; /相对余隙容积public class CalculatingConstructionalParameter /*子类，气缸计算结构参数*/ : ConstructionalParameter public class ActualConstructionalParameter /*子类，气缸实际结构参数*/ : ConstructionalParameterpublic class DesignCoefficient /*设计系数*/public CCoefficient PolytropicIndexOfExpansion; /膨胀过程多变指数public CCoefficient VolumeCoefficient; /容积系数public CCoefficient PressureCoefficient; /压力系数public CCoefficient TemperatureCoefficient; /温度系数public CCoefficient GasLeakCoefficient; /泄漏系数public CCoefficient ExhaustCoefficient; /抽气系数public CCoefficient CondensateCoefficient; /凝析系数public CCoefficient DisChargeCoefficient; /排气系数public CCoefficient AirValve; /气阀public CCoefficient PistonRing; /活塞环;public CCoefficient Filler; /填料为了方便计算活塞力，将活塞抽象出一个类，方便计算使用，代码如下：public class CPiston/*设计系数*/public static readonly uint INNER_DEAD_POINT = 0;/内止点 public static readonly uint OUTSIDE_DEAD_POINT = 1;/外止点 public static readonly uint SUCTION = 0; /吸气 public static readonly uint DISCHARGE = 1; /排气 public CArea AxleArea; /轴侧活塞面积 public CArea AxleWorkArea; /轴侧活塞工作面积 public CPressure AxlePressure;/轴侧压力 public CForce AxleForce; /轴侧活塞力 public CArea CapArea; /盖侧活塞面积 public CArea CapWorkArea; /盖侧活塞工作面积 public CPressure CapPressure;/盖侧压力 public CForce CapForce; /盖侧活塞力 public CForce PistonRodArea; /活塞杆面积 public CLength PistonDisplacement; /活塞位移 public CLength Stroke; /活塞行程在进行热力计算前，需要先创建一个活塞式压缩机对象：CPistonCompressor pc = new CPistonCompressor()，然后通过对该活塞式压缩机对象进行属性的设置和方法的调用来进行热力计算。虽然活塞式压缩机对象的方法是离散的，但是为了便于理解和减少代码的复杂度，热力计算的编程依然根据热力计算流程，将参数有序的输入，然后再计算。由于本次实际着重在于计算而且篇幅有限，对于参数输入图形界面设计将省略写出。3.2 热力计算原始数据排气量0.85m3/min（吸入状态）；进气压力1.03kgf/cm2（绝对压力）；输气压力5MPa（表压）；进气温度20；进气相对湿度0；压缩机转速750r/min；压缩机行程90mm。将进气压力和输气压力设置到压缩机对象中见图3.5，并且设置一些有关压缩机的属性，见图3.6。图3.5 设置进气压力和输气压力图3.6 设置压缩机气缸属性在设置了列数，压缩级数和气缸数目及其属性后，就可以创建StageHeads数组和LineHeads数组。代码如下：public void createStageHeads() /*创建级结点*/StageHeads = new StageHeadNodeStage + 1;StageHeads0 = null;for (ulong i = 1; i = Stage; i+)StageHeadsi = new StageHeadNode();public void createLineHeads() /*创建列结点*/LineHeads = new LineHeadNodeLine + 1;LineHeads0 = null;for (ulong i = 1; i = Line; i+)LineHeadsi = new LineHeadNode();LineHeadsi.line = i; 然后将气缸添加到StageHeads数组和LineHeads数组中。部分代码如下：node = new StageNode();node.cylinder = pc.cylindersNumber;pc.StageHeadsstage.addNode(node);/将气缸关联到列数组中linenode = new LineNode();linenode.cylinder = pc.cylindersNumber;pc.LineHeadsline.addNode(linenode);3.3 初步确定各级名义压力进气压力输气压力总压力比平均压力比各级名义吸、排气压力及压力比经调整后，列表如下：表3-1 各级名义吸、排气压力及压力比级次名义吸气压力(kgf/cm2)名义排气压力(kgf/cm2)名义压力比1.034.1244.1214.70843.5714.708452.043.54图3.7 输入名义压力比输入压力比（见图3.7）在输入各级压力比后，按级次遍历每个气缸计算名义吸排气温度，部分代码如下：public bool calSucDisPressure()if (SuctionPressure = null | DischargePressure = null)return false; /前一级的排气压力CPressure PreDisPressure = null; for (ulong i = 1; i 20321kgf/cm2循环压缩机或更大超高压压缩机达0.25这里根据压力，取相对余隙容积：, , 表3-3 膨胀过程多变指数m()1吸气压力kgf/cm2(绝对)m值1.5m=1+0.5(k-1)1.54m=1+0.62(k-1)410m=1+0.75(k-1)1030m=1+0.88(k-1)30m=k据统计，压缩机的相对余隙容积值多在一下范围内：压力20kgf/cm2 压力20321kgf/cm2循环压缩机或更大超高压压缩机达0.25这里根据压力，取相对余隙容积：, , 计算容积系数的式子：(3.2)根据式（3.2），计算容积系数：根据式（3.2）编写计算容积系数的程序：public void calVolumeCoefficient()/计算膨胀过程指数CCoefficient k = MixGas.k; /绝热过程指数double sucPressure /该级的名义吸气压力 = NPPara.SuctionPressure.KGF_CM2;CCoefficient m = null; /膨胀过程指数if (sucPressure 1.5 & sucPressure 4.0 & sucPressure 10.0 & sucPressure 30.0)m = new CCoefficient(k.COE);DesignCoe.PolytropicIndexOfExpansion = m;/计算容积系数CCoefficient v = null;CCoefficient PressureRatio = NPPara.PressureRatio; /名义压力比CCoefficient a = CCPara.RelativeClearanceVolume; /相对余隙容积CCoefficient exponent = 1.0 / m;CCoefficient coe = new CCoefficient(Math.Pow(PressureRatio.COE, exponent.COE);v = 1.0 - a * (coe - 1.0);DesignCoe.VolumeCoefficient = new CCoefficient(Math.Round(v.COE,2);图3.9 输入各级排气系数3.5.2 压力系数一般的经验值为0.950.98。对于多级压缩机，当气体压力逐级增高后，即使同样大小的压力损失，高压级的相对压力损失将变小，这时取0.981.0。在这里，各级压力系数取：,3.5.3 温度系数压力比越大，气缸温度越高，转速越低，气体导热性越好。本次设计所采用的冷却技术较好，所以温度系数取：,3.5.4 气密系数对于级差式气缸，通过活塞环由高压级向低压及的泄露，对低压级吸气量的影响仅在膨胀和吸气阶段。