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编号 无锡太湖学院毕业设计（论文）相关资料题目： 电脑渐开线齿轮齿形误差 检测仪设计 信机 系 机械工程及自动化专业学 号： 0923017 学生姓名： 朱敬松 指导教师： 屠德刚 （职称：高工 ） （职称： ） 2012年5月25日目 录一、毕业设计（论文）开题报告二、毕业设计（论文）外文资料翻译及原文三、学生“毕业论文（论文）计划、进度、检查及落实表”四、实习鉴定表无锡太湖学院毕业设计（论文）开题报告题目： 电脑渐开线齿轮齿形 误差检测仪设计 机 电 系 机械设计及自动化 专业学 号： 0923017 学生姓名： 朱敬松 指导教师： 屠德刚 （职称：高工 ） （职称： ） 2012 年 11 月 课题来源科学依据（包括课题的科学意义；国内外研究概况、水平和发展趋势；应用前景等） 从上世纪80年代开始，齿轮测量中心的开发受到众多齿轮测量仪器制造商的重视；90年代逐步形成了系列化产品推向市场。CNC齿轮测量中心是信息技术、计算机技术和数控技术在齿轮测量仪器上集成应用的结晶，主要用于齿轮单项几何精度的检测，也可用于（静态）齿轮整体误差的测量。德国KLINGELNBERG的P系列齿轮测量中心，其特点是采用了专利的三维数字式高精度光栅测量头（使用了HEINDENHAIN的超高精度光栅）；性能稳定的优质铸铁床身，高性能直线电机驱动系统；高精度滚珠轴系和密珠滚动导轨。仪器精度达到德国标准1级。据报道该厂生产并经精化的一台P65齿轮测量中心，被英国国家齿轮计量实验室选定，作为英国齿轮精度传递及标定的基准仪器。美国M&M的齿轮测量中心，其三维高精度电感测量头；花岗石基座；精密气浮轴系以及精密直线滚动体结构导轨，成为该仪器的特色（近年也采用了直线电机驱动），仪器测量不确定度为2m。德国MAHR的GMX275采用的模拟量测量头，可选择扫描或单点采样方式，可以按0.1间距转动，使测头的测尖能处于被测齿面的法面上，仪器测量不确定度在测量空间内为（2.3m+L/200）。国外齿轮测量中心厂商，大多还开发了测量软件和加工机床的参数修正软件，选用相关软件，还能用于反求工程对工件参数进行测定。高精度和一机多能的特点，使齿轮测量中心更适合于工厂计量站使用。日本的齿轮测量仪器制造商，在我国市场经过近十年的沉寂后近年来亮相频繁。大阪精机在GC-HP系列齿轮测量仪器的基础上，开发出CNC电子创成式的CLP系列齿轮测量仪器。特别值得一提的是最近在国内参展亮相的东京技术仪器公司（Tokyo Technical Instruments Inc.）。在2003年底上海中国国际齿轮传动、制造技术及装备展览会上该厂首次展出TTI-300E型CNC齿轮检测仪，据称其质量较小的测头部件能单独在径向运动，便于快速测量齿轮齿距偏差。密珠轴系的主轴回转精度可达0.03m，仪器测量重复性达到0.5m。国内近年来，CNC齿轮测量中心有了长足的发展，哈尔滨量具刃具厂、哈尔滨精达公司都先后成功开发出了系列产品。哈量的3903A齿轮测量中心，经过几年努力，仪器精度和测量速度已达到或接近KLINGELNBERG公司产品的先进水平。精达公司作为后起之秀，发展引人瞩目，其JD、JDS系列齿轮测量中心。目前在国内产品中销量很多。国产齿轮测量中心的质量和性能不断提高，已经具有和国外产品竞争的能力。不过在仪器精度、稳定性，尤其在测量软件、仪器故障诊断功能等方面，和国外还有一定差距。令人欣慰的是国内齿轮量仪制造商已有共识，已联合高校院所协同攻关努力缩小差距；随着性价比的迅速提高，参与市场竞争能力的增强，国产齿轮测量中心的发展前景看好。当前齿轮制造业的一个发展趋势，是将齿轮测量技术和齿轮设计、加工制造进行集成，实现齿轮制造信息的融合及CAD/CAM/CAT的集成，从而构建一个先进的齿轮闭环制造系统（由于通常由数字化信息来实现，可称为数字化闭环制造系统）。随着齿轮制造业的快速发展，因此齿轮测量技术和齿轮测量仪器的发展方向更加明确。江苏泰州LG冷机有限公司研究内容电脑渐开线齿轮齿形误差检测仪的设计一结构设计部分： 1检测仪的结构方案设计 2检测仪的设计计算及说明二重要零件的有限元分析拟采取的研究方法、技术路线、实验方案及可行性分析 本次毕业设计首先是对检测仪市场使用情况的数据进行采集工作，以确定设计的方案。 其次，分析所具备的条件因素，考虑厂方的成组技术要求，进行方案的制定。 最后，开始零件设计和重要零件三维绘图设计。本仪器用于测量直齿或斜齿的圆柱齿轮的渐开线齿轮误差。这种仪器不需要不同尺寸的基圆盘。通过在仪器上的数控装置可以将被测工件的基圆半径调准到0.002MM.仪器表有电感比较仪,其传感器将被测工件齿形的渐开线误差传到指示电表上。本课题主要是着重与仪器机械结构方面的设计，并制作相关的三维软件，以满足设计改进，质量控制，售后服务，商务洽谈方面的要求。研究计划及预期成果特色或创新之处本仪器的重要零件用三维软件进行有限元分析，可靠度更高。本仪器适用不同基圆大小的齿轮齿形误差，我分别在老式手动检测仪的Y向和Z向作了改动,改造后,被测齿轮通过安装心杆来固定在两顶尖之间,用两个步进电机分别代替以前的纯手动部件,控制带测头的工作台和被测齿轮的相互匹配运动,他们分别是用Y向步进电机控制测头的工作台运动,用Z向步进电机来控制被测齿轮的旋转运动,用软件(也就是用单片机语言编程)来完成这些运动。已具备的条件和尚需解决的问题目前在国内产品中销量很多。国产齿轮测量中心的质量和性能不断提高，已经具有和国外产品竞争的能力。不过在仪器精度、稳定性，尤其在测量软件、仪器故障诊断功能等方面，和国外还有一定差距。指导教师意见 指导教师签名：年 月 日教研室（学科组、研究所）意见 教研室主任签名： 年 月 日系意见 主管领导签名： 年 月 日 GEAR AND SHAFT INTRODUCTIONAbstract: The important position of the wheel gear and shaft cant falter in traditional machine and modern machines.The wheel gear and shafts mainly install the direction that delivers the dint at the principal axis box.The passing to process to make them can is divided into many model numbers, using for many situations respectively.So we must be they to the understanding of the wheel gear and shaft in many ways .Key words: Wheel gear;ShaftIn the force analysis of spur gears, the forces are assumed to act in a single plane. We shall study gears in which the forces have three dimensions. The reason for this, in the case of helical gears, is that the teeth are not parallel to the axis of rotation. And in