涤纶短纤后处理设备七辊牵伸机的牵伸辊设计
喜欢就充值下载吧。资源目录里展示的文件全都有,请放心下载,有疑问咨询QQ:414951605或者1304139763 = 喜欢就充值下载吧。资源目录里展示的文件全都有,请放心下载,有疑问咨询QQ:414951605或者1304139763 =
邵阳学院毕业设计(论文)任务书专业班级2002机本学生姓名文艺苑学 号057课题名称涤纶短纤后处理设备七辊牵伸机的牵伸辊设计设计(论文)起止时间2006 年 2 月 20 日至2006 年 6 月 10 日课题类型工程设计、应用研究、开发研究、软件工程、理论研究、其他课题性质真实一、 课题研究的目的与主要内容课题研究的目的是:1.培养学生综合运用所学理论知识、解决工程问题的能力。 2.培养学生的工程素养,使学生在文献检索,工程资料查阅及运用计算机绘图方面得到进一步锻炼。 课题研究的主要内容: 1.完成30005000个单词以上与涤纶后处理设备有关外文资料翻译(打印稿),译文要求准确、文字流畅。2.了解涤纶后处理设备加工工艺。3.根据涤纶短纤的年产量,计算牵伸力的大小,确定牵伸轴及牵伸辊的尺寸。4.完成牵伸辊的结构设计,画出整套装配图及零件图。5.按统一格式和规范撰写设计说明书。二、 基本要求1. 学生应在教师的指导下按时完成所规定的内容和工作量,编写符合要求的设计计算说明书,并正确绘制整套机械图表。2. 学生依据课题任务,认真收集有关资料,熟悉有关化学纤维加工工艺,正确使用各类工具书;掌握有关工程设计的程序、方法和技术规范;锻炼分析与解决工程实际问题的能力。3. 在设计中应树立正确的设计思想,培养严肃认真的科学态度,严谨求实的工作作风。4. 毕业设计说明书应包括与设计题目有关的阐述说明及计算,内容完整,文字流畅,符合毕业设计规范。5. 熟练运用CAD绘制机械图表。注:1、此表由指导教师填写,经各系、教研室主任审批生效; 2、此表1式3份,学生、指导教师、教研室各1份。三、课题研究已具备的条件(包括实验室、主要仪器设备、参考资料)该产品在邵阳纺织机械股份公司已开始研制,并取得一定的效果,邵阳纺织机械股份公司可提供一定的技术支持。 1.涤纶短纤生产 东南大学出版社 1999年 2.机械设计手册(上、中、下) 化学出版社 2000年 3.化纤机械设计 中国纺织出版社 1997年四、设计(论文)进度表2月20日3月10日,熟悉课题,进行调研,收集有关资料,拟订设计方案3月11日4月21日,进行有关分析计算,确定设备基本结构,完成技术设计4月22日5月21日,进行施工设计,完成所有图表,撰写设计计算说明书5月22日6月10日,设计修改、完善,完成答辩五、教研室审批意见教研室主任(签名) 年 月 日六、院(系)审批意见院(系)负责人(签名) 单位(公章) 年 月 日指导教师(签名) 学生(签名)12邵阳学院毕业设计(论文)内容提要涤纶短纤维后处理设备七辊牵伸机牵伸辊属于牵伸机的工作部分,合理设计将提高七辊牵伸机的性能。牵伸机是纺丝后处理的主要设备之一,根据纺丝的工艺要求来确定牵伸机的数量和功率。本次设计的七辊牵伸机主要是为了提高年产量,从牵伸机组的整体设计出发,按照总牵伸倍数合理布局各级牵伸倍数,按照年产量计算最大牵伸旦数,最大牵伸力;按照牵伸力求出第三牵伸机辊筒的受力情况,依据最大辊筒受力来对辊筒进行强度、刚度校核,及其螺钉的校核。根据受力情况对牵伸辊和牵伸轴进行结构设计,要求结构简单、加工方便、经济可行。牵伸辊的联接的方式采用法兰联接,比内夹套联接结构简单、装配方便。合理设计通水牵伸辊部件,利用分配板使进水和出水流量均匀,充分带走热量。参照现有的七辊牵伸机设备,设计出满足工作要求的牵伸辊,以达到大容量生产涤纶短纤维的目的,满足现代高速纺织机械的发展。AbstractPolyester staple aftertreatment equipment 7-roller drawing machines rollers are work part of the drawing machine. And the performance of 7-roller drawing machine will be improved if its correctly designed. The drawing machine is one of the main equipments in the filature aftertreatment. According to the filature processing requirement we can decide the number and power of the drawing machine. This 7-roller drawing machine design is to enhance the annual output. Taking the drawing machine group as an organic whole design, through the total drawing multiple properly distributing each class drawing multiple, according to the annual output calculating the maximal drawing denier and maximal drawing tension, then on the basis of the drawing tension figuring out the force of third drawing machine roller, and according to the maximal roller force checking the intensity and rigidity and proofing the bolt.On the basis of the rollers force designing the frames of the drawing rollers and drawing shafts, which require simple frames, convenient manufacturing, economical and feasible. The link method of the drawing roller adopts flanges, which compares with the inner sleeve link has simple structure, convenient assemblage. Correctly designing the watering drawing roller parts, using the distributing board making the in water and out water equably flowing, and taking out the heat. Consulting the existent 7-roller drawing machine equipments, designing drawing rollers which satisfy the work requirement, and reach the objective of a large amount of polyester staple are produced, meet contemporary high-speed textile mechanical development.II邵 阳 学 院毕业设计(论文)课 题 名 称 涤纶短纤后处理设备七辊牵伸机的牵伸辊设计 学 生 姓 名 文 艺 苑 学 号 0241118057 院(系)、专业 机械与能源工程系 02机制本科 指 导 教 师 姜 宏 阳 职 称 高级工程师 2006年 06 月 2 日邵 阳 学 院毕业设计(论文)开题报告书课题名称 涤纶短纤后置处理设备七辊牵伸机的牵伸辊设计 学生姓名 文 艺 苑 学 号 0241118057 院(系)、专业 机械与能源工程系 02机制本科 指导教师 姜 宏 阳 2006年 2 月 28 日一、 课题的来源、目的意义(包括应用前景)、国内外现状及水平课题来源:本课题来源于邵阳纺织机械有限公司。