外文翻譯--在精鏜中提供穩(wěn)定高頻振動的摩擦阻尼器

1、<p>　　附件I 英文文獻翻譯</p><p>　　在精鏜中提供穩(wěn)定高頻振動的摩擦阻尼器</p><p>　　Evita Edhi, Tetsutaro Hoshi</p><p><b>　　摘要</b></p><p>　　在精鏜過程中防止發(fā)生超過10000Hz的高頻振動而造成刀具壽命降低問題的摩擦阻尼

2、器已研制成功。新阻尼器結(jié)構(gòu)簡單，它由一個聯(lián)接在主振動結(jié)構(gòu)上的附加質(zhì)量與一小塊永久磁鐵構(gòu)成。其原理是簡單的，利用庫侖力和粘性摩擦將振動能量消散在阻尼器和主振動結(jié)構(gòu)的接口之間。阻尼器對高頻也有效，因此無需調(diào)諧，本文首先介紹了一種在精鏜中消除高頻顫振的摩擦阻尼器的典型設(shè)計，其有效性由切削試驗得以證明，并保證刀尖的正常壽命。對這種新型阻尼器基本原理的理解在理論和實驗分析中得以介紹。在鏜削過程中這種新型阻尼器能夠有效的防止超過5000赫茲的顫振。

3、</p><p>　　關(guān)鍵詞 高頻振動 摩擦阻尼器 精鏜</p><p><b>　　1、引言</b></p><p>　　先前有研究報告稱精鏜中出現(xiàn)超過10000赫茲的高頻顫振。這種頻率首先發(fā)現(xiàn)于留在切削表面的振紋上，然后在切削實驗中直接使用激光位移計測量得到進一步的證實。從鏜刀的自然彎曲振動以及自我激發(fā)的切削過程中的動力學再生效果、內(nèi)

4、調(diào)制虛部的影響和x-y方向的循環(huán)發(fā)現(xiàn)了這種顫振。本研究的目標是防止這種顫振振動的發(fā)生。</p><p>　　預防切削顫振的有效措施可能是通過提高刀具系統(tǒng)的阻尼能力。阻尼能力是通過以下方面產(chǎn)生的：（1）包含在刀具系統(tǒng)接口處的某些微量滑動；（2）在晶界滑移內(nèi)部振動引起的阻尼損耗（內(nèi)耗）；（3）在主振動結(jié)構(gòu)和振動阻尼器接口處的摩擦。許多研究人員對不同類型的用以防止顫振振動，并提高鏜刀或其他切削操作穩(wěn)定性的阻尼器進行了研

5、究。</p><p>　　該阻尼器已不是傳統(tǒng)阻尼器的動態(tài)特性或沖擊特性了，動態(tài)阻尼器包括額外的彈簧質(zhì)量子系統(tǒng)，通過調(diào)節(jié)系統(tǒng)的固有頻率，使之與主體結(jié)構(gòu)相匹配。一般動態(tài)阻尼器設(shè)計包括任意方向的滑動或內(nèi)部摩擦耗能的彈性材料。彈性阻尼器由一個或多個的自由移動機構(gòu)組成，其原理是利用自由移動體撞擊主體結(jié)構(gòu)來耗散顫振能量。阻尼器受一定的速度影響才能有效的發(fā)揮其功能，因此不能適用于抑制低頻振動。近來有報道一種動力與摩擦混合阻尼器

6、，并發(fā)現(xiàn)它能有效地抑制低頻振動。</p><p>　　本文中所設(shè)計的阻尼器必須能有效地抑制高達10000赫茲的高頻率顫振，而且它的設(shè)計受到鏜刀本身的工作空間及其自身大小的限制。它最完美的地方就是不需要調(diào)整。該阻尼器在本研究提出一個大規(guī)模隸屬永磁結(jié)構(gòu)的概念。</p><p>　　本研究的目的是為了分析抑制高頻振顫阻尼器的有效性及其阻尼特性。</p><p>　　為了實

