多軸鉆床設(shè)計(jì)

購(gòu)買設(shè)計(jì)請(qǐng)充值后下載，資源目錄下的文件所見即所得，都可以點(diǎn)開預(yù)覽，資料完整，充值下載可得到資源目錄里的所有文件。【注】：dwg后綴為CAD圖紙，doc,docx為WORD文檔，原稿無(wú)水印，可編輯。具體請(qǐng)見文件預(yù)覽，有不明白之處，可咨詢QQ:12401814 中文翻譯：軸承的振動(dòng)分析Dr. S. J. Lacey舍夫勒(英國(guó))有限公司工程經(jīng)理摘要：在生產(chǎn)過(guò)程中,滾動(dòng)軸承振動(dòng)產(chǎn)生的復(fù)雜幾何缺陷可能會(huì)導(dǎo)致滾動(dòng)表面上的缺陷或相關(guān)組件的幾何誤差。噪音和振動(dòng)在所有類型的設(shè)備中正變得越來(lái)越關(guān)鍵,因?yàn)樗３１徽J(rèn)為是質(zhì)量的代名詞并常被用于預(yù)測(cè)和維護(hù)。這篇文章是關(guān)于一些軸承振動(dòng)的不同來(lái)源是如何隨著缺陷的頻率特征而展現(xiàn)出來(lái)的。文中給出了一些例子來(lái)說(shuō)明了如何利用振動(dòng)來(lái)進(jìn)一步分析探測(cè)機(jī)器狀態(tài)的惡化。關(guān)鍵詞：軸承振動(dòng)，維修工程，可靠性工程，振動(dòng)探測(cè)。介紹：幾乎所有類型的旋轉(zhuǎn)機(jī)械都要用到滾動(dòng)接觸軸承，他們的可靠性依賴于軸承選定的類型以及所有相關(guān)組件的精度,即軸、墊片、螺帽等。在假定軸承正確安裝、操作和維護(hù)時(shí)，軸承工程師一般使用疲勞和正常的失效模式。今天，由于制造工藝和材料的改進(jìn)，一般情況下軸承疲勞壽命（與表面應(yīng)力相關(guān)）并不是限制因素而且不必考慮那些不足3%的誤差。不過(guò)，盡管許多軸承因?yàn)槲廴尽?rùn)滑不良、極端溫度、惡劣的裝修、不平衡和不合理的維修而過(guò)早失效，所有這些因素導(dǎo)致軸承振動(dòng)的增加，而且在使用了多年之后的狀態(tài)監(jiān)測(cè)仍然會(huì)對(duì)軸承造成災(zāi)難性失效(與停工期的相關(guān)費(fèi)用或身體機(jī)器其他部位的重大損害)。滾動(dòng)軸承通常被用于噪聲敏感的電器中，如家電用電動(dòng)機(jī)往往使用中小型軸承。因此軸承振動(dòng)不論是從它對(duì)機(jī)器質(zhì)量的重要性方面，還是從環(huán)境方面考慮，它都變得越來(lái)越重要。現(xiàn)在人們普遍認(rèn)為安靜的運(yùn)行形式是滾動(dòng)接觸表面光潔度的代名詞。因此，軸承制造商已經(jīng)開發(fā)它們作為衡量質(zhì)量和振動(dòng)試驗(yàn)的有效方法。一個(gè)常用的方法是把它安裝在一個(gè)安靜運(yùn)行的主軸軸承上和對(duì)軸承的外圈點(diǎn)和三個(gè)頻段，分別是徑向速度。 50-300，300-1800和1800-10000赫茲。軸承必須符合三個(gè)頻段的均方根速度的限制。由于軸承振動(dòng)信號(hào)是由機(jī)械結(jié)構(gòu)修改的，所以在大多數(shù)情況下軸承振動(dòng)不能被直接測(cè)量。這種情況下因?yàn)槠渌O(shè)備（如電動(dòng)馬達(dá)，齒輪，皮帶）的振動(dòng)進(jìn)一步復(fù)雜化，會(huì)使那些未受過(guò)訓(xùn)練的專家很難對(duì)振動(dòng)數(shù)據(jù)做出解釋，在某些情況下會(huì)導(dǎo)致誤診斷，造成不必要的停機(jī)時(shí)間和成本增加。振動(dòng)源： 滾動(dòng)軸承振動(dòng)是一個(gè)復(fù)雜的系統(tǒng)，其組成部分包括：滾動(dòng)體，內(nèi)滾道，外圈滾道和籠，相互作用產(chǎn)生復(fù)雜的振動(dòng)。雖然滾動(dòng)軸承是采用高精密機(jī)床加工，進(jìn)行嚴(yán)格的質(zhì)量控制和清潔，像其他制成品一樣，通過(guò)互動(dòng)的滾動(dòng)和滑動(dòng)組合，他們有缺陷且表面產(chǎn)生震動(dòng)。如今，雖然表面缺陷的幅度在納米級(jí)別，仍然可以在整個(gè)可聽頻率范圍（20赫茲- 20千赫）內(nèi)產(chǎn)生顯著的振動(dòng)。該振動(dòng)水平將取決于許多因素，包括沖擊能量，在哪個(gè)振動(dòng)測(cè)量點(diǎn)和軸承的結(jié)構(gòu)。變量合規(guī)： 即使軸承有非常完美的幾何外形，在承受徑向載荷下，軸承振動(dòng)也是滾動(dòng)軸承的固有特點(diǎn)，而非質(zhì)量差的原因。這樣的振動(dòng)類型通常被稱為變量合規(guī)，而且外部負(fù)載發(fā)生的原因是其位置由一個(gè)方面的負(fù)荷隨時(shí)間不斷變化造成的。（見圖1） 圖1變剛度振動(dòng)嚴(yán)重依賴于配套的滾動(dòng)體外所加的負(fù)載數(shù)目，滾動(dòng)體的數(shù)量越多，它的振動(dòng)就越小。由于徑向加載或錯(cuò)位軸承的游隙決定了外部負(fù)載區(qū)域，因此，一般情況下隨著間隙變合規(guī)，運(yùn)行間隙不應(yīng)與徑向內(nèi)部游隙（里克）相混淆，由于過(guò)盈配合運(yùn)行中的內(nèi)、外圈熱膨脹的原因，前者通常是低于里克。變剛度振動(dòng)水平可以比粗糙度和表面波紋度的滾動(dòng)產(chǎn)生的更高。然而，在應(yīng)用中至關(guān)重要的是振動(dòng)可以通過(guò)使用正確的水平軸向預(yù)緊力來(lái)減少到一個(gè)可以忽略的水平。幾何缺陷： 由于生產(chǎn)過(guò)程中使用的性質(zhì)，生產(chǎn)軸承零件的幾何缺陷將始終存在，其不同程度根據(jù)軸承精度等級(jí)而定。對(duì)于受壓球軸承在中等速度運(yùn)行下的臨界軋制表面形式和表面光潔度是軸承的噪音和振動(dòng)的最大來(lái)源。因此控制部件波紋和在生產(chǎn)過(guò)程中的表面光潔度是至關(guān)重要的，因?yàn)樗赡懿粌H有顯著影響，而且振動(dòng)可能會(huì)影響軸承的使用壽命。為方便起見，考慮到滾動(dòng)體，滾道的接觸寬度不完善之處幾何缺陷的波長(zhǎng) 被稱為粗糙表面特征，而波長(zhǎng)較長(zhǎng)的特點(diǎn)被稱為波紋（見圖2）。 圖2 表面粗糙度： 表面粗糙度是振動(dòng)的一個(gè)重要的來(lái)源，當(dāng)其表面粗糙度高時(shí)，在滾動(dòng)體與滾道的接觸處（見圖2）產(chǎn)生較厚的潤(rùn)滑油膜。