基于PROE平臺的立式雙軸缸孔半精鏜機床總體及刀具設計【說明書+CAD+PROE】
基于PROE平臺的立式雙軸缸孔半精鏜機床總體及刀具設計【說明書+CAD+PROE】,說明書+CAD+PROE,基于PROE平臺的立式雙軸缸孔半精鏜機床總體及刀具設計【說明書+CAD+PROE】,基于,proe,平臺,立式,雙軸缸孔半精鏜,機床,總體,整體,刀具,設計,說明書,仿單,cad
外文翻譯
專 業(yè) 機械設計制造及自動化
學 生 姓 名 康 生
班 級 BD機制042
學 號 0420110225
指 導 教 師 黃曉峰
外文資料名稱：Design and manufacture of composite high speed machinetool structures
外文資料出處：Composites Science and
technology
附 件： 1.外文資料翻譯譯文
2.外文原文
指導教師評語：
簽名：
年 月 日
復合高速機刀具結構的設計與制造
Dai Gi lLee,Jung Do Suh, Hak Sung Kim, Jong Min Kim
摘要
高傳輸速度，以及高切削速度機床重要的是生產力的提高，在制作模具/模具，因為非加工時間，被稱為空中交織的時間，數量，以70 ％的總加工時間與形狀復雜的產品。其中一個最主要的原因是生產率低，是大型群眾性的運動部件的機床，其中不能負擔快的加速和減速過程中遇到的操作。此外，振動機床結構是其他原因限制，高速運作。 在這個文件中，幻燈片的高速數控銑床的設計與纖維增強復合材料克服這種局限性?？v向和橫向的幻燈片大型數控機床制造加入高含量碳纖維環(huán)氧復合材料，以鋼筋焊接結構用粘合劑和螺栓。這些復合材料結構減少重量縱向和橫向的幻燈片，由34 ％和26 ％ ，分別增加了阻尼。不致有太大調整，這臺機器上進行了定位精度5光鏡每300毫米的減少。
1.導言
數控銑床和加工中心應用于制作各種模具/模具即用于家電，汽車內飾， 沖壓和注塑成型。在正常加工與機床，其切削工具提出與名義利用率，而價格切換至快速導線模式轉移期間切削工具，如果沒有接觸工件：時間用于傳輸一個刀具無接觸工件的，是所謂的空切時間。一般來說，只有大約30 ％的總加工時間是花費在實際切削，而其余的70 ％ 是花在空中交織的兼職[1,2]。因此，不只是具有高的切削速度，而且具有較高的傳輸速度，是必須取得資源增值的加工這是必不可少的條件，在全球競爭機床市場，雖然切割速度已增加是由于新研制的切削刀具材料，如陶瓷，立方氮化硼，金剛石等，生產力仍受制于低轉移高速大規(guī)模移動幀，其中通常是鋼。傳統(tǒng)的鋼標架的機工具與最高速度為0.2?0.8米/秒， 最大加速度0.2-2.1m/s2（常規(guī)加工中心，mynx400/ace-tc320d，大宇重工機械有限公司，韓國）。然而， 現代高速銑床須有最大加速度14 m/s2和速度。 2米/秒。這些高傳輸速度，是難以實現如果龐大的鋼鐵架利用。 此外，機床結構振動形成問題，在制造過程中，在這些高的速度，而可能導致質量低劣產品的相對位置誤差在刀具和工件[3-5]之間：最近機床都要求有一直被定位精度在10lm的，其中是密切相關的精密產品。為保證高速運行的準確性，機床結構設計應與輕動框在不消耗剛度和阻尼性能， 這是相互矛盾的要求，如果常規(guī)金屬材料是受雇于常規(guī)金屬幾乎相同的低比剛度（五= q ）的同低阻尼特性。機床結構高剛度和高阻尼要求，以增加他們的基本自然頻率并減少振動引起的。要求要比高剛度高阻尼的機床結構能滿足用人纖維增強聚合物復合材料。增強纖維復合材料構成的加固纖維具有很高的具體剛度和矩陣高阻尼，由此產生的材料復合特性反映最佳的特點，即高比剛度、高阻尼。此外，夾層結構，其面結構制成的纖維增強復合材料、其核心材料制成的蜂窩狀或發(fā)泡結構，最大限度地發(fā)揮優(yōu)勢的時候，他們適用于結構抵抗彎矩。 因此，夾層結構和復合材料我們已使用的越來越多，在宇宙飛船飛機，汽車零部件，機器人手臂 ，甚至機床 。 變形的機床結構下切削力和結構慣性負載啟動過程并停止生產，不僅產品質量差，而且有很強噪音和振動。然而，這增加了一般的機床結構，因此需要大量電動機，軸承和運動指導體系。因此， 最好的方法，以提高剛度的機床結構，沒有多大增加部件是使用高比剛度的結構，如復合材料夾層結構。 在這項研究中，縱向和橫向機床幻燈片的高速數控銑床的設計及制造所用復合材料夾層結構是膠接，以焊接鋼管結構-一種混合機床結構。垂直柱的橫向滑動（十-幻燈片）及制造與復合材料夾層結構，而橫欄的垂直滑動（ Y型幻燈片） 鋼筋與高模量復合板。該混合結構設計成具有等效結構剛度的常規(guī)鋼結構這是按經典梁理論分析。此時，自然頻率和阻尼能力以及減輕重量的復合材料混聯機床結構測定和相對于常規(guī)鋼機床結構。