据中国纺织报报道,涤纶在强力、耐磨等性能上明显超过人造纤维和天然纤维,表现出巨大的市场需求和增长空间,再加上生产流程较短,成本较低,使我国迅速成为世界上涤纶产量最大的国家。2005年,我国化学纤维产量达1424万吨,比2003年增长20%,产量居世界之首,年增幅比世界平均增幅高出13个百分点,成就喜人。中国化纤协会预计,2003年我国涤纶产量可占化纤产量的79%,到2010年涤纶在纺织纤维总量中的比重可能提高到50%左右。市场拉动了化纤产品的迅速增加,化纤产品的生产促进了化纤机械的发展。牵伸机是涤纶短纤后置处理设备之一。目的意义:目前国际上涤纶短纤维大型成套装置的单线产能最高为年产5万吨,攻克此技术已成为各国权威专家和各大生产厂家的目标。一项涤纶短纤维重大科技攻关项目年产6万吨成套涤纶短纤维工程技术开发项目,经过6个月的精心准备和试验,7月7日在上海石化公司获得突破性进展,其攻关的核心技术中心吹风的丝束准确成型技术达到了预期目标。此试验成功,标志着我国涤纶短纤维大型成套生产技术在国际上处于领先地位。我国年产6万吨短纤维国产化工程技术和软件包项目是以技术开发为主。中心吹风的丝束冷却成型技术是年产6万吨短纤维成套生产技术中的核心,全套技术设备国产化率达到80%,大大降低了投资,带来可贵的经济效益和社会效益。国内外现状及水平:国产长丝纺丝与后置处理设备已经比较成熟,大量占有国内市场。年产3万吨的涤纶短纤纺丝及后处理成套设备已供国内70多条线并投入生产,成套出口到国际市场上的项目也陆续投产,赢得了好评。年产5万吨的涤纶短纤成套设备国内建设项目已经安装完毕,近期即将投入生产。年产6万吨的成套设备正在现场安装近期也将投产。二、 课题研究的主要内容、研究方法或工程技术方案和准备采取的措施课题研究主要内容:1. 完成3000单词以上与毕业设计有关的英文资料翻译(打印稿),译文要求准确,文字流畅2. 了解涤纶后处理加工工艺3. 根据涤纶短纤的年产量,计算牵伸力,确定牵伸轴及牵伸辊的尺寸4. 完成牵伸辊的结构设计,画出整装配图及零件图5. 撰写说明书(打印稿),格式和内容符合邵阳学院的统一格式和规范要求研究方法或工程技术方案:1. 工作运动分析2. 部件联结方式3. 产品结构设计准备采取的措施:1. 进入邵阳纺织机械有限公司对该牵伸机进行调研2. 搜索和统计相关资料和数据3. 结合邵阳纺织机械有限公司的实际零件进行分析4. 完成七辊牵伸机辊筒设计三、现有基础和具备的条件现有的基础:通过四年的理论学习和几次课程设计及多次工厂实地参观,我对机械设计的设计内容、设计方法和设计步骤有了一定的了解,掌握了机械设计设计的基本知识,如设计计算、工程绘图、查阅资料和手册,熟悉标准和规范等,有一定的独立工作能力。具备的条件:1. 专业资深指导老师一位2. 设计数据一份3. 个人电脑一台4. AutoCAD2004设计软件 5. WORD办公软件 6. 图书馆有关资料四、总的工作任务,进度安排以及预期结果总的工作任务:应用自己所学的理论知识,结合自己掌握的资料,在指导老师的指导和同学讨论确定牵伸机辊筒的设计方案,完成设计计算,绘出零件图、装配图,编写一份说明书,准备答辩。进度安排:1. 2月20日3月10日,熟悉课题,进行调研、收集资料、方案拟订2. 3月11日4月21日,计算、分析、编写说明书3. 4月22日5月21日,完成图纸,修改说明书、刻录光盘4. 5月22日 6月10日,准备答辩五、指导教师审查意见指导教师(签名) 年 月 日 六、教研室审查意见教研室主任(签名) 年 月 日 七、院(系)审查意见院(系)主任(签名) 年 月 日 备 注 邵阳学院毕业设计(论文)目录前言11 概述21.1 拉伸的目的和作用21.2 牵伸机组原理22 设计参数的确定42.1 年产2万吨涤纶短纤后处理工艺流程42.2 设计基础42.3确定牵伸旦数D53 牵伸机构受力分析54 第三牵伸机功率估算65 七辊牵伸机的整体分析85.1 第一牵伸机设计85.2 第二牵伸机设计95.3 第三牵伸机设计106 牵伸辊受力分析117 牵伸辊筒的设计168 法兰联接螺钉性能等级和材料确定189 通水牵伸轴设计2010 牵伸辊的校核计算2510.1 强度计算2510.2 挠度计算2611 润滑方式与密封装置28总结30参考文献31致谢32附表133附表234附表335邵阳学院毕业设计(论文)进度考核表设计(论文)课题 涤纶短纤后处理设备七辊牵伸机的牵伸辊设计院(系) 机械与能源工程系 年级专业 02机制本科 学生姓名 文艺苑 学号 0241118057 指导教师 姜宏阳 起止日期毕业设计(论文)各阶段工作任务完成情况指导教师签字2.203.10熟悉课题,收集资料3.113.20拟订设计方案3.213.31进行总体分析计算,确定基本结构4.14.5牵伸辊受力分析4.64.10牵伸辊筒的设计4.114.15通水牵伸轴设计4.164.18润滑方式与密封装置4.195.10绘画图纸5.115.25撰写设计计算说明书5.265.31修改计算说明书6.16.4说明书排版6.56.8准备答辩备注注:本表用于考核学生毕业设计(论文)的进度及完成情况,是学生毕业答辩资格认定和成绩评定的依据之一。11邵阳学院毕业设计(论文)On the profile design of transmission splines and keysDaniel C.H. Yang, Shih-Hsi Tong Abstract: Splines and keys are machinery components placed at the interface between shafts and hubs of power-transmitting elements. A spline (or key) is usually machined (or attached) onto the shaft of a power-transmitting pair, and the corresponding groove is cut into the hub. The influence of spline profiles on the performance of power transmission is investigated in this paper. The optimal design of spline profiles for three different design criteria is presented. The method of calculus of variation is used to determine profile functions for maximum value. Analytical results are successfully obtained. They show that the splines with involute profiles lead to uniform deformation on the hub, in addition they can carry the maximum transmission load capacity. On the other hand, radial straight profiles result in optimum transmission efficiency. We think that these findings are worthy reporting and also believe