塑料包裝機(jī)構(gòu)主傳動(dòng)機(jī)構(gòu)設(shè)計(jì)-二級(jí)展開(kāi)式圓柱圓錐齒輪減速器【說(shuō)明書(shū)+CAD】,說(shuō)明書(shū)+CAD,塑料包裝機(jī)構(gòu)主傳動(dòng)機(jī)構(gòu)設(shè)計(jì)-二級(jí)展開(kāi)式圓柱圓錐齒輪減速器【說(shuō)明書(shū)+CAD】,塑料包裝,機(jī)構(gòu),傳動(dòng),設(shè)計(jì),二級(jí),展開(kāi)式,圓柱,圓錐,齒輪,減速器,說(shuō)明書(shū),仿單,cad 1 塑料包裝機(jī)構(gòu)主傳動(dòng)機(jī)構(gòu)設(shè)計(jì) 二級(jí)展開(kāi)式圓柱圓錐齒輪減速器 任務(wù)說(shuō)明書(shū) 系 別： 機(jī)電工程系 專(zhuān) 業(yè)： 機(jī)械設(shè)計(jì)制造及其自動(dòng)化 姓 名： 荊偉澤 學(xué) 號(hào)： 2005090221 指導(dǎo)教師： 賈毅超 2 目 錄 一 設(shè)計(jì)題目 .3 1塑料包裝機(jī)的傳動(dòng)示意如圖所示。 .3 2已知條件 .3 3設(shè)計(jì)內(nèi)容 .3 二 傳動(dòng)裝置總體設(shè)計(jì) .4 三 電動(dòng)機(jī)的選擇 .4 四 運(yùn)動(dòng)和運(yùn)動(dòng)參數(shù)計(jì)算： .4 1分配傳動(dòng)比 .4 2計(jì)算傳動(dòng)裝置的運(yùn)動(dòng)和動(dòng)力參數(shù) .4 五 傳動(dòng)零件的設(shè)計(jì)計(jì)算 .6 1普通 V帶的設(shè)計(jì)計(jì)算 .6 2閉式直齒輪圓錐齒輪傳動(dòng)的設(shè)計(jì)計(jì)算 .8 3閉式直齒圓柱齒輪設(shè)計(jì)計(jì)算 .13 4.軸的設(shè)計(jì) .17 1）高速軸的設(shè)計(jì) .17 2） .中間軸的設(shè)計(jì) .20 3）低速軸的設(shè)計(jì) .24 六 軸承的校核 .27 1高速軸軸承的校核 .27 2.中速軸軸承校核 .28 3.高速軸軸承的校核 .30 七.減速器機(jī)體結(jié)構(gòu) .31 八鍵的設(shè)計(jì) .33 1.高速軸鍵的設(shè)計(jì)與校核 .33 2.中間軸鍵的設(shè)計(jì)與校核 .33 3.低速軸鍵的設(shè)計(jì)與校核 .34 九減速器的各部位附屬零件的設(shè)計(jì). .34 十防滑方式的確定 .35 1滾動(dòng)軸承的潤(rùn)滑 .35 2齒輪的潤(rùn)滑 .35 3 一 設(shè)計(jì)題目 1塑料包裝機(jī)的傳動(dòng)示意如圖所示。 2已知條件 1）凸輪的轉(zhuǎn)速 n/（r/min） 35 電動(dòng)機(jī)的功率/KW 0.25 2)工作情況：兩班制，連續(xù)單向運(yùn)轉(zhuǎn)，載荷有輕微沖擊，室內(nèi)工作。 3）使用期限：10 年； 4）生產(chǎn)條件：一般機(jī)械廠，單件生產(chǎn)； 5）動(dòng)力來(lái)源：電力，三項(xiàng)交流，電壓 380220V； 6）檢修間隔：三年一大修，二年一中修，半年一小修 3設(shè)計(jì)內(nèi)容 1）擬定工作機(jī)構(gòu)和傳動(dòng)方案 2) 工作機(jī)構(gòu)和運(yùn)動(dòng)學(xué)動(dòng)力學(xué)分析 3）設(shè)計(jì)繪制減速器裝配圖一張 4）設(shè)計(jì)繪制零件圖三張 5）編寫(xiě)設(shè)計(jì)計(jì)算說(shuō)明書(shū)一份 4 二 傳動(dòng)裝置總體設(shè)計(jì) 1) 組成：傳動(dòng)裝置由電機(jī)、減速器、工作機(jī)組成。 2）特點(diǎn)：齒輪相對(duì)于軸承不對(duì)稱(chēng)布置，因而沿齒向載荷分布不均勻，要求軸有較大的剛 度 3）傳動(dòng)系統(tǒng)的作用：介于機(jī)械中原動(dòng)機(jī)與工作機(jī)之間，主要將原動(dòng)機(jī)的運(yùn)動(dòng)和動(dòng)力傳給 工作機(jī)，在此起減速作用，并協(xié)調(diào)二者的轉(zhuǎn)速和轉(zhuǎn)矩。 