顺槽架空人车及其减速器的设计【含CAD图纸+文档】
收藏
资源目录
压缩包内文档预览:(预览前20页/共65页)
编号:37128200
类型:共享资源
大小:4.54MB
格式:ZIP
上传时间:2020-01-05
上传人:机****料
认证信息
个人认证
高**(实名认证)
河南
IP属地:河南
50
积分
- 关 键 词:
-
含CAD图纸+文档
架空
及其
减速器
设计
CAD
图纸
文档
- 资源描述:
-
压缩包内含有CAD图纸和说明书,均可直接下载获得文件,所见所得,电脑查看更方便。Q 197216396 或 11970985
- 内容简介:
-
摘要 进入21世纪,科学技术有着飞速的发展,伴随着科学技术的发展机械制造技术也有了较大的发展。面对我国经济近年来的快速发展,机械行业的壮大,在国民经济中占重要地位的制造业领域得以健康快速的发展。由于减速器应用广泛,为了提高质量,降低成本,便于专业化生产和用户选用,使得作为制造行业重要设备的各类机加工艺装备也有了许多新的变化。设计既是产品开发周期中的关键环节,有贯穿于产品开发过程的始终。设计决定了实现产品功能和目标的方案,结构和选材。制造手段以及产品运行,使用和维修方法。设计不合理会导致产品功能不完善,成本提高或可靠性,安全性不好。产品设计上的缺陷造成的先天不足,难以采取制造和使用措施加以弥补。少数情下,即有可能,损失也大。严重的设计不合理甚至会造成的产品不能用或产品制造不出来,导致产品开发失败。减速器的装配图是用来表达减速器的工作原理及各零件间装配关系的图样,也是制造、装配减速器和拆绘减速器零件图的依据,故附减速器装配图。关键词:机械制造技术;减速器;优化设计 1Abstract Enter the twenty-first Century, science and technology have developed rapidly, with the development of science and technology of mechanicalmanufacturing technology has made great progress.With the rapid development of Chinas economy in recent years,machinery industry growth, occupy the important position in the nationaleconomy in the manufacturing industry can be healthy and rapid development. The speed reducer is widely used, in order to improve the quality, reduce the cost, convenient for the specialized production and the user selects, making all kinds of machining equipment as an important equipment manufacturing industry also has many new changes.Design is not only the key link in the cycle of product development, hasconsistently throughout the product development process. The designdetermines the realization of product function and objectives of thescheme, structure and material. Running manufacture method as well as the product, use and repair method. The design unreasonable can cause the product function is not perfect, cost and reliability, the security is not good. The product design defects caused by the hard to be congenitally deficient, take measures to make up for the manufacture and use of. In a few cases, where it is possible, the loss is great.Serious design unreasonable or even cause the product can not be used or product does not come out, cause product failure.The reduction gear assembly drawing is used to express assembly relation principle of gear reducer and parts manufacturing, assemblydrawings, but also speed reducer and the demolition of paintingreducer parts drawing basis, therefore attaches the reducer assembly drawings.Keywords: Machinery Manufacturing Technology Retarder OptimumDesignI前 言本方案设计的顺槽架空乘人装置由驱动部、改向装置、机头乘人站、乘人器、托压绳轮组、机尾乘人站、回绳张紧装置、牵引钢丝绳、电气控制等几部分组成。由机头驱动绳轮牵引钢丝绳,乘人器卡在钢丝绳上随之运动,随着巷道的起伏而变化,保持距地面200mm 高度。机头是驱动部分,钢丝绳在机头绳轮处换向,围包角180。机头绳轮中镶有聚氨酯绳衬,用来提高摩擦力,并减少钢丝绳的磨损。驱动单元设置为电动机+制动器+减速器+驱动绳 轮方式,具有结构驱动紧凑,分体、运输、安装灵活,运行安全可靠,故障率低、噪音低等优点。将钢丝绳安装在驱动轮、托绳轮、压绳轮、迂回轮上并经张紧装置拉紧后由驱动装置输出动力带动驱动轮和钢丝绳运行,从而实现输送矿工的原理。用地下矿用架空索道来输送矿工,其目的是缩短矿工上下井的路途时间,减轻矿工上下井的体能消耗。iii目录摘要.11 绪论. 31.1 国内矿井辅助运输现状分析. 31.2 架空乘人装置概况. 41.2.1 架空乘人装置发展史. 41.2.2 架空乘人装置结构. 51.2.3 托轮与压轮的应用. 51.2.4 防掉绳装置的应用. 71.2.5 架空乘人装置的应用效果. 81.2.6 地下矿用架空索道的特点. 81.2.7 架空乘人装置的基本形式. 91.2.8煤矿安全规程对架空乘人装置的规定. 92 设计总体方案. 102.1 矿井原始条件及主要参数. 102.1.1 原始参数. 102.1.2 其他参数. 102.2 电动机功率及型号. 122.2.1 电动机功率计算. 132.2.2 电动机的选择. 132.3传动装置选择及计算. 122.3.1 传动方案确定. 132.3.2 基本参数计算. 142.3.3 齿轮设计. 152.4 轴的结构设计. 252.4.1 第一轴设计. 25 2.4.2 第二轴设计. 262.4.3 第三轴设计. 272.4.4 第四轴设计. 28 2.5 轴的校核. 2 92.5.1 第一轴(传动轴). 2 92.5.2 第二轴(输出轴). 3 22.5.3 第三轴(输入轴). 362.5.4 第四轴(传动轴). 393箱体. 42 3.1 箱体的结构设计.4 2 4 设备的使用和维护. 43 4.1 钢丝绳的使用维护.4 44.2 轴承的润滑与密封. 45 4.3减速器的润滑. 4 5 参 考 文 献 .46 外 文 翻 译 .47 总 结 .60 致 谢 .61v 1 绪论1.1 国内矿井辅助运输现状分析 矿井辅助运输是指井下的材料、设备和人员的运输,有时也包括排矸石运输。其特点是运输类型多、运送去向多、巷道条件多样。类型多表现在既运物又运人,物品中有整件、散件,大小长短轻重差别很大,运送去向多是指需要运到各工作面和井下一切场所。 随着矿井开采规模的不断扩大和井下开拓距离的不断延伸,上下井的材料设备和增多。特别是综合机械化采煤掘进的发展,产生的集中化程度日益提高,重型设备大量在采掘工作面应用,如何保证其不间断地连续高产稳产,高效地进行工作面设备搬家运 输成为重要又急需解决的问题。 建国以来,我国矿井辅助运输作业变化不大,基本上还是小绞车、无机绳、回柱绞车、小蓄电池车在普通钢轨上牵引矿车、运料车或平板车,装卸利用手动葫芦撬棍,甚至人推肩扛,占用大量人力物力,严重阻碍着矿井产量进度和劳动生产率提高,与国外先进产煤国家相比差距很大。辅助运输的落后已成为建设现代化矿井和提高矿井全员效率的最大障碍之一。发展辅助运输机械化不仅可以大量节省人员,而且可以提高工时利用,增加采掘工作面产量进度,大量减少设备搬家停运时间提高设备利用率,从而节约设备折旧或租赁费用,还能改善采掘工人和辅助作业的劳动安全条件。确实是当前煤矿技术发展的关键和当务之急。 我国煤矿地质条件多种多样,矿井规模大小各异,开拓布置和开采方式也不尽相同,因而解决辅助运输机械化问题必须采取多条技术途径,多种系统模式,多样技术装备,认真借鉴国内外成功经验,因地制宜地结合具体条件择优选用。对于每个生产和新建矿井都应根据实际条件进行可行性研究和各种方案的比较,然后再作出在技术经济上最合理的决策。 目前,国内外矿井辅助运输设备已形成单轨吊、齿轨车、卡轨车、齿轨卡轨车、无轨胶轮车和胶套轮机车几大类型。每种设备都有一定适用的条件和范围,都有其长处和优势, 也有其短处和劣势。在一定条件下的优势在另一种条件下又可能变为重要的制约因素。因而对于各种矿井条件下选用何种设备和系统,需要认真分析,综合对比,进行全面地可行性研究后才能最后决策。 矿井辅助运输是 1 个完整的复杂的系统,必须从系统工程的角度加以研究分I 析和运筹决策。1 个大型矿井的辅助运输系统包含材料、设备、人员以及矸石等 各个子系统。而每个子系统中的负载或容器又从地面车间、仓库、料堆、排矸场 起,经过入井、大巷运输、上下山和采区运输、各处中转转载直接到工作地点卸 载等环节,然后由反向运行,经上述 系列环节出井才算完成 1 个循回。而同时各 个子系统又根据运输负载对象的特点分成若干个子系统。每个矿井辅助运输系统 或子系统都有某些特定要求,但其共同的基本的要求是: (1)从供应地点到使用地点的直达运输,尽量减少转载停顿和倒状环节。(2)使用结构和尺寸合理并便于机械化装卸的车辆、集装箱或其他容器, 减少工人装卸工作量,减低物料损耗。 (3)最大限度的保证运输系统安全可靠和快速重载,有完善的信号联络, 制动停车和自动监控系统。(4)合理组织运输调度,根据矿井生产建设地点的需要,有计划地编制作业 图标优化车次顺序和物料批量编组,提高运输效率,降低运输费用。根据以上要求不论是新建矿井或是改扩建矿井,都要在认真分析煤层地质条件矿井规模和开采设计的基础上,进行全面细致的技术经济可行性研究和方案对比,才能作出正确的决策。对于现有矿井特别是多水平多采区的大型矿井的辅助运输系统的技术改造,应采取既积极又慎重的态度,注意因地制宜,分期分布,从局部采区到全矿井,争取少花钱多办事,讲求整体的实际的经济效益。矿井的辅助运输系统需要多种设备和设施,不仅要用单轨吊、齿轨车、卡轨车、无轨胶轮车等主机设备,而且需要各种平板车、支架车、集装箱、铲车、人车、多用车、油罐车、各种地轨、吊轨、弯道、岔道、绳轮以及物料装卸存放硐室,等设施;各种设备物料的吊装、卸载、倒运、打捆等机械化高效的机具装置;以及各种维修辅助运输设备的机车库、被艰库、油库等。一个大型矿井往往需要几十台机车,有几十公里轨道,有的还可能是架线机车单轨吊,架线机车卡轨车,齿轨卡轨车,卡轨车单轨吊,加线机车无轨胶轮车等几种设备的混合系统。因而更需要各种设备互相很好地衔接和配套。 配套不完善或辅助设施装置工具不全,往往难以发挥新型设备的作用,是辅助运输系统效率不高的重要原因,这是一个应该引起重视的问题。必须同步的配套的进行装备,同时建立相应得设施,才能真正解决辅助运输机械化,提高全矿井的劳动生产率。对辅助运输设备有以下要求:1)、安全可靠;2)、能在水平、倾斜和转弯的巷道中连续运行不需要转载;3)、运输距离可变化;4)、成件设备不解体正运;5)、能运多种材料和设备;6)、易于装卸;7)、辅助操作少,使用方便;1.2 架空乘人概况1.2.1 架空乘人装置发展史 在远古时代,人们就已使用树藤,竹篾和麻绳作为缆索进行空中运输,我国在公元 2000年的三国时期就有筑吊桥为空中通道的记载。根据康熙图录可以看出,此空中通道犹如现在的客运索道。到了唐宋末年间,在南方常有利用竹篾编成溜索,作为跨河流、越深谷的交通工具。1644 年,荷兰用麻绳架起了第一条货运循环式索道。但是麻绳、溜索的强度都很低,限制了索道的发展。