機(jī)械類外文文獻(xiàn)翻譯

1、文獻(xiàn)翻譯英文原文：NOVEL METHOD OF REALIZING THE OPTIMAL TRANSMISSION OF THE CRANK-AND-ROCKER MECHANISM DESIGNAbstract： A novel method of realizing the optimal transmission of the crank-and-rocker mechanism is presented. The optimal combination design is made by finding the related optimal transmission parame

2、ters. The diagram of the optimal transmission is drawn. In the diagram, the relation among minimum transmission angle, the coefficient of travel speed variation, the oscillating angle of the rocker and the length of the bars is shown, concisely, conveniently and directly. The method possesses the ma

3、in characteristic. That it is to achieve the optimal transmission parameters under the transmission angle by directly choosing in the diagram, according to the given requirements. The characteristics of the mechanical transmission can be improved to gain the optimal transmission effect by the method

4、. Especially, the method is simple and convenient in practical use.Keywords : Crank-and-rocker mechanism, Optimal transmission angle, Coefficient of travel speed variation INTRODUCTIONBy conventional method of the crank-and-rocker design, it is very difficult torealize the optimal combination betwee

5、n the various parameters for optimal transmission. The figure-table design method introduced in this paper can help achieve this goal. With given conditions, we can, by only consulting the designing figures and tables, get the relations between every parameter and another of the designed crank-and-r

6、ocker mechanism. Thus the optimal transmission can be realized.The concerned designing theory and method, as well as the real cases of its application will be introduced later respectively.ESTABLISHMENT OF DIAGRAM FOR OPTIMAL TRANSMISSION DESIGNIt is always one of the most important indexes that des

7、igners pursue to improve the efficiency and property of the transmission. The crank-and-rocker mechanism is widely used in the mechanical transmission. How to improve work ability and reduce unnecessary power losses is directly related to the coefficient of travel speed variation, the oscillating an

8、gle of the rocker and the ratio of the crank and rocker. The reasonable combination of these parameters takes an important effect on the efficiency and property of the mechanism, which mainly indicates in the evaluation of the minimum transmission angle.The aim realizing the optimal transmission of

9、the mechanism is how to find the maximum of the minimum transmission angle. The design parameters are reasonably combined by the method of lessening constraints gradually and optimizing separately. Consequently, the complete constraint field realizing the optimal transmission is established.The foll

10、owing steps are taken in the usual design method. Firstly, the initial values of the length of rocker 13 and the oscillating angle of rocker 中 are given. Then the value of the coefficient of travel speed variation K is chosen in the permitted range. Meanwhile, the coordinate of the fixed hinge of cr

11、ankA possibly realized is calculated corresponding to value K.Length of bars of crank and rocker mechanismAs shown in Fig.1, left arc C2G is the permitted field of point A. The coordinates of point A are chosen by small step from point C2 to point G .The coordinates of point A are以=乂 2- ho(1)叫=M2 y2

12、Awhere h, the step, is increased by small increment within range(0, H). If the smaller the chosen step is, the higher the computational precision will be. Ris the radius of the design circle. d is the distance from c2 to G. d = d = l cos +2 R cos( -0) -1(3)Calculating the length of arc AC1 and AC2,

13、the length of the bars of the mechanism corresponding to point a is obtainedmMinimum transmission angle YminMinimum transmission angle Y i (see Fig.2) is determined by the equations(4) TOC o 1-5 h z + 12 - (l - l )2 cos y = q341(4)min2l 213+ 12 - (l + l )2cos Y = 341max2l lY = 180O-Yminmaxwhere Leng

14、th of crank(mm)12Length of connecting bar(mm) Length of rocker(mm) Length of machine frame(mm)Position of nununum anglePosition of nununum angleFirstly, we choose minimum comparing Y . with y. . And then we record all values of Y . greater than or equal to 40 and choose the maximum of them.Secondly,

15、 we find the maximum of Y . corresponding to any oscillating angle 甲 which is chosen by small step in the permitted range (maximum of Y . is different oscillating angle 甲 and the coefficient of travel speed variation K).Finally, we change the length of rocker 13 by small step similarly. Thus we may

16、obtain the maximum of Y . corresponding to the different length of bars, different oscillating angle 甲 and the coefficient of travel speed variation K.Fig.3 is accomplished from Table for the purpose of diagram design.I _ _二-0, 5 0.6 4 7 0. B 0-9 L0 LILeng仆 ratio 7/(/2Figure of the optirnni designTa

17、tik Par! of fnmputntlonHt vtihie 3117(擋(T)舛7 A/mmL/wmLi /mm2055.994 13&.65O2弭9曲0100.0099554 23054J71 ?24.991 7Li57100.0。109,166 04051.4H 233 IE102523 5irwcofSITOflJ5048354 &41.10S7U 9.772 7100,00【3gt5 16044.860 448759 7136.022 A100,00141,744 370q 1.072 41 00X0151398 9瓦=L1眥=成）就）%/nunli Enun2049.607 2