三 電動(dòng)機(jī)的選擇 查手冊(cè) 選電動(dòng)機(jī)型號(hào) YS7114 功率 0.25kw 380V 轉(zhuǎn)速 1400r/min 四 運(yùn)動(dòng)和運(yùn)動(dòng)參數(shù)計(jì)算： 1分配傳動(dòng)比 分配傳動(dòng)比：查手冊(cè)第十三章，表 132知 V帶 i7,開(kāi)式圓柱齒輪 i8，圓錐齒 輪 i5；總傳動(dòng)比：i =40；取 （帶輪） 04i帶 ， （減速器）0/4/1i減 取 （錐齒輪） 12.5 （柱齒輪）2/i 2計(jì)算傳動(dòng)裝置的運(yùn)動(dòng)和動(dòng)力參數(shù) （1）0 軸電動(dòng)機(jī)的轉(zhuǎn)速 =350r/min140 nIinI =140r/min 352.Ii I =35r/min140 nIinI 5 （2）各軸的功率 傳動(dòng)總效率 帶的傳動(dòng)效率： 0.961 軸圓錐滾子軸承的效率： 82 圓錐齒輪嚙合的效率： .53 軸圓錐滾子軸承的效率： 094 齒輪嚙合的效率： .75 軸圓錐滾子軸承的效率： 6 聯(lián)軸器的傳動(dòng)效率： 0.97 總的傳動(dòng)效率 1234567總 .8326總 各軸的功率： 012.5096.8IPKW0.5PKWI 34I219 2567.7II .8I 各軸的轉(zhuǎn)矩： 60.3539.109.51PITIn6417.mTNI 6.296.5.4II 938.I 0.189.109.53PITIn542.TNI 6 五 傳動(dòng)零件的設(shè)計(jì)計(jì)算 1普通 V帶的設(shè)計(jì)計(jì)算 （1）確定 V帶的型號(hào)和帶輪的直徑 工況系數(shù) 由（設(shè)計(jì)說(shuō)明書(shū)）11.5 K1.2A 計(jì)算功率 選取帶型由0K1.25ACP03PWC （設(shè)計(jì)說(shuō)明書(shū)）11.15 Y 型 小帶輪的直徑 同理由表 11.6 取 125mD 大帶輪的直徑 取210i54D0 （2）計(jì)算帶長(zhǎng) 求 m2 62.5m 求 1052 37. 初取中心距 120a 帶長(zhǎng) 2LDam48L 基準(zhǔn)長(zhǎng)度 50m （3）求中心距和包角 中心距 12()84LaLDm 5062. 2(4506.)37.5 1am 小輪包角 2118aa 0542.801 7 （4）求帶根數(shù) 帶速 1.83m/s 160nvDv 傳動(dòng)比 i=4 帶的根數(shù) 由表 11.8 由表 11.7 .4P0.89K 由表 11.20 由表 11.10 1.0LK0.1PW Z= pck = =4.76 取 Z=5 根0.3.619. 張緊力 20 25CKPFqvVZ =500 +（0.04 ） .318.08921.835 （由表 11.4 q=0.04/m） .0FN 軸上載荷 2sin0FZQ 142.85.Si 26.3Q 帶輪的結(jié)構(gòu) 由 YS741電動(dòng)機(jī) 知軸的直徑 14dm 故小帶輪的孔徑 V帶的尺寸 頂寬 6b 節(jié)寬 5.3p 高 4hm 輪緣尺寸 =4.7mm =1.6mmminhfinh e=8mm f=7mm =5mmm 帶輪計(jì)算直徑 D 大帶輪 214D102D 8 帶輪的外徑 0D10251.6ha1028.Dm 2 23 帶輪的寬度 B()2(51)827zef46B6.3 2閉式直齒輪圓錐齒輪傳動(dòng)的設(shè)計(jì)計(jì)算 選材： 直齒錐齒輪的加工多為刨齒，不宜采用硬齒面，小齒輪用 45 鋼調(diào)質(zhì)處理， 硬度為 取平均硬度為 ，大齒輪選用 45 鋼正火處理，2175HB230HB 硬度為 ，取平均硬度為 。