減速器-圓錐圓柱二級齒輪減速器設(shè)計【F=2710N V=1.8ms D=250mm】
減速器-圓錐圓柱二級齒輪減速器設(shè)計【F=2710N V=1.8ms D=250mm】,F=2710N V=1.8ms D=250mm,減速器-圓錐圓柱二級齒輪減速器設(shè)計【F=2710N,V=1.8ms,D=250mm】,減速器,圓錐,圓柱,二級,齒輪,設(shè)計,ms,mm,妹妹
機械設(shè)計基礎(chǔ)課程設(shè)計圓錐圓柱二級齒輪減速器【F=2710N V=1.8 D=250】計算說明書指導(dǎo)教師院 系班 級學(xué) 號姓 名目 錄設(shè)計任務(wù)書3傳動方案的擬訂及說明3電動機的選擇3計算傳動裝置的運動和動力參數(shù)5齒輪傳動件的設(shè)計計算7軸的設(shè)計計算.16滾動軸承的選擇及計算.38鍵聯(lián)接的選擇及校核計算.42聯(lián)軸器的選擇.43減速器附件的選擇.44潤滑與密封.44設(shè)計小結(jié).46參考資料.47設(shè)計計算及說明結(jié)果一、 設(shè)計任務(wù)書設(shè)計一用于帶式運輸機上的圓錐圓柱齒輪減速器,已知帶式運輸機輸送帶工作拉力F=2710N,帶速v=1.8m/s,卷筒直徑D=250mm,輸送機常溫下經(jīng)常滿載,空載起動,連續(xù)單向運轉(zhuǎn),載荷較平穩(wěn)。工作壽命10年(設(shè)每年工作300天),一班制。簡圖如下:(圖2)由圖可知,該設(shè)備原動機為電動機,傳動裝置為減速器,減速器為兩級展開式圓錐圓柱齒輪減速器二、傳動方案的擬訂及說明計算驅(qū)動卷筒的轉(zhuǎn)速選用同步轉(zhuǎn)速為1000r/min或1500r/min的電動機作為原動機,因此傳動裝置總傳動比約為13。根據(jù)總傳動比數(shù)值,可擬定以下傳動方案:圖一三、 選擇電動機1)電動機類型和結(jié)構(gòu)型式按工作要求和工作條件,選用一般用途的Y(IP44)系列三相異步電動機。它為臥式封閉結(jié)構(gòu)。設(shè)計計算及說明結(jié)果2)電動機容量(1)卷筒的輸出功率(2)電動機輸出功率傳動裝置的總效率查表2-1,取一對軸承效率軸承=0.99,錐齒輪傳動效率錐齒輪=0.96,斜齒圓柱齒輪傳動效率齒輪=0.97,聯(lián)軸器效率聯(lián)=0.99,得電動機到工作機間的總效率為故 (3)電動機額定功率由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表20-1選取電動機額定功率。3)電動機的轉(zhuǎn)速推算電動機轉(zhuǎn)速可選范圍,由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表2-1查得單級圓柱齒輪傳動比范圍,圓錐齒輪傳動比范圍,則電動機轉(zhuǎn)速可選范圍為:設(shè)計計算及說明結(jié)果初選同步轉(zhuǎn)速分別為1000r/min和1500r/min的兩種電動機進行比較,如下表:方案電動機型號額定功率()電動機轉(zhuǎn)速(r/min)電動機質(zhì)量(kg)總傳動比同步滿載1Y132M2-65.510009601196.982Y132S-45.5150014406810.47兩方案均可行,選定方案二 ,結(jié)構(gòu)尺寸相對較大,能適合卷筒相對重載的工況,選定電動機的型號為Y132S-44)電動機的技術(shù)數(shù)據(jù)和外形,安裝尺寸由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表20-1、表20-2查得主要數(shù)據(jù),并記錄備用。四、計算傳動裝置的運動和動力參數(shù)1)傳動裝置總傳動比2)分配各級傳動比因為是圓錐圓柱齒輪減速器,所以那么 設(shè)計計算及說明結(jié)果3)各軸轉(zhuǎn)速(軸號見圖一)4)各軸輸入功率按電動機所需功率計算各軸輸入功率,即5)各軸轉(zhuǎn)矩項目軸1軸2軸3軸4軸5轉(zhuǎn)速(r/min)14401440516.13137.63137.63功率(kw)5.55.395.174.974.91轉(zhuǎn)矩(N*m)36.4835.7595.66344.86340.70傳動比112.793.751設(shè)計計算及說明結(jié)果五、傳動件的設(shè)計計算圓錐直齒輪設(shè)計已知輸入功率,小齒輪轉(zhuǎn)速1440r/min,齒數(shù)比u=2.79,由電動機驅(qū)動,工作壽命10年(設(shè)每年工作300天),一班制,輸送機工作經(jīng)常滿載,空載起動,工作平穩(wěn)。