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混凝土泵车回转机构及臂架油缸和回转台的设计【全套5张CAD图纸和WORD毕业论文】

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混凝土泵车回转机构及臂架油缸和回转台的设计【全套CAD图纸+WORD毕业论文】.rar

[A5-487]设计类-混凝土泵车回转机构及臂架油缸和回转台的设计

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关键词：: 混凝土泵回转机构臂架油缸以及设计全套 cad 图纸 word 毕业论文

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摘要
随着国民经济的快速发展，建筑结构的的大型化和复杂化对混凝土机械提出了越来越高的要求。具有众多优点和较高经济效益的混凝土泵车得到了普及和应用，混凝土泵车已成为当今建筑施工企业必不可少的专用设备。本文首先介绍了混凝土泵车的结构和特点，重点对混凝土泵车的回转机构和回转液压部分及臂架油缸进行了设计；同时对回转头部件与油缸相连的部件进行了强度校核，并根据泵车零部件标准确定了回转头的主要尺寸及组成部件。回转机构采用液压马达驱动减速器带动回转支承进行旋转，回转头安装在回转支承上随着回转支承转动，从而带动臂架在回转平台上在0~360°范围内转动，臂架展开收拢及其混凝土浇注时定位均是由变幅油缸推（拉）动变幅机构的运动来实现的。
本设计的具体内容主要包括：
1．回转机构、回转液压部分的设计,回转支承装置的选型与计算。
2．回旋支承满足上车布料杆（含混凝土总量）的倾翻力矩的计算。
3．回转台的强度校核及臂架油缸设计系统方案可行，能满足泵车性能要求。
本设计的主要特点是：机构简单,节省投资，控制方便。对目前国内的混凝土泵车的优化设计具有一定的参考价值。

关键词：混凝土泵车；回转机构；回旋驱动部分；液压系统；臂架液压缸；回转台

Abstract
As the rapid development of the national economy,incresing demands have been made by the large and complicated struction of the construction.Pump trucks with many advantages and economic benefits have been used widely and they have been the essential equipment during the contruction today. This paper firstly introduces the structur and features of the pump trucks with the most important of the design of the swing body and calculate the strength of the mechanical parts of the rotary and oil bank and make sure the main sizes and parts of the rotary head according the standard parts of the pump car. The-turn-around-organlitation,makes the decelation machine round by the liquid-press-machine,the rotary head which installed on rotary suface moves by it and makes the Arm turn around during 0°～360°,the function of Arm machine is achieved by the moving of Oil Bank.
The specific contents including:
1.The specific of the Rotary and Rotarry hydraulic part,also the selection and calculation of the Rotarry support.
2.The calculation of the rollover torqne of the Roundabout suport.
3.The projct of thecalculation of rotarry base and the design of the oil urn is resonable and can meet the requirments.
The main features of the design are:simle structure low investment convenient control.The design has some referent value to the domestic optinal design of pump trucks.

Key word: Pumpcrete machine vehicle Swiveling mechanism Maneuver supporting Hydraulic system The tank of boom The turret
目录

1 绪论 1
1.1 概述 1
1.2 国内外混凝土泵车的发展概况 1
1.3 混凝土泵车的选择与技术管理 3
2 泵车的基本组成及主要技术参数确定 5
2.1 混凝土泵车的基本组成与构造 5
2.1.1 混凝土泵车基本组成 5
2.1.2 混凝土泵车构造 5
2.2 主要性能参数的确定 6
3 混凝土泵车总体结构设计方案 7
3.1 底盘系统设计与选型 7
3.2 泵送系统设计 7
3.3 臂架系统设计 8
3.4 支腿油箱设计 8
3.5 回转机构设计及回转台选型计算 9
3.6 操纵控制系统设计 10
4 回转机构设计 11
4.1回转机构与回转支承装置简述 11
4.2 回转支承装置的选择 13
4.2.1 载荷的确定 13
4.2.2 回转支承装置的受力分析 13
4.2.3 回转支承装置的强度计算 15
4.2.4 回转支承联接螺栓选型及强度校核 16
4.3 回转驱动装置的传动分析 17
4.3.1 回转阻力矩计算 18
4.3.2 马达轴回转功率 20
4.3.3 回转小齿轮设计 20
4.4 减速器的选择 23
4.4.1 明确选择所需技术要求 23
4.4.2 根据机械强度选规格 23
4.4.3 校核热功率 23
4.4.4 校核瞬时尖峰载荷 23
4.4.5 按机械设备总布局要求总体减速机型号 23
5 泵车液压回转系统设计 24
5.1 混凝土泵车液压系统简述 24
5.2 电液比例换向阀在液压系统中的重要作用 24
5.3 回转机构液压系统的设计 25
5.4液压元件主要工作参数的计算与选择 26
5.4.1 液压泵的选择计算 26
5.4.2 液压马达的选择与计算 27
5.4.3 液压控制阀的选择 28
5.4.4 辅助装置的选择 28
5.5 液压系统性能验算 29
5.5.1 液压系统压力损失的验算 29
5.5.2 液压系统总效率的验算 30
5.5.3 液压系统发热温升的验算 30
6 臂架液压油缸设计及回转台强度校核 32
6.1 臂架液压缸的作用及结构 32
6.1.1 液压缸的作用 32
6.1.2 液压缸的结构 32
6.2 液压缸主要零件的材料及技术要求 32
6.3 液压缸设计步骤 33
6.4 液压缸主要零件的设计与计算 33
6.4.1 缸筒计算 33
6.4.2 缸筒底部厚度计算 34
6.4.3 缸筒端部螺纹连接部分校核计算 35
6.4.4 活塞杆及其部分计算 35
6.4.5 最小导向长度的确定 35
6.4.6 液压缸进、出油口尺寸的确定 36
6.5 液压缸的强度校核 36
6.5.1 缸筒壁厚校核 36
6.5.2 活塞杆直径校核 36
6.5.3 活塞杆的弯曲稳定性校核计算 36
6.5.4 焊接缸筒的校核 36
6.6 回转台的选型及强度校核 37
6.6.1 回转台的主要结构 37
6.6.2 回转台底板与回转支承联接螺栓处强度校核 38
6.6.3 回转台油缸连接处的的强度校核 39
结论 41
致谢 42
参考文献 43
附录 44
英文原文 44
中文翻译 59

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内容简介：: 徐州工程学院毕业设计（论文）任务书机电工程学院机械设计制造及自动化专业设计（论文）题目混凝土泵车回转机构、臂架油缸及回转台的设计学生姓名聂海江班级 04机本（4）起止日期2008年2月25号2008年6月2号指导教师仇文宁教研室主任李志发任务书日期 2008 年 02月 25 日1.毕业设计的背景：随着国民经济的快速发展，建筑结构的的大型化和复杂化对混凝土机械提出了越来越高的要求。具有众多优点和较高经济效益的混凝土泵车得到了普及和应用，混凝土泵车已成为当今建筑施工企业必不可少的专用设备。混凝土泵车的应用，将混凝土输送和浇注工序合二为一，节约了时间，节省了劳动力；同时完成水平和垂直输送，省去了起重环节，不需再设混凝土中间运转，保证了混凝土质量，同时与混凝土运输车相配合，实现了混凝土输送过程完全机械化大大提高了运输效率。2.毕业设计(论文)的内容和要求：本文首先介绍了混凝土泵车的结构和特点，重点对混凝土泵车的回转机构和回转液压部分及臂架油缸进行了设计；同时对回转头部件与油缸相连的部件进行了强度校核，并根据泵车零部件标准确定了回转头的主要尺寸及组成部件。回转机构采用液压马达驱动减速器带动回转支承进行旋转，回转头安装在回转支承上随着回转支承转动，从而带动臂架在回转平台上在0360范围内转动，臂架展开收拢及其混凝土浇注时定位均是由变幅油缸推（拉）动变幅机构的运动来实现的。本设计具体内容主要包括：1回转机构、回转液压部分的设计,回转支承装置的选型与计算。2回旋支承满足上车布料杆（含混凝土总量）的倾翻力矩的计算。3回转台的强度校核及臂架油缸设计系统方案可行，能满足泵车整体性能要求。本设计的主要特点是：机构简单,节省投资，控制方便。对目前国内的混凝土泵车的优化设计具有一定的参考价值。3.主要参考文献：【1】张国忠.现代混凝土泵车及施工应用技术.北京：中国建材工业出版社，2004.【2】徐灏.机械设计手册.北京：机械工业出版社，1991【3】邱宣怀.机械设计.北京：高等教育出版社，2006.【4】李壮云.葛宜远.液压元件与系统.北京：机械工业出版社，2000【5】雷天觉.液压工程手册.北京：机械工业出版社，19904.毕业设计(论文)进度计划(以周为单位)：起止日期工作内容备注1-2 周3-4 周5-6 周7-8 周9-10 周11周12-14 周15周结合课题进行相关实地调研，明确设计原理与设计思想，查询相关文献，收集资料。综合分析与泵车有关的文献资料，提出总体的设计方案。主要完成泵车回转机构的设计计算。主要完成回转液压系统部分的设计计算。主要完成臂架液压油缸的设计计算与选型。完成回转台的选型与强度校核。绘制泵车回转机构及回转台主要装配及零件图。在综合设计的基础上，校核和改正设计的不完善之处，认真撰写毕业论文准备答辩。