东北大学机械原理课程设计铰链式颚式破碎机方案分析

机械原理课程设计说明书题目：铰链式颚式破碎机方案分析班级：机械1003******学号：*******成绩：2012年9 月12 日目录一设计题目 (1)二已知条件及设计要求 (1)2.1已知条件 (1)2.2设计要求 (2)三. 机构的结构分析 (2)3.1六杆铰链式破碎机 (2)3.2四杆铰链式破碎机 (2)四. 机构的运动分析 (3)4.1六杆铰链式颚式破碎机的运动分析 (3)4.2四杆铰链式颚式破碎机的运动分析 (5)五.机构的动态静力分析 (8)5.1六杆铰链式颚式破碎机的静力分析 (8)5.2四杆铰链式颚式破碎机的静力分析 (13)六. 工艺阻力函数及飞轮的转动惯量函数 (17)6.1工艺阻力函数程序 (17)6.2飞轮的转动惯量函数程序 (18)七 .对两种机构的综合评价 (22)八 . 主要的收获和建议 (23)九 . 参考文献 (23)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(a)所示为六杆铰链式破碎机方案简图。

主轴1的转速：n1 = 170r/min。

已知尺寸：固定铰链坐标：P1x=1.0m=1.0m;P4x =1.94,P4y=0.0;P6x=0.0,P6y=1.85;杆长：r12=0.1m, r23=1.25m, r34 =1.15m, r56=1.96m, r611=2.5 m, 质心均在各杆的中心处.构件质量：m1=0.0 kg, m2=500.0kg, m3=200.0kg, m4=200.0kg, m5=900.0kg.构件转动惯量：J1=0.0kg, J2=25.5kg, J3=9.0kg, J4=9.0kg, J5=50kg, L O5D = 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。

已知尺寸：固定铰链坐标：P1x=0.0m，P1y =2.0；P4x=0.0,P4y=1.85;杆长：r12=0.04m, r23=1.11m, r34 =1.96m, r411=0.6 m,曲柄1的质心在O1点处,质心均在各杆的中心处.构件质量：m1=0.0 kg, m2=200.0kg, m3=900.0kg.构件转动惯量：J1=0.0kg, J2=9.0kg, J3=50kg.(a) 六杆铰链式破碎机(b) 工艺阻力(c) 四杆铰链式破碎机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++3.2四杆铰链式破碎机+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2点的运动参数（2）调用rrrk函数求3点的运动参数（3）调用rrrk函数求5点的运动参数（4）程序:对5点的运动轨迹分析#include "graphics.h"#include "subk.c"#include "draw.c"main(){static double p[20][2],vp[20][2],ap[20][2],del;static double t[10],w[10],e[10],pdraw[370],vpdraw[370],apdraw[370];static int ic;double r12,r34,r23,r56,r35,r611;double pi,dr;int i;FILE *fp;r12=0.1; r34=1.0; r23=1.250;r56=1.96; r35=1.15; r611=0.6;pi=4.0*atan(1.0);dr=pi/180.0;w[1]=-170*2*pi/60; e[1]=0.0; del=5.0;p[6][1]=0.0; p[6][2]=1.85;p[1][1]=1.0; p[1][2]=0.85;p[4][1]=1.94; p[4][2]=0.0;printf(" \n The Kinematic Parameters of Point 11\n");printf("No THETA1 t11 w11 e11\n");printf(" deg rad rad/s rad/s/s\n");if((fp=fopen("file6","w"))==NULL){printf(" Can't open this file.\n");exit(0);}fprintf(fp," \n The Kinematic Parameters of Point 11\n"); fprintf(fp,"No THETA1 t11 w11 e11\n"); fprintf(fp," deg rad rad/s rad/s/s");ic=(int)(360.0/del);for(i=0;i<=ic;i++){t[1]=(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);bark(6,0,11,5,0.0,r611,0.0,t,w,e,p,vp,ap);printf("\n%2d %12.3f%12.3f%12.3f%12.3f",i+1,t[1]/dr,t[5],w[5],e[5]);fprintf(fp,"\n%2d %12.3f%12.3f%12.3f%12.3f",i+1,t[1]/dr,t[5],w[5],e[5]);pdraw[i]=t[5];vpdraw[i]=w[5];apdraw[i]=e[5];if((i%16)==0){getch();}}fclose(fp);getch();draw1(del,pdraw,vpdraw,apdraw,ic);}（5）数据:随主动件1变化的运动参数The Kinematic Parameters of Point 11No THETA1 t11 w11 e11deg rad rad/s rad/s/s1 0.000 -1.617 0.640 4.4172 15.000 -1.626 0.557 6.7533 30.000 -1.633 0.448 7.8344 45.000 -1.639 0.331 8.0305 60.000 -1.643 0.214 7.7746 75.000 -1.645 0.102 7.4237 90.000 -1.646 -0.005 7.1918 105.000 -1.645 -0.110 7.1409 120.000 -1.643 -0.215 7.19010 135.000 -1.639 -0.321 7.15611 150.000 -1.633 -0.424 6.78812 165.000 -1.626 -0.518 5.82313 180.000 -1.618 -0.592 4.05014 195.000 -1.609 -0.632 1.36715 210.000 -1.600 -0.628 -2.15616 225.000 -1.591 -0.566 -6.23117 240.000 -1.583 -0.444 -10.33018 255.000 -1.578 -0.266 -13.72919 270.000 -1.576 -0.048 -15.64520 285.000 -1.577 0.184 -15.48221 300.000 -1.581 0.397 -13.10422 315.000 -1.588 0.561 -8.96923 330.000 -1.597 0.656 -4.00924 345.000 -1.607 0.680 0.71925 360.000 -1.617 0.640 4.417（6）线图:5点水平位移，速度，加速度线图六杆机构颚板角位置、角速度、角加速度随曲柄转角的变化曲线4.2四杆铰链式颚式破碎机的运动分析（1）调用bark函数求2点的运动参数形参n1 n2 n3 k r1 r2 gam t w e p vp ap实参 1 2 0 1 r12 0.0 0.0 t w e p vp ap （2）调用rrrk函数求3点的运动参数形参m n1 n2 n3 k1k2r1 r2 t w e p vp ap 实参 1 2 4 3 2 3 r23r34t w e p vp ap（3）程序：对3点的运动轨迹分析#include "graphics.h"#include "subk.c"#include "draw.c"main(){static double p[20][2],vp[20][2],ap[20][2],del;static double t[10],w[10],e[10],pdraw[370],vpdraw[370],apdraw[370];static int ic;double r12,r34,r23,r47;double pi,dr;int i;FILE *fp;r12=0.04; r23=1.11;r34=1.96; r47=0.6;pi=4.0*atan(1.0);dr=pi/180.0;w[1]=-170*2*pi/60; e[1]=0.0; del=15.0;p[4][2]=-0.95;p[4][1]=2.0;p[1][1]=0.0;p[1][2]=0.0;printf(" \n The Kinematic Parameters of Point7 \n");printf("No THETA1 t3 w3 e3\n");printf(" deg rad rad/s rad/s/s\n");if((fp=fopen("file1","w"))==NULL){printf(" Can't open this file.\n");exit(0);}fprintf(fp," \n The Kinematic Parameters of Point 3\n");fprintf(fp,"No THETA1 t3 w3 e3\n");fprintf(fp," deg rad rad/s rad/s/s");ic=(int)(360.0/del);for(i=0;i<=ic;i++){t[1]=(-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);bark(4,0,7,3,0.0,r47,0.0,t,w,e,p,vp,ap);printf("\n%2d %12.3f%12.3f%12.3f%12.3f",i+1,t[1]/dr, t[3],w[3],e[3]);fprintf(fp,"\n%2d %12.3f%12.3f%12.3f%12.3f",i+1,t[1]/dr,t[3],w[3],e[3]);pdraw[i]=t[3];vpdraw[i]=w[3];apdraw[i]=e[3];if((i%16)==0){getch();}}fclose(fp);getch();draw1(del,pdraw,vpdraw,apdraw,ic);}（4）数据：随主动件1变化的运动参数The Kinematic