1、 選定齒輪精度等級、材料及齒數(shù)1) 圓錐圓柱齒輪減速器為通用減速器,速度不高,故選用7級精度(GB10095-88)2) 材料選擇 由機械設(shè)計(第八版)表10-1選擇小齒輪材料為(調(diào)質(zhì)),硬度為280HBS,大齒輪材料為45鋼(調(diào)質(zhì)),硬度為240HBS。3) 選小齒輪齒數(shù),大齒輪齒數(shù),取整。則2、 按齒面接觸強度設(shè)計由設(shè)計計算公式進行試算,即(1) 確定公式內(nèi)的各計算數(shù)值1) 試選載荷系數(shù)2) 計算小齒輪的轉(zhuǎn)矩3) 選齒寬系數(shù)設(shè)計計算及說明結(jié)果4)由機械設(shè)計(第八版)圖10-21d按齒面硬度查得小齒輪的接觸疲勞強度極限,大齒輪的接觸疲勞強度極限5)由機械設(shè)計(第八版)表10-6查得材料的彈性影響系數(shù)6) 計算應(yīng)力循環(huán)次數(shù)7) 由機械設(shè)計(第八版)圖10-19取接觸疲勞壽命系數(shù)8) 計算接觸疲勞許用應(yīng)力取失效概率為1%,安全系數(shù)S=1,得(2) 計算1) 試算小齒輪分度圓直徑,代入中較小的值2) 計算圓周速度v設(shè)計計算及說明結(jié)果3) 計算載荷系數(shù)根據(jù),7級精度,由機械設(shè)計(第八版)圖10-8查得動載系數(shù)直齒輪由機械設(shè)計(第八版)表10-2查得使用系數(shù)根據(jù)大齒輪兩端支撐,小齒輪作懸臂布置,查機械設(shè)計(第八版)表得軸承系數(shù),則接觸強度載荷系數(shù)4) 按實際的載荷系數(shù)校正所算得的分度圓直徑,得5) 計算模數(shù)m取標(biāo)準(zhǔn)值6) 計算齒輪相關(guān)參數(shù)7) 圓整并確定齒寬圓整取,設(shè)計計算及說明結(jié)果3、 校核齒根彎曲疲勞強度1) 確定彎曲強度載荷系數(shù)2) 計算當(dāng)量齒數(shù)3) 由機械設(shè)計(第八版)表10-5查得齒形系數(shù)應(yīng)力校正系數(shù)4) 由機械設(shè)計(第八版)圖20-20c查得小齒輪的彎曲疲勞強度極限,大齒輪的彎曲疲勞強度極限5) 由機械設(shè)計(第八版)圖10-18取彎曲疲勞壽命系數(shù)6) 計算彎曲疲勞許用應(yīng)力取彎曲疲勞安全系數(shù),得7)校核彎曲強度設(shè)計計算及說明結(jié)果根據(jù)彎曲強度條件公式進行校核滿足彎曲強度,所選參數(shù)合適。圓柱斜齒輪設(shè)計已知輸入功率,小齒輪轉(zhuǎn)速516.13r/min,齒數(shù)比u=3.75,由電動機驅(qū)動,工作壽命10年(設(shè)每年工作300天),一班制,帶式輸送機工作經(jīng)常滿載,空載起動,工作平穩(wěn)。1、 選定齒輪精度等級、材料及齒數(shù)1) 圓錐圓柱齒輪減速器為通用減速器,速度不高,故選用7級精度(GB10095-88)2) 材料選擇 由機械設(shè)計(第八版)表10-1選擇大小齒輪材料均為45鋼(調(diào)質(zhì)),小齒輪齒面硬度為250HBS,大齒輪齒面硬度為220HBS。3) 選小齒輪齒數(shù),大齒輪齒數(shù)取4) 選取螺旋角。初選螺旋角 2、按齒面接觸強度設(shè)計,設(shè)計計算及說明結(jié)果由設(shè)計計算公式進行試算,即(1) 確定公式內(nèi)的各計算數(shù)值1) 試選載荷系數(shù)2) 計算小齒輪的轉(zhuǎn)矩3) 選齒寬系數(shù)4) 由機械設(shè)計(第八版)圖10-30選取區(qū)域系數(shù)5) 由機械設(shè)計(第八版)圖10-26查得,則6) 由機械設(shè)計(第八版)表10-6查得材料的彈性影響系數(shù)7) 計算應(yīng)力循環(huán)次數(shù)8) 由機械設(shè)計(第八版)圖10-21d按齒面硬度查得小齒輪的接觸疲勞強度極限,大齒輪的接觸疲勞強度極限9) 