the case of bevel gears, the rotational axes are not parallel to each other. There are also other reasons, as we shall learn.Helical gears are used to transmit motion between parallel shafts. The helix angle is the same on each gear, but one gear must have a right-hand helix and the other a left-hand helix. The shape of the tooth is an involute helicoid. If a piece of paper cut in the shape of a parallelogram is wrapped around a cylinder, the angular edge of the paper becomes a helix. If we unwind this paper, each point on the angular edge generates an involute curve. The surface obtained when every point on the edge generates an involute is called an involute helicoid.The initial contact of spur-gear teeth is a line extending all the way across the face of the tooth. The initial contact of helical gear teeth is a point, which changes into a line as the teeth come into more engagement. In spur gears the line of contact is parallel to the axis of the rotation; in helical gears, the line is diagonal across the face of the tooth. It is this gradual of the teeth and the smooth transfer of load from one tooth to another, which give helical gears the ability to transmit heavy loads at high speeds. Helical gears subject the shaft bearings to both radial and thrust loads. When the thrust loads become high or are objectionable for other reasons, it may be desirable to use double helical gears. A double helical gear (herringbone) is equivalent to two helical gears of opposite hand, mounted side by side on the same shaft. They develop opposite thrust reactions and thus cancel out the thrust load. When two or more single helical gears are mounted on the same shaft, the hand of the gears should be selected so as to produce the minimum thrust load.Crossed-helical, or spiral, gears are those in which the shaft centerlines are neither parallel nor intersecting. The teeth of crossed-helical fears have point contact with each other, which changes to line contact as the gears wear in. For this reason they will carry out very small loads and are mainly for instrumental applications, and are definitely not recommended for use in the transmission of power. There is on difference between a crossed helical gear and a helical gear until they are mounted in mesh with each other. They are manufactured in the same way. A pair of meshed crossed helical gears usually have the same hand; that is ,a right-hand driver goes with a right-hand driven. In the design of crossed-helical gears, the minimum sliding velocity is obtained when the helix angle are equal. However, when the helix angle are not equal, the gear with the larger helix angle should be used as the driver if both gears have the same hand.Worm gears are similar to crossed helical gears. The pinion or worm has a small number of teeth, usually one to four, and since they completely wrap around the pitch cylinder they are called threads. Its mating gear is called a worm gear, which is not a true helical gear. A worm and worm gear are used to provide a high angular-velocity reduction between nonintersecting shafts which are usually at right angle. The worm gear is not a helical gear because its face is made concave to