that this approach could be used for the spline design with other performance criteria imposed.Keywords: Splines; Keys1 IntroductionA key is a machinery component placed at the interface between a shaft and the hub of a power-transmitting element such as gear and sprocket . A spline performs the same function as a key in transmitting torque from the shaft to the mating element . The main difference between splines and keys is that splines are integral with the shaft but keys are inserted between shaft and hub. As compared with one or two keys used for load transmission, there are usually four or more splines on a shaft. Therefore, the transmission torque is more uniform and the loading for each spline is lower. Splines play an important role in transmitting torque and their profiles do have the influence on the performance of power transmission. Unlike the conjugate profiles, the shaft with splines and hub have the same rotation axis and they are in surface contact without relative motion, they are connected together and have the same angular velocity. Therefore, it seems that any profiles except the shaft surface can be used for the design of splines. However, the load between the spline and hub is not evenly distributed over the entire contact surface in practice. The load may always concentrate on a small portion of contact surface and deformthe hub surface. This results in undesired clearance between the shaft and hub and will lead to serious damage of hub surface as the working cycles increase. To solve these problems, how the profiles of splines affect the torque transmission needs to be further investigated to find out the suitable design of spline profiles.Currently there are two main types of splines used, namely, straight-sided and involute splines. The involute splines provide the mating element with self-centering and can be machined with standard hob cutter used to cut gear teeth. To date, the related research work focuses on conjugate profiles and gear design as well as the design of profile curvatures for reducing the wear of contact surfaces. However, none of them can be applied to the profiles of splines directly due to different working conditions. Also, there is no research work on how to design spline profiles under given requirements. In this paper, the basic equations for spline profiles are established and used to synthesize desired profiles for different design objectives. Three design objectives, uniform deformation, maximum torque transmission, and optimum efficiency, are used to determine spline profiles. Analytical solutions are successfully obtained.2 Problem description and basic assumptionsAs shown in fig .1, The hub is driven by the shaft and the spline is fixed on the shaft. The radius of the shaft, the height of the spline, and the number of spline teeth are determined by the design requirements and cannot be altered. Only the spline profile can be modified to improve the performance of transmission. To simplify the design problem for analysis, the following assumptions were made:(1) The spline is a rigid body.Compared with the hub, the spline is made of hard material and assumed no deformation after applying the load.(2) The hub is under elastic deformationThe surface deformation of the hub is within the range of elasticity and the surface stress is proportional to the normal deformation.