Parameters of Point 3No THETA1 t3 w3 e3 deg rad rad/s rad/s/s1 0.000 2.157 0.224 5.2752 -15.000 2.161 0.292 3.9683 -30.000 2.166 0.339 2.3984 -45.000 2.171 0.362 0.6965 -60.000 2.176 0.360 -1.0056 -75.000 2.181 0.333 -2.5887 -90.000 2.186 0.285 -3.9588 -105.000 2.190 0.218 -5.0429 -120.000 2.192 0.138 -5.79310 -135.000 2.194 0.050 -6.18211 -150.000 2.194 -0.042 -6.19512 -165.000 2.192 -0.131 -5.83113 -180.000 2.190 -0.211 -5.10414 -195.000 2.186 -0.279 -4.04415 -210.000 2.182 -0.329 -2.70016 -225.000 2.177 -0.358 -1.14317 -240.000 2.171 -0.362 0.53418 -255.000 2.166 -0.342 2.21819 -270.000 2.161 -0.297 3.78820 -285.000 2.158 -0.232 5.11821 -300.000 2.155 -0.149 6.09422 -315.000 2.153 -0.054 6.62823 -330.000 2.153 0.044 6.66724 -345.000 2.155 0.139 6.20225 -360.000 2.157 0.224 5.275 （6）线图:3点水平位移，速度，加速度线图四杆机构颚板角位置、角速度、角加速度随曲柄转角的变化曲线五.机构的动态静力分析5.1六杆铰链式颚式破碎机的静力分析（1）、（2）、（3）步同运动分析1、2、3（4）调用bark函数求7的运动参数形参n1 n2 n3 k r1 r2 gam t w e p vp ap 实参 2 0 7 2 0.0r270.0 t w e p vp ap （5）调用bark函数求8的运动参数形参n1 n2 n3 k r1 r2 gam t w e p vp ap 实参 4 0 8 3 0.0r480.0 t w e p vp ap （6）调用bark函数求9的运动参数形参n1 n2 n3 k r1 r2 gam t w e p vp ap 实参 3 0 9 4 0.0r390.0 t w e p vp ap （7）调用bark函数求10的运动参数形参n1 n2 n3 k r1 r2 gam t w e p vp ap 实参 6 0 10 5 0.0r6100.0 t w e p vp ap （8）调用bark函数求11的运动参数形参n1 n2 n3 k r1 r2 gam t w e p vp ap（9）调用rrrf对4、5杆件组成的rrr杆组进行静力分析（10）调用rrrf对2、3杆组成的rrr杆组进行静力分析（11）调用barf对主动件1进行静力分析（12）程序：对质心的运动分析，对固定铰链的静态动力分析，主动反力偶#include "graphics.h"#include "subk.c"#include "subf.c"#include "math.h"#include "draw.c"main(){static double p[20][2],vp[20][2],ap[20][2],del;static double t[10],w[10],e[10];static double bt6draw[370],fr6draw[370],tbdraw[370],tb1draw[370];static double fr[20][2],fe[20][2];static int ic;double r12,r23,r34,r35,r56;double r27,r48,r39,r610,r611;int i;double pi,dr,fr6,bt6,we1,we2,we3,we4,we5,tb,tb1;FILE*fp;sm[1]=0.0; sm[2]=500.0; sm[3]=200.0; sm[4]=200.0; sm[5]=900.0;sj[1]=0.0; sj[2]=25.5; sj[3]=9.0; sj[4]=9.0; sj[5]=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;r610=r56/2;r611=0.6;pi=4.0*atan(1.0);dr=pi/180.0;w[1]=-170*2*pi/60; e[1]=0.0; del=5.0;p[1][1]=1.0; p[1][2]=1.0;p[4][1]=1.94; p[4][2]=0.0;p[6][1]=0.0; p[6][2]=1.85;printf("\n The Kineto-static Analysis of a Six-bar Linkase\n");printf(" NO THETA1 FR6 BT6 TB TB1\n");printf(" (deg.) (N) (deg.) (N.m) (N.m)\n");if((fp=fopen("file6","w"))==NULL){printf("Can't