在此條件下表面粗糙可以突破潤(rùn)滑膜，并與對(duì)方互動(dòng)的表面，造成金屬與金屬的接觸。由此產(chǎn)生的振動(dòng)，組成了一個(gè)激發(fā)所有的軸承和支撐結(jié)構(gòu)的自然模式隨機(jī)序列。 表面粗糙度產(chǎn)生的振動(dòng)主要發(fā)生在六十次頻率軸承轉(zhuǎn)速上。因此頻譜的高頻部分通常顯示為一個(gè)系列的共振。用于估計(jì)相互作用的粗程度一個(gè)常見的參數(shù)是lambda比（）。這是復(fù)合潤(rùn)滑膜厚度，表面粗 糙度糙度比率，由表達(dá)式給出 = h (2 + r2)0.5 其中 =粗糙程度的相互作用 h=油膜厚度 =粗糙度球 r=滾道表面粗糙度 圖3如果我們假定滾道表面光潔度是滾動(dòng)體的兩倍，那么對(duì)于一個(gè)典型的潤(rùn)滑油膜厚度為0.3m的表面飾面比0.06微米更加需要實(shí)現(xiàn)三值和較低的相互作用發(fā)生率。如需0.1_m表面潤(rùn)滑油膜厚度比0.025_m完成須達(dá)到= 3。 對(duì)軸承的壽命的影響見圖3。如果小于1，軸承將因破損而不可能達(dá)到估計(jì)的設(shè)計(jì)使用年限，這可能迅速導(dǎo)致滾動(dòng)表面疲勞破壞。一般來(lái)說(shuō)，比值大于三顯示完整的表面分離。從全彈流（彈流潤(rùn)滑）過(guò)渡到混合潤(rùn)滑（有些粗糙接觸彈流潤(rùn)滑膜部分）發(fā)生在1至3范圍。 波紋： 對(duì)于更長(zhǎng)波長(zhǎng)的表面特征，與赫茲觸點(diǎn)相比峰值是低的，滾動(dòng)運(yùn)動(dòng)是隨著表面輪廓與滾動(dòng)體相連續(xù)的。表面間的幾何形狀和振動(dòng)水平的關(guān)系是復(fù)雜的，視軸承和接觸幾何以及載荷和速度情況而定。波紋能夠產(chǎn)生振動(dòng)頻率高達(dá)約三百次的旋轉(zhuǎn)速度，但通常是低于六十次的頻率轉(zhuǎn)速為主。上限是由于滾動(dòng)體的滾道接觸的有限區(qū)域最終得到更短特點(diǎn)的平均波長(zhǎng)。在滾動(dòng)方向上，接觸時(shí)彈性變形減輕對(duì)簡(jiǎn)單的諧波波形接觸寬度見圖4。 圖4在極限情況下，波長(zhǎng)隨衰減水平的減小而提高，直到一個(gè)波長(zhǎng)等于接觸寬度，波紋幅度在理論上是零。接觸長(zhǎng)度也是短波長(zhǎng)的衰減表面特征。通常較差的相關(guān)性可能存在于平行面之間高度的軌道，在不同的點(diǎn)抽取不同的配置文件，并全波紋度測(cè)量幅值平均值低一級(jí)。對(duì)于典型的軸承表面的平行面只有在更短的波長(zhǎng)存在較差的相關(guān)性。即使是現(xiàn)代精密加工技術(shù)波紋也不能被完全消除，盡管在相對(duì)較低的水平，但波紋元素將始終存在。對(duì)于軸承本身，相關(guān)的零部件的質(zhì)量也會(huì)影響軸承的振動(dòng)而且任何軸的幾何外徑的誤差，可能在振動(dòng)軸承的滾道中反映出來(lái)。因此，需要特別注意形式和所有相關(guān)的軸承零件的精度。離散缺陷： 而表面粗糙度和波紋度的結(jié)果直接從軸承零部件生產(chǎn)制造工藝，離散的缺陷是指表面的滾動(dòng)由于污染，操作，安裝，保養(yǎng)不善等而造成的過(guò)大的損害。這些缺陷可能會(huì)非常小，難以察覺，但可能對(duì)振動(dòng)的關(guān)鍵設(shè)備產(chǎn)生重大影響或可能導(dǎo)致軸承壽命降低。此類缺陷可能有很多種類的形式。壓痕，劃痕和整個(gè)沿軋制表面，坑，碎片及潤(rùn)滑油中的顆粒。軸承制造商對(duì)成品缺陷的檢測(cè)都采用簡(jiǎn)單的振動(dòng)測(cè)量，但這些往往受到軸承的類型和大小的限制。這方面的一個(gè)類型的測(cè)量例子如圖5（a）和5（b）所示，與一個(gè)良好的軸承相比，在軸承外圈滾道離散損害產(chǎn)生了典型的脈沖振動(dòng)，具有較高的峰值/有效值比。圖5（a）圖5（b）在大量的缺陷發(fā)生個(gè)別峰值處不具有很明確的定義，但在RMS振動(dòng)水平數(shù)倍于通常與軸承相關(guān)的良好條件的總和。參考文獻(xiàn)1.Harris T A, Rolling Bearing Analysis (4th Ed), Wiley, New York, 2001.2.Lacey S J, Vibration monitoring of the internal centreless grinding process, Part 1: mathematical models. Proc Instn Mech Engrs. Vol 24. 1990.3.Lacey S J, Vibration monitoring of the internal centreless grinding process, Part 2: experimental results. Proc Instn Mech Engrs. Vol 24. 1990.4.Wardle F P and Lacey S J, Vibration Research in RHP. Acoustics Bulletin.外文資料：An Overview of Bearing Vibration AnalysisDr. S. J. LaceyEngineering Manager, Schaeffler (UK) Ltd AbstractVibration produced by rolling bearings can be complex and can result from geometrical imperfections during the manufacturing process, defects on the rolling surfaces or geometrical errors in associated components. Noise and vibration is becoming more critical in all types of equipment since it is often perceived to be synonymous with quality and often used for predictive maintenance. In this article the different sources of bearing vibration are considered along with some of the