索道设计说明.doc

计算项目设计计算内容设计结果一、基本参数的设计2、 索道种类和形式的确定3、 支架的设定和计算四、承载牵引索的选择五、配重的选择计算六、驱动轮，滚轮，垂直导向轮直径与包角的选择7、 驱动轮、滚轮、垂直导向轮直径和包角的货车运行阻力的计算 8、 运载索的各特征力的计算1、 基本参数的设计1.1货运索道工作制度（1） 工作日数取n=300天（2） 每日运行小时数n=19.5h （三天作业）运输不均匀系数c=1.51.2货运索道每小时运量 日运量 小时运量1.3小车及容积 货车型号：ds-10-0.5型 v有效(满载系数y=0.9） 有效r1.4发车时间 每小时发车数次 发车间隔 货车间距2、 索道种类及形式的确定 单索循环索道3、 支架的设定与计算 支架高度 支架间距（高差) 4、 承载牵引索的选择4.1 取最小张力与荷重比系数n4.2粗选择抗拉安全系数n。计算皮破断拉力rt4抗拉安全系数n=4.5 4.3承载牵引索直径的选择抗拉强度 h=4-5+4-5+6-5+6-3+4=6ml=115+130+110+150+160+140+170+160+150=1285m钢缘托索轮阻力系数单位长度自重 =165.33kg/100m选择直径为22.5mm的钢丝绳5、 配重的选择计算5.1 拉近装置设置到索道的下站5.2如图1、 拉近装置2、 拉近索导向轮3、 重锤5.3拉近重锤配重6、 驱动轮，滚轮，垂直导向轮直径与包角的选择6.1托索轮，压索轮直径与包角 取20托索轮包角6.2驱动轮，迂回轮，d与 确定驱动轮缠绕方式如下图驱动轮衬垫材料为合成橡胶，需用比压p=2mpa 由 得 取驱动轮附着系数7、 驱动轮、滚轮、垂直导向轮直径与包角的货车运行阻力计算7.1驱动轮，压索轮，垂直导向轮阻力系数 轴承阻力系数 钢丝绳的刚性阻力系数7.2阻力重车侧:空车侧：8、 运载索各个特征点拉力计算8.1 由公式可求出： 由公式 8.3 9、 小车轮数及轮压计算 取小车轮数m=4 轮压 n=300天n=19.5hv有效=0.36十一.重车侧空车侧承载索重索倾角的计算十、重车侧，空车侧承载索空索倾角计算10.1重车侧：ix=sin-1(q2*litzi)+tan-1hiliiy=sin-1(q2*li+1tzi)+tan-1hi+1li+11x=sin-1(q2*l1tz1)+tan-1h1l1=2.4821y=sin-1(q2*l2tz1)+tan-1h2l2=0.3022x=sin-1(q2*l2tz2)+tan-1h2l2=-0.0012y=sin-1(q2*l3tz2)+tan-1h3l3=2.3143x=sin-1(q2*l3tz3)+tan-1h3l3=2.5913y=sin-1(q2*l4tz3)+tan-1h4l4=-1.7434x=sin-1(q2*l4tz4)+tan-1h4l4=-1.4634y=sin-1(q2*l5tz4)+tan-1h5l5=3.0875x=sin-1(q2*l5tz5)+tan-1h5l5=2.7595y=sin-1(q2*l6tz5)+tan-1h6l6=0.2916x=sin-1(q2*l6tz6)+tan-1h6l6=0.5046y=sin-1(q2*l7tz6)+tan-1h7l7=2.9017x=sin-1(q2*l7tz7)+tan-1h7l7=2.5947y=sin-1(q2*l9tz8)+tan-1h8l8=-0.8468x=sin-1(q2*l8tz8)+tan-1h8l8=-0.7428y=sin-1(q2*l9tz8)+tan-1h9l9=2.12110.2空车侧ix=sin-1(q2*litki)+tan-1hiliiy=sin-1(q2*li+1tki)+tan-1hi+1li+11x=sin-1(q2*l1tk1)+tan-1h1l1=2.4831y=sin-1(q2*l2tk1)+tan-1h2l2=-0.0012x=sin-1(q2*l2tk2)+tan-1h2l2=0.5082y=sin-1(q2*l3tk2)+tan-1h3l3=2.7453x=sin-1(q2*l3tk3)+tan-1h3l3=2.5923y=sin-1(q2*l4tk3)+tan-1h4l4=-1.7414x=sin-1(q2*l4tk4)+tan-1h4l4=-1.4594y=sin-1(q2*l5tk4)+tan-1h5l5=2.3865x=sin-1(q2*l5tk5)+tan-1h5l5=2.7615y=sin-1(q2*l6tk5)+tan-1h6l6=0.2926x=sin-1(q2*l6tk6)+tan-1h6l6=0.5136y=sin-1(q2*l7tk6)+tan-1h7l7=2.9137x=sin-1(q2*l7tk7)+tan-1h7l7=2.6177y=sin-1(q2*l9tk8)+tan-1h8l8=-0.8458x=sin-1(q2*l8tk8)+tan-1h8l8=-1.1948y=sin-1(q2*l9tk8)+tan-1h9l9=2.123十一.