機(jī)械設(shè)計(jì)課程設(shè)計(jì)2

1、目錄1. 前言·················································

2、;····················12. 設(shè)計(jì)任務(wù)書····························&#

3、183;··································13. 傳動(dòng)方案的分析和擬定（富傳動(dòng)方案簡圖）···········

4、83;························14. 電動(dòng)機(jī)的選擇························

5、;·····································14.1電動(dòng)機(jī)功率計(jì)算···········

6、···············································24.2電動(dòng)機(jī)轉(zhuǎn)矩計(jì)算·&

7、#183;·················································&

8、#183;······24.3總傳動(dòng)比計(jì)算和分配各級傳動(dòng)比········································&

9、#183;···25. 傳動(dòng)裝置運(yùn)動(dòng)和動(dòng)力參數(shù)計(jì)算···········································&#

10、183;···35.1各軸轉(zhuǎn)速的計(jì)算············································

11、83;··············35.2各軸功率的計(jì)算·································

12、3;·························35.3各軸扭矩的計(jì)算·······················

13、;····································36. 傳動(dòng)零件的設(shè)計(jì)計(jì)算···········

14、3;············································46.1高速級齒輪傳動(dòng)的設(shè)計(jì)計(jì)算···

15、··············································46.2低速級齒輪傳動(dòng)的設(shè)計(jì)計(jì)算·&#

16、183;················································77. 軸的設(shè)計(jì)

17、計(jì)算·················································

18、3;···········87.1高速軸最小軸徑計(jì)算····································

19、83;··················87.2低速軸的設(shè)計(jì)計(jì)算·····························

20、83;·························9 7.2.1低速軸的結(jié)構(gòu)設(shè)計(jì)······················

21、·······························97.2.2低速軸彎扭組合強(qiáng)度校核················&

22、#183;······························107.2.3低速軸疲勞強(qiáng)度安全系數(shù)校核················

23、;····························107.3中間軸的設(shè)計(jì)計(jì)算···················

24、3;····································108. 滾動(dòng)軸承的選擇和計(jì)算···········&

25、#183;·········································108.1高速軸和中間軸上滾動(dòng)軸承的選擇·····

26、;·····································108.2低速軸上滾動(dòng)軸承的選擇和計(jì)算·········

27、3;··································109. 聯(lián)軸器的選擇··············

28、;···············································119.1輸入軸聯(lián)軸器的選擇

29、83;·················································

30、83;····119.2輸出軸聯(lián)軸器的選擇···········································&

31、#183;···········1110. 鍵連接的選擇和計(jì)算···································

32、3;···················1110.1高速軸和中間軸上鍵聯(lián)接的選擇···························&#

33、183;················1110.2低速軸上鍵聯(lián)接的選擇和計(jì)算······························&

34、#183;···············1211. 潤滑方式、潤滑劑牌號及密封裝置的選擇······························&

35、#183;·······1211.1潤滑方式········································

36、83;·······················1211.2潤滑油牌號························

37、3;·····································1211.3密封裝置···········

38、··················································

39、···1212. 其他技術(shù)說明（如對裝配、拆卸安裝和維護(hù)的注意事項(xiàng)及需要采取的重要措施等）···1213. 結(jié)束語···································

40、83;·······························12參考資料（“資料編號，作者。書名。出版社單位所在城市：名出版單位，出版年月”）附圖一：二級直齒圓柱齒輪減速器總裝配圖附圖二：減速器低速軸零件圖附圖三：減速器低速級大齒輪零件圖一、前言機(jī)械設(shè)計(jì)基礎(chǔ)這門課是機(jī)械類專業(yè)很重要