直到 19 世纪中叶,钢丝绳进入工业生产以后,才为建立近代的索道提供了可能性,1834 年,钢索架空索道的雏形问世,接着英国技师在 1867 年对架空索道作了研究改进。根据查考,奥地利阿巴奇在 1870 年获得索道报索器专利,并于 1873 年德国用它架设了活动循环式双线货运索道。1874 年英国又第一次建设了往复式货运索道。从此这种新型的运输设备,在世界上开始了迅速的发展。现在货运索道广泛应用于采矿工业、煤炭工业、电力站及建材企业,码头以及军事等各个部门。 我国第一条双线索道大约建立在 1910 年前后,而第一条单线索道约建于1927 年间。到解放前夕,约建有索道 20 余条。从 1949 年至今,约建单线索道 50 余条,双线索道 30 余条,总长约 380 公里,每小时货运量达到 7000 吨。在货物运输中发挥了显著作用。1.2.2 架空乘人装置结构 地下矿用架空索道,俗名猴车,主要用于地下矿山,由驱动部,托绳轮,回绳张紧装置,乘人器,牵引钢丝绳,电控系统等组成。它适用于长距离,大断 面,服务时间长度倾斜巷道,如上山等;牵引钢丝绳是无极绳,由巷道两边的托 绳轮架设,不间断地循环运行。它与断面小,多起伏,多变坡的顺槽不相适应, 不能满足采煤面推进不断移动,不影响顺槽轨道运输的要求。将钢丝绳安装在驱动轮、托绳轮、压绳轮、迂回轮上并经张紧装置拉紧后,由驱动装置输出动力带动驱动轮和钢丝绳运行,从而实现输送矿工的原理。用地下矿用架空索道来输送矿工,其目的是缩短矿工上下井的路途时间,减轻矿工上下井的体能消耗。本方案设计的顺槽架空乘人装置由驱动部、改向装置、机头乘人站、乘人器、托压绳轮组、机尾乘人站、回绳张紧装置、牵引钢丝绳、电气控制等几部分组成。由机头驱动绳 轮牵引钢丝绳,乘人器卡在钢丝绳上随之运动,随着巷道的起伏而变化,保持距地面 200mm 高度。机头是驱动部分,钢丝绳在机头绳轮处换向,围包角 180。机头绳轮中镶有聚氨酯绳衬,用来提高摩擦力,并减少钢丝绳的磨损。驱动单元设置为电动机+制动器+减速器+驱动绳轮方式,具有结构驱动紧凑,分体、运输、安装灵活,运行安全可靠,故障率低、噪音低等优点。 机尾有一从动绳轮,钢丝绳在此换向。整个机尾可在一滑道内滑动,在重锤张紧部分的拉动下,张紧主传动钢丝绳。托轮是用来在中间段承载,承受钢丝绳、乘人、乘人器的重量。托轮中也镶有聚氨酯衬。乘人器采用活动抱索器,其顶部有悬挂在牵引钢丝绳上的抱索器 , 下端有一座板,中间有一横杆用来挂工具包或乘人趴在上面,最下面是蹬杆。其设计符合人机工程学,人在其上的坐姿接近日常生活中的坐姿,安全舒适,克服了乘人抱杆、重心后仰的缺陷。拉紧部分采用动滑轮结构,拉紧重锤可节省一半,并且调整重锤高度简单,单人即可操作。电气控制部分用来控制乘人装置的主电机运行、停车,制动抱闸的开闭,打滑时可自动停车,在沿线布置有紧急停车点,出现紧急事故时可快速停车。具有通讯距离远,抗干扰能力强,可并网与全矿安全监视系统实现通讯。 1.2.3 托轮与压轮的应用 由于煤下山巷道条件较差,巷道倾角 1025,平均 24。在巷道直线段采用单 轮托轮,可以承受较轻载荷,在凸弧段采用多轮托轮承受较大载荷。由于机头变坡处 凸弧角度较大,无论是上行侧还是下行侧,都须承受较大载荷,故采用双绞支轮托轮(如 图 1-1 所示)。 图 1-1 双绞支四轮托轮使 4 个托轮共同承受载荷,可在受冲击时退让,有效地降低冲击,减缓磨损,提高乘坐的舒适性和托轮的使用寿命。正常直线段托轮设计成快速拆装单轮托轮结构,可以承受较轻载荷, 单人即可从托轮架上拆下,维修方便,托轮上下高度可通过顶杆调节,左右位置可调节托轮架。在凹弧段针对钢丝绳打梁的问题,采用单轮压轮和多轮压轮,使钢丝绳在凹弧段折曲,可以有效地避免绳打梁,并且在压轮前后 11.05m 处增加单轮托轮,以防掉绳(如图 1-2 所示)。 图 1-2 托轮与压轮安装方式 1.2.4 防掉绳装置的应用 在安装误差或调整不好的情况下,如:凹弧段处、凸弧段前后较容易掉绳,加装防掉绳托轮(压轮)和限绳器,可收到较好的效果。防掉绳托轮(压轮)有一拨盘机构(如图 1-4 所示)。1-拨盘;2-挡板;3-螺栓;4-托轮(压轮)图 1-4 放掉绳托轮(压轮)正常运行时,拨盘随托轮(压轮)转动,挡住钢丝绳,使之不能脱出绳槽,乘人器通过时,乘人器卡爪拨动拨盘转动,乘人器通过后,拨盘继续挡住钢丝绳,从而达到防掉绳的目的。 限绳器是在原托轮架上加装一转动挡绳板,正常运行时挡绳板自然下垂,与托轮外缘端面处在同一平面,相距 1015mm,挡住钢丝绳,当乘人器通过时,乘人器卡爪拨动挡绳板,通过后,挡绳板依靠重力恢复下垂,继续挡住钢丝绳,也达到防掉绳的目的(如图 1-5 所示)。 1-挡圈; 2-螺栓; 3-轴套;4-挡绳板;5-托轮;6-螺栓; 7-夹板; 8-轴 图 1-5 限绳器1.2.5 架空乘人装置的应用效果 架空乘人装置自安装投入使用后,进行了最大功率测试试验和满乘人运转试验, 与斜巷人车进行了比较。架空乘人装置有以下突出效果:架空乘人装置造价安装费较斜巷人车低;架空乘人装置乘人器过托轮无振动,乘人器按人机工程学设计,乘坐安全、舒适、可靠; 架空乘人装置驱动功率小,机头部分结构紧凑,运行噪音低;托轮安装方式简单快速,更换维护方便容易;机头驱动轮、机尾从动轮、托轮及压轮都采用聚氨酯绳衬,使钢丝绳的磨损大大低于斜巷人车,故障率较低;架空乘人装置每小时乘人数量300 余人,效率较斜巷人车高;电控部分保护齐全、可靠,安全系数高;操作简单方便,可实现多点开车、停车。可实现无人值守,遥控监视。我国的煤矿生产在国民经济中占有重要的地位,但是煤炭生产的自动化程度与发达国家相比仍有很大差距,提高煤矿机械自动化程度,改善工人的劳动环境仍然是煤矿现代化的重要任务。由于煤炭储藏面积分布复杂的原因,煤炭生产的运输系统结构庞大,在生产成本中占有重要的成分,在人员运输方面,技术设备相对落后。(1) 安全性、舒适性差; (2)乘人的时间、速度受限; (3)通信联络功能少,信息传输的可 靠性差。1.2.6 地下矿用架空索道的特点 乘坐时乘人离地近(0.2m),钢丝绳运行速度低(定抱索器时 0.8 1.2m/s),确保矿工乘坐安全;上下车有机头和机尾乘人站,上车时,乘人需乘人器通过给进器上的闭上逐锁器吊挂到上车滑到上,从上车滑到步加速,获得与钢丝绳相同的速度后,钢丝绳带动乘人器一起运行。下车时,乘人器从运行钢丝绳上过渡到下车滑到,沿下车滑到逐步减速到静止;不掉绳可靠的防掉绳和轮系装置,使运行中的钢丝绳不掉绳。高效率运量可达到 2001000 人/小时,运距可达到 3500 米,倾角可达到 40 度,变坡点可达 20 个以上。共巷 道运人和运料可共用巷道,节约巷道建设投资。 投资低 猴车投资只占斜井人车投资的 50%左右,且占地面积又少,安全性能更高。1.2.7 架空乘人装置的基本形式 架空乘人装置的基本布局形式有驱动装置悬空式、驱动装置落地式、往复式 混合架空运送装置和零速度上下车架空乘人装置,如下图 1-6 所示: 图 1-61.2.8煤矿安全规程对架空乘人装置的规定 煤矿安全规程对用架空乘人装置运送人员有如下规定:(1) 、巷道倾角不应超过 25,否则必须制订安全措施,报矿物局总工程师 批准,但最大不得超过 30; (2)、蹬坐中心至巷道一侧的距离不得小于 0.7m,运行速度不得超过 1.2m/s;(3)、驱动装置必须有制动器;(4)、吊杆和牵引钢丝绳之间的连接不得自动脱扣; (5)、在下人地点的前方,必须设有能自动停车的安全装置;(6) 、在运行中人员要坐稳,不得引起吊敢摆动,不得手扶牵引钢丝绳,不 得触及邻近的任何物体;(7)、严禁同时运送携带爆炸物品的人员; (8)、每日必须对整个装置检查一次,发现问题及时处理。2 设计总体方案2.1 矿井原始条件及主要参数2.1.1 原始参数 (1) 井长: 1800m (2) 吊椅间距: a20m (3) 运行倾角: 10 (4) 运行速度 :v1.2m/s (5) 寿命: h=5000h (6) 每小时运人量: 200 人 2.1.2 其他参数 (1)、托绳轮间距l = (0.85,1.15 2.13)a取 l = a = 20 (2)、驱动轮围包角即主导轮与钢丝绳的围包角 180 (3)、 吊椅质量:G0=5kg 人员质量: G=70kg59 2. 2电动机功率及型号 2.2.1 电动机功率计算(1)、驱动轮即摩擦轮直径确定 D(8085)d =(8085)20=16001700 mm D=1600 mm(2)、稳定运行时功率 2.2.2 电动机的选择按值和环境条件选择 YB2 新型矿用防爆电机: 电动机型号为:YB2 280M6 型 相关参数:功率55KW 转速 980 r/min 效率 92.8%外型参数参考机械设计手册。2.3 传动装置选择及计算2.3.1 传动方案确定 减速器可以选择多种形式,如:行星齿轮件速器,蜗轮蜗杆减速器, 圆柱齿轮减速器,圆锥圆柱齿轮减速器。这里选用圆锥圆柱齿轮减速器。 2.3.1.1 减速器的运动简图 如图 2-2 2.3.1.2 减速器的设计依据设计垂直传动三级减速器的齿轮传动 电动机功率 P=55Kw转速 n=980r/minni = 电动机n驱动轮n驱动轮= 60v =pD 60 1.453.14 1600 10-3= 17.37r / minn则i = 电动机n驱动轮= 980 = 56.4317.37总传动比 i 总=56.43 2 .3 .2 基本参数计算 2.3.2.1 传动比的分配 锥齿轮的制造工艺复杂,大尺寸的锥齿轮加工更复杂,因此在设计时应尽量减少其尺寸。如在传动中间同时有锥齿轮传动和圆柱齿轮传动时,应尽可能将锥齿轮传动放在高速级,这样可使设计的锥齿轮的尺寸较小,便于加工。为了使大锥齿轮的尺寸不致过大,通常,齿数比i5 则 2.3.2.2 各轴的运动参数计算及各轴计算的转速、功率和扭矩减速器效率: 轴承= 联轴器=0.99 齿轮=0.97(输入轴即电机轴) 转速 n1=980r/min 电动机功率 P1=55Kw 扭距 (一级传动) 转速 电动机功率P2=P1* 联轴器=54.45KwP扭距 T2=9550 2n 2(二级传动)n=1857.13N.m转速 n3=2 =70r/mini2电动机功率P3=P2* 轴承* 齿轮=52.28KwP3n扭距 T3=95503(三级传动)n=7132.48N.m转速 n4=3 =17.37r/mini3电动机功率 P4=P3* 轴承* 齿轮=50.2KwP扭距 T4=95504 =27599.88N.mn4 2.3.3齿轮设计 2.3.3.1 一级锥齿轮传动已知条件:传动功率 P=P1=55kw(电机高速轴)转速 =980r/min 扭距 T1=535.97 N.m传动比 i1=3.5原动机为电动机。减速器是用闭式传动通常采用齿面硬度350HBS 的硬齿面钢制齿轮。根据计算准则, 应该按齿轮弯曲疲劳强度设计,确定齿轮传动的参数、尺寸,然后演算轮齿的弯曲疲劳强 度。(一)选择材料、热处理方法及精度等级1.齿轮材料、热处理方法及齿面硬度 题意知应采用硬齿面齿轮组合,齿面硬度大致 相同,综合考虑,根据表9.6:小齿轮选用 40Cr,表面淬火,齿面硬度 4 855HRC,大齿轮选用 45 号钢,表面淬火,齿面硬度 4050HRC。2.精度等级减速器为一般齿轮传动,估计圆周速度不大于8m/s,根据表 9.8,初 选 7 级精度。3.对闭式硬齿面传动,因是按弯曲疲劳强度进行设计,当模数一定时,齿数少,分度圆 直径小,为使结构紧凑,可选取较小的齿数,通常=1820.高速齿轮或对噪声有严格要求 的齿轮传动建议取 综合考虑选小齿轮齿数 Z1=24; (二)按齿轮弯曲疲劳强度设计齿轮由于是硬齿面的闭式齿轮传动,齿轮承载能力应由轮齿齿根弯曲疲劳强度决定 校核公式 模数公式 1.确定公式内的各参数取值(1)试选载荷系数 Kc=1.3(假设值)(2)计算小齿轮传递的转矩 =535970N.mm (3)齿宽系数 R=b/r,一般取 =0.250.35 R=0.3(表9.12)(4)由图9.23 按齿面硬度中间值 52HRC 查的小齿轮弯曲疲劳极限 由图 9 .23 按齿面硬度中间值 45HRC 查的大齿轮弯曲疲劳极限 (5)计算弯曲疲劳许用应力令时效概率为 1%,弯曲最小安全系数由表 9.13 取得 =1.25,弯曲寿命系数由图9.24 取得1.0,尺寸系数Y由图9.25取得1.0,由式得出 (6) 当量齿数 有分锥角得 (7)由图9.29 查的齿形系数 YFa1=2.617 YFa2=2.137 由图9.30应力校正系数 YSa1=1.694YSa2=1.835 (8)重合度系数 得2.计算(1)计算小齿轮大端分度圆直径 d1c =6.32mm 则 d1c = m1cZ1=6.3224=151.68mm(2)计算圆周速度 V1= = p 151.68980/(601000) =7.8m/s100N/mm由表9.9 查得齿间载荷分配系数 =1.0,由表9.10查得计算公式=1.0+0.311+0.6(b/d1c)2(b/d1c)2+0.1910-3b=1.0+0.311+0.6(50.56/151.68)2(50.56/151.68)2+0.1910-350.56=1.046按图9.15由和查得 KF=1.033故载荷系数 K=KA KV KF=11.121.01.033=1.16(5)按实际载荷系数校正所算的得分度圆直径,由d1= d1C 3 K KC=151.68 3 1.16 1.3=146.03mm(6)模数 m =d1/Z1 =146.03/24=6.08mm由表9.1取标准模数第一系列中得值 m = 6mm(7)校核 抗弯强度足够。