鏈式輸送機傳動裝置-一級蝸桿蝸輪減速器設計【F=7000N v=0.2m-s Z=10】【說明書+CAD】

鏈式輸送機傳動裝置-一級蝸桿蝸輪減速器設計【F=7000N v=0.2m-s Z=10】【說明書+CAD】,F=7000N v=0.2m-s Z=10,說明書+CAD,鏈式輸送機傳動裝置-一級蝸桿蝸輪減速器設計【F=7000N,v=0.2m-s,Z=10】【說明書+CAD】,鏈式,輸送,傳動,裝置,一級,蝸桿 機械設計課程設計說明書 課程名稱: 題目名稱: 學 院: 專業(yè)班級: 學 號: 姓 名: 指導教師: 第一章1.1機械設計課程設計任務書1.1.1 設計題目：鏈式運輸機減速器1.1 .2題目數(shù)據(jù)：原始數(shù)據(jù)題 號F1曳引鏈拉力F（N）7000曳引鏈速度v（m/s）0.2曳引鏈鏈輪齒數(shù)Z10曳引鏈節(jié)距P（mm）100工作班制三班1.1.3運輸機工作條件：1.1.4設計內容：1.1.5設計成果要求 自己根據(jù)任務書填寫1.2機構運動簡圖：電動機聯(lián)軸器蝸桿減速器鏈傳動鏈式運輸機第二章 運動學計算2.1傳動裝置的運動和動力參數(shù)計算：2.1.1選擇電動機的類型：按工作要求和條件選取Y系列三相籠型異步電動機，全封閉自扇冷式結構，電壓380V。2.1.2選擇電動機容量：工作機所需的功率： =7000*0.20/1000 kw =1.4 kWw從電動機到工作機輸送帶間的總效率為：=12334式中，分別是聯(lián)軸器、軸承、蝸桿傳動、滾子鏈（開式）的傳動效率。查機械手冊有=0.99，=0.98，=0.80，=0.90 所以=0.67。故所需電動機功率2.1.3確定電動機轉速：鏈輪的輸出轉速為。查表傳動比合理范圍，蝸桿傳動的傳動比，鏈傳動的傳動比，則總傳動比的合理范圍是。故電動機轉速的可選范圍是：。符合這一范圍的同步轉速有750 ，1000 ，1500 根據(jù)容量和轉速，由機械設計基礎課程設計(269)查出有三種適用的電動機型號，因此有三種傳動比方案，入下表1所示：表1方案電動機型號額定功率電動機轉速（r/min）電動機重量總傳動比同步轉速滿載轉速1Y100L-4315001420380109.232Y132S-63100096063073.853Y132M-8375071079054.62設計中常選用同步轉速為1000或1500r/min的電動機，如無特殊要求，一般不選用轉速為750的電動機，故初選轉速為1000r/min的電動機，則方案2比較合適，因此選定電動機信號為Y132S-6，其主要性能參數(shù)如下表2所示：表2型號額定功率/kW滿載情況/A /Nm/Nm轉速r/min電流/A效率/%功率因素Y132S-6310006.882.50.817.02.02.02.2 計算傳動裝置的總傳動比并分配傳動比：2.2.1 計算總傳動比因為選用的電動機型號是Y132S-6，滿載轉速為，故總傳動比是2.2.2 各傳動部件傳動比的分配查機械設計課程設計表2-3，知鏈傳動的傳動比是24，蝸桿減速器推薦的傳動比范圍是740，所以式中，分別是鏈傳動、減速器的傳動比。鏈傳動的傳動比由其齒數(shù)決定：根據(jù)機械設計（第八版）可知，為了減少動載荷，小鏈輪的齒數(shù)，故??；為了不發(fā)生脫鏈，不宜過大，又因為鏈節(jié)通常是偶數(shù)，則最好為奇數(shù)，由鏈輪齒數(shù)優(yōu)先序列選擇，所以 蝸桿減速器， 2.3計算傳動裝置各軸的運動和動力參數(shù)2.3.1各軸轉速：蝸桿軸 蝸輪軸 大輪軸 2.3.2 各軸輸入功率：蝸桿軸 蝸輪軸 大輪軸 2.3.3各軸轉矩：電動機輸出 蝸桿軸 蝸輪軸 大鏈輪軸 2.3.4 傳動裝置各軸的運動和動力參數(shù)軸名功率P/kw轉矩T/(Nm)轉速n/(r/min)傳動比效率電機軸2.0920.7996010.99蝸桿軸2.02820.1796035.090.77蝸輪1.59554.9927.362.280.97大鏈輪軸1.401144.2611.999第三章 傳動零件的設計計算3.1 鏈輪傳動的設計計算：3.1.1選擇鏈輪齒數(shù)： 前面已經選取了小鏈輪齒數(shù)，大鏈輪的齒數(shù)為。3.1.2確定當量的單排鏈的計算功率：P式中：工況系數(shù) 主動鏈輪齒數(shù)系數(shù) 多排鏈系數(shù)，雙排鏈時=1.75，三排鏈時=2.5 傳動的功率，查機械設計（第八版）表-得，1.1, =1.1, 單排鏈=1.0,所以3.1.3選擇鏈條型號和及其主要參數(shù)計算： 根據(jù)及主動鏈輪轉速，查機械設計手冊可選用48A1型號。該型號滾子鏈規(guī)格和主要參數(shù)如下表：ISO鏈號節(jié)距P滾子直徑d1 max內鏈節(jié)圓寬b1 min銷軸直徑d2 max排距Pt內鏈板高度h2 max抗拒載荷單排min雙排minmmKw20A31.7519.0518.99.5430.1835.7686.7173.53.1.4計算鏈節(jié)數(shù)和中心距初選中心距取。則相應的鏈節(jié)數(shù)為取鏈長節(jié)數(shù)節(jié)。鏈傳動的最大中心距為：式中：為中心距計算系數(shù)，由，查機械設計手冊（第八版）表9-7得。所以，鏈傳動的最大中心距為3.1.5計算鏈速v，確定潤滑方式：式中是小鏈輪的轉速，根據(jù)鏈速和鏈20A計手冊可知應采用油池潤滑或飛濺潤滑。3.1.6計算鏈傳動作用在軸上的壓軸力：式中：有效圓周力，N壓軸力系數(shù)，水平傳動=1.15，垂直傳動=1.05。有效圓周力為所以，壓軸力3.1.7滾子鏈鏈輪的設計：（1）鏈輪的基本參數(shù)及主要尺寸由于選用單排鏈結構，因此鏈輪的基本參數(shù)是配用鏈條的節(jié)距p，套筒的最大外徑d1、排距pt及齒數(shù)z，則，pt =35.76, 分度圓直徑齒頂圓直徑齒根圓直徑齒高 最大軸凸緣直徑 齒寬齒側倒角齒側半徑齒全寬（2）鏈輪的材料材料應能保證輪齒具有足夠的強度和耐磨性，用15號鋼，齒面多經滲碳、淬火、回火的熱處理。工作時，小鏈輪輪齒參與嚙合的次數(shù)比大鏈輪多，磨損、沖擊較嚴重，所以小鏈輪的材料選用20號鋼，進行正火熱處理，齒面硬度較高。3.3 蝸桿傳動的設計計算： 3.3.1選擇蝸桿傳動類型： 根據(jù)GB/T100851988的推薦，采用漸開線蝸桿（ZI）。3.3.2選擇材料：考慮到該蝸桿傳動功率不大，速度只是中等，故蝸桿用45鋼；因希望效率高些，耐磨性好些，故蝸桿螺旋齒面要求淬火，硬度為4555HRC。蝸輪用鑄錫磷青銅ZCuSn10P1，金屬模鑄造。為了節(jié)約貴重的有色金屬，僅齒圈用青銅制造，而輪芯用灰鑄鐵HT100制造。3.3.3按齒面接觸疲勞強度進行設計：根據(jù)閉式蝸桿傳動的設計準則，先按齒面接觸疲勞強度進行設計，再校核齒根彎曲疲勞強度。由公式有：傳動中心距 (1) 作用在蝸輪上的轉矩： (2) 確定載荷系數(shù)K：因工作載荷較穩(wěn)定，查機械設計（第八版）可取使用系數(shù)=1；齒向載荷分布系數(shù)=1；由于轉速不高，沖擊不大，可取動載系數(shù)=1.05；則(3) 確定彈性影響系數(shù)因選用的是鑄錫磷青銅蝸輪和鋼蝸桿相配，故=。(4) 確定接觸系數(shù)先假設蝸桿分度圓直徑和傳動中心距的比值，查圖11-18有=3.1。(5) 確定許用接觸應力根據(jù)蝸輪材料為鑄錫磷青銅ZCuSn10P1，金屬模鑄造，蝸桿螺旋齒面硬度大于45HRC，可查設計手冊得蝸輪的基本許用應力=268MPa。壽命 應力循環(huán)次數(shù) 壽命系數(shù) 則 (6) 計算中心距取中心距160mm，因為i=35.09，故從機械設計（第八版）表11-2中取模數(shù)m=8mm，蝸桿分度圓直徑。這時，查圖11-18的接觸系數(shù)=2.75，由于，故以上計算結果可用。3.3.4蝸桿與蝸輪的主要參數(shù)與幾何尺寸（） （1）蝸桿： 蝸桿頭數(shù)；軸向齒距；直徑系數(shù)q=10；齒頂圓直徑；齒根圓直徑；分度圓導程角；蝸桿軸向齒厚： （2）蝸輪：因為變位系數(shù)：，所以變位后渦輪齒數(shù)： ； 驗算傳動比： ，這時傳動比誤差： ，是允許的。 蝸輪分度圓直徑： 蝸輪喉圓直徑 ： 蝸輪齒根圓直徑：蝸輪咽喉母圓半徑：3.3.5校核齒根彎曲疲勞強度： 當量齒數(shù) 根據(jù)，查機械設計（第八版）圖11-19可得齒形系數(shù)。