2.設計混聯機床結構
2.1特色的混合型梁
抗彎剛度簡支夾心束所示圖。
(1)
如s模面和核心。偏轉長簡支持夾層梁下的集中載荷P基于簡單梁理論是指用D1的原因彎曲變形和D2由于剪切變形[15,16]
凡與GC代表等效截面面積和剪切模芯材料，分別由于夾層結構具有較低的核心剪切剛度，
簡單梁理論，忽略剪切變形可能不會作出準確的結果。因此，在計算結果剛度的夾層梁標本相比與實測結果所得到的三點彎曲試驗表明，在圖 1以及作為結果由有限元分析。三點彎曲試驗是用英斯特朗4206年不足1毫米/分鐘位移速率和有限元分析是演出與商業(yè)軟件ANSYS5.5（美國）使用殼牌99和固體95元素。表1顯示尺寸夾心標本。夾心束標本制成的復合材料的表面和內部核心。加入表面和核心，即是一種粘合劑形狀（ af126 ， 3 M公司，美國）和環(huán)氧粘合劑圖1。尺寸的簡支夾層梁用三點彎曲試驗： （一）縱向方向; （二）
橫截面A-A1。
。
表1
尺寸（ mm ）的簡支夾層梁下threepoint 彎曲試驗
（2216，3M公司，美國） ，是用來防止脫層失敗的夾層結構[17,18]。單向碳纖維環(huán)氧復合（ usn150 ，韓國化學，韓國） 與玻璃纖維布復合（ gep215 ，韓國化學， 韓國）被用于表面材料，而芳綸纖維蜂窩（ hrh-10-1/8-4.0 ， hexcel ，英國） 用于核心材料。表2和表3列出性能這些材料。綜合面孔為夾心基礎打下了一個堆疊序列[ 0 2 100 / 0 10歲;的C / 0 1 100 / 0 5年;中] s凡標G和C代表了玻璃纖維和碳-環(huán)氧分別。 圖2顯示實測撓度以及由于計算的，由梁理論和有限元分析。梁理論和有限元分析預言實驗偏轉8 ％以內的誤差。 從以上結果，我們發(fā)現在這該夾層梁撓度因剪是不容忽視（在這種情況下3倍以上，由于彎曲）。 因此，箱式混合梁方面鋼筋與鋼板所示圖。 3 采用混合標架，以減少剪切變形的夾層梁。對于梁的鋼筋與鋼板忽視翹曲，剪應力和，它的幾何兼容性詳情如下：
其中R的比例應是剪切模量之間的鋼和蜂窩項。然后，剪應力蜂窩圖。
2.2設計的重量輕的復合鋼筋機工具框
圖4顯示照片的高速數控機床銑床的15千瓦配備35000rpm時，
圖4 照片上的高速銑床結構（ f500 ，大宇重工機械有限公司，韓國）。
主軸及混合標架，水平坐標（十-坐標）及垂直坐標（ Y型坐標） ，其垂直柱和橫向柱鋼筋與復合材料夾層結構和復合材料板（ f500 ，大宇重工＆ 機械有限公司，韓國） 。無論是移動所得到了2.0米/秒的速度，還是達到最大加速度14.0 m/s2 ，都無結果。 5和6顯示照片的X坐標和Y型坐標組成的復合材料夾層結構膠接，以焊接鋼管結構。為了估計該機床結構撓度，在高加速度， 移動鋼框架結構進行了分析，得到了有限元分析顯示圖。 如垂直的X坐標抵消了所吸收的20千牛力量產生的，由兩個直線電機裝內表面的垂直方向的X -坐標。 橫欄的Y型滑坡發(fā)生變形，在Z向由彎矩由于要伸出主軸重量4000 N，以最大限度地加固效果，在這項工作中，立柱的X -坐標和橫向欄的Y坐標被選作主要加強部分。 為了發(fā)展一個打火機，混合幀的X幻燈片鋼鐵基地，制成更薄的鋼板的16毫米厚度相比， 20毫米厚的鋼板。
常規(guī)之一，是增強復合材料夾層結構顯示圖。自剪變形的一個簡單的三角形結構通常大，在這項研究中，混合結構的目的是作為盒型結構參考。 后來，其雙方均加強了鋼鐵板塊。 為設計的箱式混合結構大于10.4 ，這意味著偏轉由于剪切小于8.8 ％的總偏轉。因此，在設計中的結構，抗彎剛度D的使用為目標參數，如
由于加固外，以增加抗彎剛度d時，內面厚度的夾心決定考慮加入5毫米的內在面臨的夾層梁，以鋼鐵為主，以螺栓為主。 厚度外，面對的夾層梁被初步確定給予最主要的一個，然后再較具體的計算其中，以確定合適的尺寸并利用有限元法考慮當地翹曲或扭曲。從分析中，它是發(fā)現較大偏轉發(fā)生在混合動力梁時，都梁有相同的抗彎剛度d ，因為交夾不具備橫向加固鋼板，而常規(guī)鋼梁被設計成一個格子型結構與加強板，圖 9 。因此，外面厚度的夾層梁增加至13毫米。 此外，尺寸的其他援軍計算通過程序入手等效抗彎剛度D和計算，然后與有限元法考慮翹曲的結構。
