铰链式颚式破碎机方案分析铰链式颚式破碎机说明书

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1301姓名宋绍诚学号20135483指导教师杨强成绩2015年10月28日目录一设计题目1二已知条件及设计要求121已知条件122设计要求2三机构的结构分析231六杆铰链式破碎机232四杆铰链式破碎机3四机构的运动分析341六杆铰链式颚式破碎机的运动分析342四杆铰链式颚式破碎机的运动分析6五机构的动态静力分析951六杆铰链式颚式破碎机的静力分析952四杆铰链式颚式破碎机的静力分析14六工艺阻力函数及飞轮的转动惯量函数1261工艺阻力函数程序1962飞轮的转动惯量函数程序20七对两种机构的综合评价20八主要的收获和建议20九参考文献21一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21已知条件图1六杆铰链式破碎机图2工艺阻力图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N1170R/MIN，各部尺寸为LO1A01M,LAB1250M,LO3B1M,LBC115M,LO5C196M,L11M,L2094M,H1085M,H21M。各构件质量和转动惯量分别为M2500KG,JS2255KGM2,M3200KG,JS39KGM2,M4200KG,JS49KGM2,M5900KG,JS550KGM2,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LO5D06M，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N1170R/MIN。LO1A004M,LAB111M,L1095M,H12M,LO3B196M，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LO3D06M。各杆的质量、转动惯量为M2200KG,JS29KGM2，M3900KG,JS350KGM2。曲柄1的质心在O1点处，2、3构件的质心在各构件的中心。22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31六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。32四杆铰链式破碎机四杆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41六杆铰链式颚式破碎机的运动分析（1）分析调用BARK函数对主动件进行运动分析。见表41。调用RRRK函数对由构件组成的RRR杆组进行运动分析。见表42。调用RRRK函数对由构件组成的RRR杆组进行运动分析。见表43。表41形式参数N1N2N3KR1R2GAMTWEPVPAP实值1201R120000TWEPVPAP表42形式参数MN1N2N3K1K2R1R2TWEPVPAP实值142332R34R23TWEPVPAP表43形式参数MN1N2N3K1K2R1R2TWEPVPAP实值136545,R35R56TWEPVPAP（2）编写程序/NOTEYOURCHOICEISCIDE/INCLUDE“GRAPHICSH“INCLUDE“SUBKC“INCLUDE“DRAWC“MAINSTATICDOUBLEP202,VP202,AP202,DELSTATICDOUBLET10,W10,E10,TDRAW370,WDRAW370,EDRAW370STATICINTICDOUBLER12,R23,R34DOUBLEPI,DRINTIFILEFPCHARM“P“,“VP“,“AP“PI40ATAN10DRPI/1800R12004R23111R34196W117PI/3E100DEL1P1100P1200P41095P4220PRINTF“NTHEKINEMATICPARAMETERSOFPOINT3N“PRINTF“NOTHETALT3W3E3N“PRINTF“DEGMM/SM/S/SN“IFFPFOPEN“6666YUNDONG“,“W“NULLPRINTF“CANTOPENTHISFILEN“EXIT0FPRINTFFP,“NTHEKINEMATICPARAMETERSOFPOINT3N“PRINTF“NOTHETALT3W3E3N“PRINTF“DEGMM/SM/S/SN“ICINT3600/DELFORI0IICIT1IDELDRBARK1,2,0,1,R12,00,00,T,W,E,P,VP,APRRRK1,2,4,3,2,3,R23,R34,T,W,E,P,VP,APPRINTF“N2D123F123F123F123F“,I1,T1/DR,T3,W3,E3FPRINTFFP,“N2D123F123F123F123F“,I1,T1/DR,T3,W3,E3TDRAWIT3WDRAWIW3EDRAWIE3IFI160GETCHFCLOSEFPGETCHDRAW1DEL,TDRAW,WDRAW,EDRAW,IC,M（3）运行结果THEKINEMATICPARAMETERSOFPOINT3100001632001462322150001632010559883300001635018953754450001638026144155600001642031731496750001647035216397900001653036400308105000165803511746912000016630313338410135000166702534807111500001670017458941216500016720082654513180000167200166703141950001671011363581521000016690201554416225000166602744339172400001661032728481825500016560357119219270000165103620501202850001646034321172130000016410301355322315000163702404731233300001634016355912434500016320077609825360000163200146232图1六杆机构颚板角位置、角速度、角加速度随曲柄转角的变化曲线42四杆铰链式颚式破碎机的运动分析（1）分析调用BARK函数对主动件进行运动分析。