为了确定气密系数，进行列表计算，把各级应考虑泄露系数的部位综合列表，见表2-43.5.5 排气系数计算排气系数式子：（2.3）根据式子（2.3），计算排气系数：表2-4 各级相对泄漏值及泄漏系数气阀0.020.020.02活塞环0.010.010.010.030.030.030.970.970.973.6 确定各级干气系数第级无水析出：第级计算式子：（3.4）第级压缩机第级以后，气体可近似认为干燥气体，此时气体中的水蒸汽的分压相对于该级的吸气压力已经很小，可以忽略不计，所以第级以后各级的干气系数可按下式计算：（3.5）根据式子（3.3）、（3.4），由于吸气相对湿度，所以3.7确定各级抽气系数本次设计的活塞式压缩机无加气阶段，所以各级抽气系数取：3.8 确定各级气缸行程容积第级行程容积按下式计算：（3.6）第j级行程容积按下式计算：（3.7）按式（3.6）计算第级行程容积：按式（3.7）计算第级行程容积：按式（3.7）计算第级行程容积：根据式（3.6）、（3.7）编写计算程序，代码如下：public void calSweptVolume()CPressure Ps1 = StageHeads1.node.cylinder.NPPara.SuctionPressure;CTemperature Ts1 = StageHeads1.node.cylinder.NPPara.SuctionTemperature;CVolume Vm = ExhaustVolume;CCoefficient Coe = new CCoefficientStage + 1;/总排气系数CCoefficient SumCoe = new CCoefficient(1.0);for (ulong i = 1; i = Stage; i+)Coei = StageHeadsi.node.cylinder.DesignCoe.DisChargeCoefficient; SumCoe = SumCoe * Coei;for (ulong i = 1; i = Stage; i+)StageNode node = StageHeadsi.node;while (node != null)if (i = 1)node.cylinder.CCPara.SweptVolume = new CVolume(Math.Round(Vm / SumCoe).M3_MIN,3),UNITTYPE.M3_MIN);node = node.next;continue;CCoefficient tmp =node.cylinder.DesignCoe.ExhaustCoefficient * node.cylinder.DesignCoe.CondensateCoefficient;tmp = tmp / node.cylinder.DesignCoe.DisChargeCoefficient;tmp = tmp * (Ps1 / node.cylinder.NPPara.SuctionPressure) * (node.cylinder.NPPara.SuctionTemperature / Ts1);if (i = Stage)node.cylinder.CCPara.SweptVolume =new CVolume(Math.Round(tmp * Vm).M3_MIN, 3), UNITTYPE.M3_MIN);elsetmp = tmp / Coei - 1;node.cylinder.CCPara.SweptVolume = new CVolume(Math.Round(tmp * Vm).M3_MIN,3),UNITTYPE.M3_MIN);node = node.next;3.9 确定各级气缸直径因为气缸是正级差式结构的且没有活塞杆，所以先计算出高压级缸径。第级气缸直径：第级气缸直径：因为所以圆整气缸直径1，取：，根据以上过程，编写计算程序，代码如下：public void calDiameter()for(ulong i = 1; i 1) double tmp = 4.0 * node.cylinder.CCPara.SweptVolume.M3_MIN;tmp /= (3.14 * node.cylinder.piston.Stroke.M *Revolution.RPM * StageHeadsi.NumbersOfNode); tmp = Math.Pow(tmp, 1.0 / 2.0); tmp = Math.Round(tmp, 3); node.cylinder.CCPara.Diameter = new CLength(tmp, UNITTYPE.M); node = node.next; if (Stage = 3)StageNode stage1_node = StageHeads1.node;while (stage1_node != null)if (stage1_node.cylinder.Type & CylinderType.DIFFERENTIAL) != 0) if (stage1_node.cylinder.Type & CylinderType.SINGEL) != 0) double tmp = 2.0 * stage1_node.cylinder.CCPara.SweptVolume.M3_MIN;tmp /= 3.14 * stage1_node.cylinder.piston.Stroke.M * Revolution.RPM;tmp += StageHeads2.node.cylinder.CCPara.Diameter.M * StageHeads2.node.cylinder.CCPara.Diameter.M / 2.0; tmp += StageHeads3.node.cylinder.CCPara.Diameter.M * StageHeads3.node.cylinder.CCPara.Diameter.M / 2.0;tmp = Math.Pow(tmp, 1.0 / 2.0);tmp = Math.Round(tmp, 3); stage1_node.cylinder.CCPara.Diameter = new CLength(tmp,UNITTYPE.M); stage1_node = stage1_node.next; 3.10 圆整后各级名义压力及温度 3.10.1 确定圆整后各级实际行程容积编写计算程序，代码如下：public void calRealSweptVolume()double S = Stroke.M;double n = Revolution.RPM;for (ulong i = 1; i = Line; i+)LineNode CurrentNode = LineHeadsi.getLastNode();while (CurrentNode != null)/无活塞杆if (CurrentNode.cylinder.Type & CylinderType.PISTONROD) = 0)if (CurrentNode.next = null)double D = CurrentNode.cylinder.RCPara.Diameter.M;double V = Math.Round(3.14 * D * D * S * n / 4.0, 2);CurrentNode.cylinder.RCPara.SweptVolume = new CVolume(V, UNITTYPE.M3_MIN); else double D1 = CurrentNode.cylinder.RCPara.Diameter.M; double D2 = CurrentNode.next.cylinder.RCPara.Diameter.M; double V = Math.Round(3.14 * (D1 * D1 - D2 * D2) * S * n / 4.0, 2); CurrentNode.cylinder.RCPara.SweptVolume = new CVolume(V, UNITTYPE.M3_MIN); CurrentNode = CurrentNode.previous;for (ulong i = 1; i = Stage; i+)CVolume sum = new CVolume(0,UNITTYPE.M3_MIN); StageNode node = StageHeadsi.node;if (node = null | node.next = null) continue; while (node != null) sum = sum + node.cylinder.RCPara.SweptVolume; node = node.next; node = StageHeadsi.node;while (node != null) node.cylinder.RCPara.SweptVolume = sum;node = node.next;3.10.2 求各级压力修正系数、编写计算程序，代码如下：public void calCorrectionFactor()StageNode FirstStageNode = StageHeads1.node;/第1级计算行程容积 / 第1级实际行程容积CCoefficient coe = FirstStageNode.cylinder.CCPara.SweptVolume /FirstStageNode.cylinder.RCPara.SweptVolume; /计算修正系数xfor (ulong i = 1; i = Stage; i+) StageNode node = StageHeadsi.node;while (node != null)CCoefficient Bx = coe * (node.cylinder.RCPara.SweptVolume / node.cylinder.CCPara.SweptVolume); node.cylinder.CPPara.Bx = new CCoefficient(Math.Round(Bx.COE, 2);node = node.next;/计算修正系数x+1for (ulong i = 1; i = Stage; i+)StageNode node = StageHeadsi.node;while (node != null)if (i != Stage) StageNode NextStageNode = StageHeadsi + 1.node;CCoefficient Bx_plus_1 = coe * (NextStageNode.cylinder.RCPara.SweptVolume / NextStageNode.cylinder.CCPara.SweptVolume); node.cylinder.CPPara.Bx_plus_1 = new CCoefficient(Math.Round(Bx_plus_1.COE, 2); elsenode.cylinder.CPPara.Bx_plus_1 = new CCoefficient(1.0); node = node.next;3.10.3 修正后各级名义压力及压力比计算修正后各级名义压力及压力比，列于表2-5。表2-5 修正后各级名义压力及压力比级次计算行程容积1.6210.3210.078实际行程容积1.440.380.11修正系数11.331.591.331.591名义吸气压力1.034.1214.7084修正后的名义吸气压力1.035.4823.39名义排气压力4.1214.708452.04修正后的名义排气压力5.4823.3952.04修正后的名义压力比5.324.272.23编写计算程序，部分代码如下：public void calCorrectionPressure_Ratio()for (ulong i = 1; i = Stage; i+)StageNode node = StageHeadsi.node;while (node != null) CPressure CorSucPressure = null; CPressure CorDisPressure = null; CCoefficient CorRatio = null; CCoefficient Bx = node.cylinder.CPPara.Bx; CCoefficient Bx_plus_1 = node.cylinder.CPPara.Bx_plus_1;CorSucPressure = Bx * node.cylinder.NPPara.SuctionPressure;CorDisPressure = Bx_plus_1 * node.cylinder.NPPara.DischargePressure;CorRatio = CorDisPressure / CorSucPressure;node.cylinder.CPPara.SuctionPressure = new CPressure(Math.Round(CorSucPressure.KGF_CM2,2),UNITTYPE.KGF_CM2);node.cylinder.CPPara.DischargePressure = new CPressure(Math.Round(CorDisPressure.KGF_CM2,2),UNITTYPE.KGF_CM2); node.cylinder.CPPara.PressureRatio = new CCoefficient(Math.Round(CorRatio.COE,2);node = node.next; 3.10.4 修正后各级排气温度表2-6 修正后各级排气温度级次压力比5.324.272.23吸气温度（）2932982980.28570.28570.28571.61211.51401.2575排气温度()472.36451.17374.74编写计算程序，代码如下：public void calCorCorrectionTemperature()for (ulong i = 1; i = Stage; i+)StageNode node = StageHeadsi.node;while (node != null)CCoefficient k = node.cylinder.MixGas.k;CCoefficient index = (k - 1.0) / k;CCoefficient ratio = node.cylinder.CPPara.PressureRatio;CCoefficient coe = new CCoefficient(Math.Pow(ratio.COE,index.COE);node.cylinder.CPPara.SuctionTemperature = node.cylinder.NPPara.SuctionTemperature; CTemperature CorDisTemperature = coe *node.cylinder.CPPara.SuctionTemperature;node.cylinder.CPPara.DischargeTemperature = new CTemperature(Math.Round(CorDisTemperature.K,2),UNITTYPE.K);node = node.next;3.11 计算活塞力 3.11.1 计算气缸内实际吸排气压力表2-7 气缸内实际吸排气压力级次修正后名义压力(kgf/cm2)相对压力损失(%)气缸内实际压力(kgf/cm2)气缸内实际压力比1.035.4571.0720.995.875.965.4823.3741.0515.3424.584.6123.3952.04240.981.0422.9254.122.36编写计算程序，部分代码如下：public void calRealPressure()for (ulong i = 1; i = Stage; i+)StageNode node = StageHeadsi.node;while (node != null)CPressure CorSucPressure = node.cylinder.CPPara.SuctionPressure; CPressure CorDisPressure = node.cylinder.CPPara.DischargePressure; CPressure RealSucPressure = null; CPressure RealDisPressure = null; CCoefficient RealRatio = null;RealSucPressure = (1.0 - node.cylinder.RPPara.SRelativePressureLoss) *CorSucPressure;RealDisPressure = (1.0 + node.cylinder.RPPara.DRelativePressureLoss) * CorDisPressure;RealRatio = RealDisPressure / RealSucPressure;node.cylinder.RPPara.SuctionPressure = new CPressure(Math.Round(RealSucPressure.KGF_CM2, 2), UNITTYPE.KGF_CM2);node.cylinder.RPPara.DischargePressure = new CPressure(Math.Round(RealDisPressure.KGF_CM2, 2), UNITTYPE.KGF_CM2);node.cylinder.RPPara.PressureRatio = new CCoefficient(Math.Round(RealRatio.COE, 2);node = node.next; 3.11.2 计算各列的活塞力表3-8 内止点活塞力列级次内止点活塞力轴侧(+)盖侧(-)(kgf/cm2)(cm2)(kgf)(kgf/cm2)(cm2)(kgf)-列1.03143.07147.36210.9986.3585.4865-241.00921.03143.07147.36215.3456.72302.8848-列1.03143.07147.36210.99127.17125.8983-342.96421.03143.07147.362122.9215.9364.428表3-9 外止点活塞力列级次外止点活塞力轴侧(+)盖侧(-)(kgf/cm2)(cm2)(kgf)(kgf/cm2)(cm2)(kgf)-列1.03143.07147.36215.8786.35506.8745-1753.691.03143.07147.362124.5856.721394.1776-列1.03143.07147.36215.87127.17746.4876-1459.63381.03143.07147.362154.1215.9860.508编写计算程序，代码如下：public void calPistonPower()for (ulong i = 1; i 1)LineNode node = LineHeadsi.node;while (node != null)/级差式if (node.cylinder.Type & CylinderType.DIFFERENTIAL) != 0)/轴侧始终为大气压if (node.cylinder.Type & CylinderType.SINGEL) != 0)/无活塞杆if (node.cylinder.Type & CylinderType.PISTONROD) = 0) CCylinder cylinder = node.cylinder; CPiston piston = node.cylinder.piston;piston.AxleArea = CArea.getAreaByDiameter(StageHeads1.node.cylinder.RCPara.Diameter);piston.AxleWorkArea = piston.AxleArea;piston.AxlePressureCPiston.SUCTION = new CPressure(1.03, UNITTYPE.KGF_CM2);piston.AxlePressureCPiston.DISCHARGE = new CPressure(1.03, UNITTYPE.KGF_CM2);piston.CapPressureCPiston.SUCTION = cylinder.RPPara.SuctionPressure; piston.CapPressureCPiston.DISCHARGE = cylinder.RPPara.DischargePressure;piston.AxleForceCPiston.INNER_DEAD_POINT = piston.AxlePressureCPiston.DISCHARGE *piston.AxleWorkArea;piston.AxleForceCPiston.OUTSIDE_DEAD_POINT = piston.AxlePressureCPiston.SUCTION *piston.AxleWorkArea;if (node.next != null)piston.CapArea = CArea.getAreaByDiameter(cylinder.RCPara.Diameter); piston.CapWorkArea = piston.CapArea - CArea.getAreaByDiameter(node.next.cylinder.RCPara.Diameter); else piston.CapArea = CArea.getAreaByDiameter(cylinder.RCPara.Diameter); piston.CapWorkArea = piston.CapArea; /内止点，盖侧吸气 piston.CapForceCPiston.INNER_DEAD_POINT = piston.CapPressureCPiston.SUCTION * piston.CapWorkArea; /外止点，盖侧排气 piston.CapForceCPiston.OUTSIDE_DEAD_POINT =piston.CapPressureCPiston.DISCHARGE * piston.CapWorkArea; node = node.next;/计算各列活塞力for (ulong i = 1; i = Line; i+)CForce force_in = new CForce(0.0,UNITTYPE.KGF);CForce force_out = new CForce(0.0,UNITTYPE.KGF);LineNode node = LineHeadsi.node;int state = 0;while (node != null)/级差式if (node.cylinder.Type & CylinderType.DIFFERENTIAL) != 0)if (node.cylinder.Type & CylinderType.SINGEL) != 0)if (state = 0)force_in = force_in + node.cylinder.piston.AxleForceCPiston.INNER_DEAD_POINT;force_out = force_out + node.cylinder.piston.AxleForceCPiston.OUTSIDE_DEAD_POINT; state+; force_in = force_in node.cylinder.piston.CapForceCPiston.INNER_DEAD_POINT; force_out = force_out node.cylinder.piston.CapForceCPiston.OUTSIDE_DEAD_POINT; node = node.next;LineHeadsi.PistonForceCPiston.INNER_DEAD_POINT = force_in; LineHeadsi.PistonForceCPiston.OUTSIDE_DEAD_POINT = force_out;3.12 计算轴功率，选取电机活塞式压缩机的驱动包括驱动机和传动装置。驱动方式和压缩机的结构方案和主要参数的选择有着密切的关系，在选择压缩机结构方案和主要参数时，应该同时考虑驱动方式的选择。驱动活塞式压缩机的却大多数是交流电动机，而交流电动机中又以鼠笼式异步电动机为最多1。中、小功率的鼠笼式电动机可按我国电动机系列（JS、JK、JSQ等）选取。不管是异步电动机还是同步电动机，共同的特点是启动电流大而启动力矩小。3.12.1 计算各级指示功率计算指示功率的式子为：（3.8）式中第x级实际吸气压力，kgf 第x级行程容积，m3/min 第x级容积系数第x级实际压力比计算各级指示功率：根据式（3.8）编写计算程序，代码如下：public void calAxlePower()for (ulong i = 1; i = Stage; i+)double k = StageHeadsi.node.cylinder.MixGas.k.COE;double Ps = StageHeadsi.node.cylinder.RPPara.SuctionPressure.KGF_CM2; double ratio = StageHeadsi.node.cylinder.RPPara.PressureRatio.COE;double COEv = StageHeadsi.node.cylinder.DesignCoe.VolumeCoefficient.COE;double V = StageHeadsi.node.cylinder.CCPara.SweptVolume.M3_MIN;double tmp = 1.634 * Ps * V * COEv * (k / (k - 1.0);tmp *= (Math.Pow(ratio, (k - 1.0) / k) - 1.0);tmp = Math.Round(tmp, 3);IndicatedPoweri - 1 = new CPower(tmp, UNITTYPE.KW); CPower SumPower = new CPower(0.0, UNITTYPE.KW);for (int i = 0; i = P2.KGF)break;tmp = Ps.KGF / Pi.KGF;tmp = Math.Pow(tmp, 1.0 / k.COE);tmp *= S1.MM;tmp = Math.Round(tmp, 3);Si = new CLength(tmp, UNITTYPE.MM);Sj = new CLength(Si.MM / S2.MM * S0.MM, UNITTYPE.MM);CPoint point = new CPoint(Si.MM * Xscale, Pi.KGF);CapErgogram.Compress.AddAPoint(point);point = new CPoint(Sj.MM * Xscale, Pi.KGF);CapErgogram.Expansion.AddAPoint(point); CapErgogram.Compress.AddAPoint(CapErgogram.Compress.End); CapErgogram.Expansion.AddAPoint(CapErgogram.Expansion.End);CapErgogram.Upper = new CLine(CapErgogram.Compress.End, CapErgogram.Expansion.End); CapErgogram.Lower = new CLine(CapErgogram.Compress.Start, CapErgogram.Expansion.Start);计算过程中所得到的数据见表4-2、表4-3、表4-4以及表4-5，由于篇幅关系，详细数据附录。代码中Xscale和 Yscale分别为比例尺，这里Xscale=10.0，Yscale=1.0，这样画下来的图，点横坐标扩大10倍，Y坐标不变。调用AutoCad库，绘出示功图。