颚式破碎机设计说明书.doc

《颚式破碎机设计说明书.doc》由会员分享，可在线阅读，更多相关《颚式破碎机设计说明书.doc（23页珍藏版）》请在沃文网上搜索。

1、东北大学机械原理课程设计 铰链式颚式破碎机方案分析一.设计题目：铰链式颚式破碎机方案分析二.已知条件及设计要求2.1 已知条件 图1.1 六杆铰链式破碎机 图1.2 工艺阻力 图1.3 四杆铰链式破碎机图(a)所示为六杆铰链式破碎机方案简图。主轴1的转速为n1 = 170r/min，各部尺寸为：lO1A = 0.1m, lAB = 1.250m, lO3B = 1m, lBC = 1.15m, lO5C = 1.96m, l1=1m, l2=0.94m, h1=0.85m, h2=1m。各构件质量和转动惯量分别为：m2 = 500kg, Js2 = 25.5kgm2, m3 = 200kg,

2、Js3 = 9kgm2, m4 = 200kg, Js4 = 9kgm2, m5=900kg, Js5=50kgm2, 构件1的质心位于O1上，其他构件的质心均在各杆的中心处。D为矿石破碎阻力作用点，设LO5D = 0.6m，破碎阻力Q在颚板5的右极限位置到左极限位置间变化，如图(b)所示，Q力垂直于颚板。图(c)是四杆铰链式颚式破碎机方案简图。主轴1 的转速n1=170r/min。lO1A = 0.04m, lAB = 1.11m, l1=0.95m, h1=2m, lO3B=1.96m，破碎阻力Q的变化规律与六杆铰链式破碎机相同，Q力垂直于颚板O3B，Q力作用点为D，且lO3D = 0.6

3、m。各杆的质量、转动惯量为m2 = 200kg, Js2=9kgm2，m3 = 900kg, Js3=50kgm2。曲柄1的质心在O1 点处，2、3构件的质心在各构件的中心。2.2 设计要求试比较两个方案进行综合评价。主要比较以下几方面：1. 进行运动分析，画出颚板的角位移、角速度、角加速度随曲柄转角的变化曲线。2. 进行动态静力分析，比较颚板摆动中心运动副反力的大小及方向变化规律，曲柄上的平衡力矩大小及方向变化规律。3. 飞轮转动惯量的大小。三.机构的结构分析3.1六杆铰链式破碎机六杆铰链式粉碎机拆分为机架和主动件，构件组成的RRR杆组，构件组成的RRR杆组。+ +3.2四杆铰链式破碎机四杆

4、铰链式破碎机拆分为机架和主动件，构件组成的RRR杆组。+ 四.机构的运动分析4.1六杆铰链式颚式破碎机的运动分析。1) 调用bark函数求主动件的运动参数。形式参数n1n2n3kr1r2gametwepvpap实 值1201r120.00.0twepvpap2）调用rrrk函数求、构件组成的RRR杆组进行运动分析。形式参数mn1n2n3k1k2r1r2t wepvpap实 值142332r34r23twepvpap3） 调用rrrk函数对、构件组成的RRR杆组进行运动分析。形式参数mn1n2n3k1k2r1r2t wepvpap实 值136545r35R56twepvpap4.2编写主程序并运

5、行。按一定的步长，改变主动件的位置角度，使其在0-360变化，便可求出机构各点在整个运动循环内的运动参数并打印输出。（1） 主程序。#include graphics.h#include subk.c#include draw.cmain()static double p202,vp202,ap202,del;static double t10,w10,e10,tdraw370,wdraw370,edraw370;static int ic;double r12,r23,r34,r35,r56;double pi,dr;int i;FILE *fp;r12=0.1; r23=1.250; r3