characteristic defect frequencies that may be present. Some examples of how vibration analysis can be used to detect deterioration in machine condition are also given.Keywords: Bearing Vibration, maintenance engineering, reliability engineering, Vibration detectionINTRODUCTIONRolling contact bearings are used in almost every type of rotating machinery whose successful and reliable operation is very dependent on the type of bearing selected as well as the precision of all associated components, i.e. shaft, housing, spacers, nuts etc. Bearing engineers generally use fatigue as the normal failure mode, on the assumption that the bearings are properly installed, operated and maintained. Today, because of improvements in manufacturing technology and materials, it is generally the case that bearing fatigue life, which is related to sub-surface stresses, is not the limiting factor and probably accounts for less than 3% of failures in service. Unfortunately though, many bearings fail prematurely in service because of contamination, poor lubrication, temperature extremes, poor fitting/fits, unbalance and misalignment. All these factors lead to an increase in bearing vibration and condition monitoring has been used for many years to detect degrading bearings before they catastrophically fail (with the associated costs of downtime or significant damage to other parts of the machine). Rolling element bearings are often used in noise sensitive applications, e.g. household appliance electric motors which often use small to medium size bearings. Bearing vibration is therefore becoming increasingly important from both an environmental consideration and because it is synonymous with quality. It is now generally accepted that quiet running is synonymous with the form and finish of the rolling contact surfaces. As a result, bearing manufacturers have developed vibration tests as an effective method for measuring quality. A common approach is to mount the bearing on a quiet running spindle and measure the radial velocity at a point on the bearings outer ring and in three frequency bands, viz. 50-300, 300-1800 and1800-10000 Hz. The bearing must meet RMS velocity limits in all three frequency bands. in most situations bearing vibration cannot be measured directly and so the bearing vibration signature is modified by the machine structure, this situation being further complicated by vibration from other equipment on the machine, i.e. electric motors, gears, belts, hydraulics, structural resonances etc. This often makes the interpretation of vibration data difficult other than by a trained specialist and can in some situations lead to a mis-diagnosis, resulting in unnecessary machine downtime and costs. In this paper the sources of bearing vibration are discussed along with the characteristic vibration frequencies that are likely to be generated.SOURCES OF VIBRATION Rolling contact bearings represents a complex vibration system whose components