【溫馨提示】 dwg后綴的文件為CAD圖，可編輯，無水印，高清圖，，壓縮包內(nèi)文檔可直接點開預覽，需要原稿請自助充值下載，請見壓縮包內(nèi)的文件及預覽，所見才能所得，請細心查看有疑問可以咨詢QQ：414951605或1304139763

邵陽學院畢業(yè)設(shè)計（論文） 目錄 前言 1 1 概述 2 1.1 拉伸的目的和作用 2 1.2 牽伸機組原理 2 2 設(shè)計參數(shù)的確定 4 2.1 年產(chǎn)2萬噸滌綸短纖后處理工藝流程 4 2.2 設(shè)計基礎(chǔ) 4 2.3確定牽伸旦數(shù)D 5 3 牽伸機構(gòu)受力分析 5 4 第三牽伸機功率估算 6 5 七輥牽伸機的整體分析 8 5.1 第一牽伸機設(shè)計 8 5.2 第二牽伸機設(shè)計 9 5.3 第三牽伸機設(shè)計 10 6 牽伸輥受力分析 11 7 牽伸輥筒的設(shè)計 16 8 法蘭聯(lián)接螺釘性能等級和材料確定 18 9 通水牽伸軸設(shè)計 20 10 牽伸輥的校核計算 25 10.1 強度計算 25 10.2 撓度計算 26 11 潤滑方式與密封裝置 28 總結(jié) 30 參考文獻 31 致謝 32 附表1 33 附表2 34 附表3 35 邵陽學院畢業(yè)設(shè)計（論文）進度考核表 設(shè)計（論文）課題 滌綸短纖后處理設(shè)備七輥牽伸機的牽伸輥設(shè)計 院（系） 機械與能源工程系 年級專業(yè) 02機制本科 學生姓名 文藝苑 學號 0241118057 指導教師 姜宏陽 起止日期 畢業(yè)設(shè)計（論文）各階段工作任務 完成情況 指導教師簽字 2.20~3.10 熟悉課題，收集資料 3.11~3.20 擬訂設(shè)計方案 3.21~3.31 進行總體分析計算，確定基本結(jié)構(gòu) 4.1~4.5 牽伸輥受力分析 4.6~4.10 牽伸輥筒的設(shè)計 4.11~4.15 通水牽伸軸設(shè)計 4.16~4.18 潤滑方式與密封裝置 4.19~5.10 繪畫圖紙 5.11~5.25 撰寫設(shè)計計算說明書 5.26~5.31 修改計算說明書 6.1~6.4 說明書排版 6.5～6.8 準備答辯 備 注 注：本表用于考核學生畢業(yè)設(shè)計（論文）的進度及完成情況，是學生畢業(yè)答辯資格認定和成績評定 的依據(jù)之一。 ·12· 邵陽學院畢業(yè)設(shè)計（論文） On the profile design of transmission splines and keys Daniel 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; Keys 1 Introduction A 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 assumptions As 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 deformation The 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 deformation The 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 It’s 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 remarks The 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. References [1] 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) 579–586. [5] S.H. Tong, New conjugate pair design—theory 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. 56–63. [8] Y. Ariga, S. Nagata, Load capacity of a new W–N gear with basic rack of combined circular and involute profile, Transaction of ASME Journal of Mechanisms, Transmissions, and Automation in Design 107 (1985) 565–572. [9] M.J. French, Gear conformity and load capacity, in: Proc Instn Mech Engrs, vol. 180(43), Pt 1, (1965–66), pp. 1013–1024. [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) 