3.几何尺寸计算 (1)锥距 (2)实际大端分度圆直径 (3) 查文献可知 (4)分度圆锥角 d 2 = 2.5 = 68.2 d1 = 90 - d 2= 21.8 (5)齿顶高 ha = m = 6mm (6)齿根高 hf = 1.2m = 7.2mm (7)齿全高 h =2.2m = 13.2mm (8) 齿顶间隙 c =0.2m = 1.2mm (9)齿顶圆直径 da1 = d1+2m cos1 = 155.16mm da2 = d2+2m cos2 = 508.44mm (10)齿根圆直径df1 = d1-2.4m cos1= 130.61mm df2 = d2-2.4m cos2= 498.67mm (11)齿宽 b =0.3 R =78mm (12)齿顶角q =haR= 1.77 (13)齿根角h f q f =R= 2.13 (14)根锥角 d f 1 = d1 - q f d f 2 = d 2 - q f= 19.67= 66.07 (15)顶锥角d a1 = d 1 +q a = 23.57d a 2 = d 2 + q a = 69.97 4结构设计(锥齿)如图 2-3图 2-32.3.3.2 二级直齿圆柱齿轮设计已知条件:传递功率 P = =54.45kw , 主动轮转速 n2 = =280 r/min 传动比 =4, 载荷平稳,扭矩 T2 = =1857.13N.m , 原动机为电动机.(一)选择材料、热处理方法及精度等级 1.齿轮材料、热处理方法及齿面硬度 由表9.6小齿轮选用 40 Cr,表面淬火,齿面硬度 4855HRC,大齿轮选用 45号钢,表面 淬火,齿面硬度 4050HRC. 2.精度等级 减速器为一般齿轮传动,估计圆周速度不大于 6 m/s,根据表 9 .8 ,初选 8 级精度。3. 根据上面提到的小齿轮齿数选取原则取小齿轮齿数 Z3=20, Z4=iZ3=4 20=80(二)按齿轮弯曲疲劳强度设计齿轮 由于硬齿面闭式齿轮传动,齿轮传载能力应由齿轮齿根弯曲疲劳决定 弯曲校核公式: 模数计算公式 : 1.确定公式内的各参数取值(1)试选载荷系数 Kc=1.4(2)计算小齿轮传递转矩T2= T=1857.13N.m=1857130N.mm (3) 根据表9.12 选取齿宽系数 Yd =1.0(4) 由图9.23按齿面硬度中间值52HRC 查得小齿轮弯曲疲劳极限=600N/mm2 由图9.23按齿面硬度中间值45HRC 查得小齿轮弯曲疲劳极限=450N/mm2 (5)算弯曲疲劳许用应力取失效概率 1% 安全系数由表 9 .13 取=1.25 ; 由 图 9. .2 4 取 得 弯 曲 寿 命 系 数 ; 由 图 9 . 2 5 取 得 尺 寸 系 数 由 式 得 出 (6)由图9.21查得齿形系数 由图9.22查的应力校正系数 (7)重合度系数2.计算(1)计算小齿轮大端分度圆直径 d2c 由齿轮弯曲疲劳强度设计模数 =6.8mm 则 (2) 计算圆周速度 = 2.00m/s100N/mm 由表 9 . 9 查得齿间载荷分配系数 = =1.0由表9.10查得计算公式=1.0+0.311+0.6(b/d1c)2(b/d1c)2+0.1910-3b =1.37由和b/h的值在图9.15查的齿向载荷分配系数故载荷系数 K = KA KV = 1 1.06 1.0 1.46= 1.55 (6)按实际载荷系数校正所算得的分度圆直径,得 d2 =d 2c3 k kc= 1363 1.551.4= 140.69mm (7)计算模数 m m = d2/Z3 = 140.69/20 = 7.03mm 取标准模数第一系列中的值 m = 8mm (8)取齿形系数和应力校正系数 由图9.21查得 齿形系数 YFa3 = 2.80YFa3 = 2.22 图9.22 应力校正系数 YSa4 = 1.55 YSa4 =1.77 (9)校核 3.几何尺寸计算 (1)分度圆直径 d3 = mZ3 = 160mm d4 = mZ4 = 640mm (2)中心距 (3)齿宽 b = 1.0 160 = 160mm 取 b4 = 160mm b3 = b4+(510) = 160+10 = 170mm (4)齿顶高*ha = ham = 1 8 = 8mm(5)齿根高*hf = (ha+c *)m = (1+0.25) = 10mm(6)齿全高h = ha+hf = 8+10 = 18mm(7)齿顶圆直径*da3 = (Z3+2 ha*da4 = (Z4+2 ha)m = (20+2 1) 8 = 176mm)m = (80+2 1) 8 = 656mm(8)齿根圆直径*df3 = (Z3-2 ha*df4 = (Z4-2 ha*-2c*-2c)m = (20-2 1-2 0.25) 8 = 140mm)m = (80-2 1-2 0.25) 8 = 620mm(9)基圆直径db3 = d3cosa = 1600.94 = 150.35mm db4 = d4cosa = 6400.94 = 601.4mm(10)周节P = p m = 25.12mm(11)齿厚S = pm225.12=2= 12.56mm(12)齿间宽pme = 12.56mm2(13)顶隙c = m = 0.25 8 = 2mm4.结构设计(直齿)2.3.3.3 三级直齿圆柱齿轮设计 已知条件: 传递功率P = P =52.28kw主动轮转速 n3 = n =70 r/min传动比 i3 =4.03 载荷平稳,扭矩 T3 =T=7132.48N.m 原动机为电动机(一)选择材料、热处理方法及精度等级1.齿轮材料、热处理方法既齿面硬度 题意对齿轮传动比无特殊要,可选一般齿轮材料,由表 9.6 小齿轮选用 40 Cr,表面淬火,齿面硬度 4855HRC,大齿轮选用 45号钢,表面淬火,齿面硬度 4050HRC.2.精度等级减速器为一般齿轮传动,估计圆周深度不大于 6 m/s,根据表 9. 8,初选 8 级精度。3.选小齿轮齿数根据上面提到的选取原则取Z5=20 Z6 =iZ5=4.03 20=81(二)齿轮弯曲疲劳强度设计齿轮 由于硬齿面闭式齿轮传动,齿轮承载能力应由齿轮弯曲疲劳强度决定,弯曲应力为校核公式 模数设计公式 1.确定公式内的各参数取值(1)试选载荷系数 Kc=1.6(2)计算小齿轮传递转矩T3= T=7132.48N.m=7132480N.mm(3)选取齿宽系数Yd =1.0(4) 由图9.23按齿面硬度中间值 52HRC 查的小齿轮弯曲疲劳 由图9.23按齿面硬度中间值 45HRC 查的大齿轮弯曲疲劳(5) 计算弯曲疲劳许用应力:取时效概率 1%;安全系数由表 9 .13 取 =1.25 由图9.24取得弯曲寿命系数,由图9.25取得尺寸系数 由得出 (6)由图9.21 查得齿形系数 =2.80,图9.22应力校正系数 =1.55 (7)重合度系数2.计算(1)计算小轮分度圆直径 d3C =9.86mm 则 d3c= m3cZ5=9.86 20=197.2mm(2)计算圆周速度 = 2.72m/s100N/mm 由表9.9 查得 由表9.10查得计算公式=1.0+0.311+0.6(b/d1c)2(b/d1c)2+0.1910-3b =1.35 由和b/h的值在图9.15查的齿向载荷分配系数 故载荷系数 K = KA KV KF a KF b= 1 1.03 1.0 1.44= 1.48(6)按实际载荷系数校正所算得的分度圆直径,得d3 =d 3c3 kkc= 197.23 1.481.6= 192mm(7)计算模数 mm = d3/Z5 = 192/20 = 9.6mm取标准模数第一系列中的值 m = 10mm(8)查取齿形系数和应力校正系数 由图9.21查得 齿形系数 YFa1 = 2.80YFa2 = 2.268 由图9.22查的应力校正系数 YSa1 = 1.55 YSa2 =1.736(9) 校核 1= 3.几何尺寸计算( 压力角a = 20 o 标准值 )(1)分度圆直径d5 = mZ5 = 10 20 = 200mm d6 = mZ6 = 10 81 = 810mm(2)齿顶高*ha = ham = 1 10= 10mm(3)齿根高*hf = (ha+c *)m = (1+0.25) 10= 12.5mm(4)齿全高h = ha+hf = 10+12.5= 22.5mm(5)齿顶圆直径*da5 = (Z5+2 hada6 = (Z6+2 ha)m = (20+2 1) 10 = 220 mm)m = (81+2 1) 10 = 830 mm(6)齿根圆直径*df5 = (Z5-2 hadf6 = (Z6-2 ha*-2c*-2c)m = (20-2 1-2 0.25) 10 = 210mm)m = (81-2 1-2 0.25) 10 = 785mm(7)基圆直径db5 = d5cosa = 2400.94 =225.53mm db6 = d6cosa = 7560.94 =710.41mm(8)周节P = p m = 3.14 10=31.4mm(9)齿厚S = pm237.68=2= 18.84mm(10)齿槽宽pme = 18.84mm2(11)顶隙*c = cm = 0.25 10= 2.5mm(12)中心距11a =(d1 +d2) =2(200+810) = 505mm2(13)齿宽b = y d5= 1.0 200 = 200mm取 b6 = 240mm图 2-4b5 = b+(5410) = 240+10 = 250mm4.结构设计(直齿)如图 2-42 . 4 轴的结构设计2.4.1 第一轴设计 已知条件 第一轴功率 P1=55Kw 扭矩 T1=535.97N.m 转速 n1=980r/min(一)第轴的选型设计1.选择轴的材料第一轴为输入轴,很重要的一轴,故采用合金钢40Cr,表面调质处理,查表12.1 得 2.按转矩计算轴的最小直径应用式(12.2)估算,由表 12. .2 取 C =105mm于是 d C3P1 = 70mm ,计算所得应是最小轴径,该轴段因有键槽,应加大3%并圆n1整取 d1=70(1+0.03)=78.5mm=80mm(圆整)d2= d1+10=90mm d3 d2+10=100mmd4=110mm(安装尺寸由表 7-2-77 查的值)d5=90mm3.轴的结构设计(机械设计手册)查手册圆柱形轴伸(GB/T1569-1990),表 6-1-13 查的 L1=130mm(1)轴承的选择由 d=110mm 查轴承参数表得左侧采用单列圆锥滚子轴承(/297-1994)轴承代号为 32322 型,查的内圈宽度B1=80mm外径D1=240mm公称宽度T=84.5mm a=57.8mm内径mm L2=L 轴承盖+20=20+20=40mm查表 得右侧采用调心滚子轴承(GB/T288-1944)轴承代号为圆柱孔 22322TN1/W33 型B2=80mmD2=240mm L3=B1/2+B2/2+6=86mm两轴承间的轴套 L 轴套=300-B1/2-B2/2=220mmL4=30mmL5=cos23.57R 锥距-cos23.57(R-b 齿宽)=72mm(2)是否采用齿轮轴Q齿轮直径 d3=160mm 公称直径 db1 max=161mm 圆锥齿轮小端齿根圆至键槽底面的径向距离 e 得 e=(R 锥距b 齿宽)sin20 o =61.7mmd3 所以必须采用齿轮轴2.4.2第二轴设计已知条件:第轴传递功率 P2 = 54.45KW转速 n2=280r/min 扭矩 T2 = 1857.13N.m 模数 m2=8mm直齿轮压力角a =20 o齿数 Z2=84 Z3=20(一)第轴的选型设计1.选择轴的材料减速器功率很大,无特殊要求,故选最常用的 45 号钢,并做正火处理,由表 12.1 查 得2.按转矩计算轴的最小直径应用式 12 .2 估算,由表 12.2 取 C = 110 计算所得应是最小轴径d1 = 91.66 = 园整 = 100mm 取手册值d2 = d1 +(15)mm = 105mm d3 d2 = 105+15 = 120mmd4 = d2 = 105mm d5 = d1 = 100mm(二)键校核:大齿轮(锥齿轮)d2 = 504mmL2 = (11.2)d2 = 504mm所需传递转矩 T2 = 1857.13N.m 载荷有轻微冲击,试选切向键联接的尺寸并校核其强 度。d2 = 504mm 查表选取 A 型普通平键,宽度 b=36mm,厚度 h=20mm 宽度 L=120mm经计算得强度足够(3) 选用双列圆锥滚子轴承(GB/T299-1995)查表由 d5=100mm 选出 32220型 轴承外径 D=180mm 轴承内径d=100mmL5=171mmL3=119.5mm =L内侧 l2-l3-l4-15=109.5mm1L1= L +B=265.5mm2.4.3 第三轴设计已知条件:第轴传递功率 P3 =52.28kw,转速 n3 = 70r/min,扭矩 T3 = 7132.48N.m 模数 m3 = 10mm直齿轮压力角a =20 o 齿数Z4=80, Z5 = 20(一)第三轴的选型设计1.