open this file./n");exit(0);}fprintf(fp,"\n The Kineto-static Analysis of a Six-barLinkase\n");fprintf(fp," NO THETA1 FR6 BT6 TB TB1\n");fprintf(fp," (deg.) (N) (deg.) (N.m) (N.m)\n");ic=(int)(360.0/del);for(i=0;i<=ic;i++){t[1]=(-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);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(3,6,5,9,10,0,11,11,4,5,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);fr6=sqrt(fr[6][1]*fr[6][1]+fr[6][2]*fr[6][2]);bt6=atan2(fr[6][2],fr[6][1]);we1=-(ap[1][1]*vp[1][1]+(ap[1][2]+9.81)*vp[1][2])*sm[1]-e[1]*w[1]*sj[1];we2=-(ap[7][1]*vp[7][1]+(ap[7][2]+9.81)*vp[7][2])*sm[2]-e[2]*w[2]*sj[2];we3=-(ap[8][1]*vp[8][1]+(ap[8][2]+9.81)*vp[8][2])*sm[3]-e[3]*w[3]*sj[3];we4=-(ap[9][1]*vp[9][1]+(ap[9][2]+9.81)*vp[9][2])*sm[4]-e[4]*w[4]*sj[4]; extf(p,vp,ap,t,w,e,11,fe);we5=-(ap[10][1]*vp[10][1]+(ap[10][2]+9.81)*vp[10][2])*sm[5]-e[5]*w[5]*sj[5]+fe[11][1]*vp[11][1]+fe[11][2]*vp[11][2];tb1=-(we1+we2+we3+we4+we5)/w[1];printf(" %3d%6.0f%11.3f%11.3f%11.3f%11.3f\n",i,t[1]/dr,fr6,bt6/dr,tb,tb1,);fprintf(fp," %3d%6.0f%11.3f%11.3f%11.3f%11.3f\n",i,t[1]/dr,fr6,bt6/dr,tb,tb1,); tbdraw[i]=tb;tb1draw[i]=tb1;fr6draw[i]=fr6;bt6draw[i]=bt6;if((i%16)==0){getch();}}fclose(fp);getch();draw2(del,tbdraw,tb1draw,ic);draw3(del,bt6draw,fr6draw,ic);}extf(p,vp,ap,t,w,e,nexf,fe)double p[20][2],vp[20][2],ap[20][2],t[10],w[10],e[10],fe[20][2];{double pi,dr;pi=4.0*atan(1.0);dr=pi/180.0;if(w[5]<0){fe[nexf][1]=(-t[1]/dr-90.0)*(85000.0/182.0)*cos(-t[5]-pi/2);fe[nexf][2]=-(-t[1]/dr-90.0)*(85000.0/182.0)*sin(-t[5]-pi/2);}else{fe[nexf][1]=0;fe[nexf][2]=0;}}（13）数据：6点固定铰链力矢；主动件平衡力偶The Kineto-static Analysis of a Six-bar LinkaseNO THETA1 FR6 BT6 TB TB1(deg.) (N) (deg.) (N.m) (N.m)0 0 9904.580 77.690 534.273 534.2731 -15 10248.086 82.670 1038.104 1038.1042 -30 10522.852 89.576 1434.513 1434.5133 -45 10757.314 97.329 1547.760 1547.7604 -60 10967.175 104.339 1270.987 1270.9875 -75 11112.158 109.009 644.228 644.2286 -90 11132.496 110.330 -144.608 -144.6087 -105 13356.757 128.454 -883.773 -883.7738 -120 16176.401 139.007 -1407.830 -1407.8309 -135 19186.867 145.561 -1626.344 -1626.34410 -150 22374.519 150.172 -1559.245 -1559.24511 -165 25846.624 153.746 -1292.854 -1292.85412 -180 29700.830 156.609 -931.213 -931.21313 -195 33968.451 158.869 -565.243 -565.24314 -210 38602.952 160.602 -260.954 -260.95415 -225 43497.372 161.905 -57.628 -57.62816 -240 48515.553 162.900 32.265 32.26517 -255 53525.123 163.703 23.978 23.97818 -270 58424.813 164.412 -39.809 -39.80919 -285 8481.823 78.617 -205.306 -205.30620 -300 8583.465 77.292 -338.729 -338.72921 -315 8793.293 75.658 -361.459 -361.45922 -330 9113.158 74.602 -227.576 -227.57623 -345 9506.210 75.059 80.824 80.82424 -360 9904.580 77.690 534.273 534.273 （14）线图：6点固定铰链力矢；主动件平衡力偶六杆机构曲柄上的平衡力矩的变化规律六杆机构颚板摆动中心运动副反力的大小及方向变化规律5.2四杆铰链式颚式破碎机的静力分析（1）、（2）步同运动分析1、2（3）、调用bark函数对5点进行运动分析形参n1 n2 n3 k r1 r2 gam t w e p vp ap实参 2 0 5 2 0.0r250.0 t w e p vp ap （4）、调用bark函数对6点进行运动分析形参n1 n2 n3 k r1 r2 gam t w e p vp ap实参 3 0 6 3 0.0r360.0 t w e p vp ap （5）、调用bark函数对7点进行运动分析形参n1 n2 n3 k r1 r2 gam t w e p vp ap实参 4 0 7 3 0.0r470.0 t w e p vp ap （6）、调用rrrf函数对2、3杆进行静力分析形参n1 n2 n3 ns1ns2 nn1 nn2nexf k1 k2 t w e p vp ap实参 2 4 3 7 80 3 0 2 3 t w e p vp ap （7）、调用barf函数对主动件1进行静力分析形参n1 ns1 nn1 k1 p ap e fr tb实参 1 1 2 1 p ap e fr tb（8）、程序：对质心的运动分析，对固定铰链的静态动力分析，主动反力偶#include "graphics.h"#include "subk.c"#include "subf.c"#include "math.h"#include "draw.c"main(){static double p[20][2],vp[20][2],ap[20][2],del;static double t[10],w[10],e[10];static double bt4draw[370],fr4draw[370],tbdraw[370],tb1draw[370]; static double fr[20][2],fe[20][2];static int ic;double r12,r23,r34;double r25,r36,r47;int i;double pi,dr,fr4,bt4,we1,we2,we3,tb,tb1;FILE*fp;sm[1]=0.0; sm[2]=200.0; sm[3]=900.0;sj[1]=0.0; sj[2]=9.0; sj[3]=50.0;r12=0.04; r23=1.11; r34=1.96;r25=r23/2;r36=r34/2;r47=0.6;pi=4.0*atan(1.0);dr=pi/180.0;w[1]=-170*2*pi/60; e[1]=0.0; del=5.0;p[1][1]=0.0; p[1][2]=0.0;p[4][1]=-0.95; p[4][2]=2.0;printf("\n The Kineto-static Analysis of a Six-bar Linkase\n"); printf(" NO THETA1 FR4 BT4 TB TB1\n");printf(" (deg.) (N) (deg.) (N.m) (N.m)\n");if((fp=fopen("file4","w"))==NULL){printf("Can't open this file./n");exit(0);}fprintf(fp,"\n The Kineto-static Analysis of a Six-bar Linkase\n");fprintf(fp," NO THETA1 FR4 BT4 TB TB1\n");fprintf(fp," (deg.) (N) (deg.) (N.m) (N.m)\n");ic=(int)(360.0/del);for(i=0;i<=ic;i++){t[1]=(-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);bark(2,0,5,2,0.0,r25,0.0,t,w,e,p,vp,ap);bark(3,0,6,3,0.0,r36,0.0,t,w,e,p,vp,ap);bark(4,0,7,3,0.0,r47,0.0,t,w,e,p,vp,ap);rrrf(2,4,3,5,6,0,7,7,2,3,p,vp,ap,t,w,e,fr);barf(1,1,2,1,p,ap,e,fr,&tb);fr4=sqrt(fr[4][1]*fr[4][1]+fr[4][2]*fr[4