6、4=1.0;r35=1.15; r56=1.96； del=15.0；pi=4.0*atan(1.0);dr=pi/180.0; w1=-170*2*pi/60;p11=0.0;p12=0.0;p41=0.94;p42=-1.0;p61=-1.0;p62=0.85;printf( n TheKinematic Parametersof member 5n);printf(No THETA1 t5 w5 e5n);printf( deg rad rad/s rad/s/sn);if(fp=fopen(file1,w)=NULL)printf( Cant open this file.n);exi

7、t(0);fprintf(fp, n The Kinematic Parameters of member 5n);fprintf(fp,No THETA1 t5 w5 e5n);fprintf(fp, deg rad rad/s rad/s/s);ic=(int)(360.0/del);for(i=0;i=ic;i+) t1=(-i)*del*dr;bark(1,2,0,1,r12,0.0,0.0,t,w,e,p,vp,ap);rrrk(1,4,2,3,3,2,r34,r23,t,w,e,p,vp,ap);rrrk(1,3,6,5,4,5,r35,r56,t,w,e,p,vp,ap);pri

8、ntf(n%2d %12.3f%12.3f%12.3f%12.3f,i+1,t1/dr,t5,w5,e5);fprintf(fp,n%2d %12.3f%12.3f%12.3f%12.3f,i+1,t1/dr,t5,w5,e5);tdrawi=t5;wdrawi=w5;edrawi=e5; if(i%16)=0)getch();fclose(fp);getch();draw1(del,tdraw,wdraw,edraw,ic);（2） 运行结果。杆件5的运动参数：The Kinematic Parameters of member 5：No THETA1 t5 w5 e5deg rad rad

9、/s rad/s/s 1 0.000 -1.658 0.346 3.956 2 -15.000 -1.653 0.392 2.002 3 -30.000 -1.647 0.400 -0.932 4 -45.000 -1.641 0.362 -4.355 5 -60.000 -1.637 0.274 -7.506 6 -75.000 -1.633 0.146 -9.612 7 -90.000 -1.632 -0.001 -10.183 8 -105.000 -1.633 -0.145 -9.165 9 -120.000 -1.637 -0.265 -6.90410 -135.000 -1.641

10、 -0.345 -3.98111 -150.000 -1.646 -0.382 -1.00812 -165.000 -1.652 -0.377 1.51913 -180.000 -1.657 -0.341 3.29714 -195.000 -1.662 -0.284 4.23715 -210.000 -1.666 -0.220 4.43616 -225.000 -1.668 -0.156 4.12117 -240.000 -1.670 -0.10 3.58418 -255.000 -1.671 -0.051 3.10519 -270.000 -1.672 -0.007 2.89820 -285

11、.000 -1.672 0.036 3.06321 -300.000 -1.671 0.085 3.57122 -315.000 -1.669 0.142 4.24723 -330.000 -1.667 0.209 4.79124 -345.000 -1.663 0.281 4.81725 -360.000 -1.658 0.346 3.956运动图形：4.3四杆铰链式颚式破碎机的运动分析。1）调用bark函数求主动件的运动参数。形式参数n1n2n3kr1r2gametwepvpap实 值1201r120.00.0twepvpap2）调用rrrk函数求、构件组成的RRR杆组进行运动分析。形式参

12、数mn1n2n3k1k2r1r2t wepvpap实 值124323r23r34twepvpap4.4编写主程序并运行。按一定的步长，改变主动件的位置角度，使其在0-360变化，便可求出机构各点在整个运动循环内的运动参数并打印输出。(1)主程序。#include graphics.h#include subk.c#include draw.cmain()static double p202,vp202,ap202,del;static double t10,w10,e10,tdraw370,wdraw370,edraw370;static int ic;double r12,r23,r34;d

13、ouble pi,dr;int i;FILE *fp;r12=0.04; r23=1.11; r34=1.96；del=15.0;pi=4.0*atan(1.0);w1=-170*2*pi/60;e1=0.0;dr=pi/180.0;p11=0.0;p12=0.0; p41=-0.95; p42=2.0;printf( n TheKinematic Parametersof member 3n);printf(No THETA1 t3 w3 e3n);printf( deg rad rad/s rad/s/sn);if(fp=fopen(file2,w)=NULL)printf( Cant o