(3) There is no beam deformation on the spline.For spline keys, usually the height of tooth shape is small relative to its width. Therefore, we assume there is no accumulated deformation at the free end. The only deformation is the normal deformation on the hub surface.(4) There is no clearance between the spline and hub when they are in contact. (Surface contact)The profile of the spline is exactly the same as that of the hub without considering manufacturing errors. They are in surface contact without clearance.3 Spline profile for uniform hub deformationThe first design objective is to have the uniform deformation on the surface of the hub, which also implies the uniform stress on the hub. This design can ensure the surface stress is evenly distributed and avoid the failure of material at some weak points. Referring to fig.2, Let denote the radius of shaft and denote a small rotation angle of spline. Since we assume that the spline is a rigid body, the change between two spline positions will be the deformation of the hub. 4 Its simply to confirmed the dangerous sections Prerequisite that traditional design method considered whether pair influence part design variable of working state, for instance stress , intensity , safety coefficient , load , environmental factor , material performance , part size and structural factor ,etc., deal with the single value variable confirmed. Describe part mathematical model of state , i.e. variable and relation of variable , to go on single value vary and win the dangerous section through deterministic function.There are several methods that usually the dangerous sections are determined: 4.1 Minimum diameter of the spline Spline dangerous sectional reliability very getting high, this to confirm according to traditional design experience because of diameter of spline. If require appropriate reliability value, then the diameter of the axle can select smaller value for use .4.2 Safety coefficient law of dependability While adopting the safety coefficient law design of dependability , must know the distribution types of stress and intensity and be distributed estimated value of the parameter . And the accumulation of dependability data is a long-term job, therefore we must utilize the existing data materials , it is (such as the terminal theorem in the centre and 3 rules to use relevant theorems and rule ), to confirm the distribution types of a lot of random variables involved of design process and is distributed the parameter. In the safety coefficient of dependability is calculated , deal with all design parameters involved a random variable, link the concept of safety coefficient to concept of dependability , thus set up corresponding probability model. Because of considering the uncertainty (randomness ) of the phenomenon taking place in project reality and sign parameter, therefore can announce the original appearances of the things even more. Theory analysis and practice indicate , the dependability design is designed more than traditional machinery , can punish some problem of the design , raise product quality , reduce part size effective, thus save the raw materials , lower costs .5 Concluding remarksThe mechanical reliability design is one kind of modern design theory and the method which in the recent several dozens years develop, it take improves the product quality as the