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畢業(yè)設(shè)計(jì)（論文）任務(wù)書
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機(jī)電工程學(xué)院
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機(jī)械工程
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題目名稱
X6130型銑床總體布局及主軸箱設(shè)計(jì)
一、 設(shè)計(jì)（論文）目的、意義
銑床（milling machine）系指主要用銑刀在工件上加工各種表面的機(jī)床。通常銑
刀旋轉(zhuǎn)運(yùn)動(dòng)為主運(yùn)動(dòng)，工件(和)銑刀的移動(dòng)為進(jìn)給運(yùn)動(dòng)。它可以加工平面、垂直面、斜面、各種溝槽或成型面，如果配一些附件（如分度頭）也可以加工螺旋槽，凸輪、成型面等。
臥式萬能升降臺(tái) 有縱、橫、垂三個(gè)進(jìn)給方向，機(jī)床操縱方便，靈活可靠，機(jī)床精度保持性好，符合國(guó)際標(biāo)準(zhǔn)。銑床除能銑削平面、溝槽、輪齒、螺紋和花鍵軸外，還能加工比較復(fù)雜的型面，效率較刨床高，在機(jī)械制造和修理部門得到廣泛應(yīng)用，適用于各類機(jī)械加工部門。
通過銑床運(yùn)動(dòng)機(jī)械變速傳動(dòng)系統(tǒng)的結(jié)構(gòu)設(shè)計(jì)，使學(xué)生在擬定傳動(dòng)和變速的結(jié)構(gòu)的結(jié)構(gòu)方案過程中，得到設(shè)計(jì)構(gòu)思，方案分析，結(jié)構(gòu)工藝性，機(jī)械制圖，零件計(jì)算，編寫技術(shù)文件和查閱技術(shù)資料等方面的綜合訓(xùn)練，樹立正確的設(shè)計(jì)思想，掌握基本的設(shè)計(jì)方法，并培養(yǎng)學(xué)生具有初步的結(jié)構(gòu)分析，結(jié)構(gòu)設(shè)計(jì)和計(jì)算能力
二、設(shè)計(jì)（論文）內(nèi)容、技術(shù)要求
（一）設(shè)計(jì)內(nèi)容
1、X6130主軸變速及傳動(dòng)機(jī)構(gòu)設(shè)計(jì)；
2、X6130外觀總體布局設(shè)計(jì)；
3、主軸、齒輪及零件部件設(shè)計(jì)和驗(yàn)算。
（二）技術(shù)要求
X6130主要規(guī)格及技術(shù)參數(shù)：工作臺(tái)臺(tái)面面積（寬×長(zhǎng)）：300mm×1150mm 主軸轉(zhuǎn)速35-1600r/min
工作臺(tái)最大行程（機(jī)動(dòng)）：
縱向 680mm
橫向 235mm
垂向 400mm
三、設(shè)計(jì)（論文）完成后應(yīng)提交的成果
（一）計(jì)算說明部分
設(shè)計(jì)說明書2份。
（二）圖紙部分
1.A0圖紙2張；
2.A1圖紙1張；
3．A3圖紙5張
四、設(shè)計(jì)（論文）進(jìn)度安排
3月01日~3月07日 查閱資料；
3月08日~3月14日 消化資料；
3月15日~3月21日 撰寫開題報(bào)告；
3月22日~4月11日 方案設(shè)計(jì)、寫說明書草稿；
4月12日~4月25日 畫草圖、寫說明書草稿；
4月26日~5月23日 畫CAD圖、整理說明書；
5月24日~5月30日 打印說明書
5月31日~6月20日 準(zhǔn)備答辯。
五、主要參考資料
[1]徐澋.機(jī)械設(shè)計(jì)手冊(cè)[M].北京：機(jī)械工業(yè)出版社，2002.03
[2]王世剛，張秀親，苗淑杰.機(jī)械設(shè)計(jì)實(shí)踐[M].哈爾濱：哈爾濱工程大學(xué)出版社，2003.08
[3]周湛學(xué).銑工[M].北京：化學(xué)工業(yè)出版社，2005.09
[4]李滬曾，G．Spur徐柄楠．升降臺(tái)銑床動(dòng)態(tài)實(shí)驗(yàn)分析[D].同濟(jì)大學(xué)學(xué)報(bào)，2006.05
[5]周宗明.金屬切削機(jī)床[M].北京：機(jī)械工業(yè)出版社，2004.09
[6]王三民，諸文俊.機(jī)械原理與設(shè)計(jì)[M].北京：機(jī)械工業(yè)出版社，2001.04
[7]侯珍秀.機(jī)械系統(tǒng)設(shè)計(jì)[M].哈爾濱：哈爾濱工業(yè)大學(xué)出版社，2004.11
[8]陳易新.金屬切削機(jī)床課程設(shè)計(jì)指導(dǎo)書[M].北京：機(jī)械工業(yè)出版社，2004.07
[9]劉品，徐曉希.機(jī)械精度設(shè)計(jì)與檢測(cè)基礎(chǔ)[M].哈爾濱：哈爾濱工業(yè)大學(xué)出版社,2004.04
[10]Creamer R H. Machine Design[M]. Addison-Wesley Pub.Co.,1996.06
六、備注
指導(dǎo)教師簽字：
年 月 日
教研室主任簽字：
年 月 日
GEAR AND SHAFT INTRODUCTION
Abstract: The important position of the wheel gear and shaft can't 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;Shaft
In 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.