619 齒面接觸強(qiáng)度計(jì)算（由于小齒輪更容易失效故按小齒輪設(shè)計(jì)）： 齒數(shù) Z和精度等級(jí) 工業(yè)用齒應(yīng)大于等于 14 選取小齒輪齒數(shù) 16Z 則大齒輪的齒數(shù)為 初取 ，2.501iZ 16Z240Z 估計(jì) 左右 由表 12.9 選 8級(jí)精度/Vms 使用系數(shù) 由表 12.9 KA 1.25KA 動(dòng)載系數(shù) 由圖 12.9 0V 齒間載荷分配系數(shù) kh 估計(jì) 10/KFAtNmb = = =0.928cos2i.5 9 = = =0.371cos21i2.51 = = =17.24ZVcs1z60.98 = = =107.822o4.37 =1.661.8cos2z =0.88 4.63Z 由此得 =1.285120.8KHz 齒向載荷分布系數(shù) 查課本表 及注釋 =1.9 2KH 載荷系數(shù) KAV 1.25.3193.42 0.25669.0PTNmn6587TI 彈性系數(shù) 查課本表 ZE1189.ZMPa 節(jié)點(diǎn)區(qū)域系數(shù) 查課本圖 H262.5ZH 接觸最小安全系數(shù) 查課本表 limS1410limS 總工作時(shí)間 th83080th 應(yīng)力循環(huán)次數(shù) NL 96143.3011nt 10 993.01.321052NLi 接觸壽命系數(shù) 查課本圖 12-18 Z 12.NZ 接觸應(yīng)力 =638.1H 670lim1.5ZSH H =590.521li2.N2 小齒輪大端分度圓的直徑 1d 1d24.73205.3ZKTEHR = 2.61.89.50.3245.8 演算圓周速度及 KFAtb =（1-0.50.3）45.84=39mm10.54ddmR =0.714m/s3.950661 nmvs =329.1N 247.1TFNtdm =221cos dRb0.35421981.6m.539./0/846KFAtNmb 確定傳動(dòng)主要尺寸 11 大端模數(shù) m = = =2.865 取 m=31dZ45.86 實(shí)際大端分度圓的直徑 =48mm2.0mz1d =120mm 5d2 錐距 R = 21Z23640.Rm 齒寬 b 0.39.87b9b 按齒根彎曲疲勞強(qiáng)度計(jì)算 齒形系數(shù) 查課本圖 12-30 =2.66 =2.31YFa1YFa2YFa 應(yīng)力修正系數(shù) 查課本表 12-22 =1.64 =2.02 重合度系數(shù) =0.710.750.75.2.21 齒間載荷分布系數(shù) 查課本表 12-10KF = 1.440.71YKF 載荷系數(shù) KAVF 1.250.493.08 彎曲疲勞極限 查課本表 limF3()c6lim1MpaF =570Mpa2 彎曲最小安全系數(shù) 查課本表 12-14 =1.60liSliS 應(yīng)力循環(huán)次 NL601350841nth8.061NL 8.62.2Li 83.2 彎曲壽命系數(shù) 查課本圖 12-24 = =1.0Y 1Y 12 尺寸系數(shù) 查課本圖 12.25 =1.0YX XY 許用彎曲應(yīng)力 Flim1YFNS =420.160.MPa1FMPa li2 YXSF =396.75701.6a2a 驗(yàn)算 4.123051KTYSFZmiR .73861.607. 5 1542Mpa 1F = F2.310546Ys 16.pa2F 傳動(dòng)無(wú)嚴(yán)重過(guò)載，故不做靜強(qiáng)度校核 錐齒輪結(jié)構(gòu) 148dm210d11(0.5).48.mRm221arcos.9.21068arctn/arctn3/4.2.6hR 13 arctn/arctn3.6/42.ffhRm19.b 3閉式直齒圓柱齒輪設(shè)計(jì)計(jì)算 材料的選?。盒↓X輪用 鋼調(diào)質(zhì)處理，硬度 ，平均取為 。大452175HB230HB 齒輪用 鋼正火處理，硬度 ，平均取為 。619 齒面接觸疲勞計(jì)算： (1)初步計(jì)算： 軸的轉(zhuǎn)矩 1T 1438.TNm 查課本表 12-3，取齒寬系數(shù) d0d 接觸疲勞極限應(yīng)力 由課本圖 limH12.7()c67li1MpaH =620Mpa2 初步計(jì)算的許用接觸應(yīng)力 0.90.9681li1MPaH 6031paH 52m2 2M 由表 取Ad85Ad 初步計(jì)算小齒輪直徑 1 14938.12531 20Tid mH = 取.7135dm 齒寬 b1035d6b (2)校核計(jì)算： 圓周速度 v1.466nms0.24v 14 精度等級(jí) 查課本表 12-6 選 8級(jí)精度 齒數(shù) Z 初取 =181Z =722 模數(shù) = 由表 12.3 