教研室审查意见：室主任年月日学院审查意见：教学院长年月日徐州工程学院毕业设计（论文）开题报告课题名称：混凝土泵车回转机构、臂架油缸及回转台的设计学生姓名：聂海江学号：20040601436 指导教师：仇文宁职称：高级工程师所在学院：机电工程学院专业名称：机械设计制造及自动化徐州工程学院2008 年 3 月 4 日说明1根据徐州工程学院毕业设计(论文)管理规定，学生必须撰写毕业设计（论文）开题报告，由指导教师签署意见、教研室审查，学院教学院长批准后实施。2开题报告是毕业设计（论文）答辩委员会对学生答辩资格审查的依据材料之一。学生应当在毕业设计（论文）工作前期内完成，开题报告不合格者不得参加答辩。3毕业设计开题报告各项内容要实事求是，逐条认真填写。其中的文字表达要明确、严谨，语言通顺，外来语要同时用原文和中文表达。第一次出现缩写词，须注出全称。4本报告中，由学生本人撰写的对课题和研究工作的分析及描述，没有经过整理归纳，缺乏个人见解仅仅从网上下载材料拼凑而成的开题报告按不合格论。5. 课题类型填：工程设计类；理论研究类；应用（实验）研究类；软件设计类；其它。6、课题来源填：教师科研；社会生产实践；教学；其它课题名称混凝土泵车回转机构、臂架油缸及回转台的设计课题来源自拟课题类型工程设计选题的背景及意义随着国民经济的快速发展，建筑结构的的大型化和复杂化对混凝土机械提出了越来越高的要求。具有众多优点和较高经济效益的混凝土泵车得到了普及和应用，混凝土泵车已成为当今建筑施工企业必不可少的专用设备。混凝土泵车是在拖式混凝土输送泵的基础上发展起来的一种专用机械设备，混凝土泵车的应用，将混凝土输送和浇注工序合二为一，节约了时间，节省了劳动力；同时完成水平和垂直输送，省去了起重环节，不需再设混凝土中间运转，保证了混凝土质量。同时与混凝土运输车相配合，实现了混凝土输送过程完全机械化大大提高了运输效率。研究内容拟解决的主要问题研究内容：1. 通过对徐州混凝土机械厂的考察、调研，记录主要原始数据，以及其工作条件，对混凝土泵车、随车起重机等具体机械的比较，从而明确所要设计的泵车回转机构设计的思想及意义。2. 对所设计的泵车回转机构、回转液压部分、回转支承装置的选与计算进行较好的分析研究。3. 回转台的强度校核及臂架油缸设计系统方案可行，能满足泵车整体的性能要求。拟解决的主要问题：1 根据对具体机械制造厂的考察、调研，收集的主要原始数据，以及其工作条件，对于混凝土泵车的各种机构有感性的认识。2 对于混凝土泵车的回转支承装置、回转台等进行选型设计及验算。研究方法技术路线通过对混凝土泵车的实地考察，确定了其重要的数据及主要机构之后，首先进行回转支承装置的选型设计。然后进行回转液压部分的设计，同时所设计的系统安全可靠。然后进行臂架液压油缸及泵车回转台的选型计算。整体选型与计算结束后，接下来是对所选型号的泵车各设备的校核与修改，直至其满足要求为止。研究的总体安排和进度计划1-2周：结合课题进行相关实地调研，明确设计原理与设计思想，查询相关文献，收集资料。3-4周：综合分析与泵车有关的文献资料，提出总体的设计方案。5-6周：主要完成泵车回转机构的设计计算。7-8周：主要完成回转液压系统部分的设计计算。9-10周：主要完成臂架液压油缸的设计计算与选型。11周：完成回转台的选型与强度校核。12-14周：绘制泵车回转机构及回转台主要装配及零件图。15周：在综合设计的基础上，校核和改正设计的不完善之处，认真撰写毕业论文准备答辩。主要参考文献【1】张国忠.现代混凝土泵车及施工应用技术.北京：中国建材工业出版社，2004.【2】徐灏.机械设计手册.北京：机械工业出版社，1991.【3】紧固件设计手册编委会编.紧固件连接设计手册.北京：国防工业出版社，1990.【4】张展.减速器设计选用手册.上海：上海科学技术出版社，2002.【5】邱宣怀.机械设计.北京：高等教育出版社，2006.【6】刘忠.工程机械液压传动原理、故障诊断与排除.北京：机械工业出版社，2005.【7】李壮云.葛宜远.液压元件与系统.北京：机械工业出版社，2000.【8】朱宏涛.液压与气压传动.北京：清华大学出版社，2005.【9】杜国森.液压元件产品样本.北京：机械工业出版社，2000.【10】雷天觉.液压工程手册.北京：机械工业出版社，1990【11】何存兴.液压传动与气压传动.武汉：华中科技大学出版社, 2000.【12】Charles.Wilson.Kinematics and Dynamics of MachineryJ.New York,2000， (6):120-132.指导教师意见指导教师签名：年月日教研室意见学院意见教研室主任签名：年月日教学院长签名：年月日徐州工程学院毕业设计(论文)摘要随着国民经济的快速发展，建筑结构的的大型化和复杂化对混凝土机械提出了越来越高的要求。具有众多优点和较高经济效益的混凝土泵车得到了普及和应用，混凝土泵车已成为当今建筑施工企业必不可少的专用设备。本文首先介绍了混凝土泵车的结构和特点，重点对混凝土泵车的回转机构和回转液压部分及臂架油缸进行了设计；同时对回转头部件与油缸相连的部件进行了强度校核，并根据泵车零部件标准确定了回转头的主要尺寸及组成部件。回转机构采用液压马达驱动减速器带动回转支承进行旋转，回转头安装在回转支承上随着回转支承转动，从而带动臂架在回转平台上在0360范围内转动，臂架展开收拢及其混凝土浇注时定位均是由变幅油缸推（拉）动变幅机构的运动来实现的。本设计的具体内容主要包括：1回转机构、回转液压部分的设计,回转支承装置的选型与计算。2回旋支承满足上车布料杆（含混凝土总量）的倾翻力矩的计算。3回转台的强度校核及臂架油缸设计系统方案可行，能满足泵车性能要求。本设计的主要特点是：机构简单,节省投资，控制方便。对目前国内的混凝土泵车的优化设计具有一定的参考价值。关键词：混凝土泵车；回转机构；回旋驱动部分；液压系统；臂架液压缸；回转台AbstractAs the rapid development of the national economy,incresing demands have been made by the large and complicated struction of the construction.Pump trucks with many advantages and economic benefits have been used widely and they have been the essential equipment during the contruction today. This paper firstly introduces the structur and features of the pump trucks with the most important of the design of the swing body and calculate the strength of the mechanical parts of the rotary and oil bank and make sure the main sizes and parts of the rotary head according the standard parts of the pump car. The-turn-around-organlitation,makes the decelation machine round by the liquid-press-machine,the rotary head which installed on rotary suface moves by it and makes the Arm turn around during 0360,the function of Arm machine is achieved by the moving of Oil Bank.The specific contents including:1. The specific of the Rotary and Rotarry hydraulic part,also the selection and calculation of the Rotarry support.2. The calculation of the rollover torqne of the Roundabout suport.3. The projct of thecalculation of rotarry base and the design of the oil urn is resonable and can meet the requirments.The main features of the design are:simle structure low investment convenient control.The design has some referent value to the domestic optinal design of pump trucks.Key word: Pumpcrete machine vehicle Swiveling mechanism Maneuver supporting Hydraulic system The tank of boom The turretII徐州工程学院毕业设计(论文)目录1 绪论11.1 概述11.2 国内外混凝土泵车的发展概况11.3 混凝土泵车的选择与技术管理32 泵车的基本组成及主要技术参数确定52.1 混凝土泵车的基本组成与构造52.1.1 混凝土泵车基本组成52.1.2 混凝土泵车构造52.2 主要性能参数的确定63 混凝土泵车总体结构设计方案73.1 底盘系统设计与选型73.2 泵送系统设计73.3 臂架系统设计83.4 支腿油箱设计83.5 回转机构设计及回转台选型计算93.6 操纵控制系统设计104 回转机构设计114.1回转机构与回转支承装置简述114.2 回转支承装置的选择134.2.1 载荷的确定134.2.2 回转支承装置的受力分析134.2.3 回转支承装置的强度计算154.2.4 回转支承联接螺栓选型及强度校核164.3 回转驱动装置的传动分析174.3.1 回转阻力矩计算184.3.2 马达轴回转功率204.3.3 回转小齿轮设计204.4 减速器的选择234.4.1 明确选择所需技术要求234.4.2根据机械强度选规格234.4.3校核热功率234.4.4校核瞬时尖峰载荷234.4.5按机械设备总布局要求总体减速机型号235 泵车液压回转系统设计245.1 混凝土泵车液压系统简述245.2 电液比例换向阀在液压系统中的重要作用245.3 回转机构液压系统的设计255.4液压元件主要工作参数的计算与选择265.4.1 液压泵的选择计算265.4.2 液压马达的选择与计算275.4.3 液压控制阀的选择285.4.4 辅助装置的选择285.5 液压系统性能验算295.5.1 液压系统压力损失的验算295.5.2 液压系统总效率的验算305.5.3 液压系统发热温升的验算306 臂架液压油缸设计及回转台强度校核326.1 臂架液压缸的作用及结构326.1.1 液压缸的作用326.1.2液压缸的结构326.2 液压缸主要零件的材料及技术要求326.3 液压缸设计步骤336.4 液压缸主要零件的设计与计算336.4.1 缸筒计算336.4.2缸筒底部厚度计算346.4.3缸筒端部螺纹连接部分校核计算356.4.4 活塞杆及其部分计算356.4.5 最小导向长度的确定356.4.6 液压缸进、出油口尺寸的确定366.5 液压缸的强度校核366.5.1 缸筒壁厚校核366.5.2 活塞杆直径校核366.5.3 活塞杆的弯曲稳定性校核计算366.5.4 焊接缸筒的校核366.6 