7、現(xiàn)這一目標，已進行一個類似于抑制精鏜中高頻顫振的切削試驗以及理論和實驗的能源阻尼耗能分析。</p><p>　　2、鏜刀測試和阻尼器結(jié)構(gòu)的構(gòu)想</p><p>　　根據(jù)研究，在精鏜中原本有一個高頻顫振問題，鏜刀本身包括一個直徑分別為13毫米和20毫米的長懸臂桿和法蘭。在桿的一端有一直徑為5.5毫米的小孔，以適應(yīng)5毫米或孔徑更小的阻尼器。該孔的位置選擇在徑向方向，因為我們已經(jīng)知道高頻振動在X

8、-Y方向循環(huán)。當鏜刀空轉(zhuǎn)時，阻尼器被孔壁的離心力推動但可以再徑向方向自由移動。上限用以保護運行中的阻尼器。</p><p>　　該阻尼器的有效性已經(jīng)通過了檢測并準備和其他鏜刀做比較。</p><p>　　用作比較的工具之一具有相同直徑的長懸臂桿即直徑為13毫米，但其延伸超出了前沿10毫米并產(chǎn)生約5000赫茲的顫振振動。其他與之比較是16毫米直徑懸臂式鏜刀，將以更大的長徑比產(chǎn)生較低頻率的顫振

9、振動。</p><p>　　新型摩擦阻尼器的基本結(jié)構(gòu)是一個附加質(zhì)量和永久磁鐵的組合，其中質(zhì)量平面平行于主結(jié)構(gòu)的振動方向。磁鐵可以是不可分割的或者是可分割的都行。另一部件，墊片，可以插入到永久磁鐵和主要結(jié)構(gòu)之間，其目的是控制電磁力的大小。新型摩擦阻尼器在抑制高頻振動的有效性已得到積極評價。</p><p><b>　　實驗方法</b></p><p&

10、gt;　　為了驗證該阻尼器控制顫振的有效性，并保證正常的刀具磨損和表面粗糙度，切削試驗將與其設(shè)計尺寸一樣，與13毫米直徑的鉆孔工具配合使用。這樣的話，鏜刀安裝在一個臥式加工中心的主軸上，通過設(shè)置調(diào)整孔直徑以自動控制刀尖徑向位置。</p><p>　　將內(nèi)表面是由旋轉(zhuǎn)刀具鏜加工的環(huán)型工件準備好。工件的材料是SCM420H合金鋼，淬火至硬度為313～332HBS，外徑為25mm，內(nèi)徑為14.72±0.05m

11、m，長度為15mm。工件由專門設(shè)計的具有足夠硬度的夾具裝夾。</p><p>　　切削試驗是在標準條件下進行的，切削速度為130m/min，進給量為0.03mm/rev,背吃刀量為0.14mm，切削過程中不使用任何切削液。一種新的尖端技術(shù)在加工過程中不斷調(diào)整加工條件。每個試驗重復兩次，其中一次在鏜刀系統(tǒng)中安裝阻尼器，而另一次不安裝。刀具材料用的是非涂層TiC金屬陶瓷，其軸向前角為-50，徑向前角為-150，刀尖圓

12、弧半徑為0.4mm。</p><p>　　對于直徑為16毫米的工件振動的測量，準備用另一個安裝程序?qū)h(huán)行工件的外表面固定。這樣的話，工件被夾緊使測試在一對立式加工中心機床基板上舉行。環(huán)行工件和機床主軸一同旋轉(zhuǎn)。</p><p>　　4.摩擦阻尼器的機理分析</p><p><b>　　4.1 理論分析</b></p><p