取1dmZ368m 使用系數(shù) 查課本表 =1.25KA129KA 動(dòng)載系數(shù) 查課本圖 =1.10VV 齒間載荷分布系數(shù) 查課本表 12-10，先求H 214938.29.46TFNtd829.4FNt 1.2589.4.36KAtNmb 8.m10 =1.65811.cos.83272z 4.3Z0.84Z 由此得 =1.28120.86KHzKH 齒向載荷分布系數(shù) HK 310.61bABCbd =1.33621.70.0KH 載荷系數(shù) K AV .51.836 2.35 15 彈性系數(shù) 查課本表 ZE12189.ZMPaE 節(jié)點(diǎn)區(qū)域系數(shù) 查課本圖 H62.5H 接觸最小安全系數(shù) 查課本表 limS40limS 接觸壽命系數(shù) 查課本圖 ZN1281.8ZN25 許用接觸應(yīng)力 H6701.25lim1ZSH7.9MpaH.li2N 38.1 驗(yàn)算 ： 21KTiZHEbd .35498.1189.250.8 a 7.6Mp H2 計(jì)算結(jié)果表明，觸疲勞強(qiáng)度較為合適，齒輪尺寸無(wú)需調(diào)整 (3)確定傳動(dòng)主要尺寸實(shí)際分度圓直徑 D 因模數(shù)取標(biāo)準(zhǔn)值時(shí)，齒數(shù)已重新確定，但并未圓整。 故分度圓直徑不會(huì)改變，即 實(shí)際分度圓直徑 218dmz361dm 742 中心距 a12()()za 9090a 齒寬 取b36dm14bm236 16 (4)齒根彎曲疲勞強(qiáng)度驗(yàn)算： 重合度系數(shù) Y0.750.75.2.2168Y0.72Y 齒間載荷分布系數(shù) 查課本表KF1 =1.4240.72YKF 齒向載荷分布系數(shù) 358(.4)bh 查課本圖 12-14 =1.24 載荷系數(shù) KKAVF 1.250.41.22.57K 齒形系數(shù) 查課本圖 YFa.Ya18Fa 應(yīng)力修正系數(shù) 查課本表 = 1.82S159s2S 彎曲疲勞極限 查課本表 lim123()c7limMp 50aF 彎曲最小安全系數(shù) 查課本表 liSF41.2liS 彎曲壽命系數(shù) 查課本圖 YN12.1YN 尺寸系數(shù) 由圖 X.5.0YX 許用彎曲應(yīng)力 Flim1FXS 580.12MPa51.2MpaFliYNSF 90.512a503.42pa 17 驗(yàn)算： 21KTYFaSbdm .5473.261.5908MPa 8.1Mpa 1F2YFS 1.2110 齒輪端面與內(nèi)機(jī) 壁距離 2 210 機(jī)蓋，機(jī)座肋厚 m,1 85.0,.1m8 軸承端蓋外徑 2D+（55.D2 5） 3d7077 82 八鍵的設(shè)計(jì) 1.高速軸鍵的設(shè)計(jì)與校核 根據(jù) 計(jì)手冊(cè)第四章，選用 圓128,1937.62dmTNm /1096GBT鍵 845 頭普通平 鍵（A 型），課本第七章表 7.1鑄鋼的許用擠壓應(yīng)力 2MPap149834.6210.07MPadlh 所以鍵的強(qiáng)度滿(mǎn)足。 所選鍵為 強(qiáng)度合格；bl 2.中間軸鍵的設(shè)計(jì)與校核 根據(jù) 查手冊(cè)第四章，選用 圓275,867.10dmTNm /1096GBT63鍵 2 頭普通平鍵（A 型），本表 7.1鑄鋼料的許用擠壓應(yīng)力 ；p 34 48657.106.532pTMPadlh 所選鍵的度滿(mǎn)足。 3.低速軸鍵的設(shè)計(jì)與校核 根據(jù) 查設(shè)手冊(cè)第四章，選用 鍵275,483.9dmTNm /1096GBT 圓頭普通平90214 鍵（A 型），查課本表 7.1鑄鋼料的許用擠壓應(yīng)力 2p53.210.9874MPadlh 所選鍵的強(qiáng)度滿(mǎn)足。 九減速器的各部位附屬零件的設(shè)計(jì). 1窺視孔蓋與窺視孔： 在減速器上部可以看到傳動(dòng)零件嚙合處要開(kāi)窺視孔, 大小只要夠手伸進(jìn)操作可。 以便檢查齒面接觸斑點(diǎn)和齒側(cè)間隙,了解嚙合情況.潤(rùn)滑油也由此注入機(jī)體內(nèi). 2放油螺塞 放油孔的位置設(shè)在油池最低處，并安排在不與其它部件靠近的一側(cè)，以便于放 油，放油孔用螺塞堵住并加封油圈以加強(qiáng)密封。 