減速器開題報告

1、精選優(yōu)質(zhì)文檔-傾情為你奉上精選優(yōu)質(zhì)文檔-傾情為你奉上專心-專注-專業(yè)專心-專注-專業(yè)精選優(yōu)質(zhì)文檔-傾情為你奉上專心-專注-專業(yè)畢業(yè)設(shè)計（論文）材料之二（2）本科畢業(yè)設(shè)計(論文)開題報告題目：某型號矯直機減速器的設(shè)計、建模及運動仿 真課 題 類 型： 設(shè)計 實驗研究 論文 學 生 姓 名：黃偉 學 號： 專 業(yè) 班 級： 機械設(shè)計制造及其自動化101 學 院：機械與汽車工程學院 指 導(dǎo) 教 師： 疏達 開 題 時 間： 2014/03/03 4年 03 月03 日開題報告內(nèi)容與要求畢業(yè)設(shè)計內(nèi)容及研究意義（價值）隨著社會的發(fā)展和人民生活水平的提高，人們對產(chǎn)品的需求是多樣化的，這就決定了未來的生產(chǎn)方

2、式趨向多品種、小批量。在各行各業(yè)中十分廣泛地使用著齒輪減速器，它是一種不可缺少的機械傳動裝置. 它是機械設(shè)備的重要成部分和核心組件。圓柱齒輪減速器是一種使用非常廣泛的機械傳動裝置。減速器是用于原動機與工作機之間的獨立的傳動裝置，用來降低轉(zhuǎn)速和增大轉(zhuǎn)矩，以滿足工作需要。在現(xiàn)代機械中應(yīng)用極為廣泛，具有品種多、批量小、更新?lián)Q代快的特點。圓柱齒輪減速器設(shè)計的內(nèi)容主要包括減速器原始數(shù)據(jù)及傳動方案的選擇，確定傳動裝置的傳動比及參數(shù)的計算，直齒圓柱齒輪傳動的設(shè)計，軸的設(shè)計 ，聯(lián)軸器的選擇 ，軸承的校核 ，鍵的強度校核 ，箱體結(jié)構(gòu)設(shè)計 ，減速器的潤滑與密封 ，減速器的三維建模 ，減速器的運動仿真。畢業(yè)設(shè)計的研

3、究現(xiàn)狀和發(fā)展趨勢（文獻綜述）研究現(xiàn)狀：1、國外減速器技術(shù)發(fā)展簡況齒輪減速器在各行各業(yè)中十分廣泛地使用著，是一種不可缺少的機械傳動裝置。當前減速器普遍存在著體積大、重量大，或者傳動比大而機械效率過低的問題。國外的減速器，以德國、丹麥和日本處于領(lǐng)先地位，特別在材料和制造工藝方面占據(jù)優(yōu)勢，減速器工作可靠性好，使用壽命長。但其傳動形式仍以定軸齒輪傳動為主，體積和重量問題，也未解決好。最近報導(dǎo)，日本住友重工研制的FA型高精度減速器，美國Alan-Newton公司研制的X-Y式減速器，在傳動原理和結(jié)構(gòu)上與本項目類似或相近，都為目前先進的齒輪減速器。當今的減速器是向著大功率、大傳動比、小體積、高機械效率以及

4、使用壽命長的方向發(fā)展。因此，除了不斷改進材料品質(zhì)、提高工藝水平外，還在傳動原理和傳動結(jié)構(gòu)上深入探討和創(chuàng)新，平動齒輪傳動原理的出現(xiàn)就是一例。減速器與電動機的連體結(jié)構(gòu)，也是大力開拓的形式，并已生產(chǎn)多種結(jié)構(gòu)形式和多種功率型號的產(chǎn)品。目前，超小型的減速器的研究成果尚不明顯。在醫(yī)療、生物工程、機器人等領(lǐng)域中，微型發(fā)動機已基本研制成功，美國和荷蘭近期研制的分子發(fā)動機的尺寸在納米級范圍，如能輔以納米級的減速器，則應(yīng)用前景遠大。2、國內(nèi)減速器技術(shù)發(fā)展簡況國內(nèi)的減速器多以齒輪傳動、蝸桿傳動為主，但普遍存在著功率與重量比小，或者傳動比大而機械效率過低的問題。另外，材料品質(zhì)和工藝水平上還有許多弱點，特別是大型的減速