由機械設(shè)計(第八版)圖10-19取接觸疲勞壽命系數(shù)設(shè)計計算及說明結(jié)果10)計算接觸疲勞許用應(yīng)力取失效概率為1%,安全系數(shù)S=1,得(2)計算1)試算小齒輪分度圓直徑,由計算公式得2) 計算圓周速度v3) 計算齒寬b及模數(shù)4) 計算縱向重合度5)計算載荷系數(shù)設(shè)計計算及說明結(jié)果根據(jù),7級精度,由機械設(shè)計(第八版)圖10-8查得動載系數(shù)由機械設(shè)計(第八版)表10-3查得由機械設(shè)計(第八版)表10-2查得使用系數(shù)由機械設(shè)計(第八版)表10-13查得 由機械設(shè)計(第八版)表10-4查得接觸強度載荷系數(shù)6)按實際的載荷系數(shù)校正所算得的分度圓直徑,得7) 計算模數(shù)取8) 幾何尺寸計算(1) 計算中心距取得(2) 按圓整后的中心距修正螺旋角因值改變不多,故參數(shù)、等不必修正(3)計算大小齒輪的分度圓直徑設(shè)計計算及說明結(jié)果(4)計算齒輪寬度圓整后取 3、 校核齒根彎曲疲勞強度1) 確定彎曲強度載荷系數(shù)2) 根據(jù)重合度,由機械設(shè)計(第八版)圖10-28查得螺旋角影響系數(shù)3) 計算當(dāng)量齒數(shù)4)由機械設(shè)計(第八版)表10-5查得齒形系數(shù)應(yīng)力校正系數(shù)5) 由機械設(shè)計(第八版)圖20-20c查得小齒輪的彎曲疲勞強度極限,大齒輪的彎曲疲勞強度極限6)由機械設(shè)計(第八版)圖10-18取彎曲疲勞壽命系數(shù) 設(shè)計計算及說明結(jié)果7) 計算彎曲疲勞許用應(yīng)力取彎曲疲勞安全系數(shù),得8) 校核彎曲強度根據(jù)彎曲強度條件公式進行校核滿足彎曲強度,所選參數(shù)合適。六、軸的設(shè)計計算輸入軸設(shè)計1、求輸入軸上的功率、轉(zhuǎn)速和轉(zhuǎn)矩 2、求作用在齒輪上的力已知高速級小圓錐齒輪的分度圓半徑為設(shè)計計算及說明結(jié)果而圓周力、徑向力及軸向力的方向如圖二所示圖二設(shè)計計算及說明結(jié)果3、 初步確定軸的最小直徑先初步估算軸的最小直徑。選取軸的材料為45鋼(調(diào)質(zhì)),根據(jù)機械設(shè)計(第八版)表15-3,取,得,輸入軸的最小直徑為安裝聯(lián)軸器的直徑,為了使所選的軸直徑與聯(lián)軸器的孔徑相適應(yīng),故需同時選取聯(lián)軸器型號。聯(lián)軸器的計算轉(zhuǎn)矩,查機械設(shè)計(第八版)表14-1,由于轉(zhuǎn)矩變化很小,故取,則查機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表17-4,選HL1型彈性柱銷聯(lián)軸器,其公稱轉(zhuǎn)矩為160000,半聯(lián)軸器的孔徑,故取,半聯(lián)軸器長度,半聯(lián)軸器與軸配合的轂孔長度為38mm。4、 軸的結(jié)構(gòu)設(shè)計(1) 擬定軸上零件的裝配方案(見圖三)圖三設(shè)計計算及說明結(jié)果(2) 根據(jù)軸向定位的要求確定軸的各段直徑和長度1) 為了滿足半聯(lián)軸器的軸向定位,1-2軸段右端需制出一軸肩,故取2-3段的直徑2) 初步選擇滾動軸承。因軸承同時受有徑向力和軸向力,故選用單列圓錐滾子軸承,參照工作要求并根據(jù),由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表15-7中初步選取0基本游隙組,標(biāo)準(zhǔn)精度級的單列圓錐滾子軸承30306,其尺寸為,而。這對軸承均采用軸肩進行軸向定位,由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表15-7查得30306型軸承的定位軸肩高度,因此取3)取安裝齒輪處的軸段6-7的直徑;為使套筒可靠地壓緊軸承, 5-6段應(yīng)略短于軸承寬度,故取。4)軸承端蓋的總寬度為20mm。根據(jù)軸承端蓋的裝拆及便于對軸承添加潤滑油 的要求,求得端蓋外端面與半聯(lián)軸器右端面間的距離,故取 5)錐齒輪輪轂寬度為64.86mm,為使套筒端面可靠地壓緊齒輪取。6) 由于,故?。?) 