螺旋角系數(shù) 許用彎曲應力 查表得由ZCuSn10P1制造的蝸輪的基本許用彎曲應力。壽命系數(shù) 所以，彎曲強度是滿足的。3.3.6 驗算效率：嚙合效率： 已知；與相對滑動速度有關。查表11-18得、；代入式中得，所以上述計算不用重算。3.3.7校核蝸輪的齒面接觸強度：蝸輪圓周速度為對于青銅或鑄鐵蝸輪與鋼蝸桿配對時材料彈性系數(shù) Ze=160查機械設計（第八版）表11-5使用系數(shù)（間隙工作）；齒向載荷分布系數(shù)=1；動載系數(shù)，載荷系數(shù) =111=1（載荷平穩(wěn)）蝸輪實際轉矩：滑動速度影響系數(shù)，查表得 許用接觸應力=223.512MPa，校核蝸輪輪齒接觸疲勞強度 =223.512MPa 即齒面強度夠。3.3.8 熱平衡校核，初步估計散熱面積A估算箱體的散熱面積其中，P為蝸桿傳遞功率，為蝸桿傳遞效率，為箱體的表面?zhèn)鳠嵯禂?shù)，取15W/（mK） 為油的工作溫度，取65度， 為周圍空氣溫度，取20度。3.3.9 精度等級公差和表面粗糙度的確定：考慮到所設計的蝸桿傳動是動力傳動，屬于用機械減速器。從GB/T10089-1988圓柱蝸桿，蝸輪精度中選擇8級精度，側隙種類為f,標注為8f GB/T10089-1988。蝸桿與軸做成一體，即蝸桿軸。蝸輪采用輪箍式，與鑄造鐵心采用H7/S6配合，并加臺肩和螺釘固定（螺釘選用6個）。第四章 軸的設計計算及校核4.1 蝸輪軸的設計計算：4.1.1軸的材料的選擇，確定許用應力：考慮到減速器為普通中用途中小功率減速傳動裝置，軸主要傳遞蝸輪的轉矩。選用45號鋼， b=600MPa b-11=55MPa4.1.2 按扭轉強度，初步估計軸的最小直徑：選取軸的材料為45鋼，調質處理。根據(jù)設計設計（第八版）表15-3，取A=112，于是得： dminA=112=43.344mm因為最小直徑處安裝鏈輪，設有一個鍵槽，故直徑相應增大，取。4.1.3 軸承類型及其潤滑與密封方式： 采用球滾子軸承，并采用凸緣式軸承蓋，實現(xiàn)軸承兩端單向固定，軸伸處用A型普通平鍵聯(lián)接，實現(xiàn)周向固定，用A型普通平鍵聯(lián)接蝸輪與軸。4.1.4軸的結構設計:渦輪軸簡圖（1）各軸段直徑的確定1）因為最小直徑處安裝鏈輪，故；2）為了滿足軸向定位的要求，第一軸段右端需要露出一個軸肩，??；3）初選滾動軸承: 因軸承同時受有徑向力和軸向力的作用，且載荷不大，故選用圓錐滾子軸承。參考工作要求并根據(jù)，查機械設計手冊初選30212型圓錐滾子軸承，其尺寸為dDT=60mm110mm23.75mm ,故選=60mm， 4）安裝蝸輪軸處的直徑（安裝鍵槽），蝸輪軸右側的軸環(huán)進行軸向定位，取即蝸輪右側軸肩處的直徑為，蝸輪軸段的右端直徑右端為定位軸肩， 。（2）各軸段長度的確定查表根據(jù)第一軸段的直徑為確定軸伸長度，為保證軸的強度、剛度，由鏈輪的輪轂寬度，取；軸承端蓋的總寬度為62mm（由減速器及軸承的結構設計而定）。根據(jù)軸承端蓋的裝拆及便于對軸承添加潤滑脂的要求，取端蓋的外端面與鏈輪的輪轂右端面的距離，故取為；蝸輪輪轂的長度，故取輪轂的長度為，采用套筒定位，為了套筒端面可以可靠地壓緊蝸輪，此段應該略短于輪轂的長度，故取與蝸輪配合的軸段長度為；因為軸環(huán)的寬度，即,取，即;根據(jù)滾動軸承寬度油板以及箱座結構取綜上所述，可知：各軸段的直徑： 各軸段的長度： 軸的總長度為。（3）軸向零件的軸向定位蝸輪：蝸輪與軸的周向定位均采用平鍵聯(lián)接，按軸段由機械設計（第八版）表6-1查得鍵平面，鍵槽用鍵槽銑刀加工，鍵長為50m，同時為了保證蝸輪與軸配合有良好的對中性，選擇蝸輪輪轂與軸的配合為；軸承與軸的周向定位是由過渡配合來保證的，此處選軸的直徑尺寸公差為。（4）確定軸上的圓角和倒角尺寸參照機械設計（第八版）表15-2取倒角，各軸肩處的圓角半徑為。4.1.5軸、軸承、鍵的強度校核：（1）確定各向應力和反力：已知蝸輪的分度圓直徑，蝸桿的分度圓直徑，所以有：蝸輪的切向力為 蝸輪的徑向力為蝸輪的軸向力為（2）垂直平面的支撐反力：其中：214兩軸承中心的跨度，108蝸輪中心到右邊軸承中心的距離。（3）水平平面支撐反力：（4）確定彎矩：1）水平彎矩 2）垂直彎矩 3）合成彎矩 4）扭矩（5）按彎矩合成應力校核軸的強度 進行校核時，通常只校核軸上承受最大彎矩和扭矩的界面（即危險截面C）的強度。軸單向旋轉扭轉切應力為脈動循環(huán)變應力。取=0.6 軸端計算應力：故是安全的。（6）軸承的校核對于圓錐滾子軸承，按表13-7派生軸向力查得Y=1.5，e=0.4，所以有其中則1被壓緊，2被放松，即則因為P1P2，故按軸承的受力大小驗算，軸承的基本額定動載荷通過查表可得則軸承的壽命為（6）鍵的強度校核：按軸段由GB1095-2003，查得鍵平面，即鍵寬b=20mm；鍵高h=12mm，取標準鍵長50。l=L-b=50-30=20mm, k=0.5h=0.512=6mm 查得靜荷時的許用擠壓應力p=150，所以擠壓強度足夠。由普通平鍵標準查得軸槽深t=7.5mm，轂槽深=4.9mm。4.2 蝸桿軸的設計4.2.1軸的材料的選擇，確定許用應力：考慮到減速器為普通中用途中小功率減速傳動裝置，軸主要傳遞蝸桿的轉矩,但蝸桿為高速軸,故選材Q235鋼，淬火處理。=600MPa =55MPa4.2.2按扭轉強度，初步估計軸的最小直徑選取軸的材料為Q235鋼，淬火處理。根據(jù)設計手冊，取A=145，于是得： 聯(lián)軸器的計算轉矩，查表14-1，取=1.5，則按照計算轉矩應小于聯(lián)軸器公稱轉矩的條件，和軸的直徑查表GB/T 5014-2003 選用HL3彈性柱銷聯(lián)軸器，其公稱轉矩為，半聯(lián)軸器的孔徑d= 48mm，即軸向直徑取=48mm，半聯(lián)軸器長度L=112mm，半聯(lián)軸器與軸配合的轂孔長度為：=112mm。4.2.3軸承類型及其潤滑與密封方式：采用單列圓錐滾子軸承，并采用凸緣式軸承通蓋和嵌入式軸承蓋，實現(xiàn)軸承系兩端單向固定。4.2.4軸的結構設計蝸桿軸簡圖（1）從軸段=48mm開始逐漸選取軸段直徑，為了滿足半聯(lián)軸器的軸向定位要求，右端需制出一軸肩，故取=54mm；右端用軸端擋圈定位，按軸端直徑取擋圈直徑D=54mm。為了保證軸端擋圈只壓在半聯(lián)軸器上而不壓在軸的端面上，故的長度應比略短一些，現(xiàn)取=112mm。（2）初步選擇滾動軸承。選用單列圓錐滾子軸承。參照工作要求并根據(jù)=54mm,初步選取0基本游隙組、標準精度級的單列圓錐滾子軸承30212，其尺寸為，故=60mm；而。軸承采用軸肩進行軸向定位。由手冊查得30212型軸承的定位軸肩高度為h=4mm，因此，取72mm。軸環(huán)寬度,取=10mm。（3）5和7處有退刀槽,因，所以選。（4）取蝸桿齒頂圓直徑。（5）軸承端蓋總寬度取44mm，根據(jù)軸承端蓋的拆裝及便于對軸承添加潤滑油的要求，取其外端面與半聯(lián)軸器左端面間的距離l=71mm ，故。（6）和為退刀槽那段軸端長度，所以=38mm。（7）軸段的長度：查手冊，又因為所以取=150mm。（8）蝸桿總長 L=（112+115+56+10+38+150+38+10+56）mm=550mm其中軸徑 =48mm； =54mm； =60mm；=72mm； =60mm； =96mm； =60mm； =72mm； =60mm。長度 ； ； 。4.2.5蝸桿、軸承、鍵的強度校核（1）校核30212 查表GB/T297-1994 表12-4 額定動載荷Cr=1.03103 N； 基本靜載荷Cor=1.3103 N,e=0.4,Y=1.5,=0.8。（2）求兩軸承受到的徑向載荷和 由前面設計蝸輪時求得的：=240.916N；=-0.522N=381.396N；=279.204N（3）求兩軸承計算軸向力和 查表GB/T297-1994 12-4 可知，e=0.37 由公式求蝸桿受軸向力 (4)求當量動載荷和由表13-5 分別計算、，取=1.0,則=(X1+Y1)=1.0 （0.4451.114+1.6747.851）=1377 N=（1）=1.0279.204=279.204 N（5）驗算軸承壽命因為，所以按軸承的受力大小計算：所以軸承滿足壽命要求（c為基本額定動載荷，由設計手冊選擇）。