代码如下：public void ThreadDraw(Object obj)CCurve curve = obj as CCurve; using (AutoCADConnector connector = new AutoCADConnector() /连接AutoCAD /取得当前AutoCAD活动图形对象 AcadDocument aDocument = connector.Application.ActiveDocument; /创建一个名为示功图的新层 AcadLayer newLayer = aDocument.Layers.Add(示功图);newLayer.color = AcColor.acBlue; aDocument.ActiveLayer = newLayer;/把示功图层设置为当前层 AcadSpline spline = aDocument.ModelSpace.AddSpline(curve.Points, curve.Start.getCoordinateArray(), curve.End.getCoordinateArray(); spline.color = ACAD_COLOR.acBlue;AcadSpline s = aDocument.ModelSpace.AddSpline(CapErgogram.Expansion.Points, CapErgogram.Expansion.Start.getCoordinateArray(), CapErgogram.Expansion.End.getCoordinateArray();s.color = ACAD_COLOR.acBlue; AcadLine line1 = aDocument.ModelSpace.AddLine(CapErgogram.Upper.Start.getCoordinateArray(), CapErgogram.Upper.End.getCoordinateArray(); line1.color = ACAD_COLOR.acBlue; AcadLine line2 = aDocument.ModelSpace.AddLine(CapErgogram.Lower.Start.getCoordinateArray(), CapErgogram.Lower.End.getCoordinateArray();Line2.color = ACAD_COLOR.acBlue;connector.Application.Update();/更新显示表4-2 第-列第级示功图数据8596.385.486511.40.714196.36.327.0073.56622.46413596.385.48650.6311.40.7140.7269.3066.327.0072.56616.16718596.385.48650.4611.40.7140.57555.3776.327.0072.0512.91823596.385.48650.3631.40.7140.48546.6976.327.0071.72910.89328596.385.48650.2991.40.7140.42340.6976.327.0071.5079.49333596.385.48650.2551.40.7140.37736.2666.327.0071.3438.4638596.385.48650.2221.40.7140.34132.846.327.0071.2167.66143596.385.48650.1961.40.7140.31330.16.327.0071.1157.02150696.385.48650.1691.40.7140.28127.066.327.0071.0026.312图4.2第-列第级设计示功图表4-3第-列第级示功图数据30397.2302.884811.40.714642.97621.42640397.2302.88480.7521.40.7140.81679.287.232.6642.42717.47650397.2302.88480.6021.40.7140.69667.6697.232.6642.07214.91660397.2302.88480.5021.40.7140.61259.4467.232.6641.8213.10470397.2302.88480.4311.40.7140.54853.2747.232.6641.63111.74380397.2302.88480.3771.40.7140.49848.4467.232.6641.48310.67990397.2302.88480.3351.40.7140.45844.5497.232.6641.3649.82100397.2302.88480.3021.40.7140.42541.3297.232.6641.2659.11110397.2302.88480.2751.40.7140.39738.6167.232.6641.1828.512120397.2302.88480.2521.40.7140.37336.2957.232.6641.1118130397.2302.88480.2321.40.7140.35334.2837.232.6641.057.557139397.2302.88480.2171.40.7140.33632.6857.232.6641.0017.205图4.3第-列第级设计示功图表4-4第-列第级示功图数据12696.3125.898311.40.714196.36.327.0073.56622.46422696.3125.89830.5571.40.7140.65963.4276.327.0072.34914.79632696.3125.89830.3861.40.7140.50748.8186.327.0071.80811.38842696.3125.89830.2961.40.7140.41940.3246.327.0071.4939.40652696.3125.89830.2391.40.7140.3634.6856.327.0071.2848.09162696.3125.89830.2011.40.7140.31830.6296.327.0071.1347.14572696.3125.89830.1731.40.7140.28627.5526.327.0071.026.42774696.3125.89830.1691.40.7140.28127.0236.327.0071.0016.304图4.4 -列第级示功图数据表4-5第-列第级示功图数据364100.8364.42811.40.7141100.810.854.5671.84719.951464100.8364.4280.7851.40.7140.84184.7710.854.5671.55416.778564100.8364.4280.6461.40.7140.73273.74810.854.5671.35214.596664100.8364.4280.5481.40.7140.65165.63710.854.5671.20312.991764100.8364.4280.4771.40.7140.58959.38210.854.5671.08811.753854100.8364.4280.4271.40.7140.54454.84410.854.5671.00510.855图4.5 -列第级设计示功图4.4 作往复惯性力图估算-列往复运动件的质量为，-列往复运动件的质量为。曲柄销旋转半径为：曲轴旋转角速度：连杆径长比取：曲柄旋转角度与活塞位移关系为1：（4.5）计算往复惯性力的公式为：（4.6）根据式（4.5），计算-列和-列往复运动的惯性力，将计算结果列于表4-6,4-7,由于表过长，这里选取头尾两段，详细内容请参见见附录。表4-6 -列往复惯性力角度(度)角度(度)01.21192.617220036011.199731192.344690.180.0135921.19891191.527320.730.0335831.197531190.165671.640.0735741.195621188.260712.920.1335651.193151185.813814.570.2135561.190151182.826696.570.335471.18661179.301488.940.4353.172-0.79803-793.117251992.2589.65188173-0.7985-793.584211994.0789.73187174-0.7989-793.985681995.6589.8186175-0.79924-794.322961996.9889.86185176-0.79952-794.597151998.0789.91184177-0.79973-794.809161998.9289.95183178-0.79988-794.95971999.5289.98182179-0.79997-795.049251999.8889.99181180-0.8-795.07813200090180图4.5 -列往复惯性力曲线图表4-7 -列往复惯性力角度(度)角度(度)01.21152.6860036011.199731152.4220.180.0135921.19891151.6320.730.0335831.197531150.3161.640.0735741.195621148.4752.920.1335651.193151146.114.570.2135561.190151143.2236.570.3354.71.18661139.8168.940.4353172-0.79803-766.5621992.2589.65188173-0.7985-767.0131994.0789.73187174-0.7989-767.4011995.6589.8186175-0.79924-767.7271996.9889.86185176-0.79952-767.9921998.0789.91184177-0.79973-768.1971998.9289.95183178-0.79988-768.3431999.5289.98182179-0.79997-768.4291999.8889.99181180-0.8-768.457200090180图4.6 -列往复惯性力曲线图4.5 计算各级往复摩擦力计算往复摩擦力的公式为：（4.7）式中摩擦功率指示功率机械效率根据第3部分热力计算的数据以及式（4.7）计算各级摩擦力为：4.6 作综合活塞力曲线图综合活塞里为气体力、往复惯性力和往复摩擦力的代数和：（4.8）由于气体力和往复惯性力都是关于曲柄旋转角度的函数，每一级的为常量，只有方向改变，所以只需按曲柄旋转角度的不停的叠加，从而求得相应柄旋转角度下的气体力和往复惯性力，然后与往复摩擦力相加即可得到曲柄转过时的综合活塞力，然后将柄旋转角度换算成活塞位移，最后根据综合活塞力，活塞位移即可描绘出综合活塞力图。