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二級(jí)斜齒圓柱齒輪減速器-在線瀏覽

2025-07-03 00:07本頁(yè)面
  

【正文】 25+1/116)] = 7) 由式84得:eb = = 125 = 8) 由式819得:Ze = = = = 9) 由式821得:Zb = = = 10) 查得小齒輪的接觸疲勞強(qiáng)度極限:sHlim1 = 650 MPa,大齒輪的接觸疲勞強(qiáng)度極限:sHlim2 = 530 MPa。 2) 中心距:a = = = 145 mm 3) 螺旋角:b = arccos = arccos = 4) 計(jì)算齒輪參數(shù):d1 = = = 51 mmd2 = = = 239 mmb = φdd1 = 51 mmb圓整為整數(shù)為:b = 51 mm。 6) 同前,ZE = 。 7) 由式83得:ea = [(1/Z1+1/Z2)]cosb = [(1/25+1/116)] = 8) 由式84得:eb = = 125 = 9) eg = ea+eb = 10) 同前,取:eb = 1Ze = = = = 11) 由式821得:Zb = = = 12) 由表82查得系數(shù):KA = 1,由圖86查得系數(shù):KV = 。5 校核齒根彎曲疲勞強(qiáng)度:(1) 確定公式內(nèi)各計(jì)算數(shù)值: 1) 當(dāng)量齒數(shù):ZV1 = Z1/cos3b = 25/ = ZV2 = Z2/cos3b = 116/ = 2) eaV = [(1/ZV1+1/ZV2)]cosb= [(1/+1/)] = 3) 由式825得重合度系數(shù):Ye = + 4) 由圖826和eb = = 5) = = 前已求得:KHa = ,故?。篕Fa = 6) = = = 且前已求得:KHb = ,由圖812查得:KFb = 7) K = KAKVKFaKFb = 1 = 8) 由圖81818查得齒形系數(shù)和應(yīng)力修正系數(shù):齒形系數(shù):YFa1 = YFa2 = 應(yīng)力校正系數(shù):YSa1 = YSa2 = 9) 由圖822c按齒面硬度查得大小齒輪的彎曲疲勞強(qiáng)度極限為:sFlim1 = 500 MPa sFlim2 = 380 MPa 10) 同例82:小齒輪應(yīng)力循環(huán)次數(shù):N1 = 109大齒輪應(yīng)力循環(huán)次數(shù):N2 = 108 11) 由圖820查得彎曲疲勞壽命系數(shù)為:KFN1 = KFN2 = 12) 計(jì)算彎曲疲勞許用應(yīng)力,取S=,由式815得:[sF]1 = = = [sF]2 = = = = = = = 大齒輪數(shù)值大選用。(3) 各齒輪參數(shù)如下:大小齒輪分度圓直徑:d1 = 51 mmd2 = 239 mmb = ydd1 = 51 mmb圓整為整數(shù)為:b = 51 mm圓整的大小齒輪寬度為:b1 = 56 mm b2 = 51 mm中心距:a = 145 mm,模數(shù):m = 2 mm(二) 低速級(jí)齒輪傳動(dòng)的設(shè)計(jì)計(jì)算1 齒輪材料、熱處理及精度: 考慮此減速器的功率及現(xiàn)場(chǎng)安裝的限制,故大小齒輪都選用漸開線斜齒輪。高速級(jí)大齒輪選用45鋼調(diào)質(zhì),齒面硬度為大齒輪:225~255HBW。2 初步設(shè)計(jì)齒輪傳動(dòng)的主要尺寸,按齒面接觸強(qiáng)度設(shè)計(jì):確定各參數(shù)的值: 1) 試選Kt = 2) T2 = Nm 3) 選取齒寬系數(shù)yd = 1 4) 由表85查得材料的彈性影響系數(shù)ZE = 5) 由圖815查得節(jié)點(diǎn)區(qū)域系數(shù)ZH = 6) 由式83得:ea = [(1/Z3+1/Z4)]cosb = [(1/26+1/92)]cos110 = 7) 由式84得:eb = = 126tan110 = 8) 由式819得:Ze = = = = 9) 由式821得:Zb = = = 10) 查得小齒輪的接觸疲勞強(qiáng)度極限:sHlim1 = 650 MPa,大齒輪的接觸疲勞強(qiáng)度極限:sHlim2 = 530 MPa。 2) 中心距:a = = = mm 3) 螺旋角:b = arccos = arccos = 110 4) 計(jì)算齒輪參數(shù):d3 = = = 79 mmd4 = = = 281 mmb = φdd3 = 79 mmb圓整為整數(shù)為:b = 79 mm。 6) 同前,ZE = 。 7) 由式83得:ea = [(1/Z3+1/Z4)]cosb = [(1/26+1/92)]cos110 = 8) 由式84得:eb = = 126tan110 = 9) eg = ea+eb = 10) 同前,取:eb = 1Ze = = = = 11) 由式821得:Zb = = = 12) 由表82查得系數(shù):KA = 1,由圖86查得系數(shù):KV = 。5 校核齒根彎曲疲勞強(qiáng)度:(1) 確定公式內(nèi)各計(jì)算數(shù)值: 1) 當(dāng)量齒數(shù):ZV3 = Z3/cos3b = 26/cos3110 = ZV4 = Z4/cos3b = 92/cos3110 = 2) eaV = [(1/ZV3+1/ZV4)]cosb= [(1/+1/)]cos110 = 3) 由式825得重合度系數(shù):Ye = + 4) 由圖826和eb = = 5) = = 前已求得:KHa = ,故?。篕Fa = 6) = = = 且前已求得:KHb = ,由圖812查得:KFb = 7) K = KAKVKFaKFb = 1 = 8) 由圖81818查得齒形系數(shù)和應(yīng)力修正系數(shù):齒形系數(shù):YFa3 = YFa4 = 應(yīng)力校正系數(shù):YSa3 = YSa4 = 9) 由圖822c按齒面硬度查得大小齒輪的彎曲疲勞強(qiáng)度極限為:sFlim3 = 500 MPa sFlim4 = 380 MPa 10) 同例82:小齒輪應(yīng)力循環(huán)次數(shù):N3 = 108大齒輪應(yīng)力循環(huán)次數(shù):N4 = 108 11) 由圖820查得彎曲疲勞壽命系數(shù)為:KFN3 = KFN4 = 12) 計(jì)算彎曲疲勞許用應(yīng)力,取S=,由式815得:[sF]3 = = = [sF]4 = = = = = = = 大齒輪數(shù)值大選用。(3) 各齒輪參數(shù)如下:大小齒輪分度圓直徑:d3 = 79 mmd4 = 281 mmb = ydd3 = 79 mmb圓整為整數(shù)為:b = 79 mm圓整的大小齒輪寬度為:b3 = 84 mm b4 = 79 mm中心距:a = 180 mm,模數(shù):m = 3 mm第七部分 傳動(dòng)軸承和傳動(dòng)軸及聯(lián)軸器的設(shè)計(jì)Ⅰ軸的設(shè)計(jì)1 輸入軸上的功率P轉(zhuǎn)速n1和轉(zhuǎn)矩T1:P1 = KW n1 = r/min T1 = Nm2 求作用在齒輪上的力: 已知高速級(jí)小齒輪的分度圓直徑為:d1 = 51 mm 則:Ft = = = 3502 NFr = Ft = 3502 = NFa = Fttanb = 3502 = N3 初步確定軸的最小直徑: 先初步估算軸的最小直徑。帶輪的寬度:B = (
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