543–553. [11] H. Iyoi, S. Ishimura, v-Theory in gear geometry, Transaction of ASME Journal of Mechanisms, Transmissions, and Automation in Design 105 (1983) 286–290. [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) 373–389. [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) 536–542. [14] Charles Fox, Calculus of Variations, Oxford University Press, 1954. ARTICLE IN PRESS 7 邵陽學院畢業(yè)設(shè)計（論文） 關(guān)于傳動花鍵和平鍵的外形設(shè)計 Daniel C.H. Yang, Shih-Hsi Tong 摘要：花鍵和平鍵是安裝在軸和鍵槽間的傳輸動力的機械零件?；ㄦI(或鍵)通常安裝在動力傳動副中的軸上，在軸上開有相應的鍵槽。本文分析了槽軸外形對動力傳輸?shù)挠绊?。本文陳述了三種不同設(shè)計類型的花鍵的外形設(shè)計。用微分的方法來計多算外形函數(shù)的最大值，可以成功地得到所要的數(shù)據(jù)。計算表明花鍵以及斷開線外形引起鍵槽的變形。此外，他們能承載最大的傳動載荷。另外，輻形平直的外形能提高傳動的效率。我們認為該發(fā)現(xiàn)值得報道，該種方法同時也可用于其他花鍵的設(shè)計。 關(guān)鍵字：花鍵，平鍵 1 介紹 鍵是安裝在軸和鍵槽等動力傳動裝置如齒輪和扣練齒輪之間的零件?；ㄦI發(fā)揮著和鍵一樣的作用，將力矩從軸傳到配合零件上?；ㄦI和平鍵的主要區(qū)別是花鍵和平鍵連為一體的，而鍵是安裝在鍵槽上的。與一個或兩個用來傳動動力的鍵相比，在軸上一般有四個或更多的花鍵。因此，傳輸?shù)牧馗愣?，每個花鍵上的所受的載荷較低。在傳輸力矩中，花鍵發(fā)揮著重要的作用，花鍵的外形對動力傳輸?shù)挠绊懞艽?。與共軛外形不同，帶有花鍵和鍵槽的軸有同樣的轉(zhuǎn)動軸，他們之間沒有相對運動，是緊密配合的。他們聯(lián)結(jié)在一起，有著相同的角速度。因此,它表明除軸外形之外的任何外形都可以用做花鍵的設(shè)計。然而，實際上花鍵和鍵槽間的載荷并不是分布在整個接觸表面的。載荷通常集中在接觸表面的某小一部分和可變形的鍵表面。當循環(huán)工作較久時，這就會引起軸和鍵槽之間不希望得到的空隙，并引起鍵槽表面的損壞。為了解決這些問題，需要更進一步分析花鍵的外形是怎樣影響力矩傳輸?shù)?，以便做出合適的花鍵外形設(shè)計。 目前使用中主要有兩種花鍵，分別為直線邊花鍵和漸進線花鍵。漸進線花鍵具有自動調(diào)心的配合零件，可以用標準平頭釘切削器切除齒輪的齒。目前，相關(guān)的研究都著重于共軛外形齒輪的設(shè)計以及彎曲外形的設(shè)計，以來減少配合表面的磨損。然而，由于不同的工作狀況，它們都不能直接應用于花鍵的外形。在本論文中，建立了花鍵外形的基本公式，在不同設(shè)計對象中用來分析所要求的外形。三個設(shè)計對象，恒定變形，傳輸最大力矩和最佳傳動效率，這三項被用來計算花鍵外形。成功地得到了分析方法。 2 陳述問題并提出基本假設(shè) 如圖1所示，軸傳動輪轂同時花鍵固定在軸上。設(shè)計要求決定了軸半徑、花鍵高度、花鍵齒數(shù)，因此不能改動。只能通過改變花鍵的輪廓來提高傳動性能。為簡化設(shè)計問題以便于分析，做出以下幾點假設(shè)： （1） 花鍵是剛體 相對輪轂，花鍵由剛性材料制成并假設(shè)它在承受負載后無變形。 （2） 輪轂屬彈性變形 輪轂表面變形在彈性變形范圍內(nèi)時，表面壓力與變形量成正比。 （3） 花鍵無軸向變形 通?；ㄦI的齒高相對于齒寬尺寸小很多。因此，我們假設(shè)鍵端無積累變形，只有輪轂面有變形。 （4） 花鍵與輪轂接觸處無間隙（面接觸） 花鍵形狀與輪轂形狀不考慮制造誤差完全一致。它們屬于面接觸沒有間隙。 圖1 花鍵 3 花鍵變形跟輪轂變形一致 設(shè)計的第一目標是使輪轂表面變形一致，那就要求輪轂上的壓力均布。這樣能保證表面承受的壓力均勻分布，以避免一些危險點損壞材料。如圖2，表示軸半徑，表示花鍵的小旋轉(zhuǎn)角。因為我們假定花鍵為剛體，所以花鍵任兩點之間的變化就是輪轂的變形?；ㄦI聯(lián)接按照鍵的橫截面開頭分為矩形花鍵聯(lián)接和漸開線花鍵聯(lián)接。 圖2 花鍵小旋轉(zhuǎn)角 4 危險截面確定簡單 傳統(tǒng)設(shè)計方法考慮的前提是把影響零件工作狀態(tài)的設(shè)計變量，如應力、強度、安全系數(shù)、載荷、環(huán)境因素、材料性能、零件尺寸和結(jié)構(gòu)因素等，都處理成確定的單值變量。