（6）鍵的強度校核鍵選擇的是：bh=16mm10mm；L=100mml=L-b=100-16=84mm；k=0.5h=0.510=5mm因此，鍵的強度足夠。第五章 箱體的設計計算5.1 箱體的結構形式和材料采用上置式蝸桿減速器。鑄造箱體，材料HT150。因其屬于中型鑄件，鑄件最小壁厚810mm，取=11mm。5.2鑄鐵箱體主要結構尺寸和關系 名稱 減速器型式及尺寸關系（mm）箱座壁厚 =16箱蓋壁厚1 1=16箱座凸緣厚度b，箱蓋凸緣厚度b1，箱座底凸緣厚度b2 b=19 b1=19 b2=40地腳螺釘直徑及數(shù)目 df=17.76 n=4箱座、箱蓋上的肋厚m=14、=12軸承旁聯(lián)接螺栓直徑 d1=13.32箱蓋，箱座聯(lián)接螺栓直徑 d2=16 螺栓間距L=150軸承端蓋螺釘直徑 d3=12 螺釘數(shù)目6視孔蓋螺釘直徑 d4=12df，d1，d2至外壁距離 C1=26,22,16 d1，d2至凸緣邊緣距離C2=16,14軸承端蓋外徑（蝸輪軸）凸緣式：D2=190，嵌入式：D2=190(蝸桿軸)凸緣式：D2=184，嵌入式：D2=184軸承旁聯(lián)接螺栓距離 S=127軸承旁凸臺半徑 R1=18軸承旁凸臺高度h根據(jù)軸承座外徑和扳手空間的要求由結構確定蝸輪外圓與箱內壁間距離 =24蝸輪輪轂端面與箱內壁距離=16地腳螺栓通孔直徑=20地腳螺栓沉頭座直徑=90地腳螺栓底座凸緣尺寸C1=35,C2=30聯(lián)接螺栓直徑d=16聯(lián)接螺栓通孔直徑=17.5聯(lián)接螺栓沉頭座直徑D=33聯(lián)接螺栓底座凸緣尺寸C1=35，C2=30定位銷直徑d=14吊環(huán)螺釘直徑D5=箱體外壁至軸承座端面的距離L1=70軸承端蓋外徑(蝸輪軸)D2=190；(蝸桿軸)D2=183第六章 減速器結構與潤滑的概要說明在以上設計選擇的基礎上，對該減速器的結構，減速器箱體的結構，軸承端蓋的結構尺寸，減速器的潤滑與密封，減速器的附件作一簡要的闡述。6.1減速器的結構本課題所設計的減速器，其基本結構設計是在參照機械設計課程設計手冊圖19-24裝配圖的基礎上完成的，該項減速器主要由傳動零件（蝸輪蝸桿、圓柱齒輪），軸和軸承，聯(lián)結零件（鍵，銷，螺栓，螺母等）。箱體和附屬部件以及潤滑和密封裝置等組成。箱體為剖分式結構，由箱體和箱蓋組成，其剖分面通過蝸輪傳動的軸線；箱蓋和箱座用螺栓聯(lián)成一體；采用圓錐銷用于精確定位以確保和箱座在加工軸承孔和裝配時的相互位置；起蓋螺釘便于揭開箱蓋；箱蓋頂部開有窺視孔用于檢查齒輪嚙合情況及潤滑情況用于加住潤滑油，窺視孔平時被封??；通氣器用來及時排放因發(fā)熱膨脹的空氣，以放高氣壓沖破隙縫的密封而致使漏油；副標尺用于檢查箱內油面的高低；為了排除油液和清洗減速器內腔，在箱體底部設有放汕螺塞；吊耳用來提升箱體，而整臺減速氣的提升得使用與箱座鑄成一體的吊鉤；減速氣用地腳螺栓固定在機架或地基上。6.2箱體的結構該減速器箱體采用鑄造的剖分式結構形式具體結構詳見裝配圖6.3端蓋的結構尺寸詳見零件工作圖6.4減速器的潤滑與密封 動部分采用潤滑油，潤滑油的粘度為118cSt（100C）查表5-11機械設計基礎課程設計 分采用脂潤滑，潤滑脂的牌號為ZL-2查表5-13機械設計基礎課程設計6.5減速器附件簡要說明該減速器的附件含窺視孔蓋，排油孔與油蓋，通氣孔，油標，吊環(huán)螺釘，吊耳， 釘，刮油板，其結構及裝配詳見裝配圖。設計總結這一次的機械設計課程設計，比上學期做的機械原理的課程設計要難得多，工作量也不是簡單的幾個機構的設計所能比擬的， 這次課程設計讓我感觸最深的莫過于計算量的繁重了，前后5個星期我重做了3次，因為設計中的傳動比分配不合理重做了一遍，因為前面的計算錯誤重做了一遍，因為強度剛度等不足的問題又重做了一遍，所以浪費了很多時間和力氣在計算方面。 電動機的選擇這一部分的設計，相對來說比較好做，因為計算量還不算大，當?shù)搅撕竺娴膫鲃恿慵脑O計部分就頻頻出錯了，數(shù)據(jù)太多，而且容易計算錯誤，結果就導致了很多參數(shù)選擇不正確，到得后來的軸的設計校核就是更加地錯誤百出了，重新計算選擇的次數(shù)也增加了很多。 設計的過程是艱苦的，也是無比充實的，它讓我體會到一個真正的工程設計人員所要面對的情況，使我學到了一樣很重要的東西耐心。之前的我總是很浮躁，很難靜得下心來做一件事情的，這一次的設計過程真真正正地讓我安靜了下來，坐在圖書館里查閱資料，坐在電腦前計算編寫說明書和畫圖，面對著一錯再錯的計算數(shù)據(jù)而沒有選擇放棄，所以真的讓我覺得很充實了。 在對課程的掌握方面，我也學到了很多非常有用的東西，通過設計把機械設計及其他有關先修課程（如機械制圖、理論力學、材料力學、工程材料等）中所獲得的理論知識在設計實踐中加以綜合運用，使理論知識和生產實踐密切的結合起來，這個也算是對以往學過的知識的檢閱了。這次設計是我首次進行完整綜合的機械設計，它讓我樹立了正確的設計思想，培養(yǎng)了我對機械工程設計的獨立工作能力；讓我具有了初步的機構選型與組合和確定傳動方案的能力，也為我今后的設計工作打了良好的基礎。附錄：參考文獻 1 楊黎明，楊志勤機械設計簡明手冊北京：國防工業(yè)出版社2008.12 吳宗澤主編 機械設計課程設計手冊 第3版 北京：高等教育出版社1992（2007重?。? 席偉光 ，楊光 ，李波主編 機械設計課程設計 北京：高等教育出版社 2003（2004重?。? 哈爾濱工業(yè)大學理論力學教研室 理論力學 北京：高等教育出版社 2002.8 （2003重?。? 孫恒 ，陳作模主編 機械原理北京：高等教育出版社 2001（2003重?。? 吳宗澤主編 機械設計 北京：高等教育出版社 20017 張代東主編 機械工程材料應用基礎北京：機械工業(yè)出版社 2001.68 趙祥主編機械零件課程設計北京：中國鐵道出版社19889 王連明主編機械設計課程設計哈爾濱：哈爾濱工業(yè)大學出版社199627編號無錫太湖學院畢業(yè)設計（論文）相關資料題目： 工業(yè)機器人專用減速器的設計 信機 系 機械工程及自動化專業(yè)學 號： 0923229學生姓名： 賁素東 指導教師： 許菊若 （職稱：副教授 ） （職稱： ）2013年5月25日目 錄一、畢業(yè)設計（論文）開題報告二、畢業(yè)設計（論文）外文資料翻譯及原文三、學生“畢業(yè)論文（論文）計劃、進度、檢查及落實表”四、實習鑒定表無錫太湖學院畢業(yè)設計（論文）開題報告題目： 工業(yè)機器人專用減速器的設計 信機 系 機械工程及自動化 專業(yè)學 號： 0923229 學生姓名： 賁素東 指導教師： 許菊若 （職稱：副教授 ） （職稱： ）2012年11月25日 課題來源導師布置的任務科學依據(jù)（包括課題的科學意義；國內外研究概況、水平和發(fā)展趨勢；應用前景等）（1）課題科學意義減速器是各種機械設備中最常見的部件,它的作用是將電動機轉速減少或增加到機械設備所需要的轉速, 擺線針輪行星減速器由于具有減速比大、體積小、重量輕、效率高等優(yōu)點，在許多情況下可代替二級、三級的普通齒輪減速器和渦輪減速器，所以使用越來越普及，為世界各國所重視。擺線針輪行星減速器作為重要的機械傳動部件具有體積小、重量輕、傳動效率高的特點。本設計在全面考慮多齒嚙合、運轉平穩(wěn)、輪齒均載等運動學和動力學的要求，實現(xiàn)高承載能力、高傳遞效率、高可靠性和優(yōu)良動力學性能等指標，而且要便于制造、裝配和檢修，設計了該具有合理結構的擺線針輪行星減速器。（2）擺線針輪減速器的研究狀況及其發(fā)展前景 擺線針輪傳動較之普通漸開線齒輪或蝸輪傳動的優(yōu)點是：高傳動比和高效率；同軸輸出，結構體積小和重量輕；傳動平穩(wěn)和噪聲低。由于擺線針輪傳動同時嚙合的齒數(shù)要比漸開線外齒輪傳動同時嚙合的齒數(shù)多，因而承載能力較大，嚙合效率要高；還由于擺線輪和針輪的輪齒均可淬硬、精磨，較漸開線少齒差傳動中內齒輪的被加工性能要好，齒面硬度更高，因而使用壽命要長；加上擺線輪的加工技術已經過關，專業(yè)加工設備齊全，擺線輪已納入專業(yè)通用件，在國內已做到通用化批量生產，生產成本下降，因此擺線針輪傳動的減速器當前廣為應用。擺線針輪減速技術至今，雖在品種、規(guī)格等方面做了不少改進，但再沒有作本質、原理上的創(chuàng)新?