3油標(biāo) 油標(biāo)用來(lái)檢查油面高度，以保證有正常的油量.因此要安裝于便于觀察油面及油面穩(wěn)定之 處即低速級(jí)傳動(dòng)件附近；用帶有螺紋部分的油尺，油尺上的油面刻度線應(yīng)按傳動(dòng)件浸入深 度確定。 4通氣器 減速器運(yùn)轉(zhuǎn)時(shí)，由于摩擦發(fā)熱,機(jī)體內(nèi)溫度升高，氣壓增大，導(dǎo)致潤(rùn)滑油從縫隙向外 滲漏,所以在機(jī)蓋頂部或窺視孔上裝通氣器，使機(jī)體內(nèi)熱空氣自由逸處，保證機(jī)體內(nèi)外壓 力均衡，提高機(jī)體有縫隙處的密封性，通氣器用帶空螺釘制成. 5啟蓋螺釘 為了便于啟蓋，在機(jī)蓋側(cè)邊的邊緣上裝一至二個(gè)啟蓋螺釘。在啟蓋時(shí)，可先擰動(dòng)此螺釘頂 起機(jī)蓋；螺釘上的長(zhǎng)度要大于凸緣厚度，釘桿端部要做成圓柱形伙半圓形，以免頂壞螺紋； 螺釘直徑與凸緣連接螺栓相同。 在軸承端蓋上也可以安裝取蓋螺釘,便于拆卸端蓋.對(duì)于需作軸向調(diào)整的套環(huán),裝上二個(gè)螺 釘,便于調(diào)整. 6定位銷(xiāo) 為了保證剖分式機(jī)體的軸承座孔的加工及裝配精度，在機(jī)體聯(lián)接凸緣的長(zhǎng)度方向兩端各安 35 置一個(gè)圓錐定位銷(xiāo)。兩銷(xiāo)相距盡量遠(yuǎn)些，以提高定位精度。如機(jī)體是對(duì)稱(chēng)的,銷(xiāo)孔位置不 應(yīng)對(duì)稱(chēng)布置. 7環(huán)首螺釘、吊環(huán)和吊鉤 為了拆卸及搬運(yùn)，應(yīng)在機(jī)蓋上裝有環(huán)首螺釘或鑄出吊鉤、吊環(huán)，并在機(jī)座上鑄出吊鉤。 8調(diào)整墊片 用于調(diào)整軸承間隙,有的起到調(diào)整傳動(dòng)零件軸向位置的作用. 9密封裝置 在伸出軸與端蓋之間有間隙,必須安裝密封件,以防止漏油和污物進(jìn)入機(jī)體內(nèi). 十防滑方式的確定 1滾動(dòng)軸承的潤(rùn)滑 滾動(dòng)軸承的潤(rùn)滑采用脂潤(rùn)滑，它不易流失密封性好加脂周期長(zhǎng)。 該滾動(dòng)軸承的工作溫度不太高的可選鈣基潤(rùn)滑脂，滾動(dòng)軸承摩擦力大?？蛇x 1號(hào)潤(rùn)滑 脂 GB491-87 2齒輪的潤(rùn)滑 由于展開(kāi)式齒輪的傳動(dòng)速度比低，載荷大，油脂容易流失，所以采用粘度很高，防銹 性好的開(kāi)式齒輪油。采用油池潤(rùn)滑，自然冷卻，侵入油中的齒輪深度為 1-2個(gè)齒高， 采用液壓油 GB1118.1-1994. 附注： 參考數(shù)據(jù) 吳宗澤，羅圣國(guó)主編機(jī)械設(shè)計(jì)課程設(shè)計(jì)手冊(cè)。 邱宣懷主編機(jī)械設(shè)計(jì)。 編號(hào) 無(wú)錫太湖學(xué)院 畢業(yè)設(shè)計(jì)（論文） 相關(guān)資料 題目：?jiǎn)渭?jí)減速機(jī)箱體和箱蓋工藝工裝設(shè)計(jì) 機(jī)電 系 機(jī)械工程及自動(dòng)化專(zhuān)業(yè) 學(xué) 號(hào)： 　　　 0923199　　　　 學(xué)生姓名： 張亞?wèn)| 指導(dǎo)教師： 　 鮑虹蘇（職稱(chēng)：高工 ） （職稱(chēng)： ） 2013年5月25日 目 錄 一、畢業(yè)設(shè)計(jì)（論文）開(kāi)題報(bào)告 二、畢業(yè)設(shè)計(jì)（論文）外文資料翻譯及原文 三、學(xué)生“畢業(yè)論文（論文）計(jì)劃、進(jìn)度、檢查及落實(shí)表” 四、實(shí)習(xí)鑒定表 無(wú)錫太湖學(xué)院 畢業(yè)設(shè)計(jì)（論文） 開(kāi)題報(bào)告 題目：?jiǎn)渭?jí)減速機(jī)箱體和箱蓋工藝工裝設(shè)計(jì) 信機(jī) 系 機(jī)械工程及自動(dòng)化專(zhuān)業(yè) 學(xué) 號(hào)： 0923199 學(xué)生姓名： 張亞?wèn)| 指導(dǎo)教師： 鮑虹蘇 （ 職稱(chēng)：高工） （職稱(chēng)： ） 2012年11月24日 課題來(lái)源 機(jī)械制造業(yè)是一個(gè)國(guó)家最基礎(chǔ)的行業(yè)，也決定了一個(gè)國(guó)家制造業(yè)的整體水平現(xiàn)在中國(guó)已經(jīng)是一個(gè)制造大國(guó)，中國(guó)的制造業(yè)規(guī)模已經(jīng)達(dá)到世界第四位，僅次于美國(guó)、日本和德國(guó)。 