X6130型铣床总体布局及主轴箱设计
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毕业设计(论文)任务书学生姓名系部机电工程学院专业、班级指导教师姓名职称教授从事专业机械工程是否外聘是否题目名称X6130型铣床总体布局及主轴箱设计一、 设计(论文)目的、意义 铣床(milling machine)系指主要用铣刀在工件上加工各种表面的机床。通常铣刀旋转运动为主运动,工件(和)铣刀的移动为进给运动。它可以加工平面、垂直面、斜面、各种沟槽或成型面,如果配一些附件(如分度头)也可以加工螺旋槽,凸轮、成型面等。 卧式万能升降台 有纵、横、垂三个进给方向,机床操纵方便,灵活可靠,机床精度保持性好,符合国际标准。铣床除能铣削平面、沟槽、轮齿、螺纹和花键轴外,还能加工比较复杂的型面,效率较刨床高,在机械制造和修理部门得到广泛应用,适用于各类机械加工部门。通过铣床运动机械变速传动系统的结构设计,使学生在拟定传动和变速的结构的结构方案过程中,得到设计构思,方案分析,结构工艺性,机械制图,零件计算,编写技术文件和查阅技术资料等方面的综合训练,树立正确的设计思想,掌握基本的设计方法,并培养学生具有初步的结构分析,结构设计和计算能力二、设计(论文)内容、技术要求(一)设计内容1、X6130主轴变速及传动机构设计;2、X6130外观总体布局设计;3、主轴、齿轮及零件部件设计和验算。(二)技术要求X6130主要规格及技术参数:工作台台面面积(宽长):300mm1150mm 主轴转速35-1600r/min 工作台最大行程(机动): 纵向 680mm 横向 235mm 垂向 400mm三、设计(论文)完成后应提交的成果(一)计算说明部分 设计说明书2份。(二)图纸部分1.A0图纸2张;2.A1图纸1张;3A3图纸5张 四、设计(论文)进度安排3月01日3月07日 查阅资料;3月08日3月14日 消化资料;3月15日3月21日 撰写开题报告;3月22日4月11日 方案设计、写说明书草稿;4月12日4月25日 画草图、写说明书草稿;4月26日5月23日 画CAD图、整理说明书;5月24日5月30日 打印说明书5月31日6月20日 准备答辩。五、主要参考资料1徐澋.机械设计手册M.北京:机械工业出版社,2002.032王世刚,张秀亲,苗淑杰.机械设计实践M.哈尔滨:哈尔滨工程大学出版社,2003.083周湛学.铣工M.北京:化学工业出版社,2005.09 4李沪曾,GSpur徐柄楠升降台铣床动态实验分析D.同济大学学报,2006.055周宗明.金属切削机床M.北京:机械工业出版社,2004.09 6王三民,诸文俊.机械原理与设计M.北京:机械工业出版社,2001.047侯珍秀.机械系统设计M.哈尔滨:哈尔滨工业大学出版社,2004.118陈易新.金属切削机床课程设计指导书M.北京:机械工业出版社,2004.079刘品,徐晓希.机械精度设计与检测基础M.哈尔滨:哈尔滨工业大学出版社,2004.0410Creamer R H. Machine DesignM. Addison-Wesley Pub.Co.,1996.06六、备注指导教师签字:年 月 日教研室主任签字: 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, useding for many situations respectively.So we must be the multilayers 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 elementsas gears, 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. Anaxle is 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 Mises-Hencky-Goodman 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.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;机床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柱上,因此它们被称为螺纹齿。与其相配的齿轮叫做蜗轮,蜗轮不是真正的斜齿轮。蜗杆和蜗轮通常是用于向垂直相交轴之间的传动提供大的角速度减速比。蜗轮不是斜齿轮,因为其齿顶面做成中凹形状以适配蜗杆曲率,目的是要形成线接触而不是点接触。