惯性力与曲柄旋转角度的关系见式（4.5）。下面来计算气体力与曲柄旋转角度的关系，如图4.7所示：压缩过程中：，根据式子（4.4），得：（4.9）把式（4.5）代进式（4.9）中，得：（4.10）当。膨胀过程中：，联立式（4.3），解得：（4.11）式中为图4.7中点距y轴的距离。联立式（4.11）和（4.4），得：（4.12）图4.7 解析法指示功图惯性力与曲柄旋转角度的关系见式（4.5）。下面来计算气体力与曲柄旋转角度的关系，如图4.7所示：压缩过程中：，根据式子（4.4），得：（4.9）把式（4.5）代进式（4.9）中，得：（4.10）当。膨胀过程中：，联立式（4.3），解得：（4.11）式中为图4.7中点距y轴的距离。联立式（4.11）和（4.4），得：（4.12）把式（4.5）代进式（4.12）中，得：（4.13）当。当时，摩擦力为正。当时，摩擦力为负。因为是在盖侧缸内，所以气体力始终为负。在编程计算综合活塞力时，由于在计算往复惯性力时，已经将曲柄转角与活塞位移一一对应的存储起来，曲柄转角与往复惯性也一一对应存储起来，在计算气体力的时候只需按曲柄转角将活塞位移取出，按压缩或膨胀过程代入式（4.9）或（4.12）中，计算出的气体力也需按曲柄转角存储。在气体力、往复惯性力以及摩擦力相加时，只要按曲柄转角分别取出气体力和往复摩擦力，然后根据曲柄转角判断摩擦力的正负，最后将它们代数相加即可得到综合活塞力。将综合活塞力按曲柄转角存储起来，最后根据活塞位移与综合活塞力绘制出综合活塞力图。代码如下：public CSumPistonForce(LineHeadNode h, ReciprocatingInertialForce I)Init(); LineHeadNode head = h; line = head.line;LineNode LStageNode = h.node; LineNode HStageNode = h.node.next; this.I = I;/低压级摩擦力double RsLStage = LStageNode.cylinder.ReciprocateFriction.KGF;/高压级摩擦力double RsHStage = HStageNode.cylinder.ReciprocateFriction.KGF;/总摩擦力double SumRs = RsLStage + RsHStage; double AngleIncrement = I.AngleIncrement; for (double a = 0.0; a = 360.0; a += AngleIncrement) double x = I.dica.x; double GasForce = 0.0; if (a = 180.0) /膨胀过程 GasForce = calGasForceBySj(x, LStageNode.cylinder, ref exDataMessageL,a); GasForce += calGasForceBySj(x, HStageNode.cylinder, ref exDataMessageH,a);GasForce += SumRs; else /压缩过程GasForce = calGasForceBySi(LStageNode.cylinder.piston.Stroke.M - x, LStageNode.cylinder, ref coDataMessageL, a); GasForce += calGasForceBySi(LStageNode.cylinder.piston.Stroke.M - x, HStageNode.cylinder, ref coDataMessageH, a);GasForce += (0.0 - SumRs);double Sum = GasForce + I.dica.I;dicSumForce.Add(a, new CForce(Sum, UNITTYPE.KGF);for (double a = 0.0; a 180.0) double x = head.node.cylinder.piston.Stroke.MM * 2 - I.dica.x * 1000.0; dicDisplacement.Add(a, x); else dicDisplacement.Add(a, I.dica.x * 1000); CCurve curve = new CCurve();curve.Start = new CPoint(dicDisplacement0.0 * 10, dicSumForce0.0.KGF);for (double a = 0.0; a = 180.0; a += AngleIncrement)CPoint point = new CPoint(dicDisplacementa * 10, dicSumForcea.KGF);curve.AddAPoint(point);curve.End = new CPoint(dicDisplacement180.0 * 10, dicSumForce180.0.KGF);SumForceCurves0 = curve;curve = new CCurve();curve.Start = new CPoint(dicDisplacement180.0 + AngleIncrement * 10, dicSumForce180.0 + AngleIncrement.KGF);for (double a = 180.0 + AngleIncrement; a = 360.0; a += AngleIncrement)CPoint point = new CPoint(dicDisplacementa * 10, dicSumForcea.KGF); curve.AddAPoint(point); curve.End = new CPoint(dicDisplacement360.0 * 10, dicSumForce360.0.KGF);SumForceCurves1 = curve;各列综合活塞力图见图4.8和图4.9，数据见附录。图4.8 -列综合活塞力曲线图图4.9 -列综合活塞力曲线图4.7 作切向力图计算切向力图的式子为：（4.14）（4.15）（4.16）联立式（4.14）、（4.15）、（4.16），得：（4.17）在4.6作综合活塞力曲线图的过程中，将各列的综合活塞力安曲柄转角存储，现在只需要按曲柄转角依次取出综合活塞力，代入式（4.17）中，即可。然后把按圆周长展开就是横坐标。代码如下，数据见附录。public TangentialForce( double s, double z, double AngleIncrement, double Xscale, double Yscale, Dictionary PistonForce)Init();this.s = s;this.z = z;this.AngleIncrement = AngleIncrement;XScale = Xscale;YScale = Yscale;dicSumPistonForce = PistonForce;XIncrement = 3.14 * s / (360.0 / AngleIncrement);for (double a = 0.0, x = 0.0; a 410103030130130320320600Cv（m/s）304525402035182815201215重度较大的气体选取较低值，重度较小的气体选取较高值；对一些功耗有较高要求的中型固定式压缩机和活塞平均速度比较低的压缩机、小型压缩机、循环机等应选取较低值，甚至可低于下限；排气阀中的气流速度允许比吸气阀高20%。阀隙速度可按下式校核：（5.4）式中活塞工作面积，mm2；活塞平均速度，m/s；同时工作的气阀数；阀隙通道面积，mm2。如图3.4所示，阀隙通道面积可按下式计算：（5.5）式中见图5.6，升程，mm；环形通道各环的平均直径，mm。阀座气流速度应小于阀隙速度，一般取，即，为阀座通道面积，可用下式计算：（5.6）式中阀座通道的宽度，mm；环形通道宽度b与阀片升程h之间的比例关系为：（5.7）也就是说，符合这一关系的气阀，只要阀隙速度合适，其阀座气流速度也是允许的。