14、pen this file.n);exit(0);fprintf(fp, n The Kinematic Parameters of member 3n);fprintf(fp,No THETA1 t3 w3 e3n);fprintf(fp,deg rad rad/s rad/s/s);ic=(int)(360.0/del);for(i=0;i=ic;i+) t1=(-i)*del*dr;bark(1,2,0,1,r12,0.0,0.0,t,w,e,p,vp,ap);rrrk(1,2,4,3,2,3,r23,r34,t,w,e,p,vp,ap);printf(n%2d %12.3f%12.3f

15、%12.3f%12.3f,i+1,t1/dr,t3,w3,e3);fprintf(fp,n%2d %12.3f%12.3f%12.3f%12.3f,i+1,t1/dr,t3,w3,e3);tdrawi=t3;wdrawi=w3;edrawi=e3; if(i%16)=0)getch();fclose(fp);getch();draw1(del,tdraw,wdraw,edraw,ic);(2)运行结果。杆件3的运动参数：The Kinematic Parameters of member 3：No THETA1 t3 w3 e3deg rad rad/s rad/s/s 1 0.000 -1.

16、632 0.014 -6.232 2 -15.000 -1.632 -0.077 -6.098 3 -30.000 -1.634 -0.163 -5.591 4 -45.000 -1.637 -0.240 -4.731 5 -60.000 -1.641 -0.301 -3.553 6 -75.000 -1.646 -0.343 -2.117 7 -90.000 -1.651 -0.362 -0.501 8 -105.000 -1.656 -0.357 1.192 9 -120.000 -1.661 -0.327 2.84810 -135.000 -1.666 -0.274 4.33911 -1

17、50.000 -1.669 -0.201 5.54412 -165.000 -1.671 -0.113 6.35813 -180.000 -1.672 -0.016 6.70314 -195.000 -1.672 0.082 6.54515 -210.000 -1.670 0.174 5.89416 -225.000 -1.667 0.253 4.80717 -240.000 -1.663 0.313 3.38418 -255.000 -1.658 0.351 1.74619 -270.000 -1.653 0.364 0.03020 -285.000 -1.647 0.352 -1.6392

18、1 -300.000 -1.642 0.317 -3.14922 -315.000 -1.638 0.261 -4.41523 -330.000 -1.635 0.189 -5.37524 -345.000 -1.632 0.105 -5.98825 -360.000 -1.632 0.014 -6.232运动图形：五.机构的动态静力分析5.1六杆铰链式颚式破碎机的动态静力分析。（1）求质点7，8，9，10及矿石破碎产生阻力的作用点11的运动参数；调用bark函数对质点7进行运动分析： 形式参数n1n2n3kr1r2gametwepvpap实 值20720.0r270.0twepvpap调用b

19、ark函数对质点8进行运动分析： 形式参数n1n2n3kr1r2gametwepvpap实 值40830.0r480.0twepvpap调用bark函数对质点9进行运动分析： 形式参数n1n2n3kr1r2gametwepvpap实 值30940.0r390.0twepvpap调用bark函数对质点10进行运动分析： 形式参数n1n2n3kr1r2gametwepvpap实 值601050.0r6100.0twepvpap调用bark函数对质点11进行运动分析： 形式参数n1n2n3kr1r2gametwepvpap实 值601150.0r6110.0twepvpap（2）调用rrrf函数对、

20、构件构成的RRR杆组进行动态静力分析：形式参数n1n2n3ns1ns2nn1nn2nexfk1实 值365910011114形式参数k2pvpaptwefr实 值5pvpaptwefr（3）调用rrrf函数对、构件构成的RRR杆组进行动态静力分析：形式参数n1n2n3ns1ns2nn1nn2nexfk1实 值423873003形式参数k2pvpaptwefr实 值2pvpaptwefr（4）调用barf函数对主动件1进行动态静力分析：形式参数n1ns1nn1k1papefrtb 实 值1121papefr&tb5.2编写主程序并运行。按一定的步长，改变主动件的位置角度，使其在0-360变化，便