，F(xiàn)今擺線針輪減速器，其原理和結構還是1926年德國的原型。研究內容 了解工業(yè)機器人的總體設計的相關內容； 熟悉擺線針輪行星減速器的各個部分； 熟練擺線針輪行星減速器的傳動比的計算； 掌握擺線輪行星曲線齒廓形成原理； 掌握對擺線輪、針輪及其他只要零件尺寸的計算及校核擬采取的研究方法、技術路線、實驗方案及可行性分析（1）技術路線：電動機的選擇及其基本參數(shù)計算；擺線輪材料的選擇；擺線輪、針輪、銷軸尺寸的計算；根據(jù)所得尺寸對零件進行校核。（2）研究方法研究方法：理論計算、校核、計算機繪圖；研究計劃及預期成果研究計劃：2012年11月12日-2012年12月2日：按照任務書要求查閱論文相關2012年12月3日-2013年1月20日：專業(yè)實訓。 2013年1月21日-2013年3月1日：按照要求修改畢業(yè)設計開題報告2013年3月1日-2013年3月8日：學習并翻譯一篇與畢業(yè)設計相關的英文資料2013年3月11日-2013年3月15日：分析資料，分析比較各種設計方案。2013年3月25日-2013年3月29日：總體設計。2013年4月8日-2013年4月12日：畢業(yè)論文撰寫和修改工作。2013年4月29日-2013年5月3日：整理說明書。2013年5月6日-2013年5月10日：完成設計說明書。預期成果：1.完成工業(yè)機器人專用減速器裝置二套（第二，三臂各一套），繪制擺線針輪減速器裝配圖（兩份）。2.完成部分零件圖設計，繪制零件圖4份。3.完成設計說明書一份。特色或創(chuàng)新之處 傳動比大，結構緊湊，傳動效率高，傳動穩(wěn)定，使用壽命長，與漸開線少齒差行星傳動相比無齒頂相碰和齒廓重疊現(xiàn)象。已具備的條件和尚需解決的問題 理論設計較為成熟，生產設備條件能夠得到滿足，材料的選擇能夠滿足要求。 制造成本高：擺線針輪行星減速器對材料的要求較高，因而增加了制造成本。 加工工藝復雜：加工擺線針輪需要專門的加床，對裝配工藝也有較嚴格的工藝要求。指導教師意見 指導教師簽名：年 月 日教研室（學科組、研究所）意見 教研室主任簽名： 年 月 日系意見 主管領導簽名： 年 月 日英文原文Mineral product monorail reduction gear synopsis、the main parts of the paper and the research on the noice reducerFirst:what is reducerReducer is a dynamic communication agencies, the use of gear speed converters, motor rotational speed reducer to the Rotary to be few, and have greater torque institutions. The reducer role 1) velocity at the same time increase the output torque, torque output ratio by motor output by slowdown, but the attention should be paid to exceed the rated torque reducer. 2) the speed at the same time reduce the inertia load, the inertia of deceleration than reduced to the square. We can look at the General Motors has a value of inertia. The type of reducer General helical gear reducer has reducer (including parallel shaft helical gear reducer, a worm reducer, bevel gear reducer, etc.), planetary gear reducer, Cycloid reducer, a worm reducer, a planetary friction CVT mechanical machines. Common reducer 1) worm reducer is the main characteristics of a reverse self-locking function, can be larger than a slowdown, input shaft and output shaft axis is not the same, nor in the same plane. But generally larger, transmission efficiency is not high, the accuracy is not high. 2) Harmonic Harmonic Drive reducer is controllable using flexible components to transfer elastic deformation and dynamic movement, not volume, high precision, but the disadvantage is that flexible wheel limited life, impatient shocks, rigidity and pieces of metal relatively poor. Not too high speed input. 3) planetary reducer its comparative advantage is compact structure, the return gap small, high precision, and have a long life span rated output torque can be done great. However, a price slightly expensive, the requirements of parts before assembly 1. Rolling cleaning with gasoline, kerosene other parts cleaning. All parts and Xiangbenna not allowed to have any impurities exist. Gear box and the inner wall (Worm), unprocessed surface has not been coated twice erosion-resistant oil paint, box has the outer surface coated primer and paint color (color requested by host). 2. Parts coated with a face wash after lubricants Second, the requirements of installation and adjustment 1. Rolling installation Rolling bearing inner ring should be installed at the shaft shoulder close to gap must not pass 0.05 mm thick Cypriot feet. 2. Bearing axial clearance of the clearance can not be adjusted bearings (such as deep groove ball bearings), axial clearance of 0.25 to 0.4 mm; the clearance adjustable bearing axial clearance numerical table. Click Tapered Roller Bearings axial clearance; angular contact ball bearing axial clearance 3. Gear (Worm) meshing tooth space available Cypriot side foot of lead or pressure. Will be lead wire on the alveolar, and then turning gear and squash lead wire, measuring two teeth side was crushed lead wire thickness and the size of which is adjacent teeth. 