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邵陽學(xué)院畢業(yè)設(shè)計(jì)（論文）任務(wù)書
專業(yè)班級
2002機(jī)本
學(xué)生姓名
文藝苑
學(xué) 號
057
課題名稱
滌綸短纖后處理設(shè)備七輥牽伸機(jī)的牽伸輥設(shè)計(jì)
設(shè)計(jì)(論文)
起止時間
2006 年 2 月 20 日至2006 年 6 月 10 日
課題類型
工程設(shè)計(jì)、應(yīng)用研究、開發(fā)研究、
軟件工程、理論研究、其他
課題性質(zhì)
真實(shí)
一、 課題研究的目的與主要內(nèi)容
課題研究的目的是：
1.培養(yǎng)學(xué)生綜合運(yùn)用所學(xué)理論知識、解決工程問題的能力。
2.培養(yǎng)學(xué)生的工程素養(yǎng)，使學(xué)生在文獻(xiàn)檢索，工程資料查閱及運(yùn)用計(jì)算機(jī)繪圖方面得到進(jìn)一步鍛煉。
課題研究的主要內(nèi)容：
1.完成3000～5000個單詞以上與滌綸后處理設(shè)備有關(guān)外文資料翻譯（打印稿），譯文要求準(zhǔn)確、文字流暢。
2.了解滌綸后處理設(shè)備加工工藝。
3.根據(jù)滌綸短纖的年產(chǎn)量，計(jì)算牽伸力的大小，確定牽伸軸及牽伸輥的尺寸。
4.完成牽伸輥的結(jié)構(gòu)設(shè)計(jì)，畫出整套裝配圖及零件圖。
5.按統(tǒng)一格式和規(guī)范撰寫設(shè)計(jì)說明書。
二、 基本要求
1. 學(xué)生應(yīng)在教師的指導(dǎo)下按時完成所規(guī)定的內(nèi)容和工作量，編寫符合要求的設(shè)計(jì)計(jì)算說明書，并正確繪制整套機(jī)械圖表。
2. 學(xué)生依據(jù)課題任務(wù)，認(rèn)真收集有關(guān)資料，熟悉有關(guān)化學(xué)纖維加工工藝，正確使用各類工具書；掌握有關(guān)工程設(shè)計(jì)的程序、方法和技術(shù)規(guī)范；鍛煉分析與解決工程實(shí)際問題的能力。
3. 在設(shè)計(jì)中應(yīng)樹立正確的設(shè)計(jì)思想，培養(yǎng)嚴(yán)肅認(rèn)真的科學(xué)態(tài)度，嚴(yán)謹(jǐn)求實(shí)的工作作風(fēng)。
4. 畢業(yè)設(shè)計(jì)說明書應(yīng)包括與設(shè)計(jì)題目有關(guān)的闡述說明及計(jì)算，內(nèi)容完整，文字流暢，符合畢業(yè)設(shè)計(jì)規(guī)范。
5. 熟練運(yùn)用CAD繪制機(jī)械圖表。
注：1、此表由指導(dǎo)教師填寫，經(jīng)各系、教研室主任審批生效；
2、此表1式3份，學(xué)生、指導(dǎo)教師、教研室各1份。
三、課題研究已具備的條件（包括實(shí)驗(yàn)室、主要儀器設(shè)備、參考資料）
該產(chǎn)品在邵陽紡織機(jī)械股份公司已開始研制，并取得一定的效果，邵陽紡織機(jī)械股份公司可提供一定的技術(shù)支持。
1.滌綸短纖生產(chǎn) 東南大學(xué)出版社 1999年
2.機(jī)械設(shè)計(jì)手冊（上、中、下） 化學(xué)出版社 2000年
3.化纖機(jī)械設(shè)計(jì) 中國紡織出版社 1997年
四、設(shè)計(jì)（論文）進(jìn)度表
2月20日～3月10日，熟悉課題，進(jìn)行調(diào)研，收集有關(guān)資料，擬訂設(shè)計(jì)方案
3月11日～4月21日，進(jìn)行有關(guān)分析計(jì)算，確定設(shè)備基本結(jié)構(gòu)，完成技術(shù)設(shè)計(jì)
4月22日～5月21日，進(jìn)行施工設(shè)計(jì)，完成所有圖表，撰寫設(shè)計(jì)計(jì)算說明書
5月22日～6月10日，設(shè)計(jì)修改、完善，完成答辯
五、教研室審批意見
教研室主任（簽名） 年 月 日
六、院（系）審批意見
