機械類外文文獻翻譯--認識曲柄搖臂機構(gòu)設計最優(yōu)傳動方法

1、<p><b>　　中文1697字</b></p><p>　　NOVEL METHOD OF REALIZING THE OPTIMAL TRANSMISSION</p><p>　　OF THE CRANK-AND-ROCKER MECHANISM DESIGN</p><p>　　Abstract: A novel method

2、 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 parameters. The diagram of the optimal transmissio

3、n 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 d

4、irectly. The method possesses the ma</p><p>　　Keywords：Crank-and-rocker mechanism, Optimal transmission angle, Coefficient of travel speed variation</p><p>　　INTRODUCTION</p><p>　　B

5、y conventional method of the crank-and-rocker design, it is very difficult to realize the optimal combination between the various parameters for optimal transmission. The figure-table design method introduced in this pap

6、er 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-rocker mechanism. Thus th

7、e optimal transmission can be realized.</p><p>　　The concerned designing theory and method, as well as the real cases of its application will be introduced later respectively.</p><p>　　ESTABLISH

8、MENT OF DIAGRAM FOR OPTIMAL TRANSMISSION DESIGN </p><p>　　It is always one of the most important indexes that designers pursue to improve the efficiency and property of the transmission. The crank-and-rocker

9、 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 angle of the roc

10、ker and the ratio of the crank and rocker. The reasonable combination of these parameters takes an important effect on the efficien</p><p>　　The aim realizing the optimal transmission of the mechanism is how

11、 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 fiel

12、d realizing the optimal transmission is established.</p><p>　　The following steps are taken in the usual design method. Firstly, the initial values of the length of rocker and the oscillating angle of rocke

13、r are given. Then the value of the coefficient of travel speed variation is chosen in the permitted range. Meanwhile, the coordinate of the fixed hinge of crank possibly realized is calculated corresponding to value .&

14、lt;/p><p>　　Length of bars of crank and rocker mechanism</p><p>　　As shown in Fig.1, left arc is the permitted field of point . The coordinates of point are chosen by small step from point to po

15、int .</p><p>　　The coordinates of point are</p><p><b>　　(1)</b></p><p><b>　　(2)</b></p><p>　　where , the step, is increased by small increment

16、within range(0,). If the smaller the chosen step is, the higher the computational precision will be. is the radius of the design circle. is the distance from to .</p><p><b>　　(3)</b></p>

17、<p>　　Calculating the length of arc and , the length of the bars of the mechanism corresponding to point is obtained[1,2].</p><p>　　1.2 Minimum transmission angle </p><p>　　Minimum tran

18、smission angle (see Fig.2) is determined by the equations[3]</p><p><b>　　(4)</b></p><p><b>　　(5)</b></p><p><b>　　(6)</b></p><p>　　wh

19、ere ——Length of crank(mm)</p><p>　　——Length of connecting bar(mm)</p><p>　　——Length of rocker(mm)</p><p>　　——Length of machine frame(mm)</p><p>　　Firstly, we choose mi

20、nimum comparing with . And then we record all values of greater than or equal to and choose the maximum of them.</p><p>　　Secondly, we find the maximum of corresponding to any oscillating angle which is

21、 chosen by small step in the permitted range (maximum of is different oscillating angle and the coefficient of travel speed variation ).</p><p>　　Finally, we change the length of rocker by small step simi

22、larly. Thus we may obtain the maximum of corresponding to the different length of bars, different oscillating angle and the coefficient of travel speed variation .</p><p>　　Fig.3 is accomplished from Table

23、 for the purpose of diagram design.</p><p>　　It is worth pointing out that whatever the length of rocker is evaluated, the location that the maximum of arises is only related to the ratio of the length of

24、rocker and the length of machine frame /, while independent of .</p><p>　　DESIGN METHOD</p><p>　　Realizing the optimal transmission design given the coefficient of travel speed variation and the

25、 maximum oscillating angle of the rocker</p><p>　　The design procedure is as follows.</p><p>　　(1) According to given and , taken account to the formula the extreme included angle is found. Th

26、e corresponding ratio of the length of bars / is obtained consulting Fig.3.</p><p><b>　　(7)</b></p><p>　　(2) Choose the length of rocker according to the work requirement, the lengt

27、h of the machine frame is obtained from the ratio /.</p><p>　　(3) Choose the centre of fixed hinge as the vertex arbitrarily, and plot an isosceles triangle, the side of which is equal to the length of rock

28、er (see Fig.4), and . Then plot , draw , and make angle . Thus the point of intersection of and is gained. Finally, draw the circumcircle of triangle .</p><p>　　(4) Plot an arc with point as the centre of

29、 the circle, as the radius. The arc intersections arc at point . Point is just the centre of the fixed hinge of the crank.</p><p>　　Therefore, from the length of the crank</p><p><b>　　(

30、8)</b></p><p>　　and the length of the connecting bar</p><p><b>　　(9)</b></p><p>　　we will obtain the crank and rocker mechanism consisted of , , , and .Thus the op