軸上的周向定位圓錐齒輪的周向定位采用平鍵連接,按由機械設(shè)計(第八版)表6-1查得平鍵截面,鍵槽用鍵槽銑刀加工,長為50mm,同時為保設(shè)計計算及說明結(jié)果證齒輪與軸配合有良好的對中性,故選擇齒輪輪轂與軸的配合為;滾動軸承與軸的周向定位是由過渡配合來保證的,此處選軸的尺寸公差為k6。(4) 確定軸上圓角和倒角尺寸取軸端倒角為5、 求軸上的載荷載荷水平面H垂直面V支反力F彎矩M 總彎矩扭矩T6、按彎扭合成應(yīng)力校核軸的強度根據(jù)上表中的數(shù)據(jù)及軸的單向旋轉(zhuǎn),扭轉(zhuǎn)切應(yīng)力為脈動循環(huán)變應(yīng)力,取,軸的計算應(yīng)力前已選定軸的材料為45鋼(調(diào)質(zhì)),由機械設(shè)計(第八版)表15-1查得,故安全。6、 精確校核軸的疲勞強度(1) 判斷危險截面截面5右側(cè)受應(yīng)力最大(2)截面5右側(cè)設(shè)計計算及說明結(jié)果抗彎截面系數(shù)抗扭截面系數(shù)截面5右側(cè)彎矩M為截面5上的扭矩為截面上的彎曲應(yīng)力截面上的扭轉(zhuǎn)切應(yīng)力軸的材料為45鋼,調(diào)質(zhì)處理。由表15-1查得。截面上由于軸肩而形成的理論應(yīng)力集中系數(shù)及按機械設(shè)計(第八版)附表3-2查取。因,經(jīng)插值后查得又由機械設(shè)計(第八版)附圖3-2可得軸的材料敏感系數(shù)為故有效應(yīng)力集中系數(shù)為設(shè)計計算及說明結(jié)果由機械設(shè)計(第八版)附圖3-2的尺寸系數(shù),扭轉(zhuǎn)尺寸系數(shù)。軸按磨削加工,由機械設(shè)計(第八版)附圖3-4得表面質(zhì)量系數(shù)為軸未經(jīng)表面強化處理,即,則綜合系數(shù)為又取碳鋼的特性系數(shù)計算安全系數(shù)值故可知安全。中間軸設(shè)計1、求中間軸上的功率、轉(zhuǎn)速和轉(zhuǎn)矩 設(shè)計計算及說明結(jié)果2、求作用在齒輪上的力已知圓柱斜齒輪的分度圓半徑而已知圓錐直齒輪的平均分度圓半徑而圓周力、,徑向力、及軸向力、的方向如圖四所示設(shè)計計算及說明結(jié)果圖四3、初步確定軸的最小直徑先初步估算軸的最小直徑。選取軸的材料為(調(diào)質(zhì)),根據(jù)機械設(shè)計(第八版)表15-3,取,得,中間軸最小直徑顯然是安裝滾動軸承的直徑和設(shè)計計算及說明結(jié)果4、 軸的結(jié)構(gòu)設(shè)計(1) 擬定軸上零件的裝配方案(見下圖圖五)(2)根據(jù)軸向定位的要求確定軸的各段直徑和長度1)初步選擇滾動軸承。因軸承同時受有徑向力和軸向力,故選用單列圓錐滾子軸承,參照工作要求并根據(jù),由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表15-7中初步選取0基本游隙組,標(biāo)準(zhǔn)精度級的單列圓錐滾子軸承30306,其尺寸為,。 這對軸承均采用套筒進行軸向定位,由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表15-7查得30306型軸承的定位軸肩高度,因此取套筒直徑。2)取安裝齒輪的軸段,錐齒輪左端與左軸承之間采用設(shè)計計算及說明結(jié)果套筒定位,已知錐齒輪輪轂長,為了使套筒端面可靠地壓緊端面,此軸段應(yīng)略短于輪轂長,故取,齒輪的右端采用軸肩定位,軸肩高度,故取,則軸環(huán)處的直徑為。3) 已知圓柱直齒輪齒寬,為了使套筒端面可靠地壓緊端面,此軸段應(yīng)略短于輪轂長,故取。4)箱體一小圓錐齒輪中心線為對稱軸,則取。(3)軸上的周向定位圓錐齒輪的周向定位采用平鍵連接,按由機械設(shè)計(第八版)表6-1查得平鍵截面,鍵槽用鍵槽銑刀加工,長為22mm,同時為保證齒輪與軸配合有良好的對中性,故選擇齒輪輪轂與軸的配合為;圓柱齒輪的周向定位采用平鍵連接,按由機械設(shè)計(第八版)表6-1查得平鍵截面,鍵槽用鍵槽銑刀加工,長為56mm,同時為保證齒輪與軸配合有良好的對中性,故選擇齒輪輪轂與軸的配合為;滾動軸承與軸的周向定位是由過渡配合來保證的,此處選軸的尺寸公差為m6。