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機(jī)械設(shè)計(jì)綜合課程設(shè)計(jì)--薄壁零件沖床機(jī)構(gòu)設(shè)計(jì)(編輯修改稿)

2025-02-08 04:55 本頁(yè)面
 

【文章內(nèi)容簡(jiǎn)介】 = 動(dòng)載荷系數(shù) ???? = 齒間載荷分配系數(shù) ?????? = 齒向載荷分配系數(shù) ?????? = 重合度系數(shù): ???? = + ????v= 齒形系數(shù): ??????1 = , ??????2 = 應(yīng)力修正系數(shù): ??????1 = , ??????2 = 螺旋角系數(shù): ???? = ????1 = 217MPa, ????2 = 203MPa ② 計(jì)算需用彎曲應(yīng)力 ?????? = ???????????????????????????????????????????????????????????? 齒根彎曲疲勞極限 ??????????1 = 300MPa, ??????????2 = 270MPa 彎曲強(qiáng)度最小安全系數(shù): lim ? 彎曲強(qiáng)度尺寸系數(shù) : ????1 = ????2 = 1 彎曲壽命系數(shù): ??????1 = , ??????2 = ??????1 = 427MPa ??????2 = 401MP 11 應(yīng)力修正系數(shù): ??????1 = ??????2 = 2 相對(duì)齒根圓攪敏感及表面狀況系數(shù): ????????????1 = ????????????2 = ????????????1 = ????????????2 = 1 ??????1 = 427MPa, ??????2 = 401MP ③ 彎曲疲勞強(qiáng)度的校核 ????1 ??????1, ????1 ??????1 核 無(wú)嚴(yán)重過(guò)載,無(wú)需靜載荷校核。 ( 2) 低速級(jí)齒輪設(shè)計(jì) 計(jì)算項(xiàng)目 計(jì)算內(nèi)容 計(jì)算結(jié)果 和精度等級(jí) 考慮到主動(dòng)輪輪速不是很高,故采用斜齒,小齒輪用 40Cr,調(diào)制處理,硬度 241~ 286HB,平均取 260HB,大齒輪用 45鋼,調(diào)制處理,硬度為 229~ 286HB平均取 240HB。 8級(jí)精度。 2.初步計(jì)算小齒輪直徑??1 因?yàn)椴捎瞄]式軟齒面?zhèn)鲃?dòng),按齒面接觸強(qiáng)度初步估算小齒輪分度圓直徑, ??1 ≥????√ ????1Ψ????????2 ??:1??3 ,初取 β = 13176。, ???? = 756,動(dòng)載荷系數(shù) K=,轉(zhuǎn)矩 ??1 = 9550 ??1??1= m,齒寬系數(shù) Ψ?? = 1 查表基礎(chǔ)疲勞強(qiáng)度 ????lim1 = 710Mpa,????lim2 = 580Mpa 則 ??????1 = ????lim1 = 639MPa ??????2 = ????lim2 = 522MPa 初步計(jì)算許用接觸應(yīng)力 ?????? = 522MPa,估算??1 ≥ 756 √5222 : = 初取 ??1 = 82mm K= ??1 = m ????lim1 = 710Mpa ????lim2 = 580Mpa ??????1 = 639MPa ??????2 = 522MPa ??1 = 82mm 參數(shù) 校核圓周速度 v和精度等級(jí) 圓周速度 v = ????1??1601000 = ??821000 =,精度等級(jí)取 8級(jí)精度合理 確定齒數(shù) ??1 = 32, ??2 = ??1 ??23 = ??1 = 32 ??2 = 101 β = 176。 d1 = d2 = 12 32 = ,取 ??2 = 101(互質(zhì)) 確定模數(shù) ???? = ??1??1= 8232 = ,查表取???? = 確定螺旋角 β = arccos????????= arccos =176。(與估計(jì)值接近) 小齒輪 直徑 d1 = mtz1 = 32 = 大齒輪直徑 d2 = mtz2 = 初步齒寬 b = d1ψd = 182 = 82mm 校核傳動(dòng)比誤差:因齒數(shù)未做圓整,傳動(dòng)比不變。 b = 82mm 接觸疲勞強(qiáng)度 由11tH H E A V H H pF uZ Z Z Z K K K d b u? ? ? ?? ? ? ? 校核齒面解除疲勞強(qiáng)度。 ① 計(jì)算齒面接觸應(yīng)力 σH 節(jié) 點(diǎn) 區(qū) 域 系 數(shù) ZH = 彈性系數(shù)ZE = √N(yùn)/mm2 重合度系數(shù) Zξ由端面重合度 ξa和縱向重合度ξ??確定,其中: 端面重合度 ξa = 12??[??1(????????????1 ???????????′)+??2(????????????2 ???????????′)] ???? = arctan(?????????????????? ) = 176。 ??????1 = ????????????????1????1= arccos(??1??????????????1)= 176。 ??????2 = ????????????????2????2= arccos(??2??????????????2)= 176。 由于無(wú)變位,端面嚙合角 αt′ = αt = 176。 解得 ξa = ??????1 = 817Mpa ??????2 = 736MPa 13 縱 向 重 合 度 為 ???? = ??sinβ??????= 82??????176。?? = 1 故 Zξ = √1????= √ = 螺旋角系數(shù) ???? = √cosβ = √??????176。 = 使用系數(shù) KA = 動(dòng)載荷系數(shù) ???? = ???? = 2??1??1= 223262082 = ?????????? =82 = 100N/mm ?????? = ?????? = cos???? = cosβcos??????????????= 齒間載荷分布系數(shù),其中:對(duì)稱支承,調(diào)質(zhì)齒輪精度等級(jí) 8級(jí) ?????? = ??+??(????1)2 +C?10。3?? = 齒面接觸應(yīng)力 σH = ② 計(jì)算許用接觸應(yīng)力 σHP ?????? = ?????????????????????????????????????????? 總 工 作 時(shí) 間 : ??總 = 10365 82 =58400h 應(yīng)力循環(huán)次數(shù): ????1 = 60γ??1??總 = 109? ????2 = ????1?? = 108? 接觸強(qiáng)度壽命系數(shù): ??????1 = , ??????2 = 接觸強(qiáng)度壽命系數(shù): ??????1 = , ??????2 = 齒面工作硬化系數(shù): ????1 = ????2 = ?14 ????2。1301700 = 接觸強(qiáng)度尺寸系數(shù): ????1 = ????2 = 潤(rùn)滑油膜影響系數(shù): ????1 = ????2 = ????1 = ????2 =????1 = ????2 = 1 接觸最小安全系數(shù)取 lim ? 解得許用接觸應(yīng)力: ??????1 = 817MPa ,??????2 = 736MPa ③ 驗(yàn)算: σH = ??????2 = 736MPa 接觸疲勞強(qiáng)度較為合適,齒輪尺寸無(wú)須調(diào)整。 5. 確定主要尺寸 中 心 距 : a = ??1:??22 = 圓整取a = 171mm 由公式 a = (??1:??2)????2???????? 可求得精確的螺旋角 β = arccos(??1:??2)????2?? = 176。 合理 端面模數(shù) ???? = ???????????? = 2??????176。 = 小齒輪直徑 ??1 = ???? ???1 = 大齒輪直徑 ??2 = ???? ???2 = 齒寬 b = 82mm ??1 = 90mm ??2 = 82mm 小齒輪當(dāng)量齒數(shù) ????1 = ??1????????3 = 取 35 大齒輪當(dāng)量齒數(shù) ????2 = ??2????????3 = 取 110 15 疲勞強(qiáng)度驗(yàn)算 σF = KA ?KV ?K???? ?K???? ? Ftbmn?YFa ?YSa ?Yε?Yβ ≤ σHP ① 計(jì)算齒根彎曲應(yīng)力 使用系數(shù) ???? = 動(dòng)載荷系數(shù) ???? = 齒間載荷分配系數(shù) ?????? = 齒向載荷分配系數(shù) ?????? = 重合度系數(shù): ???? = + ????v= 齒形系數(shù): ??????1 = , ??????2 = 應(yīng)力修正系數(shù): ??????1 = , ??????2 = 螺旋角系數(shù): ???? = ????1 = , ????2 = ② 計(jì)算需用彎曲應(yīng)力 ?????? = ???????????????????????????????????????????????????????????? 齒根彎曲疲勞極限 ??????????1 = 300MPa, ??????????2 = 270MPa 彎曲強(qiáng)度最小安全系數(shù) : lim ? 彎曲強(qiáng)度尺寸系數(shù) : ????1 = ????2 = 1 彎曲壽命系數(shù): ??????1 = , ??????2 = 應(yīng)力修正系數(shù): ??????1 = ??????2 = 2 相對(duì)齒根圓攪敏感及表面狀況系數(shù): ????????????1 = ????????????2 = ????????????1 = ????????????2 = 1 ??????1 = 427MPa, ??????2 = 401MP ③ 彎曲疲勞強(qiáng)度的校核 ????1 ??????1, ????1 ??????1 ??????1 = 427MPa ??????2 = 401MP 16 核 無(wú)嚴(yán)重過(guò)載,無(wú)需靜載荷校核。 傳送帶的設(shè)計(jì) 功率 ???? ???? = ?????? ???? = P = ???? = ???? = 根據(jù) ????和 n選取普通 V帶型號(hào): C型帶 小帶輪直徑 ????1 = 200~ 215mm ????1= 200~ 215mm 直徑和帶速 C型帶 n = 970r/min , ????1 = 210????, ε = 大帶輪直徑 ????2 = ??1??2????1(1?ε) = 取 208mm 小帶輪轉(zhuǎn)速 v = ??????1??601000 = ????1 = 210???? ????2 = 208mm v = 動(dòng)中心距 a和帶的基準(zhǔn)長(zhǎng)度 ???? ① ( ????1 +????2) ≤ ??0 ≤ 2( ????1 +????2) 230mm ≤ ??0 ≤ 836???? 取 ??0 = 600mm ② 計(jì)算帶的初步基準(zhǔn)長(zhǎng)度 ????′ ????′ = 2???? +??2(????1 +????2)+( ????1 +????2)24????= 選取基準(zhǔn)長(zhǎng)度 ???? = 2022mm ???? = ③ 求實(shí)際中心距 a a ≈ ???? + ????。????′2 = 600 +2022?2 = 取 a = 672mm ??0 = 600mm a = 672m
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