fit the curvature of the worm in order to provide line contact instead of point contact. However, a disadvantage of worm gearing is the high sliding velocities across the teeth, the same as with crossed helical gears.Worm gearing are either single or double enveloping. A single-enveloping gearing is one in which the gear wraps around or partially encloses the worm. A gearing in which each element partially encloses the other is, of course, a double-enveloping worm gearing. The important difference between the two is that area contact exists between the teeth of double-enveloping gears while only line contact between those of single-enveloping gears. The worm and worm gear of a set have the same hand of helix as for crossed helical gears, but the helix angles are usually quite different. The helix angle on the worm is generally quite large, and that on the gear very small. Because of this, it is usual to specify the lead angle on the worm, which is the complement of the worm helix angle, and the helix angle on the gear; the two angles are equal for a 90-deg. Shaft angle.When gears are to be used to transmit motion between intersecting shaft, some of bevel gear is required. Although bevel gear are usually made for a shaft angle of 90 deg. They may be produced for almost any shaft angle. The teeth may be cast, milled, or generated. Only the generated teeth may be classed as accurate. In a typical bevel gear mounting, one of the gear is often mounted outboard of the bearing. This means that shaft deflection can be more pronounced and have a greater effect on the contact of teeth. Another difficulty, which occurs in predicting the stress in bevel-gear teeth, is the fact the teeth are tapered. Straight bevel gears are easy to design and simple to manufacture and give very good results in service if they are mounted accurately and positively. As in the case of squr gears, however, they become noisy at higher values of the pitch-line velocity. In these cases it is often good design practice to go to the spiral bevel gear, which is the bevel counterpart of the helical gear. As in the case of helical gears, spiral bevel gears give a much smoother tooth action than straight bevel gears, and hence are useful where high speed are encountered.It is frequently desirable, as in the case of automotive differential applications, to have gearing similar to bevel gears but with the shaft offset. Such gears are called hypoid gears because their pitch surfaces are hyperboloids of revolution. The tooth action between such gears is a combination of rolling and sliding along a straight line and has much in common with that of worm gears.A shaft is a rotating or stationary member, usually of circular cross section, having mounted upon it such elements pulleys, flywheels, cranks, sprockets, and other power-transmission elements. Shaft may be subjected to bending, tension, compression, or torsional loads, acting singly or in combination with one another. When they are combined, one may expect to find both static and fatigue strength to be important design considerations, since a single shaft may be subjected to static stresses, completely reversed, and repeated stresses, all acting at the same time.The word “shaft” covers numerous variations, such as axles and spindles.