21、可求出机构各运动副反力及作用在主动件上的平衡力矩。（1）主程序。#include graphics.h#include subk.c#include subf.c#include draw.cmain() static double p202,vp202,ap202,del; static double sita1370,fr1draw370,sita2370,fr2draw370,sita3370,fr3draw370,tbdraw370,tb1draw370; static double fr202,fe202,t10,w10,e10; static int ic; double r12,

22、r23,r34,r35,r56,r27,r48,r39,r610,r611; int i; double pi,dr; double fr1,bt1,fr4,bt4,fr6,bt6,we1,we2,we3,we4,we5,tb,tb1; FILE*fp; sm1=0.0;sm2=500.0;sm3=200.0;sm4=200.0;sm5=900.0; sj1=0.0;sj2=25.5;sj3=9.0;sj4=9.0;sj5=50.0; r12=0.1; r23=1.25; r34=1.0; r35=1.15;r56=1.96; r27=r23/2; r48=r34/2; r39=r35/2;r

23、610=r56/2;r611=0.6; pi=4.0*atan(1.0); dr=pi/180.0; w1=-170*2*pi/60; e1=0.0; del=15; p11=0.0; p12=0.0; p41=0.94; p42=-1.0; p61=-1.0; p62=0.85; printf(n The Kineto-static Analysis of a Six-bar Linkasen);printf( NO THETA1 FR6 BT6 TB TB1n);printf( (deg.) (N) (deg.) (N.m) (N.m)n); if(fp=fopen(FILE3,w)=NU

24、LL) printf(Cant open this file./n); exit(0); fprintf(fp,n The Kineto-static Analysis of a Six-bar Linkasen);fprintf(fp,NO THETA1 FR6 BT6 TB TB1n );fprintf(fp, (deg.) (N) (deg.) (N.m) (N.m)n ); ic=(int)(360.0/del); for(i=0;i=ic;i+) t1=(-i)*del*dr; bark(1,2,0,1,r12,0.0,0.0,t,w,e,p,vp,ap); rrrk(1,4,2,3

25、,3,2,r34,r23,t,w,e,p,vp,ap); rrrk(1,3,6,5,4,5,r35,r56,t,w,e,p,vp,ap); bark(2,0,7,2,0.0,r27,0.0,t,w,e,p,vp,ap); bark(4,0,8,3,0.0,r48,0.0,t,w,e,p,vp,ap); bark(3,0,9,4,0.0,r39,0.0,t,w,e,p,vp,ap); bark(6,0,10,5,0.0,r610,0.0,t,w,e,p,vp,ap); bark(6,0,11,5,0.0,r611,0.0,t,w,e,p,vp,ap); rrrf(3,6,5,9,10,0,11,

26、11,4,5,p,vp,ap,t,w,e,fr); rrrf(4,2,3,8,7,3,0,0,3,2,p,vp,ap,t,w,e,fr); barf(1,1,2,1,p,ap,e,fr,&tb); fr1=sqrt(fr11*fr11+fr12*fr12); bt1=atan2(fr12,fr11); fr4=sqrt(fr41*fr41+fr42*fr42); bt4=atan2(fr42,fr41); fr6=sqrt(fr61*fr61+fr62*fr62); bt6=atan2(fr62,fr61); we1=-(ap11*vp11+(ap12+9.81)*vp12)*sm1-e1*w