2.3 制造混聯機床結構高強度碳纖維環(huán)氧復合（ usn150 ，韓國化學，韓國）和玻璃纖維環(huán)氧（ gep215 ，韓國化學，韓國） ，主要用于面孔夾層梁和加固板為X和Y型幻燈片。垂直欄的X抗滑被鋼筋與兩個夾層梁的1462毫米和1223毫米長，而在頂部和底部部分鋼筋分別與四個復合板六小夾層梁所示圖 5 。該Y型幻燈片，即主軸單元的銑削應該抵制彎矩產生主軸的重量，切削力和慣性力由于快速加速和減速而下落了。 橫欄的Y型幻燈片與嚴格的三維制約因素是鋼筋，具有很高的彈性模量碳纖維環(huán)氧復合材料的性能，給出表2 （ hyej34m45d ，三菱，日本） ，以避免干擾其他部分。此外，左右垂直柱的Y型幻燈片被鋼筋與三角梁所示圖6。此外，四個三角形板被用于加強扭剛度的矩形框。綜合增援保稅區(qū)向鋼鐵基地結構與環(huán)氧粘合劑（2216 ，3M公司，美國）精神結合起來，同機械結合，與螺栓，以提高可靠性和生產效率。
Design and manufacture of composite high speed machinetool structures
Dai Gil Lee *, Jung Do Suh, Hak Sung Kim, Jong Min Kim
Abstract
The high transfer speed as well as the high cutting speed of machine tools is important for the productivity improvement in thefabrication of molds/dies because non-machining time, called the air-cutting-time, amounts to 70% of total machining time withcomplex shape products. One of the primary reasons for low productivity is large mass of the moving parts of machine tools, whichcannot afford high acceleration and deceleration encountered during operation. Moreover, the vibrations of the machine toolstructure are among the other causes that restrict high speed operations.In this paper, the slides of high speed CNC milling machines were designed with fiber reinforced composite materials toovercome this limitation. The vertical and horizontal slides of a large CNC machine were manufactured by joining high-moduluscarbon-fiber epoxy composite sandwiches to welded steel structures using adhesives and bolts. These composite structures reducedthe weight of the vertical and horizontal slides by 34% and 26%, respectively, and increased damping by 1.5–5.7 times withoutsacrificing the stiffness. Without much tuning, this machine had a positional accuracy of 5 lm per 300 mm of the slidedisplacement.