i.e. rolling elements, inner raceway, outer raceway and cage interact to generate complex vibration signatures. Although rolling bearings are manufactured using high precision machine tools and under strict cleanliness and quality controls, like any other manufactured part they will have degrees of imperfection and generate vibration as the surfaces interact through a combination of rolling and sliding. Nowadays, although the amplitudes of surface imperfections are in the order of nanometres, significant vibrations can still be produced in the entire audible frequency range (20 Hz 20 kHz). The level of the vibration will depend upon many factors, including the energy of the impact, the point at which the vibration is measured and the construction of the bearing.Variable compliance Under radial and misaligning loads bearing vibration is an inherent feature of rolling bearings even if the bearing is geometrically perfect and is not therefore indicative of poor quality. This type of vibration is often referred to as variable compliance and occurs because the external load is supported by a discrete number of rolling elements whose position with respect to the line of action of the load continually changes with time (see Figure 1).圖1 Variable compliance vibration is heavily dependent on the number of rolling elements supporting the externally applied load; the greater the number of loaded rolling elements, the less the vibration. For radially loaded or misaligned bearings running clearance determines the extent of the load region, and hence, in general, variable compliance increases with clearance. Running clearance should not be confused with radial internal clearance (RIC), the former normally being lower than the RIC due to interference fit of the rings and differential thermal expansion of the inner and outer rings during operation. Variable compliance vibration levels can be higher than those produced by roughness and waviness of the rolling surfaces. However, in applications where vibration is critical it can be reduced to a negligible level by using ball bearings with the correct level of axial pre-load.Geometrical imperfectionsBecause of the very nature of the manufacturing processes used to produce bearing components geometrical imperfections will always be present to varying degrees depending on the accuracy class of the bearing. For axially loaded ball bearings operating under moderate speeds the form and surface finish of the critical rolling surfaces are generally the largest source of noise and vibration. Controlling component waviness and surface finish during the manufacturing process is therefore critical since it may not only have a significant effect on vibration but also may affect bearing life. It is convenient to consider geometrical imperfections in terms of wavelength compared with the width of the rolling element-raceway contacts. Surface features of wavelength of the order of the contact width or less are termed roughness, whereas longer wavelength features are termed waviness (see Figure 2). 