平板搓丝机的传动装置设计(带CAD图纸)
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镇 江 高 专ZHENJIANG COLLEGE毕 业 设 计 (论 文) 平板搓丝机传动装置设计Design of transmission device for flat rolling machine 系 名: (四号宋体) 专业班级: (四号宋体) 学生姓名: (四号宋体) 学 号: (四号宋体) 指导教师姓名: (四号宋体) 指导教师职称: (四号宋体) 年 月摘要由于现代工业的飞速发展,高速,大负荷,动载条件下工作的精密机器的不断出现,对螺纹联接的机械性能提出越来越高的要求。即要求螺纹联接件应具有高强度、高硬度、高精度、以及高的表面质量。 螺纹联接件数量大,质量要求高,常用的切削加工方法因为效率低,而且由于切断金属的纤维,降低了零件的质量,不能满足这种需要,所以必需寻求一种更加先进有效的螺纹加工方法。在一般情况下,用平丝板搓丝机搓制的螺纹已能满足使用制造要求,所以用平丝板搓丝的方法用的最广。本设计为机械设计基础课程设计的内容,是先后学习过机械制图、机械原理、机械设计、工程材料、加工工艺学等课程之后的一次综合应用。本设计说明书是对搓丝机传动装置设计的说明,搓丝机是专业生产螺丝的机器,使用广泛,本次设计是使用已知的使用和安装参数自行设计机构形式以及具体尺寸、选择材料、校核强度,并最终确定形成图纸的过程。通过设计,我们回顾了之前关于机械设计的课程,并加深了对很多概念的理解,并对设计的一些基本思路和方法有了初步的了解和掌握。关键词 搓丝机 执行机构 传动装置 螺纹AbstractAs the rapid development of modern industry, high speed, high load, the dynamic precision machine load work under the conditions of the emerging, put forward higher requirements on the mechanical properties of screw thread.Requested that the threaded joints with high strength, high hardness, high precision, and high surface quality.Threaded connection piece of large quantity, high quality requirements, cutting method commonly used because of low efficiency, but also because of cutting metal fiber, reducing the quality of the parts, can not meet this need, so it is necessary to seek a more advanced thread effective processing method.In general, with flat screw die flat die thread rolling machine rolling system has been able to meet the manufacture requirements, so the method with flat screw die thread rolling of the most widely used.The design for the basic mechanical design curriculum design, is a comprehensive application after has studied mechanical drawing, mechanical principle, mechanical design, engineering materials, processing technology and other courses. The design specification is to rub silk machine transmission device design, thread rolling machine is specializing in the production of screw machine, widely used, the design is known for using and installation parameters using self-designed mechanism and specific size, material selection, strength check, and ultimately determine the drawing forming process. Through the design, we look back on the mechanical design of the course, and deepen the understanding of many concepts, and some of the basic ideas and methods of design have a preliminary understanding and mastery.Key words Thread rolling machine Actuator Transmission Thread目 录1 课程设计题目1.1 平板搓丝机传动装置设计图1(1)设计背景搓丝机用于加工轴辊螺纹,基本结构如上图所示,上搓丝板安装在机头4上,下搓丝板安装在滑块3上。加工时,下挫丝板随着滑块作往复运动。在起始(前端)位置时,送料装置将工件送入上、下搓丝板之间,滑块向后运动时,工件在上、下搓丝板之间滚动,搓制出与搓丝板一致的螺纹。搓丝板共两对,可同时搓制出工件两端的螺纹。滑块往复运动一次,加工一个工件。(2)工作条件室内工作,动力源为三相交流电动机,电动机单向运转,载荷较平。(3)使用期限工作期限为十年,每年工作300天;检修期间隔为三年。(4)生产批量及加工条件中等规模的机械厂,可加工7、8级精度的齿轮、蜗轮。1.2 设计数据表最大加工直径/mm最大加工长度/mm滑块行程/mm搓丝动力/kN生产率/(件/min)10150300-32012452 拟定传动方案及方案比较根据设计要求可知:滑块每分钟要往复运动45次,所以机构系统的原动件的转速应为45 r/min。以电动机作为原动机,则需要机构系统有减速功能。运动形式为连续转动往复直线运动。根据上述要求,有以下三种备选方案。在所有方案中齿轮1、2都可以看作传动部分的最后一级减速齿轮。方案一:图2在电动机的带动下经带传动、带动齿轮传动(减速器),通过曲柄将动力传递给连杆,再有连杆带动滑块C的往复运动。方案二:图3在电动机的带动下经带传动、带动齿轮传动(减速器),通过凸轮将动力传递给杆件B,由连杆带动滑块C的往复运动。方案三图4在电动机的带动下经带传动、带动齿轮传动(减速器),通过曲柄摇杆机构将动力传递给滑块C ,从而使C往复运动。方案比较:1、方案一:采用了曲柄滑块机构,曲柄长度仅为滑块行程的一半,故机构尺寸较小,结构简洁。利用曲柄和连杆共线,滑块处于极限位置时,可得到瞬时停歇的功能。同时该机构能承受较大的载荷。2、采用凸轮机构,该机构随能满足运动规律,然而系统要求的滑块行程为340360mm,因而凸轮的径向尺寸较大,于是其所需要的运动空间也较大,同时很难保证运动速度的平稳性。3、采用了曲柄摇杆机构,利用1杆和2杆共线,机构处于极限位置时,可得到瞬时停歇的功能。但是由于机构的传力性能要求太高,对2杆的前对要求太高,一般的材料无法满足其强度与刚度要求。且机构太复杂易造成占用空间大等缺点。综合以上分析可知:方案一最为可行,应当选择曲柄滑块机构实现运动规律。整个搓丝机由电动机、带传动、二级减速器、曲柄滑块机构、最终执行机构组成。