機械扳手的新設(shè)計外文文獻翻譯、中英文翻譯

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機械扳手的新設(shè)計 全聯(lián)盟的石油機械研究機構(gòu)解釋了基于不同設(shè)計的機械扳手傳遞扭矩的規(guī)律性,由此明確的一點就是通過扳手咬合施加力所產(chǎn)生的30—40KNm扭矩足夠用來傳遞更高的扭矩（>80KNm）。由此及彼，通過減少與扭矩成正比例管子上扳手顎的強度使得減少扳手的重量并且增加它們的可靠性成為可能。當(dāng)然，在產(chǎn)生夾緊力的初期我們必須保證扳手不能滑動。然而，傳統(tǒng)設(shè)計的機械扳手不能保證在扳手扭動過程中力變化的規(guī)律性?；诓煌O(shè)計下扳手強化機構(gòu)的特征表述在『1』 在腦海中我們應(yīng)該記住的就是扳手和管子的接觸在很大程度上與杠桿的旋轉(zhuǎn)角度α有關(guān)。然后，隨著扳手杠桿外力的增加，這個角度變得越來越小，從左到右加緊螺紋的整個過程見圖1 強化機構(gòu)最有效率的結(jié)合可以由聯(lián)動機構(gòu)和鉸鏈機構(gòu)得到。當(dāng)管子第一次被加緊的時候，鏈接機構(gòu)就開始工作了（曲線1）；它的工作區(qū)域由杠桿切縫的尺寸來限制，然后就轉(zhuǎn)到由四連桿機構(gòu)操作（曲線2）來確定最高強化系數(shù)。當(dāng)杠桿最末端那一面上升到最終夾緊連接時，強化機構(gòu)便從曲柄設(shè)計和通過不同長度桿來連接的連接桿機構(gòu)（曲線4）中得到收益。因此，在經(jīng)過考慮的這個例子中，扳手連接在管子上的強度開始的強化系數(shù)是i＝18—20，增至i＝42—45，并且以i＝12—13結(jié)束。 通過鉸鏈設(shè)計的扳手加緊過程以強化系數(shù)i>25（曲線2，3）結(jié)束。這也就解釋了為什么這些扳手會比聯(lián)動機構(gòu)和鉸鏈機構(gòu)的扳手重20％。 聯(lián)動機構(gòu)和鉸鏈機構(gòu)的另一個明顯的優(yōu)勢應(yīng)當(dāng)被提及：杠桿工作有著大范圍的旋轉(zhuǎn)角度：-15 度 < α < 30 度 。 我們調(diào)查的結(jié)果被用來作為計算有著轉(zhuǎn)矩極限的混合鉸鏈機構(gòu)KMB108—2112的基礎(chǔ)。這些扳手設(shè)計的特殊之處就在于在管子上扳手夾緊過程中減少了1/2或者1/3的強化系數(shù)。這就是依靠特殊轉(zhuǎn)矩極限應(yīng)用到最末端表面杠桿制動力的結(jié)果。 扳手控制聯(lián)動機構(gòu)和鉸鏈機構(gòu)。扭矩極限，楔形斷面的一部分，鉸接到扳手的加緊部分。在杠桿最末端表面有一個相同截面的架子作為扭矩極限的凹槽。 扳手開始的時候是由鉸鏈機構(gòu)來操控；當(dāng)動作限制在滑動槽的時候，就開始由鉸接四連桿機構(gòu)來控制，當(dāng)大約達到所能達到最大夾緊力的一般時，就由緊緊鑲嵌在扭矩限制槽里面的杠桿架來操控。 由于有著最末級扳手杠桿的制動影響，它所形成的夾緊部分的動力鏈接中兩杠桿大約等于三杠桿的效果，這一點與第五設(shè)計的強化系數(shù)（看圖1）相符。因此，在扳手KMB108—212中，一個合理的操作過程形成了：進程開始時大的強化系數(shù)（i<45度），在杠桿上小的驅(qū)動力（在扳手和管子之間獲得可靠的連接力）并且在得到大的驅(qū)動力時強化系數(shù)的減少（避免扳手過載）。應(yīng)變儀測量表明在那種情況下扳手鏈接的最大壓力被減少1/3到一半。 一個扳手原型KMB108—212，計算出額定轉(zhuǎn)矩為80KNm，被用207.5KNm的轉(zhuǎn)矩在the Azerbaidzhan Institute of Petroleum Machinery的測試臺上進行測試。扳手的效率沒有絲毫的削弱。在1985年KMB108—212扳手開始連續(xù)生產(chǎn)。然而，這些工具的全容量生產(chǎn)被扳手的不穩(wěn)定質(zhì)量限制了。  附錄D NEW DESIGN OF MACHINE WRENCH FOR DRILLING AND DRIVING PIPES At the All-Union Research Institute of Petroleum Machinery investigations were carried out revealing the regularities of the transmission of torque by machine wrenches based on different schemes. It was thereby established that the clamping forces of the jaws exerted by the machine wrench at torques of 30-40 kNm suffice for transmitting much higher torques (>80 kNm). In connection with that it therefore becomes possible to reduce the weight of the wrenches and increase their reliability by reducing the intensity of the clamping of the spanner jaws on the pipes in proportion to the increase of torque. Of course, at the initial stage of loading a clamping force has to be ensured that makes slippage of the wrench impossible. However, machine wrenches of traditional design do not ensure the necessary regularity of the change of forces in the gripping links of the wrench. The characteristics of the intensifying mechanisms of wrenches based on different schemes are presented in [i]. It should be borne in mind that contact of the wrench with the pipe occurs at large values of the angles of rotation ~ of the lever. Then, as the drawing force on the lever of the wrench increases, the angle ~ becomes smaller, i.e., the process of tightening the thread proceeds from right to left (see Fig. i). The most efficient combination of intensifying mechanisms can be obtained in wrenches with link gear and hinged mechanism. When the pipe is gripped first, the link mechanism acts (curve i); its zone of action is limited by the size of the slit in the lever. Then comes the transition to operation by the hinged