二級斜齒圓柱齒輪減速器-文庫吧
2025-05-01 00:07 本頁面
【正文】 齒輪選用45鋼調(diào)質(zhì)，齒面硬度為大齒輪：225~255HBW。取小齒齒數(shù)：Z1 = 25，則：Z2 = i12Z1 = 25 = ?。篫2 = 116 2） 初選螺旋角:b = 。2 初步設(shè)計(jì)齒輪傳動的主要尺寸，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) T1 = 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/Z1+1/Z2)]cosb = [(1/25+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。 11) 計(jì)算應(yīng)力循環(huán)次數(shù)：小齒輪應(yīng)力循環(huán)次數(shù)：N1 = 60nkth = 601830028 = 109大齒輪應(yīng)力循環(huán)次數(shù)：N2 = 60nkth = N1/u = 109/ = 108 12) 由圖819查得接觸疲勞壽命系數(shù):KHN1 = ,KHN2 = 13) 計(jì)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:[sH]1 = = 650 = MPa[sH]2 = = 530 = 477 MPa許用接觸應(yīng)力:[sH] = ([sH]1+[sH]2)/2 = (+477)/2 = MPa3 設(shè)計(jì)計(jì)算:小齒輪的分度圓直徑:d1t:= = mm4 修正計(jì)算結(jié)果： 1) 確定：mn = = = mm取為標(biāo)準(zhǔn)值:2 mm。 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。 5) 計(jì)算圓周速度v:v = = = m/s由表88選取齒輪精度等級為8級。 6) 同前，ZE = 。由圖815查得節(jié)點(diǎn)區(qū)域系數(shù)為:ZH = 。 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 = 。 13) Ft = = = 3502 N = = 100 Nmm 14) 由tanat = tanan/cosb得：at = arctan(tanan/cosb) = arctan(tan200/) = 15) 由式817得：cosbb = cosbcosan/cosat = 16) 由表83查得：KHa = KFa = 17) 由表84得：KHb = +(1+)yd2+103b = 18) K = KAKVKHaKHb = 1 = 計(jì)算K值滿足要求，計(jì)算結(jié)果可用。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。(2) 按式823校核齒根彎曲疲勞強(qiáng)度：mn≥ = = mm≤2所以強(qiáng)度足夠。(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） 低速級齒輪傳動的設(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)場安裝的限制，故大小齒輪都選用漸開線斜齒輪。 1） 材料：高速級小齒輪選用40Cr鋼調(diào)質(zhì)，齒面硬度為小齒輪：274~286HBW。高速級大齒輪選用45鋼調(diào)質(zhì)，齒面硬度為大齒輪：225~255HBW。取小齒齒數(shù)：Z3 = 26，則：Z4 = i23Z3 = 26 = 取：Z4 = 92 2） 初選螺旋角:b = 110。2 初步設(shè)計(jì)齒輪傳動的主要尺寸，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。 11) 計(jì)算應(yīng)力循環(huán)次數(shù)：小齒輪應(yīng)力循環(huán)次數(shù)：N3 = 60nkth = 601830028 = 108大齒輪應(yīng)力循環(huán)次數(shù)：N4 = 60nkth = N3/u = 108/ = 108 12) 由圖819查得接觸疲勞壽命系數(shù):KHN3 = ,KHN4 = 13) 計(jì)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:[sH]3 = = 650 = 585 MPa[sH]4 = = 530 = MPa許用接觸應(yīng)力:[sH] = ([sH]3+[sH]4)/2 = (585+)/2 =
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