见表44。调用RRRK函数对由构件组成的RRR杆组进行运动分析。见表45。表44形式参数N1N2N3KR1R2GAMTWEPVPAP实值1201R120000TWEPVPAP表45形式参数MN1N2N3K1K2R1R2TWEPVPAP实值124323R23R34TWEPVPAP（2）编写程序/NOTEYOURCHOICEISCIDE/INCLUDE“GRAPHICSH“INCLUDE“SUBKC“INCLUDE“DRAWC“MAINSTATICDOUBLEP202,VP202,AP202,DELSTATICDOUBLET10,W10,E10,TDRAW370,WDRAW370,EDRAW370STATICINTICDOUBLER12,R23,R34DOUBLEPI,DRINTIFILEFPCHARM“P“,“VP“,“AP“PI40ATAN10DRPI/1800R12004R23111R34196W117PI/3E100DEL1P1100P1200P41095P4220PRINTF“NTHEKINEMATICPARAMETERSOFPOINT3N“PRINTF“NOTHETALT3W3E3N“PRINTF“DEGMM/SM/S/SN“IFFPFOPEN“4444YUNDONG“,“W“NULLPRINTF“CANTOPENTHISFILEN“EXIT0FPRINTFFP,“NTHEKINEMATICPARAMETERSOFPOINT3N“PRINTF“NOTHETALT3W3E3N“PRINTF“DEGMM/SM/S/SN“ICINT3600/DELFORI0IICIT1IDELDRBARK1,2,0,1,R12,00,00,T,W,E,P,VP,APRRRK1,2,4,3,2,3,R23,R34,T,W,E,P,VP,APPRINTF“N2D123F123F123F123F“,I1,T1/DR,T3,W3,E3FPRINTFFP,“N2D123F123F123F123F“,I1,T1/DR,T3,W3,E3TDRAWIT3WDRAWIW3EDRAWIE3IFI160GETCHFCLOSEFPGETCHDRAW1DEL,TDRAW,WDRAW,EDRAW,IC,M（3）运行结果THEKINEMATICPARAMETERSOFPOINT3100001632001462322150001632010559883300001635018953754450001638026144155600001642031731496750001647035216397900001653036400308105000165803511746912000016630313338410135000166702534807111500001670017458941216500016720082654513180000167200166703141950001671011363581521000016690201554416225000166602744339172400001661032728481825500016560357119219270000165103620501202850001646034321172130000016410301355322315000163702404731233300001634016355912434500016320077609825360000163200146232图2四杆机构颚板角位置、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51六杆铰链式颚式破碎机的静力分析（1）分析调用BARK函数对主动件进行运动分析。见表41。调用RRRK函数对由构件组成的RRR杆组进行运动分析。见表42。调用RRRK函数对由构件组成的RRR杆组进行运动分析。见表43。构件的质心7运动参数。见表51。构件的质心8运动参数。见表52。构件的质心9运动参数。见表53。构件的质心10运动参数。见表54。阻力的作用点11运动参数。见表55。调用RRRF对由杆组成的RRR杆组进行静力分析。见表56。调用RRRF对由杆组成的RRR杆组进行静力分析。见表57。调用BARF对主动件进行静力分析。见表58。表51形式参数N1N2N3KR1R2GAMTWEPVPAP实值207200R2700TWEPVPAP表52形式参数N1N2N3KR1R2GAMTWEPVPAP实值408300R4800TWEPVPAP表53形式参数N1N2N3KR1R2GAMTWEPVPAP实值309400R3900TWEPVPAP表54形式参数N1N2N3KR1R2GAMTWEPVPAP实值6010500R61000TWEPVPAP表55形式参数N1N2N3KR1R2GAMTWEPVPAP实值6011500R61100TWEPVPAP表56形式参数N1N2N3NS1NS2NN1NN2NEXFK1K2PVPAPTWEFR实值3659100111145PVPAPTWEFR表57形式参数N1N2N3NS1NS2NN1NN2NEXFK1K2PVPAPTWEFR实值4238730032PVPAPTWEFR表58形式参数N1NS1NN1K1PAPEFRTB实值1121PAPEFRSTATICDOUBLET10,W10,E10STATICDOUBLESITA1370,FR1DRAW370,SITA2370,FR2DRAW370,SITA3370,FR3DRAW370,TBDRAW370,TB1DRAW370STATICDOUBLEFR202,FE202STATICINTICDOUBLER12,R23,R34,R35,R56DOUBLER27,R48,R39,R610,R611INTIDOUBLEPI,DRDOUBLEFR6,BT6,WE1,WE2,WE3,WE4,WE5,TB,TB1FILEFPSM100SM25000SM32000SM42000SM59000SJ100SJ2255SJ390SJ490SJ5500R1201R23125R3410R35115R56196R27R23/2R48R34/2R39R35/2R610R56/2R61106PI40ATAN10DRPI/1800W117PI/3E100DEL15P1100P1200P41094P4210P6110P62085PRINTF“NTHEKINETOSTATICANALYSISOFASIXBARLINKASEN“PRINTF“NOHETA1FR6BT6TBTB1N“PRINTF“DEGNDEGNMNMN“IFFPFOPEN“6666LITXT“,“W“NULLPRINTF“CANTOPENTHISFILE/N“EXIT0FPRINTFFP,“NTHEKINETOSTATICANALYSISOFASIXBARLINKASEN“FPRINTFFP,“NOHETA1FR6BT6TBTB1N“FPRINTFFP,“DEGNDEGNMNMN“ICINT3600/DELFORI0IICIT1IDELDRBARK1,2,0,1,R12,00,00,T,W,E,P,VP,APRRRK1,4,2,3,3,2,R34,R23,T,W,E,P,VP,APRRRK1,3,6,5,4,5,R35,R56,T,W,E,P,VP,APBARK2,0,7,2,00,R27,00,T,W,E,P,VP,APBARK4,0,8,3,00,R48,00,T,W,E,P,VP,APBARK3,0,9,4,00,R39,00,T,W,E,P,VP,APBARK6,0,10,5,00,R610,00,T,W,E,P,VP,APBARK6,0,11,5,00,R611,00,T,W,E,P,VP,APRRRF3,6,5,9,10,0,11,11,4,5,P,VP,AP,T,W,E,FRRRRF4,2,3,8,7,3,0,0,3,2,P,VP,AP,T,W,E,FRBARF1,1,2,1,P,AP,E,FR,FR6SQRTFR61FR61FR62FR62BT6ATAN2FR62,FR61WE1AP11VP11AP12981VP12SM1E1W1SJ1WE2AP71VP71AP72981VP72SM2E2W2SJ2WE3AP81VP81AP82981VP82SM3E3W3SJ3WE4AP91VP91AP92981VP92SM4E4W4SJ4EXTFP,VP,AP,T,W,E,11,FEWE5AP101VP101AP102981VP102SM5E5W5SJ5FE111VP111FE112VP112TB1WE1WE2WE3WE4WE5/W1PRINTF“3D103F103F103F103F103FN“,I1,T1/DR,FR6,BT6/DR,TB,TB1FPRINTFFP,“3D103F103F103F103F103FN“,I1,T1/DR,FR6,BT6/DR,TB,TB1TBDRAWITBTB1DRAWITB1FR1DRAWIFR6SITA1IBT6FR2DRAWIFR6SITA2IBT6FR3DRAWIFR6SITA3IBT6IFI160GETCHFCLOSEFPGETCHDRAW2DEL,TBDRAW,TB1DRAW,ICDRAW3DEL,SITA1,FR1DRAW,SITA2,FR2DRAW,SITA3,FR3DRAW,ICINCLUDE“MATHH“EXTFP,VP,AP,T,W,E,NEXF,FEDOUBLEP202,VP202,AP202,T10,W10,E10,FE202DOUBLEPI,DRPI40ATAN10DRPI/1800IFW50FENEXF1T1/DR900850000/1830COST5PI/2FENEXF2T1/DR900850000/1830SINT5PI/2ELSEFENEXF10FENEXF20图3六杆机构曲柄上的平衡力矩的变化规律图4六杆机构颚板摆动中心运动副反力的大小及方向变化规律52四杆铰链式颚式破碎机的静力分析（1）分析调用BARK函数对主动件进行运动分析。见表44。调用RRRK函数对由构件组成的RRR杆组进行运动分析。见表45。各构件的质心5运动参数。见表59。各构件的质心6运动参数。见表510。阻力的作用点7运动参数。见表511。调用RRRF对由杆组成的RRR杆组进行静力分析。见表512。调用BARF对主动件进行静力分析。见表513。