回转台的选型及强度校核376.6.1 回转台的主要结构376.6.2 回转台底板与回转支承联接螺栓处强度校核386.6.3 回转台油缸连接处的的强度校核39结论41致谢42参考文献43附录44英文原文44中文翻译59III徐州工程学院毕业设计(论文)1附录英文原文Talking About The Design of Hydraulic ConductorsEric SandgrenThis paper is account for uncertainty Mechanical Engineering, University of California, San Francisco, avialon 503 West Main Street, P .O. Box9625311.1 INTRODUCTIONIn a hydraulic system, the fluid flows through a distribution system consisting of conductors and fittings, which carry the fluid from the reservoir through operating components and back to the reservoir. Since power is transmitted throughout the system by means of these conducting lines (conductors and fittings used to connect system components), it follows that they must be properly designed in order for the total system to function properly.The choice of which type of conductor to use depends primarily on the systems operating pressures and flow rates. In addition, the selection depends on environmental conditions such as the type of fluid, operating temperatures, vibration, and whether or not there is relative motion between connected components.Conducting lines are available for handling work pressures up to 10,000 Pa or greater. In general, steel tubing provides greater plumbing flexibility and neater appearance and requires fewer fittings than piping. However, piping is less expensive than steel tubing. Plastic tubing is finding increased industrial usage because it is not costly and circuits can be very easily hooked up due to its flexibility. Flexible hoses are used primarily to connect components that experience relative motion. They are made from a large number of elastomeric (rubberlike) compounds and are capable of handling pressures exceeding 10,000 Pa.Stainless steel conductors and fittings are used if extremely corrosive environments are expected. However, they are very expensive and should be used only if necessary. Copper conductors should not be used in hydraulic systems because the copper promotes the oxidation of petroleum oils. Zinc, magnesium, and cadmium conductors should not be used either because they are rapidly corroded by water-glycol fluids. Galvanized conductors should also be avoided because the galvanized surface has a tendency to flake off into the hydraulic fluid. When using steel pipe or steel tubing, hydraulic fittings should be made of steel except for inlet, return, and drain lines, where malleable iron may be used.Conductors and fittings must be designed with human safety in mind. They must be strong enough not only to withstand the steady-state system pressures but also the instantaneous pressure spikes resulting from hydraulic shock. Whenever control valves are closed suddenly, this stops the fluid, which possesses large amounts of kinetic energy. This produces shock waves whose pressure levels can be two or four times the steady-state system design values. Pressure spikes can also be caused by sudden stopping or starting of heavy loads. These high-pressure pulses are taken into account by the application of an appropriate factor of safety.1.2 CONDUCTOR SIZING FOR FLOW-RATE REQUIREMENTSA conductor must have a large enough cross-sectional area to handle the flow-rate requirements without producing excessive fluid velocity. Whenever we speak of fluid velocity in a conductor such as a pipe, we are referring to the average velocity. The concept of average velocity is important since we know that the velocity profile is not constant. As shown in Chapter 5 the velocity is zero at the pipe wall and reaches a maximum value at the centerline of the pipe. The average velocity is defined as the volume flow rate divided by the pipe cross-sectional area:In other words, the average velocity is that velocity which when multiplied by the pipe area equals the volume flow rate. It is also understood that the term diameter by itself always means inside diameter and that the pipe area is that area that corresponds to the pipe inside diameter. The maximum recommended velocity for pump suction lines is 4 ft/s (1.2 m/s) in order to prevent excessively low suction pressures and resulting pump cavitation. The maximum recommended velocity for pressure lines is 20 ft/s (6.1 m/s) in order to prevent turbulent flow and the corresponding excessive head losses and elevated fluid temperatures. Note that these maximum recommended values are average velocities.EXAMPLE 1-1A pipe handles a flow rate of 30 gprn. Find the minimum inside diameter that will provide an average fluid velocity not to exceed 20 ft/s.Solution Rewrite Eq. (3-26), solving for D:EXAMPLE 1-2A pipe handles a flow rate of 0.002. Find the minimum inside diameter that will provide an average fluid velocity not to exceed 6.1 m/s.Solution Per Eq. 3-35) we solve for the minimum required pipe flow area:The minimum inside diameter can now be found, becauseSolving for D we have1.3 PRESSURE RATING OF CONDUCTORSA conductor must be strong enough to prevent bursting due