齒輪和軸的介紹
摘 要:在傳統(tǒng)機(jī)械和現(xiàn)代機(jī)械中齒輪和軸的重要地位是不可動(dòng)搖的。齒輪和軸主要安裝在主軸箱來傳遞力的方向。通過加工制造它們可以分為許多的型號(hào)，分別用于許多的場(chǎng)合。所以我們對(duì)齒輪和軸的了解和認(rèn)識(shí)必須是多層次多方位的。
關(guān)鍵詞:齒輪；軸；機(jī)床
在直齒圓柱齒輪的受力分析中，是假定各力作用在單一平面的。我們將研究作用力具有三維坐標(biāo)的齒輪。因此，在斜齒輪的情況下，其齒向是不平行于回轉(zhuǎn)軸線的。而在錐齒輪的情況中各回轉(zhuǎn)軸線互相不平行。像我們要討論的那樣，尚有其他道理需要學(xué)習(xí)，掌握。
斜齒輪用于傳遞平行軸之間的運(yùn)動(dòng)。傾斜角度每個(gè)齒輪都一樣，但一個(gè)必須右旋斜齒，而另一個(gè)必須是左旋斜齒。齒的形狀是一濺開線螺旋面。如果一張被剪成平行四邊形（矩形）的紙張包圍在齒輪圓柱體上，紙上印出齒的角刃邊就變成斜線。如果我展開這張紙，在血角刃邊上的每一個(gè)點(diǎn)就發(fā)生一漸開線曲線。
直齒圓柱齒輪輪齒的初始接觸處是跨過整個(gè)齒面而伸展開來的線。斜齒輪輪齒的初始接觸是一點(diǎn)，當(dāng)齒進(jìn)入更多的嚙合時(shí)，它就變成線。在直齒圓柱齒輪中，接觸是平行于回轉(zhuǎn)軸線的。在斜齒輪中，該先是跨過齒面的對(duì)角線。它是齒輪逐漸進(jìn)行嚙合并平穩(wěn)的從一個(gè)齒到另一個(gè)齒傳遞運(yùn)動(dòng)，那樣就使斜齒輪具有高速重載下平穩(wěn)傳遞運(yùn)動(dòng)的能力。斜齒輪使軸的軸承承受徑向和軸向力。當(dāng)軸向推力變的大了或由于別的原因而產(chǎn)生某些影響時(shí)，那就可以使用人字齒輪。雙斜齒輪（人字齒輪）是與反向的并排地裝在同一軸上的兩個(gè)斜齒輪等效。他們產(chǎn)生相反的軸向推力作用，這樣就消除了軸向推力。當(dāng)兩個(gè)或更多個(gè)單向齒斜齒輪被在同一軸上時(shí)，齒輪的齒向應(yīng)作選擇，以便產(chǎn)生最小的軸向推力。
交錯(cuò)軸斜齒輪或螺旋齒輪，他們是軸中心線既不相交也不平行。交錯(cuò)軸斜齒輪的齒彼此之間發(fā)生點(diǎn)接觸，它隨著齒輪的磨合而變成線接觸。因此他們只能傳遞小的載荷和主要用于儀器設(shè)備中，而且肯定不能推薦在動(dòng)力傳動(dòng)中使用。交錯(cuò)軸斜齒輪與斜齒輪之間在被安裝后互相捏合之前是沒有任何區(qū)別的。它們是以同樣的方法進(jìn)行制造。一對(duì)相嚙合的交錯(cuò)軸斜齒輪通常具有同樣的齒向，即左旋主動(dòng)齒輪跟右旋從動(dòng)齒輪相嚙合。在交錯(cuò)軸斜齒設(shè)計(jì)中，當(dāng)該齒的斜角相等時(shí)所產(chǎn)生滑移速度最小。然而當(dāng)該齒的斜角不相等時(shí)，如果兩個(gè)齒輪具有相同齒向的話，大斜角齒輪應(yīng)用作主動(dòng)齒輪。
蝸輪與交錯(cuò)軸斜齒輪相似。小齒輪即蝸桿具有較小的齒數(shù)，通常是一到四齒，由于它們完全纏繞在節(jié)圓柱上，因此它們被稱為螺紋齒。與其相配的齒輪叫做蝸輪，蝸輪不是真正的斜齒輪。蝸桿和蝸輪通常是用于向垂直相交軸之間的傳動(dòng)提供大的角速度減速比。蝸輪不是斜齒輪，因?yàn)槠潺X頂面做成中凹形狀以適配蝸桿曲率，目的是要形成線接觸而不是點(diǎn)接觸。然而蝸桿蝸輪傳動(dòng)機(jī)構(gòu)中存在齒間有較大滑移速度的缺點(diǎn)，正像交錯(cuò)軸斜齒輪那樣。
蝸桿蝸輪機(jī)構(gòu)有單包圍和雙包圍機(jī)構(gòu)。單包圍機(jī)構(gòu)就是蝸輪包裹著蝸桿的一種機(jī)構(gòu)。當(dāng)然，如果每個(gè)構(gòu)件各自局部地包圍著對(duì)方的蝸輪機(jī)構(gòu)就是雙包圍蝸輪蝸桿機(jī)構(gòu)。著兩者之間的重要區(qū)別是，在雙包圍蝸輪組的輪齒間有面接觸，而在單包圍的蝸輪組的輪齒間有線接觸。一個(gè)裝置中的蝸桿和蝸輪正像交錯(cuò)軸斜齒輪那樣具有相同的齒向，但是其斜齒齒角的角度是極不相同的。蝸桿上的齒斜角度通常很大，而蝸輪上的則極小，因此習(xí)慣常規(guī)定蝸桿的導(dǎo)角，那就是蝸桿齒斜角的余角；也規(guī)定了蝸輪上的齒斜角，該兩角之和就等于90度的軸線交角。
當(dāng)齒輪要用來傳遞相交軸之間的運(yùn)動(dòng)時(shí)，就需要某種形式的錐齒輪。雖然錐齒輪通常制造成能構(gòu)成90度軸交角，但它們也可產(chǎn)生任何角度的軸交角。輪齒可以鑄出，銑制或滾切加工。僅就滾齒而言就可達(dá)一級(jí)精度。在典型的錐齒輪安裝中，其中一個(gè)錐齒輪常常裝于支承的外側(cè)。這意味著軸的撓曲情況更加明顯而使在輪齒接觸上具有更大的影響。
另外一個(gè)難題，發(fā)生在難于預(yù)示錐齒輪輪齒上的應(yīng)力，實(shí)際上是由于齒輪被加工成錐狀造成的。
直齒錐齒輪易于設(shè)計(jì)且制造簡(jiǎn)單，如果他們安裝的精密而確定，在運(yùn)轉(zhuǎn)中會(huì)產(chǎn)生良好效果。然而在直齒圓柱齒輪情況下，在節(jié)線速度較高時(shí)，他們將發(fā)出噪音。在這些情況下，螺旋錐齒輪比直齒輪能產(chǎn)生平穩(wěn)的多的嚙合作用，因此碰到高速運(yùn)轉(zhuǎn)的場(chǎng)合那是很有用的。當(dāng)在汽車的各種不同用途中，有一個(gè)帶偏心軸的類似錐齒輪的機(jī)構(gòu)，那是常常所希望的。這樣的齒輪機(jī)構(gòu)叫做準(zhǔn)雙曲面齒輪機(jī)構(gòu)，因?yàn)樗鼈兊墓?jié)面是雙曲回轉(zhuǎn)面。這種齒輪之間的輪齒作用是沿著一根直線上產(chǎn)生滾動(dòng)與滑動(dòng)相結(jié)合的運(yùn)動(dòng)并和蝸輪蝸桿的輪齒作用有著更多的共同之處。
軸是一種轉(zhuǎn)動(dòng)或靜止的桿件。通常有圓形橫截面。在軸上安裝像齒輪，皮帶輪，飛輪，曲柄，鏈輪和其他動(dòng)力傳遞零件。軸能夠承受彎曲，拉伸，壓縮或扭轉(zhuǎn)載荷，這些力相結(jié)合時(shí)，人們期望找到靜強(qiáng)度和疲勞強(qiáng)度作為設(shè)計(jì)的重要依據(jù)。因?yàn)閱胃S可以承受靜壓力，變應(yīng)力和交變應(yīng)力，所有的應(yīng)力作用都是同時(shí)發(fā)生的。
“軸”這個(gè)詞包含著多種含義，例如心軸和主軸。心軸也是軸，既可以旋轉(zhuǎn)也可以靜止的軸，但不承受扭轉(zhuǎn)載荷。短的轉(zhuǎn)動(dòng)軸常常被稱為主軸。