院（系）負(fù)責(zé)人（簽名） 單位（公章） 年 月 日
指導(dǎo)教師（簽名） 學(xué)生（簽名）
·13·
邵陽學(xué)院畢業(yè)設(shè)計(jì)（論文）
內(nèi)容提要
滌綸短纖維后處理設(shè)備七輥牽伸機(jī)牽伸輥屬于牽伸機(jī)的工作部分，合理設(shè)計(jì)將提高七輥牽伸機(jī)的性能。牽伸機(jī)是紡絲后處理的主要設(shè)備之一，根據(jù)紡絲的工藝要求來確定牽伸機(jī)的數(shù)量和功率。本次設(shè)計(jì)的七輥牽伸機(jī)主要是為了提高年產(chǎn)量，從牽伸機(jī)組的整體設(shè)計(jì)出發(fā)，按照總牽伸倍數(shù)合理布局各級牽伸倍數(shù)，按照年產(chǎn)量計(jì)算最大牽伸旦數(shù)，最大牽伸力；按照牽伸力求出第三牽伸機(jī)輥筒的受力情況，依據(jù)最大輥筒受力來對輥筒進(jìn)行強(qiáng)度、剛度校核，及其螺釘?shù)男：恕?
根據(jù)受力情況對牽伸輥和牽伸軸進(jìn)行結(jié)構(gòu)設(shè)計(jì)，要求結(jié)構(gòu)簡單、加工方便、經(jīng)濟(jì)可行。牽伸輥的聯(lián)接的方式采用法蘭聯(lián)接，比內(nèi)夾套聯(lián)接結(jié)構(gòu)簡單、裝配方便。合理設(shè)計(jì)通水牽伸輥部件，利用分配板使進(jìn)水和出水流量均勻，充分帶走熱量。參照現(xiàn)有的七輥牽伸機(jī)設(shè)備，設(shè)計(jì)出滿足工作要求的牽伸輥，以達(dá)到大容量生產(chǎn)滌綸短纖維的目的，滿足現(xiàn)代高速紡織機(jī)械的發(fā)展。
Abstract
Polyester staple aftertreatment equipment 7-roller drawing machine’s rollers are work part of the drawing machine. And the performance of 7-roller drawing machine will be improved if it’s 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 roller’s 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 陽 學(xué) 院
畢業(yè)設(shè)計(jì)(論文)
課 題 名 稱 滌綸短纖后處理設(shè)備七輥牽伸機(jī)的牽伸輥設(shè)計(jì)
學(xué) 生 姓 名 文 藝 苑
學(xué) 號 0241118057
院(系)、專業(yè) 機(jī)械與能源工程系 02機(jī)制本科
指 導(dǎo) 教 師 姜 宏 陽
職 稱 高級工程師
2006年 06 月 2 日
邵 陽 學(xué) 院
畢業(yè)設(shè)計(jì)（論文）開題報告書
課題名稱 滌綸短纖后置處理設(shè)備七輥牽伸機(jī)的牽伸輥設(shè)計(jì)
學(xué)生姓名 文 藝 苑
學(xué) 號 0241118057
院（系）、專業(yè) 機(jī)械與能源工程系 02機(jī)制本科
指導(dǎo)教師 姜 宏 陽
2006年 2 月 28 日
一、 課題的來源、目的意義（包括應(yīng)用前景）、國內(nèi)外現(xiàn)狀及水平
課題來源：
本課題來源于邵陽紡織機(jī)械有限公司。據(jù)《中國紡織報》報道，滌綸在強(qiáng)力、耐磨等性能上明顯超過人造纖維和天然纖維，表現(xiàn)出巨大的市場需求和增長空間，再加上生產(chǎn)流程較短，成本較低，使我國迅速成為世界上滌綸產(chǎn)量最大的國家。2005年，我國化學(xué)纖維產(chǎn)量達(dá)1424萬噸，比2003年增長20%，產(chǎn)量居世界之首，年增幅比世界平均增幅高出13個百分點(diǎn)，成就喜人。中國化纖協(xié)會預(yù)計(jì)，2003年我國滌綸產(chǎn)量可占化纖產(chǎn)量的79%，到2010年滌綸在紡織纖維總量中的比重可能提高到50%左右。市場拉動了化纖產(chǎn)品的迅速增加，化纖產(chǎn)品的生產(chǎn)促進(jìn)了化纖機(jī)械的發(fā)展。牽伸機(jī)是滌綸短纖后置處理設(shè)備之一。