描述零件狀態(tài)的數(shù)學模型，即變量與變量的關(guān)系，是通過確定性的函數(shù)進行單值變換獲得危險截面。 常用的危險截面的確定方法有以下幾種： 4．1 花鍵的最小直徑法 花鍵危險截面的可靠度非常高(幾乎為 100％)，這是由于花鍵的直徑是按傳統(tǒng)的設(shè)計經(jīng)驗確定的。若要求適當?shù)目煽慷戎?，則花鍵的直徑可選用較小的值。 4．2 可靠性安全系數(shù)法 采用可靠性安全系數(shù)法設(shè)計時，必須知道應力和強度的分布類型與分布參數(shù)估計值。而可靠性數(shù)據(jù)的積累又是一項長期的工作，因而我們必須利用現(xiàn)有的數(shù)據(jù)資料，運用有關(guān)定理與法則(如中心極限定理和“3 法則”等 )，來確定設(shè)計過程中所涉及的許多隨機變量的分布類型與分布參數(shù)。在可靠性安全系數(shù)計算 中，是把所涉及的設(shè)計參數(shù)都處理成隨機變量，將安全系數(shù)的概念與可靠性的概念聯(lián)系起來，從而建立相應的概率模型。由于考慮到工程實際中發(fā)生的現(xiàn)象及表征參數(shù)的不確定性(隨機性)，因而更能揭示事物的本來面貌。理論分析與實踐表明，可靠性設(shè)計比傳統(tǒng)機械設(shè)計，能更有效地處理設(shè)計中一些問題，提高產(chǎn)品質(zhì)量，減少零件尺寸，從而節(jié)約原材料，降低成本。 5 結(jié)束語 機械可靠性設(shè)計是近幾十年來發(fā)展起來的一種現(xiàn)代設(shè)計理論和方法，它以提高產(chǎn)品質(zhì)量為核心 ，以概率論 、數(shù)理統(tǒng)計為基礎(chǔ) ，綜合運用工程力學 、系統(tǒng)工程學 、運籌學等多學科知識來研究機械工程最優(yōu)設(shè)計問題。目前 ，可靠性設(shè)計的理論已趨于完善，但真正用于機械零件設(shè)計工程實際的卻很少。采用可靠性安全系數(shù)法設(shè)計時，必須知道應力和強度的分布類型與分布參數(shù)估計值。而可靠性數(shù)據(jù)的積累又是一項長期的工作，因而我們必須利用現(xiàn)有的數(shù)據(jù)資料，運用有關(guān)定理與法則，來確定設(shè)計過程中所涉及的許多隨機變量的分布類型與分布參數(shù)。 本文講述了三種花鍵（或平鍵）形狀最佳設(shè)計標準。用變量積分法來確定輪廓公式以及最大值，由此獲得分析結(jié)果。從結(jié)果可以看出，漸開線花鍵導致輪轂變形一致，此外，能傳遞的載荷最大。另外，矩形花鍵傳動最高效。相信如果要增加新的性能標準，別的形狀的花鍵很少會被用到。 參考文獻 [1] 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) 579–586. [5] S.H. Tong, New conjugate pair design—theory 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. 56–63. [8] Y. Ariga, S. Nagata, Load capacity of a new W–N gear with basic rack of combined circular and involute profile, Transaction of ASME Journal of Mechanisms, Transmissions, and Automation in Design 107 (1985) 565–572. [9] M.J. French, Gear conformity and load capacity, in: Proc Instn Mech Engrs, vol. 180(43), Pt 1, (1965–66), pp. 1013–1024. [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) 543–553. [11] H. Iyoi, S. Ishimura, v-Theory in gear geometry, Transaction of ASME Journal of Mechanisms, Transmissions, and Automation in Design 105 (1983) 286–290. [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) 373–389. [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) 536–542. [14] Charles Fox, Calculus of Variations, Oxford University Press, 1954. ARTICLE IN PRESS 5