5、器問題更突出，使用壽命不長。60年代開始生產(chǎn)的少齒差傳動、擺線針輪傳動、諧波傳動等減速器具有傳動比大，體積小、機械效率高等優(yōu)點。但受其傳動的理論的限制，不能傳遞過大的功率，功率一般都要小于40kw。90年代初期，國內(nèi)出現(xiàn)的三環(huán)(齒輪)減速器，是一種外平動齒輪傳動的減速器，它可實現(xiàn)較大的傳動比，傳遞載荷的能力也大。它的體積和重量都比定軸齒輪減速器輕，結(jié)構(gòu)簡單，效率亦高。由于該減速器的三軸平行結(jié)構(gòu)，故使功率/體積(或重量)比值仍小。且其輸入軸與輸出軸不在同一軸線上，這在使用上有許多不便。北京理工大學研制成功的內(nèi)平動齒輪減速器不僅具有三環(huán)減速器的優(yōu)點外，還有著大的功率/重量(或體積)比值，以及輸入軸

6、和輸出軸在同一軸線上的優(yōu)點，處于國內(nèi)領(lǐng)先地位。國內(nèi)有少數(shù)高等學校和廠礦企業(yè)對平動齒輪傳動中的某些原理做些研究工作，發(fā)表過一些研究論文，在利用擺線齒輪作平動減速器開展了一些工作。由于內(nèi)平動齒輪機構(gòu)傳動效率高、體積小、輸入輸出同軸線，故由廣泛的應(yīng)用前景。發(fā)展趨勢：目前國內(nèi)外齒輪減速器的發(fā)展趨向為，產(chǎn)品制造水平進一步精密化，承載能力進一步得以提高，各種不同系列產(chǎn)品之間的模塊化互換程度越來越高，這對系列產(chǎn)品的大批量生產(chǎn)提供了便利，也為產(chǎn)品的進一步擴展留下了空間。目前國際上幾大典型的傳動基礎(chǔ)件公司均擁有獨具特色的模塊化產(chǎn)品組合體系和極其豐富的產(chǎn)品系列，產(chǎn)品銷售網(wǎng)絡(luò)遍布全球。在國外，齒輪減速器系列無國家標

7、準，只有企業(yè)自己的系列產(chǎn)品和標準，各企業(yè)的產(chǎn)品及標準基本上是每5年更新一次?？傊斀袷澜绺鲊鴾p速器及齒輪技術(shù)發(fā)展總趨勢向六高二低二化方面發(fā)展。六高即高承載能力、高齒面硬度、高精度、高速度、高可靠性和高傳動效率；二低即低噪聲、低成本；二化即標準化、多樣化。減速器和齒輪的設(shè)計與制造技術(shù)的發(fā)展，在一定程度上標志著一個國家的工業(yè)水平，因此，開拓和發(fā)展減速器和齒輪技術(shù)在我國有廣闊的前景。三、畢業(yè)設(shè)計研究方案及工作計劃本設(shè)計的主要內(nèi)容是減速器原始數(shù)據(jù)及傳動方案的選擇，確定傳動裝置的傳動比及參數(shù)的計算，直齒圓柱齒輪傳動的設(shè)計，軸的設(shè)計 ，聯(lián)軸器的選擇 ，軸承的校核 ，鍵的強度校核 ，箱體結(jié)構(gòu)設(shè)計 ，減速器

8、的潤滑與密封 ，減速器的三維建模 ，減速器的運動仿真，具體工作計劃安排如下：工作計劃：起止日期 起止周工作安排 軟件備注02-2303-09 12 開題報告 03-1003-16 3相關(guān)資料搜集準備 CAD03-1703-30 45 直齒圓柱齒輪傳動和軸的設(shè)計 UG03-3104-06 6聯(lián)軸器的選擇 UG04-0704-137軸承和鍵的校核 UG04-1404-20 8箱體結(jié)構(gòu)設(shè)計 UG04-2104-27 9減速器的潤滑與密封 UG04-2805-11 1011減速器的三維建模 UG05-1205-25 12-13 減速器的運動仿真 UG05-2606-01 14撰寫設(shè)計說明書 WORD0