(4)確定軸上圓角和倒角尺寸取軸端倒角為5、 求軸上的載荷設(shè)計計算及說明結(jié)果載荷水平面H垂直面V支反力F彎矩M 總彎矩扭矩T6、按彎扭合成應(yīng)力校核軸的強度根據(jù)上表中的數(shù)據(jù)及軸的單向旋轉(zhuǎn),扭轉(zhuǎn)切應(yīng)力為脈動循環(huán)變應(yīng)力,取,軸的計算應(yīng)力前已選定軸的材料為(調(diào)質(zhì)),由機械設(shè)計(第八版)表15-1查得,故安全。7、精確校核軸的疲勞強度(1)判斷危險截面截面5左右側(cè)受應(yīng)力最大(2)截面5右側(cè)抗彎截面系數(shù)抗扭截面系數(shù)設(shè)計計算及說明結(jié)果截面5右側(cè)彎矩M為截面5上的扭矩為截面上的彎曲應(yīng)力截面上的扭轉(zhuǎn)切應(yīng)力軸的材料為,調(diào)質(zhì)處理。由表15-1查得。截面上由于軸肩而形成的理論應(yīng)力集中系數(shù)及按機械設(shè)計(第八版)附表3-2查取。因,經(jīng)插值后查得又由機械設(shè)計(第八版)附圖3-2可得軸的材料敏感系數(shù)為故有效應(yīng)力集中系數(shù)為由機械設(shè)計(第八版)附圖3-2的尺寸系數(shù),扭轉(zhuǎn)尺寸系數(shù)。軸按磨削加工,由機械設(shè)計(第八版)附圖3-4得表面質(zhì)量系數(shù)為設(shè)計計算及說明結(jié)果軸未經(jīng)表面強化處理,即,則綜合系數(shù)為又取合金鋼的特性系數(shù)計算安全系數(shù)值故可知安全。(3)截面5左側(cè)抗彎截面系數(shù)抗扭截面系數(shù)截面5左側(cè)彎矩M為設(shè)計計算及說明結(jié)果截面5上的扭矩為截面上的彎曲應(yīng)力截面上的扭轉(zhuǎn)切應(yīng)力過盈配合處的,由機械設(shè)計(第八版)附表3-8用插值法求出,并取,于是得軸按磨削加工,由機械設(shè)計(第八版)附圖3-4得表面質(zhì)量系數(shù)為故得綜合系數(shù)為計算安全系數(shù)值設(shè)計計算及說明結(jié)果故可知安全。輸出軸設(shè)計1、求輸出軸上的功率、轉(zhuǎn)速和轉(zhuǎn)矩 2、求作用在齒輪上的力已知圓柱斜齒輪的分度圓半徑而圓周力、徑向力及軸向力的方向如圖六所示設(shè)計計算及說明結(jié)果圖六設(shè)計計算及說明結(jié)果3、初步確定軸的最小直徑先初步估算軸的最小直徑。選取軸的材料為45鋼(調(diào)質(zhì)),根據(jù)機械設(shè)計(第八版)表15-3,取,得,輸出軸的最小直徑為安裝聯(lián)軸器的直徑,為了使所選的軸直徑與聯(lián)軸器的孔徑相適應(yīng),故需同時選取聯(lián)軸器型號。聯(lián)軸器的計算轉(zhuǎn)矩,查機械設(shè)計(第八版)表14-1,由于轉(zhuǎn)矩變化很小,故取,則查機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表17-4,選HL3型彈性柱銷聯(lián)軸器,其公稱轉(zhuǎn)矩為630000,半聯(lián)軸器的孔徑,故取,半聯(lián)軸器長度,半聯(lián)軸器與軸配合的轂孔長度為84mm。4、 軸的結(jié)構(gòu)設(shè)計(1) 擬定軸上零件的裝配方案(見圖六)設(shè)計計算及說明結(jié)果圖六(2)根據(jù)軸向定位的要求確定軸的各段直徑和長度1)為了滿足半聯(lián)軸器的軸向定位,1-2軸段右端需制出一軸肩,故取2-3段的 直徑,左端用軸端擋圈定位,按軸端擋圈直徑, 半聯(lián)軸器與軸配合的轂孔長度,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1-2段的長度應(yīng)比略短些,現(xiàn)取 。2) 初步選擇滾動軸承。因軸承同時受有徑向力和軸向力,故選用單列圓錐滾子軸承,參照工作要求并根據(jù),由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表15-7中初步選取0基本游隙組,標(biāo)準(zhǔn)精度級的單列圓錐滾子軸承30310,其尺寸為,而。左端軸承采用軸肩進行軸向定位,由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計計算及說明結(jié)果表15-7查得30310型軸承的定位軸肩高度,因此??;齒輪右端和右軸承之間采用套筒定位,已知齒輪輪轂的寬度為71mm,為了使套筒端面可靠地壓緊齒輪,此軸段應(yīng)略短于輪轂寬度,故取。