表59形式参数N1N2N3KR1R2GAMTWEPVPAP实值205200R2500TWEPVPAP表510形式参数N1N2N3KR1R2GAMTWEPVPAP实值406300R4600TWEPVPAP表511形式参数N1N2N3KR1R2GAMTWEPVPAP实值4073000600TWEPVPAP表512形式参数N1N2N3NS1NS2NN1NN2NEXFK1K2PVPAPTWEFR实值2435607723PVPAPTWEFR表513形式参数N1NS1NN1K1PAPEFRTB实值1121PAPEFRSTATICDOUBLET10,W10,E10STATICDOUBLESITA1370,FR1DRAW370,SITA2370,FR2DRAW370,SITA3370,FR3DRAW370,TBDRAW370,TB1DRAW370STATICDOUBLEFR202,FE202STATICINTICDOUBLER12,R23,R34,R25,R46,R47DOUBLEPI,DRDOUBLEFR1,FR4,BT1,BT4,WE1,WE2,WE3,TB,TB1INTIFILEFPCHARM“TB“,“TB1“,“FR1“,“FR2“SM100SM2200SM3900SJ100SJ290SJ3500PI40ATAN10DRPI/1800R12004R23111R34196R4706R250555R46098W117PI/3E100DEL1P1100P1200P41095P4220PRINTF“NTHEKINETOSTATICANALYSISOFASIXBARLINKASEN“PRINTF“NOHETALFR4SITALBT4SITALTBTB1N“PRINTF“DEGNDEGNMNMN“IFFPFOPEN“FILEL“,“W“NULLPRINTF“CANTOPENTHISFILE/N“EXIT0FPRINTFFP,“NTHEKINETOSTATICANALYSISOFASIXBARLINKASEN“FPRINTFFP,“NOTHETA1FR4SITALBT4SITALTBTB1N“FPRINTFFP,“DEGNDEGNMNMN“ICINT3600/DELFORI0IICIT1IDELDRBARK1,2,0,1,R12,00,00,T,W,E,P,VP,APRRRK1,2,4,3,2,3,R23,R34,T,W,E,P,VP,APBARK2,0,5,2,00,R25,00,T,W,E,P,VP,APBARK4,0,6,3,00,R46,00,T,W,E,P,VP,APBARK4,0,7,3,00,06,00,T,W,E,P,VP,APRRRF2,4,3,5,6,0,7,7,2,3,P,VP,AP,T,W,E,FRBARF1,1,2,1,P,AP,E,FR,FR1SQRTFR11FR11FR12FR12BT1ATAN2FR12,FR11FR4SQRTFR41FR41FR42FR42BT4ATAN2FR42,FR41WE1AP11VP11AP12981VP12SM1E1W1SJ1WE2AP51VP51AP52981VP52SM2E2W2SJ2EXTFP,VP,AP,T,W,E,7,FEWE3AP61VP61AP62981VP62SM3E3W3SJ3FE71VP71FE72VP72TB1WE1WE2WE3/W1PRINTF“3D103F103F103F103F103FN“,I1,T1/DR,FR4,BT4/DR,TB,TB1FPRINTFFP,“3D103F103F103F103F103FN“,I1,T1/DR,FR4,BT4/DR,TB,TB1TBDRAWITBTB1DRAWITB1FR1DRAWIFR4SITA1IBT4FR2DRAWIFR4SITA2IBT4FR3DRAWIFR4SITA3IBT4IFI160GETCHFCLOSEFPGETCHDRAW2DEL,TBDRAW,TB1DRAW,IC,MDRAW3DEL,SITA1,FR1DRAW,SITA2,FR2DRAW,SITA3,FR3DRAW,IC,MINCLUDE“MATHH“EXTFP,VP,AP,T,W,E,NEXF,FEDOUBLEP202,VP202,AP202,T10,W10,E10,FE202DOUBLEPI,DRPI40ATAN10DRPI/1800IFW30FENEXF1T1/DR30850000/1800COST3PI/2FENEXF2T1/DR30850000/1800SINT3PI/2ELSEFENEXF10FENEXF20（3）运行结果THEKINETOSTATICANALYSISOFASIXBARLINKASENOTHETA1FR4SITALBT4SITALTBTB1DEGNDEGNMNM1000010023002972954686446864215000101799166851263999639993300001260537945171261032610344500016447933303916627566275560000210341032118920323320323367500026031225151103651823651827900003126792910859524226524226810500036634610777664771164771191200004204522855127037927037921013500047425423387266806266806211150000527117442730529459529459121650005785505619942935702935701318000098762547048729962299621419500010039491715861496514965152100001017990973779457884578816225000102920837683454093540931724000010375423804843892038920182550001043207784456649664961927000010465335884903213532135202850001047841392343646156461521300000104734929580280727807272231500010451097986877489474894233300001041000810085847249472492434500010347725102212329032902536000011641204708143496634966图5四杆机构曲柄上的平衡力矩的变化规律图6四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61工艺阻力函数程序（1）六杆工艺阻力子程序EXTFP,VP