9、6-0206-0815論文的提交審核及修改 06-0906-15 16畢業(yè)答辯 四、主要參考文獻1 吳宗澤，羅圣國，機械設(shè)計課程設(shè)計手冊M.3版，北京：高等教教育育出版社，20062 濮良貴，紀名剛，機械設(shè)計M，8版.北京：高等教育出版社，20063 張展，齒輪設(shè)計與實用數(shù)據(jù)速查M.北京：機械工業(yè)出版社，20094 朱龍根，簡明機械零件設(shè)計手冊M.北京：機械工業(yè)出版社，19975 朱輝等，畫法幾何及工程制圖M，6版.上海：上?？茖W技術(shù)出版社，20076 姜繁，國內(nèi)外液壓氣動系統(tǒng)接頭手冊M.北京：中國標準出版社，19937 胡仁喜，CAXA 2006平面與實體造型機械設(shè)計高級應(yīng)用實例M.北京：機

10、械工業(yè)出版社，20068 程乃士主編，減速器和變速器設(shè)計與選用手冊M.北京市：機械工業(yè)出版社 , 20069 陶冶，材料成形技術(shù)基礎(chǔ)M.北京：機械工業(yè)出版社，200210 趙雪松，任小華，于華，機械制造裝備設(shè)計M .武漢：華中科技大學出版社，200911 張顯偉，胡靜，Word綜合應(yīng)用M.北京：清華大學出版社，200612 戴娟、 夏尊鳳、 汪大鵬，圓柱齒輪減速器設(shè)計中應(yīng)考慮的問題J.長沙大學，200513 A.M.Michael, S.D.Khepar, S.K.Sondhi. Water Wells and Pumps J. New Delhhi, 14 Dennis P. Nolan .

11、Fire Fighting Pumping Systems at Industrial Facilities J .New Jersey, 15 Garr M. Jones, Robert L. Sank, Bayard E. Baseman, George Tchobanoglous. Pumping station design J .Burlington. USA: Elsevier Inc, 2008.16 William B. Rugh, Waterville, Ohio，Right angle drive gearbox J .Publication Date: 03/07/200

12、0 ，1-6201 年 月 日五、外文文獻Talking about the optimum Design for reduction box SummaryA.M.Michael, S.D.Khepar, S.K.Sondhi. Tata-McGraw-Hill Publishing Company LTD, New Delhhi, 2008reducer is gearing widely used among the all kinds of mechanical equipment. Gearbox design merits will be directly affect the d

13、rive performance of the transmission equipment. This article analysis of two main gearbox design optimization methods by contrast analysis, then , reducer design need to considering factors was presented .which is constraints restraint conditions ,object functions and variables, and so on.Key words

14、: reducer optimizationTraditional gearbox design normally through repeated discussion together, check to determine the design, although it can get that meet the given criteria design effects, but generally not be the best. In order to make the reducer for best performance, you must be optimized for

15、speed reducer, reducer optimization can different optimization goals. Except for some very special occasions, often can be divided into the form from the structure on the pursuit of the smallest size (weight), from the use of performance pursuit of maximum load capacity, from the economic point of v

16、iew to consider pursuing the minimum fee, three class goals. First class goals and objectives of the second class of the reducer of a contradiction, i.e. mass (weight) and carrying capacity. To a certain volume, reducer load capacity is limited; in carrying capacity must, reducer volume (weight) of

17、reduce is limited. Thus, these two types of objectives embodied in essence is the same. Just before a class to load capacity as design criteria, the size (weight) as the optimization goal; the latter category instead,to a certain size (weight) as design criteria, the carrying capacity as optimizatio

18、n goals. The third goal, will involve a significant number of factors, in addition to the design of the rationality of the reducer, also depends on the companys labor organization, management, equipment, personnel and material prices and other factors. But for designers, the goal of ultimately comes

19、 down to a first class or second class target, that is, reduce or increase the volume reduction gears its carrying capacity.First, single-stage optimal design of cylindrical gear reducer or increase its carrying capacity of the volume.Single-stage final drive, which can consist of a pair of conical

20、gear, a pair of cylindrical gears or composed by the worm, has a simple structure, the quality of small, low cost, easy to use. But its main transmission ratio i= 0 not too large, the general i =0 7, and further enhance i =0 will increase the diameter of the driven gear, thereby reducing the ground

21、clearance, and so driven gear heat treatment difficult. Widely used single-stage main gear box cars and light and medium goods vehicle driven by the bridge. Single Gear reducer size is minimized by the optimal design, is a 16 6-dimensional inequality constraint optimization problem, its mathematical

22、 model can be denoted .Optimized design; meet the strength requirements reducer greatly reduce the size of, reducing material and design costs and increased efficiency and quality. Optimization method is closely associated with traditional design, optimize the design is based on the traditional desi