选择轴的材料减速器功率很大,无特殊要求,故选最常用的 45 号钢,并作调质处理。由表 12.1 查得2.按转矩计算轴的最小直径 应用式 12.2估算,由表 12 .2 取 C = 118 (因轴上受较大弯矩)最小直径为107.4mmd1=107.4=园整=120mm 取手册值 d2=d1+(15)mm=125mm d3d2=125+15=140mm d4=d2=125mmd5=d1=120mm 选用单列圆柱滚子轴承 NJ(GB/T 283-1994) 查 轴 承 参 数 表 可得: 选 NJ324 E型号轴承外径 D = 260mm 轴承内径d =120mm ,内壁宽B=108mm,则L1 = B + 20 =128mmL2 =247mmL3 = 1.4a =26mm(a = 0.07d2 + 3 = 18.75) L4 =157mmL5 = L1=128mmL = L1+ L2+ L3+ L4+ L5=128+247+26+157+128=686mm(二)键的选择与校核(1)大齿轮已知:d=640mm所需传递扭矩 T3=7132.48N.m, 载荷有轻微冲击,试选择平键联接的尺寸并校核其强度。d=640mm 选择圆头普通平键(A 型)b=50mm h=28mm L=237mm (比轮毂长度小 10 mm) L1=L b =23750=187mm挤压应力 P =2TD h L2= 2 7132.482250 14 187=168.52MPa 由表 13-6 查许用挤压应力 s P=100120MPa 强度不够 令 L2=323mm 则 L=32310 =313mm 则 L 1 =Lb=31350=263mm 代入挤压公式 挤压应力 P=2T2 7132. 4 8= 119.82120MPa 强度足够2.4.4 第四轴设计hDL1 2225 28 2632已知条件:第轴传递功率 P4 =50.2kw 转速 N4 = 15.63r/min扭矩 T4= 27599.88N.m直齿轮压力角=20 o , Z6=81 (一)第轴的选型设计1.选择轴的材料减速器功率很大,无特殊要求,故选最常用的45号钢, 并作调质处理。由表查得2.按转矩计算轴的最小直径 z应用式(13-2)估算,由表 13-3 取 A=110,(因轴上受较大弯矩)于是 d A 3 P4n4= 250mm计算所得应是最小轴径(即安装带轮处直径)该轴段因有键槽,加大 3%7%园整d1 = d(1+0.03) = 260mm d2= d1+(15) = 265mmd3 = d2+15 = 280mm d4 = d3+ 5 = 285mm d5 = d4+15 = 300mm d6 = d4 = 285mmd7 = d3 = 270mm(二) 键校核:(大齿轮) d6 = 810mm所需传递扭矩 T4 = 27599.88N.m 载荷有轻微冲击,选切向键联接的尺寸并校核其强 度。 d6 = 810mm查手册中选取 A 型普通平键 b = 63mm 厚度 h =32mm长度 L=200mm 根据轴 3 计算键的方法,检验得强度够(3) 选用调心滚子轴承(GB/T288-1994)查 轴 承 表 由查得选24156CC/W33 轴承外径 D = 460mm内径d=280mm 轴承内壁宽 B = 180mm则 L7 = 221.5mmL5 = 1.4a = 33mm (a = 0.007d6+3 =22.95mm) L3 = B = 180mmL4 = 191.5mm查表 6-1-13 圆柱形轴伸 L1 = 330mmL2 = b 轴承盖+10 = 30mm壁厚 = b 轴承盖+B = 200mm 2.5 轴的校核2.5.1第一轴(输入轴)(一)轴的结构设计 轴的具体结构见图(c1)(二)抗弯矩合成进行轴的强度校核1.轴的力学模型图 (c2)2.齿轮上的受力 齿轮分度圆直径 d1 = 144mm 齿轮所受的转距 T1 = 535970N.mm 齿轮上的作用力圆周力 Ft1 = 2T1/dm1 = 2535970/16.75 =63979Ndm1 = d1 = d1(10.5b/R) = 16.75mm 径向力 轴向力 3.计算轴的支承反力 图 (c-3 . c-5 ) 支点跨距 垂直面上的支反力 水平面上的支反力 =26373N =-4988N 4.画弯矩图 垂直面弯矩图 (c-4) 垂直平面内刨面C处弯矩 = 水平面弯矩图 (c-6) 水平面内刨面C处弯矩 = 5.合成弯矩图 (c-7)22剖面 C 处合成弯矩22MCA=M CV+ M CHA= (- 9.7 106 )2+ (- 3.0 106 )2=10106N.mmMCB=M CV+ M CHB= (- 9.7 106 )2+ (2.1 106 )2=9.9106N.mm 6.绘制弯矩图(c-8)由前知 T1=5220667N.mm又根据s B =700N/mm故得a =65/110 0.59,查表得 12. 3 ,得 s -1 b=65 N/mm和 s 0 b=110 N/mm ,aT =0.595220667=3080193.5N/mm 7. 绘制当量弯矩图对于截面 D: = aT =3080193.5 N.mm 8.绘制轴的工作图,如图2-7 图 2-7 9 滚动轴承的校核计算 已知:轴承直径 d=110mm 转速 n=980r/min (1)确定轴承类型及其额定载荷 设计中 A 处采用单列圆锥滚子轴承,查得额定动载荷 =725kN B 处采用调心滚子轴承,查得额定动载荷=795kN2 (2)确定轴承承受的径向载荷和轴向载荷 径向 FRA=RAH+ RAV22= (-4988)22 + (-22708)222= 23249N FRB =RBH+ RBV= 26373+ 86687=90610 N 轴向 FRC = Fa = 8553N轴承的内部轴向力按表 14-5 查,又查文献得 Y=1.7 查 查表 7-2-77 得 Y0 = 2根据外部轴向负载 FA 和两轴承的内部轴向力 FSA、FSB 的方向大小, FSB+FA 与 FSA 比较 (因 FSB=0)则 FSAFa1所以轴承 A 被压紧B 轴承所受轴向力 FAA = Fa1 = 8553N FBA = FSB = 22653N(3)计算轴承当量动载荷由表 7-2-79 查得= 0.35 = 0.34)FAA =FRA855323249= 0.37 eFBA = 22653 = 0.25 0.34FRB90610故可略去 FBA查表 14-6 得轴承 A 系数 XA = 0.4 YA = 1.7当量动载荷PA = XAFRA+= 0.423249+1.78553= 90610N(4)计算轴承寿命(滚子轴承 = 3 )LhA=e16670 CrA =1667010 725000 3=974440 小时12000 小时n e1500 23840 10LhB=16670 CrA =16670 795000 3=15470 小时12000 小时n 1500 90610 所以可以,选用轴承合适。2 . 5 . 2 第二轴(传动轴)(一)轴的结构设计 轴的具体结构见图 (d-1)(二)抗弯扭合成进行轴的强度校核1.画出轴的力学模型图 (d-2)2.计算齿轮上的作用力 齿轮分度圆直径 d2 = 504mmd3 = 160mm齿轮所受的转矩 T2 = 1857.13N.m=1857130N.m齿轮上的作用力圆周力 Ft2 =Ft1 = 63979N Ft3 = 2T2/d3 = 161514N径向力 Fr2 =Fa1 = 8553NFr3 = Ft3 tan a = 58786N轴向力 Fa2 = Fr1 = 21385N3.计算轴的支承反力图 (d-3d-5)L = L1+L2+L3 = 702mm垂直面上的支反力 水平面上支反力 4.画弯矩图 垂直面(d-4) 垂直平面内剖面 C 处弯矩MCV = RAVL1 =(130)255= 33150N.mm垂直平面内剖面 D 处弯矩MDV = RBVL3 =97665176.5=17.2106N.mm水平面弯矩图 (d-6) 水平面内剖面 C 处弯矩 MCHB = RBH(L2+L3)+ Fa2(d2/2) = 48210 (270.5 +176.5) + (-21385) 240 = 16.4106N.mm 水平面内剖面 D 处弯距 MDH =RBHL3=48210176.5=8.5106Nmm5.合成弯矩图(d-7)剖面 C 处合成弯矩CM =22M+ MCVCHA=331502 +(5.6 106)2= 5.6 106 N mmMM=2CCV2+ MCHB=331502 +(16.4 106)2= 16.4 106 N mm剖面 D 处合成弯距 M D = = 19.2 106 N mm6. 绘制转距图(a-8) 由前知 T2=1857130Nmm又根据 B=600Nmm 查表 12.3 s -1 b= 55 Nmm2 和s0 b= 95 Nmm2 ,故得a = 55 0.5895aT = 7.5106 N mm7.绘制当量弯矩图 对于截面 C:8.计算轴截面C处的直径M cccee3dc =0.1s -1b9.4 106= 3 0.1 55= 119.56mm 120mmM ce3dc =0.1s -1b18 106= 3 0.1 55= 148.5mm 149mm截面虽有键槽削弱,使结构设计所确定的直径已达到 135mm。所以强度足够。9.绘制轴的工作图如图 2-8图 2-810.滚动轴承的校核计算 已知:轴承直径 d=130mm,转速 n2=300r/min(1)确定轴承类型及其额定载荷设计中已确定采用双列圆锥滚子轴承,由表 7-2-80 查得额定动载荷 Cr=968KN(2)确定轴承受的径向载荷和轴向载荷径向载荷FRA=2RAH+ RAV2 =20232 + (-130)2= 2027N22FRB=RBH+ RBV=482102 + 976652= 108916N合成力FR=F 2 + F 2RARB=20272 +1089162= 108935N 轴向载荷 FRC=Fa=21385N(3)计算轴承当量动负荷(由表 7-2-80 查得:e=0.83)Fa = -21385 = -0.20 12000 所以选用轴承合适 2. 5 .4 第四轴(输出轴) (一)轴的结构设计(见装配图底稿) 轴的具体结构见图(b-1) (二)抗弯、扭矩合成进行轴的强度校核 1.轴的力学模型图(b-2) 2.齿轮上的受力 齿轮分度圆直径 d6=810mm齿轮所受的扭矩 T4=2759988N.mm齿轮上的作用力圆周力 Ft6 = 2T4/ d6 = 397186.22N径向力 Fr6 = Ft6。tan a = 144563.96N3.计算轴的支撑反力 (图 b-3 , b-5) 垂直面上的支反力RAV =Ft 6l2=248651.70N F lRBV = t 6 1 =148534.52N水平面上的支反力RAH =Fr 6l2= 90501.82N RBH =Fr 6l1= 54062.142N 4.画弯矩图垂直面弯矩图(b-4) 垂直平面内剖面 C 处弯矩7MCV =RAV.L1 = 248651.70271.5 =6.7510水平面弯矩图(b-6) 水平面内剖面 C 处弯矩N.mmMCH =RAH.L1 = 90501.82271.5 =2.4610 7 N.mm5. 合成弯矩图(b-7) 刨面C处合成弯矩 = 6.绘制转矩图 (b-8) 由前知 T4 = 2759988N.mm,又根据 =700N/ 查表12.3 得 s - 1 b=65和 故得a =65/110 0.59 aT =8.8610 7 N/mm 7.绘制当量弯矩图 对于截面 C:=CM 2 + (aT ) 2=1.4N.mm对于截面 D: = aT =8.86 N.mm 8.计算轴截面 b 处直径dC= 3= 259.8 260mm0.1s 强度足够 9.工作图 - 1b (2-6) 10.滚动轴承的校核计算已知:轴承直径 d=280mm 转速 n4=15.63r/min(1)确定轴承类型及其额定载荷设计中已确定采用圆柱滚子轴承,由表 7-2-66 查得额定动载荷 Cr=2730KN=273010 3 N22(2)确定轴承承受的径向载荷22径向载荷 FRA=RAH+ RAV= 2.6510 5 NFRB=RBH+ RBV= 1.5810 5 N(3)当量动载荷 P=FRA=2.6510 5 N(4)计算轴承寿命(滚子轴承 =10 )310e Lh=16670 Cr =16670 2730000 3n p 47.6190 2.65 105 =82569 小时12000 小时 所以可以,选用轴承合适。 3箱体3.1 箱体的结构设计1、为了便于齿轮等零件的装配,箱体采用水平部分面与轴线平面重合将箱体分成底 座和箱体两部分,箱体采用铸造结构,材料选用 H7200 这是由于灰口铸铁铸造性好,易于 切削加工,泵压强等高,减振性好。