重车侧空车侧承载索重索倾角的计算11.1载荷分布系数ix=licosiiy=li+1cosi+1由上述公式可得：1x=0.8361y=0.9452x=0.9452y=0.83x=0.83y=1.094x=1.094y=1.1645x=1.1645y=1.0186x=1.0186y=1.2367x=1.2367y=1.1638x=1.1638y=1.09111.2载荷在支架左侧ix=sin-121+ixqcosi+qli2timin+iiy=sin-12iyqcosi+1+qli+12timin+i+1重车侧q=qz timin=tziminz1x=2.214z1y=2.568z2x=7.341z2y=5.612z3x=2.315z3y=0.756z4x=6.968z4y=7.735z5x=7.392z5y=2.455z6x=7.656z6y=7.238z7x=7.074z7y=1.457z8x=4.870z8y=4.928空车侧q=qk timin=tkimink1x=3.392k1y=0.756k2x=2.119k2y=2.314k3x=3.556k3y=-1.179k4x=0.484k4y=4.140k5x=3.827k5y=0.779k6x=2.181k6y=2.275k7x=3.642k7y=-0.327k8x=0.552k8y=2.75411.3载荷在支架右侧ix=sin-12ixqcosi+qli2timin+iiy=sin-121+iyqcosi+1+qli+12timin+i+1重车侧q=qz timin=tziminz1x=6.416z1y=4,472z2x=3.428z2y=9.113z3x=4.762z3y=3.088z4x=2.889z4y=11.817z5x=5.232z5y=4.616z6x=4.077z6y=10.821z7x=5.062z7y=3.470z8x=2.251z8y=7.546空车侧q=qk timin=tkimink1x=2.882k1y=1.266k2x=1.265k2y=4.238k3x=3.005k3y=-0.628k4x=-0.477k4y=5.102k5x=3.317k5y=1.289k6x=-0.036k6y=4.754k7x=3.642k7y=0.149k8x=-0.066k8y=3.3731x=2.4821y=0.3022x=-0.0012y=2.3143x=2.5913y=-1.7434x=-1.4634y=3.0875x=2.7595y=0.2916x=0.5046y=2.9017x=2.5947y=-0.8468x=-0.7428y=2.1211x=2.4831y=-0.0012x=0.5082y=2.7453x=2.5923y=-1.7414x=-1.4594y=2.3865x=2.7615y=0.2926x=0.5136y=2.9137x=2.6177y=-0.8458x=-1.1948y=2.1231x=0.8361y=0.9452x=0.9452y=0.83x=0.83y=1.094x=1.094y=1.1645x=1.1645y=1.0186x=1.0186y=1.2367x=1.2367y=1.1638x=1.1638y=1.091z1x=2.214z1y=2.568z2x=7.341z2y=5.612z3x=2.315z3y=0.756z4x=6.968z4y=7.735z5x=7.392z5y=2.455z6x=7.656z6y=7.238z7x=7.074z7y=1.457z8x=4.870z8y=4.928k1x=3.392k1y=0.756k2x=2.119k2y=2.314k3x=3.556k3y=-1.179k4x=0.484k4y=4.140k5x=3.827k5y=0.779k6x=2.181k6y=2.275k7x=3.642k7y=-0.327k8x=0.552k8y=2.754十二 最大折角、最小折角的计算与验算十二 最大折角、最小折角的计算与验算12.1 弦倾角12.2 最小折角 重车侧 空车侧 12.3 最大折角重车侧 十三 托索轮数、压索轮数的确定十四 承载索耐久性检查 十五 计算承载索无载挠度、有载挠度。十六 索道线路绘制十七 牵引索驱动机功率的选择与计算空车侧：1max=1x+1y=4.1482max=2x+2y=4.4333max=3x+3y=2.3774max=4x+4y=4.6245max=5x+5y=4.6066max=6x+6y=4.4567max=7x+7y=3.3158max=8x+8y=3.3061max=1x+1y=4.1482max=2x+2y=5.5033max=3x+3y=2.3974max=4x+4y=4.6255max=5x+5y=4.6066max=6x+6y=4,7187max=7x+7y=3.7918max=8x+8y=3.307十三 托索轮数、压索轮数的确定 衬垫材料比压值取k=0.3 每轮允许载荷p=kdd0=0.345022.5=3037.5n n=vp=848103037.5 取n=3十四 承载索耐久性检查 小车轮压 r=qm=8484=212mpa t最低=tmin-qch=11.919-1.65330.00519= 11.843mpa h=7-（-2）=9m c=0.0051 t=t最低f=0.0623 取e=9000kg/mm2 k=rt最低ekt=0.6