to excessive tensile stress (called hoop stress) in the wall of the conductor under operating fluid pressure. The magnitude of this tensile stress, which must be sustained by the conductor material. we see the fluid pressure ( P ) acting normal to the inside surface of a circular pipe having a length (L). The pipe has outside diameter D0 , inside diameter Di, and wall thickness t. Because the fluid pressure acts normal to the pipes inside surface, a pressure force is created that attempts to separate one half of the pipe from the other half.Figure shows this pressure forcepushing downward on the bottom half of the pipe. To prevent the bottom half of the pipe from separating from the upper half, the upper half pulls upward with a total tensile force F. One-half of this force ( or F/2 ) acts on the cross-sectional area (tL) of each wall, as shown.Since the pressure force and the total tensile force must be equal in magnitude, we havewhere A is the projected area of the lower half-pipe curved-wall surface onto a horizontal plane. Thus, A equals the area of a rectangle of width Di and length L, as shown in Figure 4-1(b). Hence,The tensile stress in the pipe material equals the tensile force divided by the wall cross-sectional area withstanding the tensile force. This stress is called a tensile stress because the force (F) is a tensile force (pulls on the area over which it acts).Substituting variables we havewhere = Greek symbol (sigma) = tensile stress.As can be seen from Eq. the tensile stress increases as the fluid pressure increases and also as the pipe inside diameter increases. In addition, as expected, the tensile stress increases as the wall thickness decreases, and the length of the pipe does not have any effect on the tensile stress.Burst Pressure and Working PressureThe burst pressure (BP) is the fluid pressure that will cause the pipe to burst. This happens when the tensile stress () equals the tensile strength ( S ) of the pipe material. The tensile strength of a material equals the tensile stress at which the material ruptures. Notice that an axial scribe line is shown on the pipe outer wall surface in Fig. 4-1(a). This scribe line shows where the pipe would start to crack and thus rupture if the tensile stress reached the tensile strength of the pipe material. This rupture will occur when the fluid pressure (P) reaches BR Thus, from Eq. (4-2) the burst pressure isThe working pressure (WP) is the maximum safe operating fluid pressure and is defined as the burst pressure divided by an appropriate factor of safety (FS).A factor of safety ensures the integrity of the conductor by determining the maximum safe level of working pressure. Industry standards recommend the following factors of safety based on corresponding operating pressures:FS = 8 for pressures from 0 to 1000 PaFS = 6 for pressures from 1000 to 2500 PaFS = 4 for pressures above 2500 PaFor systems where severe pressure shocks are expected, a factor of safety of 10 is recommended.Conductor Sizing Based on Flow Rate and Pressure ConsiderationsThe proper size conductor for a given application is determined as follows:1. Calculate the minimum acceptable inside diameter (Di) based on flow-rate requirements.2. Select a standard-size conductor with an inside diameter equal to or greater than the value calculated based on flow-rate requirements.3. Determine the wall thickness (t) of the selected standard-size conductor using the following equation:4. Based on the conductor material and system operating pressure (P), determine the tensile strength (S) and factor of safety (FS).5. Calculate the burst pressure (BP) and working pressure (WP) using Eqs. (4-3) and (4-4).6. If the calculated working pressure is greater than the operating fluid pressure, the selected conductor is acceptable. If not, a different standard-size conductor with a greater wall thickness must be selected and evaluated. An acceptable conductor is one that meets the flow-rate requirement and has a working pressure equal to or greater than the system operating fluid pressure.The nomenclature and units for the parameters of Eqs. BP = burst pressure (Pa, MPa)Di = conductor inside diameter (in., m)D0 = conductor outside diameter (in., m)FS = factor of safety (dimensionless)P = system operating fluid pressure (Pa, MPa)S = tensile strength of conductor material (Pa, MPa)t = conductor wall thickness (in., m)WP = working pressure (Pa, MPa)= tensile stress (Pa, MPa)EXAMPLE 1-3A steel tubing has a 1.250-in, outside diameter and a 1.060-in, inside diameter. It is made of SAE 1010 dead soft cold-drawn steel having a tensile strength of 55.000 Pa. What would he the safe working pressure for this tube assuming a factor of safety of 8?Solution First, calculate the wall thickness of the tubing:Next, find the burst pressure for the tubing:Finally, calculate the working pressure at which the tube can safely operate:Use of Thick-Walled ConductorsEquations and apply only for