研究?jī)?nèi)容 本設(shè)計(jì)是針對(duì)減速機(jī)箱體工藝的制作，主要研究的是減速機(jī)箱蓋的工藝過(guò)程、減速機(jī)的底座的工藝過(guò)程、減速機(jī)箱體合裝后的工藝過(guò)程以及對(duì)該技術(shù)的測(cè)試和其實(shí)用性的研究。并由此做出了對(duì)現(xiàn)行的減速機(jī)的箱體的改造和進(jìn)一步的完善。在這次的箱體工藝制造中，對(duì)一些主要程序比如說(shuō)結(jié)合面聯(lián)接孔、鉆頂面螺紋底孔、攻螺紋、鉆側(cè)面測(cè)油孔、放油孔、螺紋底孔、沉孔、攻螺紋 等的研究。 擬采取的研究方法、技術(shù)路線、實(shí)驗(yàn)方案及可行性分析 設(shè)計(jì)任務(wù) 1） 設(shè)計(jì)一個(gè)中等復(fù)雜的零件的加工工藝規(guī)程； 2） 設(shè)計(jì)一個(gè)專(zhuān)用夾具； 3） 編寫(xiě)設(shè)計(jì)說(shuō)明書(shū)。 根據(jù)設(shè)計(jì)任務(wù)做出減速機(jī)箱的基本設(shè)計(jì)任務(wù) 1）繪制零件工件圖一張； 2）繪制毛坯—零件合圖一張； 3）編制機(jī)械加工工藝規(guī)程卡片一套； 4）編寫(xiě)設(shè)計(jì)說(shuō)明書(shū)一份； 5）收集和研究原始資料，為夾具結(jié)構(gòu)設(shè)計(jì)做好技術(shù)準(zhǔn)備。 6）初步擬定夾具結(jié)構(gòu)方案，繪制夾具結(jié)構(gòu)草圖，進(jìn)行必要的理論計(jì)算和分析。 選擇最佳的夾具結(jié)構(gòu)方案，確定夾具精度和夾具總圖尺寸、公差配合與技術(shù)要求。 7） 繪制夾具總圖和主要非標(biāo)準(zhǔn)件零件圖，編寫(xiě)設(shè)計(jì)說(shuō)明書(shū)。 8）編制夾具特殊使用維護(hù)、操作、制造方面的說(shuō)明或技術(shù)要求。 研究計(jì)劃及預(yù)期成果 研究計(jì)劃： 2012年11月12日-2012年12月25日：按照任務(wù)書(shū)要求查閱論文相關(guān)參考資料，填寫(xiě)畢業(yè)設(shè)計(jì)開(kāi)題報(bào)告書(shū)。 2013年1月11日-2013年3月5日：填寫(xiě)畢業(yè)實(shí)習(xí)報(bào)告。 2013年3月8日-2013年3月14日：按照要求修改畢業(yè)設(shè)計(jì)開(kāi)題報(bào)告。 2013年3月15日-2013年3月21日：學(xué)習(xí)并翻譯一篇與畢業(yè)設(shè)計(jì)相關(guān)的英文材料。 2013年3月22日-2013年4月11日：設(shè)計(jì)減速機(jī)箱體和箱蓋的結(jié)構(gòu)并畫(huà)出相關(guān)草圖 2013年4月12日-2013年4月25日：完善設(shè)計(jì)所需的各種零件圖、夾具圖，并對(duì)設(shè)計(jì)的所有數(shù)據(jù)進(jìn)行整理，做好撰寫(xiě)畢業(yè)論文的準(zhǔn)備。 2013年4月26日-2013年5月20日：畢業(yè)論文撰寫(xiě)和修改工作。 預(yù)期成果： 機(jī)械制造技術(shù)設(shè)計(jì)是培養(yǎng)機(jī)械工程類(lèi)專(zhuān)業(yè)學(xué)生應(yīng)職應(yīng)崗能力的重要實(shí)踐性教學(xué)環(huán)節(jié)，它要求學(xué)生能全面綜合地運(yùn)用所學(xué)的理論和實(shí)踐知識(shí)，進(jìn)行零件機(jī)械加工工藝規(guī)程和工藝裝備的設(shè)計(jì)。其基本目的是： 1） 培養(yǎng)工程意識(shí)。 2） 訓(xùn)練基本技能。 3） 培養(yǎng)質(zhì)量意識(shí)。 4） 培養(yǎng)規(guī)范意識(shí)。 