【正文】 and plete the reducer gear in puting and assembly, the main task contain the choice of motor to the belt transmission design and calculation, to the design and calculation of gear and shaft design and calculation, finally according to the size of the selected gear and shaft in accordance with the relevant standard plete enclosure design and other related parts and ponents selection. The most important part of this design is the core of gear transmission part of the selection calculation and design calculation and check of each gear shaft is chosen in the design of helical gear, chose a helical gear is mainly in order to ensure the stability of the transmission and the use of the relationship between the two vice gear and reverse loading offset part of the axial force, residual axial force to offset by selecting the appropriate bearing, tapered roller bearings are the main choice in the design. Another window of this design is to use puter instead of traditional manual calculation, the main use is the Solidworks software, the software is mainly used to plete the 3D entity model, and then through the explosion view more clearly express of the structure principle to this device, and the use of the software of puting functions is to plete the checking calculation of gear and shaft.Keywords： gear； drive shaft； transmission ratio。主要任務(wù)是進(jìn)行結(jié)構(gòu)設(shè)計(jì)并完成減速機(jī)中傳動裝置的計(jì)算以及裝配，設(shè)計(jì)主要從電動機(jī)的選擇到帶傳動的設(shè)計(jì)計(jì)算，再到齒輪的設(shè)計(jì)計(jì)算以及軸的設(shè)計(jì)計(jì)算，最后根據(jù)所選齒輪以及軸的尺寸根據(jù)相關(guān)標(biāo)準(zhǔn)完成箱體的設(shè)計(jì)以及其它相關(guān)零部件的選擇。它的輸送能力大、功耗小、結(jié)構(gòu)簡單、對物料適應(yīng)性強(qiáng)，因此應(yīng)用范圍很廣。帶式輸送機(jī)的工作原理如圖61所示。移動工帶式輸送機(jī)適用于零星分散煤堆的轉(zhuǎn)運(yùn)，由于結(jié)構(gòu)笨重，移動困難，目前制造廠生產(chǎn)的移動帶式輸送機(jī)帶寬為400~800mm，~25m/s，傾角為00~200，長度一般在5~20m范圍內(nèi)。.⑸..:輸送物料的最大傾角可達(dá)90176。由[2]表86和表88取主動輪基準(zhǔn)直徑 =80 mm根據(jù)[2]式（815）， 從動輪基準(zhǔn)直徑 。 ＝計(jì)算載荷系數(shù)K已知使用系數(shù)=1已知V＝，由表查得動載荷系數(shù)=由表查得：的計(jì)算公式： ＝＋（1＋）＋ ＝再由表查的： =, =公式： =1=再按實(shí)際載荷系數(shù)校正所算得分度院圓直徑： =計(jì)算模數(shù)：==：設(shè)計(jì)公式：確定計(jì)算參數(shù)：計(jì)算載荷系數(shù)：　=1 =根據(jù)縱向重合度：＝，從圖1028查得螺旋角影響系數(shù)=計(jì)算當(dāng)量齒數(shù)： = =由[課]表10－5查取齒形系數(shù)=, =查取應(yīng)力校正系數(shù)=， =再由表1020查得小齒輪彎曲疲勞強(qiáng)度極限：＝500MPa,大齒輪彎曲疲勞強(qiáng)度極限＝380MPa再由表查得彎曲疲勞系數(shù)： =, =計(jì)算彎曲疲勞許用應(yīng)力，取彎曲疲勞安全系數(shù)：S= == ==計(jì)算大，小齒輪的，并加以比較：==大齒輪的數(shù)值大，選用大齒輪 =設(shè)計(jì)計(jì)算： 對比計(jì)算結(jié)果，由齒面接觸疲勞強(qiáng)度計(jì)算的法面模數(shù)大于由齒面接觸強(qiáng)度計(jì)算的法面模數(shù)，取標(biāo)準(zhǔn)模數(shù)=2mm，既滿足彎曲強(qiáng)度，但為了滿足接觸疲勞強(qiáng)度需要按接觸疲勞強(qiáng)度計(jì)算得分度圓直徑=： ==?。?6則=97：計(jì)算中心距：將中心距圓整為：127 mm按圓整后中心距修正螺旋角： 因的值改變不大，故參數(shù)等不必修正。查表得：材料彈性影響系數(shù)ZE=再按齒面硬度查圖1021得：小齒輪得接觸疲勞強(qiáng)度極限＝590MPa，大齒輪得接觸疲勞強(qiáng)度極限：＝560MPa.由計(jì)算公式：N=算出循環(huán)次數(shù)：＝601（288300） ＝=1再由N1,N2查圖1019得接觸疲勞壽命系數(shù)=, =.計(jì)算接觸疲勞許用應(yīng)力，取安全系數(shù)S=1,失效概率1％。軸承寬度B= ,兩齒輪端面間的距離△4=10mm其余的如圖。(10)軸的細(xì)部結(jié)構(gòu)設(shè)計(jì)由表6—1查出鍵槽尺寸：bh=149(t=，r=)；由表6—2查出鍵長：L=45； (11)中間軸的精確校核：對照軸的晚矩圖和結(jié)構(gòu)圖，從強(qiáng)度和應(yīng)力集中分析Ⅰ，Ⅱ，G都是危險(xiǎn)段面，但是由于Ⅰ，Ⅱ還受到扭矩作用，再由II斷面的彎矩要大于I處，所以現(xiàn)在就對II處進(jìn)行校核。軸承預(yù)期壽命與整機(jī)壽命相同，為：830016=38400h軸承實(shí)際壽命Lh10=16670/n2(Cr/PrⅡ)ε=16670/(59800/7371)3=128554h＞38400具有足夠使用壽命。 在學(xué)校的學(xué)習(xí)生活即將結(jié)束，回顧四年來的學(xué)習(xí)經(jīng)歷，面對現(xiàn)在的收獲，我感到無限欣慰。經(jīng)校核，高、低軸的軸承均滿足要求中間軸與齒輪Ⅰ的鍵聯(lián)接運(yùn)用及計(jì)算。由手冊查得：Ⅰ剖面的安全系數(shù)： 抗彎斷面系數(shù)：抗扭斷面系數(shù)：彎曲應(yīng)力幅：彎曲平均應(yīng)力 扭轉(zhuǎn)切應(yīng)力幅：平均切應(yīng)力：鍵槽所引起的有效應(yīng)力集中系數(shù) 再由手冊查得，表面狀態(tài)系數(shù)β=，尺寸系數(shù)剪切配合零件的綜合影響系數(shù)，取進(jìn)行計(jì)算：剪切配合零件的綜合影響系數(shù)，取進(jìn)行計(jì)算，由齒輪計(jì)算循環(huán)次數(shù)，所以取壽命系數(shù) 綜合安全系數(shù)：所以具有足夠的強(qiáng)度。AC=57mm CD=88mm CB=72mm AD=217mm(2) 繪軸的受力圖(3) 計(jì)算軸上的作用力：齒輪2：Ft2=2T2/d2=2103/= Fr2=Ft2tanαn/cosβ2=tan20o/=1342N Fα2=Ft2tanβ2=3571=917N齒輪3：Ft3=2T3/d3=2103/=7899N Fr3=Ft3tann/cosβ3=7899tan20o/=2959N Fα3=Ft3tanβ3=7899=1926N(4) 計(jì)算支反力繞支點(diǎn)B的力矩和ΣMBZ=0，得RAZ=[Fr2(88+72)+Fa2d2/2+Fa3d3/2－Fr372]217 =(1342160+917+19262959) 217 =833N同理：Σ