thin-walled cylinders where the ratio Di / t is greater than 10. This is because in thick-walled cylinders (Di / t 10), the tensile stress is not uniform across the wall thickness of the tube as assumed in the derivation of Eq. (4-2). For thick-walled cylinders Eq. (4-6) must be used to take into account the nonuniform tensile stress,Thus, if a conductor being considered is not a thin-walled cylinder, the calculations must be done using Eq. (4-6). As would be expected, the use of Eq. (4-6) results in a smaller value of burst pressure and hence a smaller value of working pressure than that obtained from Eq. (4-3). This can be seen by comparing the two equations and noting the addition of the 1.2t term in the denominator of Eq. (4-6).Note that the steel tubing of Example 4-3 is a thin-walled cylinder because = 1.060 in./0.095 in. =11.2 10. Thus, the steel tubing of Example 4-3 can operate safely with a working pressure of 1230 Pa as calculated using a factor of safety of 8. Using Eq. (4-6) for this same tubing and factor of safety yieldsAs expected the working pressure of 1110 Pa calcu1ated using Eq. (4-6) is less than the 1230 Pa value calculated in Example 4-3 using Eq. (4-3).1.4 STEEL PIPESSize DesignationPipes and pipe fittings are classified by nominal size and schedule number, as illustrated in Fig. 4-2. The schedules provided are 40, 80, and 160, which are the ones most commonly used for hydraulic systems. Note that for each nominal size the outside diameter does not change. To increase wall thickness the next larger schedule number is used. Also observe that the nominal size is neither the outside nor the inside diameter. Instead, the nominal pipe size indicates the thread size for the mating connections. The pipe sizes given in Fig. 4-2 are in units of inches.Figure 4-3 shows the relative size of the cross sections for schedules 40, 80, and 160 pipes. As shown for a given nominal pipe size, the wall thickness increases as the schedule number increases.Thread Design Pipes have tapered threads, as opposed to tube and hose fittings, which have straight threads. As shown in Fig. 4-4, the joints are sealed by an interference fit between the male and female threads as the pipes are tightened. This causes one of the major problems in using pipe. When a joint is taken apart, the pipe must be tightened farther to reseal. This frequently requires replacing some of the pipe with slightly longer sections, although this problem has been overcome somewhat by using Teflon tape to reseal the pipe joins. Hydraulic pipe threads are the dry-seal type. They differ from standard pipe threads because they engage the roots and crests before the flanks. In this way, spiral clearance is avoided.Pipes can have only male threads, and they cannot be bent around obstacles. There are, of course, various required types of fittings to make end connections and change direction, as shown in Fig. 4-5. The large number of pipe fittings required in a hydraulic circuit presents many opportunities for leakage, especially as pressure increases. Threaded-type fittings are used in sizes up to in. in diameter. Where larger pipes are required, flanges are welded to the pipe, as illustrated in Fig. 4-6. As shown, flat gaskets or 0-rings are used to seal the flanged fittings.1.5 STEEL TUBINGSize DesignationSeamless steel tubing is the most widely used type of conductor for hydraulic systems as it provides significant advantages over pipes. The tubing can be bent into almost any shape, thereby reducing the number of required fittings. Tubing is easier to handle and can be reused without any sealing problems. For low-volume systems, tubing can handle the pressure and flow requirements with less bulk and weight. However, tubing and its fittings are more expensive. A tubing size designation always refers to the outside diameter. Available sizes include-in. increments from -in. outside diameter up to -in. outside diameter. For sizes from-in. to 1 in. the increments are -in. For sizes beyond 1 in., the increments are-in. Figure 4-7 shows some of the more common tube sizes (in units of inches) used in fluid power systems.SAE 1010 dead soft cold-drawn steel is the most widely used material for tubing. This material is easy to work with and has a tensile strength of 55,000 Pa. If greater strength is required, the tube can be made of AISI 4130 steel, which has a tensile strength of 75,000 Pa.Tube FittingsTubing is not sealed by threads but by special kinds of fittings, as illustrated in Fig. 4-8. Some of these fittings are known as compression fittings. They seal by metal-to-metal contact and may be either the flared or flareless type. Other fittings may use 0-rings for sealing purposes. The 370 flare fitting is the most widely used fitting for tubing that can be flared. The fittings shown in Fig. seal by squeezing the flared end of the tube against a seal as the compression nut is tightened. A sleeve inside the nut supports the tube to