圖2SURFACE ROUGHNESS Surface roughness is a significant source of vibration when its level is high compared with the lubricant film thickness generated between the rolling element-raceway contacts (see Figure 2). Under this condition surface asperities can break through the lubricant film and interact with the opposing surface, resulting in metal-to-metal contact. The resulting vibration consists of a random sequence of small impulses which excite all the natural modes of the bearing and supporting structure. Surface roughness produces vibration predominantly at frequencies above sixty times the rotational speed of the bearing. Thus the high frequency part of the spectrum usually appears as a series of resonances. A common parameter used to estimate the degree of asperity interaction is the lambda ratio (). This is the ratio of lubricant film thickness to composite surface roughness and is given by the expression = h (2 + r2)0.5 where =degree of asperity interaction h =the lubricant film thickness =RMS roughness of the ball r =RMS roughness of the racewayIf we assume that the surface finish of the raceway is twice that of rolling element, then for a typical lubricant film thickness of 0.3m surface finishes better than 0.06 m are required to achieve avalue of three and a low incidence of asperity interaction. For a lubricant film thickness of 0.1_m surface finishes better than 0.025 _m are required to achieve =3. The effect of on bearing life is shown in Figure 3.圖3If is less than unity it is unlikely that the bearing will attain its estimated design life because of surface distress, which can lead to a rapid fatigue failure of the rolling surfaces. In general, ratios greater than three indicate complete surface separation. A transition from full EHL (elastohydrodynamic lubrication) to mixed lubrication (partial EHL film with some asperity contact) occurs in the range .Waviness For longer wavelength surface features, peak curvatures are low compared with that of the Hertzian contacts and rolling motion is continuous with the rolling elements following the surface contours. The relationship between surface geometry and vibration level is complex, being dependent upon the bearing and contact geometry as well as conditions of load and speed. Waviness can produce vibration at frequencies up to approximately three hundred times rotational speed but is usually predominant at frequencies below sixty times rotational speed. The upper limit is attributed to the finite area of the rolling element raceway contacts which average out the shorter wavelength features.In the direction of rolling, elastic deformation at the contact attenuates simple harmonic waveforms over the contact width (see Figure 4).