以完成预定的设计目的。3 传动装置设计3.1 机构初步设计采用同轴式的主要优点是结构长度较小两对齿轮的吃油深度可大致相,利于润滑等。曲柄长取滑块行程的一半,即150mm,初取箱体浸油深度为50mm,箱体底座厚30mm,初取滑块所在导轨厚度为60mm,连杆与滑块接触点距导轨高为40mm,则可大致得出减速器中心轴的高度为150+50+4=240mm,曲柄滑块机构的偏心距e=180mm,考虑到留下足够的空间防止减速器箱体与滑块干涉接触,初取连杆长度为1400mm,此时可以计算出急回特性为1.024,传动平稳。3.2 设计参数(1)工作机输出功率计算:已知水平搓丝力大小为12KN,生产率为45件/min,则有则曲柄的功率为又滑块效率为0.9,铰链效率为0.95,则补充系统总效率为电动机所需实际功率为要求Ped略大于Pd,则选用Y系列电动机,额定功率15KW (2) 工作机转速45r/min传动比范围:V型带:减速器:总传动比电动机转速可选范围为:nd=i*n w=384-3840r/min 可知电动机应选型号为Y180M6,同步转速1000r/min,满载转速为970r/min(3)总传动比初步取带轮效率i1=2,则减速器传动比取两级圆柱齿轮减速器高速级传动比(4)各轴转速(5)各轴输入功率(6)各轴输入转矩电动机所需实际转矩及电动机的输出转矩为轴输入功率输出功率输入转矩输出转矩转速传动比效率电机轴15KW147.68Nm970r/min高速轴11.45KW225.46Nm485r/min20.96中间轴11KW996.53Nm105.435r/min4.60.96低速轴10.56KW4208.49Nm23.963r/min4.40.964 带传动主要参数及几何尺寸计算计算项目计算内容计算结果确定计算功率由表31-7由公式选取带型由图31-15选用A带选取小带轮直径由表31-3dd1=125mm大带轮直径dd2=idd1dd2=250mm小带轮带速1=dd1n1601000初选中心距a0初选a0=700mm带初步基准长度LdLd=1994.3mm带基准长度Ld由表31-2Ld=2000mm实际中心距a=678.8mm选取a=680mm小带轮包角带的根数由表31-3求P0由表31-4的基本额定功率增量P0由表31-9取包角系数k由表31-2取长度系数kLP0=1.50KwP0=0.14Kwk=0.98kL=1.03z=Pc(P0+P0)kkLz=9.97取z=10带的初拉力带的压轴力由表31-1取l=0.10初拉力:F0=187.362NFQ=3732.98N5 齿轮传动设计计算计算项目计算内容计算结果材料选取小齿轮使用40Cr,调质处理,硬度241-286HBS;大齿轮使用45钢,调质处理,硬度217-255HBS;精度等级均为8级有关数据以及公式引自机械设计基础(下册)5.1 低速级计算项目计算内容计算结果(1)初步计算转矩T1齿宽系数d由表27-14d=1.2接触疲劳极限Hlim由表27-14bHlim1=710MPaHlim2=580MPa需用接触应力计算HPHP1=0.9Hlim1HP2=0.9Hlim2HP1=639MPaHP2=522MPaAd由表B1,估计 Ad=756动载荷系数K K=1.4初步计算小齿轮直径d1d1=131.28mm取d1=132mm初步齿宽bb=dd1=158.4mmb=160mm(2)校核计算圆周速度=d1n1601000=3.35m/s精度等级由表27-1选取8级精度8级精度齿数z取z1=35z2=iz1=154由于z1,z2互质取z1=35 z2=153 模数mt=d1z1查表27-4取标准值确定齿数z1=d1mtz2=iz1=arccosmnmtd2=mtz2mt=3.0857mmd2=472.1121mm取mn=3使用系数KA由表27-7KA=1.35动载系数KV由表27-6KV=1.1齿间载荷分配系数首先求解Ft=2T1d1非硬齿面斜齿轮,8级精度Ft=1718.47NKH=1.52齿向载荷分配系数KHKH=1.67区域系数ZH由图27-18ZH=2.43弹性系数ZE由表27-15ZE=189.8MPa重合度系数Z由表27-5同理由于无变位,端面啮合角t=t=bsinmnz=1t=20.525at1=26.481at2=22.073=1.448=3.231z=0.831螺旋角系数ZZ=cosZ=0.986许用接触应力由表27-17取最小安全系数SHlim总工作时间th=33008盈利循环次数NL1=60n1th 单向运转=1NL2=NL1i由图27-27取接触寿命系数ZNT齿面工作硬化系数ZW由表27-18接触强度尺寸系数ZX润滑油膜影响系数取值HP=HlimZNTZLZVZRZWZXSHlimSHlim=1.05th=7200hNL1=4.555107NL2=1.035107ZNT1=1.18ZNT2=1.25ZW1=ZW2=1.14ZX1=ZX2=1.0ZL1=ZL2=1.0ZR1=ZR2=1.0ZV1=ZV2=1.0HP1=909.6MPaHP2=787MPa验算H=ZHZEZZKAKVKHKHFtbd1u+11H=661.523 MPa(3)确定主要传动尺寸中心距a=d1+d22=290.056mm取整a=290mm螺旋角端面模数mt=mn/cosmt=2.0851分度圆直径d=mnz/cosd1=107.979mmd2=472.021mm齿宽b=130mm当量齿数ze1=z1/cos3=38.06取ze1=38取ze2=166(4)齿根弯曲疲劳强度验算齿形系数YFa由当量齿宽查图27-20取值YFa1=2.48YFa2=2.20应力修正系数由图27-21取值YSa1=1.65YSa2=1.78螺旋角系数Y由图27-22取值Y=0.88齿向载荷分配系数由图27-9取值KF=1.52许用弯曲应力由图27-30取试验齿轮的齿根弯曲疲劳极限Flim由表27-17取最小安全系数SFmin由表27-33确定尺寸系数YX由图27-32确定弯曲寿命系数YNT另外取值如右FP=FlimYNTYSTYVrelTYRrelTYXSFlimFlim1=300N/mm2Flim2=270N/mm2SFmin=1.25YX1=YX2=1.0YNT1=0.96YNT2=0.98YST1=YST2=2YVrelT1=YVrelT2=1.0YRrelT1=YRrelT2=1.0FP1=460.8N/mm2FP2=423.36N/mm2验算F=KAKVKFKFYFaYSaYYFtb1mnF1=239.91MPaF2=229.59MPa(5)齿轮主要传动尺寸列表压力角n20螺旋角分度圆直径dd1=107.979mmd2=472.021mm齿顶高齿根高齿顶间隙CC=0.25mC=0.75mm中心距aa=d1+d22a=290mm5.2 高速级由于低速级齿轮受力远比高速级严重,而且二者中心距相等,采用相同齿宽的条件下,高速级齿轮必然满足强度刚度等要求,而且还有不小的过盈量。在此不再校核高速级齿轮的强度,根据中心距相等,直接计算其相关尺寸,必定能满足使用要求。