： a shaft, wither stationary or rotating, nor subjected to torsion load. A shirt rotating shaft is often called a spindle.When either the lateral or the torsional deflection of a shaft must be held to close limits, the shaft must be sized on the basis of deflection before analyzing the stresses. The reason for this is that, if the shaft is made stiff enough so that the deflection is not too large, it is probable that the resulting stresses will be safe. But by no means should the designer assume that they are safe; it is almost always necessary to calculate them so that he knows they are within acceptable limits. Whenever possible, the power-transmission elements, such as gears or pullets, should be located close to the supporting bearings, This reduces the bending moment, and hence the deflection and bending stress.Although the von method is difficult to use in design of shaft, it probably comes closest to predicting actual failure. Thus it is a good way of checking a shaft that has already been designed or of discovering why a particular shaft has failed in service. Furthermore, there are a considerable number of shaft-design problems in which the dimension are pretty well limited by other considerations, such as rigidity, and it is only necessary for the designer to discover something about the fillet sizes, heat-treatment, and surface finish and whether or not shot peening is necessary in order to achieve the required life and reliability.Because of the similarity of their functions, clutches and brakes are treated together. In a simplified dynamic representation of a friction clutch, or brake, two inertias I1 and I2 traveling at the respective angular velocities W1 and W2, one of which may be zero in the case of brake, are to be brought to the same speed by engaging the clutch or brake. Slippage occurs because the two elements are running at different speeds and energy is dissipated during actuation, resulting in a temperature rise. In analyzing the performance of these devices we shall be interested in the actuating force, the torque transmitted, the energy loss and the temperature rise. The torque transmitted is related to the actuating force, the coefficient of friction, and the geometry of the clutch or brake. This is problem in static, which will have to be studied separately for eath geometric configuration. However, temperature rise is related to energy loss and can be studied without regard to the type of brake or clutch because the geometry of interest is the heat-dissipating surfaces. The various types of clutches and brakes may be classified as flows1. Rim type with internally expanding shoes2. Rim type with externally contracting shoes3. Band type4. Disk or axial type5. Cone type6. Miscellaneous typeThe analysis of all type of friction clutches and brakes use the same general procedure. The following step are necessary: 1. Assume or determine the distribution of pressure on the frictional surfaces.2. Find a relation between the maximum pressure and the pressure at any point3. Apply the condition of statical equilibrium to