13、>　　振動的產(chǎn)生，一旦達到一定的振動幅度，阻尼器將開始滑動，由此引起阻尼器的主體結(jié)構(gòu)和界面的摩擦，從而耗散振動能量，并防止振幅不斷增大甚至超出極值振幅。</p><p><b>　　實驗分析</b></p><p>　　為了確定該假設(shè)庫侖力和粘性摩擦的區(qū)別，一個主體結(jié)構(gòu)模型振動的兩個理論模型的有效性監(jiān)測了二者的不同狀況，并激發(fā)了電動式激振器外部。用作主體結(jié)構(gòu)的是

14、一直徑為16毫米的懸臂鋼梁，它和原長為170mm的鏜刀具有相似的設(shè)計，其二階彎曲頻約能達到5700Hz。在檢測梁的端部振動時將使用微型加速度測量計。阻尼器主體結(jié)構(gòu)的頂部有一磁鐵，并通過此處與油管口相接。</p><p>　　首先采用隨機激勵確定主體結(jié)構(gòu)的固有頻率。然后是應(yīng)用在正弦激勵變幅的動力輸入f至z微調(diào)周圍隨機激勵確定固有頻率。與此同時，用FFT分析儀分析振幅在主體結(jié)構(gòu)出的響應(yīng)差異。激發(fā)各周期能源供應(yīng)量的正弦

15、振動是從測量f時開始的，計算如下</p><p>　　當x是降低阻尼器或與供油接口相連接時，主體結(jié)構(gòu)的振幅也降低了。當使用阻尼器時，激勵由0.3N增至0.6N時，振幅x將不會增大。對于較低的頻率，雖然也能有一定大的抗振效應(yīng)，但效果并不明顯。</p><p><b>　　5、結(jié)論</b></p><p>　　為了控制頻率高達10000Hz的高頻顫

16、振，正如以前報道的精鏜過程一樣，利用一種新的阻尼器與主體結(jié)構(gòu)之間的摩擦效應(yīng)，削弱振動能量而達到減振目的。</p><p>　　新的阻尼器由一個聯(lián)接在主振動結(jié)構(gòu)上的附加質(zhì)量與一小塊永久磁鐵構(gòu)成。據(jù)目前的研究已證實了庫侖力和粘性摩擦在滑動界面的產(chǎn)生。由于庫倫摩擦力，發(fā)生在主體結(jié)構(gòu)處的滑移就能抵消一部分顫振能量，而且它們之間大致是呈線性關(guān)系的。如果在此條件下能夠充分的消耗顫振能量，則就可以抑制顫振了。</p>

17、;<p>　　在抑制高頻顫振時，該阻尼器顯得更為有效。由于受到阻尼器主體結(jié)構(gòu)自身條件的限制，在精鏜中該阻尼器能抑制的最高顫振頻率只能略高于5000Hz。</p><p>　　由于簡單的結(jié)構(gòu)設(shè)計，也無需經(jīng)常調(diào)整，使用擬阻尼器抑制連續(xù)切削高頻率顫振（如精鏜等）是一種可行性方法。</p><p><b>　　致謝</b></p><p>

18、;　　本研究得到了NT工程公司的大力支持。他們提供了大量的研究材料和工具，得到了Y. Komai先生和M. Nakagawa先生的大力支持和幫助。</p><p>　　附件II 英文文獻原文</p><p>　　Stabilization of high frequency chatter vibration in fine boring by friction damper</p

19、><p>　　Evita Edhi*, Tetsutaro Hoshi</p><p><b>　　Abstract</b></p><p>　　Friction damper has been found successful to prevent high frequency chatter occurring at more than 10,

20、000Hz, and causing problem of reduced tool life in fine boring operation. The new damper is characterized by simple structure that consists of an additional mass attached to the main vibrating structure with small piece

21、of permanent magnet. The principle is straightforward in which Coulomb and viscous frictions dissipate vibration energy at the interface between the damper and main vibrating str</p><p>　　Keywords: High freq

22、uency chatter; Friction damper; Fine boring.</p><p>　　Introduction</p><p>　　A previous study reported fine boring tools exhibiting chatter at high frequency, more than 10,000Hz . The frequency w