][2]);bt4=atan2(fr[4][2],fr[4][1]);we1=-(ap[1][1]*vp[1][1]+(ap[1][2]+9.81)*vp[1][2])*sm[1]-e[1]*w[1]*sj[1]; we2=-(ap[5][1]*vp[5][1]+(ap[5][2]+9.81)*vp[5][2])*sm[2]-e[2]*w[2]*sj[2]; extf(p,vp,ap,t,w,e,7,fe);we3=-(ap[6][1]*vp[6][1]+(ap[6][2]+9.81)*vp[6][2])*sm[3]-e[3]*w[3]*sj[3]+fe[7][1]*vp[7][1]+fe[7][2]*vp[7][2];tb1=-(we1+we2+we3)/w[1];printf("%3d%6.0f%11.3f%11.3f%11.3f%11.3f%11.3f\n",i,t[1]/dr,fr4,bt4/dr,tb,tb1,w[3]);fprintf(fp,"%3d%6.0f%11.3f%11.3f%11.3f%11.3f%11.3f\n",i,t[1]/dr,fr4,bt4/dr,tb,tb1,w[3]);tbdraw[i]=tb;tb1draw[i]=tb1;fr4draw[i]=fr4;bt4draw[i]=bt4;if((i%16)==0){getch();}}fclose(fp);getch();draw2(del,tbdraw,tb1draw,ic);draw3(del,bt4draw,fr4draw,bt4draw,fr4draw,bt4draw,fr4draw,ic);}extf(p,vp,ap,t,w,e,nexf,fe)double p[20][2],vp[20][2],ap[20][2],t[10],w[10],e[10],fe[20][2];{double pi,dr;pi=4.0*atan(1.0);dr=pi/180.0;if(w[3]<0){fe[nexf][1]=(-t[1]/dr-147.0)*(85000.0/180.0)*cos(-t[3]-pi/2);fe[nexf][2]=-(-t[1]/dr-147.0)*(85000.0/180.0)*sin(-t[3]-pi/2);}else{fe[nexf][1]=0;fe[nexf][2]=0;}}（9）、数据：对质心的运动分析，对固定铰链的静态动力分析，主动反力偶The Kineto-static Analysis of a Six-bar LinkaseNO THETA1 FR4 BT4 TB TB1(deg.) (N) (deg.) (N.m) (N.m)0 0 13495.618 46.529 82.962 82.9621 -15 51740.886 7.648 -32.118 -32.1182 -30 46297.709 9.048 -115.603 -115.6033 -45 40445.098 10.981 -153.006 -153.0064 -60 34265.975 13.793 -114.230 -114.2305 -75 27893.436 18.089 5.046 5.0466 -90 21549.857 25.094 180.471 180.4717 -105 15663.741 37.619 364.033 364.0338 -120 11239.466 61.651 497.291 497.2919 -135 10237.474 98.609 530.267 530.26710 -150 13049.547 128.023 440.499 440.49911 -165 17481.613 143.398 245.361 245.36112 -180 22128.717 151.296 1.782 1.78213 -195 11578.708 130.569 -274.821 -274.82114 -210 10921.444 127.756 -487.405 -487.40515 -225 10146.674 121.159 -561.288 -561.28816 -240 9523.273 110.618 -474.223 -474.22317 -255 9330.073 97.214 -252.532 -252.53218 -270 9684.879 83.423 39.775 39.77519 -285 10461.997 71.531 322.750 322.75020 -300 11409.304 62.337 524.218 524.21821 -315 12299.225 55.608 597.660 597.66022 -330 12984.650 50.899 530.546 530.54623 -345 13391.185 47.906 343.504 343.50424 -360 13495.618 46.529 82.962 82.962（3）、线图：对质心的运动分析，对固定铰链的静态动力分析，主动反力偶四杆机构曲柄上的平衡力矩的变化规律四杆机构颚板摆动中心运动副反力的大小及方向变化规律六. 