升程限制器的气流速度比阀座气流速度还要小，其环形通道的宽度：（5.8）图5.6 环状阀计算图根据式（5.7）和（5.8），列表计算如下：表5-5 升程h、阀座通道的宽度b以及环形通道宽度级次气阀升程h（mm）阀座通道的宽度b（mm）环形通道宽度（mm）吸气阀1.70.8544排气阀1.50.7544吸气阀1.50.7544排气阀1.50.7544根据式（5.5）和（5.6）以及表5-3，计算阀隙通道面积和阀座通道面积，列表计算，见表5-6：表5-6 阀隙通道面积和阀座通道面积级次气阀升程h（mm）阀座通道的宽度b（mm）环形通道各环的平均直径（mm）吸气阀1.7428.646.6802.83944.51排气阀1.541935508.68678.24吸气阀1.541935508.68678.24排气阀1.541935508.68678.24根据式（5.4）以及表5-2和表5-4列表校核阀隙速度（见表5-7），从表5-7得知：，阀隙速度在允许的范围内。表5-7 阀隙速度的校核级次气阀活塞工作面积F（mm2）活塞平均速度（m/s）同时工作的气阀数Z阀隙通道面积（mm2）工作压力（kgf/cm2）阀隙速度（m/s）（m/s）吸气阀86352.251802.830.9924.2045排气阀86352.251508.685.8738.1940吸气阀56722.251508.685.3425.0840排气阀56722.251508.6824.5825.0835 弹簧力弹簧力是影响气阀启闭、阻力和寿命的主要因素，必须正确的选用。气阀弹簧力，可分为阀全闭时和阀全开时的弹簧力。阀全闭时弹簧力与阀片开启有关，直接影响压力损失；阀全开时的弹簧力与阀片开启程度及关闭有关，不仅影响压力损失，还影响阀片寿命。在设计气阀时主要控制阀全开时的弹簧力。为了计算方便，气阀弹簧力用单位阀座通道面积上的弹力q（kgf）来表示。弹簧力的大小与压缩机转速、气阀工作压力、气阀中气流速度、气阀运动件质量、阀片升程等因素有关。由于因素比较复杂，在统计分析现有压缩机气阀弹簧力的范围和使用情况的基础上，对于中小型移动式高转速（n500rpm）的动力压缩机，阀全开时的弹簧力q按表5-8选取。一般的选取原则是：气阀工作压力、转速和气阀中气流速度越高，则应选用较大的弹簧力；处于同一级的排气阀弹簧力应高于吸气阀。气阀全闭时的弹簧力为气阀全开时弹簧力的3070%。表5-8 气阀全开时弹簧力q级别阀全开时的弹簧力q（kgf/mm2）第一级0.00080.0020第二级0.00120.0020 阀座上密封口宽度a级阀片厚度为改善密封起见，密封口宽度a宜取小值，但过小则比压增大，容易磨损。一般选用a=0.752.5mm。密封口的比压K可按下式验算：（5.9）式中阀座通道宽度，mm；密封口宽度，mm；排气压力，kgf/cm2 吸气压力，kgf/cm2 允许比压，灰铸铁、青铜为300kgf/cm2。碳钢为500kgf/cm2。根据式（3.10），如下列表计算：表5-9 密封口比压K级次气阀阀座通道宽度b（mm）密封口宽度a（mm）排气压力（kgf/cm2）吸气压力（kgf/cm2）密封口比压K（kgf/cm2）吸气阀415.870.9912.2排气阀415.870.9912.2吸气阀4124.585.3448.1排气阀4124.585.3448.1如表5-7所示，密封口比压，所以a=1mm符合。阀片厚度在“三化”标准中已有规定，一般在0.080.3cm范围。大直径、压力高者选大值。阀片厚度应进行强度校核。按下式进行校核：（5.10）按式（5.10）校核弯曲应力，阀片许用弯曲应力，对于30CrMnSiA为3000kgf/cm2，根据表5-8，所以符合。表5-10 弯曲应力级次气阀阀座通道宽度b（mm）密封口宽度a（mm）排气压力（kgf/cm2）吸气压力（kgf/cm2）阀片厚度（mm）弯曲应力（kgf/cm2）吸气阀415.870.990.8142.97排气阀415.870.991.354.12吸气阀4124.585.341.3213.46排气阀4124.585.341.3213.47 气阀材料气阀在工作时承受反复撞击和交变弯曲载荷。为了保证寿命，阀片应具有强制高、韧性好、耐磨、耐腐蚀等性能。本次设计中阀片材料采用3Cr13。超高压压缩机，由于气阀两侧压差很大，要求有更高的强度，阀芯常用35CrMo、35CrMoV及轴承钢GCr15等制造。阀座的材料，可根据气阀两侧压差按表5-11选取。升程限制器材料一般与阀座材料相同，也可选用比阀座低一级的材料。气阀弹簧一般采用碳素弹簧钢、合金弹簧钢及不锈钢等材料。根据表5-1，在本次设计中，阀座的材料为ZG2Cr13。表5-11 阀座材料压差（kgf/cm2）材料压差（kgf/cm2）材料6HT20401640稀土球墨铸铁或锻钢616HT30-54、合金铸铁、稀土球铁40锻钢35、45、40Cr、35CrMo等VF-0.8/50空气压缩机的设计（整体设计编程，一、二级缸设计）结论与展望6.1 结论本次设计的压缩机为VF-0.8/50空气压缩机。在设计的过程中，通过计算机编程，采用面向对象的方法，完成了热力计算和动力计算，尤其是在动力计算过程中，对AutoCad进行编程二次开发，较为精确的绘制出了设计示功图、往复惯性力图和切向力图等，从而方便了飞轮距的计算。在一、二级气缸设计过程中，选取气缸的结构型式为极差式气缸，低压级在下，高压级在上。在气阀的布置上，一级气阀径向布置，二级气阀轴向布置。为了空气在压缩时不为润滑油所污染，本次设计采用自润滑材料聚四氟乙烯活塞环，化学稳定，耐高温和低温，摩擦系数小。对气阀主要参数选取并校核，这些参数都在允许的范围内。6.2 不足之处及未来展望可能由于经验的原因，对某些系数的选取有欠妥当。但所设计的压缩机的一、二级气缸能满足工艺、安装、维修等方面的要求。本设计完成了设计任务要求的内容。在这几个月的设计过程中，我通过学习，利用类比的方法，即用已知类型的压缩机来设计未知类型的压缩机，这使我了解了一个压缩机的设计过程。在我以后学习设计中，这次设计经历将会成为丰富的经验。致谢在论文完成的此刻，谨向我的导师致以最诚挚的敬意和感谢！感谢导师在我做毕业设计的这段期间，给予我无尽的关怀和帮助，尤其在完成课题和论文撰写过程中，耐心并详细的给予指导。老师的敬业务实工作作风都给予我莫大的感触和激励！在这次毕业设计的过程中，我也得到了身边许多同学的帮助，感谢他们的无私的帮助和关心。感谢大学四年来所有的老师，没有他们的谆谆教导，我不能顺利的毕业。最后，我要感谢我的女朋友，没有她的全力支持以及理解我的学习和工作，我不能顺利并很好的完成本次毕业设计！参考文献1 潘永密，李斯特化工机器（上册）M 北京：化学工业出版社，1987：1-1862 郁永章，姜培正，孙嗣莹压缩机工程手册M 北京：中国石化出版社，2011：137-4293 李郁锡机械设计课程设计M 北京：高等教育出版社，2008：1784 韩绿霞活塞式压缩机计算方法的研究D 郑州：郑州大学，20055 武亚静，史锋往复活塞式压缩机设计软件J 计算机辅助工程，2009，18(2)：60-636 王再顺夹角为90的V型压缩机往复惯性力平衡的探讨J 压缩机技术，1986，82（2）：7-117 林梅，孙嗣莹活塞式压缩机原理M 北京：机械工业出版社，1987：65-778 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Science,2003,12(4):310-317附录-列第级示功图数据8596.385.486511.40.714196.36.327.0073.56622.4649096.385.48650.9451.40.7140.9692.4686.327.0073.42421.579596.385.48650.8951.40.7140.92488.9836.327.0073.29520.75710096.385.48650.8511.40.7140.89185.7986.327.0073.17720.01410596.385.48650.811.40.7140.86182.8736.327.0073.06919.33211096.385.48650.7741.40.7140.83380.1766.327.0072.96918.70311596.385.48650.741.40.7140.80777.6816.327.0072.87618.12112096.385.48650.711.40.7140.78375.3656.327.0072.79117.5812596.385.48650.6811.40.7140.7673.2076.327.0072.71117.07713096.385.48650.6551.40.7140.73971.1936.327.0072.63616.60713596.385.48650.6311.40.7140.7269.3066.327.0072.56616.16714096.385.48650.6091.40.7140.70167.5356.327.0072.50115.75414596.385.48650.5881.40.7140.68465.8696.327.0072.43915.36515096.385.48650.5681.40.7140.66864.2986.327.0072.38114.99915596.385.48650.551.40.7140.65262.8146.327.0072.32614.65316096.385.48650.5331.40.7140.63861.416.327.0072.27414.32516596.385.48650.5171.40.7140.62460.0796