齿轮主要传动尺寸列表计算项目计算内容计算结果中心距aa=d1+d22a=290mm分度圆直径dd2=i12d1d1=102.143mmd2=469.857mm齿数d1=mtz1 d2=mtz2取z1=33 z2=152模数mt=2a/(z1+z1)mt=3.102 mn=3传动比i12=d2/d1i12=4.61螺旋角分度圆直径d=mnz/cosd1=102.366mmd2=477.634mm齿宽b=123mm(5)齿轮主要传动尺寸列表压力角n20螺旋角分度圆直径dd1=102.366mmd2=477.634mm齿顶高齿根高齿顶间隙CC=0.25mC=0.75mm中心距aa=d1+d22a=290mm6 轴的设计与校核6.1 初估轴径电机轴取d00=24mm高速轴取d11=35mm中间轴取d22=50mm低速轴取d33=75mm6.2 轴强度校核1 高速轴齿轮上的作用力转矩圆周力径向力轴向力Ft=2T1d1Fr=FttanncosFa=FttanT1=225.46NmFt=3416.1NFr=1248.8NFa=889.8N支反力Y-Z平面FQ80+Ft97=FAV218FAV=2890NFBV=3207NMV1=630NmMV2=630NmX-Z平面FBH+FAH=FrFBH97+Fa51=FAH194FAH=1717NFBH=-469NMH1=45.49NmMH2=333.1Nm合成弯矩Mc1=MV12+MH12Mc2=MV22+MH22Mc1=632NmMc2=713Nm转矩T1=225.46Nm当量弯矩Mec1=Mc12+T12Mec2=Mc22+T12=0.579Mec1=645NmMec2=725Nm校核bc2=Mec2Wc2 中间轴高速级大齿轮齿轮上的作用力转矩圆周力径向力轴向力Ft=2T2d2Fr=FttanncosFa=FttanT2=996.35NmFt1=4240NFr1=1595NFa1=1104N低速级小齿轮齿轮上的作用力转 矩圆周力径向力轴向力Ft=2T2d2Fr=FttanncosFa=FttanT2=996.35NmFt2=4484.13NFr2=1678.39NFa2=1075.65N支反力Y-Z平面FBV+FAV=Ft1+Ft2-FAV232+Ft1132=Ft2102FAV=3260.38NFBV=5528.56NMV1=319.71NmMV2=457.38NmX-Z平面FBH+FAH=Fr1+Fr2Fa254+FAH230=Fa1239+Fr1132+Fr2102FAH=87.29NFBH=2425.06NMH1=8554.4NmMH2=130.72NmMH3=229.28NmMH4=229.28Nm合成弯矩Mc1=MV12+MH12Mc2=MV22+MH42Mc1=345.40NmMc2=511.63Nm转矩T1=500.977Nm当量弯矩Mec1=Mc12+T12Mec2=Mc22+T12=0.579Mec1=451.37NmMec2=588.38Nm校核bc1=Mec1Wcbc2=Mec1Wc3 低速轴齿轮上的作用力转矩圆周力径向力轴向力Ft=2T2d3Fr=FttanncosFa=FttanT3=4208.49NmFt=4484.13NFr=1678.39NFa=1075.65N支反力Y-Z平面FBV+FAV=FtFAV103=Ft103FAV=2242.065NFBV=2242.065NMV1=230.93NmX-Z平面FBH+FAH=FrFAH=2071.49NFBH=393.10NMH1=40.49NmMH2=213.36Nm合成弯矩Mc1=MH12+MV12Mc2=MH22+MV12Mc1=234.45NmMc2=310.66Nm转矩T1=2116.598Nm当量弯矩Mec1=Mc12+T12Mec2=Mc22+T12=0.579Mec1=1249.815NmMec2=1266.325Nm校核bc1=Mec1Wcbc2=Mec2Wc7 轴承的选择与校核7.1 高速轴轴承30209计算项目计算公式计算结果轴承主要性能参数轴承30209性能参数e=0.4,Y=1.6轴承受力情况FrA=FAH2+FAV2,FrB=FBH2+FBV2FSA=FrA/2Y,FSB=FrB/2YFrA=1246.05NFrB=1138.92NFSA=389.39NFSB=355.91NFA=582.74N求FFSB+FAe=0.4X=0.4Y=1.6冲击载荷系数由表38-4得fd=1.4当量动载荷PB=fdXFr+YFaPB=2815.37N轴承AFFFaAFrA=0.312FSBFaB=FSA+FAFaB=2012.35NFaA=1519.44N轴承BX,Y取值FaBFrB=0.33eX=0.4Y=1.5冲击载荷系数fd=1.4当量动载荷PA=fdXFr+YFaPA=5017.292NPmaxP=maxPA,PBP=8451.86N轴承寿命L10=6.402105h结论:所选用轴承可用。7.3 低速轴轴承30217计算项目计算公式计算结果轴承性能参数轴承30217性能参数e=0.42轴承受力情况FrA=FAH2+FAV2,FrB=FBH2+FBV2FSA=FrA/2Y,FSB=FrB/2YFrA=2393.97NFrB=2393.9NFSA=1090.19NFSB=812.95NFA=1075.65N求FFSA+FAFSBFaB=FSA+FAFaB=2165.84NFaA=1090.19N轴承BFFFaBFrB=0.951e=0.42X=1Y=0冲击载荷系数由表38-4得fd=1.4当量动载荷PB=fdXFr+YFaPB=5914.026N轴承AFFFaAFrA=0.357 eX=0.4Y=1.4冲击载荷系数由表38-4得fd=1.4当量动载荷PA=fdXFr+YFaPA=4578.795NPmaxP=maxPA,PBP=5914.026N轴承寿命L10=4.14107h结论:所选用轴承可用。8 键的选择与校核高速轴键的选择和参数选用普通平键,圆头, d1=38mm,d2=50mm,选用键bh=108, bh=149,转 矩T1= 225.46Nm键长L1= 100mmL2= 110mm接触长度l1=30mml2=96mm许用挤压应力查表铸铁许用挤压应力为P1=14.83MPaP2=6.71MPaPP满足要求,可用中间轴键的选择和参数选用普通平键,圆头,d1=65mm,d2=55mm,选用键bh=1811, bh=1610转 矩T1= 996.35Nm键长L1= 110mmL2= 110mm接触长度许用挤压应力查表铸铁许用挤压应力为P1=30.97MPaP2=38.54MPaP1PP2P满足要求,可用低速轴键的选择和参数选用普通平键,圆头, d1=90mm,d2=75mm,选用键bh=2514, bh=2016转 矩T1=4208.49Nm键长L1= 110mmL2= 110mm接触长度l1=85mml2=50mm许用挤压应力查表铸铁许用挤压应力为P1=78.59MPaP2=77.9MPaP1PP2P满足要求,可用9 减速器箱体各部分结构尺寸1 箱体名称符号尺寸箱盖壁厚=10mm箱座壁厚11=12mm箱盖凸缘厚度bb=18mm箱座凸缘厚度b1b1=15mm地脚螺钉直径地脚螺钉数目nn=6轴承旁连接螺钉直径d1d1=20mm箱盖与箱座连接螺钉直径d2d2=16mm轴承端盖螺钉直径d31d31=8mmd32d32=10mm窥视孔盖螺钉直径d4d4=8mm定位销直径dd=10mm起盖螺钉直径d5d5=16mm大齿轮顶圆与内壁距离=15mm齿轮端面与内壁距离1111=12mm1212=14mm轴承端盖外径D21D21=85mmD22D22=110mmD23D23=150mm轴承端盖凸缘厚度tt=12mm2 润滑及密封形式选择设计项目设计内容密封装置高速轴密封毡圈密封,d=44mm,挡油板内密封中间轴密封挡油板内密封低速轴密封毡圈密封,d=73mm,挡油板内密封润滑油以及润滑脂的选择轴承脂润滑齿轮油润滑3 箱体附件设计设计项目设计内容设计结果通气器指标:M271.5mm d1=M481.5mm,d2=12mmd3=4.5mm,d4=24mm,D=60mm a=15mmb=10mm c=22mm R=60mm D1=36.9mm, S=32mmk=7mme=2mm f=2mm油标指标:d=M20, d1=6mm, d2=16mm, d3=8mm, a=15mm,b=10mm,c=6mm,D=32mm, D1=26mm,选用C型油标排油螺塞指标:M242mm ,d1=21mm, D=34mm, e=31.2mm, S=27mm, L=32mm, b=4mm, b1=4mm, C=1.5mm, D0=35mm管螺纹六角螺塞及其组合件致 谢本次设计能顺利完成,得益于我的指导老师的悉心指导和适时督促。由于自身知识的匮乏,加上设计资料的欠缺,在设计过程中,遇到了较多的技术问题和未知知识,使得设计过程显得异常的困难。在解决上述难题的过程中,指导老师给予了大力的帮助,老师在每周答疑时间里总是对我们遇到的问题能给予详细的讲解。在其余时间,也时时关注着我们设计的进度、方法。我很欣赏指导老师的教学方式,她在解决学生问题的过程中,总能以一种探索的方式去鼓励学生追求学术领域的新知,即是她强调学生的主观能动性,激励学生增强解决问题的能力。在这里,我还得感谢曾经教导过我的所有老师,感谢他们授予了我知识,感谢他们教会了我怎样生活,怎样去解决生活中遇到的困难。