4. Tooth contact dot cylinder gear tooth contact Dot 2-10-4; bevel gear tooth contact Dot 2-11-4; Gearing contact Dot 2-12-4 Third, seal requirements 1. Box partition between the surface does not allow any pads filled, but can be coated or water glass sealant to ensure that the seal; 2. Assembly, the bolt tightening box, before using 0.05 mm Cypriot-foot inspection Covers Block with me and between the sealing surface; 3. Shaft seal should stretch to smear grease. The seal should be installed in strict accordance with the requirements Forth, lubrication requirements 1. Rationally determine the types of lubricants and greases and grades 2. Bearing lubrication fat, grease filled in the general Fatliquor space can be 1 / 2 to 2 / 3. 3. Lubricants should be regularly replaced, the new reducer used for the first time, the operation of oil-7 14 days, according to the situation can be after every 3 to 6 months for first oil. Fifth, the test requirements 1. Empty operation: at rated speed is, anti-running 1 to 2 hours; 2. Load test: at rated speed, rated load operation, the oil temperature balance to date. On the gear reducer, requested the pool temperature is not more than 35 oC, bearing temperature rise no more than 40 oC; the worm reducer, requested the pool temperature not more than 60 oC, bearing temperature of not more than 50 oC; 3. Entire testing process for the smooth operation, noise, not loosening the fixed link, sealed, not with the Sixth, packaging and transportation requirements 1. Protruding shaft and its annex should Oiler packaging; 2. Handling, lifting may not use screw rings and lug all of the above technical requirements are not necessarily listed, and sometimes also by other projects, mainly by the specific design requirements. Seventh. Technical requirements 1. Assembly, all parts cleaning with kerosene, gasoline Rolling cleansing, while the existence of any debris. Oil is not painted wall corrosion coatings twice; 2. Backlash with lead wire mesh test of not less than 0.16 mm, lead wire Backlash may not exceed the smallest of the four times; 3. Used Tu-color dot test. Tooth high point of contact by not less than 40% of contact spots on teeth not less than 50 per cent. Can be used when necessary, grinding or scraping after grinding to improve contacts; 4. Bearing axial clearance should be adjusted: 40 0.05 - 0.1 mm, 55 0.08 - 0.15 mm; 5. Test reducer subdivision surface, the contact surface and seal, oil spills are not allowed. Split-Tu allowed to paint or water glass seal and allow the use of any filler; 6. Engine lubricants to the contents N100 provisions height; Below I introduce our country reduction gear the development present situation First, the domestic reduction gear many by the gear drive, the worm drive primarily, but has the power and the load ratio generally is small, or velocity ratio great and mechanical efficiency excessively low question.Moreover, in the material quality and the technological level also has many weakness, the large-scale reduction gear question is specially more prominent, the service life is not long.The domestic use large-scale reduction gear (above 500kw), many from overseas (for example Denmark, Germany and so on) imports The 60s start few tooth reduction gears and so on difference transmission, cycloid pin gear transmission, overtone