2、箱体各部分民尺寸的设计计算 表 5-1(1)下箱座壁厚d= 30 mm(2)上箱座壁厚d 1 = 25 mm(3)下箱座下凸像厚度P = 2.5d= 75mm(4)地脚螺钉直径 = 30mm(5)轴承旁联接螺栓直径d1 = 24mm(6)轴承盖螺钉直径 轴的 d2 = 14mm 轴的 d3 = 16mm(7)到凸缘边距离C1 = 40mm C2 =40mm d1 到凸缘边距离C1 = 34mmC2 =28mm d2 到凸缘边距离C1 = 20mmC2 =18mm d3 到凸缘边距离C1 = 22mmC2 =20mm(8)放油孔油塞直径D = 45mmM = 32mm(9)视孔盖 L = 500mmB = 300mmR = 20mm孔数 N = 10 (10) 通气器M36(11) 油尺M163、轴承盖的设计(1) 根据选用的轴承型号确定轴承盖止口的尺寸。(2) 根据齿轮箱的结构确定轴承盖与轴的密封形式。(3) 选用迷宫油封形式,可以有效预防齿轮轴转动过程中的漏油现象。 (4) 迷宫圈的设计为了有效预防齿轮箱内齿轮油的外漏,采用迷宫圈与挡圈的 结构,配合轴承盖上的沟槽,利用旋转所产生的气流的由外向内的压力, 起到了气隙密封的作用。4 设备的使用和维护4.1 钢丝绳的使用维护 提升钢丝绳是提升设备中的重要组成部分,除了合理地选择钢丝绳的结构以外,还应 正确地使用维护,以便延长钢丝绳的使用寿命,这不仅有一定的经济意义,而且对提升设 备的安全也有很重要的作用。 在钢丝绳的使用中,一定要满足煤矿安全规程中的规定,绳槽直径必须合理,绳槽过小时会引起钢丝绳过度挤压而提前断丝,绳槽过大时,会使钢丝绳在绳槽中支持面积减少,增大其接触应力,导致绳与绳槽的加速磨损。钢丝绳使用过程中应该注意润滑,良好地、定期地润滑对提高钢丝绳使用寿命影响很大。润滑的主要作用有三:(1)保护外部钢丝绳不受锈蚀;(2)起润滑作用,减少股间和丝间的磨损;(3)阻止湿气和水份浸入绳内,并经常补充绳芯油量。 对润滑油的要求:(1)粘稠性能好,振动、淋水甩冲不掉;(2)有较好的粘温特性,低温不硬化,高温不流失; (3)防锈和润滑性好,不含碱性,并有一定的透明度,以便发现磨损和断丝。为确 保钢丝绳的使用安全,防止断绳事故的发生,对钢丝绳要进行定期地检查和试验。4.2 轴承的润滑与密封 滚动轴承运转时,应通过润滑避免元件表面金属直接接触。润滑除降低摩擦和减轻 磨外,也有吸振、冷却、防锈和密封等作用,合理润滑对提高轴承性能、延长轴承寿命 有重要意义。 (1)脂润滑滚动轴承速度较低 (dn 2 105 mmr/min , d为轴承内径,n为转速)时, 常采用脂润滑。脂润滑结构简单,易于密封。一般每隔半年左右补充或更换一次润滑 脂。 润滑脂的装填量不应超过轴承空间的13 12 ,可通过轴承座上的注油孔和通道注 入。为防止箱内的油浸入轴承与润滑脂混合,并防止润滑脂流失,应在箱体内侧装挡油 环,产品生产批量较大时,可采用冲压档油环。 (2)油润滑 油润滑多用箱体内的油直接润滑轴承。油润滑有利于轴承的冷却散热,但对密封要求高,并且油的性能由传动件确定,长期使用的油中含有杂质,这对轴承润滑 有不利影响。油润滑方式可分为以下三种: 飞溅润滑 当箱内传动件圆周速度较大时 (v 2 3 m/s),常用传动件转动时飞溅带起的油润滑轴承。为此,应在箱体剖分面上开输油沟,使溅起的油沿箱体内壁流到沟内, 并应在端盖上开缺口。为防止装配时缺口没有对准油沟而将油路堵塞,可将端盖孔配合部 分的外径取小些。 在传动件圆周速度 v 5 m/s 时,油飞溅激烈,也可不开输油沟,但应将轴承尽量靠近 箱体内壁布置。 浸油润滑 这种润滑方式是轴承直接进入箱体内的油中润滑(如下置式蜗杆减速器的蜗杆轴承),但油面高度不应超过轴承最低滚动体中心,以免加大搅油损失。若传动件直径小于轴承滚动体中心分布直径时,可在轴上装设溅油轮,使其浸入油中,传动件不接触油面而靠溅油润滑。 对于高速运转的蜗杆和斜齿轮,由于齿的螺旋线作用,会迫使润滑油冲向轴承,带入杂质,影响润滑效果,故在轴承前常设挡油环。但挡油环不应封死轴承孔,以利于油进入润滑轴承。 刮油润滑 当较大传动件(蜗轮及大齿轮)的圆周速度很低时( v 2 m/s),可在传动件侧面(约离传动件 0.1 0.5 mm)安装刮油板,此时要求传动件端面跳动轴向窜动较小。为使轴承内保持一定油量,可在轴承室端部装设挡油板,但应使油面高度不超过轴承最低滚动体中心。 (3)密封 轴伸端密封方式有接触式和非接触式两种。橡胶油封是接触式密封中性能较好的一种,可用于油或脂润滑的轴承中。骨架式油封因有金属骨架,与孔径配合装配即可。无骨架式油封则可装于紧固套中,并进行轴向固定。 应注意油封的安装方向。以防漏油为主时,油封唇边对着箱内;以防外界灰尘、杂质为主时,唇边对着箱外;当两油封相背放置时,则防漏防尘能力都好。为安装油封方便,轴上可做出斜角。对于紧配合的骨架油封,可在密封盖上钻小孔,以便于卸。另外,还可在与油封接触的轴段上做出 0.02mm 深的螺旋槽或刻出倾斜的滚花。在单向运转时,则可使泄露到轴段上的油被推回到箱内,提高了密封效果,但密封件的磨损较严重。 其改进措施是在密封件内孔表面做出浅的螺纹槽,而把轴的表面做成十分光洁,其 表面粗糙度 Ra值不超过 0.4um。 毡圈密封在接触式密封中寿命较低,密封性能相对较差,但简单、经济,适用于脂 润滑轴承中。为避免磨损,可采用非接触式密封。油沟密封是其中常用的一种。使用油沟密封时,应该用脂填满间隙,以加强密封性能。开设回油槽效果更好。油沟密封结构简单,但不够 可靠,适用于脂润滑及工作环境清洁的轴承中。若要求更高的密封性能,可采用迷宫密封,适用于环境恶劣的油润滑轴承。若与接触式密封配合使用,则效果更佳。其缺点是结构复杂,对加工及装配要求高。选择密封方式,要考虑密封处的轴表面圆周速度、润滑剂的种类、密封要求、工作温度、环境条件等因素。4.3 减速器润滑 减速器传动零件和轴承都需要良好的润滑,其目的是为了减少摩擦,磨损,提高效率,防锈,冷却和散热。箱体内应有足够的润滑油,以保证润滑及散热的需要,为了保证传动零件充分润滑且避免搅油损失过大,传动零件应有合适的浸油深度。 常用的润滑方式有以下七种: (1)手工注油:用油壶、油枪和脂枪注油。 (2)飞溅注油:依靠旋转的机件或附加于轴上的甩油盘、甩油片等,将油池中的油甩起,使油溅落到润滑部位上。 (3)油环和油链润滑:利用套在轴上的油环和油链将油带起,供润滑部位润滑。 (4)油绳、油垫润滑:利用虹吸管原理和毛细管作用实现润滑,主要用于低速、轻载的机械润滑。 (5)强制给油润滑:利用油泵将润滑油间歇地压向润滑点进行润滑。 (6)油雾润滑:利用压缩空气将润滑油喷出并雾化后,送入润滑点。润滑油在饱和状态下析出,在摩擦面上黏附一层油膜,起到润滑作用。 (7)压力循环润滑:利用油泵使润滑油获得一定压力,然后输送到各润滑点。用过的润滑油回到油箱,经冷却、过滤后再供循环使用。无论采用哪种润滑方式,都要保证润滑系统的正常工作。润滑系统完好标准的内容是:润滑系统油质合格、油量适当、油压正常、油路畅通、油圈转动灵活、润滑系统不漏油。 参考文献【1】吴宗泽机械零件设计手册。机械工业出版社.2003.【2】陈立德机械设计基础课程设计高等教育出版社.2006【3】孙本绪.熊万武机械加工余量手册国防工业出版社.1999.【4】 曾志新.吕明机械制造技术基础.武汉理工大学出版社.2001.【5】 姚云英.公差配合与测量技术.机械工业出版社.2004.【6】 李海萍.机械设计基础北京工业出版社.1999.【7】 陈宏钧实用机械加工工艺手册(第2版)机械工业出版社.2004.【8】 李益明.工艺设计简明手册哈尔滨工业大学出版社.1993.【9】 安琦.顾大强机械设计北京科学技术出版社.2004.【10】王世刚.张秀亲机械设计实践(修订版)哈尔滨工业大学出版社.2003.【11】王文斌.机械设计手册机械工业出版社.2004.【12】陈心昭.机械加工工艺装备设计手册.机械工业出版社,1998.【13】杨叔子机械加工工艺师手册机械工业出版社.1997.【14】李洪.机械加工技术手册.北京出版社.1989.【15】邓文英.金属工艺学.高等教育出版社.1991.外文翻译 Hardened gear reducerHardened gear reducer include all kinds of expansion - gear reducer,the coaxial gear reducer, planetary gear reducer of various types of special gear and various groups of the derivative products, gearcarburizing, quenching, grinding technology, precision grade 47,widely used in metallurgy, mining, lifting, petrochemical, building,building materials, light industry and energy industry. Its main features are:1) the main specification parameters (center distance, transmission ratio) the number priority priority number system, and meet the relevant standards.2) the main structure size parameters, the optimization design of gear transmission. Standardization, high level of generalization, about 1500parts, a speed reducer 4500 different capacity, different transmission ratio, different assembly type.3) gear made of high strength alloy steel forging quality. Hardened gearreducer after carburizing, quenching, grinding, precision. Allowablebearing capacity of bearing capacity of old products for more than 3 times. Hardened gear with a special modulation processing, precisiongear hobbing. Design life of 10 years.4) the performance of reducer through bench test and practicalappraisal to achieve the advanced level of similar products in the world80 years. Can replace imported products, can be exported.5) product quality inspection and grading, loading test, reliability test,use and maintenance of related technique and technical specifications.But generally limited in:Gearbox high-speed shaft is not higher than 1500r/min;Slow speed gear circle is not higher than 20m/s;Deceleration working environment temperature is 40 45 degrees Celsius -, below 0 degrees Celsius, before the start of the lubricating oil should be preheated.If the utility conditions beyond a limit, and the design or manufacturingunits, a negotiated solution.Selection method:Bearing capacity standard reducer by the mechanical strength and heatbalance two allowable power limit. Therefore the reducer must beaccording to the two power meter and related coefficient to choose.Firstly, according to the mechanical reducer strength permissiblenominal power selection. If the input speed and carrying capacity inthree (15001000750) speed of relative error less than 4%, it should bethe nominal power according to the practical speed reducer selectionat. Then check reducer heat balance