當(dāng)軸的彎曲或扭轉(zhuǎn)變形必需被限制于很小的范圍內(nèi)時(shí)，其尺寸應(yīng)根據(jù)變形來確定，然后進(jìn)行應(yīng)力分析。因此，如若軸要做得有足夠的剛度以致?lián)锨惶螅敲春蠎?yīng)力符合安全要求那是完全可能的。但決不意味著設(shè)計(jì)者要保證；它們是安全的，軸幾乎總是要進(jìn)行計(jì)算的，知道它們是處在可以接受的允許的極限以內(nèi)。因之，設(shè)計(jì)者無論何時(shí)，動(dòng)力傳遞零件，如齒輪或皮帶輪都應(yīng)該設(shè)置在靠近支持軸承附近。這就減低了彎矩，因而減小變形和彎曲應(yīng)力。
雖然來自M.H.G方法在設(shè)計(jì)軸中難于應(yīng)用，但它可能用來準(zhǔn)確預(yù)示實(shí)際失效。這樣，它是一個(gè)檢驗(yàn)已經(jīng)設(shè)計(jì)好了的軸的或者發(fā)現(xiàn)具體軸在運(yùn)轉(zhuǎn)中發(fā)生損壞原因的好方法。進(jìn)而有著大量的關(guān)于設(shè)計(jì)的問題，其中由于別的考慮例如剛度考慮，尺寸已得到較好的限制。
設(shè)計(jì)者去查找關(guān)于圓角尺寸、熱處理、表面光潔度和是否要進(jìn)行噴丸處理等資料，那真正的唯一的需要是實(shí)現(xiàn)所要求的壽命和可靠性。
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I 摘 要 本題主要是X6130臥式萬能升降臺(tái)銑床的總體布局及主軸箱的設(shè)計(jì)，主軸箱 及進(jìn)給箱是由異步電動(dòng)機(jī)進(jìn)行驅(qū)動(dòng)，通過齒輪傳動(dòng)，分別使主軸獲得12級(jí)轉(zhuǎn)速， 進(jìn)給系統(tǒng)實(shí)現(xiàn)14級(jí)變速。通過對(duì)主軸箱中零部件的分析和校核，合理的選擇零 部件包括齒輪，軸等，滿足工作時(shí)的加工要求，確保加工時(shí)銑削零件尺寸、形 狀的精度要求。該銑床適用于對(duì)平面、斜面、螺旋面及成型表面加工，機(jī)床具 有足夠的剛度和強(qiáng)度,能進(jìn)行高速度切削和承受一定強(qiáng)度的切削工作。通過對(duì)主 軸箱進(jìn)行了簡(jiǎn)要的設(shè)計(jì)和較核，設(shè)計(jì)的總體布局滿足工藝要求，傳動(dòng)系統(tǒng)滿足 加工要求。X6130銑床具有主軸轉(zhuǎn)速高、調(diào)速范圍寬、操作方便、工作臺(tái)進(jìn)給速 度寬等特點(diǎn)，大大提高了加工范圍。 關(guān)鍵詞： 總體布局；傳動(dòng)系統(tǒng)；主軸箱 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 錄 摘要 ...............................................................................................................................I Abstract........................................................................................................................II 第 1 章 緒論 ............................................................................................................1 1.1 銑床在國(guó)民經(jīng)濟(jì)中的地位 ..............................................................................1 1.2 銑床工業(yè)發(fā)展概況和目前水平 ......................................................................1 1.3 銑床的類型和編號(hào) ..........................................................................................2 第 2 章 X6130 臥式升降臺(tái)銑床總體方案設(shè)計(jì) ............................................4 2.1 X6130 型銑床的結(jié)構(gòu)特點(diǎn)主要參數(shù)和主要用途 ..........................................4 2.1.1 X6130 型銑床的結(jié)構(gòu)和特點(diǎn) ...............................................................4 2.1.2 X6130 型銑床的主要參數(shù) ...................................................................4 2.1.3 X6130 型銑床的主要用途 ...................................................................4 2.2 主要部分的名稱和用途 .................................................................................5 2.3 銑床的常用卡具 .............................................................................................6 2.3.1 夾具的概念 ..........................................................................................6 2.3.2 夾具的作用 ..........................................................................................6 2.3.3 銑床夾具的類型 ..................................................................................7 