23、gn, follows the traditional design of large amounts of data accumulate in, while taking into account the traditional design of the relevant factors involved. Optimal design although traditional design of some, but the design still has its limitations so that it can be used in optimum design reliabil

24、ity technology, introduced in fuzzy logic, forming reliability optimization or reliability and other modern design, engineering design and technology by hard to soft development.Second, concrete mixer truck Optimal Design of gear reducer1. the main argumentsConcrete mixer truck mixer drum (tank) vol

25、ume 8 10m3, maximum 12 angle, speed 2 4r/min and 10 12r/min (discharge of reverse speed); reducer, 131: 1 gear ratio for maximum output torque 60 kN m, require transmission of high efficiency, sealing, noise, interchange. 2.2 The structural design includes the front cover components, passive wheel a

26、ssembly, the first stage planetary gear assembly, the second stage planetary gear assembly, the central component and the body flange 6 most of the components. Body connection between the use of bolts and pins and positioning, between the body and the inner ring gear pins using flexible set of insti

27、tutions are set out. In order to facilitate the user in using assembly and disassembly, the main axis reducer design and installation of a 15 angle, flange axis can X, Y and Z direction of swing 6 , and use special spherical bearings as bearing. Into planetary gear bearings, the spring ring mounted

28、on the lateral and axial bearing clearance 0.2 mm, reducer maximum dimensions 467 mm 460 mm 530 mm, total weight (without oil) to 290 kg.2. Drive SystemThe reduction reducer with three options: first-class high-speed gear transmission, the other two for the NGW planetary gear transmission. Among the

29、m, the second and third respectively, three and four hollow-type planet wheel, planetary gear rack installed in the arm-type planets, planetary gear and the use of rolling bearing as floating bearing; the second level between the planet carrier and the flange use of double tooth gear coupling to con

30、nect, concrete mixer truck on the tooth surface contact fatigue strength reducer, gear tooth root bending fatigue strength and wear requirements are too stringent, so a reasonable choice of coefficient and for modification calculation is very important.Third, the mathematical model of optimal design

31、 reducer1. the objective functionFor the C-type problem, the objective function is A = min (f (x) = min (f (x1, x2, ., xn) type in: A - Total pitch reducer, that the sum of all levels of the center distance ; x - the design variables (including all levels of pitch, module, helix angle,number of teet

32、h, tooth width and the coefficient, etc.); n - the number of design variables. For the P-type problem, the objective function is P = max (f (x) = max (f (x1, x2, ., xn). The formula: P - Reducer license bearing power; x - with the C-type; n - the same C type.2. ConstraintsThe constraint is the judgm

33、ent of the objective function in the design of the variable if possible some provisions, therefore reducer optimization process each choice of designs; should be are all constraints are satisfied of the optimization. For reducer, in the lists for the optimal design of constraints, should respect thi

34、s has to be considered in a careful and comprehensive. For example, the design of the variable itself takes rules, gear and other parts of the relationship between, and so on. Reducer optimization should consider the following constraints:(1) values of the discrete design variable constraintsTeeth:

35、The teeth of each gear should be integers; module: module should be standard gear module series (GB1357-78); center distance: In order to avoid the creation and maintenance of the various problems, the center distance to 10mm for the unit step long.(2) design variable values of upper and lower bound

36、s constraintsHelix Angle: The zero gear, helical gear by the use of engineering to take 8 15 ; total coefficient: Given that the coefficient will affect the carrying capacity of gear, often taken to be 0 to 0.8.(3)gear strength constraintsGear strength constraint is the gear tooth contact fatigue st

37、rength and tooth bending fatigue strength, both calculated according to national standard GB3480-83 in the method. Strength is sufficient, according to the actual factor of safety is reached or exceeded a predetermined factor of safety inspection.(4) gear of undercutting constraintsTo avoid undercut

38、ting, a minimum number of teeth, gears is 17, helical gear is 14 16.(5) parts of the interference constraintsRequirements of Center distance, addendum circle and shaft diameter among meet geometric relationship of non-interference. For tri-reducer (Figure 1), interference constraint is equivalent to

39、 two constraints: the second level of Center distance should be greater than the level 1 large gear top RADIUS and third-level Pinion addendum circle radius of and; at the third level of Center distance should be greater than the second-largest gear top RADIUS and 4th axis radius of and. L2 gear ana

