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1、凸轮机构设计1•设计题目如图2-J所示直动从动件盘形凸轮机构.其原始参数见表2-4从表2-1岀选择一纽凸轮机构的原始参数，搦此设计该凸轮机构。1S2-12•凸轮的推程运动方程，回程运动方程与远休止，近休止方程。a.推程运动方程0<(p<27r/3S=3O(l—cos(30/2))v=4569]sin(3^?/2)a=47.5691cos(3©/2)b.远休止运动方程27l/3<(p<7lS=h=60mmv=a=0a.回程运动方程7l<(P<37l/25=60(3-2^/^)v=-120©17Va=0b.近休止运动方程371/2<(p<271S=h=0v=0a=0计算机编程结果•推
2、杆位移图像xl=0:0.001:2*pi/3;x2=2*pi/3:0.001：pi;x3=pi:0・001:3*pi/2;x4=3*pi/2:0.001:2*pi;sl=30*(1-cos(3*xl/2))；s2=60;s3=60*(3-2*x3/pi);s4=0;holdonplot(xlzsi,1k1)；plot(x2,s2,1k1);plot(x3zs3,1k1);plot(x4,s4,1k1)；xlabel(1phi1)zylabel(1s1)title(1s-phi1)•推杆速度图像xl=0:0.001:2*pi/3;x2=2*pi/3:0.001：pi;x3=pi
3、:0.001:3*pi/2;x4=3*pi/2:0・001:2*pi;vl=45*sin(3*xl/2)；v2=0;v3=-1200/pi;v4=0;holdonplot(xl,vl,1k1)；plot(x2zv2,1k1)；plot(x3,v3,1k1);plot(x4zv4,1k1);xlabel('phi'),ylabel('v')title(1v-phi1)•推杆加速度图像xl=0:0.001:2*pi/3;x2=2*pi/3:0.001：pi;x3=pi:0・001:3*pi/2;x4=3*pi/2:0.001:2*pi;al=67.5*cos(3*xl/2)；a2
4、=0;a3=0;a4=0；holdonplot(xlzal,1k1)；plot(x2,a2,1k1)；plot(x3,a3,1k1);plot(x4,a4,1k1)；xlabel(1phi1)zylabel(1a1)title(1a-phi1)a-4>-8011111111012345674>凸轮机构的二-$线图，并依次确定凸轮的基圆半径和偏距d(p1•凸轮机构--5图像d(pxl=0:0・001®pi/3;x2=2*pi/3:0.001:7*pi/6;x3=7*pi/6:0.001:5*pi/3;x4=5*pi/3:0.001:2*pi；sl=30*(1-cos(3*xl/
5、2));s2=60;s3=60*(3-2*x3/pi);s4=0;vl=45*sin(3*xl/2)；v2=0;v3=-120/pi;v4=0;plot(vl,si,1k1,s2,1k1,v3，s3Jk",v4，s4Jk")xlabel(1ds/dphi1)zylabel(1s1)xlim([-60,100])；ylim([-100,100])axis([-100,100,-100,100])gridon2•确定凸轮的基圆半径和偏距由图可知：可取S°=80mm,e=20mm所以基圆半径=V802+202=82.5/n/n偏距e=20/h/h。3.滚子半径的确定及凸轮理论轮廓和实
6、际轮廓绘制h=60；w=l；e=20;rr=20;s0=80;q=120*pi/180；qs=(120+60)*pi/180；ql=(120+60+90)*pi/180;fori=l:1:120qq(i)=i*pi/180.0;sl=h/2-h/2*cos(pi*qq(i)/q);vl=(pi*w*h/q/2)*sin(pi*qq(i)/q);x(i)=(sO+sl)*cos(qq(i))-e*sin(qq(i))；y(i)=(s0+sl)*sin(qq(i))+e*cos(qq(i))；b(i)=(sO+sl)*cos(qq(i))-e*sin(qq(i))-vl*sin(qq
7、(i))；a(i)=-(sO+sl)*sin(qq(i))-e*cos(qq(i))+vl*cos(qq(i))；xx(i)=x(i)-rr*b(i)/sqrt(a(i)*a(i)+b(i)*b(i))；yy(i)=y(i)+rr*a(i)/sqrt(a(i)*a(i)+b(i)*b(i))；endfori=121:l:180qq(i)=i*pi/180；s2=h；v2=0;x(i)=(s0+s2)*cos(qq(i))-e*sin(qq(i))；y(i)=(s0+s2)*sin