2.3.4 夾具的組成 ..........................................................................................7 2.3.5 典型工件在銑床上的裝夾方式 ..........................................................7 2.4 本章小結(jié) .........................................................................................................8 第 3 章 X6130 型臥式萬能升降臺(tái)銑床的運(yùn)動(dòng)設(shè)計(jì) ...................................9 3.1 主運(yùn)動(dòng) .............................................................................................................9 3.1.1 主軸傳動(dòng)結(jié)構(gòu)式 ..................................................................................9 3.2 確定結(jié)構(gòu)網(wǎng)及主軸轉(zhuǎn)速表 .............................................................................9 3.3 本章小結(jié) .......................................................................................................11 第 4 章 主軸箱電動(dòng)機(jī)的選擇 .........................................................................12 4.1 主軸箱電機(jī)的選擇 .......................................................................................12 2 4.1.1 選擇電動(dòng)機(jī)的容量 .........................................................................12 4.1.2 分配總降速比 ...................................................................................12 4.1.3 確定傳動(dòng)軸的軸數(shù) ...........................................................................12 4.1.4 繪制轉(zhuǎn)速圖 .......................................................................................13 4.3 本章小結(jié) .......................................................................................................13 第 5 章 帶傳動(dòng)的設(shè)計(jì) ..........................................................................................15 5.1 概述 ...............................................................................................................15 5.1.1 帶傳動(dòng)的分類 ....................................................................................15 5.1.2 帶傳動(dòng)的失效形式 ............................................................................15 5.1.3 帶傳動(dòng)的設(shè)計(jì)要求 ............................................................................15 5.2 帶傳動(dòng)的計(jì)算及選定 ....................................................................................16 5.2.1 計(jì)算帶傳動(dòng)的條件 ............................................................................16 5.2.2 計(jì)算內(nèi)容和步驟 ................................................................................16 5.4 本章小結(jié) .......................................................................................................17 第 6 章 主軸箱齒輪設(shè)計(jì)和應(yīng)力計(jì)算 ...........................................................18 6.1 齒輪的概述 ....................................................................................................18 6.1.1 齒輪的類型 ........................................................................................18 6.1.2 