41、的一門基礎(chǔ)課程，我們平時(shí)上課是按部就班地按照學(xué)，學(xué)的比較散，沒有真正地聯(lián)系貫通也沒有實(shí)際用過，而課程設(shè)計(jì)將我們學(xué)的知識整個(gè)聯(lián)系起來，讓我們用自身學(xué)到的知識去處理實(shí)際問題，也真正貫徹我校 “學(xué)以致用” 的校訓(xùn)二、設(shè)計(jì)任務(wù)書（附紙）三傳動(dòng)方案的分析和擬定 1. 組成：傳動(dòng)裝置由電動(dòng)機(jī)、減速器、工作機(jī)組成。2. 特點(diǎn)：齒輪相對于軸承不對稱分布，故沿軸向載荷分布不均勻，要求軸有較大的剛度。方案圖如下：改sbsnvepaccbhyujvicoq四電動(dòng)機(jī)的選擇4.1電動(dòng)機(jī)功率Ped的選擇電動(dòng)機(jī)功率Ped，設(shè)：工作機(jī)（卷筒）所需功率PW，卷筒效率W，電機(jī)至卷筒軸的傳動(dòng)總效率a（減速器效率）電機(jī)需要的功率Pd

42、 計(jì)算如下：=0.99 查手冊取，對于Ped=4kW的電動(dòng)機(jī)型號有四種：型號Y112M-2Y112M-4Y132M1-6Y160M1-8同步轉(zhuǎn)速3000 r/min1500 r/min1000 r/min750 r/min滿載轉(zhuǎn)速2890 r/min1440 r/min960 r/min720 r/min改4.2電動(dòng)機(jī)轉(zhuǎn)速的選擇已知卷筒轉(zhuǎn)速為60r/min，二級減速器的總傳動(dòng)比合理范圍是ia=825。所以：電動(dòng)機(jī)轉(zhuǎn)速為nd=ia·n=4801500 r/min，該范圍內(nèi)的轉(zhuǎn)速有 750 r/min, 1000 r/min, 1500 r/min。方案電動(dòng)機(jī)額定功率Ped（kW）電動(dòng)機(jī)

43、轉(zhuǎn)速r/min電動(dòng)機(jī)重量（kg）參考價(jià)格減速器傳動(dòng)比ia型號同步轉(zhuǎn)速滿載轉(zhuǎn)速 1Y112M-441500144043242Y132M1-64100096073163Y160M1-8475072011812通過比較和計(jì)算，知道如果選用方案1，則在后面分配傳動(dòng)比時(shí)將出現(xiàn)i1=5.58,不符合教材P249頁直齒傳動(dòng)比要求（i<3,最大可達(dá)5）。2號方案相對而言，其重量輕，價(jià)格便宜，傳動(dòng)比適中，故選2號方案。4.3總傳動(dòng)比計(jì)算和分配各級傳動(dòng)比由上表讀出Ia=16，按浸油潤滑條件考慮，取高速級傳動(dòng)比i1=1.3·i2則 ia=1.3 i2·i2=1.3·i22所以i2

44、=3.51，i1 =ia/i2=4.56.改五、傳動(dòng)裝置運(yùn)動(dòng)和動(dòng)力參數(shù)計(jì)算5.1各軸轉(zhuǎn)速的計(jì)算n1=nd=960 r/minn2= n1/ i1 =960/4.56=210.53 r/minn3= n2/ i2= 210.53/3.51=59.98 r/min5.2各軸功率的計(jì)算電動(dòng)機(jī)：Pd=3.77kW高速軸3.77×0.99=3.73中間軸低速軸5.2各軸扭矩的計(jì)算將各軸的運(yùn)動(dòng)和動(dòng)力參數(shù)列于下表上：電動(dòng)機(jī)軸軸軸軸滾筒軸轉(zhuǎn)速n/(r/min)960960210.53 59.98 59.98 功率P/(kW)3.773.73 3.58 3.44 3.37 扭矩T/(N·m)