同时,也要感谢学院领导,是你们的精心管、教,才让我们有了一个安定的学习环境。最后,还得感谢我的同学、朋友对我的帮助,在这里就一并作谢了。参考文献1、机械原理第七版,孙桓、陈作模、葛文杰主编,西北工业大学机械原理及机械零件教研室编,高等教育出版社2、机械原理课程设计指导书郭红利 主编,西北农林科技大学3、机械设计手册(第三版)吴宗泽 主编,化学工业出版社4、机械制图(第六版)大连理工大学工程图学教研室,高等教育出版社5、材料力学(第四版)刘鸿文主编,高等教育出版社6、理论力学(第七版)哈尔滨工业大学理论力学教研室7、A utoCAD2007 机械设计绘图应用教程 陈敏 刘晓旭 主编 重庆大学出版8、机械设计基础(下册)吴文祥等主编,北京航空航天大学出版社出版9、机械设计综合课程设计王之栋、王大康主编,机械工业出版社外文文献及译文本科毕业设计外文文献及译文院 (部): 专 业: 班 级: 姓 名: 学 号: 外文文献:ORIGINAL ARTICLEArtif Life Robotics (2011) 16:8689 ISAROB 2011DOI 10.1007/s10015-011-0892-1S. Ueki H. Kawasaki Y. Ishigure K. KoganemaruY. MoriDevelopment and experimental study of a novel pruning robot only one commercial product is available in Japan.6 The machine climbs a tree spirally and cuts branches using a chainsaw. However, the machines weight (25 kg) and slow speed hinder it from being an optimal solution to resolve the forest crisis. A lightweight platform is required, because most of the mountains in Japan have steep slopes, and the transportation of a pruning robot is a demanding task. To advance the state of the art of pruning robots, we present an innovative pruning robot that has its center of mass outside the tree. The wheel mechanism is designed for a hybrid climbing method, i.e., the robot is able to switch between straight and spiral climbs. This method ensures both lightweight and high climbing speed features in the Robot. In an earlier publication,7 we introduced the basic design concept and described some experiments with the prototype robots in detail. Moreover, the hybrid climbing method has proven that the proposed pruning robot can climb up and down a tree at high speed.8 Here, we report our progress in developing the robot, focusing on straight climbing, its behavior on uneven surfaces, and pruning. 2 Developed pruning robot With the ultimate goal of building a lightweight pruning robot, we have developed a novel climbing method that uses no pressing or grasping mechanism, but relies on the weight of the robot itself, like a traditional Japanese timberjack does when climbing a tree (Fig. 1). The timberjack uses a set of rods and ropes, which is called “Burinawa,” and does not hold or grasp the tree strongly, while his center of mass is located outside the tree. That is, the timberjack can stay on the tree using his own weight. Based on this new design concept and the requirements of the forestry industry, the pruning robot has been developed. As shown in Fig. 2, the robot is equipped with four active wheels. Wheels 1 and 2 are located on the upper side, and wheels 3 and 4 are located on the lower side. Each wheel is driven by a DC servomotor and a warm wheelAbstract This article presents the development of a timberjack- like pruning robot. The climbing principal is an imitation of the climbing approach of timberjacks in Japan. The robots main features include having its center of mass outside the tree, and an innovative climbing strategy fusing straight and spiral climbs. This novel design brings both lightweight and high climbing speed features to the pruning robot. We report our progress in developing the robot, focusing on straight climbing, 1behavior on uneven surfaces, and pruning.Key words Pruning robot Climbing robot1 Introduction The timber industry in Japan has gone into decline because the price of timber is falling and forestry workers are aging rapidly. This has caused the dilapidation of forests, resulting in landslides following heavy rainfall and the dissolution