18、1W744。47 $1 DO血94.742 443,615 H24J90 870.6 7 7lOO.Ofl99J58 84046.539.131449 5眺 01B 7t GOODJ Q7.797 35044.092 44t).377 6IQ3E 6100.0011655 46041.071 447,981 6(1187J 3100.00136,222 $7&nim A點(diǎn)AFig.L Posiucn of nim A點(diǎn)A的座標(biāo)是(1)當(dāng)h0,高度，在range(0 , h )被逐漸增加。如果選的越小，計(jì)算精度將越高。R是設(shè)計(jì)圓的半徑。d是從。?到G的距離。平 d = l平 d = l COSy

19、 +2 R cos( ? -0) -1cos墮2(3)計(jì)算弧AC1和AC2的長(zhǎng)度，機(jī)械桿對(duì)應(yīng)于點(diǎn)A的長(zhǎng)度是obtained1,2 。1.2極小的傳動(dòng)角度Ymin極小的傳動(dòng)角度Y(參見Fig.2)由equations3確定min12 +12 -(l -1)2 TOC o 1-5 h z COS Y = 341(4)min 2l ll2 +12 (l +1 )2cos y = -2341(5)max2l ly. = 180。-y(6)由于11 曲柄的長(zhǎng)度（毫米）12 連桿的長(zhǎng)度（毫米）13搖臂的長(zhǎng)度（毫米）機(jī)器的長(zhǎng)度（毫米）Position of minimuni已 of tMnsciissiDB

20、首先，我們比較極小值Ymin和Y屈。并且我們記錄所有Ymin的值大于或等于40。，然后選擇他們之間的最大值。第二，我們發(fā)現(xiàn)最大值Y 對(duì)應(yīng)于一個(gè)逐漸變小的范圍的任一個(gè)擺動(dòng)的角度 min甲（最大值Y min是不同于擺動(dòng)的角度和滑移速度變化系數(shù)K）。最后，我們相似地慢慢縮小搖臂匕的長(zhǎng)度。因而我們能獲得最大值Ymin對(duì)應(yīng)于桿的不同長(zhǎng)度，另外擺動(dòng)的角度甲和滑移速度變化系數(shù)K。Fig.3成功的表達(dá)設(shè)計(jì)的目的。它確定了無論是搖臂的長(zhǎng)度13，最大值Ymin出現(xiàn)的地點(diǎn)，只與搖臂的長(zhǎng)度和機(jī)械的長(zhǎng)度的比率13/14有關(guān)，當(dāng)確定七時(shí)。40Fig.3 Figure of the optima I designTable

21、Parr oT fAmputntloniit value此yC)P=1(T )h Jinni/mm帝也E“EE2055.944 1It?蹌死8 0100.0099554 23054471924991 7ULI 57 3100.00L 09.166 04051.411 233 1355102.723 5irwoo Iflfll5048.3fi4 841.10&7119772 71 iJO.QO頃.926 16044.RM)443,739 7136.022 4100,00144744 370*11.072 456119 4t47.t28 3】0。,。153 3照 9KF.網(wǎng))M )A/mm/iJt

22、nn.Him2049.607 216.4174血的8100.0094.742 43。48.615 82J390 870.674 7100.0099J58 B4046.539 J-32.449 5R9. 01E 7I GO ODl旺為”5044.092 44WJ77 603.799 6100.00116.955 46041.071447.981 6(17.8713100.00126.222 fi7。402設(shè)計(jì)方法2.1認(rèn)識(shí)最優(yōu)傳動(dòng)設(shè)計(jì)下滑移速度變化系數(shù)和搖臂的最大擺動(dòng)的角度設(shè)計(jì)步驟如下。 根據(jù)所給的K和中，通常采取對(duì)發(fā)現(xiàn)極限角度9的解釋。桿的長(zhǎng)度的 對(duì)應(yīng)的比率IJI4是從圖Fig.3獲得的。 TOC o 1-5 h z 9 = K1 x180。(7)K +1根據(jù)工作要求選擇搖臂的長(zhǎng)度l，機(jī)械的長(zhǎng)度是從比率l /1獲得的。334任意地選擇固定的鉸接的中心D作為端點(diǎn)，并且做一個(gè)等腰三角形，令一條邊與搖臂的長(zhǎng)度l相等(參見Fig.4)，令A(yù)C DC =p。然后做CM 1 CC， 31221 2連接C1N，并且做角度/C* = 90。-9。因而增加了交點(diǎn)C2M和C1N。最 后，畫三角形冏、。Fig,.4以點(diǎn)D作為圓的中心，l