圖4 The level of attenuation increases as wavelength decreases until, in the limit, for a wavelength equal to the contact width, waviness amplitude is theoretically zero. The contact length also attenuates short wavelength surface features. Generally poor correlation can exist between parallel surface height profiles taken at different points across the tracks and this averages measured waviness amplitudes to a low level. For typical bearing surfaces poor correlation of parallel surface heights profiles only exists at shorter wavelengths.Even with modern precision machining technology waviness cannot be eliminated completely and an element of waviness will always exist albeit at relatively low levels. As well as the bearing itself, the quality of the associated components can also affect bearing vibration and any geometrical errors on the outside diameter of the shaft or bore of the housing can be reflected on the bearing raceways with the associated increase in vibration. Therefore, careful attention is required to the form and precision of all associated bearing components. Discrete defectsWhereas surface roughness and waviness result directly from the bearing component manufacturing processes, discrete defects refer to damage of the rolling surfaces due to assembly, contamination, operation, mounting, poor maintenance etc. These defects can be extremely small and difficult to detect and yet can have a significant impact on vibration-critical equipment or can result in reduced bearing life. This type of defect can take a variety of forms, viz. indentations, scratches along and across the rolling surfaces, pits, debris and particles in the lubricant. Bearing manufacturers have adopted simple vibration measurements on the finished product to detect such defects but these tend to be limited by the type and size of bearing. An example of this type of measurement is shown in Figures 5(a) and 5(b) where, compared to a good bearing, the discrete damage on a bearing outer ring raceway has produced a characteristically impulsive vibration which has a high peak/RMS ratio. Where a large number of defects occurs individual peaks are not so clearly defined but the RMS vibration level is several times greater than that normally associated with a bearing in good conditio圖5（a）圖5（b）Bearing characteristic frequenciesAlthough the fundamental frequencies generated by rolling bearings are expressed by relatively simple formulas they cover a wide frequency range and can interact to give very complex signals. This is often further complicated by the presence on the equipment of other sources of mechanical, structural or electro-mechanical .REFERENCES1.Harris T A, Rolling Bearing Analysis (4th Ed), Wiley, New York, 2001.2.Lacey S J, Vibration monitoring of the internal centreless grinding process, Part 1: mathematical models. Proc Instn Mech Engrs. Vol 24. 1990.3.Lacey S J, Vibration monitoring of the internal centreless grinding process, Part 2: experimental results. Proc Instn Mech Engrs. Vol 24. 1990.4.Wardle F P and Lacey S J, Vibration Research in RHP. Acoustics Bulletin.