23、as first identified from the chatter mark left on the surface, then further confirmed in cutting test by direct measurement using the laser displacement meter. The chatter was found attributable to bending natural vibrat

24、ion of the boring tool, self-excited by cutting process dynamics that include the regenerative effect, the imaginary part effect of inner modulation, and X-Y Loop</p><p>　　Effective chatter prevention during

25、 cutting operations may be achieved by increasing the damping capacity of cutting tool system. Damping capacity is generated through (i) micro-slip at certain interfaces included in the tool system, (ii) slip at the grai

26、n boundary within a vibrating body by material damping (internal friction), (iii) friction at an interface between the main vibrating body and the damper structure . Studies on various kind of damper to prevent chatter v

27、ibration, and to improve </p><p>　　Practical types of damper have been conventionally either dynamic or impact damper . Dynamic damper consists of additional spring-mass sub-system, and needs tuning of natur

28、al frequency of the sub-system to match that of the main structure. The dynamic damper is usually designed to include energy dissipation by either sliding or internal friction of the spring material. Impact damper consis

29、ts of one or more of free moving bodies, and the principle mechanism is to dissipate energy by the impact of</p><p>　　In the present study, the damper is required to be effective at frequencies as high as 10

30、,000Hz, and it should be designed within size limitation of the boring tool to accommodate space for seating the tool insert, chip pocket and the damper itself. It is also preferable that the damper needs no tuning. The

31、damper proposed in the present study consists of a piece of mass attached to the main structure by permanent magnet.</p><p>　　The objective of the present study is to analyze the effectiveness and characteri

32、stics of the proposed damper in preventing chatter vibration that occurs at high frequency.</p><p>　　To achieve the objective, cutting tests have been conducted in boring operation analogues to the one havin

33、g high frequency chatter problem in the plant, as well as theoretical and experimental analyses of energy dissipation of the proposed damper.</p><p>　　Boring tools tested and the proposed damper structure<

34、;/p><p>　　The boring tool under study that originally had a problem of high frequency chatter consists of a 13mm diameter and 20mm long cantilevered steel bar integral with a base flange. A small diameter hole,

35、 5.5 mm, is prepared at the end of the bar to accommodate the damper mass of which diameter may be 5mm or less. The position of the hole is selected in radial orientation om1, because the high frequency vibration due to

36、X-Y looping has been known to occur dominantly in the orientation om2 as depicte</p><p>　　The effectiveness of the damper has been tested for the tool as shown in the figure, as well as other boring tools th

37、at have been prepared for comparison.</p><p>　　One of the comparison tools has the same diameter 13mm, but extended 10mm beyond the cutting edge, and generates chatter vibration at about 5,000Hz. Other compa

38、risons are 16mm diameter cantilever type boring tools, designed with greater length (L) to diameter (D) ratios that exhibit chatter at lower frequencies.</p><p>　　Basic structure of the new friction damper i

39、s the combination of a mass and permanent magnet, which anchors the mass to the main structure on a flat surface parallel to the direction of vibration. The magnet may be either integral or separated with the mass. A thi

40、rd member, a spacer, may be inserted between the permanent magnet and the main structure whose purpose is to control magnitude of magnetic force. Effectiveness of the friction dampers in suppressing high frequency chatte

41、r has been evalu</p><p>　　3. Method of experiment</p><p>　　To validate the effectiveness of the damper in view of controlling the chatter, and to assure normal tool wear and surface roughness ge

42、nerated, cutting tests have been performed with the 13mm diameter boring tool rotated as it is in production site. In this case,the boring tool is mounted on the main spindle of a horizontal machining center via a settin

43、g head whose function is to adjust the radial position of the tool tip for automatic control of the hole diameter in production.</p><p>　　Ring type workpieces have been prepared whose inner surface is to be