齒輪的左端采用軸肩定位,軸肩高度,故取,則軸環(huán)處的直徑為。軸環(huán)寬度,取。4)軸承端蓋的總寬度為20mm,根據(jù)軸承端蓋的裝拆及便于對軸承添加潤滑油的要求,求得端蓋外端面與半聯(lián)軸器右端面間的距離,故取 5)箱體一小圓錐齒輪中心線為對稱軸,則取。(3)軸上的周向定位齒輪、半聯(lián)軸器的周向定位均采用平鍵連接,按由機械設(shè)計(第八版)表6-1查得平鍵截面,鍵槽用鍵槽銑刀加工,長為50mm,同時為保證齒輪與軸配合有良好的對中性,故選擇齒輪輪轂與軸的配合為;同樣,半聯(lián)軸器與軸的連接,選用平鍵,半聯(lián)軸器與軸的配合為,滾動軸承與軸的周向定位是由過渡配合來保證的,此處選軸的尺寸公差為k6。(4)確定軸上圓角和倒角尺寸取軸端倒角為5、求軸上的載荷設(shè)計計算及說明結(jié)果載荷水平面H垂直面V支反力F彎矩M 總彎矩扭矩T6、按彎扭合成應(yīng)力校核軸的強度根據(jù)上表中的數(shù)據(jù)及軸的單向旋轉(zhuǎn),扭轉(zhuǎn)切應(yīng)力為脈動循環(huán)變應(yīng)力,取,軸的計算應(yīng)力前已選定軸的材料為45鋼(調(diào)質(zhì)),由機械設(shè)計(第八版)表15-1查得,故安全。7、精確校核軸的疲勞強度(1)判斷危險截面截面7右側(cè)受應(yīng)力最大(2)截面7右側(cè)抗彎截面系數(shù)抗扭截面系數(shù)設(shè)計計算及說明結(jié)果截面7右側(cè)彎矩M為截面7上的扭矩為截面上的彎曲應(yīng)力截面上的扭轉(zhuǎn)切應(yīng)力軸的材料為45鋼,調(diào)質(zhì)處理。由表15-1查得。截面上由于軸肩而形成的理論應(yīng)力集中系數(shù)及按機械設(shè)計(第八版)附表3-2查取。因,經(jīng)插值后查得又由機械設(shè)計(第八版)附圖3-2可得軸的材料敏感系數(shù)為故有效應(yīng)力集中系數(shù)為由機械設(shè)計(第八版)附圖3-2的尺寸系數(shù),扭轉(zhuǎn)尺寸系數(shù)。軸按磨削加工,由機械設(shè)計(第八版)附圖3-4得表面質(zhì)量系數(shù)為設(shè)計計算及說明結(jié)果軸未經(jīng)表面強化處理,即,則綜合系數(shù)為又取碳鋼的特性系數(shù)計算安全系數(shù)值故可知安全。七、滾動軸承的選擇及計算輸入軸滾動軸承計算初步選擇滾動軸承,由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表15-7中初步選取0基本游隙組,標(biāo)準(zhǔn)精度級的單列圓錐滾子軸承30306,其尺寸為, ,載荷水平面H垂直面V支反力F則設(shè)計計算及說明結(jié)果則則則,則 則故合格。中間軸滾動軸承計算初步選擇滾動軸承,由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表15-7中初步選取0基本游隙組,標(biāo)準(zhǔn)精度級的單列圓錐滾子軸承30306,其尺寸為,載荷水平面H垂直面V支反力F設(shè)計計算及說明結(jié)果則則則則,則 則故合格。輸出軸軸滾動軸承計算初步選擇滾動軸承,由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表15-7中初步選取0基本游隙組,標(biāo)準(zhǔn)精度級的單列圓錐滾子軸承30310,其尺寸為,設(shè)計計算及說明結(jié)果載荷水平面H垂直面V支反力F則則則則,則 則故合格設(shè)計計算及說明結(jié)果八、鍵聯(lián)接的選擇及校核計算輸入軸鍵計算1、 校核聯(lián)軸器處的鍵連接該處選用普通平鍵尺寸為,接觸長度,則鍵聯(lián)接所能傳遞的轉(zhuǎn)矩為:,故單鍵即可。2、 校核圓錐齒輪處的鍵連接該處選用普通平鍵尺寸為,接觸長度,則鍵聯(lián)接所能傳遞的轉(zhuǎn)矩為:,故單鍵即可。中間軸鍵計算1、 校核圓錐齒輪處的鍵連接該處選用普通平鍵尺寸為,接觸長度,則鍵聯(lián)接所能傳遞的轉(zhuǎn)矩為:,故單鍵即可。2、 校核圓柱齒輪處的鍵連接該處選用普通平鍵尺寸為,接觸長度,則鍵聯(lián)接所能傳遞的轉(zhuǎn)矩為:設(shè)計計算及說明結(jié)果,故單鍵即可。