31、timal transmission property is realized under given conditions.</p><p>　　2.2 Realizing the optimal transmission design given the length of the rocker (or the length of the machine frame) and the coefficient

32、of travel speed variation</p><p>　　We take the following steps.</p><p>　　(1) The appropriate ratio of the bars / can be chosen according to given . Furthermore, we find the length of machine fra

33、me (the length of rocker ).</p><p>　　(2) The corresponding oscillating angle of the rocker can be obtained consulting Fig.3. And we calculate the extreme included angle .</p><p>　　Then repeat (3

34、) and (4) in section 2.1</p><p>　　DESIGN EXAMPLE</p><p>　　The known conditions are that the coefficient of travel speed variation and maximum oscillating angle . The crankandrocker mechanism re

35、alizing the optimal transmission is designed by the diagram solution method presented above.</p><p>　　First, with Eq.(7), we can calculate the extreme included angle . Then, we find consulting Fig.3 accordi

36、ng to the values of and .</p><p>　　If evaluate mm, then we will obtain mm.</p><p>　　Next, draw sketch(omitted).</p><p>　　As result, the length of bars is mm, mm, mm, mm.</p&g

37、t;<p>　　The minimum transmission angle is</p><p>　　The results obtained by computer are mm, mm, mm, mm.</p><p>　　Provided that the figure design is carried under the condition of the

38、Auto CAD circumstances, very precise design results can be achieved.</p><p>　　CONCLUSIONS </p><p>　　A novel approach of diagram solution can realize the optimal transmission of the crank-and-ro

39、cker mechanism. The method is simple and convenient in the practical use. In conventional design of mechanism, taking 0.1 mm as the value of effective the precision of the component sizes will be enough.</p><p

40、>　　REFERENCES</p><p>　　[1]Shigley J E,Uicher J J. Theory of Machines and Mechanisms[M].New York: McGraw-Hill Book Company,1980.</p><p>　　[2]天津大學. 機械原理[M].北京:人民教育出版社,1997.</p><p>

41、　　[3]孫桓. 機械原理[M].北京:高等教育出版社,1996.</p><p><b>　　譯文：</b></p><p>　　認識曲柄搖臂機構(gòu)設計最優(yōu)傳動方法</p><p>　　摘要：一種曲柄搖臂機構(gòu)設計的最優(yōu)傳動的方法被提出。這種優(yōu)化組合設計被用來找出最優(yōu)的傳遞參數(shù)。得出最優(yōu)傳遞圖。在圖中，在極小的傳動角度之間, 滑移速度變化系數(shù)，搖

42、臂的擺動角度和桿的長度被直觀地顯示。 這是這種方法擁有的主要特征。根據(jù)指定的要求，它將傳動角度之下的最優(yōu)傳動參數(shù)直接地表達在圖上。通過這種方法，機械傳動的特性能用以獲取最優(yōu)傳動效果。特別是， 這種方法是簡單和實用的。</p><p>　　關(guān)鍵字：曲柄搖臂機構(gòu) 最優(yōu)傳動角度 滑移速度變化系數(shù)</p><p><b>　　0 介紹</b></p>

43、<p>　　由曲柄搖臂機構(gòu)設計的常規(guī)方法, 在各種各樣的參量之間很難找出優(yōu)化組合的最優(yōu)傳動。通過本文介紹的圖面設計方法可以幫助達到這個目的。在指定的情況下，通過觀查設計圖面, 我們就能得到每個參量和另外一個曲柄搖臂機構(gòu)設計之間的聯(lián)系。由因認識最優(yōu)傳動。</p><p>　　具體的設計的理論和方法， 以及它們各自的應用事例將在以下介紹。</p><p>　　1 優(yōu)化傳動設計的建

44、立 </p><p>　　優(yōu)化傳動的設計一直是設計師改進傳輸效率和追求產(chǎn)量的最重要的索引的當中一個。曲柄搖臂機構(gòu)被廣泛應用在機械傳動中。如何改進工作效率和減少多余的功率損失直接地與滑移速度變化系數(shù)，搖臂的擺動角度和曲柄搖臂的比率有關(guān)系。這些參數(shù)的合理組合采用對機械效率和產(chǎn)量有重要作用, 這些主要體現(xiàn)在極小的傳輸角度上。</p><p>　　認識機械優(yōu)化傳動目的是找到極小的傳輸角度的最大值。

45、設計參數(shù)是適度地減少限制而且分開的合理優(yōu)化方法的結(jié)合。因此，完全限制領域的優(yōu)化傳動建立了。</p><p>　　以下步驟被采用在通常的設計方法。 首先，測量出搖臂的長度和搖臂的擺動角度的初始值。 然后滑移速度變化系數(shù)的值被定在允許的范圍內(nèi)。 同時，曲柄固定的鉸接座標可能被認為是任意值。</p><p>　　1.1 曲柄搖臂機構(gòu)桿的長度</p><p>　　由圖Fi