44、machined by the rotating boring tool. Rings are made of SCM420H alloy steel, hardened to 313 to 332 Brinnell hardness with 25mm outer diameter, 14.72±0.05mm inner diameter, and 15mm length. A milling chuck clamps th

45、e ring on a specially designed fixture with sufficient stiffness.</p><p>　　The standard condition for cutting test is set to 130m/min cutting speed, 0.03mm/rev feed rate, 0.14mm depth of cut, and using no cu

46、tting fluid. A new cutting edge is prepared for each set of cutting tests in which workpieces are continuously machined. The cutting test is repeated twice for each boring tool system with and without the damper. Tool in

47、sert material used for the boring tool is TiC Cermet non-coated, with axial rake angle -5°, radial rake angle -15°, and nose radius 0.4mm.</p><p>　　For measuring vibration of the 16mm diameter tool

48、, another setup was prepared with the tool held stationary, and used to machine outer surface of the rotating ring workpiece. In this setup, the tool is clamped by a milling chuck staged on a baseplate on the machine tab

49、le of vertical machining center. The ring workpiece is mounted and rotated by the machine spindle.</p><p>　　4. Analysis of friction damper mechanism</p><p>　　4.1 Theoretical analysis</p>

50、<p>　　During the development of chatter, once the vibration reaches certain threshold amplitude, the damper will start sliding, therefore introducing friction at the interface between the damper mass and the main st

51、ructure. The friction dissipates the vibration energy, and prevents the chatter from growing beyond the threshold amplitude.</p><p>　　4.2 Experimental analysis</p><p>　　In order to ascertain val

52、idity of the two theoretical models assuming Coulomb and viscous friction respectively, vibration of a main structure model has been monitored with and without the damper mass attached, and excited externally by an elect

53、ro-dynamic exciter. a cantilevered steel beam 16mm diameter, having similar cutting edge design with the original boring tool and 170mm length, has been used as the main structure whose second order bending mode was exci

54、ted around 5,700Hz frequency. The v</p><p>　　Random excitation is first applied to identify the natural frequency of the main structure. Then sinusoidal excitation is applied at variable amplitude f of the i

55、nput dynamic force F at frequency Z finely tuned around the natural frequency identified by random excitation. At the same time, amplitude x of response vibration X of the main structure, and the phase difference between

56、 input dynamic force and response vibration , are measured by the FFT Analyzer.</p><p>　　Amount of energy supplied Es per vibration cycle by the sinusoidal excitation is computed from the measured f,as follo

57、ws:</p><p>　　vibration amplitude x of the main structure is reduced when the damper is attached on either dried or oiled interface. When the damper is used, the amplitude x exhibits a stagnant step during th

58、e excitation force increment from 0.3 to 0.6N.</p><p>　　5. Conclusion</p><p>　　To control chatter vibration occuring at frequencies as high as 10,000Hz, as previously reported in fine boring ope

59、ration, performance of a new damper mechanism utilizing friction between a damper mass and the main vibrating structure has been evaluated by cutting and excitation experiments.</p><p>　　The new damper consi

60、sts of a piece of mass attached to the main structure by permanent magnet. It has been confirmed by the present study that both Coulomb and viscous frictions are occurring at the sliding interface. Due to the Coulomb fri

61、ction, there occurs threshold amplitude where the mass starts sliding with respect to the main structure and dissipates a certain amount of vibration energy, which is approximately in linear proportion to the vibration a

62、mplitude. When the energy dissipation at</p><p>　　The damper has been found to be more effective for tools that generate chatter vibration at higher frequencies. From the physical size limit of the damper ma

63、ss for attachment to the main structure, friction damper is practical for tools which vibrate at frequencies higher than 5,000Hz.</p><p>　　Due to simple structural design and no need of tuning, the proposed

64、damper is a viable solution for the high frequency chatter vibration of continuous cutting operations such as fine boring.</p><p>　　Acknowledgements</p><p>　　This research was supported by NT-En