工艺阻力函数及飞轮的转动惯量函数6.1工艺阻力函数程序（1）六杆工艺阻力函数程序#include"math.h"extf(p,vp,ap,t,w,e,nexf,fe)double p[20][2],vp[20][2],ap[20][2],t[10],w[10],e[10],fe[20][2];int nexf;{double pi,dr;pi=4.0*atan(1.0);dr=pi/180.0;if(w[5]<0){fe[nexf][1]=(-t[1]/dr-90.0)*(85000.0/182.0)*cos(-t[5]-pi/2);fe[nexf][2]=(-t[1]/dr-90.0)*(85000.0/182.0)*sin(-t[5]-pi/2);}else{fe[nexf][1]=0;fe[nexf][2]=0;}}（2）四杆工艺阻力函数程序#include"math.h"extf(p,vp,ap,t,w,e,nexf,fe)double p[20][2],vp[20][2],ap[20][2],t[10],w[10],e[10],fe[20][2]; int nexf;{double pi,dr;pi=4.0*atan(1.0);dr=pi/180.0;if(w[3]<0){fe[nexf][1]=(-t[1]/dr-147.0)*(85000.0/180.0)*cos(-t[3]-pi/2); fe[nexf][2]=(-t[1]/dr-147.0)*(85000.0/180.0)*sin(-t[3]-pi/2); }else{fe[nexf][1]=0;fe[nexf][2]=0;}}6.2飞轮的转动惯量函数程序（1）程序：六杆铰链式颚式破碎机的转动惯量计算#include "graphics.h"#include "stdio.h"#include "subk.c"#include "subf.c"main(){static double p[20][2],vp[20][2],ap[20][2],del;static double t[10],w[10],e[10];static double tbdraw[370],tb1draw[370],y[370],en[370];static double fr[20][2],fe[20][2];static int ic;double r12,r23,r34,r35,r56;double r27,r48,r39,r610,r611;int i;double pi,dr,td,tb,emax,emin,x,jf;FILE*fp;sm[1]=0.0;sm[2]=500.0;sm[3]=200.0;sm[4]=200.0;sm[5]=900.0;sj[1]=0.0;sj[2]=25.5;sj[3]=9.0;sj[4]=9.0;sj[5]=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; r610=r56/2;r611=0.6;y[0]=0.0;en[0]=0.0;td=0.0;pi=4.0*atan(1.0);dr=pi/180.0;w[1]=-170.0*2.0*pi/60.0; e[1]=0.0; del=15.0;p[1][1]=1.0;p[1][2]=1.0;p[4][1]=1.94;p[4][2]=0.0;p[6][1]=0.0;p[6][2]=1.85;if((fp=fopen("filejf6","w"))==NULL){printf("Can't open this file./n");exit(0);}fprintf(fp,"\nThe Moment of Inertia Analysis of a Six-bar Linkase:\n"); ic=(int)(360.0/del);for(i=0;i<=ic;i++){ t[1]=(-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);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(3,6,5,9,10,0,11,11,4,5,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);tbdraw[i]=tb;td=td+tbdraw[i];}td=td/ic;printf("%10.3f\n",td) ;for(i=0;i<=ic;i++){ if(i>0){y[i]=del*dr*td-del*dr/2.0*(tbdraw[i]+tbdraw[i-1]);en[i]=en[i-1]+y[i];}printf("%10.3f%10.3f\n",y[i],en[i]);}for(i=0;i<25;i++)if(en[i]>en[i+1]){ x=en[i];en[i]=en[i+1];en[i+1]=x;} emax=x;for(i=0;i<25;i++)if(en[i]<en[i+1]){ x=en[i];en[i]=en[i+1];en[i+1]=x;} emin=x;jf=(emax-emin)/(w[1]*w[1]*0.05);printf("%10.3f\n",jf) ;fprintf(fp," jf=%10.3f kg*m*m\n",jf);}#include "math.h"extf(p,vp,ap,t,w,e,nexf,fe)double p[20][2],vp[20][2],ap[20][2],t[10],w[10],e[10],fe[20][2];{double