.327.0072.22514.01517096.385.48650.5011.40.7140.61158.8156.327.0072.17813.7217596.385.48650.4871.40.7140.59857.6136.327.0072.13313.43918096.385.48650.4741.40.7140.58656.4696.327.0072.09113.17318596.385.48650.4611.40.7140.57555.3776.327.0072.0512.91819096.385.48650.4491.40.7140.56454.3356.327.0072.01212.67519596.385.48650.4371.40.7140.55453.3396.327.0071.97512.44220096.385.48650.4261.40.7140.54452.3856.327.0071.9412.2220596.385.48650.4161.40.7140.53451.4716.327.0071.90612.00721096.385.48650.4061.40.7140.52550.5956.327.0071.87311.80221596.385.48650.3971.40.7140.51749.7546.327.0071.84211.60622096.385.48650.3881.40.7140.50848.9456.327.0071.81211.41722596.385.48650.3791.40.7140.548.1676.327.0071.78311.23623096.385.48650.3711.40.7140.49247.4196.327.0071.75611.06123596.385.48650.3631.40.7140.48546.6976.327.0071.72910.89324096.385.48650.3551.40.7140.47846.0026.327.0071.70310.73124596.385.48650.3481.40.7140.47145.3316.327.0071.67810.57425096.385.48650.3411.40.7140.46444.6826.327.0071.65410.42325596.385.48650.3351.40.7140.45744.0566.327.0071.63110.27726096.385.48650.3281.40.7140.45143.456.327.0071.60910.13626596.385.48650.3221.40.7140.44542.8646.327.0071.5879.99927096.385.48650.3161.40.7140.43942.2976.327.0071.5669.86727596.385.48650.311.40.7140.43441.7476.327.0071.5469.73828096.385.48650.3051.40.7140.42841.2146.327.0071.5269.61428596.385.48650.2991.40.7140.42340.6976.327.0071.5079.49329096.385.48650.2941.40.7140.41740.1956.327.0071.4889.37629596.385.48650.2891.40.7140.41239.7086.327.0071.479.26330096.385.48650.2841.40.7140.40739.2356.327.0071.4539.15230596.385.48650.281.40.7140.40338.7766.327.0071.4369.04531096.385.48650.2751.40.7140.39838.3296.327.0071.4198.94131596.385.48650.2711.40.7140.39337.8946.327.0071.4038.8432096.385.48650.2671.40.7140.38937.476.327.0071.3878.74132596.385.48650.2631.40.7140.38537.0586.327.0071.3728.64533096.385.48650.2591.40.7140.38136.6576.327.0071.3578.55133596.385.48650.2551.40.7140.37736.2666.327.0071.3438.4634096.385.48650.2511.40.7140.37335.8856.327.0071.3298.37134596.385.48650.2471.40.7140.36935.5136.327.0071.3158.28435096.385.48650.2441.40.7140.36535.156.327.0071.3018.19935596.385.486140.36134.7976.327.0071.2888.11736096.385.48650.2371.40.7140.35834.4516.327.0071.2768.03636596.385.48650.2341.40.7140.35434.1146.327.0071.2637.95837096.385.48650.2311.40.7140.35133.7846.327.0071.2517.88137596.385.48650.2281.40.7140.34733.4626.327.0071.2397.80638096.385.48650.2251.40.7140.34433.1486.327.0071.2277.73238596.385.48650.2221.40.7140.34132.846.327.0071.2167.66139096.385.48650.2191.40.7140.33832.5396.327.0071.2057.5939596.385.48650.2161.40.7140.33532.2456.327.0071.1947.52240096.385.48650.2131.40.7140.33231.9576.327.0071.1837.45540596.385.48650.2111.40.7140.32931.6756.327.0071.1737.38941096.385.48650.2081.40.7140.32631.3996.327.0071.1637.32441596.385.48650.2061.40.7140.32331.1286.327.0071.1537.26142096.385.48650.2031.40.7140.3230.8636.327.0071.1437.19942596.385.48650.2011.40.7140.31830.6046.327.0071.1337.13943096.385.48650.1991.40.7140.31530.356.327.0071.1247.0843596.385.48650.1961.40.7140.31330.16.327.0071.1157.02144096.385.48650.1941.40.7140.3129.8566.327.0071.1056.96544596.385.48650.1921.40.7140.30829.6166.327.0071.0976.90945096.385.486140.30529.3816.327.0071.0886.85445596.385.48650.1881.40.7140.30329.156.327.0071.0796.846096.385.48650.1861.40.7140.328.9246.327.0071.0716.74746596.385.48650.1841.40.7140.29828.7026.327.0071.0636.69547096.385.48650.1821.40.7140.29628.4836.327.0071.0556.64447596.385.486140.29428.2696.327.0071.0476.59448096.385.48650.1781.40.7140.29128.0596.327.0071.0396.54548596.385.48650.1761.40.7140.28927.8526.327.0071.0316.49749096.385.48650.1741.40.7140.28727.6496.327.0071.0246.4549596.385.48650.1731.40.7140.28527.4496.327.0071.0166.40350096.385.48650.1711.40.7140.28327.2536.327.0071.0096.35750596.385.48650.1691.40.7140.28127.066.327.0071.0026.312-列第级示功图数据30397.2302.884811.40.714642.97621.42630897.2302.88480.9841.40.7140.98896.077.232.6642.94121.17731397.2302.88480.9681.40.7140.97794.9717.232.6642.90820.93431897.2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