40、logy.Figure 1 Schematic diagram of three reducerFour. concluding remarksMechanical optimization is in general machinery on the basis of the design development and extension of the new design, and optimization of the gearbox is one of them is to traditional designs, follows the traditional design of

41、large amounts of data accumulate in, while taking into account the traditional design of the relevant factors involved. In practice has produced a good technical and economic efficiency, reduced material and design costs and increased efficiency and quality, the reducer to best performance.譯文:淺談減速機的

42、優(yōu)化摘要：減速器是各類機械設(shè)備中廣泛應(yīng)用的傳動裝置。減速器設(shè)計的優(yōu)劣直接影響機械設(shè)備的傳動性能。本文通過對兩種減速器主要優(yōu)化設(shè)計方法的分析，提出了減速器設(shè)計中應(yīng)考慮的約束條件、目標函數(shù)和變量等。關(guān)鍵詞：減速器 優(yōu)化設(shè)計傳統(tǒng)的減速器設(shè)計一般通過反復(fù)的試湊、校核確定設(shè)計方案，雖然也能獲得滿足給定條件的設(shè)計效果，但一般不是最佳的。為了使減速器發(fā)揮最佳性能，必須對減速器進行優(yōu)化設(shè)計，減速器的優(yōu)化設(shè)計可以在不同的優(yōu)化目標下進行。除了一些極為特殊的場合外，通?？梢苑譃閺慕Y(jié)構(gòu)形式上追求最小的體積(重量)、從使用性能方面追求最大的承載能力、從經(jīng)濟效益角度考慮追求最低費用等三大類目標。第一類目標與第二類目標體現(xiàn)

43、著減速器設(shè)計中的一對矛盾，即體積(重量)與承載能力的矛盾。在一定體積下，減速器的承載能力是有限的；在承載能力一定時，減速器體積(重量)的減小是有限的。由此看來，這兩類目標所體現(xiàn)的本質(zhì)是一樣的。只是前一類把一定的承載能力作為設(shè)計條件，把體積(重量)作為優(yōu)化目標；后一類反之，把一定的體積(重量)作為設(shè)計條件，把承載能力作為優(yōu)化目標。第三類目標的實現(xiàn)，將涉及相當多的因素，除減速器設(shè)計方案的合理性外，還取決于企業(yè)的勞動組織、管理水平、設(shè)備構(gòu)成、人員素質(zhì)和材料價格等因素。但對于設(shè)計人員而言，該目標最終還是歸結(jié)為第一類或第二類目標，即減小減速器的體積或增大其承載能力。一、單級圓柱齒輪減速器的優(yōu)化設(shè)計單級主

44、減速器可由一對圓錐齒輪、一對圓柱齒輪或由蝸輪蝸桿組成，具有結(jié)構(gòu)簡單、質(zhì)量小、成本低、使用簡單等優(yōu)點。但是其主傳動比i0不能太大，一般i07，進一步提高i0將增大從動齒輪直徑，從而減小離地間隙，且使從動齒輪熱處理困難。單級主減速器廣泛應(yīng)用于轎車和輕、中型貨車的驅(qū)動橋中。單級圓柱齒輪減速器以體積最小為優(yōu)化目標的優(yōu)化設(shè)計問題，是一個具有16個不等式約束的6維優(yōu)化問題，采用優(yōu)化設(shè)計方法后，在滿足強度要求的前提下，減速器的尺寸大大地降低，減少了用材及成本，提高了設(shè)計效率和質(zhì)量。優(yōu)化設(shè)計法與傳統(tǒng)設(shè)計密切相關(guān)，優(yōu)化設(shè)計是以傳統(tǒng)設(shè)計為基礎(chǔ)，沿用了傳統(tǒng)設(shè)計中積累的大量資料，同時考慮了傳統(tǒng)設(shè)計所涉及的有關(guān)因素。優(yōu)化設(shè)計雖然彌補了傳統(tǒng)設(shè)計的某些不足，但該設(shè)計法仍有其局限性，因此可在優(yōu)化設(shè)計中引入可靠性技術(shù)、模糊技術(shù)，形成可靠性優(yōu)化設(shè)計或模糊可靠性優(yōu)化設(shè)計等現(xiàn)代設(shè)計法，使工程設(shè)計技術(shù)由“硬”向“軟”發(fā)展。二、混凝土攪拌運輸車減速器的優(yōu)化設(shè)計1.主要參數(shù)混凝土攪拌運輸車攪拌筒(罐)