特色或創(chuàng)新之處 1、 設(shè)計(jì)了一副可以多方面加工的夾具，減少了原材料的應(yīng)用和所需的工時(shí)。 2、 設(shè)計(jì)了多種加工方案，并對(duì)其比較，選出最佳方案。 已具備的條件和尚需解決的問(wèn)題 1、一是對(duì)鏜床的不熟悉，二是在公差與配合方面的知識(shí)所學(xué)較少。 2、學(xué)院圖書(shū)館相關(guān)資料有限，并且很多資料不外借處學(xué)校，設(shè)計(jì)此項(xiàng)目任務(wù)重工作量大物力條件有限以及經(jīng)濟(jì)上的原因造成難以落實(shí)原材料加工出成品 3、經(jīng)過(guò)努力，設(shè)計(jì)達(dá)到了預(yù)想的成功，由于條件的限制沒(méi)能加工出成品，但對(duì)于我自己來(lái)說(shuō)已經(jīng)學(xué)到了不少東西。 指導(dǎo)教師意見(jiàn) 指導(dǎo)教師簽名： 2011年 11 月 20 日 教研室（學(xué)科組、研究所）意見(jiàn) 教研室主任簽名： 年 月 日 系意見(jiàn) 主管領(lǐng)導(dǎo)簽名： 年 月 日 英文原文 Mineral product monorail reduction gear synopsis First:what is reducer Reducer 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: φ40 0.05 - 0.1 mm, φ55 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 60's 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 90's 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 (6~12) 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. 中文譯文 一、 什么是減速器 減速器是一種動(dòng)力傳達(dá)機(jī)構(gòu)，利用齒輪的速度轉(zhuǎn)換器，將馬達(dá)的回轉(zhuǎn)數(shù)減速到所要的回轉(zhuǎn)數(shù)，并得到較大轉(zhuǎn)矩的機(jī)構(gòu)。 1、減速器的作用 1）降速同時(shí)提高輸出扭矩，扭矩輸出比例按電機(jī)輸出乘減速比，但要注意不能超出減速器額定扭矩。 2） 減速同時(shí)降低了負(fù)載的慣量，慣量的減少為減速比的平方。大家可以看一下一般電機(jī)都有一個(gè)慣量數(shù)值。 2、減速器的種類(lèi) 一般的減速器有斜齒輪減速器(包括平行軸斜齒輪減速器、蝸輪減速器、錐齒輪減速器等等)、行星齒輪減速器、擺線針輪減速器、蝸輪蝸桿減速器、行星摩擦式機(jī)械無(wú)級(jí)變速機(jī)等等。 3、常見(jiàn)減速器 1） 蝸輪蝸桿減速器的主要特點(diǎn)是具有反向自鎖功能，可以有較大的減速比，輸入軸和輸出軸不在同一軸線上，也不在同一平面上。但是一般體積較大，傳動(dòng)效率不高，精度不高。 2） 諧波減速器的諧波傳動(dòng)是利用柔性元件可控的彈性變形來(lái)傳遞運(yùn)動(dòng)和動(dòng)力的，體積不大、精度很高，但缺點(diǎn)是柔輪壽命有限、不耐沖擊，剛性與金屬件相比較差。輸入轉(zhuǎn)速不能太高。 3） 行星減速器其優(yōu)點(diǎn)是結(jié)構(gòu)比較緊湊，回程間隙小、精度較高，使用壽命很長(zhǎng)，額定輸出扭矩可以做的很大。但價(jià)格略貴一、對(duì)裝配前零件的要求 ： 1.滾動(dòng)軸承用汽油清洗，其他零件用煤油清洗。所有零件和箱體內(nèi)不許有任何雜質(zhì)存在　。箱體內(nèi)壁和齒輪（蝸輪）等未加工表面先后涂?jī)纱尾槐粰C(jī)油侵蝕的耐油漆，箱體外表　面先后涂底漆和顏色油漆（按主機(jī)要求配色）。 2.零件配合面洗凈后涂以潤(rùn)滑油 二、安裝和調(diào)整的要求　 1.滾動(dòng)軸承的安裝　　滾動(dòng)軸承安裝時(shí)軸承內(nèi)圈應(yīng)緊貼軸肩，要求縫隙不得通過(guò)0.05mm 厚的塞尺。 2.軸承軸向游隙　　對(duì)游隙不可調(diào)整的軸承（如深溝球軸承），其軸向游隙為0.25~0.4mm；對(duì)游隙可調(diào)整　　的軸承軸向游隙數(shù)值見(jiàn)表。