目的意義：
目前國際上滌綸短纖維大型成套裝置的單線產(chǎn)能最高為年產(chǎn)5萬噸，攻克此技術(shù)已成為各國權(quán)威專家和各大生產(chǎn)廠家的目標(biāo)。一項(xiàng)滌綸短纖維重大科技攻關(guān)項(xiàng)目——年產(chǎn)6萬噸成套滌綸短纖維工程技術(shù)開發(fā)項(xiàng)目，經(jīng)過6個月的精心準(zhǔn)備和試驗(yàn)，7月7日在上海石化公司獲得突破性進(jìn)展，其攻關(guān)的核心技術(shù)——中心吹風(fēng)的絲束準(zhǔn)確成型技術(shù)達(dá)到了預(yù)期目標(biāo)。此試驗(yàn)成功，標(biāo)志著我國滌綸短纖維大型成套生產(chǎn)技術(shù)在國際上處于領(lǐng)先地位。我國年產(chǎn)6萬噸短纖維國產(chǎn)化工程技術(shù)和軟件包項(xiàng)目是以技術(shù)開發(fā)為主。中心吹風(fēng)的絲束冷卻成型技術(shù)是年產(chǎn)6萬噸短纖維成套生產(chǎn)技術(shù)中的核心，全套技術(shù)設(shè)備國產(chǎn)化率達(dá)到80%，大大降低了投資，帶來可貴的經(jīng)濟(jì)效益和社會效益。
國內(nèi)外現(xiàn)狀及水平：
國產(chǎn)長絲紡絲與后置處理設(shè)備已經(jīng)比較成熟，大量占有國內(nèi)市場。年產(chǎn)3萬噸的滌綸短纖紡絲及后處理成套設(shè)備已供國內(nèi)70多條線并投入生產(chǎn)，成套出口到國際市場上的項(xiàng)目也陸續(xù)投產(chǎn)，贏得了好評。年產(chǎn)5萬噸的滌綸短纖成套設(shè)備國內(nèi)建設(shè)項(xiàng)目已經(jīng)安裝完畢，近期即將投入生產(chǎn)。年產(chǎn)6萬噸的成套設(shè)備正在現(xiàn)場安裝近期也將投產(chǎn)。
二、 課題研究的主要內(nèi)容、研究方法或工程技術(shù)方案和準(zhǔn)備采取的措施
課題研究主要內(nèi)容：
1. 完成3000單詞以上與畢業(yè)設(shè)計(jì)有關(guān)的英文資料翻譯（打印稿），譯文要求準(zhǔn)確，文字流暢
2. 了解滌綸后處理加工工藝
3. 根據(jù)滌綸短纖的年產(chǎn)量，計(jì)算牽伸力，確定牽伸軸及牽伸輥的尺寸
4. 完成牽伸輥的結(jié)構(gòu)設(shè)計(jì)，畫出整裝配圖及零件圖
5. 撰寫說明書（打印稿），格式和內(nèi)容符合邵陽學(xué)院的統(tǒng)一格式和規(guī)范要求
研究方法或工程技術(shù)方案：
1. 工作運(yùn)動分析
2. 部件聯(lián)結(jié)方式
3. 產(chǎn)品結(jié)構(gòu)設(shè)計(jì)
準(zhǔn)備采取的措施：
1. 進(jìn)入邵陽紡織機(jī)械有限公司對該牽伸機(jī)進(jìn)行調(diào)研
2. 搜索和統(tǒng)計(jì)相關(guān)資料和數(shù)據(jù)
3. 結(jié)合邵陽紡織機(jī)械有限公司的實(shí)際零件進(jìn)行分析
4. 完成七輥牽伸機(jī)輥筒設(shè)計(jì)
三、現(xiàn)有基礎(chǔ)和具備的條件
現(xiàn)有的基礎(chǔ)：
通過四年的理論學(xué)習(xí)和幾次課程設(shè)計(jì)及多次工廠實(shí)地參觀，我對機(jī)械設(shè)計(jì)的設(shè)計(jì)內(nèi)容、設(shè)計(jì)方法和設(shè)計(jì)步驟有了一定的了解，掌握了機(jī)械設(shè)計(jì)設(shè)計(jì)的基本知識，如設(shè)計(jì)計(jì)算、工程繪圖、查閱資料和手冊，熟悉標(biāo)準(zhǔn)和規(guī)范等，有一定的獨(dú)立工作能力。
具備的條件：
1. 專業(yè)資深指導(dǎo)老師一位
2. 設(shè)計(jì)數(shù)據(jù)一份
3. 個人電腦一臺