of mountain village society. However, a pruned tree in a suitably trimmed state is worth money because its lumber has a beautiful surface with well-formed annual growth rings. The development of a pruning robot is important for the creation of sustainable forest management. The research and development of a pruning robot 15 has been rare, and Received and accepted: February 25, 2011S. Ueki (*)Department of Mechanical Engineering, Toyota National Colleges ofTechnology, 2-1 Eiseicho, Toyota, Aichi 471-8525, Japane-mail: s_uekitoyota-ct.ac.jpH. Kawasaki K. KoganemaruDepartment of Human and Information Systems Engineering, GifuUniversity, Gifu, JapanY. IshigureMarutomi Seikou Co. Ltd., Seki, JapanY. MoriHashima Karyuu Kougyou Ltd., Gifu, JapanThis work was presented in part at the 16th International Symposiumon Artifi cial Life and Robotics, Oita, Japan, January 2729, 201187the batteries. The center of mass was located with a margin of error, because the friction coeffi cient is unclear and the position of the center of mass may be moved by disturbance. For example, the robot will be tilted when it climbs up an uneven surface. In Fig. 2a, the center of mass was located with parameters H = 0.3 m and W = 0.22 m, where H is the distance between the upper side wheel and the lower side wheel, and W is the distance between the surface of the trunk and the center of mass, as shown in Fig. 3. The analysis shows that the robot is robust when D is 0.25 m, even if it is tilted about 0.1 rad. The controller is constructed using a CPU board which is equipped with a wireless LAN. The controller is able to communicate data/commands with a personal computer via the wireless LAN. Each wheel is controlled by a velocity PI control. A velocity feedback input through a high-pass filter is appended. By comparison with the 2nd prototype,8 the 3rd prototype is lightweight except for the controller and batteries. Also, the controller and the electrical source were located externally in the 2nd prototype. The 3rd prototype is also equipped with a wireless LAN and a chainsaw. Although details of the chainsaw are omitted here, an experiment was performed to show the cutting of a branch using the 3rd prototype.3 Experiments Three experiments were performed to evaluate the 3rd prototype. The 1st experiment was to evaluate its basic performance. The 2nd experiment was to evaluate its robustness on uneven surfaces. The 3rd experiment was to show whether the robot can prune a branch. All experiments were performed using a substitute tree indoors. The diameter of the substitute tree was 0.25 m. The frictional coeffi - cient of the substitute tree was about 0.4, which is less than that of a natural tree. To collect the experimental data, the motor current, the position of the robot, and the orientation of the robot were measured. The motor current was measured using shunt resistance. The position was measured by a 3-D position measurement device (OPTOTRAK, Northern Digital). The orientation was measured by a 3-D orientation sensor (InertiaCube2, InterSense).Fig. 1. Tree climbing method using “BURINAWA”Fig. 2. 3rd prototype of pruning robot. a Photo image. b CAD image reduction mechanism which has non-back-drivability. The steering angle of each wheel is also driven by the DC servomotor and the warm wheel reduction mechanism. Based on analysis,79 the center of mass was located outside the tree with the help of the weight of the controller andFig. 3. 