45、37.50 37.13 162.58 548.02 537.11 傳動(dòng)比i14.563.511改六.傳動(dòng)零件設(shè)計(jì)計(jì)算6.1高速級齒輪的傳動(dòng)設(shè)計(jì)計(jì)算1.選擇齒輪材料級精度等級按教材表11.8選擇齒輪的材料為：小齒輪選用45鋼調(diào)質(zhì)，硬度為220250HBS；大齒輪選用45鋼正火，硬度為170210HBS。因?yàn)槭瞧胀p速器，由教材表11.20選8級精度，要求齒面粗糙度Ra3.26.3um。2.確定設(shè)計(jì)準(zhǔn)則由于該減速器為閉式齒輪傳動(dòng)，而且兩齒輪均為齒面硬度HBS小于等于350的軟齒面，齒面點(diǎn)蝕是主要的失效形式。應(yīng)現(xiàn)按齒面接觸疲勞強(qiáng)度進(jìn)行設(shè)計(jì)計(jì)算，確定齒輪的主要參數(shù)和尺寸，然后再按彎曲強(qiáng)度校核齒根的彎曲

46、強(qiáng)度。3.按齒面接觸疲勞強(qiáng)度設(shè)計(jì)因兩齒輪均為鋼質(zhì)齒輪，可應(yīng)用教材P228頁（11.23）求出d1值。確定有關(guān)參數(shù)與系數(shù)：（1）轉(zhuǎn)矩T1由上表可以讀出T1 =37.13N·m=37130 N·mm(2) 載荷系數(shù)K直齒，圓周速度高，精度相對較低，齒寬系數(shù)大，齒輪在兩軸承間非對稱布置時(shí)取大值。由教材P226頁表11.10查出K=1.2（3）齒數(shù)z1和齒寬系數(shù)根據(jù)教材P249，在閉式軟齒面齒輪傳動(dòng)中，齒輪的承受能力主要決定于齒面接觸疲勞強(qiáng)度，齒輪的彎曲強(qiáng)度總是足夠的，因此齒數(shù)可多些，推薦z1=2440小齒輪的齒數(shù)z1取為24。此處小齒輪的齒數(shù)z1取24，則大齒輪的齒數(shù)z2= i1

47、·z1=4.56×24=109.44，因z1和z2最好互質(zhì)，所以z2取109。實(shí)際齒數(shù)比為齒數(shù)傳動(dòng)比誤差因二級直齒圓柱齒輪為不對稱布置，而齒輪表面又軟齒面由教材P250頁表11.19選取=11.2。（4）許用接觸應(yīng)力由教材圖11.23查得，由教材P224頁表11.9查得取=1。=60×960×1×（15×250×10）=2.16×根據(jù)教材P222頁，圖11.26讀出接觸疲勞系數(shù)ZN1=1, ZN2=1根據(jù)教材P222頁式（11.15）計(jì)算齒面接觸疲勞許用應(yīng)力故=42.56則根據(jù)教材P201頁表11.3取模數(shù)標(biāo)準(zhǔn)值m

48、1=2mm4.主要尺寸計(jì)算由此處取b2=50mmb1= b2+（510）取b1為55mm5.按齒根彎曲疲勞強(qiáng)度校核根據(jù)教材P230頁，若能得出,則校核合格。確定有關(guān)系數(shù)與參數(shù)：（1）齒形系數(shù)根據(jù)教材P229頁，表11.12得出（2）應(yīng)力修正系數(shù)YS根據(jù)教材P230頁,表11.13得出(3)許用彎曲應(yīng)力根據(jù)教材224頁，圖11.24查得由教材P224頁，表11.9查得SF=1.3;教材P225頁圖11.25查得根據(jù)教材P222頁式（11.16）可得由教材230頁式（11.25）可得齒根彎曲強(qiáng)度較和合格。6.驗(yàn)算齒輪得圓周速度由表11.21可知，選8級精度是合適的。7.幾何尺寸計(jì)算小齒輪：da1=