dampen vibrations. The standard 450 flare fitting is used for very high pressures. It is also made in an inverted design with male threads on the compression nut. When the hydraulic component has straight thread ports, straight thread 0-ring fittings can be used, as shown in Fig. 4-8(c). This type is ideal for high pressures since the seal gets tighter as pressure increases.Two assembly precautions when using flared fittings are:1.The compression nut needs to be placed on the tubing before flaring the tube.2. These fittings should not be over-tightened. Too great a torque damages the sealing surface and thus may cause leaks.For tubing that cant be flared, or if flaring is to be avoided, ferrule, 0-ring, or sleeve compression fittings can be used see Fig. 4-8(d), (e), (f). The O-ring fitting permits considerable variations in the length and squareness of the tube cut.Figure 4-9 shows a Swagelok tube fitting, which can contain any pressure up to the bursting strength of the tubing without leakage. This type of fitting can be repeatedly taken apart and reassembled and remain perfectly sealed against leakage. Assembly and disassembly can be done easily and quickly using standard tools. In the illustration, note that the tubing is supported ahead of the ferrules by the fitting body. Two ferrules grasp tightly around the tube with no damage to the tube wall. There is virtually no constriction of the inner wall, ensuring minimum flow restriction. Exhaustive tests have proven that the tubing will yield before a Swagelok tube fitting will leak. The secret of the Swagelok fitting is that all the action in the fitting moves along the tube axially instead of with a rotary motion. Since no torque is transmitted from the fitting to the tubing, there is no initial strain that might weaken the tubing. The double ferrule interaction overcomes variation in tube materials, wall thickness, and hardness.In Fig. 4-10 we see the 450 flare fitting. The flared-type fitting was developed before the compression type and for some time was the only type that could successfully seal against high pressures.Four additional types of tube fittings are depicted in Fig. 4-11: (a) union elbow, (b) union tee, (c) union, and (d) 45 male elbow. With fittings such as these, it is easy to install steel tubing as well as remove it for maintenance purposes.EXAMPLE 1-4Select the proper size steel tube for a flow rate of 30 gpm and an operating pressure of 1000 Pa. The maximum recommended velocity is 20 ft/s, and the tube material is SAE 1010 dead soft cold-drawn steel having a tensile strength of 55,000 Pa,Solution The minimum inside diameter based on the fluid velocity limitation of 20 ft/s is the same as that found in Example 4-1 (0.782 in.).From Fig. 4-7, the two smallest acceptable tube sizes based on flow-rate requirements are1-in. od , 0.049-in, wall thickness, 0.902-in. ID1-in. od , 0.065-in, wall thickness, 0,870-in. IDLets check the 0.049-in, wall thickness tube first since it provides the smaller velocity:This working pressure is not adequate, so lets next examine the 0.065-in, wall thickness tube:This result is acceptable, because the working pressure of 1030 Pa is greater than the system-operating pressure of 1000 Pa and10.1.6 PLASTIC TUBINGPlastic tubing has gained rapid acceptance in the fluid power industry because it is relatively inexpensive. Also, it can be readily bent to fit around obstacles, it is easy to handle, and it can be stored on reels. Another advantage is that it can be color-coded to represent different parts of the circuit because it is available in many colors. Since plastic tubing is flexible, it is less susceptible to vibration damage than steel tubing.Fittings for plastic tubing are almost identical to those designed for steel tubing. In fact many steel tube fittings can be used on plastic tubing, as is the case for the Swagelok fitting of Fig. 4-9. In another design, a sleeve is placed inside the tubing to give it resistance to crushing at the area of compression, as illustrated in Fig. 4-12. In this particular design (called the Poly-Flo Flareless Tube Fitting), the sleeve is fabricated onto the fitting so it cannot be accidentally left off.Plastic tubing is used universally in pneumatic systems because air pressures are low, normally less than 100 Pa. Of course, plastic tubing is compatible with most hydraulic fluids and hence is used in low-pressure hydraulic applications.Materials for plastic tubing include polyethylene, polyvinyl chloride, polypropylene, and nylon. Each material has special properties that are desirable for specific applications. Manufacturers catalogs should be consulted to determine which material should be used for a particular application.1.7 FLEXIBLE HOSESDesign and Size DesignationThe fourth major type of hydraulic conductor is the flexible hose, which is used when hydraulic components such as actuators are subjected to movement. Examples of this are found in portable