core, take the theory of probability, the mathematical statistic as the foundation, synthesizes using the engineering mechanics, the system engineering, the operations research and so on the multi-disciplinary knowledge studies the mechanical engineering most superior design question. At present, the reliability design theory tended to the consummation, but uses in the machine parts design project actual very being actually few truly. When uses the reliable security method of correlates design, must know the stress and the intensity distributed type and the distributed parameter estimated value. But the reliable data accumulation also is a long-term work, thus we must use the existing data material, the utilization related theorem and the principle, determined in the design process involves many random variable distributed types and distributed parameter. In this paper the optimal design of spline (or key) profiles for three different design criteria is presented. The method of calculus of variation is used to determine profile functions for maximum value. Analytical results are successfully obtained. It shows that the splines with involute profiles lead to uniform deformation on the hub, in addition they can carry the maximum transmission load capacity. On the other hand radial straight profiles result in optimum transmission efficiency. We believe similar approach could be used to determine other spline profiles when new performance criteria are imposed.References1 Robert L. Mott, Machine Elements in Mechanical Design, third ed., Prentice-Hall Inc., 1999.2 M.F. Spotts, Design of Machine Elements, third ed., Prentice-Hall Inc., 1961.3 Joseph E. Shigley, Larry D. Mitchell, Mechanical Engineering Design, fourth ed., McGraw-Hill Inc., 1983.4 D.C.H. Yang, S.H. Tong, J. Lin, Deviation-function based pitch curve modification for conjugate pair design, Transaction of ASME Journal of Mechanical Design 121 (4) (1999) 579586.5 S.H. Tong, New conjugate pair designtheory and application, PhD Dissertation, Mechanical and Aerospace Engineering Department, UCLA, 1998.6 F.L. Litvin, Gear Geometry and Applied Theory, Prentice-Hall Inc., 1994.7 D.B. Dooner, A.A. Seireg, The Kinematic Geometry of Gearing, John Wiley & Sons Inc., 1995, pp. 5663.8 Y. Ariga, S. Nagata, Load capacity of a new WN gear with basic rack of combined circular and involute profile, Transaction of ASME Journal of Mechanisms, Transmissions, and Automation in Design 107 (1985) 565572.9 M.J. French, Gear conformity and load capacity, in: Proc Instn Mech Engrs, vol. 180(43), Pt 1, (196566), pp. 10131024.10 A.O. Lebeck, E.I. Radzimovsky, The synthesis of tooth profile shapes and spur gears of high load capacity, Transaction of ASME Journal of Engineering for Industry (1970) 543553.11 H. Iyoi, S. Ishimura, v-Theory in gear geometry, Transaction of ASME Journal of Mechanisms, Transmissions, and Automation in Design 105 (1983) 286290.12 J.E. Beard, D.W. Yannitell, G.R. Pennock, The effects of the generating pin size and placement on the curvature and displacement of epitrochoidal gerotors, Mechanism and Machine Theory 27 (4) (1992) 373389.13 H.C. Liu, S.H. Tong, D.C.H. Yang, Trapping-free rotors for high sealing lobe pumps, Transaction of ASME Journal of Mechanical Design 122 (4) (2000) 536542.14 Charles Fox, Calculus of Variations, Oxford University Press, 1954.ARTICLE IN PRESS7
收藏