3D fi gure of a pruning robot on a tree. a Side view. b Top view883.1 Basic performanceA straight climbing experiment was performed to evaluate the robots basic performance. The desired speed of the four wheels was given by the trapezoidal profi le. The acceleration was 0.2 m/s2, and the speed was 0.2 m/s per 0.075 m of wheel radius. The experimental results are shown in Figs. 4, 5, and 6. Figure 4 shows the speed of the robot. The speed of each wheel was calculated from the values of the rotary encoder. The robot was able to climb at 0.2 m/s. Although there was a starting delay of about 0.5 s owing to the control law, this was not a problem. Figure 5 shows the distance moved. The “3D” value was measured by a 3D position measurement device, and the distance moved by each wheel was calculated from the value on the rotary encoder. In Fig. 5, we found three types of error: errors in the distance moved between each wheel and the 3D position measurement device (E1); error between wheel 1 (or 3) and wheel 2 (or 4) (E2); error between wheel 1 and wheel 3 (and error between wheel 2 and wheel 4) (E3). We considered two possible reasons for these errors. The fi rst was differences in the deformation of each wheel. The distance moved by each wheel was calculated as 0.075 m of the radius of the wheel. The wheel was composed of urethane and an inner tube which was deformed by the force acting on it. The deformation volume depended on the magnitude of the force. From a theoretical analysis,79 the magnitude of the force in the third prototype tended to be as follows. The normal force near the center of mass becomes larger than the force at the opposite side. Hence, Fn4 = Fn2 Fn3 = Fn1 was considered, where Fni is magnitude of the normal force of wheel i. Both (E1) and (E2) can be explained in this way. We also considered that the reason for (E3) was slippage of the wheel on the trunk. Figure 6 shows the electric current in the wheel motors, which were measured by the shunt resistance. The theoretical analysis79 also showed that the tangential force on the lower side is larger than that on the upper side. Figure 6 tends toward the theoretical analysis.3.2 Behavior on uneven surfacesTo use the robot safely, it must be robust on an uneven tree trunk. There will always be bumps caused by the growth of the remnants of a pruned branch. Therefore, a straight climbing experiment was performed to evaluate the robustness of the pruning robot for bumps on trunk. This experiment was performed on a substitute bump. The bump was made of ABS plastics, and was larger than a natural bump.The desired speed of the four wheels was given by a trapezoidal profile. The acceleration was 0.2 m/s2 and the speed was 0.2 m/s for every 0.075 m of the radius of the wheel. The experimental results are shown in Fig. 7, which shows the trajectories of angles 1 and 2 (see also Fig. 2b). Angle 2 rotated toward the plus direction in all cases, indicating that the control box was rising. This means that the center of mass moved toward the tree. The center of mass also moved toward the tree when angle 1 rotated toward the plus direction. This means that there is a decrease in the friction force keeping the robot on the tree. However, the electric currents in wheels 2 and 4 were larger than the continuous current in the experiment. Therefore, there was no danger of the robot falling down. Moreover, these angles returned to their former orientation, even though both angles 1 and 2 had changed when a wheel went over the bump. These results show the good robustness of the robot.3.3 Pruning experiment An experiment was carried out to discover whether the 3rd prototype could prune a branch. An attached chainsaw was driven by a DC motor with a 24-V battery. The robot climbed the tree spirally at a speed of 0.03 m/s. The diameter of the target branch was 0.01 m.Fig. 4. Climbing speedFig. 