輸出軸鍵計算1、 校核聯(lián)軸器處的鍵連接該處選用普通平鍵尺寸為,接觸長度,則鍵聯(lián)接所能傳遞的轉(zhuǎn)矩為:,故單鍵即可。2、 校核圓柱齒輪處的鍵連接該處選用普通平鍵尺寸為,接觸長度,則鍵聯(lián)接所能傳遞的轉(zhuǎn)矩為:,故單鍵即可。九、聯(lián)軸器的選擇在軸的計算中已選定聯(lián)軸器型號。輸入軸選HL1型彈性柱銷聯(lián)軸器,其公稱轉(zhuǎn)矩為160000,半聯(lián)軸器的孔徑,故取,半聯(lián)軸器長度,半聯(lián)軸器與軸配合的轂孔長度為38mm。輸出軸選選HL3型彈性柱銷聯(lián)軸器,其公稱轉(zhuǎn)矩為630000,半聯(lián)軸器的孔徑,故取,半聯(lián)軸器長度,半聯(lián)軸器與軸配合的轂孔長度為84mm。設(shè)計計算及說明結(jié)果十、減速器附件的選擇由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計選定通氣帽,A型壓配式圓形油標(biāo)A20(GB1160.1-89),外六角油塞及封油墊,箱座吊耳,吊環(huán)螺釘M12(GB825-88),啟蓋螺釘M8。十一、潤滑與密封齒輪采用浸油潤滑,由機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計表16-1查得選用N220中負荷工業(yè)齒輪油(GB5903-86)。當(dāng)齒輪圓周速度時,圓錐齒輪浸入油的深度約一個齒高,三分之一齒輪半徑,大齒輪的齒頂?shù)接偷酌娴木嚯x3060mm。由于大圓錐齒輪,可以利用齒輪飛濺的油潤滑軸承,并通過油槽潤滑其他軸上的軸承,且有散熱作用,效果較好。密封防止外界的灰塵、水分等侵入軸承,并阻止?jié)櫥瑒┑穆┦?。十二、設(shè)計小結(jié)這次關(guān)于帶式運輸機上的兩級圓錐圓柱齒輪減速器的課程設(shè)計是我們真正理論聯(lián)系實際、深入了解設(shè)計概念和設(shè)計過程的實踐考驗,對于提高我們機械設(shè)計的綜合素質(zhì)大有用處。通過兩個星期的設(shè)計實踐,使我對機械設(shè)計有了更多的了解和認識.為我們以后的工作打下了堅實的基礎(chǔ).機械設(shè)計是機械工業(yè)的基礎(chǔ),是一門綜合性相當(dāng)強的技術(shù)課程,它融機械原理、機械設(shè)計、理論力學(xué)、材料力學(xué)、互換性與技術(shù)測量、工程材料、機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計等于一體。這次的課程設(shè)計,對于培養(yǎng)我們理論聯(lián)系實際的設(shè)計思想、訓(xùn)練綜合運用機械設(shè)計和有關(guān)先修課程的理論,結(jié)合生產(chǎn)實際反應(yīng)和解決工程實際問題的能力,鞏固、加深和擴展有關(guān)機械設(shè)計方面的知識等方面有重要的作用。本次設(shè)計得到了指導(dǎo)老師的細心幫助和支持。衷心的感謝老師的指導(dǎo)和幫助。設(shè)計計算及說明結(jié)果設(shè)計中還存在不少錯誤和缺點,需要繼續(xù)努力學(xué)習(xí)和掌握有關(guān)機械設(shè)計的知識,繼續(xù)培養(yǎng)設(shè)計習(xí)慣和思維從而提高設(shè)計實踐操作能力。十三、參考文獻1、機械設(shè)計(第八版)高等教育出版社2、機械設(shè)計(機械設(shè)計基礎(chǔ))課程設(shè)計高等教育出版社48編號無錫太湖學(xué)院畢業(yè)設(shè)計(論文)相關(guān)資料題目: 工業(yè)機器人專用減速器的設(shè)計 信機 系 機械工程及自動化專業(yè)學(xué) 號: 0923229學(xué)生姓名: 賁素東 指導(dǎo)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(shè)計(論文)開題報告二、畢業(yè)設(shè)計(論文)外文資料翻譯及原文三、學(xué)生“畢業(yè)論文(論文)計劃、進度、檢查及落實表”四、實習(xí)鑒定表無錫太湖學(xué)院畢業(yè)設(shè)計(論文)開題報告題目: 工業(yè)機器人專用減速器的設(shè)計 