點(diǎn)擊查看圓錐滾子軸承軸向游隙；角接觸球軸承軸向游隙　 3.齒輪（蝸輪）嚙合的齒側(cè)間隙　　可用塞尺或壓鉛法。即將鉛絲放在齒槽上，然后轉(zhuǎn)動(dòng)齒輪而壓扁鉛絲，測(cè)量?jī)升X側(cè)被　　壓扁鉛絲厚度之和即為齒側(cè)的大小?！? 4.齒面接觸斑點(diǎn)圓柱齒輪齒面接觸斑點(diǎn)2-10-4；圓錐齒輪齒面接觸斑點(diǎn)2-11-4；蝸桿傳動(dòng)接觸斑點(diǎn)2-12-4 三、密封要求　 1.箱體剖分面之間不允許填任何墊片，但可以涂密封膠或水玻璃以保證密封；　 2.裝配時(shí)，在擰緊箱體螺栓前，應(yīng)使用0.05mm的塞尺檢查箱蓋和箱座結(jié)合面之間的密封性；　 3.軸伸密封處應(yīng)涂以潤(rùn)滑脂。各密封裝置應(yīng)嚴(yán)格按要求安裝 四、潤(rùn)滑要求　 1.合理確定潤(rùn)滑油和潤(rùn)滑脂類(lèi)型和牌號(hào)　 2.軸承脂潤(rùn)滑時(shí)，潤(rùn)滑脂的填充量一般為可加脂空間的1/2~2/3?！? 3.潤(rùn)滑油應(yīng)定期更換，新減速器第一次使用時(shí)，運(yùn)轉(zhuǎn)7~14天后換油，以后可以根據(jù)情況每隔3~6個(gè)月?lián)Q一次油。 五、試驗(yàn)要求　 1.空載運(yùn)轉(zhuǎn)：在額定轉(zhuǎn)速下正、反運(yùn)轉(zhuǎn)1~2小時(shí)；　 2.負(fù)荷試驗(yàn)：在額定轉(zhuǎn)速、額定負(fù)荷下運(yùn)轉(zhuǎn)，至油溫平衡為止?！　?duì)齒輪減速器，要求油池溫升不超過(guò)35oC,軸承溫升不超過(guò)40oC；　　對(duì)蝸桿減速器，要求油池溫升不超過(guò)60oC,軸承溫升不超過(guò)50oC；　 3.全部試驗(yàn)過(guò)程中，要求運(yùn)轉(zhuǎn)平穩(wěn)，噪聲小，聯(lián)接固定處不松動(dòng)，各密封、結(jié)合處不 六、包裝和運(yùn)輸要求　 1.外伸軸及其附件應(yīng)涂油包裝；　 2.搬運(yùn)、起吊時(shí)不得使用吊環(huán)螺釘及吊耳以上技術(shù)要求不一定全部列出，有時(shí)還需另增項(xiàng)目，主要由設(shè)計(jì)的具體要求而定。 七、技術(shù)要求　 1.裝配前，所有零件用煤油清洗，滾動(dòng)軸承用汽油清洗，不許有任何　　雜物存在。內(nèi)壁涂上不被機(jī)油腐蝕的涂料兩次；　 2.嚙合側(cè)隙用鉛絲檢驗(yàn)不小于0.16mm，鉛絲不得大于最小側(cè)隙的4倍；　 3.用涂色法檢驗(yàn)斑點(diǎn)。按齒高接觸點(diǎn)不小于40%；按齒長(zhǎng)接觸斑點(diǎn)不　　小于50%。必要時(shí)可用研磨或刮后研磨以便改善接觸情況；　 4.應(yīng)調(diào)整軸承軸向間隙：φ40為0.05--0.1mm,φ55為0.08--0.15mm;　 5.檢驗(yàn)減速器剖分面、各接觸面及密封處，均不許漏油。剖分面允許　　涂以密封油漆或水玻璃，不允許使用任何填料；　 6.機(jī)座內(nèi)裝N100潤(rùn)滑油至規(guī)定高度。 八、下面我介紹我國(guó)減速器的發(fā)展現(xiàn)狀 （一）、國(guó)內(nèi)的減速器多以齒輪傳動(dòng)、蝸桿傳動(dòng)為主，但普遍存在著功率與重量比小，或者傳動(dòng)比大而機(jī)械效率過(guò)低的問(wèn)題。另外，材料品質(zhì)和工藝水平上還有許多弱點(diǎn)，特別是大型的減速器問(wèn)題更突出，使用壽命不長(zhǎng)。國(guó)內(nèi)使用的大型減速器（500kw以上），多從國(guó)外（如丹麥、德國(guó)等）進(jìn)口。60年代開(kāi)始生產(chǎn)的少齒差傳動(dòng)、擺線針輪傳動(dòng)、諧波傳動(dòng)等減速器具有傳動(dòng)比大，體積小、機(jī)械效率高等優(yōu)點(diǎn)?。但受其傳動(dòng)的理論的限制，不能傳遞過(guò)大的功率，功率一般都要小于40kw。由于在傳動(dòng)的理論上、工藝水平和材料品質(zhì)方面沒(méi)有突破，因此，沒(méi)能從根本上解決傳遞功率大、傳動(dòng)比大、體積小、重量輕、機(jī)械效率高等這些基本要求