5. Climbing distanceFig. 6. Electric current of each wheelFig. 7. Roll angle and pitch angle in each case. a Wheel 1 goes over thebump, b Wheel 2 goes over the bump, c Wheel 3 goes over the bump,d Wheel 4 goes over the bumpFig. 8. Pruning experiment with the pruning robot The experimental scene is shown in Fig. 8. In this experiment, the branch was cut off leaving only a short remnant which was less than 0.005 m, and the trunk was not injured.4 ConclusionThe developmental progress of a timberjack-like pruning robot has been described, focusing on straight climbing, its behavior on an uneven surface, and pruning a branch. The straight climbing experiment showed that the 3rd prototype gave a good basic performance. The result of the climbing experiment on an uneven surface showed good robustness for bumps, because most bumps on real trees are smaller than the experimental bump. Moreover, the pruning experimentalso showed that the 3rd prototype can prune a branch from a tree.In future work, we hope to test the robot in a real environment,and try to make some further improvements.References1. Takeuchi M, et al (2009) Development of street tree climbing robotWOODY-2 (in Japanese). Proceedings of Robomec 2009, 1A2D072. Kushihashi Y, et al (2006) Development of structure of measuringgrasping power to control simplifi cation of tree, climbing andpruning robot Woody-1 (in Japanese). Proceedings of the 2006JSME Conference on Robotics and Mechatronics3. Suga Y, et al (2006) Development of tree-climbing and pruningrobot WOODY. Actuator arrangement on the end of arms forrevolving motion (in Japanese). Proceedings of SI2006, pp126712684. Yokoyama T, Kumagai K, Arai Y, et al (2006) Performance evaluationof branches map building system for pruning robot (in Japanese).Proceedings of the 2006 JSME Conference on Robotics andMechatronics5. Yamada T, Maeda K, Sakaida Y, et al (2005) Study on a pruningsystem using robots: development of prototype units for robots (inJapanese). Proceedings of the 2005 JSME Conference on Roboticsand Mechatronics6. Seirei Industry. http:/www.seirei.com/products/fore/ab232r/ab232r.html. Accessed May 20117. Kawasaki H, Murakami S, Kachi H, et al (2008) Analysis and experimentof novel climbing method. Proceedings of the SICE AnnualConference 2008, pp 1601638. Kawasaki H, Murakami S, Koganemaru K, et al (2010) Developmentof a pruning robot with the use of its own weight. Proceedings ofClawar 2010, pp 4554639. Kato T, Koganemaru K, Tanaka A, et al (2010) Development of apruning robot with the use of its own weight (in Japanese). Proceedingsof RSJ2010, Nagoya中文译文:人工生命的机器人(2011)16:8689isarob201110.1007/s10015-011-0892-1S. Ueki H. Kawasaki Y. Ishigure K. KoganemaruY. Mori一个新的修剪机器人的实验研究进展在日本只有一个商业产品。这台机螺旋地爬上一棵树使用电锯修剪树枝。然而,机器的重量(25公斤)和缓慢的速度阻碍它成为解决森林危机的最佳解决方案。一个轻量级的平台是必需的,因为在日本,大部分山脉有陡峭的山坡,一个修剪机器人运输是一项艰巨的任务。以提前修剪机器人的艺术状态,我们提出一个创新的修剪机器人对于外面大多数的树都能高效工作。它的轮系机构的设计是为了适应于混合爬山,即,机器人能够开关之间的直线和螺旋爬升。该方法保证了机器人的轻量化和高爬的速度特征在早期的出版物,我们介绍了基本的设计概念和描述的原型实验机器人了。此外,混合爬山法已经证明,该修剪机器人可以高速的爬上爬下大树。在这里,我们报告我们开发机器人的进展,专注于直爬,善于不平坦的表面上的工作,和修剪。