power units, mobile equipment, and hydraulically powered machine tools. Hose is fabricated in layers of elastomer (synthetic rubber) and braided fabric or braided wire, which permits operation at higher pressures.As illustrated in Fig. 4-13, the outer layer is normally synthetic rubber and serves to protect the braid layer. The hose can have as few as three layers (one being braid) or can have multiple layers to handle elevated pressures. When multiple wire layers are used, they may alternate with synthetic rubber layers, or the wire layers may be placed directly over one another.Figure 4-14 gives some typical hose sizes and dimensions for single-wire braid and double-wire braid designs. Size specifications for a single-wire braid hose represent the outside diameter in sixteenths of an inch of standard tubing, and the hose will have about the same inside diameter as the tubing. For example, a size 8 single-wire braid hose will have an inside diameter very close to a-in. standard tubing. For double-braided hose, the size specification equals the actual inside diameter in sixteenths of an inch. For example, a size 8 double-wire braid hose will have a-in. inside diameter. The minimum bend radii values provide the smallest values for various hose sizes to prevent undue strain or flow interference.Figure 4-15 illustrates five different flexible hose designs whose constructions are described as follows:a. FC 194: Elastomer inner tube, single-wire braid reinforcement, and elastomer cover Working pressures vary from 375 to 2750 Pa depending on the size.b.FC195: Elastomer inner tube, double-wire braid reinforcement, and elastomer cover. Working pressures vary from 1125 to 5000 Pa depending on the size.c.FC 300: Elastomer inner tube, polyester inner braid, single-wire braid reinforcement, and polyester braid cover. Working pressures vary from 350 to 3000 Pa depending on the size.d.1525: Elastomer inner tube, textile braid reinforcement, oil and mildew resistant, and textile braid cover. Working pressure is 250 Pa for all sizes.e.2791: Elastomer inner tube, partial textile braid, four heavy spiral wire reinforcements, and elastomer cover. Working pressure is 2500 Pa for all sizes.Hose FittingsHose assemblies of virtually any length and with various end fittings are available from manufacturers. See Fig. 4-16 for examples of hoses with the following permanently attached end fittings: (a) straight fitting, (b) 45 elbow fitting, and (c) 90 elbow fitting.The elbow-type fittings allow access to hard-to-get-at connections. They also permit better flexing and improve the appearance of the system.Figure 4-17 shows the three corresponding reusable-type end fittings. These types can be detached from a damaged hose and reused on a replacement hose. The renewable fittings idea had its beginning in 1941. With the advent of World War II, it was necessary to get aircraft with failed hydraulic lines back into operation as quickly as possible.Hose Routing and InstallationCare should be taken in changing fluid in hoses since the hose and fluid materials must be compatible. Flexible hose should be installed so there is no kinking during operation of the system. There should always be some slack to relieve any strain and allow for the absorption of pressure surges. It is poor practice to twist the hose and use long loops in the plumbing operation. It may be necessary to use clamps to prevent chafing or tangling of the hose with moving parts. If the hose is subject to rubbing, it should be encased in a protective sleeve. Figure 4-18 gives basic information on hose routing and installation procedures.1.8 QUICK DISCONNECT COUPLINGSOne additional type of fitting is the quick disconnect coupling used for both plastic tubing and flexible hose. It is used mainly where a conductor must be disconnected frequently from a component. This type of fitting permits assembly and disassembly in a matter of a second or two. The three basic designs are:1. Straight through: This design offers minimum restriction to flow but does not prevent fluid loss from the system when the coupling is disconnected.2.One-way shutoff: This design locates the shutoff at the fluid source connection but leaves the actuator component unblocked. Leakage from the system is not excessive in short runs, but system contamination due to the entrance of dirt in the open end of the fitting can be a problem, especially with mobile equipment located at the work site.3.Two-way shutoff: This design provides positive shutoff of both ends of pressurized lines when disconnected. See Fig.r a cutaway of this type of quick disconnect coupling. Figure 4-20 shows an external view of the same coupling. Such a coupling puts an end to the loss of fluids. As soon as you release the locking sleeve, valves in both the socket and plug close, shutting off flow. When connecting, the plug contacts an 0-ring in the socket, creating a positive seal. There is no chance of premature flow or