transmission which produces has the velocity ratio to be big, volume small, mechanical efficiency higher merit? .But its transmission theory limit, cannot transmit the oversized power, the power all must be smaller than generally 40kw. Because in the transmission theoretically, the technological level and the material quality aspect has not broken through, therefore, has not been able fundamentally to solve the transmission power in a big way, the velocity ratio big, the volume small, the weight light, mechanical efficiency higher these requests basically.The 90s initial period, the home appears three links (gear) the reduction gear, is one kind of outside stable motion gear drive reduction gear, it may realize the great velocity ratio, transmission load ability is also big. Its volume and the weight are all lighter than the dead axle speed reducer gear, the structure is simple, the efficiency is also high.Because this reduction gear three axle parallel structure, therefore caused the power/volume (or weight) the ratio is still small.Also its input axis and the output shaft on the identical spool thread, this do not have in the use many inconveniently. Not only Beijing Institute of Technology develops in successful stable motion speed reducer gear to have outside three link reduction gear merit, but also has the big power/weight (or volume) the ratio, as well as the input axis and the output shaft on identical spool thread merit, is at the domestic leading position.The home has the minority college and the factory and mining enterprise does the research work to in stable motion gear drive certain principles, has published some research paper, in has done some work using the cycloidal tooth crop rotation stable motion reduction gear. Second, the stable motion speed reducer gear principle of work synopsis, the stable motion speed reducer gear is refers to in a counter gear transmission, a gear in the stable motion generator actuation mean plane parallel motion, meshing through tooth profile between, actuates another tooth crop rotation dead axle to decelerate the rotation, the realization reduction gear function.The stable motion generator may use the parallelogram organization, either sine organization or cross slide organization.This achievement uses the parallelogram organization to take the stable motion generator. The stable motion generator may be the hypothesized use parallelogram organization, also may be the entity use parallelogram organization.Has the practical value stable motion gear mechanism for in counter gear organization, therefore may divide into the internal tooth crop rotation stable motion movement and the external tooth crop rotation stable motion movement two kind of situations.Outside the stable motion gear reduction organization, its internal tooth crop rotation stable motion movement, actuates the external gear and makes the deceleration rotation output.This organization also calls three links (gear) the reduction gear. As a result of the internal tooth crop rotation stable motion, two crank centers establish outside the annular gear tooth ring, therefore its size is not compact, cannot solve the volume major problem.? In stable motion gear reduction, its external tooth crop rotation stable motion movement, actuation internal tooth crop rotation deceleration rotation output.As a result of the external tooth crop rotation stable motion, two crank centers can establish in the external gear tooth ring, reduced the organization overall size greatly. Because in stable motion gear mechanism transmission efficiency high, volume small, input output coaxial line, therefore by widespread application prospect. Third, this project technical characteristic and key technologies? 