2先进的修剪机器人随着建设轻修剪的终极目标机器人,我们已经开发了一种新型的爬山法,采用无压或抓机制,而是依靠机器人本身的重量,像日本传统的伐木工不会爬树的时候(图1)。该用的一套杆和绳子,这是所谓的“burinawa,“不握不住或抓住树干,而他的质量中心位于树。是的,该可以用自己的重量停留在树上。基于这一新的林业产业的设计概念和要求,修剪机器人有了很大的发展。如图2所示,该机器人配备了四主动轮。轮1和2位于上侧,轮3和4位于下侧。每个轮由直流伺服电机、蜗轮驱动。摘要 本文介绍了一个伐木工的发展像修剪机器人。攀登主要是模仿在日本的timberjacks攀登方法。机器人的主要功能包括对外面的树进行修剪工作,和一个创新的爬山策略融合直线和螺旋式攀升的方式。这种新颖的设计带来了轻量化和高爬升速度特征的修剪机器人。我们报告我们在发展机器人进展,针对直爬,不平坦的表面上的工作、修剪。关键词 修剪机器人 爬壁机器人1引言日本木材工业已经进入下降的原因,木材价格下降和林业工人老龄化迅速。这导致了森林的破坏,导致在暴雨和山体滑坡的破坏山村地区。然而,在一个适当的配平状态修剪树是值得在上面投资的,因为其形成一个美丽的表面形成年轮。一个修剪机器人的发展对可持续森林管理的创新是很重要的。研究开发的修剪机器人15已经很少见了。2011年2月25日S.植木机械工程系,丰田民族院校丰田471-8525,爱知县,日本电子邮件:s_uekitoyota-ct.ac.jp川崎koganemaruH.K.人与信息系统工程系,岐阜大学,岐阜县,日本Y.石博marutomi有限公司,日本Y.森雪蛤karyuu兴业有限公司,岐阜县,日本这部分工作是在第十六届国际研讨会在人工生命与机器人项目展现的,日本,一月27日29日,2011年。87电池,质量中心位于一个错误的边缘,由于摩擦系数不明确、质量中心的位置可能被干扰。例如,机器人会倾斜,当它爬上一个不均匀的表面。在图2a,质心定位参数H =0.3M和W=0.22米,其中H为上轮和下侧面之间的距离轮,和W的表面之间的距离躯干和质量中心,如图3所示。分析表明机器人当D为0.25米,即使它倾斜约0.1拉德。控制器使用一个CPU板构成,配备了无线局域网。该控制器能够通信数据/命令与个人电脑通过无线局域网。每一轮由速度PI控制。通过一个高通滤波器的速度反馈输入附加。通过与第二个原型比较,第三原型重量轻,除控制器和电池。同时,控制器和电源分布在外部的第二个原型。第三原型也配备一个无线局域网和电锯。虽然的电锯细节在这里省略了,实验表明一个分支使用第三切削原型。3实验三实验进行评估的第三个原型。第一个实验是对其基本性能。第二个实验是评价其在不平坦的表面的性能。第三实验表明机器人是否可以修剪树枝。所有的实验使用替代树在室内进行。替代树直径的是0.25米的摩擦系数有效的替代树大约是0.4,这是小于这一自然的树。收集实验数据包括,该电机电流,机器人的位置和方向,机器人的测定,测量电机电流。使用分流电阻。测定位置的一个三维位置测量装置(OPTOTRAK,北数字)。用三维定位测量定位传感器(inertiacube2,InterSense)。图1。爬树方法使用“burinawa”图2。第三修剪机器人原型。照片图像。BCAD图像还原机制具有非回驾驶性能。每个车轮的转向角度也由直流驱动,伺服电机和蜗轮减速机构。在分析的基础上,79质量中心位于外树与控制器的重量。图3。对一棵树的修剪机器人三维图。侧视图。俯视图3.1基本性能直爬实验进行评估,机器人的基本性能。这四个预期的速度轮子是由梯形的简介。加速度0.2米/S2,和速度为0.2米/秒 ,车轮半径0.075米,。实验结果显示在图。4,5,和6。图4显示了机器人的速度。各自的速度从旋转编码器的值计算出轮。机器人能爬在0.2米/秒。虽然有一个约0.5由于控制法启动延迟,这是一个问题。图5显示移动的距离。它的实现是由一个三维位置测量设备,和移动的距离每轮计算从价值上的旋转编码器。在图5中,我们发现三种类型的错误:在距离误差的感动每一轮的三维位置测量之间装置(E1)之间的误差;轮1(或3)和2(或轮4)(E2);轮1和轮3之间的误差(误差之间的2和4轮轮)(E3)。我们考虑了两这些错误的可能原因。第一个是差异在每一轮的变形。移动的距离按0.075米的半径为每个车轮的每一圈。车轮是由聚氨酯合成的管,它是作用在它变形的力。它的变形量的大小取决于力。从理论上分析,79级在第三原型的力量往往是如下。的正常力近质心变得大于在对面的力。因此,填充扶手椅形=FN2FN3=FN1被认为是,在法国是正常的力的大小第一轮(E1)和(E2)可以这样解释。我们认为原因是滑移(E3)树干上的车轮。图6显示了电流在轮毂电机,这是由并联测量电阻。理论分析也表明,在下侧切向力大于上面。图6倾向于理论分析,不平坦的表面上安全使用的机器人正常工作,它必须在不平的树是强大的树干。总是会有由增长引起的颠簸一个修剪枝的遗迹。因此,直爬坡实验进行评估颠簸在树干修剪机器人的性能。这个实验在一个替代的凹凸进行。采用ABS塑料,和大于天然凹凸。在四轮所需的速度是由一个梯形了简介。加速度为0.2米/S2和速度为0.2米/秒,每0.075米半径的车轮。实验结果如图7所示,其中显示角度1的轨迹和2(参见图2B)。2角旋转对所有病例加方向,指示这个控制箱上升。这意味着,大众走向树中心。质量中心也走向了树当1角方向旋转正方向。这意味着减少摩擦力使机器人在树上。然而,在2个轮子的电流和4均大于在实验中连续电流。因此,有没有危险的机器人跌倒。此外,这些角度回到原来的方向,即使角度1和2发生了当一轮了凹凸。这些结果显示了良好的性能。3.3修剪试验进行实验,发现无论是第三原型可以修剪树枝。一个附加的电锯是由一个24V蓄电池直流电机驱动。机器人爬上螺旋的速度在0.03米/秒的直径的树该目标分为0.01米。图7。在每一种情况下滚角和俯仰角。一轮1过去的凹凸,B轮2通过凹凸,C轮3通过凹凸,D轮4通过凹凸图8。机器人与修剪修剪试验,实验的场景如图8所示。在这个实验中,树枝被切断,只留下一个短暂的残这是小于0.005米,与树干没有受伤。4结论一个伐木工像修剪的发育进程,机器人已经被描述,针对直爬,其在不平坦的表面行为,修剪树枝。的实验表明,直爬第三原型给了一个很好的基本性能。攀爬的结果在不平坦的路面上试验中表现出良好的鲁棒性颠簸,因为真正的树最凸起的小比实验碰撞。此外,修剪试验还表明第三的原型可以修剪树枝从一棵树。在今后的工作中,我们希望在实际环境中的机器人测试,试着做一些进一步的改进。工具书类1。张军军,等人2009年开发行道树爬壁机器人木本。2009促进了程序,1A2D07的发展。2。kushihashiY,等人2006年发展了结构测量抓树力修剪树,攀爬修剪机器人木本(日本)。2006年开展程序与机器人与机电一体化会议。3。Suga Y,等人2006年开发攀树和修剪机器人木本。执行器布置在臂端为了旋转运动(日本)。促进了si2006,PP126712684。Yokoyama T, Kumagai K, Arai Y,等人(2006)评估了树枝修剪机器人地图构建系统的绩效(日本)。在2006年开展了程序和机器人机电一体化会议。5。Yamada T, Maeda K, Sakaida Y,et al(2005)研究用于机器人的修剪系统:发展了机器人样机单元(日本)。开展了机器人2005日本机械学会与机电一体化会议。6。圣隶工业。http:/www.seirei.com/products/fore/ab232r/ab232r。HTML。2011年5月可以访问7。Kawasaki H, Murakami S, Kachi H,等人(2008)分析与实验新型爬山法。开展了2008,PP 160163的SICE会议。8。Kawasaki H, Murakami S, Koganemaru K,等人(2010)开发一个用其自身的重量的修剪机器人。促进455CLAWAR2010,PP463行业的发展9。Kato T, Koganemaru K, Tanaka A,等人(2010)开发的一个利用自身的重量的修剪机器人(日本)。促进着rsj2010,名古屋的发展。11
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