four-link mechanism (curve 2) ensuring the highest coefficients of intensification. When the end face of the lever comes up against the final gripping link, intensification proceeds by the scheme of the crank and connecting rod mechanism (curve 4) with a connecting rod of variable length. Thus, in the case under consideration, tightening of the wrench links on the pipe begins at an intensification coefficient i = 18-20, which increases to i = 42-45, and ends with i = 12-13. With wrenches with hinged scheme the process of tightening ends with the coefficient of intensification i > 25 (curves 2, 3). This also explains why these wrenches weigh 20%[2] more than wrenches with link gear and hinged mechanism. Another substantial advantage of the link gear and hinged wrench should be mentioned: the wider range of working angles of rotation of the lever: -15 < e < 30 . For wrenches with the hinged scheme -5 < ~ < 18 ~because of the unreliable gripping with i < 18-20 at the onset of the process and the better operation of such wrenches by the scheme of the crank and connecting rod mechanism (curve3). The results of our investigations were made the basis for working out the multihinge machine wrench KMB 108-2112 for drilling pipes with torque limiter [3]. The special feature of the design of these wrenches consists in the reduction of the coefficient of intensification to one-half or one-third when the process of tightening the wrench on the pipe is concluded; this is the result of a braking force being applied to the end face of the lever by means of a special torque limiter. The wrench operates on the link gear and hinge mechanism scheme. The torque limiter, a part with a groove of wedge-shaped section, is hinged to the drawing link of the gripping part of the wrench. On the end face of the lever there is a rack with the same section as the groove of the torque limiter. The wrench begins to operate by the link gear scheme; when the motion is limited in the slide groove, it operates by the scheme of the hinged four-link mechanism, and when approximately half the maximal drawing force is attained, it operates by a scheme where the rack of the lever fits tightly into the groove of the torque limiter. Thanks to the effective braking of the wrench lever at the last stage, it forms with the drawing link of the gripping part a two-armed lever with the ratio of the arms approximately equal to three, which corresponds to the coefficient of intensification of the fifth scheme (see Fig. i). Thus in the wrench KMB 108-212 a rational combination of t]he operating regimes was effected: with large intensification (i <_ 45) at the beginning of the process with small drawing loads on the lever (to attain reliable cohesion between the wrench and the pipe) and with considerable reduction of the intensification when high drawing loads are attained (to prevent overloading of the wrench). Strain-gauge measurements showed that in that case the maximal stresses in the links of the wrench are reduced by one third to one half. A prototype of the wrench KMB 108-212, calculated for a nominal torque of 80 kN~ was tested on a test bench of the Azerbaidzhan Institute of Petroleum Machinery with a torque of 207.5 kN-m. The efficiency of the wrench was not impaired in any way. In 1985 series production of the wrenches KMB 108-212 started. However, production to full capacity of these tools is prevented by the unstable quality of cast blanks for the wrench.