1. this project technical characteristics, in this new stable motion speed reducer gear and domestic and foreign had the speed reducer gear compares, has the following characteristic: (1) velocity ratio scope is big, gets up from I=10, may reach most greatly several thousand.If manufactures the great velocity ratio the reduction gear, then demonstrates this reduction gear the merit.(2) transmission power scope is big: And may connect a body manufacture with the electric motor. (3) structure simple, the volume small, the weight is light.Reduces about 1/3 compared to the existing speed reducer gear.(4) mechanical efficiency is high.95 (5) this reduction gear input axis and the output shaft are on the identical spool thread.This reduction gear see Table 1 with other reduction gear performance comparison. Because lacks the data, various reduction gears power/load ratio which in the table arranges in order is most superior.? Table 1? Each kind of reduction gear comparison model power (kw) reduction gear ratio quality (kg) QI-450? 93 31.5 1820 ZSY-250? 95 31.5 540 NGW-92 88.1 31.5 577 SEW (Germany)? 90 28.61 1300 NP-100? 100 30 400 Note: NP-100 is in the stable motion speed reducer gear, the SEW reduction gear quality contains the electrical machinery.2. this project key technologies? May know by Figure 2, in “stable motion speed reducer gear is by annular gear Z2, external gear Z1 and the parallelogram organization combination becomes.Its transmission principle is: The electrical machinery input rotary motion, the external tooth crop rotation parallel migration, its center of circle path is a circle, makes the dead axle rotation with it meshing annular gear. Because external tooth crop rotation parallel migration, therefore name stable motion gear mechanism.The gear parallel migration needs to have the auxiliary body help realization, may use (612) to sell the axis, the roller takes the hypothesized auxiliary stable motion organization, also may use the eccentric shaft to take the entity auxiliary stable motion organization.In the stable motion speed reducer gear key technologies and the essential craft are the composition parallelogram component size computation and the request processing precision, the gear teeth main parameter choice. These factors will all affect the transmission ability and the transmission quality.Overall speaking, the group cost reduction gear various spare parts all request to have the high precision, they will be deciding the reduction gear overall transmis3. this project survey this project has obtained the Chinese practical new patent, the patent number: ZL95227767.0? .? This project trial produced the first prototype from 1995 (power 2.5kW, after velocity ratio I=32), with some factory and mine cooperation, has one after another designed following several kind of different powers, the different velocity ratio reduction gear.(1) electrically operated on rollers gate uses the reduction gear, power 550W, velocity ratio I=26, is united as one body with the electrical machinery.sion quality. (2) mixer uses the reduction gear, power 370W, velocity ratio I=17.(3) some military goods use two kind of reduction gears, one kind of power 370W, velocity ratio I=23.5; Another kind of power 370W, velocity ratio I=103 two level of transmission reduction gear.(4) steel mill large package rotary abutment reduction gear, power 7.5kw, velocity ratio I=64.