1. Introduction
CNC milling machines and machining centers areemployed in the fabrication of various molds/dies thatare used for electrical appliances, automobile interiors,
stamping and injection molding. During normal machiningwith machine tools, their cutting tools aremoved with nominal feed rates, while the feed rates are
switched to a rapid traverse mode during the transfer ofcutting tools without contacting workpieces: The timespent to transfer a cutting tool without contactingworkpieces is called air-cutting-time. Generally, onlyabout 30% of the total machining time is spent in theactual cutting or making chips, while the remaining 70%is spent in the air-cutting-time [1,2]. Therefore, not onlyhigh cutting speeds but also high transfer speeds arerequired to obtain the enhanced productivity of machiningwhich is essential to survive in the global competitionof machine tool markets. Although the cuttingspeed has been increased due to newly developed cuttingtool materials such as ceramic, CBN, diamond and soon, productivity is still restricted by the low transferspeed of massive moving frames which are usually madeof steel. Conventional steel moving frames of machinetools operate with maximum speeds of 0.2–0.8 m/s, andmaximum acceleration of 0.2–2.1 m/s2 (ConventionalMachining Center, Mynx400/ACE-TC320D, DaewooHeavy Industries & Machinery Ltd., Korea). However,modern high speed milling machines are required tohave the maximum acceleration of 14 m/s2 and the speedof 2 m/s. These high transfer speeds are hard to be realizedif massive steel moving frames are employed.Furthermore, machine tool structures vibrate creatingproblems during manufacturing at these high speeds,which may result in poor quality products by the relativepositional error between the cutting tools and workpieces[3–5]: Recently machine tools are required to havebeen kept the positional accuracy within 10 lm, whichis closely related to the precision of products [6]. For thehigh speed operation with accuracy, machine toolstructures should be designed with light moving frameswithout sacrificing stiffness and damping properties,which are contradictory requirements if conventionalmetallic materials are employed because conventionalmetals have almost same low specific stiffness (E=q) withlow damping characteristics. Machine tool structureswith high specific stiffness and high damping are requiredto increase their fundamental natural frequenciesand decrease the vibration induced. The requirement ofhigh specific stiffness with high damping for high speedmachine tool structures can be satisfied by employingfiber reinforced polymer composite materials [7,8]. Sincethe fiber reinforced composite materials consist of reinforcingfibers with very high specific stiffness and matrixwith high damping, the resulting material characteristicsof composite materials reflect the best characteristics ofeach material, i.e., high specific stiffness with highdamping. Moreover, sandwich structures whose facestructures are made of fiberreinforced composite materialsand whose core materials are made of honeycombor foam structures maximize their advantages when theyare applied to the structures resisting bending moment.Consequently, sandwich structures and composite materialshave been employed increasingly in spacecrafts,airplanes, automobile parts [9], robot arms [8,10], andeven machine tools [11,12].The deformation of machine tool structures undercutting forces and structural inertia loads during startand stop motions produces not only poor qualityproducts but also noise and vibration. A simple way toreduce the deformation is to employ structures withlarge cross-sections. However, it increases the mass ofmachine tool structures and consequently requires largemotors, bearings and motion guide systems. Therefore,the best way to enhance the stiffness of machine toolstructures without much increase of mass is to employhigh specific stiffness structures such as compositesandwich structures.In this study, the vertical and horizontal machine toolslides of a high speed CNC milling machine were designedand manufactured with sandwich compositestructures that are adhesively bonded to welded steelstructures – a hybrid machine tool structure. The verticalcolumn of the horizontal slide (X-slide) was manufacturedwith composite sandwich structures while thehorizontal column of the vertical slide (Y-slide) wasreinforced with high modulus composite plates. Thehybrid structures were designed to have the equivalentstructural stiffness of conventional steel structures,which was calculated by the classical beam theory andFEM analysis. Then, the natural frequency and dampingcapacity as well as weight savings of the compositehybrid machine tool structures were measured and
compared with those of comparable conventional steelmachine tool structures.