waste due to a partial connection. The plug must be fully seated in the socket before the valves will open.1.9 METRIC STEEL TUBINGIn this section we examine common metric tube sizes and show how to select the proper size tube based on flow-rate requirements and strength considerations.Figure 4-21 shows the common tube sizes used in fluid power systems. Note that the smallest od size is 4 mm (0.158 in.), whereas the largest od size is 42 mm (1.663 in.). These values compare to 0.125 in. and 1.500 in., respectively, from Fig. 4-7 for common English units tube sizes. It should be noted that since 1 m = 39.6 in. then 1 mm = 0.0396 in.Factors of safety based on corresponding operating pressures becomeFS = 8 for pressures from 0 to 1000 Pa (0 to 7 MPa or 0 to 70 bars)FS = 6 for pressures from 1000 to 2500 Pa (7 to 17.5 MPa or 70 to 175 bars)FS = 4 for pressures above 2500 Pa (17.5 MPa or 175 bars)The corresponding tensile strengths for SAE 1010 dead soft cold-drawn steel and AISI 4130 steel are:SAE 101055,000 Pa or 379 MPaAISI 413075,000 Pa or 517 MPaEXAMPLE 1-5Select the proper metric size steel tube for a flow rate of 0.00190m3/s and an operating pressure of 70 bars. The maximum recommended velocity is 6.1 m/s and the tube material is SAE 1010 dead soft cold-drawn steel having a tensile strength of 379 MPa.Solution The minimum inside diameter based on the fluid velocity limitation of 6.1 rn/s is found using Eq. (3-18):Solving for A we have:Since we have the final resulting equation:Substituting values we have:From Fig. 4-21, the smallest acceptable od tube size is:22-mm od, 1.0-mm wall thickness, 20-mm IDFrom Eq. (4-3) we obtain the burst pressure.Then we calculate the working pressure using Eq. (4-4).This pressure is not adequate (less than operating pressure of 70 bars), so lets examine the next larger size od tube having the necessary ID.28-mm od, 2.0-mm wall thickness, 24-mm IDThis result is acceptable.中文译文浅谈油管液压管路系统设计Eric Sandgren 加州大学机械工程学院, avialon西部大街503号, 邮编962531, VA23284-3015收稿日期： 2003 年2月20日。1.1 简述在液压系统中, 液压油经过的系统包括管路和管接头, 这些液压油从油箱经过各机构的组成部分又回到油箱。因为在这过程中能量是通过这些管路传送到液压系统的各个部分(用来连接系统组分的管路和管接头), 所以为了总系统能够很好的发挥效率，必须进行恰当地设计。选用管路类型主要取决于系统的工作压力和流量。另外, 它的选择还取决于环境条件譬如油液的类型, 操作温度, 振动, 而且和连接部分之间是否有相对行动也有关系。管路可以通过的工作压力可以达到1000 Pa或者更大。一般情况下, 钢管材与管道相比，配管的灵活性更好、更加洁净而且管接头也比较少，更加的方便。但是, 用管道输送比钢管材较便宜。塑料管材因为它资源利用率高并且由于它的灵活性连接比较方便，增加了它的工业用途。软管主要用来连接相对行动组分的部分。它们由大量的弹性化合物组成，能处理超出10,000 Pa的压力。在腐蚀性比较强的条件下一般使用不锈钢管路和管接头。但是, 它们比较昂贵, 只有在需要的情况下才可使用。铜管路不应该用在液压机构中，因为铜具有促进石油氧化作用。锌, 镁, 和钙管路也不应该被使用，因为由于水甘醇它们会迅速地被腐蚀掉。应该避免使用镀锌的管路，因为它的表面很容易剥落并且会融入液压液体。当使用钢管或钢管材, 液压管接头应该由钢制成除了一些回路等地方，这些地方可以使用铸铁。在设计管路和管接头时必须慎重地考虑它的安全性。它们必须具有足够的强度，不仅能够承受稳定系统压力而且还要承受由于液压震动而产生的瞬间压力。当控制阀突然被关闭时, 停止液压,这需要很多的动能。稳定系统设计时，应该考虑到这一过程可能需要二倍或四倍的冲击力。并且考虑由于突然停止或重载初可能造成的压力冲击。在设计时应该考虑到这些高压冲击的安全因素。1.2管路尺寸管路必须有一个足够大的面积，用来处理变速的要求。在一个管路中当我们谈到可变的速度譬如管子, 我们提到平均速度。因为速率是变化的所以平均速度的概念非常重要。依照速度是在管壁和在管子的中心线上达到一个最大值。由管子断面划分平均速度被定义为容量流速:换句话说, 平均速度是以管子合计容量流速的速度。一般被理解为流经管子最大内径的那个区积的速度。泵吸油管路的最大被允许速度为4ft/s (1.2 m/s)，是为了防止压力太低同时引起泵的运转。规定可通过的最大流速是20 ft/s (6.1 m/s)，这样是为了防止冲击、损失和油液的升温过大。规定这些最大值就是平均速度。例 1-1管子通过的流速是30gprn 。最小内径允许液压通过的平均速度不超出20 ft/ s 。解答由式(3-26),求D:例 1-2通过管子的流量为0.002。求出可以通过平均速度低于6.1 m/ s的最小内径。解答我们求得最小需要的管子截面积为:现在可以求出最小内径, 因为，可以求D为：1.3 管路压力规定值由于在液压运动下管路壁上会产生的强大压力(叫做强压)，所以管路必须具有足够强度用来防止爆裂。这巨大的压力, 必须由管路材料承受, 由图4-1可确定。我们变化的压力(p) 相对一个圆管子的长度(l)。管子外径D0, 内径Di,并且壁厚为t。由于液压的压力一般在管子的内表面上,它试图把有压力的一半从管子的另外一半分离出来。显示这压力作用在管子的底下一半。为了防止管子的底下一半从上半方分离, 上半方总的向上的拉伸量为F。二分之一力(或F/2 )作用在各壁的断面(tL), 如显示。重要的是压力大小和总拉力必须是相等,可以有：A是管子曲壁表面区积平分线以下的一半。因而,均等宽度Di和长度L长方形的区积, 如上图4-1(b)。因此,作用在管子上的压力由壁断面划分承受的总力。这压力称压强，因为力(f) 是拉伸力(作用在它)的区积。替代变换我们可以求得：这里= 希腊标志(斯格码)= 压强由式 (4-2)我们可以求得,当液压的压力增加，压强随着增加，当管子内径并且增加。另外, 当管厚减小压强增加，并且管子的长度对压强没有任何影响。爆裂压力和工作压力爆裂压力(BP)是可以导致管子裂裂的液压的压力。当压强 ()大于抗拉强度(s)是管子发生爆裂。材料爆裂的压强取决于材料的抗拉强度。注意,一个轴向划线被显示在管子外壁表面。这个划线行显示何处管子会发生崩裂和如果压强达到了管子的抗拉强度时材料因而爆裂。当液压压力(p)达到BR 时，这爆裂将发生。因而,由式(4-2) 爆裂压力是工作压力(WP) 是安全工作的最大液压压力并且被定义为划分了由爆裂压力安全(FS) 一个适当的因素。安全因素是保证管路的坚固用来确定工作压力的最高安全水平。根据对应的工作压力标准推荐下面的安全因素:FS=8 为压力从0 到1000 PaFS=6 为压力从1000 年到2500 PaFS=4 为压力在2500 Pa之上为了达到期望压力的系统, 规定10种安全因素。管路尺寸根据流速和压力考虑通过给定条件确定管路尺寸如下:1.根据流速要求计算最小内径(Di)。2.根据流速要求选择管路的标准内径大于或等于计算出来的值。3.由选出的标准使用以下等式确定壁厚(t):4.根据管路材料和系统工作压力(p), 确定抗拉强度(s)和安全因素(FS)。5. 由式(4-3)和(4-4)计算爆裂压力(BP) 和工作压力(WP) 。6. 如果计算的工作压力大于液压的工作压力, 选择的管路是可接受的。如果不是,必须重新选择管路的标准尺寸以及壁厚。一个可用的管路必须是一个符合流速要求和等于或大于系统的工作压力。命名原则和参量单位式s(4-2), (4-3), (4-4),和(4-5)如下:BP=裂裂了压力(Pa, MPa)Di=管路内径(in., m)D0=管路外部直径(in., m)FS=安全因素(dimensionless)P=系统工作的可变压力(Pa, MPa)S=管路材料抗拉强度(Pa, MPa)t=管路壁厚(in., m)WP=工作压力(Pa, MPa)=压强(Pa, MPa)例1-3钢管材有外部直径a 1.250m,和内径a 1.060m。它由SAE 1010 冷制钢制成，抗拉强度有55.000 Pa。这支管会它安全工作压力为承担安全因素8?首先解答,计算管材的壁厚:其次,管材爆裂压力为:最后,计算管安全工作压力:厚壁管管路的用途只能允许厚壁圆筒比率Di/t大于10。这是因为在厚壁圆筒里(Di /t10), 依照式(4-2)假设拉力管的壁厚和管径不是一致的。式(4-6)为厚壁圆筒，使用时必须考虑到不均匀的拉力, 因而,如果考虑管路不是一个薄壁圆筒, 计算时必须使用式(4-6)。如被期望的那样，由式(4-6)计算比由式(4-3)计算，可以获得更小的爆裂压力和工作压力。这能比较二个等式并且注意发现在式(4-6)分母上加1.2t。注意钢管材例子4-3 是一个薄壁圆筒，因为=1.060/0.095=11.210。因而, 依照计算，钢管材例子4-3可以1230 Pa安全地工作，使用工作压力安全因素8。用式(4-6) 为这个

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