find (a) the actuating force, (b) the torque, and (c) the support reactions. Miscellaneous clutches include several types, such as the positive-contact clutches, overload-release clutches, overrunning clutches, magnetic fluid clutches, and others. A positive-contact clutch consists of a shift lever and two jaws. The greatest differences between the various types of positive clutches are concerned with the design of the jaws. To provide a longer period of time for shift action during engagement, the jaws may be ratchet-shaped, or gear-tooth-shaped. Sometimes a great many teeth or jaws are used, and they may be cut either circumferentially, so that they engage by cylindrical mating, or on the faces of the mating elements. Although positive clutches are not used to the extent of the frictional-contact type, they do have important applications where synchronous operation is required. Devices such as linear drives or motor-operated screw drivers must run to definite limit and then come to a stop. An overload-release type of clutch is required for these applications. These clutches are usually spring-loaded so as to release at a predetermined toque. The clicking sound which is heard when the overload point is reached is considered to be a desirable signal. An overrunning clutch or coupling permits the driven member of a machine to “freewheel” or “overrun” because the driver is stopped or because another source of power increase the speed of the driven. This type of clutch usually uses rollers or balls mounted between an outer sleeve and an inner member having flats machined around the periphery. Driving action is obtained by wedging the rollers between the sleeve and the flats. The clutch is therefore equivalent to a pawl and ratchet with an infinite number of teeth. Magnetic fluid clutch or brake is a relatively new development which has two parallel magnetic plates. Between these plates is a lubricated magnetic powder mixture. An electromagnetic coil is inserted somewhere in the magnetic circuit. By varying the excitation to this coil, the shearing strength of the magnetic fluid mixture may be accurately controlled. Thus any condition from a full slip to a frozen lockup may be obtained. 齿轮和轴的介绍摘要:在传统机械和现代机械中齿轮和轴的重要地位是不可动摇的。齿轮和轴主要安装在主轴箱来传递力的方向。通过加工制造它们可以分为许多的型号，分别用于许多的场合。所以我们对齿轮和轴的了解和认识必须是多层次多方位的。关键词:齿轮；轴在直齿圆柱齿轮的受力分析中，是假定各力作用在单一平面的。我们将研究作用力具有三维坐标的齿轮。因此，在斜齿轮的情况下，其齿向是不平行于回转轴线的。而在锥齿轮的情况中各回转轴线互相不平行。像我们要讨论的那样，尚有其他道理需要学习，掌握。斜齿轮用于传递平行轴之间的运动。倾斜角度每个齿轮都一样，但一个必须右旋斜齿，而另一个必须是左旋斜齿。齿的形状是一溅开线螺旋面。如果一张被剪成平行四边形（矩形）的纸张包围在齿轮圆柱体上，纸上印出齿的角刃边就变成斜线。如果我展开这张纸，在血角刃边上的每一个点就发生一渐开线曲线。直齿圆柱齿轮轮齿的初始接触处是跨过整个齿面而伸展开来的线。斜齿轮轮齿的初始接触是一点，当齿进入更多的啮合时，它就变成线。在直齿圆柱齿轮中，接触是平行于回转轴线的。在斜齿轮中，该先是跨过齿面的对角线。它是齿轮逐渐进行啮合并平稳的从一个齿到另一个齿传递运动，那样就使斜齿轮具有高速重载下平稳传递运动的能力。斜齿轮使轴的轴承承受径向和轴向力。当轴向推力变的大了或由于别的原因而产生某些影响时，那就可以使用人字齿轮。双斜齿轮（人字齿轮）是与反向的并排地装在同一轴上的两个斜齿轮等效。他们产生相反的轴向推力作用，这样就消除了轴向推力。当两个或更多个单向齿斜齿轮被在同一轴上时，齿轮的齿向应作选择，以便产生最小的轴向推力。交错轴斜齿轮或螺旋齿轮，他们是轴中心线既不相交也不平行。交错轴斜齿轮的齿彼此之间发生点接触，它随着齿轮的磨合而变成线接触。因此他们只能传递小的载荷和主要用于仪器设备中，而且肯定不能推荐在动力传动中使用。交错轴斜齿轮与斜齿轮之间在被安装后互相捏合之前是没有任何区别的。它们是以同样的方法进行制造。一对相啮合的交错轴斜齿轮通常具有同样的齿向，即左旋主动齿轮跟右旋从动齿轮相啮合。在交错轴斜齿设计中，当该齿的斜角相等时所产生滑移速度最小。然而当该齿的斜角不相等时，如果两个齿轮具有相同齿向的话，大斜角齿轮应用作主动齿轮。蜗轮与交错轴斜齿轮相似。小齿轮即蜗杆具有较小的齿数，通常是一到四齿，由于它们完全缠绕在节圆