pi,dr;pi=4.0*atan(1.0);dr=pi/180.0;if(w[5]<0){fe[nexf][1]=(-t[1]/dr-90.0)*(85000.0/182.0)*cos(-t[5]-pi/2);fe[nexf][2]=-(-t[1]/dr-90.0)*(85000.0/182.0)*sin(-t[5]-pi/2);}else{fe[nexf][1]=0;fe[nexf][2]=0;}}（2）六杆铰链式颚式破碎机的转动惯量输出结果The Moment of Inertia Analysis of a Six-bar Linkase:Jf = 129.185 kg*m*m（3）程序：四杆铰链式颚式破碎机的转动惯量计算#include "graphics.h"#include "stdio.h"#include "subk.c"#include "subf.c"main(){static double p[20][2],vp[20][2],ap[20][2],del;static double t[10],w[10],e[10];static double tbdraw[370],tb1draw[370],y[370],en[370];static double fr[20][2],fe[20][2];static int ic;double r12,r23,r34;double r25,r36,r47;int i;double pi,dr,td,tb,emax,emin,x,jf;FILE*fp;sm[1]=0.0; sm[2]=200.0; sm[3]=900.0;sj[1]=0.0; sj[2]=9.0; sj[3]=50.0;r12=0.04; r23=1.11; r34=1.96;r25=r23/2;r36=r34/2; r47=0.6;y[0]=0.0;en[0]=0.0;td=0.0;pi=4.0*atan(1.0);dr=pi/180.0;w[1]=-170.0*2.0*pi/60.0; e[1]=0.0; del=15.0;p[1][1]=0.0; p[1][2]=0.0;p[4][1]=-0.95; p[4][2]=2.0;if((fp=fopen("filejf6","w"))==NULL){printf("Can't open this file./n");exit(0);}fprintf(fp,"\nThe Moment of Inertia Analysis of a Six-bar Linkase:\n"); ic=(int)(360.0/del);for(i=0;i<=ic;i++){ t[1]=(-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);bark(2,0,5,2,0.0,r25,0.0,t,w,e,p,vp,ap);bark(3,0,6,3,0.0,r36,0.0,t,w,e,p,vp,ap);bark(4,0,7,3,0.0,r47,0.0,t,w,e,p,vp,ap);rrrf(2,4,3,5,6,0,7,7,2,3,p,vp,ap,t,w,e,fr);barf(1,1,2,1,p,ap,e,fr,&tb);tbdraw[i]=tb;td=td+tbdraw[i];}td=td/ic;for(i=0;i<=ic;i++){ if(i>0){y[i]=del*dr*td-del*dr/2.0*(tbdraw[i]+tbdraw[i-1]);en[i]=en[i-1]+y[i];}printf("%10.3f%10.3f\n",y[i],en[i]);}for(i=0;i<25;i++)if(en[i]>en[i+1]){ x=en[i];en[i]=en[i+1];en[i+1]=x;} emax=x;for(i=0;i<25;i++)if(en[i]<en[i+1]){ x=en[i];en[i]=en[i+1];en[i+1]=x;} emin=x;jf=(emax-emin)/(w[1]*w[1]*0.05);fprintf(fp," jf=%10.3f kg*m*m\n",jf);}#include "math.h"extf(p,vp,ap,t,w,e,nexf,fe)double p[20][2],vp[20][2],ap[20][2],t[10],w[10],e[10],fe[20][2];{double pi,dr;pi=4.0*atan(1.0);dr=pi/180.0;if(w[3]<0){fe[nexf][1]=(-t[1]/dr-147.0)*(85000.0/180.0)*cos(-t[3]-pi/2);fe[nexf][2]=-(-t[1]/dr-147.0)*(85000.0/180.0)*sin(-t[3]-pi/2);}else{fe[nexf][1]=0;fe[nexf][2]=0;}}（4）四杆铰链式颚式破碎机的转动惯量输出结果The Moment of Inertia Analysis of a Six-bar Linkase:jf= 43.669 kg*m*m七 .对两种机构的综合评价从运动角度分析：颚板的摆动范围：四杆机构Δt=0.037rad，六杆机构Δt=0.069rad；颚板最大角速度：四杆机构w[3]max=0.314357rad/s,六杆机构w[5]max=0.679758rad/s；颚板最大角加速度：四杆机构e[3]max=6.712194rad/s2, 六杆机构e[5]max=15.840246rad/s2。