49、d1+2ha=48+2×1×2=52mm，直徑較小做成齒輪軸。df1=d1-2hf=48-2×（1+0.25）=43mm大齒輪：da2=d2+2ha=218+2×1×2=222mm，由于200mm<da2<500mm,所以采用腹板式結(jié)構(gòu)。df2=d2-2hf=218-5=213mm整理求得的參數(shù)a12=133 m12=2 z1=24 b1=55 d1=48 da1=52 df1=43z2=109 b2=50 d2=218 da2= 222 df2=2136.2低速級齒輪的傳動(dòng)設(shè)計(jì)計(jì)算1.疲勞強(qiáng)度設(shè)計(jì)（1）齒數(shù)z3和齒寬系數(shù)齒數(shù)z3取

50、為29。則大齒輪的齒數(shù)z2= i1·z1=3.51×29=101.79，因z3和z4最好互質(zhì)，所以z4取102。實(shí)際齒數(shù)比為齒數(shù)傳動(dòng)比誤差因二級直齒圓柱齒輪為不對稱布置，而齒輪表面又軟齒面由教材P250頁表11.19選取=11.2。（2）許用接觸應(yīng)力由教材圖11.23查得，由教材P224頁表11.9查得取=1。=60×210.53×1×（15×250×10）=4.74×根據(jù)教材P222頁，圖11.26讀出接觸疲勞系數(shù)ZN3=1.07, ZN4=1.12根據(jù)教材P222頁式（11.15）計(jì)算齒面接觸疲勞許用應(yīng)力=68

51、.215則根據(jù)教材P201頁表11.3取模數(shù)標(biāo)準(zhǔn)值m34=2.5mm2.主要尺寸計(jì)算由此處取b2=75mmb3= b4+（510）取b1為80mm整理求得的參數(shù):a34=163.75 m34=2.5 z3=29 b3=80 d3=72.5 da3=77.5 df3=66.25z4=102 b4=75 d4=255 da4=260 df4= 248.75由于200mm<da4<500mm,所以采用腹板式結(jié)構(gòu)。七軸的設(shè)計(jì)計(jì)算7.1高速軸最小軸徑計(jì)算（1）選擇軸的材料，確定需用應(yīng)力由前部分計(jì)算得知，減速器傳遞的功率屬于中小功率，對材料無特殊要求，故選用45鋼并經(jīng)調(diào)質(zhì)處理。（1） 按扭轉(zhuǎn)強(qiáng)

52、度估算軸徑（最小直徑）根據(jù)教材P341頁表16.2得C=118107。又由式（16.2）得mm考慮到軸的最小直徑處要安裝聯(lián)軸器，會(huì)有鍵槽存在，故需將估算直徑加大3%5%，取為17.319.5，再根據(jù)聯(lián)軸器軸徑要求，由設(shè)計(jì)手冊取標(biāo)準(zhǔn)直徑d1min=20mm。7.2低速軸的設(shè)計(jì)計(jì)算最小軸徑計(jì)算mm考慮到軸的最小直徑處要安裝聯(lián)軸器，會(huì)有鍵槽存在，故需將估算直徑加大3%5%，取為42.547.8，再根據(jù)聯(lián)軸器軸徑要求，再初算轉(zhuǎn)矩要求，直徑需要取大一點(diǎn)，則由設(shè)計(jì)手冊取標(biāo)準(zhǔn)直徑d1min=50mm7.2.1低速軸的結(jié)構(gòu)設(shè)計(jì)軸的結(jié)構(gòu)如圖所示。(1)各軸段直徑的確定d31：最小直徑，和聯(lián)軸器相連d31=d1m

53、in=50mmd32：密封處軸段，d32= d31 +2a，a為軸肩高度，通常a（0.070.1）d，得d32在60左右，此處取d32=59mm,以便于下一步軸承的選取。d33：d33= d32+15 mm，此處安裝軸承，由設(shè)計(jì)手則選取d33=60 mmd34：此段起過渡作用d34= d33+15 mm,此處取65mmd35：d35 =d34+15 mm應(yīng)與齒輪相配取d35=70mmd36：此處安裝軸承，所以d36=d33=60 mm(2)各軸段長度確定l 31：由Y聯(lián)軸器長度可以選得l 31 =110mml32：由箱體結(jié)構(gòu)、軸承端蓋、裝配關(guān)系等確定l32=30mml33：由滾動(dòng)軸承、擋油盤及