齒輪傳動(dòng)的主要特點(diǎn) ........................................................................18 6.1.3 失效形式及設(shè)計(jì)準(zhǔn)則 ........................................................................18 6.1.4 齒輪材料及其選擇原則 ....................................................................18 6.2 主軸箱齒輪的設(shè)計(jì) .......................................................................................19 6.3 直齒圓柱齒輪應(yīng)力的計(jì)算 ...........................................................................21 6.4 本章小結(jié) .......................................................................................................24 第 7 章 軸的設(shè)計(jì)計(jì)算 .......................................................................................25 7.1 軸的概述 .......................................................................................................25 7.1.1 軸的功用及分類 ................................................................................25 7.1.2 軸的受力分析、失效形式和設(shè)計(jì)準(zhǔn)則 ............................................25 7.1.3 軸上零件的固定 ................................................................................26 7.1.4 軸的加工和裝配工藝性 ....................................................................26 7.2 軸的設(shè)計(jì)及計(jì)算 ...........................................................................................27 7.3 軸的設(shè)計(jì) ........................................................................................................28 3 7.3.1 傳動(dòng)軸直徑的確定 ............................................................................28 7.3.2 主軸軸徑的確定 ................................................................................29 7.3.3 核算轉(zhuǎn)速 ............................................................................................29 7.3.4 主軸的校核 ........................................................................................30 7.4 本章小結(jié) ......................................................................................................34 第章 零部件的選擇 .......................................................................................35 8.1 鍵的選擇 .......................................................................................................35 8.2 滑移齒輪的軸向移動(dòng) ...................................................................................36 8.3 潤(rùn)滑系統(tǒng)設(shè)計(jì) ...............................................................................................37 8.4 本章小結(jié) .......................................................................................................37 結(jié)論 .............................................................................................................................38 參考文獻(xiàn) ...................................................................................................................39 致謝 .............................................................................................................................40