2. Design of hybrid machine tool structures
2.1. Characteristics of hybrid beam
The bending stiffness D of a simply supported sandwichbeam as shown in Fig. 1 is expressed as followswhen Ef >> Ec and d >> t [13–15]:
( 1)
where Ef and Ec represent the Youngs moduli of faceand core, respectively. The deflection D of the simplysupported sandwich beam under a concentrated load P
based on the simple beam theory is the sum of D1 due tobending deformation and D2 due to shear deformation[15,16]:
where A and Gc represent equivalent cross-section areaand the shear modulus of core material, respectively.Since the sandwich structure has low core shear stiffness,the simple beam theory neglecting shear deformationmay not give an accurate result. Therefore, the calculatedresults of stiffness of sandwich beam specimen werecompared with the measured results obtained by thethree-point bending test shown in Fig. 1 as well as theresults by FEM analysis. The three-point bending testwas performed using Instron 4206 under 1 mm/mindisplacement rate and the FEM analysis was performedwith a commercial software ANSYS 5.5 (USA) usingshell 99 and solid 95 elements. Table 1 shows the dimensionsof sandwich specimens. The sandwich beamspecimens were made of composite faces and honeycombcore. To join the faces and the core, both an adhesivefilm (AF126, 3M, USA) and an epoxy adhesive
Fig. 1. Dimensions of the simply supported sandwich beam used forthree-point bending test: (a) longitudinal direction; (b) cross-section ofA–A1.
Table 1
Dimensions (mm) of the simply supported sandwich beam under threepointbending test
(2216, 3M, USA) was used to prevent delaminationfailure of sandwich structures [17,18]. Unidirectionalcarbon-epoxy composite (USN150, SK Chemical, Korea)and glass fabric composite (GEP215, SK Chemical,Korea) were used for the face material while aramid fiberhoneycomb (HRH-10-1/8-4.0, Hexcel, UK) wasused for the core material. Tables 2 and 3 list theproperties of these materials. The composite faces forthe sandwich specimens were laid up with a stackingsequence of [02;G/010;C/01;G/05;C]S where the subscriptsG and C represent glass-fabric and carbon-epoxy, respectively.Fig. 2 shows the measured deflection as wellas the calculated ones by the beam theory and FEManalysis. Both the beam theory and the FEM analysispredicted the experimental deflection within 8% error.From the above results, it was found that the deflectionof the sandwich beam due to shear was not negligible(three times larger than that due to bending in this case).Therefore, box type hybrid beams with side surfacesreinforced with steel plates as shown in Fig. 3 wereadopted for the hybrid moving frames to reduce theshear deformation of the sandwich beam. For the boxtype beams reinforced with steel plates neglectingwarping, the shear stress sxz;h in the honeycomb and sxz;sin the side steel are related from the geometric compatibilityas follows:
where R is the ratio of the shear moduli between the steel(Gxz;s) and honeycomb (Gxz;h). Then, the shear stress inthe honeycomb in Fig.
2.2. Design of light weight composite reinforced machinetool frames
Fig. 4 shows the photograph of a high speed CNCmilling machine of 15 kW equipped with 35,000 rpm
Fig. 4. Photograph of a high speed milling machine tool structure(F500, Daewoo heavy industries & Machinery Ltd., Korea).
In order to develop a lighter hybrid frame, the X-slidesteel base, made of thinner steel plates of 16 mmthickness compared to 20 mm thick steel plates for
conventional one, was reinforced with composite sandwichstructure as shown in Figs. 5 and 8. Since the sheardeformation of a simple sandwich structure is usuallylarge, in this study, the hybrid structure was designed asa box type structure as shown in Figs. 8 and 9 whosesides were reinforced with steel plates. The calculatedvalues of RBS from Eq. (7) for the designed box typehybrid structure was larger than 10.4, which meant thatthe deflection due to shear was less than 8.8% of thetotal deflection. Therefore, during the design of thestructure, the flexural rigidity D was used as the objectiveparameter, where
Since the reinforcement of the outer face of the movingframes is most effective to increase the flexural rigidityD, the inner face thickness of the sandwich was determinedto be 5 mm considering the joining of the innerfaces of the sandwich beams to the steel base with bolts.
14
收藏