然而蜗杆蜗轮传动机构中存在齿间有较大滑移速度的缺点,正像交错轴斜齿轮那样。蜗杆蜗轮机构有单包围和双包围机构。单包围机构就是蜗轮包裹着蜗杆的一种机构。当然,如果每个构件各自局部地包围着对方的蜗轮机构就是双包围蜗轮蜗杆机构。着两者之间的重要区别是,在双包围蜗轮组的轮齿间有面接触,而在单包围的蜗轮组的轮齿间有线接触。一个装置中的蜗杆和蜗轮正像交错轴斜齿轮那样具有相同的齿向,但是其斜齿齿角的角度是极不相同的。蜗杆上的齿斜角度通常很大,而蜗轮上的则极小,因此习惯常规定蜗杆的导角,那就是蜗杆齿斜角的余角;也规定了蜗轮上的齿斜角,该两角之和就等于90度的轴线交角。当齿轮要用来传递相交轴之间的运动时,就需要某种形式的锥齿轮。虽然锥齿轮通常制造成能构成90度轴交角,但它们也可产生任何角度的轴交角。轮齿可以铸出,铣制或滚切加工。仅就滚齿而言就可达一级精度。在典型的锥齿轮安装中,其中一个锥齿轮常常装于支承的外侧。这意味着轴的挠曲情况更加明显而使在轮齿接触上具有更大的影响。另外一个难题,发生在难于预示锥齿轮轮齿上的应力,实际上是由于齿轮被加工成锥状造成的。直齿锥齿轮易于设计且制造简单,如果他们安装的精密而确定,在运转中会产生良好效果。然而在直齿圆柱齿轮情况下,在节线速度较高时,他们将发出噪音。在这些情况下,螺旋锥齿轮比直齿轮能产生平稳的多的啮合作用,因此碰到高速运转的场合那是很有用的。当在汽车的各种不同用途中,有一个带偏心轴的类似锥齿轮的机构,那是常常所希望的。这样的齿轮机构叫做准双曲面齿轮机构,因为它们的节面是双曲回转面。这种齿轮之间的轮齿作用是沿着一根直线上产生滚动与滑动相结合的运动并和蜗轮蜗杆的轮齿作用有着更多的共同之处。轴是一种转动或静止的杆件。通常有圆形横截面。在轴上安装像齿轮,皮带轮,飞轮,曲柄,链轮和其他动力传递零件。轴能够承受弯曲,拉伸,压缩或扭转载荷,这些力相结合时,人们期望找到静强度和疲劳强度作为设计的重要依据。因为单根轴可以承受静压力,变应力和交变应力,所有的应力作用都是同时发生的。“轴”这个词包含着多种含义,例如心轴和主轴。心轴也是轴,既可以旋转也可以静止的轴,但不承受扭转载荷。短的转动轴常常被称为主轴。当轴的弯曲或扭转变形必需被限制于很小的范围内时,其尺寸应根据变形来确定,然后进行应力分析。因此,如若轴要做得有足够的刚度以致挠曲不太大,那么合应力符合安全要求那是完全可能的。但决不意味着设计者要保证;它们是安全的,轴几乎总是要进行计算的,知道它们是处在可以接受的允许的极限以内。因之,设计者无论何时,动力传递零件,如齿轮或皮带轮都应该设置在靠近支持轴承附近。这就减低了弯矩,因而减小变形和弯曲应力。虽然来自M.H.G方法在设计轴中难于应用,但它可能用来准确预示实际失效。这样,它是一个检验已经设计好了的轴的或者发现具体轴在运转中发生损坏原因的好方法。进而有着大量的关于设计的问题,其中由于别的考虑例如刚度考虑,尺寸已得到较好的限制。设计者去查找关于圆角尺寸、热处理、表面光洁度和是否要进行喷丸处理等资料,那真正的唯一的需要是实现所要求的寿命和可靠性。4I 摘 要 本题主要是X6130卧式万能升降台铣床的总体布局及主轴箱的设计,主轴箱 及进给箱是由异步电动机进行驱动,通过齿轮传动,分别使主轴获得12级转速, 进给系统实现14级变速。通过对主轴箱中零部件的分析和校核,合理的选择零 部件包括齿轮,轴等,满足工作时的加工要求,确保加工时铣削零件尺寸、形 状的精度要求。该铣床适用于对平面、斜面、螺旋面及成型表面加工,机床具 有足够的刚度和强度,能进行高速度切削和承受一定强度的切削工作。通过对主 轴箱进行了简要的设计和较核,设计的总体布局满足工艺要求,传动系统满足 加工要求。X6130铣床具有主轴转速高、调速范围宽、操作方便、工作台进给速 度宽等特点,大大提高了加工范围。 关键词: 总体布局;传动系统;主轴箱 II ABSTRACT This problem is mainly X6130 Universal horizontal milling machine lifts the overall layout and design of headstock, headstock and feed box is driven by the induction motor, through gear transmission, respectively, were 12 to spindle speed, feed system to achieve 14 speed. Components of the spindle box through the analysis and verification, a reasonable choice parts, including