1、有瑞说明书毕业设计(此文档为word格式,下载后您可任意编辑修改!)摘 要术进行压力加工的设备。它是用于锻压、轴类零件的压装或校正、冷挤、冲压、弯曲、压块、粉沫冶金、成型等工艺过程的压力加工机械,与机械压力机相比,它具有压力和速度可在广泛的范围内无级调整,可在任意位置输出全部功率和保持所需压力,并能完成压制成型和定程成型等工艺方式,结构布局灵活,各执行机构动作可很方便地达到所希望的配合关系等优点;然而,该液压机也具有一定的缺点:它的机身刚度较小,由于用四立柱作导向,活动横梁内侧导向套与四立柱磨损后不易调整。本次设计采用软件与硬件相结合的方法,设计的液压机是YA321000KN四柱万能型,最大压
2、制力为100吨,液压最大工作压力为16MPa,它的加工工艺较其它类型液压机简单。主机为三梁四柱式结构,油缸由四柱导向,顶出缸布置于工作台中间孔内。各操纵调整机构均集中设置在操纵箱面板上,动力机构(包括电动机、泵、阀等元件)设置于右侧。根据给定的有关技术参数绘制液压机的动作线图,从动作线图上可以清楚的反映出各动作行程,速度和它们的配合关系,液压系统和电控系统的设计很重要,包括确定系统的执行元件(液压缸)的主要结构尺寸,绘制液压系统图,选择各类元件及辅件的形式和规格,确定系统的主要参数,进行必要的性能估算。电器控制采用可编程控制,实行以油为工作介质,其油缸工作过程由按钮集中操作,使液压速度可调。最
3、后进行液压机的总体设计。 此次设计目的明确,通过老师细心指导,自己查阅有关资料,及到实习工厂观察学习,顺利完成设计任务。通过这次设计培养了自己动手、综合运用多学科的理论知识和技能解决工程实际问题的能力,为以后实际工作打下基础。关键词:液压机;四柱;电器控制;液压缸AbstractThis design topic is a the shaping using the technology the equipment. It uses in the forging and stamping, the axis class components pressure installs or the a
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11、or the later practical work.Key words: -安全系数;4 D-油缸内径; d-活塞杆外径;-回程速度; -工进速度 已知=100 mms; =80 mms 所以 = 1.253.强度校核当只受轴向力推或拉力,可以近似地用直杆承受拉压载荷的简单强度计算公式进行计算: (4-23) =82.86 MPa 危险截面的合成应力: =5.5 MPa MPa主缸的总效率1.机械效率: 由活塞及活塞杆密封处的摩擦阻力所造成的摩擦损失,在额定压力下通常可取: =0.90.95, 这里取: =0.932.容积效率: 由各密封件的泄露所造成,当活塞密封为弹性材料时;取=0.98
12、3.反作用力效率:由排出口背压差所产生的反向作用力。 (4-24) =0.987 MPa -当活塞杆伸出是为进油压力,当活塞杆缩回是为排油压力-当活塞杆伸出时为排油压力,当活塞杆缩回时为进油压力= (4-25) = =0.981 MPa主缸的总效率: = (4-26) =0.930.980.98 =0.893 说明:该系统背压0.4 MPa顶出液压缸的设计材料顶出缸材料强度如表4.4所示表4.4顶出缸材料强度型号MPa MPa%35CrMo100085012顶出缸内径的设计1顶出液压缸内径:D= (4-27)=0.249m2顶出液压缸活塞杆径dd= (4-28)=0.145m3顶出液压缸有效面
13、积:A=D (4-29)=0.00785 m=79 cmA= ( D-d) (4-30)= (0.10-0.08)=0.0028 m=28 cmA=d (4-31)=0.08=0.0050 m=50 cm4顶出液压缸实际顶出力和回程力:R=PA (4-32)=25100.00785=21.4 MPaR=60KN5顶出液压缸的工作压力和回程工作压力:PA=25100.00785=196.3KNR=60KN6顶出液压缸的工作压力和回程压力:P=25 MPaP= (4-33)=21.4 MPa液压缸的理论作用力F F=45.59KN (4-34)取 =0.6; =0.90缸筒壁厚 公式: =+关于的
14、值,分别计算;当时,为薄壁缸筒=0.0134m (4-35)=83.3 mP-缸筒材料的许用应力 当0.3时,液压缸的安全系数: n=12 = =0.0156 m取 =0.025 m当时,材料使用不够经济,应改用高屈服强度的材料.顶出缸所受载荷如表4.5所示表4.5 缸筒所受载荷材料静载荷交变载荷冲击载荷不对称对称钢35812缸筒壁厚校核 额定工作压力, 应该低于一个极限值,以保证其安全. MPa (4-36)=0.35=100MPa=外径 D=内径 同时额定工作压力也应该完全塑性变形的发生: (4-37)=60.7672.9 MPa (4-38)=2.3850=2.38500.0888=17
15、3.6 MPa-缸筒完全塑性的变形压力, -材料屈服强度MPa缸筒的暴裂压力 (4-39) =204.24 MPa 缸筒底部厚度 缸筒底部为平面时: 0.433 (4-40) 0.433 mm 取 mm缸筒端部法兰厚度h (4-41) =12.72 mm 取 -安全系数;液压缸活塞杆往复运动时的速度比 = (4-47) 已知 =100 mms; =80 mms 所以 = 1.25D-油缸内径; d-活塞杆外径; -回程速度; -工进速度 取 d=0.22m 则 =1.24 ;3.强度校核当只受轴向力推或拉力,可以近似地用直杆承受拉压载荷的简单强度计算公式进行计算: (4-48) =82.86 MPa 危险截面的合成应力 :=2.7 MPa MPa顶出缸的总效率1.机械效率 由活塞及活塞杆密封处的摩擦阻力所造成的摩擦损失,在额定压力下,通常可取: =0.90.95 这里取: =0.932.容积效率 由
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