allowable power (the thermal power) if the shaft extension in addition to withstand the torque, but alsobear the axial, radial load, should check the shaft extension factor of safety and service life of bearing. Should also check the peak loadwhen necessary.Particular attention should be paid to the choice is, in addition to considering load coefficient, but also by the importance of equipmentand the accuracy of load actual size master selection of adequate safety factor.The hardened gear reducer price situation is analyzed briefly.1 gear reducer product prices are fluctuating between 2.56 million / ton, as the single weight, precision, material type, matching pieces ofdifferent level etc. In general, higher requirements of platform weightlight using imported parts or materials and precision, the price upper limit, lower limit of general price should be stated, because it is notserious domestic market order is not standard and individualproduction enterprises in the production process, the market is flooded with a certain proportion of not in strict accordance with the productionprocess in hard surface for the production of products, its prominent characteristic is the short life, because the tooth surface withoutgrinding, noise is large, the products to the market low price shocks,some users due to the production process of reducer products is not familiar with, or due to other reasons, it only takes the price as the mainpurchase basis, often leads to the regular manufacturers products to enter the procurement perspective, to the user also causedunnecessary losses, but also to the illegal manufacturers an opportunity,seriously affecting a mature reducer products market development and growth.The 2 planetary gear reducer and includes many kinds of products,such as low speed heavy planetary gear box, all kinds of special rotaryplanetary gear and planetary transmission device, the general external gear carburized gear grinding, gear quenched and tempered or nitrideon GM products, prices generally in the 36 million / ton, for rotary typeplanetary single table light weight reducer, the table of valuation, the price slightly higher than the former, in general, the planetary gear reducer, the manufacturing and assembly process are more complex,so the price is hardened cylinder gear reducer to be higher. Such asfittings imported bearings, and purchasing high-quality gear steel, the price will be higher.3 price analysis, according to the number of domestic productionenterprises of the reducer, and the level of the status quo, the industry price competition in a certain scope and time will still be very fierce.Especially with the impending entry into the WTO, foreign products willenter the domestic market, some foreign manufacturers have startedtheir localization strategy, resulting in product competition, pricecompetition will more hasten is intense.But it is unavoidable, because of limitation of the means of production,management level, enterprise scale and the ability of independent development, at present domestic enterprises price competition is also general level of the product, with the further enhancement of the quality of the user awareness. The rise of industrycompetition further differentiation and domestic well-known brand,market competition includes price competition will tend to be rationaland normative agriculture step. Development situation and contrastthroughout the industry, there are two points should be attracted industry attention, (1) large-scale production advantage should not be ignored,Only up to a certain size is likely to form the economies of scale, to reduce costs and enhance competitiveness, therefore, qualified enterprises can be through the expansion of scale, capital operation and other means to promote enterprise production scale, and enhancemarket competition ability. (2) to strengthen the ability of product development, with special attention to changes of the market, timely adjustment of product development strategy, to update the oldgeneration products, constantly with new products in large-scale production to replace old products, occupy the city often present the domestic gear reducer industry has not yet appeared to have adapted to the scale and level with foreign counterparts competition of enterprises with high technology content of products, in product development and upgrading also teeter, product specifications, typesand level compared with foreign counterparts have a certain gap, thissituation is not changed as soon as possible, will have a serious impact on after Chinas entry into the WTO transmission foundation industry the survival and development, so we should pay attention to, hope industry colleagues together, work together, to change the situation as soon as possible, so that the reducer industry of our country in a fair, orderlycompetition and healthy development.Reduction gear transmission device with a fixed gear ratio to realize deceleration. Often installed as an independent component in the box body. Reducer due to its compact structure, high efficiency, accurate and reliable transmission of motion, good lubrication, long service life,simple maintenance and can be mass production, it is widely used in modern machines.There are many kinds of reducer, according to the type of transmission,a gear reducer, the worm reducer, gear worm reducer, planetary gear reducer; according to the drive series, there are 1 stage reducer, 2 stage reducer, 3 stage reducer and multi-stage reducer; according to the shaft position, vertical type and the horizontal reducer; according to the power transmission line, a expansion, coaxial and split