27、1*sj1; we2=-(ap71*vp71+(ap72+9.81)*vp72)*sm2-e2*w2*sj2; we3=-(ap81*vp81+(ap82+9.81)*vp82)*sm3-e3*w3*sj3; we4=-(ap91*vp91+(ap92+9.81)*vp92)*sm4-e4*w4*sj4; extf(p,vp,ap,t,w,e,11,fe); we5=-(ap101*vp101+(ap102+9.81)*vp102)*sm5-e5*w5*sj5+fe111*vp111+fe112*vp112; tb1=-(we1+we2+we3+we4+we5)/w1;printf(%3d %

28、10.3f %10.3f %10.3f %10.3f %10.3f n,i+1,t1/dr,fr6,bt6/dr,tb,tb1);fprintf(fp,%3d %10.3f %10.3f %10.3f %10.3f %10.3f n,i+1,t1/dr,fr6,bt6/dr,tb,tb1)； tbdrawi=tb;tb1drawi=tb1;fr1drawi=fr1;sita1i=bt1; fr2drawi=fr4;sita2i=bt4; fr3drawi=fr6;sita3i=bt6; if(i%16)=0)getch(); fclose(fp); getch(); draw2(del,tbd

29、raw,tb1draw,ic); draw3(del,sita1,fr1draw,sita2,fr2draw,sita3,fr3draw,ic); #include math.hextf(p,vp,ap,t,w,e,nexf,fe) double p202,vp202,ap202,t10,w10,e10,fe202; double pi,dr; pi=4.0*atan(1.0);dr=pi/180.0; if(w50) fenexf1=(-t1/dr-90.0)*(85000.0/182.0)*cos(-t5-pi/2); fenexf2=(-t1/dr-90.0)*(85000.0/182.

30、0)*sin(-t5-pi/2); elsefenexf1=0;fenexf2=0; （2）运行结果： The Kineto-static Analysis of a Six-bar Linkase：NO THETA1 FR6 BT6 TB TB1 (deg.) (N) (deg.) (N.m) (N.m) 1 0.000 9904.580 77.690 534.273 534.273 2 -15.000 10248.086 82.670 1038.104 1038.104 3 -30.000 10522.852 89.576 1434.513 1434.513 4 -45.000 10757

31、.314 97.329 1547.760 1547.760 5 -60.000 10967.175 104.339 1270.987 1270.987 6 -75.000 11112.158 109.009 644.228 644.228 7 -90.000 11132.496 110.330 -144.608 -144.608 8 -105.000 12694.785 130.968 -883.503 -883.503 9 -120.000 15067.304 144.368 -1406.751 -1406.751 10 -135.000 17747.445 153.528 -1623.93

32、2 -1623.932 11 -150.000 20694.648 160.499 -1555.124 -1555.124 12 -165.000 24022.489 166.115 -1286.981 -1286.981 13 -180.000 27824.537 170.602 -923.989 -923.989 14 -195.000 32106.137 174.034 -557.444 -557.444 15 -210.000 36785.996 176.536 -253.496 -253.496 16 -225.000 41731.070 178.304 -51.307 -51.30

33、7 17 -240.000 46795.855 179.558 36.912 36.912 18 -255.000 51853.137 -179.507 26.634 26.634 19 -270.000 56814.061 -178.745 -39.410 -39.410 20 -285.000 8481.823 78.617 -205.306 -205.306 21 -300.000 8583.465 77.292 -338.729 -338.729 22 -315.000 8793.293 75.658 -361.459 -361.459 23 -330.000 9113.158 74.

34、602 -227.576 -227.576 24 -345.000 9506.210 75.059 80.824 80.824 25 -360.000 9904.580 77.690 534.273 534.273 （3）平衡力矩曲线：(4)反力的矢端图曲线：5.3四杆铰链式颚式破碎机的动态静力分析。（1）求质点5，6及矿石破碎产生阻力的作用点7的运动参数；调用bark函数对质点5进行运动分析： 形式参数n1n2n3kr1r2gametwepvpap实 值20520.0r250.0twepvpap调用bark函数对质点6进行运动分析： 形式参数n1n2n3kr1r2gametwepvpap实 值40630.0r460.0twepvpap调用bark函数