信機 系 機械工程及自動化 專業(yè)學(xué) 號: 0923229 學(xué)生姓名: 賁素東 指導(dǎo)教師: 許菊若 (職稱:副教授 ) (職稱: )2012年11月25日 課題來源導(dǎo)師布置的任務(wù)科學(xué)依據(jù)(包括課題的科學(xué)意義;國內(nèi)外研究概況、水平和發(fā)展趨勢;應(yīng)用前景等)(1)課題科學(xué)意義減速器是各種機械設(shè)備中最常見的部件,它的作用是將電動機轉(zhuǎn)速減少或增加到機械設(shè)備所需要的轉(zhuǎn)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(shè)計在全面考慮多齒嚙合、運轉(zhuǎn)平穩(wěn)、輪齒均載等運動學(xué)和動力學(xué)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(xué)性能等指標(biāo),而且要便于制造、裝配和檢修,設(shè)計了該具有合理結(jié)構(gòu)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(jié)構(gòu)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(nèi)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(shù)已經(jīng)過關(guān),專業(yè)加工設(shè)備齊全,擺線輪已納入專業(yè)通用件,在國內(nèi)已做到通用化批量生產(chǎn),生產(chǎn)成本下降,因此擺線針輪傳動的減速器當(dāng)前廣為應(yīng)用。擺線針輪減速技術(shù)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(zhì)、原理上的創(chuàng)新。現(xiàn)今擺線針輪減速器,其原理和結(jié)構(gòu)還是1926年德國的原型。研究內(nèi)容 了解工業(yè)機器人的總體設(shè)計的相關(guān)內(nèi)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(shù)路線、實驗方案及可行性分析(1)技術(shù)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(yù)期成果研究計劃:2012年11月12日-2012年12月2日:按照任務(wù)書要求查閱論文相關(guān)2012年12月3日-2013年1月20日:專業(yè)實訓(xùn)。 2013年1月21日-2013年3月1日:按照要求修改畢業(yè)設(shè)計開題報告2013年3月1日-2013年3月8日:學(xué)習(xí)并翻譯一篇與畢業(yè)設(shè)計相關(guān)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(shè)計方案。2013年3月25日-2013年3月29日:總體設(shè)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(shè)計說明書。預(yù)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(shè)計,繪制零件圖4份。3.完成設(shè)計說明書一份。特色或創(chuàng)新之處 傳動比大,結(jié)構(gòu)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(shè)計較為成熟,生產(chǎn)設(shè)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(fù)雜:加工擺線針輪需要專門的加床,對裝配工藝也有較嚴(yán)格的工藝要求。指導(dǎo)教師意見 指導(dǎo)教師簽名:年 月 日教研室(學(xué)科組、研究所)意見 教研室主任簽名: 年 月 日系意見 主管領(lǐng)導(dǎo)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
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