(5) steel mill table reduction gear, power 7.5kw, transmission I=11. In this patent foundation, has developed one kind of new ultra-large reduction gear, the power may reach 1000kw, at present is developing subminiature (outlook size for a millimeter level) miniature reduction gear. Graduation design task First, a design Monorail Driver Design reducer Second, the design of the original data 1 Monorail drive reducer Power Rating: 7.5 KW; 2 Monorail reducer drive the total transmission ratio: 15 around; 3 Monorail reducer drive car driven by the side of the output shaft from the race distance of not more than 200 mm; 4 Monorail reducer drive the total length of less than 420 mm, the width is not more than 450 mm and the total height of not more than 690 mm; Third, the equipment and the working environment This can be used to mine underground, open-air, dust, humidity, air quality, bad comparison bad work environment, and the operational requirements of a safe space. Fourth, the design requirements To meet the application requirements under the premise that the minimum cost of manufacturing. From the following aspects considered; (L) to streamline the shape of each parts, machinery simple structure; (2) merge the functions of spare parts, reducing the types or quantities of spare parts; (3) Application of the new structure, new technology, new materials, product reliability; (4) decomposition components, its assembly, the assembly of the most simple structure; (5) similar to parts of the division; (6) standards for similar products by product serial number sequence analysis; (7) The realization of the common parts of the product and standardization. (8) assembly equipment design a map (0), the Six Parts (3), the design specification of a (not less than 30,000 words), and the design of technical and economic analysis.GEAR AND SHAFT INTRODUCTIONIn the force analysis of spur gears, the forces are assumed to act in a single plane. We shall study gears in which the forces have three dimensions. The reason for this, in the case of helical gears, is that the teeth are not parallel to the axis of rotation. And in the case of bevel gears, the rotational axes are not parallel to each other. There are also other reasons, as we shall learn.Helical gears are used to transmit motion between parallel shafts. The helix angle is the same on each gear, but one gear must have a right-hand helix and the other a left-hand helix. The shape of the tooth is an involute helicoid. If a piece of paper cut in the shape of a parallelogram is wrapped around a cylinder, the angular edge of the paper becomes a helix. If we unwind this paper, each point on the angular edge generates an involute curve. The surface obtained when every point on the edge generates an involute is called an involute helicoid.The initial contact of spur-gear teeth is a line extending all the way across the face of the tooth. The initial contact of helical gear teeth is a point, which changes into a line as the teeth come into more engagement. In spur gears the line of contact is parallel to the axis of the rotation; in helical gears, the line is diagonal across the face of the tooth. It is this gradual of the teeth and the smooth transfer of load from one tooth to another, which give helical gears the ability to transmit heavy loads at high speeds. Helical gears subject the shaft bearings to both radial and thrust loads. When the thrust loads become high or are objectionable for other reasons, it may be desirable to use double helical gears. A double helical gear (herringbone) is equivalent to two heli