reducer.Reducer box should have sufficient rigidity, so as to avoid excessive deformation after loading affect the transmission quality, usually made of gray cast iron, a small amount of production is available whenwelding structure, mass production of small reducer can be used for sheet metal and. Lubricating gear speed reducer drive the oil bath lubrication, for heavy or high-speed transmission should adopt oillubrication; lubrication of bearings generally use the splash lubrication(circumferential speed in the 2 3 meters / seconds) or scraping lubrication (peripheral speed at 2 3 M / s below). In addition, similarwith the speed reducer, also use the accelerator in a few cases, it is closed with a gear fixed transmission ratio of the transmission device in the box body.Domestic reducer industry key enterprises product varieties,specifications and parameters coverage in recent years are in constantexpansion, product quality has reached the international advanced level of similar products in the industrial countries, can undertake to provideany heavy transmission device for supporting national economic industries, some products are also exported to Europe and Southeast asia.At present, the standard series of various types of domestic general reducer has reached hundreds of, can basically meet the industrydemand for general reducer. Based on the first generation of generalhardened gear reducer and circular cylindrical worm reducer series of products, a new generation of cylindrical and conical study by XianHeavy Machinery fell developed and completed standardized -cylindrical gear reducer and circular cylindrical worm reducer hasinvestment market. Prominent features of the new generation of the speed reducer is not only in product performance parameters on furtheroptimization, and fully comply with the modular design principle in theseries design, product appearance more beautiful, more suitable formass production, more adapt to the development of modern industryand higher on the basis of the product and matching requirements. In addition, the Nanjing high precision gear Limited by Share Ltd alsopromoted the PR Series modular gear reducer series product. But overall, the domestic development and update the reducer series products in the past few years, progress is slow, with foreign counterparts in this aspect have widened the gap between the trend.But with the market demand is also very does not adapt, Xian Heavy Machinery Research Institute and other units have embarked on the development level of standardization work this year.In general reducer manufacturing device, domestic manufacturersnumber, such as various types of cylindrical gear machine taper -cylindrical gear or gear - worm reducer series products, the major domestic manufacturers have Nanjing high precision gear Limited by Share Ltd, Ning Bodong force transmission equipment Co., Ltd.,Jiangyin gear box manufacturing Co., Ltd., Jiangsu Taixing reducerCompany Limited, Jiangsu Jinxiang reducer Co. Ltd., Shanxi Pingyao reducer factory. Object worm reducer, the current domestic production of arc cylindrical worm reducer, cone enveloping cylindrical worm reducer, two plane enveloping toroidal worm reducer and other types,the major manufacturers have Jiangsu Jinxiang reducer Co., ShougangMachinery manufacturing company, Hangzhou vacuum machine factory,Hangzhou Wanjie speed reducer Co. Ltd., Tianjin million speed reducer factory, Shanghai Pujiang reducer Co. Ltd., the universal planetary gear reducer NGW series planetary gear, including the standard speed reducer, including various kinds of rotary planetary reducer and closed planetary gear. The Jingzhou Jujing movingmachinery Co. Ltd., Luoyang heavy gear box Co. Ltd., Xian Heavy Machinery Research Institute, Shijiazhuang, a heavy industry limited company, Inner Mongolia Xinghua Machinery factory.In the development of machine manufacturing various types of specialtransmission device, the domestic in recent years made significant progress, such as MDH28 type mill edge Chongqing gearbox limited liability company production drive transmission, its maximum power isup to 7000KW, torque reaches 5000KN.m, weight 46 tons, maximum modulus of main drive gear box have 1700 Hot Strip mill yield is 30, the weight of 180 tons. Gear box gear box Co. Ltd. the production of type gwc70/76 and 12000 tons container ship by Hangzhou advance,transmission power has reached 6250KW. By the Nanjing high precision gear Limited by Share Ltd and Chongqing gear box company limited production of the grinding gear box maximum power has reached 3800KW, heavy-duty planet gear box series products fromXian Heavy Machinery Research Institute, Luoyang heavy gear box Co. Ltd., Jingzhou Jujing Transmission Machinery Co., Ltd., the development of manufacturing in the mine, metallurgy, building materials, coal and water and electricity industries have also beenwidely used, the input power development of Xian Heavy Machinery Research Institute of the cement industry roller suspension series planetary gear box has reached 1250KW, used for aluminum made millplanetary gear box with wind power gear box Company Ltd., Hangzhouimport and on the box, Xian Heavy Machinery Development Co. Ltd.the series of products are gradually replace imported products, widely used in the domestic wind power industry. In the manufacture of largegear ring, currently the largest diameter of 9.936 meters, gear ring netweighing 80 tons has been manufactured by CITIC Heavy machinerycomplete, and for the Wuhan Iron and Steel Group 5000000 tons annual production capacity of oxidized ball production line, thus for largedriving device of large