4. AutoCAD2004設(shè)計(jì)軟件
5. WORD辦公軟件
6. 圖書館有關(guān)資料
四、總的工作任務(wù)，進(jìn)度安排以及預(yù)期結(jié)果
總的工作任務(wù)：
應(yīng)用自己所學(xué)的理論知識，結(jié)合自己掌握的資料，在指導(dǎo)老師的指導(dǎo)和同學(xué)討論確定牽伸機(jī)輥筒的設(shè)計(jì)方案，完成設(shè)計(jì)計(jì)算，繪出零件圖、裝配圖，編寫一份說明書，準(zhǔn)備答辯。
進(jìn)度安排：
1. 2月20日－3月10日，熟悉課題，進(jìn)行調(diào)研、收集資料、方案擬訂
2. 3月11日－4月21日，計(jì)算、分析、編寫說明書
3. 4月22日－5月21日，完成圖紙，修改說明書、刻錄光盤
4. 5月22日 －6月10日，準(zhǔn)備答辯
五、指導(dǎo)教師審查意見
指導(dǎo)教師（簽名）
年 月 日
六、教研室審查意見
教研室主任（簽名）
年 月 日
七、院（系）審查意見
院（系）主任（簽名）
年 月 日
備 注
邵陽學(xué)院畢業(yè)設(shè)計(jì)（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(jī)組原理 2
2 設(shè)計(jì)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(jì)基礎(chǔ) 4
2.3確定牽伸旦數(shù)D 5
3 牽伸機(jī)構(gòu)受力分析 5
4 第三牽伸機(jī)功率估算 6
5 七輥牽伸機(jī)的整體分析 8
5.1 第一牽伸機(jī)設(shè)計(jì) 8
5.2 第二牽伸機(jī)設(shè)計(jì) 9
5.3 第三牽伸機(jī)設(shè)計(jì) 10
6 牽伸輥受力分析 11
7 牽伸輥筒的設(shè)計(jì) 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(jì) 20
10 牽伸輥的校核計(jì)算 25
10.1 強(qiáng)度計(jì)算 25
10.2 撓度計(jì)算 26
11 潤滑方式與密封裝置 28
總結(jié) 30
參考文獻(xiàn) 31
致謝 32
附表1 33
附表2 34
附表3 35
邵陽學(xué)院畢業(yè)設(shè)計(jì)（論文）進(jìn)度考核表
設(shè)計(jì)（論文）課題 滌綸短纖后處理設(shè)備七輥牽伸機(jī)的牽伸輥設(shè)計(jì)
院（系） 機(jī)械與能源工程系 年級專業(yè) 02機(jī)制本科
學(xué)生姓名 文藝苑 學(xué)號 0241118057 指導(dǎo)教師 姜宏陽
起止日期
畢業(yè)設(shè)計(jì)（論文）各階段工作任務(wù)
完成情況
指導(dǎo)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(jì)方案
3.21~3.31
進(jìn)行總體分析計(jì)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(jì)
4.11~4.15
通水牽伸軸設(shè)計(jì)
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(jì)計(jì)算說明書
5.26~5.31
修改計(jì)算說明書
6.1~6.4
說明書排版
6.5～6.8
準(zhǔn)備答辯
備
注
注：本表用于考核學(xué)生畢業(yè)設(shè)計(jì)（論文）的進(jìn)度及完成情況，是學(xué)生畢業(yè)答辯資格認(rèn)定和成績評定
的依據(jù)之一。
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邵陽學(xué)院畢業(yè)設(shè)計(jì)（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
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