gears, shafts, etc., to meet the processing requirements work to ensure that when the milling machining parts size, shape precision. The new machine suitable for plane, bevel, helical and molding surface processing, the machine has enough stiffness and strength, to carry out a certain strength to withstand high-speed cutting and cutting work. Through a brief spindle box design and more nuclear, the overall layout of the design meet the technical requirements of transmission system to meet the processing requirements. X6130 milling machine has a spindle speed of high, wide speed range, easy operation, wide table feed speed, etc., greatly increased the range of processing. Key words :Overall layout;Driving System;Headstock 1 目 录 摘要 .I Abstract.II 第 1 章 绪论 .1 1.1 铣床在国民经济中的地位 .1 1.2 铣床工业发展概况和目前水平 .1 1.3 铣床的类型和编号 .2 第 2 章 X6130 卧式升降台铣床总体方案设计 .4 2.1 X6130 型铣床的结构特点主要参数和主要用途 .4 2.1.1 X6130 型铣床的结构和特点 .4 2.1.2 X6130 型铣床的主要参数 .4 2.1.3 X6130 型铣床的主要用途 .4 2.2 主要部分的名称和用途 .5 2.3 铣床的常用卡具 .6 2.3.1 夹具的概念 .6 2.3.2 夹具的作用 .6 2.3.3 铣床夹具的类型 .7 2.3.4 夹具的组成 .7 2.3.5 典型工件在铣床上的装夹方式 .7 2.4 本章小结 .8 第 3 章 X6130 型卧式万能升降台铣床的运动设计 .9 3.1 主运动 .9 3.1.1 主轴传动结构式 .9 3.2 确定结构网及主轴转速表 .9 3.3 本章小结 .11 第 4 章 主轴箱电动机的选择 .12 4.1 主轴箱电机的选择 .12 2 4.1.1 选择电动机的容量 .12 4.1.2 分配总降速比 .12 4.1.3 确定传动轴的轴数 .12 4.1.4 绘制转速图 .13 4.3 本章小结 .13 第 5 章 带传动的设计 .15 5.1 概述 .15 5.1.1 带传动的分类 .15 5.1.2 带传动的失效形式 .15 5.1.3 带传动的设计要求 .15 5.2 带传动的计算及选定 .16 5.2.1 计算带传动的条件 .16 5.2.2 计算内容和步骤 .16 5.4 本章小结 .17 第 6 章 主轴箱齿轮设计和应力计算 .18 6.1 齿轮的概述 .18 6.1.1 齿轮的类型 .18 6.1.2 齿轮传动的主要特点 .18 6.1.3 失效形式及设计准则 .18 6.1.4 齿轮材料及其选择原则 .18 6.2 主轴箱齿轮的设计 .19 6.3 直齿圆柱齿轮应力的计算 .21 6.4 本章小结 .24 第 7 章 轴的设计计算 .25 7.1 轴的概述 .25 7.1.1 轴的功用及分类 .25 7.1.2 轴的受力分析、失效形式和设计准则 .25 7.1.3 轴上零件的固定 .26 7.1.4 轴的加工和装配工艺性 .26 7.2 轴的设计及计算 .27 7.3 轴的设计 .28 3 7.3.1 传动轴直径的确定 .28 7.3.2 主轴轴径的确定 .29 7.3.3 核算转速 .29 7.3.4 主轴的校核 .30 7.4 本章小结 .34 第章 零部件的选择 .35 8.1 键的选择 .35 8.2 滑移齿轮的轴向移动 .36 8.3 润滑系统设计 .37 8.4 本章小结 .37 结论 .38 参考文献 .39 致谢 .40
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