sintering machine, ball mill, rotary kiln as well as for the converter and sintering equipment large flexible transmission device can trap domestic supply, without the need to re import.In the development of new products and other types of enterprises, the industry has also made a lot of achievements, the large ring gear box of large mine differential energy saving control device, Luoyang heavygear box Co. Ltd. as Xian Heavy Machinery Research Institutedeveloped engineering vehicle gear box and the fan and pump hoist of planetary gear box, mill Jiangsu Jinxiang the driving gear box reducer,Beijing tieforce drive Co. Ltd. and the transmission device, arewelcomed by the market and be widely applied.In the capacity expansion and technological transformation ofenterprises, in recent years, showing a rapid development, on the one hand, due to the recent years the strong market demand, on the other hand is driven by the subjective desire of enterprises to expand production scale, enhance the level of manufacturing, processing andenhance the competitiveness of enterprises, the key processingequipment at home the main products manufacturers in recent two years, purchased, such as large grinding machine, milling machine,technical center and heat treatment equipment, a total of more thanmore than 200 Taiwan (sets), industry production capacity is expectedto expand by more than one time, technical work for solid and objective effect of industry scale and concentration of production andcompetitiveness, but because still industry enterprise quantity is many,small size and level of such practical problems as uneven, with the decline in market demand and foreign manufacturers have entered the domestic market, competition will be further intensified, which will promote the integration of merger, enterprises and transformation.In product sales market competition, foreign manufacturers in recent years in China expansion momentum is increasingly strong, SEW company continues on the national deployment of the production and sales base, expand market share. FLEDER company, state flying company, Bray Vinnie and FORK, Sumitomo and other companieshave also increased to establish a production base and sales center in the pace of China, actively to the infiltration of various industries, foreign manufacturers of advanced management, business philosophy, rich market competition and development experience and unique series of products will highlight the challenges and the impact on the domesticmanufacturers, domestic production enterprises feel will be increasinglyfierce trade competition.In the expansion of domestic transmission products, at present still withsmall power, small size, products exported or with the host exports as the main form, on the one hand, the president share is still relatively small, and strive to improve product quality and scalability, and actively explore the international market, should be an important the way for domestic enterprises market development.Looking at the status quo and reducer industry, in order to maintain industry health sustainable development fully affirmed in industry development, progress at the same time, should also see the problems,and actively study countermeasures, measures, and strive to within a short time progress. At present, the deceleration problems device industry there is ability to develop new products, the whole industry is weak, technological innovation and the low level of management,enterprise management mode is more extensive, a considerable proportion of the products is still low, the lack of international influence of the brand, the industry as a whole,is still very seriousdisorder scattered. Based on this, promote the integration of merger and acquisition, enterprise inter industry, as soon as possible the formation of a certain brand in the market influence, larger scale and strength, has a strong product development and technical supportcapabilities of such a group enterprise, so put can maintain a certain advantage in competition with foreign count constantlydevelopment.中文译文硬齿面齿轮类减速器:硬齿面齿轮类减速器包括了各类展开式圆模齿轮减速器、同轴齿轮减速器、行星齿轮减速器各类专用齿轮装置以及各类组各派生产品,齿轮采用渗碳、淬火、磨齿工艺、精度47级,广泛应用于冶金、起重、矿山、石化、建筑、建材、轻工及能源等行业。其主要特点有:1)主要规格参数(中心距、传动比等)采用优先数系的优先数,并符合有关标准。2)齿轮传动参数、主要结构尺寸经优化设计。标准化、通用化程度高,约1500种零件,组成4500多台不同承载能力、不同传动比、不同装配型式的减速器。3)齿轮材料采用锻造优质高强度合金钢。硬齿面齿轮类减速器经渗碳、淬火、磨齿,精度高。许用承载能力为旧产品承载能力的3倍以上。中硬齿面齿轮经特殊调制处理、精滚齿。设计寿命10年。4)减速器的性能经台架试验与实用考核达到80年代世界同类产品的先进水平。可以替代进口产品,可以出口。5)产品质量的检验和分等、加载试验、可靠性考核、使用维护等均有相应的配套技术和技术规范。但一般限制在:减速器高速转轴不高于1500r/min;减速器齿轮圆周速度不高于20m/s;减速器的工作环境温度为4045摄氏度,低于0摄氏度时,启动前润滑油应预热。如果实用条件超越以上限制时,可与设计或制造单位联系,协商解决办法。选用方法:标准减速器的承载能力受机械强度和热平衡两许用功率限制。因此减速器必须按两个功率表及有关系数来选用。首先按减速器机械强度许用公称功率选择。如果实用输入转速与承载能力表中的三档(1500,1000,750)转速之一相对误差不超过4,则应按实用转速折算减速器的公称功率选取。然后校核减速器热平衡许用功率(简称热功率)如果轴伸除承受转矩外,还承受轴向、径向载荷,应校核轴伸安全系数与轴承寿命。必要时还应校核尖峰载荷。应该特别注意的是,选用时除考虑工况系数外,还要按设备的重要性和对负载实际大小掌握的准确程度选择足够的安全系数。现对硬齿面齿轮减速器的价格现状进行简要的分析。 1齿轮减速器产品的价格目前波动在2.56万/吨之间,视单机重量、精度高低、材质种类、配套件水平等而有所不同。一般平台重量轻者、要求采用进口配套件或材质及精度要求较高者,价格偏上限,通用产品价格偏下限应当说明的是,由于国内目前市场秩序的不规范和个别生产企业生产工艺的不严肃性,市场上充斥着一定比例的未严格按硬齿面生产工艺要求进行生产的产品,其突出特征是寿命短,由于齿面未进行磨削,噪声也较大,该类产品以低价格冲击市场,部分用户由于对减速器产品的生产工艺情况并不熟悉,或由于其它原因,采购中一味地只以价格作为主要采购依据,常导致正规厂家产品难以进入采购视野,给用户也造成了不应有的损失,也给不法生产厂家以可乘之机,
- 温馨提示:
1: 本站所有资源如无特殊说明,都需要本地电脑安装OFFICE2007和PDF阅读器。图纸软件为CAD,CAXA,PROE,UG,SolidWorks等.压缩文件请下载最新的WinRAR软件解压。
2: 本站的文档不包含任何第三方提供的附件图纸等,如果需要附件,请联系上传者。文件的所有权益归上传用户所有。
3.本站RAR压缩包中若带图纸,网页内容里面会有图纸预览,若没有图纸预览就没有图纸。
4. 未经权益所有人同意不得将文件中的内容挪作商业或盈利用途。
5. 人人文库网仅提供信息存储空间,仅对用户上传内容的表现方式做保护处理,对用户上传分享的文档内容本身不做任何修改或编辑,并不能对任何下载内容负责。
6. 下载文件中如有侵权或不适当内容,请与我们联系,我们立即纠正。
7. 本站不保证下载资源的准确性、安全性和完整性, 同时也不承担用户因使用这些下载资源对自己和他人造成任何形式的伤害或损失。

人人文库网所有资源均是用户自行上传分享,仅供网友学习交流,未经上传用户书面授权,请勿作他用。