46、g.1，左弧是點被允許的領域。點的座標的選擇從點到點。</p><p><b>　　點的座標是</b></p><p><b>　　(1)</b></p><p><b>　　(2)</b></p><p>　　當，高度，在range(0 ，) 被逐漸增加。如果選的越小,計算精

47、度將越高。 是設計圓的半徑。是從到的距離。</p><p><b>　　(3)</b></p><p>　　計算弧和的長度，機械桿對應于點的長度是obtained[1,2 ] 。</p><p>　　1.2 極小的傳動角度 </p><p>　　極小的傳動角度 (參見Fig.2) 由equations[3]確定<

48、/p><p><b>　　(4)</b></p><p><b>　　(5)</b></p><p><b>　　(6)</b></p><p>　　由于——曲柄的長度(毫米)</p><p>　　——連桿的長度（毫米）</p><p&g

49、t;　　——搖臂的長度（毫米）</p><p>　　——機器的長度（毫米）</p><p>　　首先, 我們比較極小值和。 并且我們記錄所有的值大于或等于，然后選擇他們之間的最大值。</p><p>　　第二, 我們發(fā)現(xiàn)最大值對應于一個逐漸變小的范圍的任一個擺動的角度 (最大值是不同于擺動的角度和滑移速度變化系數(shù)) 。</p><p>　　最

50、后, 我們相似地慢慢縮小搖臂的長度。 因而我們能獲得最大值對應于桿的不同長度, 另外擺動的角度和滑移速度變化系數(shù)。</p><p>　　Fig.3成功的表達設計的目的。</p><p>　　它確定了無論是搖臂的長度,最大值出現(xiàn)的地點，只與搖臂的長度和機械的長度的比率/有關(guān), 當確定時。</p><p>　　2 設計方法</p><p>

51、;　　2.1 認識最優(yōu)傳動設計下滑移速度變化系數(shù)和搖臂的最大擺動的角度</p><p><b>　　設計步驟如下。</b></p><p>　　(1) 根據(jù)所給的和， 通常采取對發(fā)現(xiàn)極限角度的解釋。 桿的長度的對應的比率/是從圖Fig.3獲得的 。</p><p><b>　　(7)</b></p>&l

52、t;p>　　(2) 根據(jù)工作要求選擇搖臂的長度， 機械的長度是從比率/獲得的。</p><p>　　(3) 任意地選擇固定的鉸接的中心作為端點，并且做一個等腰三角形,令一條邊與搖臂的長度相等 (參見Fig.4)，令。 然后做， 連接，并且做角度。 因而增加了交點和。 最后， 畫三角形。</p><p>　　(4)以點作為圓的中心，為半徑畫圓弧。 弧交點在點。 點是曲柄的固定鉸接的中心

53、。</p><p>　　所以, 從曲柄的長度</p><p><b>　　(8)</b></p><p><b>　　并且連桿的長度</b></p><p><b>　　(9)</b></p><p>　　我們將獲得曲柄搖臂機構(gòu)包括，，和。因而優(yōu)化傳動加

54、工會在指定的情況下進行。</p><p>　　2.2 認識優(yōu)化傳動設計下?lián)u臂的長度(或機械的長度) 和滑移速度變化系數(shù)</p><p><b>　　我們采取以下步驟。</b></p><p>　　(1)根據(jù)選擇的確定桿的適當比率/。 此外，我們得出機械 (搖臂的長度) 。</p><p>　　(2) 搖臂對應的擺動的角

55、度可以從圖Fig.3 獲得。 并且我們計算出極限角度。</p><p>　　然后根據(jù)2.1重覆(3) 和(4)</p><p><b>　　3 設計例子</b></p><p>　　已知的條件是, 滑移速度變化系數(shù)和最大擺動角度。 提出曲柄搖臂機械優(yōu)化傳動圖方法設計方案。</p><p>　　首先， 通過公式(7)，我

56、們能計算出極限角度。 然后，我們通過表格Fig.3 查出以及和的值。</p><p>　　假設mm, 然后我們將得出mm。</p><p>　　然后, 做sketch(omitted) 。</p><p>　　最后, 算出桿的長度分別是 mm, mm, mm, mm.</p><p><b>　　極小傳動角度是</b>&

57、lt;/p><p>　　結(jié)果由計算可得 mm， mm， mm， mm。</p><p>　　在運用Auto CAD 制圖設計的情況, 可達到非常精確設計結(jié)果。</p><p><b>　　4結(jié)論</b></p><p>　　認識圖解法解答曲柄搖臂機構(gòu)的最優(yōu)傳動。這種方法是簡單和實用的。通常在機械設計中, 將0.1 毫米

58、作為最小有效精度是足夠的。</p><p><b>　　參考文獻</b></p><p>　　[1]Shigley J E,Uicher J J. Theory of Machines and Mechanisms[M].New York: McGraw-Hill Book Company,1980.</p><p>　　[2]天津大學. 機械