54、裝配關(guān)系等確定l33=50mml34：由裝配關(guān)系，箱體結(jié)構(gòu)等確定l34=50mml35：由齒輪位置關(guān)系等確定l35=12mml36：由齒輪寬度確定l36=73mml37：由箱體結(jié)構(gòu)、裝配關(guān)系滾動(dòng)軸承、擋油盤等關(guān)系確定l37=50mm7.2.2低速軸彎扭組合強(qiáng)度校核作用在齒輪上的圓周力： 徑向力： 則求垂直面的支反力：NN計(jì)算垂直彎矩：N·M N·M求水平面的支承力計(jì)算、繪制水平面彎矩圖： N·MN·M求合成彎矩圖： N·M求危險(xiǎn)截面當(dāng)量彎矩：由圖可知，C-C處截面最危險(xiǎn)，因減速器單項(xiàng)運(yùn)轉(zhuǎn)，故可以認(rèn)為轉(zhuǎn)矩為脈動(dòng)循環(huán)變化，修正系數(shù)為0.6。其當(dāng)量彎

55、矩為： N·M計(jì)算危險(xiǎn)截面處的直徑：軸的材料為45鋼調(diào)質(zhì)處理，根據(jù)教材P342頁表16.3查得Mpa，許用彎曲應(yīng)力，則考慮到鍵槽的影響，取d=1.0537.5=39.4mm則可以得出，所以軸是安全的。7.2.3低速軸的疲勞強(qiáng)度安全系數(shù)校核（略）7.3中間軸的設(shè)計(jì)計(jì)算最小軸徑計(jì)算最小軸徑處安裝滾動(dòng)軸承，根據(jù)設(shè)計(jì)手則滾動(dòng)軸承的標(biāo)準(zhǔn)可以得出d21=30mm，其他各段尺寸根據(jù)兩齒輪寬度及箱體尺寸和安裝要求可分別得出d22=48mm，d23=10mm，d24=77mm，d25=45mm八、滾動(dòng)軸承的選擇和計(jì)算8.1高速軸和中間軸上滾動(dòng)軸承的選擇因?yàn)樵O(shè)計(jì)的齒輪都是直齒，所以軸向不受力，再結(jié)合速度

56、情況，選用深溝球軸承。高速軸安裝軸承的軸段直徑為25mm，由設(shè)計(jì)手則查得應(yīng)選用深溝球軸承6205 GB/T276-94，中間軸安裝軸承的軸段直徑為30mm，由設(shè)計(jì)手則查得應(yīng)選用深溝球軸承6206 GB/T276-94。8.2低速軸上滾動(dòng)軸承的選擇和計(jì)算選擇：高速軸安裝軸承的軸段直徑為60mm，由設(shè)計(jì)手則查得應(yīng)選用深溝球軸承6212 GB/T276-94校核：因?yàn)樗訬此處軸承只由教材P381頁，表17.11查得應(yīng)選1.1。受軸向載荷驗(yàn)算軸承壽命：h所選軸承具有足夠的壽命。九、聯(lián)軸器的選擇9.1輸入軸聯(lián)軸器的選擇(1)選擇類型電動(dòng)機(jī)與減速器高速軸聯(lián)結(jié)用的聯(lián)軸器，一般選用彈性可移式聯(lián)軸器，所以此處與高速軸聯(lián)接的聯(lián)軸器選彈性柱銷聯(lián)軸器。（2）求計(jì)算轉(zhuǎn)矩前面已經(jīng)求出電動(dòng)機(jī)的扭矩Td=37.5 N·M，由教材P435表19.1查得，工作情況系數(shù)KA =1.25,故計(jì)算轉(zhuǎn)矩TC =KATd=37.5×1.25=46.875 NN&#